Sliding bearing

FIELD: machine building.

SUBSTANCE: sliding bearing consists of half-round upper insertion and half-round lower insertion separated one from another. The upper insertion consists of the first oil-conducting channel for supply of lubricating material (motor oil) from outside into a gap between the bearing and a shaft and the second oil-conducting channel facilitating flow of oil in a circular direction of the bearing. The first channel includes an opening in internal circumference opened into internal circumference of the upper insertion. The upper insertion includes a part without an internal recess without a channel on a back side relative to the opening in internal circumference in the direction of shaft rotation. An auxiliary oil-conducting channel for oil release from the second channel is made in at least one of lower insertions and in a zone on the next side of the opening in circumference in the direction of rotation. The second channel runs to a front side in the direction of shaft rotation from the opening in internal circumference to the auxiliary channel. In the second version the upper insertion of the bearing included a front end part on the front side relative to the opening, while the lower insertion includes the back end part corresponding to the front part. The auxiliary channel is formed with channels of an unloading recess and a face made on the internal circular side of at least one of the front parts of the upper insertions and the back part of the lower insertion. Oil consumption of the face channel is bigger, than oil consumption of material in the channel of the unloading recess. Also there is claimed the facility of torque transfer and the engine containing the sliding bearing.

EFFECT: sliding bearing with decreased amount of lubricating material coming out of oil gap preventing damages caused with foreign impurities.

14 cl, 48 dwg

 

The technical field

The present invention relates to a sliding bearing, which is divided into a pair of semicircular bearing housings and holds a rotating shaft using a lubricant.

The level of technology

The sliding bearing is used, for example, as crankshaft bearing for holding a crankshaft of the engine. A typical crankshaft bearing configured by a combination of a semicircular upper bearing shell and a semi-circular lower bearing shell. The upper bearing is supplied with oil hole for supplying the engine oil from the main body of the engine oil clearance, which is the space between the indigenous bearing and radical necks of a cranked shaft, and a lubrication groove, allowing engine oil supplied into the oil clearance through the lubricating hole to pass around the main bearing.

However, because conventional main bearing oil groove is formed to connect one of the mating surfaces of the upper bearing shell on the other mating surface lubricity main bearing decreases when the number of engine oil, which comes from the oil gap increases. Publication laid patent application of Japan No. 2005-249024 RA is open crankshaft bearing, in which both ends of the lubrication grooves are formed so that they end at positions circumferentially inward from the mating surfaces.

However, in the engine equipped with the indigenous bearing described in the above publication, since a large number of impurities remains in the lubricating groove, there is a high probability of damage to the main bearing or bearing damage, the retaining rod. Thus there is a need in the main bearing, which reduces the amount of engine oil, which comes from the oil gap, preventing damage caused by impurities. This problem is not limited to the indigenous engine bearing, but may occur with any sliding bearing, which is divided into a pair of semicircular bearing housings and holds a rotating shaft using a lubricant.

Brief description of the invention

Accordingly, the present invention is the creation of a sliding bearing, which reduces the amount of lubricant that comes out of the oil clearance, preventing damage caused by impurities, and device transfer torque and engine, provided with a sliding bearing.

To solve the above problems and, in compliance and with the first object of the present invention created a slide bearing for holding a rotating shaft. The sliding bearing includes a semicircular main bearing shell and a semi-circular lower bearing shell, which can be separated from each other. Main bearing shell includes first masloprovody channel for introducing lubricant from the outside into the gap between the sliding bearing and the rotating shaft and the second masloprovody channel, allowing lubricant introduced between the sliding bearing and the rotating shaft to pass through in the radial direction of the sliding bearing. First masloprovody channel includes an inner bore that is open at the inner circumference of the main bearing. Main bearing shell includes part without internal boning, which is not formed masloprovody channel on the rear side relative to the holes in the inner circumference direction of rotation of the rotating shaft. Auxiliary masloprovody channel to release lubricant from the second maloprodaja channel outward from the axial direction of the sliding bearing is made in at least one lower bearing shell and in the field on the front side relative to the holes in the inner circumference of the main bearing in the direction of rotation of the rotating shaft.

In accordance with the second object of the present image is etenia created a slide bearing for holding a rotating shaft. The sliding bearing includes a semicircular main bearing shell and a semi-circular lower bearing shell, which can be separated from each other. Main bearing shell includes first masloprovody channel for introducing lubricant from the outside into the gap between the sliding bearing and the rotating shaft and the second masloprovody channel, allowing lubricant introduced between the sliding bearing and the rotating shaft to pass through in the radial direction of the sliding bearing. First masloprovody channel includes an inner bore in the inner circle, which is open on the inner circumference of the main bearing. Main bearing shell includes part without internal boning, which is not formed masloprovody channel on the rear side relative to the holes in the inner circumference direction of rotation of the rotating shaft. Main bearing shell includes a front end part located on the front side relative to the holes in the inner circumference direction of rotation of the rotating shaft, and the lower part of the bearing includes a rear end portion corresponding to the front end portion. Auxiliary masloprovody channel which connects the second masloprovody channel with a lateral bearing surface is calgene, made in the mating portion between the front end part of the main bearing and the rear end part of the lower bearing shell. Unloading recess, which forms masloprovody channel discharge hole chamfer that forms masloprovody channel chamfer is made on the inner circumference, at least one of the front end portion of the main bearing and the rear end portion of the lower bearing shell. Auxiliary masloprovody channel formed masloprovody discharge channel excavation and masloprovody channel chamfer. The relationship between the cross-sectional area maloprodaja channel chamfer and the cross-sectional area maloprodaja channel discharge grooves are set so that the lubricant consumption in macroprotodon channel chamfer is greater than the flow rate of the lubricant in macroprotodon the discharge channel excavation.

In accordance with a third object of the present invention a device for the transmission of torque, comprising a sliding bearing, which holds the rotating shaft, and main shaft, which rotates in one direction and serves as a rotating shaft. The device transmitting torque includes a sliding bearing according to any one of items 1 to 10 of the claims.

In accordance with the fourth object nastojasih the invention, received the engine, comprising a sliding bearing, which holds the rotating shaft and the crankshaft, which serves as a rotating shaft, held by the sliding bearing. The engine includes a sliding bearing according to any one of items 1 to 10 of the claims.

Brief description of drawings

Figure 1 is a perspective view of the engine including crankshaft bearing according to the first variant implementation of the present invention;

figure 2 is a view in cross section showing the cylinder and surrounding the design of the engine 1;

figure 3 is a front view showing the crankshaft of the engine of figure 1;

4 is a view in section, showing a radical neck crankshaft and environmental design of the engine 1;

figure 5(a) is a schematic view showing masloprovody channel for engine oil of the engine 1;

figure 5(b) is the enlarged view of the part indicated by circle 5b figure 5(a);

figure 5(c) is the enlarged view of the part indicated by circle 5c figure 5(a);

6 is a perspective view showing the state when the crankshaft bearing of the first variant embodiment of the invention is divided into the upper bearing and the lower bearing liner;

Fig.7 is a view in plan showing the upper bearing shell, is shown in Fig.6;

Fig - bottom view showing the upper bearing shell, pakatan the th figure 6;

Fig.9 is a front view showing the upper bearing shell, is shown in Fig.6;

figure 10 is a view in cross section showing the upper bearing shell, is shown in Fig.6;

11 is an enlarged view showing the portion indicated by the circle 11 of figure 10;

Fig enlarged view showing the portion indicated by the circle 12 figure 10;

Fig - view in plan, showing the internal circular surface of the lower bearing shell, is shown in Fig.6;

Fig is a front view showing the lower bearing shell, is shown in Fig.6;

Fig enlarged view showing the portion indicated by a circle 15 on Fig;

Fig enlarged view showing the portion indicated by the circle 16 on Fig;

Fig is a front view showing the upper shell of the first imaginary bearing;

Fig - bottom view showing the inner circular surface of the upper bearing shell, shown in Fig;

Fig is a front view showing the lower bearing of the first imaginary bearing;

Fig - view in plan, showing the internal circular surface of the lower bearing shell, shown in Fig;

Fig is a front view showing the upper bearing of the second imaginary bearing;

Fig - bottom view showing the inner circular surface of the upper vladychetsey, shown in Fig;

Fig is a front view showing the lower bearing of the second imaginary bearing;

Fig - view in plan, showing the internal circular surface of the lower bearing shell, shown in Fig;

Fig is a view in section, showing a radical neck crankshaft and environmental design of the engine shown in figure 1;

Fig enlarged view showing the portion indicated by the circle 26 on Fig;

Fig enlarged view showing the portion indicated by the circle 27 on Fig;

Fig - bottom view showing the inner circular surface of the upper bearing shell, shown in Fig;

Fig is a front view showing the upper bearing shell according to the comparative example, in which part of the upper bearing of the first variant embodiment of the invention modified;

Fig - bottom view showing the inner circular surface of the upper bearing shell, shown in Fig;

Fig - bottom view showing the inner circular surface of the upper bearing shell according to the second variant of implementation of the present invention;

Fig - bottom view showing the inner circular surface of the upper bearing shell according to the third variant of implementation of the present invention;

Phi is .33 - bottom view, showing the inner circular surface of the upper bearing shell according to the fourth variant of implementation of the present invention;

Fig - bottom view showing the inner circular surface of the upper bearing shell according to the fifth variant of implementation of the present invention;

Fig is a view in cross section showing the upper bearing shell according to the sixth variant of implementation of the present invention;

Fig - bottom view showing the inner circular surface of the upper bearing shell according to a seventh variant of implementation of the present invention;

Fig(a) is a view in cross section showing the upper bearing shell according to the eighth variant of implementation of the present invention;

Fig(b) is an enlarged view showing the portion indicated by a circle 37b on Fig(a);

Fig(a) is a view in cross section showing the upper bearing shell according to the ninth variant of implementation of the present invention;

Fig(b) is an enlarged view showing the portion indicated by a circle 38b on Fig(a);

Fig is a view in cross section showing the upper bearing shell according to the tenth variant of implementation of the present invention;

Fig is a view in cross section showing the upper bearing shell according to the eleventh variant of the implementation of the infusion is of his own invention;

Fig - bottom view showing the inner circular surface of the upper bearing main bearing shown in Fig;

Fig is a view in cross section showing the upper bearing shell according to the twelfth variant of implementation of the present invention;

Fig - view in plan, showing the internal circular surface of the lower bearing main bearing shown in Fig; and

Fig is a view in cross section showing the upper bearing shell according to the thirteenth variant implementation of the present invention.

The best way of carrying out the invention

The first variant of implementation of the present invention will now be described with reference to Fig 1-30. In the first embodiment of the invention the bearing corresponding to the present invention, applied to the main bearing 6, which holds the crankshaft 5 inline four-cylinder engine 1.

Engine design 1

1 shows a diagram illustrating the complete design of the engine 1. The engine 1 includes a cylinder block 3 to the combustion mixture of air and fuel, the cylinder head 11 for the location of the components of the valve mechanism, the crankcase 12 of the engine to position the crankshaft 5 and the pallet 13 Carter for keeping lubricant that t is aetsa engine oil 41 in the first embodiment of the invention. The engine 1 also includes a lubricating device 4 for supplying the engine oil 41 to each part of the engine 1.

Block 3 cylinder includes a cylinder 31 which is formed a combustion chamber that burns fuel mixture. Each cylinder 31 contains a piston 26, which performs reciprocating motion in accordance with the combustion of the combustible mixture. Around the crankshaft 5 wrapped the chain 25 timing for transmitting torque from the engine 1 to each device. Each cylinder 31 is attached to the connecting rod 27, which converts the reciprocating motion of the piston 26 during the rotation of the crankshaft 5. The head 11 of the cylinder provided with inlet valves 21, which selectively open and close the intake ports of the cylinders 31 relative to the combustion chambers and the intake Cam shaft 23, which drives the intake valves 21. The cylinder head 11 provided with exhaust valves 22, which selectively open and close the outlet opening of the cylinder 31 relative to the combustion chambers, and an exhaust Cam shaft 24, which causes the exhaust valves 22.

Lubricating device 4 includes an oil pump 42, which feeds the engine oil 41 that is contained in the bottom part of the tray 13 of the crankcase to each part of the engine 1. In addition, the lubricating device 4 includes a grid 43 masasabi the ka, which filters the engine oil 41 upstream of the inlet of the oil pump 42, and the oil filter 44, which filters the engine oil 41 further flow out of the oil pump 42. Oil pump 42 is driven torque of the crankshaft 5 is transmitted through the chain 25 timing.

Now with reference to figure 2-4 will be described a specific construction of the cylinder block 3 and the crankshaft 5. Figure 2 shows in cross section the construction of the cylinders 31 and surrounding the design of the engine 1 and the crankshaft 5. Figure 3 shows the design of the crankshaft 5 in the front view. Figure 4 shows in cross section the construction of the root of the neck 51 of the crankshaft 5 and the surrounding structure in the engine 1.

Block 3 cylinder provided with a first cylinder 31A, the second cylinder 31B, the third cylinder 31C and the fourth cylinder 31D as the cylinder 31. Block 3 cylinder provided with a first baffle 32A, the second baffle 32B, the third baffle 32C, the fourth baffle 32D and the fifth baffle 32E as dividing walls 32 to separate the crank chamber 30 with several cameras.

To each of the partition wall 32 attached to the cover 33 of the crank chamber. Each cover 33 of the crank chamber holds the crankshaft 5 are joint by the corresponding baffle 32. The first partition wall 32A is located at the position closest to the chain 25 timing among the dividing walls 32. The second partition wall 32B is in the position corresponding to the position between the first cylinder 31A and the second cylinder 31B. The third partition wall 32C is in the position corresponding to the position between the second cylinder 31B and the third cylinder 31C. The fourth partition 32D is in the position corresponding to the position between the third cylinder 31C and the fourth cylinder 31D. Fifth partition 32E is in position, the most remote from the circuit 25 timing among the dividing walls 32.

The crankshaft 5 includes, as indigenous 51 necks of a cranked shaft (rotating shaft), which is the core shaft, the first radical neck 51A of the crankshaft, the second radical neck 51B of the crankshaft, the third radical neck 51C of the crankshaft, the fourth radical neck 51D of the crankshaft and the fifth root neck 51E of the crankshaft. The crankshaft 5 also includes, as the connecting rod journals 52 for installation of connecting rods 27 of the first crank pin 52A, the second crank pin 52B, a third crank pin 52C and the fourth crank pin 52D. The crankshaft 5 also includes the shoulders 53 of the crank to connect the of indigenous necks 51 of the crankshaft and connecting rod journals 52, which are adjacent to each other. In addition, the shoulders 53 of the crank provided with a counterweight 54.

The first radical neck 51A of the crankshaft is located in the position closest to the circuit 25 timing among indigenous necks 51 of the crankshaft. The second fundamental neck 51B of the crankshaft is in the position corresponding to the position between the first cylinder 31A and the second cylinder 31B. The third radical neck 51C of the crankshaft is in the position corresponding to the position between the second cylinder 31B and the third cylinder 31C. The fourth radical neck 51D of the crankshaft is in the position corresponding to the position between the third cylinder 31C and the fourth cylinder 31D. Fifth radical neck 51E of the crankshaft is located in the position most remote from the circuit 25 timing among indigenous necks 51 of the crankshaft. The first connecting rod and the neck 52A is in a position corresponding to the first cylinder bore 31A. The second connecting rod neck 52B is in a position corresponding to the second cylinder 31B. The third connecting rod neck 52C is in a position corresponding to the third cylinder 31C. The fourth connecting rod neck 52D is in a position corresponding to the fourth cylinder 31D.

The cylinder block 3 includes a host crankshaft parts 34 for holding the crankshaft is Ala 5 with a possibility of rotation relative to the cylinder block 3, the first portion 34A for receiving the crankshaft, the second part 34B for receiving the crankshaft, the third portion 34C for receiving the crankshaft, the fourth part 34D for receiving the crankshaft and the fifth part 34E for receiving the crankshaft. The first part 34A for receiving the crankshaft is the part with the bearing for holding the first root of the neck 51A of the crankshaft, formed the first baffle 32A and associated lid 33 of the crank chamber. The second part 34B for receiving the crankshaft is the part with the bearing for holding the second cervical root 51B of the crankshaft, formed the second dividing wall 32B and the associated lid 33 of the crank chamber. The third portion 34C for receiving the crankshaft is the part with the bearing for holding the third root of the neck 51C of the crankshaft is formed of the third baffle 32C and the associated lid 33 of the crank chamber. The fourth part 34D for receiving the crankshaft is the part with the bearing for holding the fourth main journal 51D crankshaft, formed the fourth baffle 32D and the associated lid 33 of the crank chamber. The fifth part 34E for receiving the crankshaft is the part with the bearing for holding the fifth cervical root 51E crankshaft,formed the fifth baffle 32E and the associated lid 33 of the crank chamber.

Each portion 34 for receiving a crankshaft provided with an indigenous bearing 6 to reduce friction caused by the rotation of the crankshaft 5. That is, as a main bearing 6 is applied to the first crankshaft bearing 6A, which holds the first radical neck 51A of the crankshaft, the second crankshaft bearing 6B, which holds the second radical neck 51B of the crankshaft, the third crankshaft bearing 6C, which holds the third radical neck 51C of the crankshaft, the fourth crankshaft bearing 6D, which holds the fourth radical neck 51D of the crankshaft, and the fifth crankshaft bearing 6E, which holds the fifth root neck 51E of the crankshaft. Main bearings 6 are separable bearings, each of which is formed of the upper bearing 7 bearing, which is semicircular housing main bearing attached to appropriate the partition wall 32, and the lower bearing 8 bearing, which is semi-circular lower bearing liner attached to the corresponding cover 33 of the crank chamber. Each crankshaft bearing 6 is configured so that the gap (oil clearance 60) is formed between its inner circular surface and the outer circular surface 51Z main journal 51 in a state where the crankshaft bearing 6 holds for the for the neck 51 of the crankshaft. Oil groove bearing 32R for supplying the engine oil 41 in the third maloprodaja channel 35 of the main body to lubricating hole 77 (first masloprovody channel) of the upper bearing 7 bearing made in part with the bearing of each of the dividing walls 32.

Each rod 27 is formed main body 27A of the connecting rod, on which you have installed the corresponding piston 26, and the cover 27B of the connecting rod, which is attached to the end portion of the main body 27A of the connecting rod. Each rod 27 provided with a part 27C of the connecting rod with a bearing for mounting the connecting rod 27 on the crank shaft 5 for rotation relative to the crankshaft 5. Part 27C of the connecting rod with a bearing provided with a bearing 28 of the connecting rod to reduce friction caused by the rotation of the crankshaft 5. The bearing 28 of the connecting rod is a split bearing formed semicircular upper liner 28A of the bearing, which is attached to the main body 27A of the connecting rod, and a semicircular bottom liner 28B bearing, which is attached to the cover 27B of the rod. The bearing 28 of the connecting rod is configured so that between its inner circular surface and the outer circular surface of the crank pin 52 formed gap (oil clearance 29 (see figure 5)) in a state where the bearing 28 of the rod holds the crank pin 52.

The lubricant structure of the engine 1

As shown in figure 1, the cylinder block 3 has masloprovody channel 35 of the main body for supplying the engine oil 41 is discharged from the oil pump 42, to each part of the engine 1. Masloprovody channel 35 of the main body includes a first masloprovody channel 35A of the main body, the second masloprovody channel 35B of the main body and the third masloprovody channels 35 of the main body. First masloprovody channel 35A of the main body is masloprovody channel, which feeds the engine oil 41 that is outside of the cylinder block 3, the second masloprovody channel 35B of the main body. Second masloprovody channel 35B of the main body is masloprovody channel to distribute the engine oil 41, filed on the first macroprolactinoma channel 35A of the main body, the third masloprovody channels 35 of the main body. Third masloprovody channels 35 of the main body are masloprovody the channels for supplying the engine oil 41, filed on the second macroprolactinoma channel 35B of the main body, to indigenous bearings 6 receiving the crankshaft parts 34.

As shown in figure 3, the crankshaft 5 is masloprovody channel 55 of the crankshaft. Masloprovody channel 55 of the crankshaft takes the engine oil 41 from the oil clearance 60 indigenous on the bearings 6 to the oil clearances 29 bearing rods 28. Masloprovody channel 55 of the crankshaft includes a first masloprovody channel 55A of the crankshaft, the second masloprovody channel 55B of the crankshaft, the third masloprovody channel 55C of the crankshaft and the fourth masloprovody channel 55D of the crankshaft. Each masloprovody channel 55 of the crankshaft includes an input masloprovody channel 55J, allowing engine oil 41 from the oil clearance 60 of the respective main bearing 6 to go in the root of the neck 51, and the output masloprovody channel 55P, allowing engine oil 41 from the input maloprodaja channel 55J take place in the oil gap 29 of the corresponding bearing of the connecting rod 28.

First masloprovody channel 55A of the crankshaft includes a first input masloprovody channel 55JA, which is the first root neck 51A of the crankshaft, and the first output masloprovody channel 55PA, which is located in the corresponding shoulder 53 of the crank and the first connecting rod and the neck 52A. Second masloprovody channel 55B of the crankshaft includes a second input masloprovody channel 55JB, which is located in the second radical neck 51B of the crankshaft, and the second output masloprovody channel 55PB, which is located in the corresponding shoulder 53 of the crank and the second crank neck 52B. Third masloprovody channel 55C crankshaft includes a third input Malop Obvodny channel 55JC, which is located in the third root-51C the crankshaft, and a third output masloprovody channel 55PC, which is located in the corresponding shoulder 53 of the crank and the third connecting rod neck 52C. Fourth masloprovody channel 55D crankshaft includes a fourth input masloprovody channel 55JD, which is located in the fourth radical neck 51D of the crankshaft, and the fourth output masloprovody channel 55PD, which is located in the corresponding shoulder 53 of the crank and the fourth connecting rod neck 52D.

Now with reference to figure 5 will be described the flow of the engine oil 41 to lubricate the crankshaft 5. Figure 5 schematically shows masloprovody channel 35 of the main body and masloprovody channel 55 of the crankshaft.

Engine oil 41 that is contained in the pallet 13 Carter, absorbed in the oil pump 42 through a grid 43 maslosborny. Engine oil 41 is discharged from the oil pump 42 and held in the first masloprovody channel 35A of the main body through the oil filter 44. Engine oil 41 of the first maloprodaja channel 35A of the main body passes through the second macroprolactinoma channel 35B of the main body in the third masloprovody channels 35 of the main body. Engine oil 41 of each of the third maloprodaja channel 35 of the main body is held in the oil clearance 60 via the lubricating groove 32R bearing according to the respective partition walls 32 and lube hole 77 of the corresponding main bearing 6. Engine oil 41 from the oil clearance 60 is held in a radical neck 51 of the crankshaft through the input of the corresponding input maloprodaja channel 55J. Engine oil 41 from the input maloprodaja channel 55J takes place in the oil gap 29 of the respective bearing 28 of the connecting rod through the corresponding input masloprovody channel 55P.

The design of the main bearing 6

The specific design of the main bearing 6 will be described with reference to Fig.6-16. Figure 6 shows the state in which one of the bearing 6 is divided into the upper bearing 7 bearing and the lower bearing liner 8. 7 shows the design of the upper bearing 7 bearing in the top view. On Fig shows the structure of the upper bearing 7 bearing in the form below. Figure 9 shows the structure of the upper bearing 7 bearing in the front view. Figure 10 shows a sectional view of the upper bearing 7 bearing, made in the radial direction. Figure 11 and 12 shows a partial magnified view shown in figure 10. On Fig shows the construction of the lower bearing 8 bearing in the front view. On Fig shows the construction of the lower bearing 8 bearing in the front view. On Fig and 16 shows a partial magnified view shown in Fig. In addition, in each of the drawings, the dimensions of the chamfers and the discharge grooves is increased in comparison with others what blastema main bearing 6.

As shown in Fig.6, crankshaft bearing 6 is formed by a combination of the upper bearing 7 bearing and the lower bearing liner 8. More specifically, the inserts 7, 8 of the bearing are combined in such a way that a pair of mating surfaces 72 of the upper bearing 7 bearing comes in contact with a pair of mating surfaces 82 of the lower bearing liner 8. Further, when making reference to any provision of each of the upper bearing 7 bearing and the lower bearing liner 8, the forward direction in the direction of rotation of the crankshaft 5 from the original position in the radial direction of each of the inserts 7, 8 of the bearing is referred to as rotation in the direction AF forward and backward in the direction of rotation of the crankshaft 5 from the original position in the radial direction of each of the inserts 7, 8 of the bearing is referred to as the direction of the AR rotation back.

As shown in Fig.7-12, in the upper liner 7 bearing used lubricating hole 77, allowing engine oil 41 to pass between the outer circumference and the inner circumference of each main bearing 6, and the oil groove 78 functioning as a second masloprovody channel and allowing engine oil 41 to go in a circular direction along the inner circumference of the main bearing 6. On each of the pair of end parts 71 in rnego liner 7 bearing on the inner circular surface 75 is handling the recess 73. Unloading recesses 73 permit deformation of the end parts 71, caused by the combination of the upper bearing 7 bearing and the lower bearing liner 8. On one of the edges of each mating surface 72 on the inner circumference of the upper bearing 7 bearing made chamfer 74. Between the end parts 71 in the radial direction is formed intermediate section 7E of the liner to form a film (lubricating film) engine oil 41 for holding the root of the neck 51 of the crankshaft. The intermediate section 7E of the liner is provided with a part 7EF with an internal recess including a lubrication groove 78, which is masloprovody channel for the engine oil 41, and part 7ER without internal boning, which is not formed masloprovody channel.

The mating surface 72 of the end portion 71 (the front end portion 71F) in the direction AF forward referred to as the mating surface is about 72 front side, and the mating surface 72 of the end portion 71 (the rear end portion 71R) in the direction of the AR ago referred to as the mating surface 72R of the rear side. Unloading the recess 73 of the front end portion 71F referred to as the unloading recess 73F front side. Chamfer 74 front end portion 71F referred to as a chamfer 74F front side. Unloading the recess 73 of the rear end portion 71R referred to as & other fix spot labeling the internal notch 73R back. Chamfer 74 of the rear end portion 71R is referred to as a chamfer 74R back.

The discharge grooves 73 are formed so that their depth is maximum at the mating surfaces 72. The discharge grooves 73 are formed so that their depth gradually decreases from the mating surfaces 72 to the middle part of the upper bearing 7 bearing in the radial direction, and the depth becomes zero at the position most remote from the mating surfaces 72 in the radial direction. The depth of discharge of notches 73 refers to the magnitude of the cut inner circular surface 75 in the radial direction.

Chamfer 74 is held in the axial direction of each main bearing 6 from one of the side surfaces 76 of the upper bearing 7 bearing to the other side surface 76. Chamfer 74F front passes so that it connects the lubricating groove 78 with side surfaces 76.

Lubricating hole 77 passes through the upper bearing 7 bearing in the radial direction and connects the hole 77A in the inner circle with a hole 77B in the outer circle. Lubricating hole 77 is located on the side in the direction of the AR back from the centre (center in the circumferential direction) of the upper bearing 7 bearing in the radial direction.

Oil groove 78 extends from the area between the hole 77A in NR the inner circle and part 7ER without internal undercut mating surfaces is about 72 front side. More specifically, when the end part 78 lubricating grooves in the direction AF forward referred to as the front end portion 78F, and the end part of the lubrication grooves 78 in the direction of the AR ago referred to as the rear end portion 78R, the front end portion 78F opened outward from the upper bearing 7 bearing on the mating surface of ABOUT 72 of the front side and the rear end portion 78R ends immediately before part 7ER without internal undercut. Oil groove 78 passes for connection lubrication holes 77 to the relief notch 73F front side and a facet 74F front side. The center in the radial direction (center ST. circumferential lubricating groove 78 is located on the side in the direction AF forward from the centre of SA along the circumference of the upper bearing 7 bearing. Oil groove 78 is formed by a pair of side surfaces 78A lubricating groove and a bottom surface 78B lubricating groove, which connects the side surfaces 78A lubricating grooves. Side surfaces 78A lubricating grooves are formed so that they pass from the radially outer side of the main bearing 6 to the radially inner side of the main bearing 6 and related to each other. The width of the lubricating groove 78 is less than the radius of the lubrication holes 77 (radius of the hole 77A in the inner circle). The depth of the lubricating groove 78 is abolla in the centre of ST along the circumference and gradually decreases from the center of ST along the circumference of the rear end portion 78R. The depth of the lubricating groove 78 is set so that it becomes zero at the rear end portion 78R. The depth of the lubricating groove 78 is set so that it gradually decreases from the center of ST along the circumference of the front end portion 78F.

Part 7ER without internal undercut is located on the side in the direction of the AR back from the hole 77A in the inner circle and on the side in the direction AF forward from the discharge 73R notch rear. That is, in the upper liner 7 of the bearing area between the rear end part 78R lubricating grooves 78 and unloading excavation 73R back complies with part 7ER without internal undercut.

As shown in Fig, the upper bearing 7 bearing subdivided in the radial direction as follows. That is, the upper bearing 7 bearing can be divided into the first beveled section 7A, in which the chamfer 74F front side, the second beveled section 7B, in which the chamfer 74R rear side, the first discharge section 7C, which made unloading recess 73F front side, the second discharge section 7D, which made unloading recess 73R rear side, and an intermediate section 7E of the liner, which made the hole 77A in the inner circumference of the lubrication holes 77. The inner cylindrical surface 75 of the upper bearing 7 bearing may be modernization to modernization is Lena as follows on the basis of units of the upper bearing 7 bearing. That is, the internal circular surface 75 is divided into a bottom surface 78B lubricating grooves, the inner circular surface 75A of the first swing section 7A, excluding the bottom surface 78B lubricating grooves, the inner circular surface 75B of the second beveled section 7B, the inner circular surface 75C of the first discharge section 7C, excluding the bottom surface 78B lubricating grooves, the inner circular surface 75D second discharge section 7D and the inner circular surface 75E intermediate section 7E of the liner, excluding the bottom surface 78B lubricating grooves.

As shown in Fig-16, the discharge recess 83 is performed on each of the pair of end portions 81 of the lower bearing 8 bearing on the inner circular surface 85. Unloading recesses 83 allow deformation of the terminal parts 81, caused by Association of the upper bearing 7 bearing and the lower bearing liner 8. Chamfer 84 is made on one of the edges of each mating surface 82 located on the inner circumference of the lower bearing liner 8. The intermediate section 8E of the liner to form a film (lubricating film) engine oil 41 that is suitable for holding the root of the neck 51 of the crankshaft, is located between the end portions 81 in the radial direction.

The mating surface 82 of the end portion (the front to zeway part 81F) in the direction AF forward referred to as the mating surface 82F front side, and the mating surface 82 of the end portion (rear end portion 81R) in the direction of the AR ago referred to as the mating surface 82R back. Unloading the notch 83 of the front end portion 81F referred to as the unloading recess 83F front side. Chamfer 84 front end portion 81F is referred to as a chamfer 84F front side. Unloading the notch 83 of the rear end portion 81R referred to as the unloading recess 83R back. Chamfer 84 of the rear end portion 81R is referred to as a chamfer 84R back.

Unloading recesses 83 are formed so that their depth is greatest at the mating surfaces 82. Unloading recesses 83 are formed so that their depth gradually decreases from the mating surfaces 82 to the middle part of the lower bearing liner 8 in the radial direction and the depth becomes zero at the position most remote from the mating surfaces 82 in the radial direction. The depth of discharge of notches 83 refers to the magnitude of the cut on the inner circular surface 85 in the radial direction. Chamfer 84 are held in the axial direction of each main bearing 6 from one of the side surfaces 86 of the lower bearing liner 8 to the other side surface 86.

As shown in Fig, the lower bearing liner 8 can be subdivided in Rugova direction as follows. The lower bearing liner 8 is divided into a first beveled section 8A, in which the chamfer 84F front side, the second beveled section 8B, in which the chamfer 84R rear side, the first discharge section 8C, which made unloading recess 83F front side, the second discharge section 8D, which made unloading recess 83R rear side, and an intermediate section 8E of the liner, which is made between the first discharge section 8C and the second discharge section 8D. The inner circular surface 85 of the lower bearing liner 8 may be subdivided as follows on the basis of units of the lower bearing liner 8. That is, the internal cylindrical surface 85 is divided into an inner circular surface 85A of the first swing section 8A, the inner circular surface 85B of the second beveled section 8B, the inner circular surface 85C of the first discharge section 8C, the inner circular surface 85D second discharge section 8D and the inner circular surface 85E intermediate section 8E of the insert.

Oil clearance main bearing

In the engine 1 oil clearance 60 is formed between each indigenous bearing 6 and the corresponding radical neck 51 of the crankshaft, as radical neck 51 of the crankshaft is held by indigenous bearing 6. T is there oil clearance 60 is formed between the inner circular surfaces 75, 85 upper and lower inserts 7, 8 of the bearing and the outer circular surface 51Z root of the neck 51.

As a Preface to the description of the details of the oil clearance 60 will be described imaginary crankshaft bearing (first imaginary bearing 100, shown in Fig-20, and imaginary crankshaft bearing (second imaginary bearing 200)shown in Fig-24. On Fig shows the structure of an upper liner 110 of the bearing of the first imaginary bearing 100 in the front view. On Fig shows the structure of an upper liner 110 of the bearing in the form below. On Fig shows the construction of the lower liner 120 bearing the first imaginary bearing 100 in the front view. On Fig shows the construction of the lower liner 120 of the bearing in the top view. On Fig shows the structure of an upper pad 210 of the bearing of the second imaginary bearing 200 in the front view. On Fig shows the structure of an upper pad 210 of the bearing in the form below. On Fig shows the construction of the lower liner 220 of the bearing of the second imaginary bearing 200 in the front view. On Fig shows the construction of the lower liner 220 of the bearing in the top view. The components of the bearing 100, 200 that are similar to components of the main bearing 6, assigned to the same reference position.

The first imaginary bearing 100 has the same design is the construction, as crankshaft bearing 6, except that the discharge grooves 73, 83, chamfers 74, 84 and the oil groove 78 is not performed. The second imaginary bearing 200 has the same construction as crankshaft bearing 6, except that the chamfers 74, 84 and the oil groove 78 is not executed.

The design of the first imaginary bearing 100 becomes similar in design to the second imaginary bearing 200 by performing the unloading recesses 73F front side and the discharge grooves 73R back on top liner 110 of the bearing and the execution of the discharge grooves 83F front side and the discharge grooves 83R back on the bottom liner 120 of the bearing. Mass remote from the first imaginary bearing 100 for forming the discharge grooves 73, 83 on the liner 100, defined as follows. There is a lot removed from the top of the liner 110 of the bearing in the formation of the discharge grooves 73F front side on the upper liner 110 bearing, referred to as the first discharge mass 111 front side. The mass removed from the top of the liner 110 of the bearing in the formation of the discharge grooves 73R back on top liner 110 bearing, referred to as the first discharge mass 112 back. The mass removed from the bottom of the liner 120 of the bearing during the formation of the discharge in the capacious 83F front side on the lower liner 120 of the bearing, referred to as the second discharge mass 121 front side. The mass removed from the bottom of the liner 120 of the bearing in the formation of the discharge grooves 83R back on the bottom liner 120 bearing, referred to as the second discharge mass 122 back.

The design of the second imaginary bearing 200 is the same as the design of the main bearing 6, the execution result of the chamfer 74F front side bevel 74R back, the lubrication grooves 78 on the upper pad 210 of the bearing and bevel 84F front side and chamfer 84R back on the bottom liner 220 of the bearing. Mass remote from the bearing 200 by forming chamfers 74, 84 on the second imaginary bearing 200 is set as follows. There is a lot removed from the top of the liner 210 of the bearing by forming the chamfer 74F front side on the upper pad 210 of the bearing, referred to as the first mass 211 chamfer the front side. The mass removed from the top of the bearing 210 by forming the chamfer 74R back on top liner 210 bearing, referred to as the first mass 212 chamfer the back side. The mass removed from the bottom of the liner 220 of the bearing by forming the chamfer 84F front side on the lower liner 220 of the bearing, referred to as the second mass 221 chamfer the front side. The mass is remote from the bottom of the liner 220 of the bearing by forming the chamfer 84R back on the bottom liner 220 of the bearing, referred to as the second mass 222 chamfer the back side.

Details of the oil clearance 60 each main bearing 6 will be described with reference to Fig-28. On Fig shown in cross-section design in a state where the radical neck 51 of the crankshaft is held by indigenous bearings 6, 100, 200, and in a state where the centers of the bearing 6, 100, 200 aligned with the center main journal 51. In each of the drawings, the dimensions of the main bearing 6 and the oil clearance 60 is increased relative to the root of the neck 51.

Oil clearance 60 each main bearing 6 in General divided into the first zone of the U formed between the upper bearing 7 bearing and radical neck 51 of the crankshaft, and a second area L, formed between the lower bearing liner 8 and radical neck 51 of the crankshaft.

The first zone U further subdivided as follows. That is, the first area U is divided into zone UA corresponding to the first discharge mass 111 front side, area UB corresponding to the first discharge mass 112 rear side, the area UC corresponding to the first discharge mass 211 of the front side, area UD corresponding to the first unloading the weight of the rear side 212, the area UE, formed between the outer circular surface 51Z root of the neck 51 and the inner circular surface 75 of the upper liner 110 bearing the first imaginary bearing 100, and the area UF corresponding to the lubricating groove 78. Area UE further subdivided as follows. That is, the area of the UE is divided into zone UE1 corresponding to the first beveled section 7A and the first discharge section 7C, the area UE2 corresponding to the second beveled section 7B and the second discharge section 7D, and the area UE3, the corresponding intermediate section 7E of the bearing shell. As shown in Fig, area UE3 further subdivided as follows. That is, the zone UE3 is divided into zone UE31 corresponding lubricating groove 78, and the area UE32, corresponding to the zone where the oil groove 78 is not generated.

Area L, the corresponding lower bearing liner 8, further subdivided as follows. That is, the zone L is divided into the LA area corresponding to the second discharge mass 121 front side, area LB corresponding to the second discharge mass 122 back, zone LC corresponding to the second mass 221 chamfer the front side, area LD corresponding to the second mass 222 chamfer the back side, the zone LE, formed between the outer circular surface 51Z root of the neck 51 and the inner circular surface 75 of the lower liner 120 bearing the first imaginary bearing 100. The zone LE is further subdivided as follows. That is, the zone LE is divided into zone LE1 corresponding to the second beveled section 8B and the second discharge section 8D,zone LE2, corresponding to the first beveled section 8A and the first discharge section 8C, and the LE3 area corresponding to the intermediate section 8E of the bearing shell.

Oil clearance 60 is masloprovody channel 61 of the bearing, which makes the pressure of the oil film necessary to properly maintain the rotation of the main journal 51, masloprovody channel 62 in the groove, having a significantly lower pressure of the oil film in comparison with masloprovody channels 61 of the bearing facing the groove masloprovody channel 63, masloprovody end channel 64, masloprovody channel 65 unloading excavation and masloprovody channel 66 chamfer. More specifically, masloprovody channels are formed as follows. Further, the inner cylindrical surface 75 of the first imaginary bearing 100, corresponding to the first beveled section 7A and the first discharge section 7C of the upper bearing 7 bearing, referred to as an imaginary inner circular surface 101. The inner cylindrical surface 75 of the first imaginary bearing 100, the corresponding second beveled section 7B and the second discharge section 7D of the upper bearing 7 bearing, referred to as an imaginary inner circular surface 102. The inner cylindrical surface 75 of the first imaginary bearing 100, corresponding to the first beveled section 8A of the first discharge section 8C of the lower bearing liner 8, referred to as an imaginary inner circular surface 103. The inner cylindrical surface 75 of the first imaginary bearing 100, the corresponding second beveled section 8B and the second discharge section 8D of the lower bearing liner 8 is referred to as an imaginary inner circular surface 104. The inner cylindrical surface 75 of the second imaginary bearing 200 corresponding to the first beveled section 7A and the first discharge section 7C of the upper bearing 7 bearing, referred to as an imaginary inner circular surface 201. The inner cylindrical surface 75 of the second imaginary bearing 200 corresponding to the second beveled section 7B and the second discharge section 7D of the upper bearing 7 bearing, referred to as an imaginary inner circular surface 202. The inner cylindrical surface 75 of the second imaginary bearing 200 corresponding to the first beveled section 8A and the first discharge section 8C of the lower bearing liner 8 is referred to as an imaginary inner circular surface 203. The inner cylindrical surface 75 of the second imaginary bearing 200 corresponding to the second beveled section 8B and the second discharge section 8D of the lower bearing liner 8 is referred to as an imaginary inner circular surface 204.

Masloprovody channel modernica includes first masloprovody channel 61A of the bearing, located between the inner circular surface 75E intermediate section 7E of the liner top liner 7 of the bearing and the outer circular surface 51Z main journal 51, and the second end masloprovody channel 61B located between the inner circular surface 85E intermediate section 8E of the lower bearing liner 8 and the outer circular surface 51Z root of the neck 51.

Masloprovody end channel 64 includes a first masloprovody end channel 64A located between the imaginary inner circular surfaces 101, 104 of the first imaginary bearing 100 and the external circular surface 51Z main journal 51, and the second masloprovody end channel 64B located between the imaginary inner circular surfaces 102, 103 of the first imaginary bearing 100 and the external circular surface 51Z root of the neck 51.

Masloprovody channel 65 of the discharge recess includes first masloprovody channel 65A unloading recesses located between an imaginary inner circular surface 201, 204 second imaginary bearing 200 and imaginary inner circular surfaces 101, 104 of the first imaginary bearing 100, and the second masloprovody channel 65B unloading recesses located between the imaginary inner circular surfaces 202, 203 second is th imaginary bearing 200 and imaginary inner circular surfaces 102, 103 first imaginary bearing 100.

Masloprovody channel 66 chamfer includes a first masloprovody channel 66A chamfer and the second masloprovody channel 66B chamfer. First masloprovody channel 66A chamfer located between the imaginary inner circular surface 204 of the second imaginary bearing 200 and the inner circular surfaces 75A, 85B first beveled section 7A of the upper bearing 7 bearing and the second beveled section 8B of the lower bearing liner 8 and the imaginary inner circular surface 201. Second masloprovody channel 66B chamfer located between the inner circular surfaces 75B, 85A second beveled section 7B of the upper bearing 7 bearing and the first beveled section 8A of the lower bearing liner 8 and imaginary inner circular surfaces 202, 203 second imaginary bearing 200. Masloprovody channel 66 chamfer corresponds to the auxiliary macroprolactinoma passage in the adjacent part of the main bearing 6.

Masloprovody channels can be described as follows based on the subdivided as described above, areas of the oil clearance 60. That is, the first masloprovody channel 61A of the bearing formed by the area UE32. Second masloprovody channel 61B of the bearing formed by the LE3 area. Masloprovody channel 62 in the groove formed by the area UF. Converts the output to the groove masloprovody channel 63 formed area UE31. First masloprovody end channel 64A formed area UE1 and area LE1. Second masloprovody end channel 64B formed area UE2 and LE2 area. First masloprovody channel 65A discharge grooves formed area UA and LA area. Second masloprovody channel 65B discharge grooves formed area UB and area LB. First masloprovody channel 66A chamfer formed area UC and area LC. Second masloprovody channel 66B chamfer formed area UD and area LD.

The flow of engine oil in the oil clearance

Now with links to Fig-28 will be described the flow of the engine oil 41 in the oil clearance 60 each main bearing 6.

The force that acts on the direction of the AR back to the direction AF forward, attached to the engine oil 41 in the oil clearance 60 in accordance with the rotation of the crankshaft 5. Thus, in the oil clearance 60 is a big part of the engine oil 41 passes from the direction of the AR back in the direction AF forward. Engine oil 41 passes through masloprovody channels 61-65 of the oil clearance 60 is as follows.

Engine oil 41 of maloprodaja channel 62 within the groove goes in facing the groove masloprovody channel 63, the first masloprovody channel 65A unloading recesses or first masloprovody channel 66A chamfer. Engine oil 41 of facing the groove maloprodaja channel 63 is held in the first maslar the water channel 61A of the bearing, first masloprovody end channel 64A or input masloprovody channel 55J. Engine oil 41 of the first maloprodaja channel 61A of the bearing is held in the first masloprovody end channel 64A. Alternatively, the engine oil 41 of the first maloprodaja channel 61A of the bearing comes out of the oil clearance 60 via the side surface 76 of the upper bearing 7 bearing. Engine oil 41 of the first maloprodaja end of the channel 64A passes in the first masloprovody channel 65A unloading recess or the second masloprovody channel 61B of the bearing shell. Alternatively, the engine oil 41 of the first maloprodaja end of the channel 64A comes out of the oil clearance 60 or through the side surface 76 of the upper bearing 7 bearing, or through the side surface 86 of the lower bearing liner 8. Engine oil 41 of the first maloprodaja channel 65A unloading excavation takes place in the first masloprovody channel 66A chamfer or first masloprovody end channel 64A. Alternatively, the engine oil 41 of the first maloprodaja channel 65A discharge notches out of the oil clearance 60 or through the side surface 76 of the upper bearing 7 bearing, or through the side surface 86 of the lower bearing liner 8. Engine oil 41 of the first maloprodaja channel 66A chamfer extends from Mac is anago gap 60 or through the side surface 76 of the upper bearing 7 bearing, or through the side surface 86 of the lower bearing liner 8.

Alternatively, the engine oil 41 of the first maloprodaja channel 66A chamfer held in the first masloprovody channel 65A discharge grooves. Engine oil 41 in the second maloprodaja channel 61B of the bearing is held in the second masloprovody end channel 64B. Alternatively, the engine oil 41 in the second maloprodaja channel 61B of the bearing comes out of the oil clearance 60 via the side surface 86 of the lower bearing liner 8. Engine oil 41 in the second maloprodaja end-channel 64B is held in the second masloprovody channel 65B unloading recesses or first masloprovody channel 61A of the bearing shell. Alternatively, the engine oil 41 in the second maloprodaja end-channel 64B comes out of the oil clearance 60 or through the side surface 86 of the lower bearing liner 8, or through the side surface 76 of the upper bearing 7 bearing. Engine oil 41 in the second maloprodaja channel 65B unloading excavation takes place in the second masloprovody channel 66B chamfer or second masloprovody end channel 64B. Alternatively, the engine oil 41 in the second maloprodaja channel 65B discharge notches out of the oil clearance 60 or through the side surface 86 of nizhnegorskaya 8 bearing, or through the side surface 76 of the upper bearing 7 bearing. Engine oil 41 in the second maloprodaja channel 66B chamfer comes out of the oil clearance 60 or through the side surface 86 of the lower bearing liner 8, or through the side surface 76 of the upper bearing 7 bearing. Alternatively, the engine oil 41 in the second maloprodaja channel 66B chamfer is the second masloprovody channel 65B unloading excavation.

In the main bearing 6 the ratio between the square of the SA section of the first maloprodaja channel 65A unloading excavation and the area of the TA section of the first maloprodaja channel 66A chamfer and the ratio between the area SB of the second section maloprodaja channel 65B unloading excavation and the area of the TB section of the second maloprodaja channel 66B bevel is set, as shown in the following positions (A) and (B). More specifically, the area SA of the cross-section area of the TA section, the area SB of the cross section and the area of the TB section presents the squares of the section as follows. That is, the area SA of the first section maloprodaja channel discharge grooves 65A corresponds to the sum of the cross-sectional area of the first discharge mass 111 front side in the radial direction of the main bearing 6 and the cross-sectional area of the second discharge mass 122 of the rear side in the radial direction of the main bearing 6. The area of the T-section of the first maloprodaja channel 66A chamfer corresponds to the sum of the cross-sectional area of the first mass 211 chamfer the front side in the radial direction of the main bearing 6 and the area AR of the cross-section of the second mass 222 chamfer the back side in the radial direction of the main bearing 6. The area SB of the second section maloprodaja channel 65B unloading recesses corresponds to the sum of the cross-sectional area of the first discharge mass 112 rear side in the radial direction of the main bearing 6 and the cross-sectional area of the second discharge mass 121 front side in the radial direction of the main bearing 6. The area of the TB section of the second maloprodaja channel 66B chamfer corresponds to the sum of the cross-sectional area of the first mass 212 chamfer the back side in the radial direction of the main bearing 6 and the cross-sectional area of the second mass 221 chamfer the front side in the radial direction of the main bearing 6.

(A) with respect to the first maloprodaja channel 65A discharge grooves and the first maloprodaja channel 66A chamfer, the ratio between the square of the SA section of the first maloprodaja channel discharge grooves 65A and area TA of the first section maloprodaja channel 66A chamfer set so that the flow rate of the engine oil 41 (flow rate QB in the first chamfer), which comes out of the oil clearance 60 via the first masloprovody channel 66A chamfer is greater than the flow rate of the engine oil 41 (flow rate QA in the first discharge groove), which comes out of the oil clearance 60 via the first masloprovody canola discharge grooves. The ratio between the square of the SA section and area TA of the section specified by setting the relationship between the size (formed by the length and depth) of the discharge grooves 73F front side and chamfer dimension 74F front side, and the relationship between size (formed by the length and depth) of the discharge grooves 83R back and chamfer dimension 84R rear side such that the first flow rate QB in the chamfer is greater than the first flow rate QA in the discharge slot.

(B) for the second maloprodaja channel 65B discharge grooves and the second maloprodaja channel 66B chamfer, the ratio between the area SB of the second section maloprodaja channel 65B unloading excavation and the area of the TB section of the second maloprodaja channel 66B chamfer installed so that the flow rate of the engine oil 41 (the second flow QD in the facet), which comes out of the oil clearance 60 via the second masloprovody channel 66B chamfer is greater than the flow rate of the engine oil 41 (second flow rate QC in the discharge recess), which comes out of the oil clearance 60 via the second masloprovody channel 65B of the discharge recess. The ratio between the square of the SB section and the area of TB section is specified by setting the relationship between the size (formed by the length and depth) of the discharge grooves 73R back and chamfer dimension back 74R, and the relationship between size (formed of protag is the oneness and depth) of the discharge grooves 83F front side and chamfer dimension 84F front side is the second flow rate QD of the chamfer is greater than the second flow rate QC in the discharge slot.

This variant embodiment of the invention has the following advantages.

(1) Each crankshaft bearing 6 provided with a part 7ER without internal boning, positioned on the side in the direction of the AR backward relative to the holes 77A lubricant channel 77 in the inner circle. Oil groove 78 is formed to connect the holes 77A lubricant channel 77 in the inner circle of the mating surface is about 72 front side through the discharge recess 73F front side and a facet 74F front side. Thus, as the engine oil 41 that is served in the oil clearance 60 on the side in the direction of the AR backward relative to the holes 77A lubricant channel 77 in the inner circle through the lubricating groove 78 is reduced, the engine oil 41 that extends from the oil clearance 60, is reduced compared with the case where the portion 7ER without internal undercut does not apply. In addition, since the engine oil 41 is supplied to the second masloprovody channel 65B discharge grooves and the second masloprovody channel 66B chamfer is reduced, the engine oil 41 that extends from the oil clearance 60 is reduced. Since impurities that would take place in the oil clearance 60 via skazochnosti 77, out of the oil clearance 60 in the axial direction of the main bearing 6 by passing through the lubricating groove 78 and the first masloprovody channel 65A unloading excavation, damage which may be caused by impurities, is prevented. As part 7ER without internal undercut is made on the side in the direction of the AR backward relative to the holes in the inner circumference 77A lubrication holes 77, the rotation of the crankshaft 5 prevents the passage of impurities in the lubricating groove 78 in the oil clearance 60, the corresponding part of the 7ER without internal undercut. Thus, the damage which may be caused by impurities, suitable prevented. As described above, according to the main bearing 6 of the first variant embodiment of the invention, the engine oil 41 that extends from the oil clearance 60 is reduced, preventing damage caused by impurities.

(2) According to the main bearing 6 of the first variant embodiment of the invention the width of the lubricating groove 78 is set smaller than the diameter of the lubrication holes 77 (diameter holes 77A in the inner circle). Thus, as the resistance to the passage in the lubricating groove 78 is increased compared with the case where the width of the lubricating groove 78 is set greater than the diameter of smasa the aqueous holes 77, the engine oil 41 that extends from the oil clearance 60 is reduced. According to the main bearing 6 of the first variant of the invention, since the width of the lubricating groove 78 is set to the minimum within the value which is not materially reduces the adaptability of the formation of the lubrication grooves 78, the rate of leakage of the engine oil 41 from the oil clearance 60 is further reduced, without reducing the efficiency of the main bearing 6.

(3) According to the main bearing 6 of the first variant embodiment of the invention the hole 77A in the inner circumference of the lubrication holes 77 is made on the side in the direction of the AR back from the centre of SA along the circumference of the upper bearing 7 bearing. Thus, compared with the case where the hole 77A in the inner circumference of the lubrication holes 77 is made on the side in the direction AF forward from the centre of SA along the circumference, the distance from the hole 77A in the inner circle to the front end portion 78F lubricating groove 78 is increased. Resistance to the passage of a lubricating groove 78 is thus increased. Thus, the engine oil 41 that extends from the oil clearance 60 is reduced.

(4) According to the main bearing 6 of the first variant embodiment of the invention the upper bearing 7 bearing with only one smasa the th hole 77, which takes the engine oil 41 outside the main bearing 6 in the oil clearance 60. Thus, compared with the case where carry out some lube holes for supplying the engine oil 41 in the oil clearance 60, the engine oil 41 supplied from the outside of the oil clearance 60 main bearing 6, is reduced. The engine oil 41 that extends from the oil clearance 60 is thus reduced.

(5) According to the main bearing 6 of the first variant embodiment of the invention the depth of the lubrication grooves 78 in the section on the side in the direction AF forward relative to the holes 77A in the inner circumference of the lubrication holes 77 is set to the minimum in the front end portion 78F. Thus, for example, compared with the case where the depth of the lubrication grooves 78 in the section on the side in the direction AF forward relative to the holes 77A in the inner circumference of the lubrication holes 77 are set constant, the engine oil 41 that passes out of the lubrication grooves 78 from the inner part of the lubrication grooves 78 decreases. This reduces the amount of engine oil 41 that extends from the oil clearance 60.

(6) it Was found through experiments that the engine 1, which is applied crankshaft bearing 6, the amount of impurities produced out of oil C is Zora 60, increased, since the first flow rate QB in the chamfer is increased relative to the first flow rate QA in the discharge recess. On the basis of these facts the ratio between the square of the TA section of the first maloprodaja channel 66A chamfer and the area SA of the first section maloprodaja channel 65A discharge grooves are set so that the first flow rate QB in the chamfer is greater than the first flow rate QA in handling the notch in the main bearing 6 of the first variant embodiment of the invention. Thus, since most of the impurities that come in oil clearance 60 with the engine oil 41 is produced from the oil clearance 60 via the first masloprovody channel 66A chamfer, damage caused by impurities, prevents a more suitable way.

(7) it Was found through experiments that the engine 1, which is applied crankshaft bearing 6, the amount of impurities that are produced outside of the oil clearance 60 is increased, since the second flow QD in the chamfer is increased relative to the second flow rate QC in the discharge recess. On the basis of such a fact, the ratio between the square of the TB section of the second maloprodaja channel 66B chamfer and the area SB of the second section maloprodaja channel 65B discharge grooves are set so that the second flow QD in the chamfer is greater than the second flow rate QC in handling you is the MCA in the main bearing 6 of the first variant embodiment of the invention. Thus, as most of the impurities that would take place in the oil clearance 60 with the engine oil 41 is produced from the oil clearance 60 via the second masloprovody channel 66B chamfer, damage caused by impurities, prevents a more suitable way.

(8) In the first macroprotodon channel 66A chamfer, as the distance between the indigenous bearing 6 and a radical neck 51 of the crankshaft compared to the first masloprovody channel 65A discharge grooves and the second masloprovody channel 61B of the bearing shell, the possibility of damage to the main bearing 6 by impurities in the first macroprotodon channel 66A chamfer assessed as very low. Thus, in the main bearing 6 of the first variant embodiment of the invention the area of the TA section is set to maximum in the range in which the engine oil 41 that passes outside of the oil clearance 60 via the first masloprovody channel 66A chamfer does not exceed the amount of the upper limit, that is the number that is valid as the engine oil 41 that extends from the oil clearance 60. Accordingly, most of the impurities from the oil clearance 60 is released to the outside of the oil clearance 60 via the first masloprovody channel 66A chamfer. Damage which may be caused by the impurities, thus preventing a more suitable way.

(9) Because the second macroprotodon channel 66B chamfer distance between the indigenous bearing 6 and a radical neck 51 of the crankshaft is large compared with the second masloprovody channel 65B discharge grooves and the first masloprovody channel 61A of the bearing, the possibility of damage to the main bearing 6 by impurities in the second macroprotodon channel 66B chamfer is assumed very small. Thus, in the main bearing 6 of the first variant embodiment of the invention the area of the TB section is set to maximum in the range in which the engine oil 41 that passes outside of the oil clearance 60 via the second masloprovody channel 66B chamfer does not exceed the amount of the upper limit, i.e., the amount allowed as the engine oil 41 that extends from the oil clearance 60. Accordingly, most of the impurities from the oil clearance 60 is released to the outside of the oil clearance 60 via the second masloprovody channel 66B chamfer. The damage which may be caused by impurities, thus preventing a more suitable way.

(10) According to the main bearing 6 of the first variant embodiment of the invention masloprovody channel 66 chamfer formed as an auxiliary weight is Provody channel, which produces impurities from lubricating grooves 78 to the outside of the oil clearance 60 using chamfers 74, 84. Accordingly, reduction of the bearing capacity main bearing 6 is prevented compared with the case where the auxiliary masloprovody channel formed separately from the chamfers 74, 84.

(11) According to the main bearing 6 of the first variant embodiment of the invention masloprovody channel 65 of the discharge grooves formed as an auxiliary masloprovody channel, which produces impurities from lubricating grooves 78 to the outside of the oil clearance 60 using the discharge grooves 73, 83. Accordingly, reduction of the bearing capacity main bearing 6 is prevented compared with the case where the auxiliary masloprovody channel formed separately from the discharging grooves 73, 83.

(12) the advantages of the main bearing 6 according to the present variant embodiment of the invention will be described on the basis of comparison with the indigenous bearing 6X according to the comparative example shown in Fig. 29 and 30. On Fig shows the structure of an upper liner 7X main bearing 6X in the front view. On Fig shows the structure of an upper liner 7X bearing in the form below.

As shown in Fig and 30, crankshaft bearing 6X differs from the main bearing 6 PE the first variant implementation of the invention in the following points. That is, the upper shell 7X main bearing 6X provided with a lubrication groove 7XA instead of the lubrication grooves 78. Oil groove 7XA passes for connection of the mating surfaces is about 72 front side with the mating surface 72R of the rear side through holes 77A in the inner circumference of the lubrication holes 77. In addition, the upper shell 7X bearing is not equipped with part 7ER without internal undercut. Crankshaft bearing 6X has essentially the same design as crankshaft bearing 6 of the first variant of the invention, except for the above modifications. In addition, in the drawings, components that are similar to those described in the first embodiment of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

In the engine 1, which is applied crankshaft bearing 6X, engine oil 41 of the lubrication grooves 7XA goes in facing the groove masloprovody channel 63, the first masloprovody channel 65A unloading recesses, the first masloprovody channel 66A chamfer, the second masloprovody channel 65B unloading recess or the second masloprovody channel 66B chamfer. Because the force that acts on the direction of the AR back to the direction AF forward, attached to the engine oil 41 in the oil clearance 60 in accordance with the rotation of the crankshaft 5, a part of mo is ornago oil 41 in the second macroprotodon channel 65B unloading excavation passes from the second maloprodaja channel 65B unloading recesses in the first masloprovody channel 61A of the bearing before going out from the oil gap 60 through the side surface 76 of the upper liner 7X bearing and the side surface 86 of the lower bearing liner 8. At this point, there is a high likelihood of damage to the top of the liner 7X bearing or jamming of the crankshaft 5, since impurities in the engine oil 41 also pass from the second maloprodaja channel 65B unloading recesses, in which the distance between the indigenous bearing 6 and a radical neck 51 of the crankshaft is great in the first masloprovody channel 61A of the bearing, in which the distance is small.

In contrast, since a root bearing 6 of the first variant embodiment of the invention provided with a part 7ER without internal boning, part 7ER without internal boning prevents the passage of engine oil 41 of the lubrication grooves 78 in the second masloprovody channel 65B of the discharge recess. Thus, the amount of impurities that pass in the second masloprovody channel 65B unloading excavation, is reduced compared with the case where the engine 1 is applied crankshaft bearing 6X. Accordingly, the amount of impurities that pass from the second maloprodaja channel 65B unloading recesses in the first masloprovody channel 61A of the bearing in accordance with the rotation of the crankshaft 5 is reduced. Chrome is also damage to the upper bearing 7 bearing and jamming of the crankshaft 5 is prevented suitable manner.

(13) In the engine 1 of the first variant of the invention, the engine oil 41 that extends from the oil clearance 60 is reduced, when the crankshaft bearing 6 holds the crankshaft 5. Thus, the lubricity of the crankshaft 5 is improved, and the rate of fuel consumption is improved by reducing the amount of operation of the oil pump 42.

(14) as the number of impurities that are in the oil gap 29 of the bearing 28 of the connecting rod is reduced, damage to the bearing 28 of the connecting rod and the jamming of the rod 27 is prevented.

The first variant implementation of the invention can be modified as follows.

The depth of field of the lubrication grooves 78 on the side in the direction AF forward relative to the holes 77A in the inner circumference of the lubrication holes 77 is not limited to the example of the first variant embodiment of the invention. That is, the depth of field of the lubrication grooves 78 on the side in the direction AF forward relative to the holes 77A in the inner circumference of the lubrication holes 77 can be set to any value, if exists, at least one section where the relative cross-sectional area becomes minimum.

The configuration of the discharge neck is OK 73, 83 and chamfers 74, 84 may be modified to receive any of the configurations in the following paragraphs (A)to(D). In addition, the configuration in the following paragraphs (A)to(D) can be combined as required.

(A) In the upper liner 7 bearing unloading recess 73F front side and chamfer 74F front side can be excluded from the design. In this case, the area LA of the oil clearance 60 generates the first masloprovody channel 65A discharge grooves. In addition, the area LC of the oil clearance 60 generates the first masloprovody channel 66A chamfer. The first flow rate QB in the chamfer can be made larger than the first flow rate QA in the discharge recess, by regulating the relationship between the size (formed by the length and depth) of the discharge grooves 83R rear side of the lower bearing liner 8 and the size of the chamfer 84R rear side of the lower bearing liner 8.

(B) In the upper liner 7 bearing unloading recess 73R back and chamfer 74R rear side can be excluded from the design. In this case, the zone LB oil clearance 60 forms the second masloprovody channel 65B of the discharge recess. In addition, the area LD oil clearance 60 forms the second masloprovody channel 66B chamfer. The second flow QD in the chamfer can be made larger than the second flow rate QC in the discharge recess, by regulating the relationship between the size of the m (formed by the length and depth) of the discharge grooves 83F front side of the lower bearing liner 8 and the size of the chamfer 84F front side of the lower bearing liner 8.

(C) In the lower bearing liner 8 discharge recess 83R back and chamfer 84R rear side can be excluded from the design. In this case, the area UA of the oil clearance 60 generates the first masloprovody channel 65A discharge grooves. In addition, the area UC oil clearance 60 generates the first masloprovody channel 66A chamfer. The first flow rate QB in the chamfer can be made larger than the first flow rate QA in the discharge recess, by regulating the relationship between the size (formed by the length and depth) of the discharge grooves 73F front side of the upper bearing 7 bearing and size of the chamfer 74F front side of the upper bearing 7 bearing.

(D) In the lower bearing liner 8 discharge recess 83F front side and chamfer 84F front side can be excluded from the design. In this case, the area UB of the oil clearance 60 forms the second masloprovody channel 65B of the discharge recess. In addition, the area UD oil clearance 60 forms the second masloprovody channel 66B chamfer. The second flow QD in the chamfer can be made larger than the second flow rate QC in the discharge recess, by regulating the relationship between the size (formed by the length and depth) of the discharge grooves 73R rear side of the upper bearing 7 bearing and size of the chamfer 74R rear side of the upper bearing 7 bearing.

Then sssylkami on Fig will be described a second variant implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to those described in the first embodiment of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig, main bearing 6 for the second variant of the invention, the width of the lubricating groove 78 is set equal to the diameter of the lubrication holes 77 (diameter holes 77A in the inner circle). In addition, the depth of the lubricating groove 78 is set to the largest in Central ST. circumferential lubricating grooves 78. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the rear end portion 78R and zero in the rear end portion 78R. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the front end portion 78F.

As described above, according to the main bearing 6 for the second variant of the invention, the following advantage (15) in addition to the advantages (1) and (3)to(14) of the first variant embodiment of the invention.

(15) since the oil groove 78 is easily formed compared with the case of the AEM, when the width of the lubricating groove 78 is set smaller than the diameter of the lubrication holes 77, the productivity in the manufacture of main bearing 6 is improved.

Next, with reference to Fig will be described third alternative implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig, main bearing 6 of this variant of the invention, the lubricating hole 91 is made in part of the intermediate section 7E of the liner on the side in the direction AF forward relative to the lubrication holes 77. Lubricating hole 91 allows the engine oil 41 of the lubrication grooves 32R bearing partition walls 32 to pass into the oil clearance 60 regardless lubrication holes 77. Lubricating hole 91 is located on the side in the direction AF forward relative to the center of SA along the circumference of the upper bearing 7 bearing. The diameter of the lubrication holes 91 is set equal to the diameter of the lubrication holes 77.

As described to enter the, according to the main bearing 6 of the third variant of the invention, the following advantage (16) in addition to the advantages (1)to(3) and (5)to(14) of the first variant embodiment of the invention.

(16) since the engine oil 41 is supplied to the oil clearance 60 is increased compared with the case where the lubricating hole 91 is not used, suitable prevents insufficient amount of the engine oil 41 in the oil clearance 60.

Next, with reference to Fig will be described a fourth variant of implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig, main bearing 6 of the fourth variant of the invention, the lubricating hole 77 is located on the side in the direction AF forward relative to the center of SA along the circumference. Oil groove 78 is located within the range that is on the side in the direction AF forward relative to the center of SA along the circumference of the top of the liner 7 of the bearing. The rear end portion 78R lubricating groove 78 is located in the inner hole 77A of the circle lubrication holes 77. The depth of the lubrication grooves 78 in the rear end portion 78R is set greater than zero, so that the engine oil 41 of the lubrication holes 77 is held in the lubricating groove 78 through the rear end portion 78R. The area between the rear end part 78R lubricating grooves 78 and unloading excavation 73R back complies with part 7ER without internal undercut.

As described above, according to the main bearing 6 of the third variant embodiment of the invention, the following advantages (17) and (18) in addition to the advantages (1), (2) and (4)to(14) of the first variant embodiment of the invention.

(17) the Reference surface of the upper bearing 7 bearing increased compared with the case where the lubricating hole 77 is located on the side in the direction of the AR back relative to the center of SA along the circumference, i.e. in comparison with a case when the oil groove 78 passes from the section, which is located on the side in the direction of the AR back relative to the center of SA along the circumference of the mating surfaces is about 72 front side. Thus, the bearing capacity of the main bearing 6 is improved.

(18) since the engine oil 41 that flows from the lubrication grooves 78 in the first masloprovody channel 61A p is Lipnica, decreases the amount of impurities that are in the first masloprovody channel 61A of the bearing is reduced accordingly. Thus, the damage which may be caused by impurities and by jamming of the crankshaft 5, prevents a more suitable way.

Next, with reference to Fig will be described a fifth variant of implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the fourth variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

In the main bearing 6 of the fifth variant of the invention, the width of the lubricating groove 78 is set equal to the diameter of the lubrication holes 77 (diameter holes 77A in the inner circle), as shown in Fig. The depth of the lubricating groove 78 is set to the largest in Central ST. circumferential lubricating grooves 78. The depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the rear end portion 78R and becomes zero at the rear end portion 78R. The depth of the lubricating groove 78 is set to p is gradually decreasing from the centre of ST along the circumference of the front end portion 78F.

As described above, according to the main bearing 6 of the fifth variant of the invention, the advantage obtained (15) of the second variant embodiment of the invention in addition to the advantages (1), (2) and (4)to(14) of the first variant embodiment of the invention and the advantages (17) and (18) of the fourth variant embodiment of the invention.

Next, with reference to Fig will be described a sixth variant of implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the fourth variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig, the depth of the lubrication grooves 78 in the main bearing 6 of this variant of the invention defined in the following way. That is, the depth of the lubricating groove 78 is set to the largest in the front end portion 78F. The depth of the lubricating groove 78 is set to the smallest at the rear end portion 78R. The depth of the lubrication grooves 78 in the rear end portion 78R is set greater than zero so that the engine oil 41 of the lubrication holes 77 is held in the lubricating groove 78 through the back to nawou portion 78R. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the front end portion 78F to the rear end portion 78R.

As described above, according to the main bearing 6 of a sixth variant of the invention, the following advantage (19) in addition to the advantages (1), (2) and (4)to(14) of the first variant embodiment of the invention and the advantages (17) and (18) of the fourth variant embodiment of the invention.

(19) compared with the case where the depth of the lubricating groove 78 is set to the largest in the centre of ST along the circumference and reduced end portions, limit processing during the formation of the lubrication grooves 78 are reduced. Thus, the productivity in the manufacture of main bearing 6 is increased.

Next, with reference to Fig will be described a seventh variant of implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying the shape of the lubrication grooves 78 main bearing 6, corresponding to the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

In the main bearing 6 of these variations is the embodiment of the invention, the first discharge section 7C of the upper bearing 7 bearing provided with a lubrication groove 92, which connects one of the side surfaces 76 on the other side surface 76, as shown in Fig. Oil groove 92 produces engine oil 41 of the lubrication grooves 78 and the first maloprodaja channel 65A unloading recess to the outside of the oil clearance 60 of the side surfaces 76.

As described above, according to the main bearing 6 of the seventh variant embodiment of the invention receive the following benefit (20) in addition to the advantages (1)to(14) of the first variant embodiment of the invention.

(20) since the engine oil 41 of the lubrication grooves 78 and the first maloprodaja channel 65A unloading recesses are produced outside of the oil clearance 60 via the lubricating groove 92, impurities from the oil clearance 60 is produced more reliably. Thus, the damage that can be caused by impurities, prevents a more suitable way.

Next, with reference to Fig will be described eighth variant of implementation of the present invention.

Crankshaft bearing 6 of the eighth variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position than the ranks to those in the first embodiment of the invention.

As shown in Fig, oil groove 78 in the main bearing 6 of the eighth variant embodiment of the invention is formed as follows. That is, the oil groove 78 is formed in such a way that it passes from the area between the hole 77A in the inner circumference of the lubrication holes 77 and part 7ER without internal undercut to the field within the first discharge section 7C. That is, the oil groove 78 is formed to connect the holes 77A in the inner circumference of the discharge recess 73F front side. In addition, the center of ST. circumferential lubricating grooves 78 formed so that it is located on the side in the direction AF forward relative to the center of SA along the circumference of the upper bearing 7 bearing. The width of the lubricating groove 78 is set smaller than the diameter of the lubrication holes 77 (diameter holes 77A in the inner circle). The depth of the lubricating groove 78 is set to the largest in the centre of ST along the circumference. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the rear end portion 78R and becomes zero at the rear end portion 78R. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the front end portion 78F.

As described above, according to the main bearing 6 of the eighth variationbetween of the invention the benefits, which are similar to the advantages (1)to(14) of the first variant embodiment of the invention.

Next, with reference to Fig will be described ninth variant of implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig, oil groove 78 in the main bearing 6 of the ninth variant embodiment of the invention is formed as follows. That is, the oil groove 78 is formed in such a way that it passes from the area between the hole 77A in the inner circumference of the lubrication holes 77 and part 7ER without internal undercut to the field within the first beveled section 7A. In addition, the oil groove 78 is formed for communication with the hole 77A in the inner circumference of the discharge recess 73F front side and a facet 74F front side. In addition, the oil groove 78 is formed so that the center of ST. circumferential lubricating groove 78 is located on the side in the direction AF forward relative to the center is along the circumference of the upper bearing 7 bearing. The width of the lubricating groove 78 is set smaller than the diameter of the lubrication holes 77 (diameter holes 77A in the inner circle). The depth of the lubricating groove 78 is set to the largest in the centre of ST along the circumference. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the rear end portion 78R and becomes zero at the rear end portion 78R. The depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the front end portion 78F.

As described above, according to the main bearing 6 of the ninth variant embodiment of the invention obtained advantages similar to the advantages (1)to(14) of the first variant embodiment of the invention.

Next, with reference to Fig will be described tenth variant of implementation of the present invention.

Crankshaft bearing 6 of the tenth variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig, main bearing 6 of this variant of the invention, the PR is changed, the lubrication grooves 93 instead of the chamfers 74 of the upper bearing 7 bearing according to the first variant embodiment of the invention. The lubrication grooves 93 include lubricating groove 93F front side and the lubricating groove 93R back. In addition, the applied lubricant grooves 94 instead of chamfers 84 of the lower bearing liner 8 according to the first variant embodiment of the invention. The lubrication grooves 94 include lubricating groove 94F front side and the lubricating groove 94R back. According to the modification of the oil clearance 60 tenth variant embodiment of the invention equipped with masloprovody grooves 67, corresponding masloprovody channels 66 of the chamfers of the first variant embodiment of the invention.

As for lubricating grooves 93 of the upper bearing 7 bearing oil groove 93F front side is formed to connect one of the side surfaces 76 on the other side surface 76. Oil groove 93F front side is masloprovody channel to release the engine oil 41 of the lubrication grooves 78 and the first maloprodaja channel 65A unloading recess to the outside of the oil clearance 60 of the side surfaces 76. Oil groove 93R rear side is formed to connect one of the side surfaces 76 on the other side surface 76. Oil groove 93R back is masloprovody channel to release the engine oil 41 in the second maloprodaja channel 65B unloading viem and outside of the oil clearance 60 of the side surfaces 76.

The upper bearing 7 bearing subdivided in the radial direction as follows. That is, the upper bearing 7 bearing is divided into the first section 7G with groove, in which the oil groove 93F front side, the second section 7H with groove, in which the oil groove 93R rear side, the first discharge section 7C, which made unloading recess 73F front side, the second discharge section 7D, which made unloading recess 73R rear side, and an intermediate section 7E of the liner, which made the hole 77A in the inner circumference of the lubrication holes 77.

As for lubricating grooves 94 of the lower bearing 8 bearing oil groove 94F front side is formed to connect one of the side surfaces 86 on the other side surface 86. Oil groove 94F front side is masloprovody channel to release the engine oil 41 in the second maloprodaja channel discharge grooves 65B outside of the oil clearance 60 from the side surfaces 86. Oil groove 94R rear side is formed to connect one of the side surfaces 86 on the other side surface 86. Oil groove 94R back is masloprovody channel to release the engine oil 41 of the first maloprodaja channel 65A Accel is utcnow excavation outside of the oil clearance 60 from the side surfaces 86.

The lower bearing liner 8 is subdivided in the radial direction as follows. The lower bearing liner 8 is divided into the first section 8G with groove, in which the oil groove 94F front side, the second section 8H with a groove in which the oil groove 94R rear side, the first discharge section 8C, which made unloading recess 83F front side, the second discharge section 8D, which made unloading recess 83R rear side, and an intermediate section 8E of the liner, is made between the first discharge section 8C and the second discharge section 8D.

Masloprovody grooves 67 includes a first masloprovody groove 67A and the second masloprovody groove 67B. First maloprodaja groove 67A is located between the inner circular surface of the first section 7G with the groove in the top of the liner 7 of the bearing and the inner circular surface of the second section 8H with the groove in the lower bearing liner 8 and the imaginary inner circular surface 201 and an imaginary inner circular surface 204 of the second imaginary bearing 200. Second maloprodaja groove 67B is located between the inner circular surfaces of the second section 7H with the groove of the upper bearing 7 bearing and the first section 8G with the groove in the lower bearing liner 8 and oobr the message of the inner circular surfaces 202, 203 second imaginary bearing 200. Masloprovody grooves 67 correspond to the auxiliary masloprovody channels made in the mating parts of the main bearing 6.

In the main bearing 6 the ratio between the square of the SA section of the first maloprodaja channel 65A unloading excavation and area TC section first masloprovody grooves 67A and the ratio between the area SB of the second section maloprodaja channel 65B unloading excavation and TD square cross-section of the second masloprovody grooves 67B set, as shown in the following paragraphs (A) and (B).

(A) with respect to the first maloprodaja channel 65A discharge grooves and the first masloprovody grooves 67A, the ratio between the square of the SA section of the first maloprodaja channel 65A unloading excavation and area TC section first masloprovody grooves 67A are set so that the flow rate (the flow rate QE in the first groove) of the engine oil 41 that passes outside of the oil clearance 60 via the first masloprovody groove 67A, is greater than the flow rate of the first flow rate QA in handling the notch) of the engine oil 41 that passes outside of the oil clearance 60 via the first masloprovody channel 65A discharge grooves. The ratio between the square of the SA section and area TC section is specified by setting the relationship between the size of the discharge grooves 73F front side and the size of lubricating ka is where it is refuelled 93F front side, and the relationship between the size of the discharge grooves 83R the rear and the size of the lubrication grooves 94R rear side are set so that the first flow rate QE in the groove is greater than the first flow rate QA in the discharge slot.

(B) for the second maloprodaja channel 65B discharge grooves and the second masloprovody grooves 67B, the ratio between the area SB of the second section maloprodaja channel 65B unloading excavation and TD square cross-section of the second masloprovody grooves 67B are mounted so that the flow rate of the second flow rate QF in the groove) of the engine oil 41 that passes outside of the oil clearance 60 via the second masloprovody groove 67B, is greater than the flow rate of the second flow rate QC in the discharge recess) of the engine oil 41 that passes outside of the oil clearance 60 via the second masloprovody channel 65B of the discharge recess. The ratio between the square of the SB section and TD square cross-section defined by setting the relationship between the size of the discharge grooves 73R rear and the size of the lubrication grooves 93R back and the relationship between the size of the discharge grooves 83F front side and the size of the lubrication grooves 94F front side so that the second flow rate QF in the groove is greater than the second flow rate QC in the discharge slot.

As described above, advantages similar to the advantages (1)to(14) the first option is sushestvennee of the invention, obtained according to the main bearing 6 of the tenth variant embodiment of the invention.

Next, with reference to Fig and 41 will be described eleventh variant of implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig and 41 components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

In the main bearing 6 eleventh variant embodiment of the invention the discharge grooves 73 and chamfers 74 of the upper bearing 7 bearing excluded, as shown in Fig and 41. In addition, in the lower bearing liner 8 eleventh variant embodiment of the invention the discharge grooves 83 and chamfers 84 excluded. The front end part 78F lubricating groove 78 is located between the hole 77A in the inner circle and the mating surface is about 72 front side. The upper bearing 7 bearing provided with a lubrication groove 95, which connects the lubricating groove 78 with side surfaces 76 of the upper bearing 7 bearing. Oil groove 95 is masloprovody channel to release the engine oil 41 is C lubricating grooves 78 to the outside of the oil clearance 60 of the side surfaces 76. The depth of the lubricating groove 78 is set to the largest in the centre of ST along the circumference. In addition, the depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the front end portion 78F. The depth of the lubricating groove 78 is set to a gradually decreasing from the centre of ST along the circumference of the rear end portion 78R and becomes zero at the rear end portion 78R. Oil groove 95 may be parallel to the axis of the main bearing 6, or may be tilted relative to the axis of the main bearing 6. The width of the lubricating groove 95 may change between the oil groove 78 and the side surfaces 76.

As described above, according to the main bearing 6 eleventh variant embodiment of the invention receive the following benefit (21) in addition to the benefits(2)-(4), (13) and (14) of the first variant embodiment of the invention.

(21) In the main bearing 6 of this variant of the invention, the portion 7ER without internal undercut is made on the side in the direction of the AR backward relative to the holes 77A in the inner circumference of the lubrication holes 77. Crankshaft bearing 6 of this variant embodiment of the invention is also provided with a lubrication groove 95, which connects the lubricating groove 78 with side surfaces 76. Thus, the engine oil 41 that is served in the mA area is Lenogo gap 60 on the side in the direction of the AR backward relative to the holes 77A in the inner circumference of the lubrication holes 77 through the lubricating groove 78, reduced compared with the case where the portion 7ER without internal undercut not apply. This reduces the amount of engine oil 41 that passes outside of the oil clearance 60. Furthermore, since the impurities that would take place in the oil clearance 60 via the oil hole 77, are outside of the oil clearance 60 in the axial direction of the main bearing 6 by passing through the lubricating groove 78 and lubricating groove 95, the damage which may be caused by impurities, is prevented. As part 7ER without internal undercut is made on the side in the backward direction relative to the holes 77A in the inner circumference of the lubrication holes 77, the passage of impurities from lubricating grooves 78 in the oil clearance 60, the corresponding part of the 7ER without internal boning, prevents rotation of the crankshaft 5. Thus, the damage which may be caused by impurities, prevents suitable way. As described above, according to the main bearing 6 eleventh variant embodiment of the invention, the engine oil 41 that extends from the oil clearance 60 is reduced, preventing damage that can be caused by impurities.

Next, with reference to Fig and 43 will be described twelfth variant of implementation, the program of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig and 43 components that are similar to components of the first variant of the invention, assigned to the reference position, similar to those in the first embodiment of the invention.

As shown in Fig and 43, in main bearing 6 of this variant of the invention, the unloading recesses 73 and chamfers 74 of the upper bearing 7 bearing excluded from the design. In addition, the discharge grooves 83 and chamfers 84 of the lower bearing liner 8 are excluded from the design. The lower shell 8 of the bearing provided with a lubrication groove 96, which is communicated with the oil groove 78 of the upper bearing 7 bearing, and lubrication groove 97, which connects the lubricating groove 96 with the side surfaces 86 of the lower bearing liner 8. Oil groove 96 is masloprovody channel, allowing engine oil 41 supplied from the lubrication grooves 78, held in the circular direction of the lower bearing liner 8. Oil groove 97 is masloprovody channel to release the engine oil 41 of the lubrication grooves 96 to the outside of the oil clearance 60 of the side surfaces 86. Matchmaker.avi 97 may be parallel to the axis of the main bearing 6, or may be rejected relative to the axis of the main bearing 6. The width of the lubricating groove 97 may vary between lubrication groove 96 and the side surfaces 86.

As described above, according to the main bearing 6 twelfth variant embodiment of the invention receive the following benefit (22) in addition to the benefits(2)-(5), (13) and (14) of the first variant embodiment of the invention.

(22) In the main bearing 6 of this variant of the invention, the portion 7ER without internal undercut is made on the side in the direction of the AR backward relative to the holes in the inner circumference of the lubrication holes 77A 77. Crankshaft bearing 6 twelfth variant embodiment of the invention provided with a lubrication groove 97, which connects the lubricating groove 96 of the lower bearing liner 8 with the side surfaces 86. Thus, compared with the case where the portion 7ER without internal undercut is not used, the engine oil 41 that is served in the area of the oil clearance 60 on the side in the direction of the AR backward relative to the holes 77A in the inner circumference of the lubrication holes 77 through the lubricating groove 78 is reduced. This reduces the amount of engine oil 41 that passes outside of the oil clearance 60. Since impurities that would take place in the oil clearance 60 via the oil hole 77, are outside of the oil clearance 60 against axial direction is placed main bearing 6, passing through the lubricating groove 78, lubricating groove 96 and lubricating groove 97, the damage which may be caused by impurities, is prevented. As part 7ER without internal undercut is made on the side in the direction of the AR backward relative to the holes 77A in the inner circumference of the lubrication holes 77, the passage of impurities from lubricating grooves 78 in the oil clearance 60, the corresponding part of the 7ER without internal boning, prevents rotation of the crankshaft 5. Thus, the damage which may be caused by impurities, prevents suitable way. As described above, according to the main bearing 6 twelfth variant embodiment of the invention, the engine oil 41 that extends from the oil clearance 60 is reduced, preventing damage that can be caused by impurities.

Next, with reference to Fig will be described thirteenth variant implementation of the present invention.

Crankshaft bearing 6 of this variant embodiment of the invention is formed by modifying a part of the main bearing 6 of the first variant embodiment of the invention as follows. On Fig components that are similar to components of the first variant of the invention, assigned to the reference position similar to that is new in the first embodiment of the invention.

As shown in Fig, main bearing 6 of the thirteenth variant of the invention, the unloading recesses 73 and chamfers 74 of the upper bearing 7 bearing excluded from the design. In addition, the discharge grooves 83 and chamfers 84 of the lower bearing liner 8 are excluded from the design. The depth of the lubricating groove 78 is set so that impurities from the front end portion 78F lubricating grooves 78 are held in the oil clearance 60 corresponding to the lower bearing liner 8.

As described above, according to the main bearing 6 of the thirteenth variant of the invention, the following advantage (23) in addition to the benefits(2)-(5), (13) and (14) of the first variant embodiment of the invention.

(23) In the main bearing 6 of the thirteenth variant of the invention, the portion 7ER without internal undercut is made on the side in the direction of the AR backward relative to the holes 77A in the inner circumference of the lubrication holes 77. Oil groove 78 is formed to connect the inner bore 77A in the inner circumference of the lubrication holes 77 with the mating surface is about 72 front side. Thus, compared with the case where the portion 7ER without internal undercut is not used, the engine oil 41 that is served in the oil clearance 60 on the side in the direction of the AR ago Rel is relatively holes 77A in the inner circumference of the lubrication holes 77 through the lubricating groove 78, reduced. This reduces the amount of engine oil 41 that extends from the oil clearance 60. Impurities that have entered the oil clearance 60 via the oil hole 77, are routed through the lubricating groove 78 to the place near the boundary between the oil clearance 60, corresponding to the upper liner 7 of the bearing, and the oil clearance 60 corresponding to the lower bearing liner 8. Thus, since the impurities in the lubricating groove 78 pass from the oil clearance 60 corresponding to the upper liner 7 bearing, oil clearance 60 corresponding to the lower bearing liner 8, across the border, the damage to the upper liner 7 of the bearing is prevented. In addition, as part of the 7ER without internal undercut is made on the side in the direction of the AR backward relative to the holes 77A in the inner circumference of the lubrication holes 77, the passage of impurities from lubricating grooves 78 in the oil clearance 60, the corresponding part of the 7ER without internal boning, prevents rotation of the crankshaft 5. Thus, damage to the top of the liner 7 of the bearing is prevented suitable way. As described above, according to the main bearing 6 of the thirteenth variant of the invention, the engine oil 41 that extends from the oil clearance 60 is reduced, prevent the I damage which can be caused by impurities.

Each of the above embodiments of the invention may be modified as follows.

The above embodiments of the invention can be combined as required.

In each of the embodiments of the invention the bearing corresponding to the present invention, performed in the main bearing 6 of the engine 1. However, the present invention can be used for other bearings except the main bearing. That is, the present invention can be applied with respect to any sliding bearing according to each of the above embodiments of the invention, if the bearing is divided into a pair of semicircular bearing housings and keeps rotating shaft by means of a lubricant.

In each of the above embodiments of the invention the bearing corresponding to the present invention, is used for inline four-cylinder engine 1, while the bearing corresponding to the present invention can be used with engines having other cylinder configuration.

In each of the above embodiments of the invention, the engine 1 is understood as the transfer device and the BP is to prohibit the moment, uses a sliding bearing corresponding to the present invention. However, the bearing corresponding to the present invention can be used in any device transmitting torque, which includes a main shaft, which rotates in one direction, and the liner slides for the main shaft that holds the main shaft.

1. A sliding bearing for holding a rotating shaft containing a semicircular main bearing shell and a semi-circular lower bearing shell, which can be separated from each other, and the main bearing shell includes a first masloprovody channel for introducing lubricant from the outside into the gap between the sliding bearing and the rotating shaft and the second masloprovody channel that allows lubricant to enter between the bearing and the rotating shaft in the radial direction of the sliding bearing, in which: the first masloprovody channel comprises a hole in the inner circle, which is open on the inner circumference of the main bearing, main bearing shell includes part without internal boning, which is not formed masloprovody channel on the rear side relative to the holes in the inner circumference direction of rotation rotation is ashegoda shaft, auxiliary masloprovody channel to release lubricant from the second maloprodaja channel outward from the axial direction of the sliding bearing is made in at least one of the lower bearing shell and the region on the front side relative to the holes in the inner circumference of the main bearing in the direction of rotation of the rotating shaft, and the second masloprovody channel continuously passes to the front side in the rotation direction of the rotating shaft from the hole in the inner circumference of the supporting macroprolactinoma channel.

2. The sliding bearing according to claim 1, in which each of the main bearing and the lower bearing shell includes mating surfaces that come into contact with the other bearing housing at the ends in the circumferential direction, and the mating surface of the main bearing, located on the front side relative to the holes in the inner circumference direction of rotation of the rotating shaft, is formed as a mating surface of the front side, and the auxiliary masloprovody channel formed by the chamfer on one edge of the mating surface of the front side.

3. The sliding bearing according to claim 1, in which each of the main bearing and the lower bearing bearing which includes a mating surface, which come into contact with the other bearing housing at the ends in the circumferential direction, and the mating surface of the main bearing, located on the front side relative to the holes in the inner circumference direction of rotation of the rotating shaft, is defined as the mating surface of the front side and the end part of the main bearing shell including a mating surface of the front side is set as the front end part, while the auxiliary masloprovody channel formed discharge groove on the front end.

4. The sliding bearing according to claim 1, in which each of the main bearing and the lower bearing shell includes mating surfaces that come into contact with the other bearing housing at the ends in the circumferential direction, and the mating surface of the node main bearing, located on the front side relative to the holes in the inner circumference direction of rotation of the rotating shaft, is defined as the mating surface of the front side, and the depth of the second maloprodaja channel set reduces to the mating surface of the front side of the longitudinal middle part of the second maloprodaja channel.

5. The sliding bearing according to claim 1, in which the applied one hole in which nutrena circumference, and the hole in the inner circle is located on the rear side relative to the center along the circumference of the main bearing in the direction of rotation of the rotating shaft.

6. The sliding bearing according to claim 1, in which there is one hole in the inner circle, located on the front side relative to the center along the circumference of the main bearing in the direction of rotation of the rotating shaft.

7. The sliding bearing according to claim 1, in which the main bearing shell includes a front end part located on the front side relative to the holes in the inner circumference direction of rotation of the rotating shaft, and the rear end part located on the rear side relative to the holes in the inner circumference direction of rotation of the rotating shaft, the lower bearing shell has a rear end part, which corresponds to the front end portion of the main bearing, and the front end part, which corresponds to the rear end portion of the main bearing, and auxiliary masloprovody channel represents the first auxiliary masloprovody channel located in the mating part between the front end part of the main bearing and the rear end part of the lower liner is of Podshipnik, and the second auxiliary masloprovody channel is located in the mating portion between the rear end part of the main bearing and the rear end part of the lower bearing shell.

8. A sliding bearing for holding a rotating shaft containing a semicircular main bearing shell and a semi-circular lower bearing shell, which can be separated from each other, and the main bearing shell includes a first masloprovody channel for introducing lubricant from the outside into the gap between the sliding bearing and the rotating shaft and the second masloprovody channel, allowing lubricant introduced between the sliding bearing and the rotating shaft to pass through in the radial direction of the sliding bearing, in which: the first masloprovody channel comprises a hole in the inner circle, which is open in the inner circumference of the main bearing, main bearing shell includes part without internal boning, which is not formed masloprovody channel on the back side of the hole in the inner circumference direction of rotation of the rotating shaft, the main bearing shell includes a front end part on the front side relative to the holes in the inner circumference direction of rotation rotation is ashegoda shaft, and the lower bearing shell includes a rear end portion corresponding to the front end portion, and an auxiliary masloprovody channel which connects the second masloprovody channel with a lateral surface of the sliding bearing, made in the mating portion between the front end part of the main bearing and the rear end part of the lower bearing shell, the second masloprovody channel continuously passes to the front side in the rotation direction of the rotating shaft from the hole in the inner circumference of the supporting macroprolactinoma channel, the discharge recess, which forms masloprovody channel discharge hole chamfer that forms masloprovody channel chamfer performed on the inner circumferential side least one of the front end portion of the main bearing and the rear end portion of the lower bearing and auxiliary masloprovody channel formed masloprovody discharge channel excavation and masloprovody channel chamfer, and the relationship between the cross-sectional area maloprodaja channel chamfer and the cross-sectional area maloprodaja channel discharge grooves are set so that the lubricant consumption in macroprotodon channel chamfer is greater than the flow rate of the lubricant in macroprotodon ka the ale unloading excavation.

9. The sliding bearing of claim 8 in which each of the main bearing and the lower bearing shell includes mating surfaces that come into contact with the other bearing housing at the ends in the circumferential direction, and the mating surface on the front end portion of the main bearing, defined as the mating surface of the front side, while unloading the notch is located on the front end portion of the main bearing, and a chamfer is located on one edge of the mating surface of the front side.

10. The sliding bearing of claim 8 in which each of the main bearing and the lower bearing shell includes mating surfaces that come into contact with the other bearing housing at the ends in the circumferential direction, and the mating surface on the front end portion of the main bearing, defined as the mating surface of the front side and the mating surface of the lower bearing shell, which comes in contact with the mating surface of the front side is defined as the mating surface of the rear side, while unloading the notch is located on the rear end portion of the lower bearing, and a chamfer is located on one edge of the mating surface C the days of hand.

11. The sliding bearing of claim 8 in which each of the main bearing and the lower bearing shell includes mating surfaces that come into contact with the other bearing housing at the ends in the circumferential direction, and the mating surface on the front end portion of the main bearing, defined as the mating surface of the front side and the mating surface of the lower bearing shell, which comes in contact with the mating surface of the front side is defined as the mating surface of the rear side, while unloading the notch is located on the front end portion of the main bearing and the rear end portion of the lower bearing and the bevel located on one edge of the mating surface of the front side and on one edge of the mating surface of the rear side.

12. The sliding bearing of claim 8, in which the auxiliary masloprovody channel represents the first masloprovody channel, in which the main bearing shell includes a rear end portion located on the rear side relative to the holes in the inner circumference direction of rotation of the rotating shaft, the lower bearing shell includes a front end portion corresponding to the rear end portion, and the second in popularily masloprovody channel made in the mating portion between the rear end part of the main bearing and the front end part of the lower bearing shell.

13. Device transmit torque, containing the sliding bearing according to any one of claims 1 to 12 and the main shaft, which rotates in one direction, while the main shaft is a rotating shaft held by the bearings.

14. The engine containing the sliding bearing according to any one of claims 1 to 12 and the crankshaft, which is a rotating shaft held by the sliding bearing.



 

Same patents:

FIELD: mechanical engineering.

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FIELD: power engineering.

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FIELD: mechanical engineering.

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FIELD: engines and pumps.

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Sliding bearing // 2324081

FIELD: engineering industry; sliding bearings.

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2 cl, 4 dwg.

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31 cl, 4 dwg

FIELD: mechanical engineering.

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Stern gear // 2397106

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FIELD: mechanical engineering.

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EFFECT: upgraded wear resistance and operability of bearing and improved prossessability of manufacture.

2 cl, 3 dwg

FIELD: mechanics.

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EFFECT: increased wear resistance and serviceability, ease of manufacture.

2 cl, 3 dwg

FIELD: mechanics.

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EFFECT: higher bearing capacity, stability and efficiency.

2 cl, 4 dwg

Gas-static bearing // 2357119

FIELD: machine building.

SUBSTANCE: invention is related to machine building, mostly may be used in machines and devices with moving parts that operate in conditions of gas lubrication, for instance in spindles of metalworking machines. Gas-static bearing consists of body, chamber that communicates to supply manifold with insert installed inside body to close chamber. Insert is arranged in the form of bush from gasproof material and porous inserts installed in bush holes. Porous inserts are arranged in the form of keys and are installed in two rows, at that width of every insert is equal to 0.15-0.20 of bearing diametre, length of every insert is equal to 0.26-0.35 of bearing length. Number of inserts in one row of supercharge is equal to 10-14. Separation of supercharge lines makes 0.5 of bearing length and defines distance between centers of every rows inserts along axis of insert symmetry, which is perpendicular to bearing ends.

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2 dwg

FIELD: engines and pumps.

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EFFECT: lower vibration, higher load-bearing capacity of the plain bearing assembly with siliconised graphite working surface.

6 dwg

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