Hinge for a vehicle (options) and dual tapered roller bearing unit

 

(57) Abstract:

The inventive hinge of transport with trailer has front and rear frames are connected at a pair of coaxially on a vertical hinge. Each hinge includes a similar roller bearing assemblies attached to the front of the frame and having a rotatable protruding pin. The rear portion of the frame includes an undercut for going down pins and the cover for holding pins. Pin each bearing Assembly includes made with the ledge of the finger with the first bearing cone, located at the ledge, and the second bearing cone, spaced from the first cone, spacer ring, calling on the finger is shifted to the second cone by means of end caps attached to the end of the finger. Package shims between the end cap and the end of the finger limits the amount by which the space between the cones can be narrowed to limit and control the pre-load of the bearing unit. The technical result is that the design of the exoskeleton allows you to allow easy adjustment and replacement. 3 S. and 8 C.p. f-crystals, 5 Il.

The invention otnositel means a semi-trailer, having the front and rear frames connected by the pivot point.

Transport the trailer to withstand significant force effects that occur due to loading, moving, force interaction of components and the weight of the conveyor means. Ideally, the hinge nodes should not be too massive or heavy, it must be ensured the possibility of their easy adjustment and replacement.

In the first known system uses spherical bearings, as shown in U.S. patent N 3806158 in the name of Casey. Spherical bearings operate by way of a "ball and socket" and able to withstand high radial and axial loads due to the large areas of contact of the bearing surfaces. However, spherical bearings vulnerable to wear and tear due to the fact that they use a contact slip. Wear can enhance abrasive contamination present in the environment of execution of mining or construction work.

In order to avoid problems of wear, interconnected with spherical bearings in a known transport means with a semi-trailer used roller bearings. However, Lucaya in weight, the bulkiness and complexity of maintenance and replacement. One known system uses two roller bearing Assembly. The first node represents a large main bearing with double raceway tapered rollers to transfer a substantial part of the radial load between the parts of the frame and to hold the entire vertical axial load. The second node includes a self-aligning vertical bearing which transmits only radial loads. The second bearing must be capable of self for adapting to the gaps between the welded joints of the frame, which carries the bearings. Fairly accurate gap between the welded connections can only be achieved by machining the welded joints, which requires a high cost. If two such bearing Assembly tapered roller would be attached to the frame of the conveyor means with error tolerances for welding, this would lead to unacceptable pre-axial immersion bearings, which greatly weakened the ability of the bearings to withstand the operating loads.

Additional deficiencies shall bear all of the axial load, that makes it bulky and heavy. Although self-aligning bearing can be more compact and have a small weight, bulkiness and weight of the fixed bearing makes it undesirable for certain applications, for example in the case of underground mining conveyor means requiring structures with small dimensions. In addition, the frame itself must be heavier than the welded joints, to which is attached a fixed bearing to transfer all vertical loads.

In the case of the known hinges of the conveyor means, in which roller bearings are used, there are difficulties in carrying out their maintenance and replacement. When the maximum stiffness of the bearing system nodes with conical rollers are usually regulated at the pre-load, meaning that the conical raceways are shifted toward each other to compress the rollers of the bearing between the cones and the outer ring. For less wear, it may be necessary to carry out the adjustment of the bearing to return a pre-load to the desired level. Existing roller bearing assemblies require removal and disassembly of such nodes in order to produce them is Lipnica and there is the possibility of contaminants into the interior node, which leads to a particularly serious problem when the adjustment must be performed in the operating conditions. In addition, a complete replacement of the known bearing arrangement usually requires at least two setups for the selection of appropriate shims to achieve the desired preload in the new bearing. Maintenance and installation conditions also requires heavy use of special tools, which are usually not available and the inclusion of which in the structure of transport would lead to significant costs.

In view of the above problems, interconnected with the existing transport means with the trailer, there is a need to develop a joint for such transport, which would help to alleviate these problems. Therefore, this is the main purpose of the present invention.

Other important objectives of the present invention include the following nodes:

above the pivot point of transport with trailer, not susceptible to excessive wear,

the above site, which has limited who can be served and pre-adjusted prior to installation on the conveyor means,

the above-mentioned node, which can be adjusted without disturbing the seals bearings

the above site, pre-loading of which can be adjusted without demounting operations of the shipping agent.

According to a variant of implementation of the construction of the present invention, the main goal is achieved by creating a pivot point for the transport with trailer, with the front part of the frame with two made in one piece with the plates of the chassis, each of them has an attached tapered roller bearing unit containing a rotary protruding pin. The rear part of the frame contains the corresponding undercut and cover for holding pins. Each bearing unit has identical dimensions to separate the radial and axial load with pin, including the neck, which come apart from each other, the first and second cones, when this period is limited to the ledge of the neck, adjacent the first sleeve, and the compression ring, the setting on the neck adjacent to the second cone and limited end cap attached to the end of the neck. The gasket between tarocchino can be adjusted by loosening one of the covers of the trunnion, remove end cover and replace the gasket on the gasket of a different thickness, replace the end cover and re-mount cap trunnion.

In Fig. 1 presents a side view of the conveyor means with a semi-trailer according to a preferred variant implementation of the present invention.

In Fig. 2 presents a side view cross-section of the hinge unit, performed according to the variant shown in Fig.1 along the line 2-2.

In Fig.3 presents a top view of the hinged node according to the variant shown in Fig.1.

In Fig.4 shows a side view cross-ecene exoskeleton shown in Fig.1 and 2, showing details of the bearing Assembly as the pivot point.

In Fig. 5 presents a side view similar to Fig.2 and 4, but showing the cross-section of the bearing unit according to the alternative implementation designs.

In Fig.1 presents a low-profile mine transport vehicle 10 with a semi-trailer having a front part 12 of the frame and its rear part 14 connected to each other through upper strut 18 and the lower pivot point 20, providing a swivel to rotate on vertor. Front frame 12 includes front wheels 34 and node 36 in the boot of the bucket located at the front part of the conveyor means.

In Fig.2 shows the upper hinge 18, which essentially has the same structure and performs the same function as the lower hinge 20. Rear frame 14 includes a top rear plate 40 of the chassis and the bottom of the rear plate 42 of the chassis. Chassis plate are in the front direction in a horizontal spaced apart parallel planes. Front frame 12 includes a protruding in the rear direction, the front plate 44 of the chassis, which is oriented horizontally and can be located in the middle between the rear plates 40 and 42 of the chassis.

Bearing unit 48 has an outer fixed portion 50 attached to the front plate of the chassis, and a rotary cylindrical trunnion 52 held within the fixed part. The trunnion has a cylindrical portion 54 protruding up and down in the vertical direction of the bearing unit 48, and is attached to the rear plates 40, 42 of the chassis.

The front plate 44 of the chassis includes a round reinforced end portion 56, which is above and below the respective upper and lower powerstock 58, centered on the vertical axis 22 perpendicular to the plate 44. Reinforced portion 56 advanced forms ravenously circular series of holes 60 with guaranteed clearance, fully drilled through the reinforced portion 56. Plate 44 additionally includes a socket 62, forming a channel 66 which is connected through a hole (not shown) with the interior of the bore 58 in order to transfer the lubricant in the bore.

As shown in Fig. 3, the upper back plate 40 of the chassis ends in front of the flat surface 68 and forms a semi-cylindrical recess 70 with a vertical axis located in the plane of the flat surface 68 and is centered in the middle of it. Cover 74 axle, forming a semi-cylindrical recess 76, with the possibility of removal attached to the back plate 40 of the chassis by means of bolts 78 to firmly grasp the cylindrical portion 54 of the pin 52. The radii of curvature of the cylindrical portions 54 and the semi-cylindrical recesses 70, 76 essentially the same, so as to provide maximum contact area between the pin and recesses.

In Fig. 4 shows a bearing unit 48 without construction of transport, to which it is usually attached at Aeromonas part 50. The fixed part 50 includes a cylindrical plug ring 82 having an outer diameter which value is chosen such that it tightly went into the bore 58, as shown in Fig.2. Push the ring 82 has a height equal to the thickness of the reinforced portion 56, and forms a certain amount of running around the circumference of the grooves 84 in order to facilitate the circulation of the lubrication provided by the pipe 62. Using a large number of radial holes (not shown) transfers lubricant from the grooves 84 to the inner part of the ring 82. The outer ring 88 of the bearing with double raceway in the press fit tightly installed inside the ring 82 and provides a pair of conical raceways 90, 92, turned inward, c upper raceway 90, slightly turned up, and with the lower raceway 92, slightly facing down. The outer ring 88 of the bearing forms a large number of lubricating holes 94 to move the lubricant to the raceway 90, 92.

Above and below the outer ring 88 are located opposite one another, the plates 96, 98, intended to hold the bearing. Each plate has an outer diameter corresponding to the diameter of the reinforced portion 56 of the front plates of the opposite drilled holes 102 with guaranteed clearance, coinciding with the holes 60 with guaranteed clearance of the front chassis plate, as shown in Fig.3. If you again refer to Fig.4, each of the plates 96, 98 forms a Central opening 106 which carries the seal 108 to tight and provides a seal overriding protruding cylindrical portions 54 of the trunnion 52. Each plate 96, 98 additionally includes a rim 110, concentric with the hole 106 and corresponding to the diameter of the outer ring 88. Flanges 110 sufficiently protrude above the surface of the plates, so that the filler ring 82 is not in contact with the surfaces of both plates when the outer ring 88 is compressed between the edges 110. As a result, the ring 82 provides only radial coincidence with the bore 58 and does not determine the axial position of the plates 96, 98 relative to each other or the front plate 44 of the chassis.

If we refer to Fig.2, each retaining plate 96, 98 is attached to the front plate 44 of the chassis by a number of bolts 114 with the screw thread passing through holes 60 with guaranteed clearance. The screw heads recessed in the bore hole 102 with a guaranteed gap, and on the ends of the bolts are screwed nuts 116, held in orelena to the front plate 44 of the chassis by six equally spaced from each other bolts 114. In the case where the interval between the holding plates is determined by the height of the outer ring 88, only installed the first lower holding plate 98 is pressed against the front plate 44 of the chassis.

As shown in Fig. 4, the pin 52 includes a neck or finger 118 having a cylindrical part 120, centered on the axis 22 of the hinge, and a coaxial cylindrical head 124, the diameter of which is larger than the diameter of the cylindrical part 120 to ensure ledge 126. The head 124 with providing a seal walks into a seal 108 and serves as a lower protruding cylindrical part 54 of the trunnion. The cylindrical portion 120 opposite ends of the cylinder 124 at the forward surface 128 perpendicular to the axis 22 of the hinge. In the fore part of the finger 118 is formed by a number of threaded bores 130.

The first cone 134 bearing having a conical surface 136 raceway, tightly enters the cylindrical part 120 for linking up to the ledge 126, while the cone 134 is oriented so that the surface 136 of the raceway mainly directed radially outward and axially slightly away from the head 124 of the finger 118. The first group of tapered roller bearings 138 surrounds the first concenus 142, identical to the first cone 134, enters the cylindrical part 120, but with the opposite orientation, so that the cones 138 and 142 taper in opposite directions. The second cone 142 has a tapered surface 144 of the raceway, which faces radially outwardly and slightly axially to the head 124 of the finger 118. The second group of tapered roller bearings 146 is located between the second cone 142 and the upper raceway 90 of the outer ring 88 of the bearing.

In a preferred embodiment, the structure shown in Fig. 4, the first and second cones 134 and 142 are separated from each other by a gap 148. The narrowing of the gap 148 is limited by the axial component of the forces between the surfaces of the raceways and rollers, so that the displacement of the cones to each other will create a pre-load of the bearing unit. That is, the rollers will be compressed between tracks even when the load bearing to the node 48 is not attached. This pre-loading is useful when you need to maximize the stiffness of the system.

Solid spacer ring 152 tightly comes on the cylindrical portion 120 of the finger 118 so that it is adjacent to the second cone 142. Spacer ring 152 and the and the upper seal 108, in order to be compacted around the circumference of the installation process. Having cut the spacer ring 154 tightly enters the cylindrical part 120 to the junction of the intermediate ring 152. As shown in Fig.2, with the cut spacer ring 154 is higher than the thickness of the upper rear plate 40 of the chassis in order to provide a separate surface for clamping the chassis plate, and the cover 74 of the stud. The ring 154 has a slit to allow transmission of pressure generated by tightening of the cap 74 axle, to the finger 118 in order to avoid slippage. The ring 154 slit is usually held for a short distance beyond the nose portion 128 of the finger. As shown in Fig.4, this provides a recess for the gasket or group of spacers 158, intended for the location of the bow 128 without passing above the split ring 154.

End cover 160, formed of a rigid circular plate has an outer diameter corresponding to the diameter of the head portion 124 of the finger. Cover 160 coincides with the split ring 154, lying end to end relative to the strips 158. End cover 160 forms a large number of holes 162 with a guaranteed gap coinciding with the screw cutting holes 0, to force to cause the split ring 154 in the power contact pads 158 and cause the spacer ring 152 and the second cone 142 to come to the first cone 134, thereby increasing the pre-load of the node. The gap 148 between the cones and the amount of pre-load is limited by the thickness of spacers 158, which provide positive stop against excessive tightening of bolts 164. Rings 152 and 154, the end cap 160 and bolts 164 in conjunction with each other to form a compressive element. The head portion 124 of the finger 118 forms a Central bore 168 which is designed for engagement with a torque wrench when testing pre-load of the node by determining the resistance to rotation.

In Fig.5 shows an alternative implementation of a bearing Assembly 48', which differs from the variant according to Fig.4 in that it uses a different approach in relation to adjustment by using thin strips. Alternative node 48' includes the adjustment ring 170 located between the first cone 134 and the second cone 142 so that it completely took the gap 148, while the cones are adjacent to opposite sides of the ring 170. Gasket 158 agree adjustable ring 170 determines the gap between the cones 134 and 142, and thereby determines the amount of preload of the bearing. When mounting the end cover 160 is bolted to the finger 118 to compress the set of spacer rings 152, 154, cones 134 and 142 and the adjustment ring 170 to the ledge 126. Although access to the adjusting ring 170 to replace the node 48' should be largely dismantled, this option provides the absolutely exact gap between the cones for specified values of pre-load.

The outer ring of the bearing cones and rollers equivalent part numbers 63788 and 673220, which can be obtained from the Timken Company, Canton, Ohio. These details include the adjustment ring 170, which is removed in a preferred variant of the construction according to Fig.1-4. The bearing according to a preferred variant implementation of the design has a hole with a diameter of five inches (127 mm) for going down on him finger of the same diameter.

Installation and replacement.

Bearing unit 48 according to a preferred variant implementation structures to a significant extent can be assembled, adjusted and tested prior to its installation. The subassembly consists of the entire bearing unit 48 minus the retaining plates of the first cone 134, 2) the first bearing group 138, 3) outer ring 88 of the bearing with the related plug ring 82, 4) of the second group of roller bearings 146, 5) of the second cone 142, 6) spacer ring 152, 7) split ring 154 with spacers 158, positioned at a forward portion 128 of the finger and then fastened by means of the end cap 160. This subassembly, though not sealed against contaminants that can be tested in torsion and adjusted at the factory without the need for subsequent disassembly for installation in an enterprise or conditions.

For mounting on a transport vehicle of the lower holding plate 98 is bolted to the underside of the plate 44 of the chassis, so that the subassembly can be installed from the top with the head part 124 of the finger, moving through the lower seal 108, and with the detachable ring 82, tight coming into the bore 58. After this is installed from above the upper holding plate 96, so that the upper seal 108 slides down the end cap 160 and the spacer rings 154, 152. Then the upper holding plate 96 is bolted to the plate 44 of the chassis.

If the bearing Assembly 48 is mounted on the front part of the conveyor means, seznamime cylindrical portions 54 of the pin 52 within the semi-cylindrical recesses 70 of the rear plates of the chassis. With this arrangement, the cover 74 trunnion mounted for reliable clamping of the head 124 of the finger and a split spacer ring 154. Rear chassis plate are separated from each other at a sufficient distance, so that between each plate of the chassis and the corresponding plate to hold the bearing, a gap 171. This allows you to set a pin in any place within the range of vertical positions, and therefore, allowed significant errors vertical dimensions between the various plates of the chassis frame.

To replace a damaged or worn out bearing unit in operation stage of the installation is performed in reverse order. Going to replace the bearing unit can be installed by using the original mounting procedure to prevent contact of pollutants with roller bearings, usually protected by seals.

Adjusting the preload of the bearing.

Adjusting pre-load the bearing can easily be performed under operating conditions without significant disassembly or any violation of the seal of the bearing. If normal wear and tear leads to the fall of the led is OK on a more subtle package will reduce the gap between the cones and to increase pre-load. For re-adjustment of the upper cover 74 of the axle is released, to allow axial sliding split spacer ring 154 relative to the finger 118. Then together with the end cap 160 is removed bolts 164 having a threaded cuts. After this package 158 thin strips replaced by a more subtle package pads and re-install end cover bolts, moving the spacer ring and the second cone is closer to the first cone. Seals 108 are not violated, and the transport vehicle is fully assembled, the lower cover 74 axle remains attached to the head 124 of the finger during the whole process oscillations.

Although the illustration and description of the principles of the invention presents preferred implementation for qualified specialists will be obvious that the device according to the invention and existing components can be modified, however, without deviating from its principles. The claimed invention includes not only presents its implementation, but all of its modifications, alternatives and equivalents that are within the scope of the following claims and not deviating osobnicy node, includes a roller bearing mounted on the axle with the fixation of radial offset and placed in the oven front frame, oriented horizontally, with the axle installed in the upper and lower oriented horizontal plates of the rear frame, which is placed between the oven front frame, a second bearing Assembly comprising a roller bearing mounted on the axle and placed in the front plate of the front frame, oriented horizontally, the pin is installed in the upper and lower oriented horizontal plates of the rear frame, which is placed between the oven front frame, this roller bearing of this node are fixed against radial and axial displacement relative to its axle, and both bearings have the possibility of rotation around the vertical axis as the pivot point, wherein the roller bearing of the first bearing Assembly is fixed against axial displacement relative to its axle, and the rear plate frames are made with removable covers, each of which together with your plate when you pin forms a hole for the mounting stud, with the stud inserted in the holes of the plates of the rear frame rotatably around Vertica the x nodes includes a pair of tapered roller bearings.

3. Site under item 2, wherein each of the bearing assemblies includes a pair of tapered roller bearings.

4. Site under item 1, characterized in that the inner raceway of the bearing of the first bearing Assembly mounted on the trunnion, with the possibility of retrieval.

5. Dual bearing unit designed for use in the hinge connection of the vehicle with a trailer containing a pin having a cylindrical neck, ring, surrounds the neck of the axle, the two tapered roller bearing located on the neck of the stud and secured against axial displacement along the cervical roll neck, with speakers from the ring of the cylindrical part for connection with parts of the frame of the vehicle and semitrailer, a cylindrical cap mounted on one end of the axle to tighten the rings to the side bearings, bolts for attaching the cover to the axle and change the radial load on the bearings, characterized in that that pin is installed in parts of the frames with the possibility of rotation and has a Central bore for engagement with a torque wrench to measure the radial load during the rotation of the axle in roller bearings and the wife between the ledge and the ring.

6. Site under item 5, characterized in that it contains a gasket placed between the cover and the pin to limit movement of the cover when it's fixed with bolts.

7. Hinge for a vehicle with a trailer containing two bearing units, each of which contains a pin with a cylindrical neck having first and second ends, the ring, covering the middle part of the specified cervix so that the first and second ends of the neck are in the form of cylindrical parts of the ring and are used to connect with the parts of one frame of the vehicle, and two tapered roller bearing, mounted on the neck between the ring and the first end of the neck and pressed to contact through the ring of the cylindrical cap from the second end of the neck to limit axial displacement of the bearings, this hinge Assembly is provided with a latch for each bearing unit for connecting this site with other parts of the frame, wherein the side frames are made with lids for pressing the protruding cylindrical portions cervical axle to these frames, axles installed in parts of the frames with the possibility of rotation and with a ledge on the neck, the bearings are located between the ledge and the ring.

8. Node mi to change the position of the cap relative to the neck.

9. Site under item 7, characterized in that for measuring the radial load by cervical rotation in roller bearings the neck is made with the possibility of attaching thereto a torque wrench.

10. Site under item 7, wherein to restrict the movement of the lid when its fastening bolts it comes with spacers placed between the cap and neck.

11. Site under item 7, characterized in that it is equipped with an adjusting ring, which is placed between the two roller bearings to limit movement of the cover when tightening its bolts.

 

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