CN210665060U

CN210665060U - Wide-temperature-range four-dimensional driving joint bearing testing machine

Info

Publication number: CN210665060U
Application number: CN201921955418.2U
Authority: CN
Inventors: 张斌; 任宁; 卓继志; 吴飞; 徐建波; 章有良; 陈芳华; 孙岩
Original assignee: Zhejiang Testing & Inspection Institute For Mechanical And Electrical Products Quality; Zhejiang Institute of Mechanical and Electrical Engineering Co Ltd
Current assignee: Zhejiang Mechanical And Electrical Product Quality Inspection Institute Co ltd
Priority date: 2019-11-13
Filing date: 2019-11-13
Publication date: 2020-06-02
Anticipated expiration: 2029-11-13

Abstract

The utility model relates to a bearing test technical field specifically discloses a wide temperature range four-dimensional drive joint bearing testing machine, includes fuselage, high low temperature environment case at least, is located test unit, X axle loading subassembly, X axle swing subassembly, Z axle loading subassembly and Z axle swing subassembly in the high low temperature environment case. In the structure, the high-temperature and low-temperature environment box is arranged, so that the bearing to be tested is subjected to a simulation test in a sealed environment, test conditions at different temperatures can be simulated, the simulation test conditions are closer to the operation working condition of the bearing, and the test result is more reliable; the four-dimensional driving system is provided with an X-axis loading assembly, an X-axis swinging assembly, a Z-axis loading assembly and a Z-axis swinging assembly, and the test working condition requirements of the knuckle bearing on two-dimensional swinging and two-dimensional push-pull load are met.

Description

Wide-temperature-range four-dimensional driving joint bearing testing machine

Technical Field

The utility model relates to a bearing test technical field, concretely relates to wide temperature range four-dimensional drive joint bearing testing machine.

Background

The joint bearing is a mechanical universal part, has the characteristics of small volume and high bearing capacity, and is widely applied to the fields of aviation, aerospace, trains, automobiles, mining machinery, machine tools, engineering machinery and the like when in actual work.

The dynamic life of a joint bearing is generally evaluated by means of a simulation test machine, since the joint bearing is generally subjected to four-dimensional loading, namely: the reciprocating deflection of the outer ring around the radial direction, the bidirectional push-pull loading of the outer ring along the radial direction, the reciprocating swing or rotation of the inner ring around the axis, and the bidirectional push-pull loading of the inner ring along the axial direction. In addition, the linkage of the four dimensions is realized by the inner ring and the outer ring independently to move correspondingly, and the phenomenon of mutual interference cannot be generated between the loading motions of the dimensions.

However, the existing bearing test equipment cannot simultaneously simulate the four-dimensional loading. Therefore, the applicant specially designs a wide-temperature-range four-dimensional driving joint bearing testing machine to realize the simulation test of the joint bearing.

Disclosure of Invention

The to-be-solved technical problem of the utility model is, solve among the prior art bearing test equipment and can't realize the loaded technical defect to joint bearing four dimensions.

In order to solve the technical problem, the utility model provides a technical scheme as follows: a wide temperature range four-dimensional drive joint bearing testing machine at least comprises:

the machine body is fixedly arranged;

the high-low temperature environment box is fixedly arranged on the machine body;

the test unit at least comprises a workbench fixed in a high and low temperature environment box, a bearing test tool, an inner ring follow-up assembly and an outer ring follow-up assembly are arranged above the workbench, the bearing test tool at least comprises a test shaft assembly for fixing a bearing inner ring to be tested and an outer ring fixing member sleeved on the outer ring of the bearing to be tested, the outer ring follow-up assembly is connected with the outer ring fixing member, and a pair of inner ring follow-up assemblies are respectively connected with two ends of the test shaft assembly;

the X-axis loading assembly is fixedly arranged on one side of the high and low temperature environment box, and the output end of the X-axis loading assembly extends into the high and low temperature environment box and is connected with the inner ring follow-up assembly on one side;

the X-axis swinging assembly is fixedly arranged on one side of the high and low temperature environment box far away from the X-axis loading assembly, and the output end of the X-axis swinging assembly extends into the high and low temperature environment box and is connected with the inner ring follow-up assembly on the other side;

the Z-axis loading assembly is fixedly arranged on the lower side of the high and low temperature environment box, and the output end of the Z-axis loading assembly extends into the high and low temperature environment box and is connected with the outer ring follow-up assembly;

and the Z-axis swinging assembly is arranged on the upper side of the high-low temperature environment box, and the output end of the Z-axis swinging assembly extends into the high-low temperature environment box and is connected with the outer ring follow-up assembly.

The inner ring follow-up assembly at least comprises a bearing seat and a supporting shaft arranged in the bearing seat, the bearing seat is fixed on the workbench, a pair of inner ring flange-free cylindrical roller bearings arranged side by side is arranged between the supporting shaft and the bearing seat, the outer ring of the inner ring flange-free cylindrical roller bearing is fixedly arranged relative to the bearing seat, and the inner ring of the inner ring flange-free cylindrical roller bearing is fixedly connected to the supporting shaft.

The utility model provides a preferred embodiment, the back shaft includes the bearing linkage segment at least, locates the bulge loop of bearing linkage segment one end and is located the support connecting portion that the bulge loop kept away from bearing linkage segment one side, support connecting portion including the fixed supporting part and the movable supporting part of mutual adaptation lock, support the inside support shaft hole that is equipped with of connecting portion, be equipped with the keyway that extends along axial direction on the inner wall in support shaft hole one, the position that is close to the hole bottom in the support shaft hole is equipped with the screens groove.

According to a preferred embodiment, the outer ring follow-up assembly at least comprises an outer ring bearing assembly and a radial loading seat, the outer ring bearing assembly is connected with the outer ring fixing piece, a pair of tapered roller bearings are arranged between the radial loading seat and the outer ring bearing assembly, and the tapered roller bearings are installed back to back.

In a preferred embodiment, the X-axis loading assembly includes at least:

the X-axis loading supporting seat is fixedly connected with the machine body;

the X-axis linear loading cylinder body is fixedly connected with the X-axis loading supporting seat;

the X-axis piston rod is axially and movably connected with the X-axis linear loading cylinder body;

the guide shaft is axially and movably connected with the X-axis loading support seat and is positioned on one side of the X-axis loading support seat, which is far away from the X-axis linear loading cylinder body;

the X-axis pulling pressure sensor is arranged between the X-axis piston rod and the guide shaft;

the X-axis linear loading device comprises an X-axis linear loading rod, one end of the X-axis linear loading rod is rotatably and movably connected with a guide shaft, and an X-axis linear loading flange is arranged at the free end of the X-axis linear loading rod.

According to a preferred embodiment, an X-axis fixed plate is arranged at the free end of the X-axis linear loading cylinder, an X-axis movable plate matched with the X-axis fixed plate is arranged at the free end of the X-axis piston rod, and an X-axis displacement sensor and an X-axis anti-rotation mechanism are arranged between the X-axis fixed plate and the X-axis movable plate.

In a preferred embodiment, the Z-axis loading assembly includes at least:

the Z-axis loading supporting seat is fixedly connected with the machine body;

the Z-axis linear loading cylinder body is fixedly connected with the Z-axis loading supporting seat;

the Z-axis piston rod is axially and movably connected with the Z-axis linear loading cylinder body;

one end of the Z-axis linear loading rod is connected with the Z-axis piston rod through a Z-axis pull pressure sensor, and the other end of the Z-axis linear loading rod is fixedly connected with the radial loading seat.

According to a preferred embodiment, a Z-axis fixed plate is arranged at the free end of the Z-axis linear loading cylinder, a Z-axis movable plate matched with the Z-axis fixed plate is arranged at the free end of the Z-axis piston rod, and a Z-axis displacement sensor and a Z-axis anti-rotation mechanism are arranged between the Z-axis fixed plate and the Z-axis movable plate.

In a preferred embodiment, the X-axis oscillating assembly comprises at least:

the X-axis swinging support seat is fixedly connected with the machine body;

the X-axis swing flange is arranged at one end of the X-axis swing shaft, and the X-axis spline shaft is arranged at the other end of the X-axis swing shaft;

the X-axis spline housing is axially and movably connected with the X-axis spline shaft;

the X-axis spline sleeve is fixedly connected with the X-axis spline connecting shaft, and the X-axis spline connecting shaft is rotatably and movably connected with the X-axis swinging supporting seat;

the X-axis swinging cylinder is fixedly connected to one side, far away from the X-axis swinging shaft, of the X-axis swinging support seat, and an X-axis torque sensor is arranged between an output shaft of the X-axis swinging cylinder and the X-axis spline connecting shaft;

and the X-axis encoder assembly is arranged at one end, far away from the X-axis swinging supporting seat, of the X-axis swinging cylinder.

In a preferred embodiment, the Z-axis oscillating assembly comprises at least:

the Z-axis swinging support seat is fixedly connected to the lower side of the high-low temperature environment box;

a Z-axis swinging flange used for being connected with the outer ring bearing assembly is arranged at one end of the Z-axis swinging shaft, and a Z-axis spline shaft is arranged at the other end of the Z-axis swinging shaft;

the Z-axis spline sleeve is axially and movably connected with the Z-axis spline shaft;

the Z-axis spline sleeve is fixedly connected with the Z-axis spline connecting shaft, and the Z-axis spline connecting shaft is rotatably and movably connected with the Z-axis swinging supporting seat;

the Z-axis swinging cylinder is fixedly connected to one side, far away from the Z-axis swinging shaft, of the Z-axis swinging support seat, and a Z-axis torque sensor is arranged between an output shaft of the Z-axis swinging cylinder and the Z-axis spline connecting shaft;

and the Z-axis encoder component is arranged at one end, far away from the Z-axis swinging support seat, of the Z-axis swinging cylinder.

The wide temperature range four-dimensional drive joint bearing testing machine of this embodiment has following beneficial effect:

(1) through setting up high low temperature environment case, make the bearing that awaits measuring simulation test in sealed environment, can simulate the test condition under the different temperatures for the simulation test condition more is close to bearing operating condition, and the test result is more reliable.

(2) The four-dimensional driving system is provided with the X-axis loading assembly, the X-axis swinging assembly, the Z-axis loading assembly and the Z-axis swinging assembly, and the test working condition requirement of the four-dimensional bearing load of the joint bearing is met.

(3) The inner ring of the bearing to be tested is limited and fixed through the test shaft assembly, the outer ring of the bearing to be tested is limited and fixed through the outer ring fixing piece, so that the test shaft assembly and the outer ring fixing piece can be respectively used as load bearing parts of the inner ring and the outer ring of the bearing to be tested, loads borne by the inner ring and the outer ring are separated, and the loads acting on the inner ring and the outer ring are not interfered with each other.

(4) In the inner ring follow-up component, the support shaft is connected with the bearing seat through the pair of inner ring flange-free cylindrical roller bearings, and based on the characteristic and the connection relation of axial micro-displacement between the inner ring and the outer ring of the inner ring flange-free cylindrical roller bearings, the inner ring of the bearing to be tested can swing in a reciprocating manner and bear axial push-pull load, the two do not interfere with each other, and the inner ring follow-up component has the technical advantages of simple structure and ingenious conception.

(5) In the outer ring follow-up assembly, a pair of tapered roller bearings which are installed back to back are arranged between the outer ring bearing assembly and the radial loading seat, and based on the bearing characteristics and the connection relation between the inner ring and the outer ring of the tapered roller bearings, the outer ring of the bearing can be tested to swing in a reciprocating manner and bear radial push-pull load, and the two bearings are not interfered with each other; based on the structural characteristic that the tapered roller bearings can bear unidirectional axial load, when the radial loading assembly bears the load in a unidirectional mode, one tapered roller bearing bears the unidirectional axial load, the other tapered roller bearing does not bear the axial load, and when the two tapered roller bearings are installed back to back, the radial push-pull load of the radial loading assembly can be effectively applied to the outer ring bearing assembly through the tapered roller bearings.

In summary, in the wide temperature range four-dimensional drive knuckle bearing testing machine of this embodiment, firstly, the inner ring and the outer ring of the bearing to be tested are structurally separated through the test shaft assembly and the outer ring fixing member, secondly, the reciprocating swing and the axial push-pull load borne by the inner ring of the bearing to be tested are separated through the inner ring follow-up assembly, thirdly, the yawing motion and the radial push-pull load borne by the outer ring of the bearing to be tested are separated through the outer ring follow-up assembly, and finally, the bearing test is placed in a closed high-low temperature environment box, so that the test environment temperature of the knuckle bearing is controllable, and the bearing to be tested can simultaneously realize that the two-dimensional swing and the two-dimensional push-pull load do not interfere with each other, so that the simulation test of the knuckle bearing is closer to the.

Drawings

Fig. 1 is a schematic structural diagram of a wide temperature range four-position drive joint bearing testing machine according to the embodiment;

fig. 2 is a schematic connection diagram of a four-dimensional driving system composed of an X-axis loading assembly, an X-axis swinging assembly, a Z-axis loading assembly and a Z-axis swinging assembly and a test unit in this embodiment;

FIG. 3 is a schematic structural diagram of a four-dimensional motion separation mechanism applied to a bearing test according to the present embodiment;

FIG. 4 is an exploded view of the four-dimensional motion separation mechanism of FIG. 3;

FIG. 5 is a cross-sectional structural view of the four-dimensional kinematic separation mechanism of FIG. 3;

fig. 6 is a structural schematic diagram of an assembly state of the inner ring follower assembly and the bearing test tool in the embodiment;

FIG. 7 is a cross-sectional structural view of the assembled state of FIG. 6;

FIG. 8 is a structural diagram of the inner race follower assembly in an exploded state in the present embodiment;

FIG. 9 is a schematic structural view of the support shaft of the present embodiment;

FIG. 10 is a schematic cross-sectional structural view of the bearing testing tool in this embodiment;

FIG. 11 is a schematic structural diagram of the bearing testing tool in an exploded state in the present embodiment;

FIG. 12 is a schematic structural diagram of a loading ring in the bearing test tool of the present embodiment;

fig. 13 is a structural schematic diagram of an assembly state of the outer race follower assembly and the bearing test fixture in this embodiment;

FIG. 14 is a cross-sectional structural view of the assembled state of FIG. 13;

FIG. 15 is an exploded structural view of the assembled condition of FIG. 13;

FIG. 16 is a schematic structural view of the radial loading upper seat in the present embodiment;

FIG. 17 is a cross-sectional structural view of the radially loaded upper housing of FIG. 16;

fig. 18 is a schematic structural view of the outer pouch in this embodiment;

fig. 19 is a schematic structural view of the inner fixing sleeve in the present embodiment;

fig. 20 is a cross-sectional view of the inner hub shown in fig. 19;

FIG. 21 is a schematic structural diagram of an X-axis loading assembly in the present embodiment;

FIG. 22 is a cross-sectional structural view of the X-axis loading assembly of FIG. 21;

FIG. 23 is a schematic structural diagram of a Z-axis loading assembly in the present embodiment;

FIG. 24 is a cross-sectional structural view of the Z-axis loading assembly of FIG. 23;

FIG. 25 is a schematic structural diagram of the X-axis swing assembly in the present embodiment;

FIG. 26 is a schematic structural view of an X-axis axial loading shaft and an X-axis spline housing of the X-axis oscillating assembly of the present embodiment;

FIG. 27 is a schematic structural diagram of a Z-axis swing assembly in the present embodiment;

fig. 28 is a schematic structural view of the Z-axis axial loading shaft and the Z-axis spline housing in the Z-axis oscillating assembly of this embodiment.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or element referred to must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may include, for example, a fixed connection, an integral connection, or a detachable connection; may be communication within two elements; they may be directly connected or indirectly connected through an intermediate, and those skilled in the art can understand the specific meaning of the above terms in the present invention in specific situations.

As shown in fig. 1 and fig. 2, the wide temperature range four-dimensional drive joint bearing testing machine of the present embodiment includes a machine body 900 fixedly disposed, a high and low temperature environment box 910 is disposed on the machine body 900, and a control cabinet 920 is disposed on one side of the machine body 900. It should be noted that, in the technical field of bearing tests, the high and low temperature environment box 910 is a relatively common test environment box, and the high and low temperature environment box in this embodiment adopts the prior art, which is not described herein again. Meanwhile, the components of the control cabinet 920 are not the invention of the present application, and are not described herein.

In this embodiment, the test unit for mounting the bearing to be tested is mounted in the high and low temperature environment box 910.

In this embodiment, the left side of the high and low temperature environment box 910 is fixedly provided with an X-axis loading assembly, the right side is fixedly provided with an X-axis loading assembly, the upper side is fixedly provided with a Z-axis swinging assembly, and the lower side is provided with a Z-axis loading assembly. The output ends of the X-axis loading assembly, the Z-axis swinging assembly and the Z-axis loading assembly are all arranged in the high-low temperature environment box and connected with the test unit so as to apply corresponding loading to the test unit.

The test unit in this embodiment, as shown in fig. 3 to 5, includes a fixed workbench 300, a bearing test fixture 400 for fixing a bearing to be tested, a pair of inner ring follower assemblies 100 located at two axial sides of the bearing test fixture, and an outer ring follower assembly 200 located between the pair of inner ring follower assemblies.

The bearing test fixture 400 of the present embodiment, as shown in fig. 10-12, includes a test shaft assembly 410 and an outer ring fixture 420. The outer ring fixing member 420 includes a fixing ring 421 sleeved on the outer ring 12 of the bearing 10 to be tested, and a fixing rod 422 extending along the radial direction of the fixing ring 421.

In this embodiment, the test shaft assembly 410 includes a test shaft 411, a loading collar 412, and a lock 414.

As shown in fig. 11, the test shaft 411 of the present embodiment includes a test shaft section 4111, a swing angle transmission section 4112 disposed on both sides of the test shaft section 4111, and a locking section 4113 connected to the swing angle transmission section. The test shaft 4111 has a symmetrical structure in the axial direction, that is, the tilt angle transmission section 4112 and the locking section 4113 at the two ends are symmetrical to each other. The test shaft segment 4111 is configured to penetrate through the inner ring 11 of the bearing 10 to be tested, and preferably, the bearing 10 to be tested is located in the middle of the test shaft 411.

In a preferred embodiment, the cross section of the swing angle transmitting section 4112 in this embodiment is a polygon, in this embodiment, a regular quadrilateral, wherein the diameter of the outer circle of the polygon is not larger than the diameter of the test shaft section 4111.

In a preferred embodiment, in this embodiment, the locking section 4113 is provided with an external thread, and the locking member 414 is a locking nut and is in threaded connection with the locking section 4113.

As shown in fig. 10-12, the loading collar 412 of this embodiment has two, respectively symmetrically mounted on both sides of the outer ring fixture 420. The inner part of the test shaft is provided with a test shaft mounting hole 4123 matched with the test shaft section 4111 and a swing angle transmission hole 4124 matched with the swing angle transmission section, wherein the swing angle transmission section and the swing angle transmission hole form a swing angle transmission structure between the loading ferrule and the test shaft, and a swing angle load applied to the loading ferrule by the loading mechanism is transmitted to the test shaft through the swing angle transmission structure. The swing angle transmission structure formed by the swing angle transmission section with the polygonal cross section and the swing angle transmission hole in the embodiment has the advantages of simple structure and low cost

In this embodiment, one end of the loading ring 412 is provided with an inner ring abutting end 4127, the inner ring abutting end 4127 is used for abutting against an end surface of the inner ring 11 of the bearing 10 to be tested, and the inner ring abutting ends 4127 of the pair of loading rings 412 press and fix the inner ring 11, so that a load applied to the inner ring, especially an axial bidirectional push-pull load, is loaded through the loading ring, and can adapt to a wider variety of bearing tests.

In a preferred embodiment, the outer ring of the loading collar 412 is provided with a pair of flanges 4122 near both ends, and an axial loading groove 4126 is formed between the pair of flanges 4122. The width of the axial loading groove 4126 is matched with the part between the groove wall of the clamping groove in the support shaft hole and the end part of the support connecting part, and the axial loading groove and the part are matched to be used for transmitting the axial push-pull load of the support shaft to the loading ferrule and further applying the axial push-pull load to the inner ring 11 through the loading ferrule.

In a preferred embodiment, the groove bottom 4121 of the axial loading groove 4126 is provided with at least two key grooves two 4125, and the flat keys 413 are installed in the key grooves two 4125. The reciprocating oscillation of the loading member on the loading collar is transmitted through the flat key 413. Preferably, the plurality of second key grooves 4125 are uniformly distributed along the circumferential direction. The position and the structure of the second key groove 4125 are matched with the first key groove, and the second key groove and the first key groove are connected through the flat key 413 and transmit reciprocating swing. In the structure, the axial loading groove is used for bearing the axial bidirectional push-pull load applied to the loading ferrule by the loading part, and meanwhile, the flat key arranged in the key groove in the groove bottom of the axial loading groove is used for transmitting the swing angle applied to the loading ferrule by the swing part

In a preferred embodiment, an avoiding outer conical surface 4128 is arranged between the abutting end 4127 of the inner ring and the convex edge of the same end, and the avoiding outer conical surface 4128 can effectively prevent the loading ferrule from generating motion interference with the outer ring of the bearing to be tested or the outer ring loading seat, thereby further ensuring the test mode that the loading of the inner ring and the loading of the outer ring are independent and do not interfere with each other.

As shown in fig. 10-11, the locking member 414 of this embodiment is fixedly disposed at the free end of the test shaft and is adapted to secure the loading collar between the locking member and the outer race loading seat. The locking piece is provided with an internal thread hole matched with the locking section to realize threaded connection with the locking section.

In this embodiment, as shown in fig. 6 to 8, the inner race follower assembly 100 includes a bearing housing 101 fixed to a table 300, and a support shaft 102 is mounted in the bearing housing.

The inner ring non-flange type cylindrical roller bearings 103 are arranged between the supporting shaft 102 and the bearing seat 101 in parallel, an outer space ring 107 is arranged between the outer rings of the inner ring non-flange type cylindrical roller bearings 103, bearing end covers 104 are respectively installed at two ends of the bearing seat 101, an end cover hole for accommodating the supporting shaft 102 to pass through is formed in the center of each bearing end cover 104, the end faces of the bearing end covers 104 at two sides are respectively attached to the end faces of the outer rings of the inner ring non-flange type cylindrical roller bearings 103, and therefore the outer rings of the inner ring non-flange type cylindrical roller bearings 103 are fixed in the bearing seats.

The structure of the supporting shaft 102 is shown in fig. 9, and includes a bearing connecting section 1021, a convex ring 1025 disposed at one end of the bearing connecting section, and a supporting connecting portion located at a side of the convex ring away from the bearing connecting section. The pair of inner-ring non-flange cylindrical roller bearings 103 is sleeved on the bearing connecting section 1021 of the support shaft 102. Preferably, an inner ring of the inner ring non-flange cylindrical roller bearing 103 close to one side of the convex ring abuts against one side end face of the convex ring, and in this embodiment, an inner spacer 108 is further disposed between the convex ring and the inner ring of the inner ring non-flange cylindrical roller bearing 103.

In the present embodiment, an inner spacer 108 is provided between the inner rings of the pair of inner ring non-flange cylindrical roller bearings 103 corresponding to the outer spacer 107. A flange end cover 106 is attached to an end of the support shaft 102 away from the convex ring, and one end surface of the flange end cover 106 is attached to the inner ring of the inner ring non-flange cylindrical roller bearing, so that the inner rings of the pair of inner ring non-flange cylindrical roller bearings are fixed between the flange end cover and the convex ring.

In the above connection structure, since the bearing is the inner ring non-flange type cylindrical roller bearing, and the inner ring non-flange type cylindrical roller bearing has the characteristic that the inner ring and the outer ring are relatively movable in the axial direction, in the connection structure of the embodiment, the axial displacement between the inner ring and the outer ring of the inner ring non-flange type cylindrical roller bearing, that is, the axial displacement between the support shaft and the bearing seat, is not limited. Therefore, the axial push-pull load and the reciprocating swing around the axis can be simultaneously applied to the support shaft, the structure of the bearing seat does not influence the application of various superposed loads, the support shaft is used for being connected with the inner ring 11 of the bearing 10 to be tested, the superposed loads can be applied to the inner ring 11 of the bearing 10 to be tested through the support shaft, and the superposed loads are not interfered with each other by applying the loads to the outer ring 12 of the bearing 10 to be tested, so that a relatively independent load application form is formed.

As shown in fig. 9, the supporting connection portion of the present embodiment includes a fixed support portion 1022 and a movable support portion 1023 that are engaged with each other, and a supporting shaft hole is formed inside the supporting connection portion formed after the fixed support portion 1022 and the movable support portion 1023 are engaged with each other. Through the arrangement of the movable supporting part, the connection form of the test tool and the supporting connection part is changed, and the connection efficiency is improved

The inner wall of the supporting shaft hole is provided with a first key groove 1024 which is oppositely arranged and extends along the axial direction. Furthermore, a position close to the hole bottom in the support shaft hole is provided with a clamping groove 1027, and the hole bottom of the support shaft hole is provided with an avoiding groove 1026. The bypass slot 1026 is configured to accommodate the structure in which the locking member is positioned.

As shown in fig. 13-15, outer race follower assembly 200 of the present embodiment includes an outer race carrier assembly and a radial load seat for fixedly coupling with outer race retainer 420.

In this embodiment, the outer ring carrier assembly includes an inner sleeve 230 and an outer sleeve 260. The structure of the inner fixing sleeve 230 is shown in fig. 19 and 20, the inner fixing sleeve 230 is provided with an internal threaded hole 231 with an opening at one end, and correspondingly, the fixing rod 422 is provided with an external thread adapted to the internal threaded hole 231, and the fixing rod is in threaded connection with the inner fixing sleeve.

As a special feature of the present embodiment, the inner fixing sleeve 230 is provided with an outer tapered portion 232 at the opening side of the female screw hole 231, and the outer tapered portion 232 is provided with a plurality of through grooves 233 extending in the axial direction and penetrating the wall of the female screw hole in the circumferential direction; the end of the inner fixing sleeve 230 remote from the external taper 232 is provided with a threaded end 234, and the threaded end 234 is provided with external threads.

The structure of the outer fixing sleeve 260 of this embodiment is shown in fig. 18, the outer fixing sleeve 260 is provided with a through hole 261 axially penetrating for accommodating the inner fixing sleeve 230, one end of the through hole 261 is provided with an inner cone 262 adapted to the outer cone 232, and the end far away from the inner cone is provided with a counter bore 263.

As shown in fig. 14 and 15, in the connection state of the outer fixing sleeve 260 and the inner fixing sleeve 230, a counterbore 263 is used for placing a washer 271, and a nut 272 is fittingly mounted on the threaded connection end 234. Since the through grooves 233 are formed in the circumferential direction of the outer tapered portion 232, when the nut 272 is tightened, the inner tapered portion 262 and the outer tapered portion 232 are separated into portions by the through grooves 233 and the portions are moved toward the center, so that a great tightening force is applied to the fixing rod. This kind of connected mode for the outer lane holds the connection between carrier and the outer lane mounting very reliable, guarantees under the effect of continuous reciprocal swing and push-and-pull load, and the outer lane mounting can not take place to become flexible, position change etc. with being connected between the interior fixed cover.

As shown in fig. 18, the outer fixing sleeve 260 of the present embodiment has an end cap 264 at an end where the counterbore 263 is located, and a connecting external thread 266 at an end remote from the end cap 264. One end of the end cover 264 facing the connecting external thread 266 forms a stopper end face 265 for abutting contact with the inner ring of the tapered roller bearing.

The radial loading shoe in this embodiment, as shown in fig. 13-15, includes a radial loading upper shoe 220 and a radial loading lower shoe 210 fixedly connected to each other. The connection mode is not limited to a bolt connection mode, a welding connection mode, a snap connection mode and other connection modes, and preferably, in the embodiment, the bolt connection mode and the snap connection mode are detachably connected.

Wherein, radial loading lower base 210 is equipped with and holds the chamber 211, should hold the chamber 211 and be used for holding the experimental frock of bearing.

The structure of the radial loading upper seat 220 adapted to the radial loading lower seat 210 is shown in fig. 16 and 17, a through hole 223 for accommodating the outer fixing sleeve 260 to pass through is formed in the radial loading upper seat 220, and a first bearing mounting hole 221 and a second bearing mounting hole 222 for accommodating the tapered roller bearing 250 are respectively formed at two ends of the through hole 223.

In this embodiment, the radially loaded upper housing 220 is coupled to the stationary outer sleeve 260 by a pair of tapered roller bearings 250 mounted back-to-back. The connection mode is shown in fig. 14 and 15, wherein an inner ring end surface of one of the tapered roller bearings 250 abuts against a limit end surface 265 of the outer fixing sleeve 260, and an outer ring of the tapered roller bearing 250 is installed in the first bearing installation hole 221 of the radial loading upper seat 220. The outer ring of the other tapered roller bearing 250 is mounted in the second bearing mounting hole 222 of the radial loading upper seat 220, and the inner ring of the tapered roller bearing 250 is sleeved on the outer fixing sleeve 260. Wherein, an interval ring 270 sleeved on the outer fixed sleeve 260 is installed between the inner rings of the two tapered roller bearings 250, a sealing ring 273 is arranged on one side of the inner ring of the tapered roller bearing far away from the spacing ring on one side of the limiting end face, a locking nut 274 matched with the connecting external thread 266 is installed on one side of the sealing ring 273 far away from the tapered roller bearing 250, and the outer fixed sleeve 260, the radial loading upper seat 220, the pair of tapered roller bearings 250, the interval ring 270 and the sealing ring 273 are fixed together by the locking nut 274.

Preferably, in this embodiment, a sealing cover 275 fixedly coupled to the radial loading upper seat 220 is provided at one side of the first bearing mounting hole 221, a sealing ring 276 is provided between the sealing cover 275 and the outer fixing sleeve 260, and the sealing cover 275 and the sealing ring 276 form a sealing structure to seal the side of the first bearing mounting hole 221. Similarly, a seal structure including a seal cover 275 and a seal ring 276 is also provided on the second bearing mounting hole 222 side to seal the side.

Preferably, as shown in fig. 13 to 15, in the present embodiment, a pair of oppositely disposed mounting grooves 212 is disposed on a side where the radial loading lower seat 210 is connected to the radial loading upper seat 220, a supporting plate 213 is connected between the pair of oppositely disposed mounting grooves 212, and a supporting plate hole 214 penetrating through the supporting plate is disposed in a middle portion of the supporting plate 213. The supporting plate hole 214 is used for accommodating the outer ring fixing piece to pass through, and aims to keep the outer ring fixing piece and the inner fixing sleeve at a vertical upward position through the supporting plate hole 214 after the outer ring fixing piece is in threaded connection with the inner fixing sleeve in the installation process of the bearing to be tested 10, so that the outer fixing sleeve is prevented from toppling or changing positions, and the connection between the outer fixing sleeve and the inner fixing sleeve is facilitated.

As shown in fig. 21-22, the X-axis loading assembly 500 of the present embodiment is provided with an X-axis loading support 510, which is fixedly mounted on the body 900. One side of the X-axis loading support base 510 is fixedly connected with an X-axis linear loading cylinder 520, an X-axis piston rod 530 is arranged in the X-axis linear loading cylinder 520, the X-axis piston rod 530 is axially and movably connected with the X-axis linear loading cylinder, and the extension and retraction of the X-axis piston rod 530 are used for applying axial bidirectional push-pull load to the bearing to be tested.

An X-axis linear bearing sleeve 561 is arranged on one side, far away from the X-axis linear loading cylinder, of the X-axis loading supporting seat, a guide shaft 560 is connected in the X-axis linear bearing sleeve 561, and the guide shaft 560 is axially movably connected with the X-axis loading supporting seat through the X-axis linear bearing sleeve 561.

Wherein, one end of the guide shaft 560 is fixedly connected with the X-axis piston rod 530. Preferably, an X-axis tension and pressure sensor 540 is disposed between the guide shaft 560 and the X-axis piston rod 530 for acquiring and monitoring the magnitude of the X-axis linear loading force.

In this embodiment, the other end of the guide shaft 560 is a connecting flange end 562, the connecting flange end 562 is connected to a connecting sleeve 563, and a bearing cavity is formed between the connecting flange end 562 and the connecting sleeve 563.

The X-axis loading assembly 500 of the present embodiment further includes an X-axis linear loading rod 550, one end of the X-axis linear loading rod 550 is provided with an X-axis linear loading flange 551, and the X-axis linear loading flange 551 is fixedly connected with the flange end cover 106 for transmitting the linear movement load to the supporting shaft.

The other end of the X-axis linear loading rod 550 is located in the bearing cavity, the end is connected with the inner cavity of the bearing cavity through a thrust ball bearing 553, and the end is provided with a locking piece 552 for fixing the thrust ball bearing 553 on the end of the X-axis linear loading rod in the bearing cavity.

In this embodiment, the connection between the bearing cavity and the X-axis linear loading rod 550 forms a motion separation mechanism, wherein the X-axis linear loading rod is used to transmit the push-pull load of the X-axis piston rod to the supporting shaft, and the X-axis loading rod simultaneously bears the reciprocating swing of the X-axis swinging assembly along with the transmission of the supporting shaft, so that the X-axis linear loading rod can rotate while moving linearly. So that the loads of the X-axis loading assembly and the X-axis swinging assembly coexist and do not interfere with each other.

In this embodiment, the free end of the X-axis linear loading cylinder 520 is provided with an X-axis fixing plate 570, and the free end of the X-axis piston rod is provided with an X-axis moving plate 570 adapted to the X-axis fixing plate. An X-axis displacement sensor 580 is arranged between the X-axis fixed plate and the X-axis movable plate and used for collecting and monitoring the linear displacement of the X axis.

In addition, in order to prevent the X-axis piston rod from rotating along the axis relative to the X-axis linear loading cylinder, an X-axis rotation preventing mechanism is arranged between the X-axis fixed plate and the X-axis movable plate, and comprises an X-axis guide rod 590 fixedly connected with the X-axis fixed plate and an X-axis guide sleeve 591 arranged on the X-axis movable plate.

As shown in fig. 23 to 24, the Z-axis loading assembly 600 of the present embodiment includes a Z-axis loading supporting seat 610 fixedly connected to the body 900 through a bracket, a Z-axis linear loading cylinder 620 is fixedly connected to a side of the Z-axis loading supporting seat 610 away from the worktable, a Z-axis piston rod 630 is disposed in the Z-axis linear loading cylinder 620, the Z-axis piston rod 630 is axially movably connected to the Z-axis linear loading cylinder, and the extension and contraction of the Z-axis piston rod 630 is used for applying a radial bidirectional push-pull load to the bearing to be tested.

The Z-axis loading assembly 600 further includes a Z-axis linear loading rod 650, one end of the Z-axis linear loading rod 650 is connected to the Z-axis piston rod 630 through a Z-axis tension/pressure sensor 640, and the other end of the Z-axis linear loading rod passes through the worktable and then is fixedly connected to the radial loading lower base 210. The Z-axis tension pressure sensor 640 is used for acquiring and monitoring the magnitude of the Z-axis linear loading force.

In this embodiment, the free end of the Z-axis linear loading cylinder 620 is provided with a Z-axis fixing plate 670, and the free end of the Z-axis piston rod is provided with a Z-axis movable plate 671 matched with the Z-axis fixing plate. And a Z-axis displacement sensor 660 is arranged between the Z-axis fixed plate and the Z-axis movable plate and used for acquiring and monitoring Z-axis linear displacement.

In addition, in order to prevent the Z-axis piston rod from rotating along the axis relative to the Z-axis linear loading cylinder, a Z-axis rotation preventing mechanism is arranged between the Z-axis fixing plate and the Z-axis movable plate, and comprises a Z-axis guide rod 680 fixedly connected with the Z-axis fixing plate and a Z-axis guide sleeve 681 arranged on the Z-axis movable plate.

As shown in fig. 25, the X-axis swing assembly 700 of the present embodiment includes an X-axis swing support 710, and the X-axis swing support 710 is fixedly mounted on the main body 900.

In this embodiment, an X-axis swing shaft 720 is disposed on one side of the X-axis swing assembly 700, an X-axis swing flange 722 for connecting with the support shaft is disposed on one end of the X-axis swing shaft, and the X-axis swing flange 722 is fixedly connected with the flange end cover 106 for transmitting the reciprocating swing of the X-axis swing assembly to the support shaft.

As shown in fig. 26, in this embodiment, the other end of the X-axis axial loading shaft 720 is an X-axis spline shaft 721, and an X-axis spline housing 723 that is fittingly connected to the X-axis spline shaft 721 is connected to the X-axis swing support 720 through an X-axis spline connection shaft 760. Preferably, the X-axis spline housing 723 is a ball spline in which a plurality of rows of balls 225 are disposed and is engaged with the spline grooves 724 of the X-axis spline shaft 721, and the ball spline has an advantage of small friction resistance.

The X-axis spline shaft and the X-axis spline housing have the effect that when the inner ring of the bearing to be tested generates axial displacement after being subjected to axial push-pull load, the axial displacement of the X-axis spline shaft relative to the X-axis spline housing is used for eliminating the displacement, so that the X-axis swing assembly is not influenced. Meanwhile, the reciprocating swing of the X-axis swing assembly can be transmitted through the ball and the spline groove.

The X-axis swing support seat 710 is provided with an X-axis connecting flange 711, and the X-axis spline connecting shaft 760 is rotatably and movably connected with the X-axis connecting flange 711. An X-axis swing cylinder 740 is arranged on the other side of the X-axis swing support seat 710, the X-axis swing cylinder 740 is fixed on the X-axis swing support seat 710 through an X-axis connecting plate 712, an output shaft of the X-axis swing cylinder 740 is connected with an X-axis spline connecting shaft 760, and preferably, an X-axis torque sensor 730 is arranged between the output shaft of the X-axis swing cylinder 740 and the X-axis spline connecting shaft 760 and used for monitoring swing torque and/or controlling reciprocating swing.

In addition, an X-axis encoder assembly 750 is further disposed at an end of the X-axis swing cylinder 740 away from the X-axis swing support seat, and is used for acquiring data and controlling a working state of the X-axis swing cylinder.

As shown in fig. 27, the Z-axis swinging assembly 800 of the present embodiment includes a Z-axis swinging support seat 810, and the Z-axis swinging support seat 810 is fixedly mounted on the body 900 through a bracket.

In this embodiment, a Z-axis swinging shaft 820 is disposed on one side of the Z-axis swinging assembly 800 close to the test unit, a Z-axis swinging flange 822 for connecting with the outer fixing sleeve 260 is disposed at one end of the Z-axis swinging shaft, and the Z-axis swinging flange 822 is fixedly connected with the end cover 264 and is used for transmitting the reciprocating swinging of the Z-axis swinging assembly to the outer ring bearing assembly.

As shown in fig. 27 to 28, in this embodiment, the other end of the Z-axis swing shaft 820 is a Z-axis spline shaft 821, and a Z-axis spline sleeve 823 adapted to be connected to the Z-axis spline shaft 821 is connected to the Z-axis swing support 820 through a Z-axis spline connection shaft 860. Preferably, the Z-axis spline housing 823 is a ball spline, in which a plurality of rows of balls 825 are disposed and are matched with the spline grooves 824 on the Z-axis spline shaft 821, and the ball spline has an advantage of small friction resistance.

This Z axle integral key shaft lies in with Z axle spline housing's effect, and when the outer lane of the bearing that awaits measuring received radial push-and-pull load after taking place radial displacement, the axial displacement of the relative Z axle spline housing of Z axle integral key shaft is used for eliminating above-mentioned displacement to do not influence other subassemblies such as Z axle swing jar. Meanwhile, reciprocating swing generated by the Z-axis swing cylinder can be transmitted through the ball and the spline groove.

The Z-axis swing support seat 810 is provided with a Z-axis connecting flange 811, and the Z-axis spline connecting shaft 860 is rotatably and movably connected with the Z-axis connecting flange 811. The other side of the Z-axis swinging support seat 810 is provided with a Z-axis swinging cylinder 840, the Z-axis swinging cylinder 840 is fixed on the Z-axis swinging support seat 810 through a Z-axis connecting plate 812, an output shaft of the Z-axis swinging cylinder 840 is connected with a Z-axis spline connecting shaft 860, and preferably, a Z-axis torque sensor 830 is arranged between the output shaft of the Z-axis swinging cylinder 840 and the Z-axis spline connecting shaft 860 and used for monitoring swinging torque and/or controlling reciprocating swinging.

In addition, a Z-axis encoder assembly 850 is further disposed at one end of the Z-axis swinging cylinder 840, which is far away from the Z-axis swinging support seat, and is used for acquiring data and controlling the working state of the Z-axis swinging cylinder.

In summary, the above description is only a preferred embodiment of the present invention and should not be taken as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principles of the present invention should be included within the scope of the present invention.

Claims

1. The utility model provides a wide temperature range four-dimensional drive joint bearing testing machine which characterized in that includes at least:

the machine body is fixedly arranged;

2. The testing machine for the four-dimensional driving joint bearing in the wide temperature range according to claim 1, wherein the inner ring follow-up assembly at least comprises a bearing seat and a supporting shaft arranged in the bearing seat, the bearing seat is fixed on the workbench, a pair of inner ring flange-free cylindrical roller bearings arranged side by side are arranged between the supporting shaft and the bearing seat, an outer ring of the inner ring flange-free cylindrical roller bearing is fixedly arranged relative to the bearing seat, and an inner ring of the inner ring flange-free cylindrical roller bearing is fixedly connected to the supporting shaft.

3. The testing machine for the four-dimensional driving knuckle bearing of claim 2, wherein the supporting shaft comprises at least a bearing connecting section, a protruding ring at one end of the bearing connecting section, and a supporting connecting portion at a side of the protruding ring away from the bearing connecting section, the supporting connecting portion comprises a fixed supporting portion and a movable supporting portion which are matched with each other and buckled with each other, a supporting shaft hole is formed in the supporting connecting portion, a first key groove extending in the axial direction is formed in the inner wall of the supporting shaft hole, and a clamping groove is formed in the supporting shaft hole close to the bottom of the hole.

4. The wide temperature range four-dimensional drive joint bearing testing machine according to claim 1, wherein the outer ring follow-up assembly at least comprises an outer ring bearing assembly and a radial loading seat, the outer ring bearing assembly is connected with the outer ring fixing member, a pair of tapered roller bearings are arranged between the radial loading seat and the outer ring bearing assembly, and the pair of tapered roller bearings are installed back to back.

5. The wide temperature range four-dimensional drive joint bearing testing machine according to any one of claims 1 to 4, wherein the X-axis loading assembly comprises at least:

the X-axis loading supporting seat is fixedly connected with the machine body;

6. The wide temperature range four-dimensional drive joint bearing testing machine according to claim 5, wherein the free end of the X-axis linear loading cylinder is provided with an X-axis fixed plate, the free end of the X-axis piston rod is provided with an X-axis movable plate matched with the X-axis fixed plate, and an X-axis displacement sensor and an X-axis rotation preventing mechanism are arranged between the X-axis fixed plate and the X-axis movable plate.

7. The wide temperature range four-dimensional drive joint bearing tester according to any one of claims 1 to 4, wherein the Z-axis loading assembly comprises at least:

the Z-axis loading supporting seat is fixedly connected with the machine body;

8. The wide temperature range four-dimensional drive joint bearing testing machine according to claim 7, wherein the free end of the Z-axis linear loading cylinder is provided with a Z-axis fixed plate, the free end of the Z-axis piston rod is provided with a Z-axis movable plate matched with the Z-axis fixed plate, and a Z-axis displacement sensor and a Z-axis rotation preventing mechanism are arranged between the Z-axis fixed plate and the Z-axis movable plate.

9. The wide temperature range four-dimensional drive joint bearing testing machine according to any one of claims 1 to 4, 6 or 8, wherein the X-axis oscillating assembly comprises at least:

the X-axis swinging support seat is fixedly connected with the machine body;

10. The wide temperature range four-dimensional drive oscillating bearing testing machine according to claim 4, wherein the Z-axis oscillating assembly at least comprises: