Liquid-cooled connector assembly

FIELD: machine building.

SUBSTANCE: invention relates to machine building. The connector assembly used for force transfer includes the housing, which contains a part of the rotating disk. The housing is fitted with plate element, coolant duct, and inlet and outlet holes. The plate element with the force transfer surface contacts through the circular zone of the lateral surface with the rotating disk for deceleration of relative rotation of the housing and disk. The coolant duct is partially formed by the side of the plate element counter to the force transfer surface. Through the inlet hole water enters the coolant duct, and through the outlet hole water leaves the coolant duct. The internal lateral surface of the plate element counter to the force transfer surface, comprises multiple hemispherical recesses, intended for forming of turbulence and a secondary turbulent water flow in the coolant duct for improvement of heat exchange between the plate element of the housing and water, flowing through the coolant duct.

EFFECT: device cooling improvement is achieved at the expense of increase of heat transfer coefficient.

11 cl, 8 dwg

 

The level of technology

The present invention relates to a new and improved connecting device Assembly, which may be a clutch and/or brake.

The connecting device is used as a brake, is described in U.S. patent No. 4,262,789. This connecting device Assembly uses the flow of the cooling medium (water) for cooling the copper wear plates which are in contact with the rotor to retard relative rotation of the rotor and the housing. Other connecting device Assembly described in U.S. patent No. 3530965 and 5577581.

During use of these connecting devices Assembly produces heat after switching the connecting device Assembly from an off state to an on state. It was suggested to affect the elements of the connecting device Assembly flow of the cooling medium (water) for heat transfer from the elements of the connecting device Assembly to a cooling environment. Although elements of these connecting devices in the collection are exposed to the flow of the cooling medium, there is a tendency to the accumulation of heat in the elements of the connecting device Assembly. Under very severe operating conditions there is a tendency to the accumulation of excessive heat in places overheating on the elements of the connecting device sat in the re.

Brief description of the invention

The present invention provides a new and improved connecting device Assembly with liquid cooling, which has improved the flow of the cooling medium to accelerate heat transfer from the elements of the connecting device Assembly. Convective heat transfer from the elements of the connecting device Assembly to the flow of the cooling medium can contribute to the creation of secondary turbulent flow of the cooling medium due to the grooves on the surface of the copper wear plate to increase the heat transfer coefficient.

The connecting device Assembly may include a rotary disk, which is at least partially contained in a housing Assembly. The housing Assembly may have a plate-like element and transmitting the force of the surface, which may come in contact with the area of the side surface of the rotary disk to retard relative rotation of the disk and the housing. The housing can also be the channel for the cooling medium, which is at least partially formed side plate element opposite to the surface that transfers the force.

To improve heat transfer and to minimize cases, the formation of hot spots many of grooves located on the inner surface of the plate section, create a secondary tour is olenty the flow in the channel for the cooling medium. Additional turbulence in the flow of the cooling medium can be initiated due to the presence of ribs protruding into the channel for the cooling medium.

Inlet for the intake of the medium in the channel for the cooling medium can have a site with a relatively large cross-sectional area which is connected with a radial outer section of the channel for the cooling medium. The inlet opening may have an area with a relatively small cross-sectional area which is connected with the radial inner section of the channel for the cooling medium.

The connecting device is designed according to the present invention, has many different characteristics, which mainly can be used together, as indicated in the description. However, these characteristics can be used separately or in conjunction with other characteristics. For example, the inlet opening for the cooling medium of various sizes for radial inner and radial outer sections of the channel for the cooling medium can be used with the tabs in the channel for the cooling medium. As another example, the protrusions may include or may not include the ribs.

Although described here, the connecting device Assembly is used as a brake, it should be understood that the connecting device Assembly may be and what to use as a clutch. Also provides that the connecting device Assembly may be a combination clutch and brake Assembly.

Brief description of drawings

The above and other features of the invention will become better understood upon consideration of the following description with reference to the attached drawings, on which:

Fig.1 is a front view of the connection device Assembly, made according to the present invention;

Fig.2 is an enlarged view in section along the plane 2-2 in Fig.1, additionally showing the design of the connecting device Assembly;

Fig.3 - the image on the plane 3-3 in Fig.2, showing the relationship of the wear-resistant plate with another element of the housing of the connecting device Assembly;

Fig.4 is a view in section along the plane 4-4 in Fig.3, showing the relationship of the inlet for the cooling medium and an outlet for the cooling medium with the element body of the connecting device Assembly of Fig.1 and 2;

Fig.5 is a top view showing the construction of the lower surface of the wear plate element according to the variant of implementation of the present invention;

Fig.6 is an enlarged fragmentary image of the wear-resistant plate element;

Fig.7 is an enlarged fragmentary view in section, showing the construction of the projections for scenario execution; and

Fig.8 - led the military fragmentary view of the inner side surface of the wear plate.

Detailed description

The connecting device 10 in the collection (Fig.1 and 2) is used to transfer forces between the rotary leading element 12 and the stationary element 14 (Fig.2). In the shown embodiment, the connecting device 10 in the collection is used as a brake, and to counteract the rotation of a driving element force through the connecting device Assembly 10 is transmitted from the fixed element 14 to the drive element 12. If the connecting device 10 in the collection is used as the coupling element 14 can be rotated under the force transmitted from the driving element 12 through the connecting device 10 Assembly to the element 14. It should be clear that the coupling device 10 can be a combination brake and clutch Assembly.

The connecting device 10 in the collection (Fig.2) includes a rotatable annular plate 18 is attached to the leading element 12. In the shown embodiment, the leading element 12 is gear connected to a rotary drive shaft (not shown). Ring group of teeth on the periphery of the gear 12 is in mesh with the corresponding teeth formed radially in the inner portion 20 of the disk 18. From opposite sides of the disk 18 in the axial direction are mounted annular friction the pads 24 and 26, having a common axis with the drive and the leading element 12.

The disk 18 is at least partially located in the housing 32 in the collection. The housing 32 in the collection still connected to the element 14. As mentioned above, when the connecting device 10 in the collection is used as a brake element 14 is fixed. However, if the connecting device 10 in the collection is used as the clutch case 32 Assembly and element 14 can be movable.

The housing 32 Assembly includes a cover or cylinder 38, the movable push plate 40 (Fig.2-4) and the support flange or stationary pressure plate 42 (Fig.2). In the annular chamber 48 formed in the cover or the cylinder 38, is mounted an annular piston 46 (Fig.2). Cover or cylinder 38 and the mounting flange 42 is still connected, so they can not move in the axial direction or to rotate relative to each other. However, the push plate 40 can be moved along continuing in the axial direction of the support legs 52 under the force transmitted from the piston 46 to the pressure plate 40.

When in the chamber 48 is pressurized with the appropriate environment, for example, with air, the piston 46 is rigidly presses the push plate 40 to the friction pad 24 on the left (as shown in Fig.2) side of the disk 18. This force causes the plate 18 to move in the axis of the second direction in the teeth of a driving element 12, to press the right (as shown in Fig.2) friction pad 26 to the support flange or pressure plate 42. Since the mounting flange or cover plate 42 is still connected with the fixed element 14, this leads to the fact that the disk 18 is rigidly clamped between the pressure plate 40 and the support flange 42 to slow the rotation of the disk relative to the housing 32 in the collection.

The annular movable push plate 40 includes a base 56 (Fig.3 and 4) and the plate element 60. The annular plate element 60 is stationary connected to the annular base 56 and has a common axis. Plate element 60 is combined with the base 56 for the formation of the annular channel 64 to the cooling medium.

Annular channel 64 to the cooling medium inlet opening 68 (Fig.2, 3 and 4) formed in the base 56 of the pressure plate 40. The flow through the inlet 68 passes through the inlet port 70 (Fig.4) in the base 56. Inlet port 70 communicates with the channel 64 to the cooling medium (Fig.2 and 3). In the shown embodiment, a cooling medium passing through the channel 64 to the cooling medium is water. However, if necessary, can be used for other cooling medium.

Medium passes from the annular channel 64 for cooling medium to the exhaust hole 74 (Fig.4), soobshayem channel 64 for cooling cf the water through the outlet channel 76 (Fig.2 and 4). The medium flows from the channel 64 to the cooling medium through the outlet channel 76 and the outlet 74. The discharge channel 76 is located diametrically opposite the inlet channel 70.

If the connecting device Assembly 10 is in a disconnected state (Fig.2), the leading element 12 and the disk 18 to rotate drive shaft (not shown), which is connected to the leading element. At this time, the friction plate 24 is located at a distance from the plate element 60 of the pressure plate 40. Similarly, the friction pad 26 is located at a distance from the fixed support flange or pressure plate 42.

If the connecting device Assembly 10 is switched from an off state to an on state, the plunger 64 (Fig.2) moves the push plate 40 in the axial direction to the rotary disc 18. This leads to sliding contact wear plate element 60 of the pressure plate 40 with a friction lining 24 on the rotary disk 18. Contact the wear plate element 60 of the pressure plate 40 with a friction lining 24 leads to the formation of heat at the sliding friction on the surface of the wear plate element. This heat is transmitted through the wear plate element 60 to the cooling medium in the channel 64 to the cooling medium.

Despite the fact that wear place is INCITY element 60 can be made of many different materials, in the shown embodiment, a wear-resistant plate element 60 made of copper or a copper alloy. Copper material wear plate element 60 efficiently conducts heat to the cooling medium in the annular channel 64 to the cooling medium. Heat transferred to the cooling medium in the channel 64 to the cooling medium, is removed from the connecting device 10 to collect the flow of cooling medium through the outlet 74. This prevents excessive heating of the wear plate element 60 and other elements of the connecting device 10 in the collection.

Wear-resistant plate element 60 includes an essentially flat outer side 60A with a wear resistant surface, as shown in Fig.3 and 4, and lower inner annular surface 60, as shown in Fig.5. The lower or inner surface 60b includes lots located therein recesses 61. The recess 61 can be located so that they take up the entire bottom surface 60b to create a turbulent secondary flow to improve heat transfer to the option to run, or can be located according to the configuration in different locations.

The recess 61 may be a hole formed through molding, pressing, stamping, cutting or machining in the bottom is th surface, and may be of any shape. According to the variant of execution of the recesses 61 are holes semicircular shape or a concave shape forming recesses hemispherical shape. Wells variant execution are the ratio of the depth (d) and diameter (D) in the range of from about 0.06 to about 0.25 for holes having a hemispherical shape, as most clearly shown in Fig.7 and 8. The ratio of step (b) holes 61 and height (H) of the channel 64 to the cooling medium is from about 2.5 to about a 4.5. The height (H) of the channel 64 to the cooling medium to the diameter (D) of the hole 61 is from about 0.2 to about 1. Other variants of execution may include other shapes, including square, rectangular, triangular or polygonal shape.

The channel 64 to the cooling medium based on the use of recesses 61 is designed to accelerate the transfer of heat from the wear plate element 60 to the flow of the cooling medium in the channel for the cooling medium. The heat transfer medium in the channel 64 to the cooling medium is accelerated through holes 61, which creates turbulent flow and the secondary flow to increase the heat transfer coefficient. Alternatively perform improved heat transfer is achieved by increasing the flow of the cooling medium in the radial outer area of the channel 64 to the cooling medium than in the radial inner area of the channel d is I the cooling medium.

Another embodiment of enhances the heat transfer by reducing the depth of the channel 64 to the cooling medium and the heat transfer is improved by the selection of areas of increased flow turbulence created by the recesses 61. The turbulence increased flow promotes mixing of the cooling medium moving along the inner side of the plate element 60, with a cooling medium moving along the inner side of the base 56 of the pressure plate 40. Despite the reduced cross-sectional area of the channel 64 to the cooling medium, the volumetric flow rate of the cooling medium through the channel to the environment is reduced. Of course, this leads to an increase in the speed at which the medium flows through the channel 64 to the cooling medium.

The channel 64 to the cooling medium has a ring configuration, which corresponds to the annular configuration of the plate element 60 of the pressure plate 40. The cooling medium flows in opposite directions, i.e. clockwise and counterclockwise from inlet 68 (Fig.2, 3 and 4) to the intake opening 74 (Fig.2 and 4). The flow of the cooling medium is divided to flow in one direction and the flow in the opposite direction immediately after the cooling medium flows from the inlet port 70 (Fig.4) in canal for the cooling medium.

The channel 64 to the cooling medium is divided into annular radial outer section 82 of the channel for the cooling medium (Fig.6) and an annular radial inner section 84 of the channel for a cooling medium through serving in the axial direction of the annular partition wall or rib 86. For additional support can be provided for an additional rib 86. Alternatively, the rib 86 may be wider to provide additional support. The radial inner and outer sections 82 and 84 of the channel have the same radial dimension. Thus, the distance from the radial outer side 90 (Fig.6) a circular section with a wall or rib 86 to the annular radial facing the inside of the side 92 of the radial outer section 82 of the channel is the same as the distance from the ring of the radial inner side 94 of the partition wall or rib 86 to the annular radial face outward side 96 of the channel 64 to the cooling medium.

Ring section with a wall or rib 86 communicates with plate element 60 (Fig.3) of the pressure plate 40 and the base 56 of the pressure plate for the formation of a radial outer and radial inner sections 82 and 84 (Fig.5) channel for the cooling medium. According to the variant of execution of the inner side 60b of the wear-resistant plate element 60 is in contact with the protruding in the axial direction is the section with the wall or rib 86 to block flow through the partition wall or rib 86.

The radial outer section 82 (Fig.6) channel has an annular bottom surface 100. The bottom surface 100 extends from the outer side 90 of the annular partition wall or rib 86 to facing the inside of the side 92 of the base 56. Similarly, the radial inner section 84 of the channel has a circular bottom surface 102 formed on the base 56. The annular bottom surface 102 extends from the radial inner side 94 of the annular partition wall or rib 86 to radial outwards of the side 96 of the base 56.

The bottom surface 100 on the radial outer section 82 of the channel is located at the same distance from facing the inside of the inner surface 60b of the wear-resistant plate element 60, and the bottom surface 102 on the radial inner section 84 of the channel. The bottom surface 100 on the radial outer section 82 of the channel is located in the same plane with the bottom surface 102 on the radial inner section 84 of the channel. Therefore, the radial outer and radial inner sections 82 and 84 of the channel have the same constant depth throughout. However, one of the sections 82 or 84 of the channel, if necessary, may be deeper than the other sections of the channel.

The recess 39 can be divided into many groups along the length of the inner side 60b of the wear-resistant plate element 60 on top of idealnoi outer and radial inner sections 82 and 84 of the channel. Group of recesses 61, located on the radial outer section 82 of the channel can be radially offset from the other groups of recesses 61 at the top of each subsection 116 radial outer section 82 of the channel. Similarly, groups of recesses 61 on top of the radial inner section 84 of the channel can be radially offset from the other groups of recesses 61 above subsection 122 radial inner section 84 of the channel.

In other versions of the top of each subsection 116 may be located the same number of recesses 61, or from top to subsection 116 or other subsections 118 in the radial outer section 82 of the channel may be provided by a different number of recesses 61. For example, from top to subsection 116 may be provided with a greater number of holes than the above subsection 118. Similarly, from top to subsection 122 may be provided with a greater number of recesses 61 than on top of the other subsections 124 in the radial inner section 84 of the channel.

Due to the presence of the recesses 61 in the subsections 116, 118, 122 and 124 (Fig.6) radially offset from each other, the flow through the radial outer and radial inner sections 82 and 84 of the channel to some extent is rejected, thereby contributing to the turbulence of flow and heat transfer from the plate element 60 (Fig.3 and 4) to the cooling medium flowing in the radial outer is the first and inner sections 82 and 84 of the channel. Of course, that if you want to deepen in subsection 116 may be radially aligned with the grooves in subsection 118. Similarly, holes in subsection 122 may be radially aligned with the grooves in subsection 124.

If the connecting device Assembly 10 is in the off state, the inner side surface 60b of the wear-resistant plate element 60 is separated some distance from the upper side surface of the partition wall or rib 86. If the connecting device Assembly 10 is in an on state, the flat portion inner side surface 60b with the recesses 61 of the wear-resistant plate element 60 (Fig.3) rests on the flat upper side surface of the partition wall or rib 86. Therefore, if the connecting device Assembly 10 is in an on state, the wear plate element 60 has a support by contacting the flat portion inner side surface 60b of the wear-resistant plate element 60 with the partition wall or rib 86. This promotes a uniform sliding contacting the outer or upper (as shown in Fig.3 and 4) lateral surface of the wear plate element 60 with a friction pad 24 (Fig.2) when the connecting device 10 in the collection of switches included in the state.

During the course of the cooling medium in the radial outer section 82 of the channel (Fig.6) a distinctive feature of the recesses 61 is that they do not reduce the area available for flow of the cooling medium, and provide improved heat transfer with less pressure drop, not speaking to the stream. Therefore, a checkerboard arrangement of the recesses 61 has the potential to create an elliptical flux field in which the phenomena occurring in the flow in one recess 61 can have a relationship with the phenomena in the flow occurring in other recesses 61. The recesses 61 are used to improve heat transfer and to promote instability of the flow, when the flow of the cooling medium moves with acceleration along the cooling channel.

In an embodiment of the invention shown in Fig.1-7, recesses 61 formed in the form of hemispherical recesses in the surface of the inner side 60b of the wear-resistant plate element 60 of the pressure plate 40. The inner side 60b of the wear-resistant plate element 60 closes the channel 64 to the cooling medium. If necessary, the recess 61 on the inner side surface 60b of the wear-resistant plate element 60 may be used in conjunction with the tabs 112 on the base 56 of the pressure plate 40. The protrusions 112 may have an elliptical shape, as shown in Fig.6.

Ug is obline 61 can be formed in the bottom surface 100, 102 of the cooling channel in the base 56 or, in other variants of execution, as in the base and the wear plate element 60. The recess 61 can be formed separately in a copper material and later connected with the base and/or wear-resistant plate element 60.

In an embodiment of the invention shown in Fig.1-7, all the cavities 61 have the same configuration. It is assumed that the recess 61 may have configurations that are different from each other and differ from the shown configurations. For example, the indentations 61 in Fig.7 can be in the form of a polygon in a plane parallel to the surface of the inner side 60b. It is expected that some of the recesses 61 may have the same configuration, and the other recess 61 may have a different configuration.

The base 56 of the pressure plate 40 may include a set of edges 150 (Fig.6) that protrude into the channel 64 to the cooling medium. Thus, the ribs 150 are protrusions, which extend between the radial facing the inside of the outer side 92 (Fig.6) channel 64 to the cooling medium and the radial inner side facing outwards 90 on the partition wall on the edge 86. In addition, the ribs 150 are continuing between the radial side facing the inside 94 section with a wall or rib 86 and the radial side facing outwards 96 Cana is and 64 for the cooling medium. Despite the fact that the ribs 150 continue along the radii of the annular channel 64 for cooling medium, if necessary, the ribs 150 may be inclined relative to the radii of the channel 64 to the cooling medium.

The height of the ribs 150 less than the height of the partition walls or ribs 86 which divides the channel 64 to the cooling medium on the radial outer section 82 of the channel and the radial inner section 84 of the channel. The section with the wall or rib 86 is in contact with the wear plate element 60 and communicates with the wear plate element for blocking flow between the radial outer and radial inner sections 82 and 84 of the channel. Ribs 150 are placed at a distance from the wear plate element 60, i.e., the upper side of the ribs 150 are placed at a distance from the bottom or inner side of the wear plate element 60.

Despite the fact that the ribs 150 in the radial outer section 82 of the channel radially aligned with the ribs 150 in the radial inner section 84 of the channel, the ribs in one section of the channel can be offset relative to the ribs in the other sections of the channel. Optionally, the ribs 150 may be shifted by a distance sufficient to position a multitude of recesses 61 in the inner side surface 60b of the wear-resistant plate element 60 between adjacent ribs, with the society, at the same radial distance from the center of curvature of the channel 64 to the cooling medium.

During the course of the cooling medium in the radial inner and outer sections 82 and 84 of the channel, the cooling medium flows in a confined space between the inner side of the wear plate element 60 and the upper sides of the ribs 150. Ribs 150 also increase the speed of the cooling medium and initiate turbulence in the cooling environment. The turbulence induced in the flow of the cooling medium ribs 150, causes the cooling fluid to collide with the flat part of the surface of the inner side 60b of the wear-resistant plate element 60 and the cavities of the recesses 61. This turbulence helps the mixing environment in the area of the ribs and the effect on heat transfer.

In addition, the ribs 150 reduce the cross-sectional area of the channel 64 to the cooling medium in the ribs 150. Thus, the area of flow of the cooling medium at the edges 150 is reduced to the space between the upper (as shown in Fig.6) the side surfaces of the ribs and the inner side surface of the wear plate element 60. By reducing the area available for flow of the cooling medium, the velocity of the cooling medium as it passes through the fins 150 increases. Increase the speed of the cooling medium contributes tour is Wantnot flow near the edges 150.

The use of ribs 150, together with the recesses 61 has been described for the variant implementation of the invention. It should be understood that the ribs 150 are additional elements to be used in conjunction with the recesses 61. The recess 61 can be used with the ribs 150 or without them. Despite the fact that the partition wall or rib 86 is preferably used for the separation of the channel 64 to the cooling medium on the radial inner and radial outer sections 82 and 84 of the channel of the cooling medium, the partition wall or rib 86 may also be provided, and may be used only deepen 61 in the inner side surface 60b of the wear-resistant plate element 60.

When switching the connecting device 10 in the collection of the off state of Fig.1 is in its on position the wear plate element 60 of the pressure plate 40 is pressed against the rotary friction plate 24 on the disk 18. The radial outer area of the disk 18 rotates at a higher speed than the radial inner area of the disk. Therefore, when switching the connecting device 10 Assembly from an off state to an on state near the radial outer area of the wear-resistant plate element 60 generates more heat than near the radial inner area snooty the CSOs plate element.

For fast cooling of the radial outer area of the wear-resistant plate element 60, where during the switching device to an on state produces the most heat, the inlet opening 68 (Fig.4) now directs a greater flow of cooling medium in the radial outer section 82 of the channel (Fig.5-6) than in the radial inner section 84 of the channel. To ensure the passage of larger flow through the radial outer section 82 of the channel cylindrical radial outer initial section 160 (Fig.4) the inlet channel 70 has a larger diameter than the cylindrical inner second section 162 of the inlet port 70.

The initial section 160 with a relatively large diameter inlet port 70 is connected with a radial outer section 82 of the channel by multiple connection channels 166 (Fig.4). Similarly, the second section 162 with a relatively small diameter inlet channel is connected with the radial inner section 84 of the channel by multiple connection channels 168. The flow of the cooling medium enters into the inlet channel 70 (Fig.4) inlet 68. From the initial section 160 of the inlet port 70 of the environment to the radial outer section 82 of the channel is relatively large volume of the cooling medium. A smaller amount of the cooling medium passes from a relatively small second section 162 of the inlet the second channel 70 environment to the radial inner section 84 of the channel.

A cylindrical initial part 160 of the inlet port 70 is approximately coaxial with the cylindrical second section 162 of the inlet channel. However, the Central axis of the second section 162 of the inlet port 70 may be offset from the Central axis of the initial section 160 of the inlet channel. If necessary, the initial section 160 of the inlet port 70 may be located on the side of the second section 162 of the inlet port, so as to have a single path of flow to the radial outer section 82 of the channel and a second separate path of flow to the radial inner section 84 of the channel.

The radial outer section 82 of the channel continues in opposite directions from the connecting channels 166 (Fig.4 and 6) to the outlet channel 76. Thus, the radial outer section 82 of the channel continues in a clockwise direction and a counterclockwise direction from the inlet port 70 to the exhaust channel 74. Similarly, the radial inner section 84 continues in opposite directions from the inlet port 70 to the exhaust channel 76. Thus, the radial inner section 84 of the channel continues in a clockwise direction and a counterclockwise direction (as shown in Fig.3) from the inlet 68 to the outlet openings 74 (Fig.4). The flow in the radial outer is the first section 82 of the channel equally divided into sections leakage flow clockwise and counterclockwise in a radial outer section of the channel. Similarly, the flow in the radial inner section 84 of the channel equally divided into sections leakage flow clockwise and counterclockwise in the radial inner section of the channel.

The discharge channel 76 (Fig.4) has the same construction as the inlet channel 70. Thus, a cylindrical discharge channel 76 has a radial outer or outlet section 174 with a larger diameter than the diameter of the radial inner or inlet pipe 176. The medium flowing in the radial inner section 84 of the channel is routed to the input section 176 through the connecting channels 180. Similarly, the environment is routed from the radial outer section 82 of the channel to the input section 174 of the outlet channel 76 through the connecting channels 182.

Cylindrical output section 174 of the outlet port 76 is located essentially on the same axis with a cylindrical inlet pipe 176 exhaust channel. However, the Central axis of the inlet pipe 176 the outlet port 76 may be offset from the Central axis of the output section 174 of the outlet channel. If necessary, the inlet section 176 of the discharge channel 76 can be located on the side of the output section 174 of the outlet, so as to have a single path of flow from the radial inner section 84 of the channel and a second separate path of flow from the radial outer is the first section 82 of the channel.

The intake and exhaust ports 70 and 76, which provide a greater flow rate for radial outer section 82 of the channel than to the radial inner section 84 of the channel, can be used in conjunction with channels for the cooling medium, having a design different from the design of the channel 64 to the cooling medium.

If the connecting device Assembly 10 is in the off state of Fig.2, the friction pads 24 and 26 on the disk 18 are located at a slight distance from moving in the axial direction of the pressure plate 40 and the fixed support flange or pressure plate 42. This allows the disk 18 to rotate freely relative to the fixed element 14 of the housing 32 in the collection.

If the connecting device Assembly 10 is switched from an off state to an on state, the piston 46 moves the push plate 40 in the axial direction of the supporting flange or pressure plate 42 to rigidly clamp the disk 18 between the pressure plate 40 and the supporting flange or pressure plate 42.

The mounting flange or cover plate 42 may be of a design similar to the design of the pressure plate 40. In this case, the elements of the support flange or pressure plate 42 are the same elements as the elements of the pressure plate 40.

Given the above description it is clear that the present invention affords the t new and improved connecting device 10 in the collection, providing improved flow of cooling medium to facilitate the transfer of heat from the elements of the connecting device Assembly. Convective heat transfer from the elements of the connecting device 10 to collect the flow of the cooling medium is facilitated by the presence of the recesses 61 in the inner surface 60b of the wear-resistant plate element 60 and, optionally, increase the speed of the cooling medium located at a distance locations along the channel 64, through which flows a cooling medium. In an enabled state of the connecting device 10 in the collection there is a tendency to the formation of a larger amount of heat in the radial outer area of the rotary disc 18 than in the radial inner area of the disk. To remove this heat flux cooling medium near the radial outer area of the rotary disc 18 may be greater than the flow of the cooling medium near the radial inner area of the rotary disk.

The connecting device 10 Assembly may include a rotary disk 18, which is at least partially contained in a housing 32 in the collection. The housing 32 in the collection may have a plate-like element 60 and transmitting the force of the surface, which may come in contact with the area of the side surface of the rotary disk 18 to retard relative rotation of the disk and the housing. To bus 32 may also have a channel 64 for cooling medium, which is at least partially formed by the inner side plate 60b of the element 60, the opposite surface, transmitting the force.

To improve heat transfer and to minimize cases, the formation of hot spots in the inner side surface 60b, a plurality of recesses 61 for the promotion of turbulence with less pressure drop in the path of flow of cooling medium through the channel 64 to the cooling medium.

The inlet 68 to the inlet of the medium in the channel 64 to the cooling medium can have a plot 160 of relatively large cross-sectional area which is connected with a radial outer section 82 of the channel for the cooling medium. The inlet opening 68 may have a plot 162 with a relatively small cross-sectional area which is connected with the radial inner section 84 of the channel 64 to the cooling medium.

The connecting device 10. designed according to the present invention, has many different characteristics, which mainly can be used together, as indicated in the description. However, these characteristics can be used separately or in conjunction with different characteristics from the current level of technology. For example, the inlet opening 68 for the cooling medium of various sizes for radial inner and radial outer sections 82 and 84 to the channel 64 to the cooling medium may be used with the tabs in the channel for the cooling medium. As another example, the channel for the cooling medium may include or may not include ribs 150.

Although described here, the connecting device 10 in the collection is used as a brake, it should be understood that the connecting device Assembly may be used as a clutch. Also provides that the connecting device Assembly may be a combination clutch and brake Assembly.

Although specific embodiments of the invention have been presented and described in detail to show the application of the present invention, it should be understood that the invention may be practiced otherwise without deviating from the principles of the invention.

1. Water-cooled connecting device Assembly for use in power transmission, comprising a housing and at least partially located in the ring of the rotary disc, the body is equipped with
vane element and transmitting the force of the surface in contact with an annular zone of the lateral surface with the above-mentioned rotary disc to retard relative rotation above the housing and a drive,
channel for the cooling medium, which is at least partially formed side plate element opposite to the transmitting force of the surface is t,
- inlet opening through which water enters above the channel for the cooling medium,
the exhaust hole through which water exits the above-mentioned channel for the cooling medium,
characterized in that
- the inner side surface of the plate element, the opposite surface of the transmitting force includes many covers her holes hemispherical shape, designed to create turbulence and turbulent secondary flow channel for the cooling medium to improve heat transfer between the plate element body and the water flowing through the channel for the cooling medium.

2. Water-cooled connecting device Assembly under item 1, characterized in that it contains multiple tabs, which includes many ribs located at a distance from each other along the channel for the cooling medium, each of the ribs is located between the radial inner section of the channel for the cooling medium and the radial outer section of the channel for the cooling medium.

3. Water-cooled connecting device Assembly under item 1, characterized in that the channel for the cooling medium has a ring configuration, with some of the many recesses are arranged in the radial outer area of the DL channel the cooling medium, and some of the above sets of recesses are arranged in the radial inner area above the channel for the cooling medium.

4. Water-cooled connecting device Assembly under item 1, characterized in that the channel for the cooling medium has a ring configuration, the above-mentioned inlet opening through which water enters the channel for the cooling medium, includes an inlet channel having a first portion which communicates with the radial outer section of the channel for the cooling medium, and a second portion which communicates with the radial inner section of the channel for the cooling medium, while the first section of the intake channel has a first cross-sectional area in a first plane located perpendicular to the longitudinal Central axis of the first section of the intake channel, and the second section of the intake channel has a second cross-sectional area in the second plane located perpendicular to the longitudinal Central axis of the second segment of the inlet channel, and the first cross-sectional area than the second cross-sectional area of to ensure the effective bandwidth of the intake channel of flow from the first section of the intake channel in the second section of the intake channel.

5. Water-cooled connecting device Assembly under item 1, characterized in that the above uglublenie who have an elliptical shape.

6. Water-cooled connecting device Assembly under item 1, characterized in that the channel for the cooling medium has an annular configuration and has a first section, continued in the first direction from the inlet to the outlet, and a second section, continued in the second direction from the inlet to the outlet.

7. Water-cooled connecting device Assembly under item 1, characterized in that the channel for the cooling medium has a ring configuration and further comprises a set of protrusions located at a distance from each other, which are located between the radial inner and radial outer marginal areas of the channel for a cooling medium and which are located at a distance from the radial inner and outer marginal areas of the channel for the cooling medium.

8. Water-cooled connecting device Assembly under item 2, characterized in that the above set of protrusions includes a set of edges, which extend between the radial inner and outer marginal areas of the channel for the cooling medium.

9. Water-cooled connecting device Assembly under item 1, characterized in that each of these recesses has a depth (d) and diameter (D), with respect to the depth (d) d is ametro (D) is from 0.06 to 0.25.

10. Water-cooled connecting device Assembly under item 1, characterized in that the channel for the cooling medium has a height (H), and each of these recesses has a diameter (D), and the ratio of height (H) of the channel for the cooling medium (d) to the diameter (D) of the recess ranges from 0.2 to 1.

11. Water-cooled connecting device Assembly under item 1, characterized in that each of these recesses is located at a distance, defined as the pitch (p) between the approximate center of each recess, and a channel for the cooling medium has a height (H), with respect to the above-mentioned step (p) to the height (H) is from 2.5 to 4.5.



 

Same patents:

FIELD: machine building.

SUBSTANCE: connecting device includes a housing, into which a rotating disc is placed. The housing has a plate-like component with an annular surface transmitting the force, which contacts the rotating disc. A medium cooling channel having an annular structure is formed with a side of plate-like component, which is opposite to the surface transmitting the force. The cooling medium channel has an inlet hole, through which medium enters the above channel and an outlet hole, through which cooling medium leaves the above channel. External radial section of the above channel is separated from internal radial section of the above channel with a section with a wall. The first and the second ribs are continued from the section with a wall through external radial part of the above channel, and the third and the fourth ribs are continued from the section with the wall through internal radial section of the above channel. Each of the ribs is located at some distance from the side of plate-like component located opposite the surface transmitting the force. Connecting device also includes the first and the second varieties of projections, which contact the side of plate-like component, which is opposite to the surface transmitting the force.

EFFECT: acceleration of heat transfer from components of the connecting device.

4 cl, 8 dwg

FIELD: transport.

SUBSTANCE: in compliance with first version, brake cooling system comprises cylinder with pressurised water-alcohol fluid, electrically driven valve, sprayer and extra pipeline. Extra pipeline comprises cylinder with low-boiling-point fluid, for example, nitrogen, filling neck with check valve and electrically driven valve arranged upstream of pipeline connection nearby sprayer. In compliance with second version, brake cooling system comprises cylinder with pressurised water-alcohol fluid, electrically driven valve, sprayer and extra pipeline. Water is said fluid in cylinder. In compliance with third version, brake cooling system comprises cylinder with pressurised water-alcohol fluid, electrically driven valve, sprayer and extra pipeline. Alcohol is said fluid in cylinder. In compliance with fourth version, system comprises electrically driven valve and sprayer arranged nearby brake disks of every wheel and cylinder with low-boiling-point fluid, for example, nitrogen, filling neck with check valve.

EFFECT: higher efficiency of cooling and safety.

4 cl, 1 dwg

FIELD: machine building.

SUBSTANCE: hydraulic jacket of disk brake consists of circular case. The circular case has a multitude of concentric channels. The first axial channel has a hydraulic connection with the first channel out of said multitude of concentric channels. The second axial channel has a hydraulic connection with the second channel out of the said multitude of concentric channels. The second channel is separated from the first channel with the third channel out of the multitude of concentric channels. According to the first version the circular case of the hydraulic jacket consists of a radial channel between the first and second axial channels, and of an entry for liquid connected to the radial channel. Direct flow of liquid from the radial channel into the third channel along axis is excluded. According to the second version the circular case of the hydraulic jacket consists of the third channel hydraulically connected with one of the first or second axial channels. Diameter of one axial channel runs across a portion of radial length of the third channel and a portion of radial length of corresponding one of the first or second channels out of the said multitude of the concentric channels. The brake consists of a stationary jacket, of a driven shaft, of the first friction disk, of the second friction disk and of a pressure plate. The first friction disk has a hydraulic jacket. The brake according to the first version has the hydraulic jacket made according to the first version. The brake according to the second version has the hydraulic jacket made according to the second version.

EFFECT: balanced flow of cooling liquid through channels of hydraulic jacket for disk brake; efficient removal of heat from disk brake.

35 cl, 3 dwg

FIELD: transport.

SUBSTANCE: proposed braking system comprises axle, support element, braking ring, braking clip to transmit braking force to braking ring, and set of appliance to force air flow through said set of holes arranged above braking ring and braking clip to transfer of heat by convection from braking ring and braking clip. Braking ring is connected with support element to form channel to transmit heat from braking ring to support element. Support element has peripheral surface with set of holes and is fitted on axle and running from said set toward peripheral surface. Braking ring comprises inner surface and is jointed with support element peripheral surface. Braking clip transmitting braking force to braking ring is arranged on braking ring inner surface to interact therewith.

EFFECT: improved cooling and expanded operating performances.

9 cl, 6 dwg

FIELD: mechanical engineering.

SUBSTANCE: braking device comprises the stack of friction disks cooled by fluid. The movable disks are set in the grooves in the rotating bushing, and unmovable disks are set in the grooves in the unmovable housing. The braking device is provided with the block of eight cylinders and eight clearance controllers. The cylinder block is provided with three connecting pipes. One connecting pipe is connected with the brake actuator. The two other connecting pipes are used for supplying and discharging fluid for cooling the brake. Both sides of the friction disks are provided with sectors made of a friction material. The movable disks are provided with eight sectors made of metal ceramic, and unmovable disks are provided with eight bimetallic sectors.

EFFECT: enhanced reliability.

4 dwg

FIELD: transport mechanical engineering.

SUBSTANCE: disk block comprises housing with projections having friction surface, back side, and cooling jacket. The cooling jacket is made of at least one metallic pipe mounted inside the block concentrically to its axis from the back side to eliminate the space between the metallic pipe and housing of the block. The ends of the pipe project over the back side of the disk block. The metallic pipe is flush-mounted with the back side of the block and has oval cross-section whose greater axis is parallel to the friction surface.

EFFECT: enhanced heat exchange and prolonged service life.

1 dwg

The invention relates to a device for the clutch and brake operating on lubrication and cooling oil

The invention relates to mechanical engineering and can be used in heavily loaded drum-Shoe brakes hoisting-and-transport, road and construction machines and vehicles

FIELD: transport.

SUBSTANCE: invention relates to railway transport, specifically to braking systems of rail vehicles. The parking brake includes braking cylinder with piston actuated by working fluid, as well as with parking brake having control lever installed with rotation possibility which rotation is transferred to shaft. The piston actuates piston rod of wheel brake cylinder which rod is coaxial with braking cylinder axis. The shaft is installed with possibility to turn perpendicular to braking cylinder axis via shaft bearing in body. Control lever is intended to initiate shaft rotating movement which is transformed into parallel to braking cylinder axis linear movement of support roller installed with possibility to rotate by means of support roller bearing on parallel to shaft axis of rotation by means of cam. The cam has working surface interacting with radial outer surface of support roller during clamping or releasing travel of parking brake. Cam working surface is made as portion of cylinder surface circumference the central axis of which performs circular trajectory of movement around shaft axis during clamping or releasing travel of parking brake.

EFFECT: higher efficiency factor of device.

13 cl, 6 dwg

FIELD: machine building.

SUBSTANCE: invention refers to an adjustment device for a disk brake mechanism. The adjustment device (1) is intended to control wear of brake pads (23) and pneumatically controlled disk brake mechanism (20) with a brake disk (20). The adjustment device (1) is actuated by a rotating lever of a clamping device. The clamping device can be inserted into an adjustment screw (25) of the disk brake mechanism (20). The adjustment device (1) comprises a connection ring (8) for coupling with a bush (14) made from resilient material which is engaged with the adjustment screw (25). A blocking unit is installed between the adjustment screw (25) and the adjustment device (1) and forms a limiter in the tangential direction in relation to the direction of rotation for the adjustment screw (25).

EFFECT: limitation of return rotation of the adjustment screw is provided.

6 cl, 13 dwg

FIELD: transport.

SUBSTANCE: invention relates to disc brake. Proposed brake comprises brake beam calliper (1) surrounding the brake disc (2) and brake shoe-linings (3) to be pressed against disc (2) both sides, one can be actuated on clamp side by the cam of clamping device brake lever (5) turning about the pin. Besides, this brake comprises the self-reinforcing device that features self-reinforcement factor selected so that after braking this brake releases automatically. Compressed air brake cylinder push-rod can act on lever (5). Said lever (5) thrusts on at least one ball-like support element (10) in calliper (1) that makes the cam pivot pin. Said element (10) abuts on support ball (9) located in direction of push-rod action above support element (10) and positioned in brake plunger (6) connected with lining (3) located on clamp side. Pressure plungers (7) are arranged on both sides of plunger (6) and spaced apart. One end of said pressure plunger rests on clamp (1) while opposite end thrusts via support ball (16) on lining (3). Pressure plunger (7) is secured in guide plate (4) arranged to displace to the axis of brake disc (2) in the brake mechanism shield (8).

EFFECT: optimised design, weight and sizes, higher efficiency.

9 cl, 4 dwg

FIELD: transport.

SUBSTANCE: invention relates to disc brake. Propose brake comprises brake external clamp (1), brake shoe linings (2) to be pressed against brake disc, one being driven by brake lever (5) that turns about clamp cam pin. Brake rod (6) abuts on the clamp from end side, said rod being connected from opposite side to lining (2) from clamp side or to guide plate (9) connected therewith. It comprises two spaced apart pressure rods (4) located in one direction connected to clamp (1) and lining (2) or to guide plate (9), and self-booster. Clamp (1) has hemisphere-shaped bearing seats (13, 15) accommodating plain bearing elements (14, 16) fitted therein for brake lever (5) and pressure rod (4) to thrust by their side bent off lining (2) against clamp (1). Brake rod (6) is coupled with lining (2) and latch.

EFFECT: perfected simple design, lower costs, longer life and higher reliability.

7 cl, 4 dwg

FIELD: automobile production.

SUBSTANCE: disc brake includes a calliper, an actuating mechanism and a fastener to fix an actuating mechanism on the calliper. Functional holes of the calliper and the actuating mechanism serve for connection of the actuating mechanism to a clamping device. The fastener is designed so that the second flange surface in the area located between the second functional hole and the fastener can be bent or deformed against elastic restoring force, and the restoring force can bring the second flange surface in individual sections to the pre-tension state in the direction to the first flange surface. The disc brake calliper, in which the first flange surface between the fastener and the functional holes is not flat. The actuating mechanism of the brake, in which the second flange surface between the fastener and the functional holes is not flat.

EFFECT: improving reliability owing to reducing negative effects on an actuating mechanism and a disc brake.

16 cl, 8 dwg

FIELD: transport.

SUBSTANCE: disc brake consists of shoe body, shoe friction linings, brake disc, mechanism with two bell cranks and springs, brake air cylinder and pins of said bell cranks. Brake disc is fitted at mounted axle of transport facility. Disc brake comprises friction discs arranged at both sides of friction disc that make, along with shoe friction linings, at least three surfaces of friction. Inner friction discs are composed of segments secured at body axle. Outer friction discs are composed of segment rings secured at brake disc axles with straps coupling said segments by screws. Friction discs comprises extra springs fitted at axles to make clearance over friction surface.

EFFECT: higher efficiency of braking, decreased sizes, simplified design, expanded operating performances.

2 dwg

FIELD: machine building.

SUBSTANCE: automatic slack adjuster includes a casing in which there provided is a hole into which a breaking cam shaft is inserted, a worm gear having the possibility of being engaged with a breaking worm shaft, a drive of a slack adjuster, a lever of the breaking drive and an assembly of one-sided coupling. Assembly of one-sided coupling includes a supporting arm, a supporting bracket attached to the supporting arm without any rotation possibility, a side plate, a gear and a one-sided clutch. The supporting arm has a hole into which a break cam shaft is inserted. The hole in the supporting arm is located coaxially to the hole made in the casing. The sided plate and the gear are coaxially pressed between the supporting arm and the supporting bracket so that rotation of the side plate and the gear about a common axis is provided. One-sided latch is located on the supporting bracket and deflected in radial outside direction from one-sided teeth formed on internal radius of the gear. Teeth of the gear on the outside circumference of the gear of the one-sided coupling are engaged with an adjusting screw that will transfer movement of the gear to the slack adjuster drive.

EFFECT: simpler manufacture of a slack adjuster.

8 cl, 7 dwg

FIELD: machine building.

SUBSTANCE: disk braking mechanism with self-boosting includes a clamp of disk braking mechanism, which is retained on a stationary support of disk braking mechanism, with brake pads, a self-boosting device and a brake plunger having the possibility of being brought into action by means of a brake lever, with a clamping device and with an adjustment device to adjust wear rate of brake pad and/or brake disk. Self-boosting device has a pressure plunger that adjoins the brake pad through an expanding support on end surface on the clamp side and that is located with its end zone facing the brake pad in a guide plate movably retained in the braking mechanism support. Expanding support in non-operating position of the self-boosting device is enclosed with sealing structure. Brake pad includes a cavity having a ramp outline, and pressure disk of the brake pad or another disk include a collar on the side facing from the friction pad, with a receiving element having the possibility of retaining pressure plunger.

EFFECT: improving operating reliability and increasing service life.

24 cl, 1 dwg

FIELD: transport.

SUBSTANCE: invention relates to machine building, particularly, to combine brake cylinders. Combined brake cylinder comprises cylinder of working braking mechanism, an active working brake, driven by working fluid displaced by piston and braking mechanism cylinder with spring energy accumulator, a passive parking brake. Piston of aforesaid braking mechanism cylinder with spring energy accumulator and rod of cylinder of working braking mechanism piston are aligned. In case piston stroke in aforesaid braking mechanism cylinder with spring energy accumulator increases power transfer ratio increases as well. Rail mounted vehicle disc type braking mechanism support unit incorporates said combined braking cylinder.

EFFECT: compact design, maximised force of braking.

25 cl, 15 dwg

FIELD: transport.

SUBSTANCE: invention relates to rolling stock brake systems. Disc brake comprises friction unit. Friction unit is composed of radial double-row thrust bearing with medium ring making the brake disc rigidly fitted on mounted axle while two thrust rings make linings. Said linings are pressed to medium ring by levers coupled with brake cylinder. Outer surface of medium ring and inner surfaces of thrust rings have taper grooves to accommodate the balls.

EFFECT: reduced thermal load and wear of disc brake friction pair.

4 dwg

Coupling // 2466310

FIELD: machine building.

SUBSTANCE: coupling includes housing that consists of cylinder with flanges on ends and connected to it input and output covers. In the central hole of input cover there fixed is a coupling position stabiliser that is connected to air pipe-line. Inside the housing there is an internal part of hollow rod with piston fixed on it. Input cover with fixed levers has central hole with sealing for passing of hollow rod external part. At the external part of hollow rod there fixed is a disk with slots on the periphery, with annular recess in the hub and projections closed by partition from gas permeable material. The cavity formed between disk and partition is connected to internal cavity of the rod via hole in annular recess wall and hole in hollow rod wall. The end of external part of hollow rod is made in a form of external cone contacting the internal cone made in the bush fixed in the cage at pneumatic unit shaft. Flat end of the bush contacts permeable partition on disk, in the periphery slots of which there inserted are the levers fixed at the input cover.

EFFECT: increase of coupling pressurisation, extension of sealing element service life, structure simplification.

3 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to devices for transmission of rotation and it can be used in drives of heavy loaded processing equipment. Proposed hydrostatic safety flexibly damping coupling contains two coupling members mechanically intercoupled by transfer device and hydraulic cylinder. Hydraulic cylinder is connected with damper and hydraulic accumulator through controllable hydraulic distributor with system of control according to torque on coupling. Inputs and outputs of hydraulic distributor are made for alternate connection of hydraulic cylinder with damper and hydraulic accumulator. Transfer device is made in form of screw-nut mechanism and splined bushing. Screw is secured on one coupling member and is coupled with nut and hydraulic cylinder, and splined bushing is secured on other coupling member, being coupled with nut by splined joint. Said mechanism is provided with non-self-braking thread.

EFFECT: provision of larger angle of relative turning of coupling members; improved of damping properties of coupling, reduced contact stresses in parts of transfer device; improved reliability and increased service life of coupling.

9 cl, 9 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to devices for transmission of rotation and it can be used in drives of heavy loaded processing equipment. Proposed hydrostatic safety flexibly damping coupling contains two coupling members mechanically intercoupled by transfer device and hydraulic cylinder. Hydraulic cylinder is connected with damper and hydraulic accumulator through controllable hydraulic distributor with system of control according to torque on coupling. Inputs and outputs of hydraulic distributor are made for alternate connection of hydraulic cylinder with damper and hydraulic accumulator. Transfer device is made in form of screw-nut mechanism and splined bushing. Screw is secured on one coupling member and is coupled with nut and hydraulic cylinder, and splined bushing is secured on other coupling member, being coupled with nut by splined joint. Said mechanism is provided with non-self-braking thread.

EFFECT: provision of larger angle of relative turning of coupling members; improved of damping properties of coupling, reduced contact stresses in parts of transfer device; improved reliability and increased service life of coupling.

9 cl, 9 dwg

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