CN107741323B - Elastic bushing fatigue testing machine - Google Patents
Elastic bushing fatigue testing machine Download PDFInfo
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- CN107741323B CN107741323B CN201711251546.4A CN201711251546A CN107741323B CN 107741323 B CN107741323 B CN 107741323B CN 201711251546 A CN201711251546 A CN 201711251546A CN 107741323 B CN107741323 B CN 107741323B
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- 238000009661 fatigue test Methods 0.000 title claims abstract description 29
- 230000007246 mechanism Effects 0.000 claims abstract description 119
- 229910000831 Steel Inorganic materials 0.000 claims abstract description 79
- 239000010959 steel Substances 0.000 claims abstract description 79
- 238000005096 rolling process Methods 0.000 claims description 26
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 238000004088 simulation Methods 0.000 abstract description 8
- 238000001514 detection method Methods 0.000 abstract description 2
- 230000033001 locomotion Effects 0.000 description 44
- 238000012360 testing method Methods 0.000 description 16
- 230000035882 stress Effects 0.000 description 15
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 7
- 230000009471 action Effects 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 241001247986 Calotropis procera Species 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 125000004122 cyclic group Chemical group 0.000 description 3
- 238000001228 spectrum Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000003292 glue Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000008707 rearrangement Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
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Abstract
The invention discloses an elastic bushing fatigue testing machine, which belongs to the field of part detection equipment, and comprises an axial loading mechanism, a clamping mechanism and a clamping mechanism, wherein the axial loading mechanism is connected with an inner steel sleeve of an elastic bushing and is used for applying axial force to the inner steel sleeve of the elastic bushing; the radial loading mechanism is connected with the outer steel sleeve of the elastic bushing and applies radial force to the outer steel sleeve of the elastic bushing; the first torsion mechanism is connected with the inner steel sleeve of the elastic bushing and drives the inner steel sleeve of the elastic bushing to twist reciprocally around the central shaft of the elastic bushing; and the second torsion mechanism is connected with the outer steel sleeve of the elastic bushing and drives the outer steel sleeve of the elastic bushing to reciprocate around the radial direction of the outer steel sleeve. The elastic bushing fatigue testing machine provided by the invention has the advantages of simple structure, strong functionality, high universality and the like, and can enable the fatigue stress simulation of the elastic bushing to be closer to the actual stress.
Description
Technical Field
The invention relates to the technical field of part detection equipment, in particular to an elastic bushing fatigue testing machine.
Background
With the development of the automobile industry, automobiles become an indispensable riding tool for most people, and the requirements of people on various performances and reliability of the automobiles are also higher and higher. The elastic bearing bushing has the advantages of being capable of attenuating and absorbing high-frequency vibration and noise, small in size, light in weight and the like, and is widely used as an important shock absorption part in places where the automobile is stressed in a complex manner, such as a frame, a torsion beam, a connecting rod, a control arm and the like. The structure of the elastic bearing bush generally comprises an outer steel sleeve, an inner steel sleeve and a rubber bush arranged between the outer steel sleeve and the inner steel sleeve, wherein the rubber bush is bonded with the inner steel sleeve and the outer steel sleeve through glue and is subjected to high-temperature interference press fit. During running of the automobile, the elastic bearing bush bears various complex and changeable loads such as torsion, inclination, axial direction, radial direction and the like, so that the rubber bush is in fatigue failure, and the phenomena of separation, tearing, rubber crack aging and the like can occur at the bonding position of the rubber and the metal, thereby seriously affecting the reliability, smoothness and riding comfort of an automobile system. Therefore, the elastic bearing bush needs to be tested in various ways before being developed or produced, and various stresses to which the elastic bearing bush is subjected under the working environment are simulated and fatigue tests are carried out.
The prior art discloses a rubber bushing double-shaft fatigue endurance test bench, which comprises a radial loading device and a swinging loading device, wherein the radial loading device comprises a first linear actuator and a bushing clamp, the bushing clamp is used for clamping the outer ring of a rubber bushing to be tested, and the radial loading force of the first linear actuator acts on the rubber bushing to be tested through the bushing clamp; the swinging loading device comprises a second linear actuator and a swinging transmission mechanism, one end of the swinging transmission mechanism is connected with the loading end of the second linear actuator, the other end of the swinging transmission mechanism is connected with the bushing clamp through the rubber bushing to be tested, and the linear loading force of the second linear actuator is converted into swinging moment for driving the rubber bushing to be tested to swing around the center of the rubber bushing to be tested through the swinging transmission mechanism.
The rubber bushing double-shaft fatigue endurance test bench can load axial force and swing torque on the rubber bushing, but because the stress of the rubber bushing is complex in the running process of an automobile, the rubber bushing is not only subjected to the action of the axial force and the swing torque, but also subjected to the combined action of radial force, other forces such as the swing torque and the like, and therefore, the test bench is difficult to simulate the complex stress condition of the rubber bushing in an automobile system.
Disclosure of Invention
The invention aims to provide an elastic bushing fatigue testing machine so as to enable stress simulation of an elastic bushing to be closer to actual stress.
In order to achieve the above purpose, the invention adopts the following technical scheme:
An elastic bushing fatigue testing machine, comprising:
The axial loading mechanism is connected with the inner steel sleeve of the elastic bushing and applies axial force to the inner steel sleeve of the elastic bushing;
The radial loading mechanism is connected with the outer steel sleeve of the elastic bushing and applies radial force to the outer steel sleeve of the elastic bushing;
The first torsion mechanism is connected with the inner steel sleeve of the elastic bushing and drives the inner steel sleeve of the elastic bushing to twist reciprocally around the central shaft of the elastic bushing;
and the second torsion mechanism is connected with the outer steel sleeve of the elastic bushing and drives the outer steel sleeve of the elastic bushing to reciprocate around the radial direction of the outer steel sleeve.
Preferably, the elastic bushing is sleeved and fixed on a connecting rod, one end of the connecting rod is fixedly connected with the axial loading mechanism, and the other end of the connecting rod is fixedly connected with the first torsion mechanism; the radial loading mechanism is connected to the outer steel sleeve of the elastic bushing through a first clamping block, the second torsion mechanism is connected to the outer steel sleeve of the elastic bushing through a second clamping block, and the first clamping block is connected with the second clamping block and clamps the outer steel sleeve of the elastic bushing in the radial direction of the outer steel sleeve. The axial loading mechanism and the first torsion mechanism can apply axial force and/or torque to the inner surface of the elastic bushing through the connecting rod; through first fixture block and second fixture block, radial loading mechanism and second torsion mechanism can apply radial force and/or moment to the outer steel bushing of elastic bushing to make fatigue testing machine can apply the combination of various forces to elastic bushing, make the simulation atress of elastic bushing more press close to true atress.
Preferably, the radial loading mechanism comprises a radial loading rod and a first piston cylinder connected with and driving the radial loading rod, and the radial loading rod is fixedly connected with the first clamping block; the axial loading mechanism comprises an axial loading rod and a second piston cylinder connected with and driving the axial loading rod, and the axial loading rod is fixedly connected with one end of the connecting rod.
Preferably, a first adapter sleeve is connected between the radial loading rod and the first piston cylinder, the first adapter sleeve is fixedly connected with the first piston cylinder, and a first rolling bearing is arranged between the radial loading rod and the first adapter sleeve; a second adapter sleeve is connected between the axial loading rod and the second piston cylinder, the second adapter sleeve is fixedly connected with the second piston cylinder, and a second rolling bearing is arranged between the axial loading rod and the second adapter sleeve. By arranging the first rolling bearing and the first adapter sleeve, the loading influence of torsion movement loading of the first torsion mechanism on the axial loading mechanism can be eliminated; by providing the second rolling bearing and the second adapter sleeve, the loading influence of the torsional movement loading of the second torsion mechanism on the radial loading mechanism can be eliminated.
Preferably, the first torsion mechanism comprises a first torsion loading rod and a first torsion actuator connected with and driving the first torsion loading rod to twist reciprocally around the axis of the first torsion loading rod, the axis of the first torsion loading rod coincides with the central shaft, and one end of the first torsion loading rod, which is not connected with the first torsion actuator, is connected with the other end of the connecting rod;
The second torsion mechanism comprises a second torsion loading rod and a second torsion actuator which is connected with and drives the second torsion loading rod to twist reciprocally around the axial direction of the second torsion loading rod, the axis of the second torsion loading rod coincides with the radial direction, and one end of the second torsion loading rod, which is not connected with the second torsion actuator, is fixedly connected with the second clamping block.
Preferably, the first torsion loading bar and the second torsion loading bar are both ball spline. When the spline shaft of the ball spline has axial translational motion, the spline shaft drives the balls between the spline shaft and the spline sleeve to translate along the axial direction, so that the translational motion of the spline shaft is eliminated by the balls and cannot be transmitted to the spline sleeve, and the influence of the axial translational motion of the axial loading mechanism on torsion loading of the first torsion mechanism and the influence of the translational motion of the radial loading mechanism on torsion loading of the second torsion mechanism can be eliminated.
Preferably, the first torsion loading rod is supported on the torsion fixing seat, and a third rolling bearing is arranged between the first torsion loading rod and the torsion fixing seat.
Preferably, the first torsion actuator comprises a first deflection arm, a first connecting swing rod and a third piston cylinder which are connected in turn in a rotating mode, and one end, which is not connected with the first connecting swing rod, of the first deflection arm is connected with the first torsion loading rod in a penetrating mode.
Preferably, the first torsion actuator is a first rotary oil cylinder, and the first rotary oil cylinder is connected with the first torsion loading rod through a flange.
Preferably, the elastic bushing outer steel sleeve is sleeved with a universal sleeve, and the universal sleeve is abutted to the inner surface of the first clamping block and the inner surface of the second clamping block. Through setting up general cover, can not change under the condition that other settings of elastic bushing fatigue testing machine, carry out fatigue test to the elastic bushing of different models and size, make the commonality of fatigue testing machine stronger.
The beneficial effects of the invention are as follows:
According to the elastic bushing fatigue testing machine provided by the invention, through independent or simultaneous loading of the radial loading mechanism, the axial loading mechanism, the first torsion mechanism and/or the second torsion mechanism, independent or combined stress of torsion, axial direction, radial direction and inclination of the elastic bushing can be reproduced, so that the stress working condition of the elastic bushing is more close to the stress condition in a real working state, the simulation result is more realistic and reliable, the simulation test of a road spectrum is better realized, the testing functionality is strong, and the testing accuracy is good.
Drawings
FIG. 1 is a schematic view of an elastic bushing fatigue testing machine according to embodiment 1 of the present invention;
FIG. 2 is an enlarged view of a portion of FIG. 1 at I;
FIG. 3 is a schematic view of another structure of the elastic bushing fatigue testing machine according to embodiment 1 of the present invention;
FIG. 4 is an enlarged view of a portion of J in FIG. 3;
FIG. 5 is a cross-sectional view of the elastic bushing fatigue tester of example 1 of the present invention along the x-direction;
FIG. 6 is an enlarged view of a portion of FIG. 5 at K;
FIG. 7 is an enlarged view of a portion at L in FIG. 5;
FIG. 8 is a cross-sectional view of the elastic bushing fatigue tester of example 1 of the present invention along the y-direction;
FIG. 9 is an enlarged view of a portion of the portion of FIG. 8 at M;
FIG. 10 is an enlarged view of a portion at N in FIG. 8;
fig. 11 is a schematic structural diagram of a first latch according to embodiment 1 of the present invention;
Fig. 12 is a schematic structural diagram of a second latch according to embodiment 1 of the present invention;
Fig. 13 is a schematic structural view of an elastic bushing fatigue tester according to embodiment 2 of the present invention.
The figures are labeled as follows:
10-an elastic bushing; 11-a first clamping block; 111-a first arcuate surface; 112-connecting the bumps; 12-a second clamping block; 121-a second arcuate surface; 122-connecting grooves; 13-connecting rods; 14-universal sleeve; 15-a first lock nut;
2-radial loading mechanism; 21-radial loading bar; 22-a first piston cylinder; 221-a first piston rod; 23-a first adapter sleeve; 24-end caps; 25-a first rolling bearing; 26-a second lock nut; 27-a first translation mount;
3-an axial loading mechanism; 31-axial loading rod; 32-a second piston cylinder; 33-a second adapter sleeve; 37-a second translation mount;
4-a first torsion mechanism; 41-a first torsion loading bar; 411-spline shaft; 412-spline housing; 42-a third piston cylinder; 43-a first deflection arm; 431-flange portion; 432-deflection section; 44-loop bar; 45-twisting the fixing seat; 451-third rolling bearings; 452-a linkage; 453-first connection flange; 454-a first circlip; 455-a second circlip; 456-an inner baffle ring; 46-a first connecting swing rod; 461-knuckle bearing; 47-a second connecting flange; 471-first flange; 472-a second flange; 473-a fixed block; 410-a first rotary cylinder;
5-a second torsion mechanism; 51-a second torsion loading bar; 52-a fourth piston cylinder; 53-a second deflection arm; 553, a third connecting flange; 56-a second connecting swing rod; 510-a second rotary cylinder;
6-a test bed; 61-ruler.
Detailed Description
The invention is described in further detail below with reference to the drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting thereof. It should be further noted that, for convenience of description, only some, but not all of the structures related to the present invention are shown in the drawings.
Example 1
As shown in fig. 1, embodiment 1 of the present invention provides an elastic bushing fatigue testing machine, which comprises an axial loading mechanism 3 capable of applying an axial force to an inner steel bushing of an elastic bushing 10 along a central axis direction of the elastic bushing 10, a radial loading mechanism 2 capable of applying a radial force to an outer steel bushing of the elastic bushing 10 along a radial direction of the elastic bushing 10, a first torsion mechanism 4 capable of driving the elastic bushing 10 to reciprocally twist around the central axis, and a second torsion mechanism 5 capable of driving the elastic bushing 10 to twist around the radial direction. By means of the individual or combined action of the axial loading means 3 and the first torsion means 4, the axial forces and/or moments exerted on the inner steel jacket of the elastic bushing 10 during actual operation can be simulated; the radial force and/or moment borne by the outer steel sleeve of the elastic bushing 10 in the actual running process can be simulated through the independent or combined action of the radial loading mechanism 2 and the second torsion mechanism 5, the independent or combined stress of torsion, inclination, axial direction and radial direction of the elastic bushing 10 can be realized through controlling the independent or combined loading movements of the four mechanisms, the stress of the elastic bushing 10 is more close to the stress working condition of the elastic bushing 10 in the running process of an automobile, the fatigue test data is more accurate, and the road spectrum simulation test can be better realized.
The axial loading mechanism 3, the radial loading mechanism 2, the first torsion mechanism 4 and the second torsion mechanism 5 are all arranged on the test bench 6, the loading direction of the axial loading mechanism 3 is perpendicular to the loading direction of the radial loading mechanism 2 and the loading direction of the second torsion mechanism 5, and the loading direction of the first torsion mechanism 4 is perpendicular to the loading direction of the second torsion mechanism 5. Wherein the axial loading mechanism 3 and the first torsion mechanism 4 are respectively connected to the inner steel sleeve of the elastic bushing 10, and the radial loading mechanism 2 and the second torsion mechanism 5 are respectively connected to the outer steel sleeve of the elastic bushing 10. Because the rubber sleeve is arranged between the inner steel sleeve and the outer steel sleeve of the elastic bushing 10, the reciprocating translational motion and/or the cyclic centering torsional motion of the inner steel sleeve of the elastic bushing 10 are consumed due to the elasticity of the rubber sleeve, so that the influence on the loading motion of the outer steel sleeve of the elastic bushing 10 is small; similarly, the reciprocating translational movement of the outer steel jacket of the elastic bushing 10 and/or the cyclic torsional movement about the axis of the elastic bushing 10 is also consumed by the elasticity of the rubber jacket, so that the loading movement of the steel jacket within the elastic bushing 10 is less affected.
As shown in fig. 2, the first torsion mechanism 4 includes a first torsion loading lever 41 and a first torsion actuator connected to and driving the first torsion loading lever 41 to twist about the central axis of the elastic bushing 10. In this embodiment 1, the first torsion actuator includes a first deflection arm 43, a first connection swing link 46, and a third piston cylinder 42, which are rotatably connected in this order. The first deflecting arm 43 is vertically connected with a loop bar 44, and the loop bar 44 is rotatably connected with a first connecting swing rod 46. When the piston rod of the third piston cylinder 42 reciprocates, the piston rod drives the first connecting swing rod 46 to reciprocate along the direction perpendicular to the first torsion loading rod 41, so as to drive the first deflection arm 43 to reciprocate relative to the axis of the first torsion loading rod 41, and since the swinging movement of the first deflection arm 43 around the axis of the first torsion loading rod 41 causes the first connecting swing rod 46 to move without being in the same straight line as the piston rod, in order to ensure that the straight line translational movement of the piston rod is converted into the swinging movement of the first deflection arm 43, the first connecting swing rod 46 is connected with the first deflection arm 43 and the piston rod by adopting the joint bearing 461.
The second torsion mechanism 5 has the same structure as the first torsion mechanism 4 and comprises a second torsion loading rod 51, a second deflection arm 53, a second connecting swing rod 56, a fourth piston cylinder 52 and other parts which are sequentially connected, wherein the difference is that the second torsion loading rod 51 is connected with an outer steel sleeve of the elastic bushing 10, and when the fourth piston cylinder 52 drives the second torsion loading rod 51 to twist around the axial direction of the second torsion loading rod 51, the outer steel sleeve of the elastic bushing 10 driven by the second torsion loading rod 51 is twisted back and forth around the radial direction of the elastic bushing 10.
As shown in fig. 4, the radial loading mechanism 2 includes a radial loading rod 21 connected to the outer steel jacket of the elastic bushing 10 and a first piston cylinder 22 connected to and driving the radial loading rod 21 to apply a radial force. In order to ensure that the loading direction of the radial loading rod 21 is perpendicular to the central axis of the elastic bushing 10, the radial loading rod 21 is supported on a first translation fixing seat 27, the first translation fixing seat 27 is fixed on the test stand 6, a through hole penetrating through the radial loading rod 21 is formed, and one end of the radial loading rod 21 penetrates through the through hole and is fixedly connected with the outer steel sleeve of the elastic bushing 10. The first translation fixing seat 27 can support the radial loading rod 21 on one hand and prevent the radial loading rod 21 from axial displacement under the loading action of the second torsion mechanism 5; on the other hand, the movement of the radial loading rod 21 can be guided, so that the telescopic movement of the first piston cylinder 22 drives the loading force of the radial loading rod 21 to be accurately applied to the radial position of the elastic bushing 10.
The loading movement process of the radial loading mechanism 2 is as follows: the first piston cylinder 22 drives the first piston rod 221 to do telescopic motion, and the first piston rod 221 drives the radial loading rod 21 to do linear reciprocating motion; the radial loading rod 21 drives the first clamping block 11 to reciprocate, so that the outer steel sleeve and the inner steel sleeve of the elastic bushing 10 perform circular relative movement, and further the fatigue property of the elastic bushing 10 and the radial rigidity of the elastic bushing 10 can be tested when the elastic bushing 10 is acted by radial loading force.
The axial loading mechanism 3 has the same structure as the radial loading mechanism 2 and comprises an axial loading rod 31 and a second piston cylinder 32 which are connected. The axial loading rod 31 is connected with the inner steel sleeve of the elastic bushing 10, and when the second piston cylinder 32 drives the piston rod to do telescopic motion, the axial loading rod 31 drives the inner steel sleeve of the elastic bushing 10 to do reciprocating motion, so that the inner steel sleeve of the elastic bushing 10 is relatively displaced with respect to the outer steel sleeve, and the fatigue property of the elastic bushing 10 under the cyclic axial force and the axial rigidity of the elastic bushing 10 are tested.
As shown in fig. 5, the axial loading mechanism 3 and the first torsion mechanism 4 apply an axial force or moment to the inner steel jacket of the elastic bushing 10 via the connecting rod 13, respectively. As shown in fig. 6, the elastic bushing 10 is sleeved and fixed on the connecting rod 13, and two ends of the connecting rod 13 are respectively connected with the axial loading mechanism 3 and the first torsion loading mechanism. In this embodiment 1, the connecting rod 13 is a double-ended screw, the screw is matched to pass through the central hole of the elastic bushing 10, and the two ends of the elastic bushing 10 are locked and fixed by the first locking nuts 15, so that the elastic bushing 10 is prevented from moving axially relative to the connecting rod 13.
When the axial loading mechanism 3 and the first torsion mechanism 4 are loaded simultaneously, the axial loading mechanism 3 drives the steel sleeve in the elastic bushing 10 to reciprocate along the central axis direction, so as to drive the first torsion loading rod 41 to reciprocate along the axis direction. To eliminate the effect of the reciprocating displacement of the first torsion loading bar 41 on the centering torsion loading of the first torsion mechanism 4, the first torsion loading bar 41 is selected as a ball spline. As shown in fig. 7, the spline shaft 411 of the ball spline is fixedly connected with the connecting rod 13, the spline housing 412 is fixedly connected with the torsion fixing seat 45, and because balls capable of moving along the axial direction of the spline shaft 411 exist between the spline shaft 411 and the spline housing 412, when the spline shaft 411 is driven by the connecting rod 13 to perform translational motion, the spline shaft 411 drives the balls between the spline shaft 411 and the spline housing 412 to move along the axial direction of the spline shaft 411, and the spline housing 412 does not move, so that relative movement is generated between the spline shaft 411 and the spline housing 412, and the axial movement of the spline shaft 411 is eliminated through the balls and cannot be transmitted to the spline housing 412. When the first deflection arm 43 is connected and drives the spline housing 412 to twist around the axis thereof, the swinging movement of the first deflection arm 43 is not affected by the axial movement of the spline shaft 411, so that the movement of the first torsion mechanism 4 for applying the centering torsion force to the elastic bushing 10 is not affected by the axial loading mechanism 3, and the accuracy of the fatigue test is ensured. Like the first torsion mechanism 4, the second torsion loading rod 51 is a ball spline to eliminate the influence of displacement generated by the radial loading motion of the radial loading mechanism 2 on the loading motion of the second torsion mechanism 5.
In order to make the first deflecting arm 43 drive the first torsion loading rod 41 to make torsion movement, the deflecting arm 43 is in a flange structure as a whole, and comprises a flange portion 431 for connecting the first torsion loading rod 41 and a deflecting portion 432 extending radially along the flange portion 431. The flange portion 431 of the first deflection arm 43 is connected with a first connection flange 453, an inner diameter of the first connection flange 453 is in radial fit with an outer diameter of the spline housing 412, a second key slot matched with the first key slot on the spline housing 412 is formed in the inner surface, and the spline housing 412 and the first connection flange 453 are fixedly connected with the first connection flange 453 in the circumferential direction through a connection key 452 assembled between the first key slot and the second key slot. In order to fix the spline housing 412 and the first connection flange 453 in the axial direction of the spline housing 412, one end of the first connection flange 453 passes through the torsion fixing seat 45, and an opening caliber at an end face near one end of the elastic bushing 10 is smaller than the outer diameter of the spline housing 412 and larger than the outer diameter of the spline shaft 411; the first connection flange 453 is provided with a first circlip 454 in the cavity near one end of the first deflection arm 43, and the first circlip 454 is fixed on the inner surface of the cavity and one end of the first circlip 454 is abutted against the spline housing 412.
A pair of third rolling bearings 451 is disposed between the first connection flange 453 and the torsion fixing base 45, and the opposite movement of the two third rolling bearings 451 is defined by a shoulder disposed on an axially outer wall of the first connection flange 453 and a second circlip 455, wherein the shoulder is disposed on a side close to the first deflection arm 43, the second circlip 455 is disposed on a side close to the elastic bushing 10, and the first connection flange 453 can be fixed to the torsion fixing base 45 through the shoulder and the elastic bushing 10. The relative movement of the two third rolling bearings 451 is defined by an inner stop ring 456 protruding from the steel sleeve inside the torsion fixing seat 45.
One end of the spline shaft 411, which is close to the elastic bushing 10, is fixedly connected with the connecting rod 13 through the second connecting flange 47, and the axis of the spline shaft 411 and the axis of the second connecting rod 13 are positioned on the same straight line. The second connection flange 47 includes a first flange 471 connected to one end of the spline shaft 411 and a second flange 472 connected to one end of the connection rod 13, wherein the first flange 471 is fixedly connected to the spline shaft 411 through a key, the second flange 472 is fixedly connected to the second flange 472 through a fixing block 473, and the first flange 471 and the second flange 472 are fixedly connected to each other, so that the spline shaft 411 is fixedly connected to the connection rod 13.
The loading process of the first torsion mechanism 4 is as follows: when the third piston cylinder 42 drives the piston rod to reciprocate, the piston rod drives the first connecting swing rod 46 so as to drive the first deflection arm 43 to reciprocate; the swing rotation of the first deflection arm 43 drives the spline housing 412 to twist around the axis thereof, thereby driving the spline shaft 411 to twist around the axis; the spline shaft 411 drives the connecting rod 13 connected with the spline shaft to twist reciprocally, so that the inner steel sleeve of the elastic bushing 10 connected with the connecting rod 13 is driven to twist around the axis.
As shown in fig. 8, the radial loading mechanism 2 and the second torsion mechanism 5 are connected to the inner steel jacket of the elastic bushing 10 by a first snap 11 and a second snap 12, respectively. As shown in fig. 9, one end of the radial loading mechanism 2 is fixedly connected with a first clamping block 11, and radial force is applied to the outer steel sleeve of the elastic bushing 10 through the first clamping block 11; one end of the second torsion mechanism 5 is fixedly connected with a second clamping block 12, and a torsion moment for driving the elastic bushing 10 to twist around the radial direction is applied to the outer steel sleeve of the elastic bushing 10 through the second clamping block 12; the first clamping block 11 and the second clamping block 12 are fixedly connected and can clamp the elastic bushing 10 in the radial direction.
In order to improve the universality of the elastic bushing fatigue testing machine for the elastic bushings 10 of different types, a universal sleeve 14 is connected between the elastic bushing 10 and the first clamping block 11 and the second clamping block 12. The universal sleeve 14 is sleeved on the outer steel sleeve of the elastic bushing 10 and is in interference fit connection with the elastic bushing 10, so that the elastic bushing 10 is tightly matched with the universal sleeve 14 to jointly move in the test process. The outer wall of the universal sleeve 14 abuts against the inner surfaces of the first and second clamping blocks 11 and 12, respectively, to fix the universal sleeve 14 in the radial direction.
As shown in fig. 10, in order to prevent the second torsion mechanism 5 from driving the elastic bushing 10 to twist around the radial direction and affecting the radial force loading of the radial loading mechanism 2 on the elastic bushing 10, a first adapter sleeve 23 is connected between the radial loading rod 21 and the first piston rod 221. The first adapter sleeve 23 has a sleeve-like structure with one end opened and the other end provided with a threaded hole, and the threaded hole is formed at one end to fix the first piston rod 221 of the first piston cylinder 22 by threaded connection. One end of the radial loading rod 21, which is far away from the first clamping block 11, is positioned in the cavity of the first adapter sleeve 23 and is connected with the first adapter sleeve 23 through a first rolling bearing 25.
In order to prevent the first rolling bearing 25 from displacing in the axial direction of the radial loading rod 21, a shaft shoulder is provided at one end of the radial loading rod 21 located in the cavity of the first adapter sleeve 23, and a thread is provided at the end, and the axial displacement of the first rolling bearing 25 along the radial loading rod 21 is defined by a second lock nut 26 and the shaft shoulder located at both ends of the first rolling bearing 25, respectively. In order to fix the first rolling bearing 25 and the first adapter sleeve 23 along the axial direction, an annular step is formed on the inner surface of the first adapter sleeve 23, an end cover 24 is fixedly connected to the end face of one end close to the opening, the end cover 24 stretches into the first adapter sleeve 23 towards one end of the first adapter sleeve 23 and abuts against the step face of the annular step, the outer diameter of the stretching-in end is matched with the inner diameter of the first adapter sleeve 23 towards one end of the elastic bushing 10, and the inner diameter of the stretching-in end is in interference fit with the outer diameter of the first rolling bearing 25. The two end surfaces of the first rolling bearing 25 are respectively abutted against the step surface of the annular step and the inner surface of the end cover 24, so that the first rolling bearing 25 is fixed relative to the first adapter sleeve 23 in the axial direction. In order to improve the connection tightness of the end cover 24 and the first adapter sleeve 23, a convex ring is convexly arranged at one end of the end cover 24 extending into the first adapter sleeve 23, an annular groove is formed in the inner surface of the first adapter sleeve 23 relative to the position of the convex ring, and the convex ring and the annular groove are matched to prevent the first adapter sleeve 23 and the end cover 24 from loosening and displacing in the axial direction of the radial loading rod 21 to influence the loading movement of the radial loading rod 21 when the first piston cylinder 22 drives the radial loading rod 21 to reciprocate.
When the radial loading mechanism 2 and the second torsion mechanism 5 act simultaneously, the elastic bushing 10 is twisted around the radial direction due to the torsion moment applied to the elastic bushing 10 by the second torsion mechanism 5, so as to drive the first clamping block 11 to twist, and further drive the radial loading rod 21 to twist reciprocally. Since the radial loading rod 21 is connected to the first adapter sleeve 23 through the first rolling bearing 25, when the radial loading rod 21 rotates, the first rolling bearing 25 is driven to rotate relative to the first adapter sleeve 23, so that the rotational motion of the radial loading rod 21 is eliminated by the first rolling bearing 25 and cannot be transmitted to the first piston cylinder 22, and thus the linear reciprocating motion of the first piston cylinder 22 is not affected, that is, the loading of the radial force of the elastic bushing 10 by the linear motion of the radial loading rod 21 is not affected. Similarly, in order to prevent the first torsion mechanism 4 from driving the elastic bushing 10 to twist around the axis and affecting the loading of the axial loading mechanism 3 on the axial force of the steel sleeve in the elastic bushing 10, a second adapter sleeve 23 is connected between the axial loading rod 31 and the piston rod of the second piston cylinder 32.
As shown in fig. 11, a surface of the first clamping block 11 connected with the radial loading mechanism 2 is a plane, and is provided with a plurality of connecting holes for being connected with the radial loading mechanism 2 through a flange; the surface of the first clamping block 11 facing the elastic bushing 10 is provided with a first arc-shaped surface 111 matched with the outer diameter radian of the universal sleeve 14, and two ends of the first arc-shaped surface 111 are provided with connecting lugs 112. As shown in fig. 12, the second clamping block 12 is a U-shaped clamping block, the opening of the U-shaped clamping block faces the universal sleeve 14, the surface opposite to the second torsion mechanism 5 is a plane, the surface abutting against the universal sleeve 14 is provided with a second arc-shaped surface 121 matched with the universal sleeve 14, and both ends of the second arc-shaped surface 121 are provided with connecting grooves 122. The first clamping block 11 and the second clamping block 12 are matched and connected with the universal sleeve 14 through the first arc-shaped surface 111 and the second arc-shaped surface 121 which are opposite to each other so as to fix the radial direction of the universal sleeve 14, and the connecting convex block 112 of the first clamping block 11 and the connecting groove 122 of the second clamping block 12 are matched and clamped and connected fixedly through threads, so that the first clamping block 11 and the second clamping block 12 are prevented from loosening relatively in the test process, the stress change of the elastic bushing 10 is caused, and the accuracy of the test result is affected. The connection and fixation of the elastic bushing 10 to the respective mechanisms in the axial and radial directions described above may be also be performed in other manners, and the present embodiment 1 is not limited in this respect too.
In this embodiment, the first piston cylinder 22, the second piston cylinder 32, the third piston cylinder 42 and the fourth piston cylinder 52 are all servo cylinders, and the stroke of each cylinder can be precisely controlled by controlling the servo cylinders through a servo control system, so that the force and the moment applied to the elastic bushing 10 are controlled, the response and the fatigue state of the elastic bushing 10 under different force and moment states are precisely simulated, and the operation is safer and more reliable.
The scale 61 is disposed at the position of the test stand 6 relative to the elastic bushing 10, the scale 61 is disposed along the central axis direction of the elastic bushing 10, and the second translation fixing base 37 of the axial loading mechanism 3 and the torsion fixing base 45 of the first torsion mechanism 4 can move along the length direction of the scale 61 relative to the scale 61 to change the distance between the second translation fixing base 37 and/or the torsion fixing base 45 relative to the elastic bushing 10. When the elastic bushings 10 of different types are tested, the distance between the second translation fixing seat 37 of the axial loading mechanism 3 and the torsion fixing seat 45 of the first torsion structure and the elastic bushings 10 can be accurately adjusted according to the types and the sizes of the elastic bushings 10, so that the fatigue test can be performed on the elastic bushings 10 of different types and sizes on the basis of not changing the stroke and the control parameters of each servo oil cylinder, and the fatigue tester of the elastic bushings 10 has better universality.
Example 2
As shown in fig. 13, the structure of the elastic bushing fatigue testing machine provided in this embodiment 2 is substantially the same as that of the elastic bushing fatigue testing machine provided in embodiment 1, and the details of this embodiment are not repeated, except that: the first torsion actuator and the second torsion actuator adopted in this embodiment are both rotary cylinders: the rotating rod of the first rotating cylinder 410 is connected with the first connecting flange 453, when the first rotating cylinder 410 drives the rotating rod to rotate, the rotating rod rotates to drive the first connecting flange 453 to rotate, so as to drive the ball spline connected with the first connecting flange 453 to rotate, and further drive the connecting rod 13 to twist around the center, and further realize the twisting around the center of the steel sleeve in the elastic bushing 10; the rotary rod of the second rotary cylinder 510 is connected with the third connecting flange 553, when the second rotary cylinder 510 drives the rotary rod to rotate, the rotation of the rotary rod drives the third connecting flange 553 to rotate, thereby driving the ball spline connected with the third connecting flange 553 to rotate, and driving the second clamping block 12 to twist around the radial direction of the elastic bushing 10, and further realizing the radial twisting around the outer steel sleeve of the elastic bushing 10. In this embodiment, the two rotating cylinders 53 are servo cylinders, which can precisely control the rotation angle and direction of the rotating rod, so as to control the torsion amplitude of the steel sleeve around the center in the elastic bushing 10 and the torsion amplitude of the steel sleeve around the axis outside the elastic bushing 10.
According to the elastic bushing fatigue testing machine provided by the invention, through independent or simultaneous loading of the radial loading mechanism 2, the axial loading mechanism 3, the first torsion mechanism 4 and/or the second torsion mechanism 5, torsion, axial, radial and inclined combined stress of the elastic bushing 10 can be reproduced, so that the stress working condition of the elastic bushing 10 is more similar to the stress condition in a real working state, the simulation result is more realistic and reliable, the simulation test of a road spectrum is better realized, and the functionality is strong; by modifying the inner diameter of the universal sleeve 14, the elastic bushings 10 with different types and sizes can be tested under the condition of not changing other structures of the fatigue testing machine, so that the universality is strong; the rotational influence of the second torsion loading motion on the radial loading motion is eliminated by adopting the first adapter sleeve 23 and the first rolling bearing 25, the rotational influence of the first torsion loading motion on the axial loading motion is eliminated by adopting the second adapter sleeve 33 and the second rolling bearing, and the displacement influence of the radial loading or the axial loading on the torsion loading motion is eliminated by adopting the ball spline, so that the test result is more accurate. The elastic bushing fatigue tester provided by the invention has the advantages of simple structure, safety, reliability, strong functionality, high universality, good accuracy and the like.
Note that the above is only a preferred embodiment of the present invention and the technical principle applied. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious changes, rearrangements and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, while the invention has been described in connection with the above embodiments, the invention is not limited to the embodiments, but may be embodied in many other equivalent forms without departing from the spirit or scope of the invention, which is set forth in the following claims.
Claims (7)
1. An elastic bushing fatigue testing machine, comprising:
an axial loading mechanism (3) connected with the inner steel sleeve of the elastic bushing (10) and applying axial force to the inner steel sleeve of the elastic bushing (10);
the radial loading mechanism (2) is connected with the outer steel sleeve of the elastic bushing (10) and applies radial force to the outer steel sleeve of the elastic bushing (10);
The first torsion mechanism (4) is connected with the inner steel sleeve of the elastic bushing (10) and drives the inner steel sleeve of the elastic bushing (10) to twist reciprocally around the central shaft of the elastic bushing (10);
the second torsion mechanism (5) is connected with the outer steel sleeve of the elastic bushing (10) and drives the outer steel sleeve of the elastic bushing (10) to reciprocate around the radial direction of the outer steel sleeve;
The elastic bushing (10) is sleeved and fixed on the connecting rod (13), one end of the connecting rod (13) is fixedly connected with the axial loading mechanism (3), and the other end of the connecting rod is fixedly connected with the first torsion mechanism (4);
The radial loading mechanism (2) is connected to the outer steel sleeve of the elastic bushing (10) through a first clamping block (11), the second torsion mechanism (5) is connected to the outer steel sleeve of the elastic bushing (10) through a second clamping block (12), and the first clamping block (11) is connected with the second clamping block (12) and clamps the outer steel sleeve of the elastic bushing (10) along the radial direction of the outer steel sleeve;
The radial loading mechanism (2) comprises a radial loading rod (21) and a first piston cylinder (22) connected with and driving the radial loading rod (21), and the radial loading rod (21) is fixedly connected with the first clamping block (11);
the axial loading mechanism (3) comprises an axial loading rod (31) and a second piston cylinder (32) connected with and driving the axial loading rod (31), and the axial loading rod (31) is fixedly connected with one end of the connecting rod (13);
The outer steel sleeve of the elastic bushing (10) is sleeved with a universal sleeve (14), and the universal sleeve (14) is abutted to the inner surface of the first clamping block (11) and the inner surface of the second clamping block (12).
2. The elastic bushing fatigue testing machine according to claim 1, wherein a first adapter sleeve (23) is connected between the radial loading rod (21) and the first piston cylinder (22), the first adapter sleeve (23) is fixedly connected with the first piston cylinder (22), and a first rolling bearing (25) is arranged between the radial loading rod (21) and the first adapter sleeve (23);
A second adapter sleeve (33) is connected between the axial loading rod (31) and the second piston cylinder (32), the second adapter sleeve (33) is fixedly connected with the second piston cylinder (32), and a second rolling bearing is arranged between the axial loading rod (31) and the second adapter sleeve (33).
3. The elastic bushing fatigue testing machine according to claim 1, wherein the first torsion mechanism (4) includes a first torsion loading rod (41) and a first torsion actuator connected to and driving the first torsion loading rod (41) to twist reciprocally about an axis of the first torsion loading rod (41), the axis of the first torsion loading rod (41) coincides with the central axis, and one end of the first torsion loading rod (41) not connected to the first torsion actuator is connected to the other end of the connecting rod (13);
The second torsion mechanism (5) comprises a second torsion loading rod (51) and a second torsion actuator which is connected with and drives the second torsion loading rod (51) to twist reciprocally around the axial direction of the second torsion loading rod (51), the axis of the second torsion loading rod (51) coincides with the radial direction, and one end of the second torsion loading rod (51) which is not connected with the second torsion actuator is fixedly connected with the second clamping block (12).
4. A machine as claimed in claim 3, wherein said first torsion loading bar (41) and said second torsion loading bar (51) are both ball splines.
5. The elastic bushing fatigue testing machine according to claim 4, wherein the first torsion loading rod (41) is supported on a torsion fixing seat (45), and a third rolling bearing (451) is arranged between the first torsion loading rod (41) and the torsion fixing seat (45).
6. The elastic bushing fatigue testing machine according to claim 5, wherein the first torsion actuator comprises a first deflection arm (43), a first connecting swing rod (46) and a third piston cylinder (42) which are connected in turn in a rotating manner, and one end of the first deflection arm (43) which is not connected with the first connecting swing rod (46) is connected with the first torsion loading rod (41) in a penetrating manner.
7. A machine according to claim 3, wherein the first torsion actuator is a first rotary cylinder (410), and the first rotary cylinder (410) is flanged to the first torsion loading rod (41).
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| CN201711251546.4A CN107741323B (en) | 2017-12-01 | 2017-12-01 | Elastic bushing fatigue testing machine |
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| CN201711251546.4A CN107741323B (en) | 2017-12-01 | 2017-12-01 | Elastic bushing fatigue testing machine |
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| CN108627341A (en) * | 2018-06-06 | 2018-10-09 | 慈兴集团有限公司 | A kind of bearing high-speed performance test machine |
| CN109269886B (en) * | 2018-09-28 | 2024-02-23 | 西安力创材料检测技术有限公司 | Dynamic and static rigidity testing device for three-way loading of engine suspension bushing |
| CN110702409B (en) * | 2019-09-29 | 2021-10-15 | 中国航发北京航空材料研究院 | Elastic joint bearing fatigue test device |
| CN110553843B (en) * | 2019-10-17 | 2024-05-31 | 上海精智实业股份有限公司 | Triaxial elastic bearing bush fatigue testing machine |
| CN111929048A (en) * | 2020-08-06 | 2020-11-13 | 广州汽车集团股份有限公司 | Bushing fatigue endurance test device |
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