CN113008480B - Comprehensive performance test device for differential lock control mechanism - Google Patents
Comprehensive performance test device for differential lock control mechanism Download PDFInfo
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- CN113008480B CN113008480B CN202110219704.8A CN202110219704A CN113008480B CN 113008480 B CN113008480 B CN 113008480B CN 202110219704 A CN202110219704 A CN 202110219704A CN 113008480 B CN113008480 B CN 113008480B
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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
- G01M3/00—Investigating fluid-tightness of structures
- G01M3/02—Investigating fluid-tightness of structures by using fluid or vacuum
- G01M3/26—Investigating fluid-tightness of structures by using fluid or vacuum by measuring rate of loss or gain of fluid, e.g. by pressure-responsive devices, by flow detectors
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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
- G01M5/00—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings
Abstract
The invention discloses a comprehensive performance test device for a differential lock control mechanism, and relates to the technical field of automobile tests. This differential lock operating mechanism comprehensive properties test device includes: the air outlet end of the air supply mechanism is communicated with the compression chamber so as to supply air into the compression chamber; the differential lock gear sleeve comprises a movable gear sleeve and a fixed gear sleeve which are coaxially and oppositely arranged, and the piston is in transmission connection with the movable gear sleeve through a shifting fork so as to drive the movable gear sleeve to move relative to the fixed gear sleeve along the axial direction of the piston, so that the movable gear sleeve is meshed with or separated from the fixed gear sleeve; the rotary driving mechanism is in transmission connection with the movable gear sleeve and is used for driving the movable gear sleeve to rotate; and the moving mechanism is detachably connected with the moving gear sleeve and is used for moving the moving gear sleeve to a preset position along the self axial direction and keeping the moving gear sleeve still. The test device can test the air cylinder tightness, response time and axial rigidity of the differential lock control mechanism, thereby obtaining the comprehensive performance of the differential lock control mechanism.
Description
Technical Field
The invention relates to the technical field of automobile tests, in particular to a device for testing the comprehensive performance of a differential lock control mechanism.
Background
When the ground adhesion conditions such as wet and slippery, muddy, ice and snow are not good or the adhesion conditions of the left and right driving wheels are greatly different during the running of the vehicle, the differential lock of the driving axle is used when the driver needs to increase the driving force of the vehicle, and the functional characteristics of the differential lock are particularly important. Specifically, the differential lock includes an operating mechanism for urging a moving sleeve of the differential lock to move, causing the moving sleeve to engage, maintain engagement, and disengage from a fixed sleeve.
The performance of the differential lock operating mechanism is mainly embodied by the dynamic sealing performance of a cylinder in the differential lock operating mechanism, the response time of the differential lock operating mechanism and the axial rigidity of the differential lock operating mechanism.
The cylinder is a core execution mechanism of the differential lock control mechanism, and the tightness of the cylinder is the key performance of the cylinder. In the existing drive axle test, the tightness of the cylinder at a specific working position is usually tested only, and the tightness comprises the tightness of a starting point of a piston of the cylinder, the tightness when a tooth crest of a movable gear sleeve is opposite to a tooth crest of a fixed gear sleeve and the tightness when the movable gear sleeve and the fixed gear sleeve of the differential lock are completely meshed, but the tightness of the cylinder in the middle moving process of the cylinder from the starting point of the piston to the complete meshing point is not verified, and the tightness of the cylinder is not verified comprehensively.
The time during which the driver can feel the power response of the differential lock operating mechanism when it is operating includes the time it takes for the differential lock operating mechanism to push the lock moving sleeve into engagement with the fixed sleeve (referred to simply as the engagement response time) and the time it takes for the subsequent moving sleeve and fixed sleeve to disengage (referred to simply as the disengagement response time). When the vehicle is in working conditions such as climbing, the driving quality of the vehicle can be improved by shorter combination response time; when the driver disengages the differential lock, the longer the disengagement response time, the worse the qualities of driving safety, vehicle handling, and the like of the vehicle are indicated. Therefore, knowing the response time of the differential lock manipulation structure is particularly important to improve the driving experience.
In the process of pushing the movable gear sleeve by the differential lock operating mechanism, the rigidity value of a rod system consisting of a shifting fork shaft, a shifting fork and the like of the differential lock operating mechanism can influence the slightly inclined state of the movable gear sleeve of the differential lock when the movable gear sleeve of the differential lock operates on the second section of spline of the half shaft, and further influence the meshing condition of the movable gear sleeve and the fixed gear sleeve of the differential lock. Therefore, the test of the rigidity of the shifting fork and the shifting fork shaft along the axial direction of the half shaft has guiding significance for the design, development, use and the like of the differential lock.
However, there is still a lack of devices for testing the above characteristics, and the performance of the differential lock operating mechanism cannot be fully measured. Therefore, a comprehensive performance testing device for a differential lock operating mechanism is needed to solve the above problems.
Disclosure of Invention
The invention aims to provide a comprehensive performance test device for a differential lock operating mechanism, which can measure the dynamic sealing performance of a cylinder in the differential lock operating mechanism, measure the response time and the axial rigidity of the differential lock operating mechanism and comprehensively obtain the performance of the differential lock operating mechanism.
In order to achieve the purpose, the invention adopts the following technical scheme:
the utility model provides a differential lock operating mechanism comprehensive properties test device for the comprehensive properties of the differential lock operating mechanism that awaits measuring, the differential lock operating mechanism that awaits measuring includes cylinder and shift fork, the cylinder includes cylinder body and piston, the piston with the cylinder body cooperation forms the compression chamber, differential lock operating mechanism comprehensive properties test device includes:
the air outlet end of the air supply mechanism is communicated with the compression chamber so as to supply air into the compression chamber;
the differential lock gear sleeve comprises a movable gear sleeve and a fixed gear sleeve which are coaxially and oppositely arranged, and the piston is in transmission connection with the movable gear sleeve through the shifting fork so as to drive the movable gear sleeve to move relative to the fixed gear sleeve along the self axial direction and enable the movable gear sleeve and the fixed gear sleeve to be meshed with each other or separated from each other;
the rotary driving mechanism is in transmission connection with the movable gear sleeve and is used for driving the movable gear sleeve to rotate;
and the moving mechanism is detachably connected with the moving gear sleeve and is used for moving the moving gear sleeve to a preset position along the self axial direction and keeping the moving gear sleeve still.
Optionally, the device for testing the comprehensive performance of the differential lock operating mechanism further comprises a pressure sensor and a displacement sensor, the pressure sensor and the displacement sensor are respectively connected with the cylinder, the pressure sensor is used for measuring the air pressure in the compression chamber, and the displacement sensor is used for measuring the displacement of the piston.
Optionally, the air supply mechanism comprises an air source and an air servo valve, and the air outlet end of the air source is communicated with the compression chamber through the air servo valve.
Optionally, the rotary driving mechanism comprises a bearing seat, a rotating shaft and a half shaft, wherein the rotating shaft is mounted on the bearing seat;
the first end of semi-axis is provided with the ring flange, the second end of semi-axis is provided with the spline, the one end of pivot is passed through the ring flange with the semi-axis transmission is connected, the semi-axis passes through the spline with remove tooth cover sliding transmission and connect, just the semi-axis with remove the coaxial setting of tooth cover.
Optionally, a ring groove is circumferentially arranged on the movable gear sleeve;
one end of the shifting fork is connected with one side of the compression chamber, which deviates from the piston, and the other end of the shifting fork is sleeved on the annular groove and is in clearance fit with the bottom wall of the annular groove.
Optionally, the moving mechanism comprises a fixed seat and a moving sleeve;
follow on the fixing base the axial of removing the tooth cover is provided with fixing base screw thread through-hole, the fixing base passes through fixing base screw thread through-hole interval cover is established the outside of semi-axis, the also interval cover of removal sleeve is established the outside of semi-axis, just the first end threaded connection of removal sleeve is in the fixing base screw thread through-hole, removal sleeve's second end with it can dismantle the connection to remove the tooth cover.
Optionally, the moving mechanism includes a fixed seat and a moving sleeve, a smooth through hole is formed in the fixed seat along the axial direction of the moving gear sleeve, the fixed seat is sleeved outside the half shaft at intervals through the smooth through hole, the moving sleeve is sleeved outside the half shaft at intervals, a first end of the moving sleeve is slidably connected in the smooth through hole, and a second end of the moving sleeve is detachably connected with the moving gear sleeve;
moving mechanism still includes the electric drive subassembly, the electric drive subassembly includes driving motor, hold-in range, action wheel and follows the driving wheel, the both ends of hold-in range are established respectively the action wheel with follow the driving wheel on, driving motor with the action wheel transmission is connected in order to drive the action wheel rotates, still be provided with from driving wheel screw thread through-hole along the axial on the follow driving wheel, pass through from the driving wheel screw thread through-hole threaded connection be in outside the removal sleeve, just follow the driving wheel and be located between the removal sleeve's the both ends.
Optionally, the driving motor is set as a servo motor, the synchronous belt is set as a toothed belt, and the driving wheel and the driven wheel are both set as toothed belt wheels.
Optionally, from the first end of the movable sleeve to the second end of the movable sleeve, the movable sleeve includes a guide sleeve, an intermediate sleeve and a connection sleeve which are coaxially arranged and sequentially connected;
the guide sleeve with the fixing base is connected, middle telescopic first end with the guide sleeve passes through the tang location and passes through the fastener fixed, middle telescopic second end with the first end of connecting sleeve rotates to be connected, the second end of connecting sleeve with it can dismantle the connection to remove the tooth cover.
Optionally, the moving mechanism further comprises a thrust bearing, and the second end of the intermediate sleeve is rotatably connected with the first end of the connecting sleeve through the thrust bearing.
The invention has the beneficial effects that:
the invention provides a comprehensive performance test device for a differential lock control mechanism, which can test the air tightness of an air cylinder when a moving mechanism is connected with a moving gear sleeve: the movable gear sleeve is moved and fixed to a preset position through the moving mechanism, the air pressure supplied to the compression chamber from the air supply mechanism to the air cylinder reaches standard pressure (namely the actual pressure of a whole vehicle brake system), the pressure drop condition in the air cylinder within a certain period of time is tested, and the air cylinder tightness test can be completed.
When the moving mechanism is separated from the moving sleeve, the response time of the differential lock operating mechanism can be tested: before the test, the movable gear sleeve is properly rotated through the rotary driving mechanism, so that the movable gear sleeve is positioned at a subsequent working position which can be completely meshed with the fixed gear sleeve; during testing, the air supply mechanism is used for supplying air into the compression chamber, and the movable gear sleeve is driven to move through the piston and the shifting fork in sequence, so that the movable gear sleeve can be meshed with the fixed gear sleeve; and then, the air supply mechanism stops supplying air and exhausts the compression chamber, and the shifting fork returns and drives the movable gear sleeve to be separated from the fixed gear sleeve. The engagement and disengagement process between the movable gear sleeve and the fixed gear sleeve is monitored, and the response time of the differential lock control mechanism can be obtained.
When the moving mechanism is separated from the moving gear sleeve, the axial rigidity of the differential lock operating mechanism can be tested: before the test, the movable gear sleeve is properly rotated through the rotary driving mechanism, so that the tooth top of the movable gear sleeve is opposite to the tooth top of the fixed gear sleeve; during the test, the air pressure of the air supply mechanism for ventilating the compression chamber into the compression chamber reaches the standard pressure, so that the piston drives the movable gear sleeve to move through the shifting fork until the tooth top of the movable gear sleeve is abutted against the tooth top of the fixed gear sleeve; then, the compression chamber is exhausted to reduce the air pressure in the compression chamber to a certain pressure. And monitoring the air pressure change in the compression chamber and the displacement change of the piston in the test process, and calculating the ratio of the air pressure change amount to the displacement change amount, wherein the ratio is the axial rigidity value of the differential lock control mechanism.
In a whole view, the device for testing the comprehensive performance of the differential lock operating mechanism can test the cylinder tightness, the response time, the axial rigidity and the like of the differential lock operating mechanism, thereby obtaining the comprehensive performance of the differential lock operating mechanism.
Drawings
FIG. 1 is a schematic overall structure diagram of a device for testing the comprehensive performance of a differential lock operating mechanism according to an embodiment of the present invention;
FIG. 2 is a schematic structural diagram of a moving mechanism in the device for testing the comprehensive performance of the control mechanism of the differential lock according to the first embodiment of the present invention;
FIG. 3 is a schematic overall structural diagram of a device for testing the comprehensive performance of a differential lock operating mechanism according to a second embodiment of the present invention;
fig. 4 is a schematic structural diagram of a moving mechanism in the device for testing the comprehensive performance of the differential lock operating mechanism according to the second embodiment of the present invention.
In the figure:
100. the differential lock control mechanism to be tested; 101. a cylinder; 1011. a cylinder body; 1012. a piston; 1013. a compression chamber; 102. a reducer housing; 103. a fork shaft; 104. a shifting fork; 105. a shift fork return spring;
1. an air supply mechanism; 11. a gas source; 12. an air servo valve;
2. a differential lock gear sleeve; 21. moving the gear sleeve; 22. fixing a gear sleeve;
3. a rotation driving mechanism; 31. a bearing seat; 32. a rotating shaft; 33. a transition piece; 331. a half coupling; 332. a flange member; 34. a half shaft; 341. a flange plate;
4. a moving mechanism; 41. a fixed seat; 411. a support; 412. fixing the sleeve; 42. moving the sleeve; 421. a guide sleeve; 422. an intermediate sleeve; 4221. a first circular ring; 423. a connecting sleeve; 4231. a second circular ring; 4232. a plug-in part; 43. a thrust bearing; 44. a handle; 45. an electric drive assembly; 451. a drive motor; 452. a synchronous belt; 453. a driving wheel; 454. a driven wheel;
5. a pressure sensor; 6. a displacement sensor; 7. measurement and control and electric mechanism.
Detailed Description
In order to make the technical problems solved, the technical solutions adopted and the technical effects achieved by the present invention clearer, the technical solutions of the present invention are further described below by way of specific embodiments with reference to the accompanying drawings.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
In the description of the present embodiment, the terms "upper", "lower", "left", "right", and the like are used based on the orientations and positional relationships shown in the drawings only for convenience of description and simplification of operation, and do not indicate or imply that the referred device or element must have a specific orientation, be configured and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used only for descriptive purposes and are not intended to have a special meaning.
Example one
The embodiment provides a device for testing the comprehensive performance of a differential lock operating mechanism, which is used for testing the comprehensive performance of the differential lock operating mechanism 100 to be tested. As shown in fig. 1, the differential lock operating mechanism 100 to be tested includes a cylinder 101 and a fork 104, the cylinder 101 includes a cylinder body 1011 and a piston 1012 disposed in the cylinder body 1011, and the piston 1012 and the cylinder body 1011 cooperate to form a compression chamber 1013.
The comprehensive performance test device for the differential lock control mechanism comprises an air supply mechanism 1, a differential lock gear sleeve 2, a rotary driving mechanism 3 and a moving mechanism 4. Wherein, the air outlet end of the air supply mechanism 1 is communicated with the compression chamber 1013 to supply air into the compression chamber 1013. The differential lock gear sleeve 2 comprises a movable gear sleeve 21 and a fixed gear sleeve 22 which are coaxially and oppositely arranged, and a piston 1012 is in transmission connection with the movable gear sleeve 21 through a shifting fork 104 so as to drive the movable gear sleeve 21 to move relative to the fixed gear sleeve 22 along the axial direction of the piston, so that the movable gear sleeve 21 and the fixed gear sleeve 22 are meshed with each other or separated from each other. The rotary driving mechanism 3 is in transmission connection with the movable gear sleeve 21, and the rotary driving mechanism 3 is used for driving the movable gear sleeve 21 to rotate. The moving mechanism 4 is detachably connected with the moving gear sleeve 21, and the moving mechanism 4 is used for moving the moving gear sleeve 21 to a preset position along the self axial direction and keeping the moving gear sleeve 21 still.
The specific working process of the differential lock control mechanism comprehensive performance test device is explained.
When the moving mechanism 4 is connected to the moving sleeve 21, the cylinder tightness of the differential lock operating mechanism 100 to be tested can be tested. Specifically, three specific measurement points, including a start point, an intermediate point, and an end point, may be determined based on the actual operating conditions in which the cylinder 101 is located. Here, the starting position of the piston 1012 is set as a starting point, the position of the tooth tip to the tooth tip of the movable sleeve 21 and the fixed sleeve 22 is set as an intermediate point, and the position where the movable sleeve 21 and the fixed sleeve 22 are completely engaged is set as an end point. Further, a plurality of measurement points are provided between the start point and the intermediate point and between the intermediate point and the end point, respectively.
In this embodiment, the starting point, the intermediate point, and the end point are calculated, and 23 measurement points are provided in total, and the position of the movable sleeve 21 corresponding to the measurement points is a preset position to be reached by the movable sleeve 21. At the beginning, the moving gear sleeve 21 is moved and fixed to a first preset position through the moving mechanism 4, the air pressure supplied to the compression chamber 1013 in the air cylinder 101 through the air supply mechanism 1 reaches a standard pressure (namely the actual pressure of the whole vehicle brake system), the pressure drop condition in the air cylinder 101 in the subsequent 90 seconds is tested and recorded, and then the air cylinder sealing performance at the starting point can be measured. And then, referring to the process, the air cylinder sealing performance at the rest measuring points can be measured in sequence, and the air cylinder sealing performance test is finished.
When the moving mechanism 4 is separated from the moving sleeve 21, the response time and the axial rigidity of the differential lock operating mechanism 100 to be tested can be tested.
Here, the response time test is described first. Before the test, the rotary driving mechanism 3 appropriately rotates the movable gear sleeve 21, so that the movable gear sleeve 21 is in a subsequent working position capable of being completely meshed with the fixed gear sleeve 22. During the test, the air supply mechanism 1 supplies air into the compression chamber 1013 to move the piston 1012, so that the piston 1012 can drive the movable gear sleeve 21 to move through the shifting fork 104 to mesh the movable gear sleeve 21 with the fixed gear sleeve 22; after that, when the gas supply means 1 stops supplying gas into the compression chamber 1013 and exhausts the compression chamber 1013, the fork 104 returns to the original position and the movable sleeve 21 is separated from the fixed sleeve 22. By monitoring the above test process, the engagement start time, the engagement end time, the disengagement start time, and the disengagement end time of the movable sleeve 21 and the fixed sleeve 22 can be measured, thereby obtaining the response time of the differential lock operating mechanism.
For the axial stiffness test, before the test, the movable sleeve 21 was appropriately rotated by the rotary drive mechanism 3 so that the tooth tips of the movable sleeve 21 were opposed to the tooth tips of the fixed sleeve 22. During the test, the air supply mechanism 1 supplies air into the compression chamber 1013 until the air pressure in the compression chamber 1013 reaches the standard pressure, so that the piston 1012 drives the movable gear sleeve 21 to move through the shifting fork 104 until the tooth tops of the movable gear sleeve 21 are abutted with the tooth tops of the fixed gear sleeve 22 and are kept for 3 seconds; thereafter, the compression chamber 1013 was slowly vented to reduce the pressure in the compression chamber 1013 to 30% of the standard pressure, and the pressure release was stopped and the test was terminated after 3 seconds. The air pressure change in the compression chamber 1013 and the displacement change of the piston 1012 during the above test are monitored, and the ratio of the air pressure change amount to the displacement change amount is calculated, which is the axial stiffness value of the differential lock operating mechanism.
As can be seen from the above description, the device for testing the comprehensive performance of the differential lock operating mechanism can test the air cylinder tightness, the response time, the axial rigidity and the like of the differential lock operating mechanism, so as to obtain the comprehensive performance of the differential lock operating mechanism. Meanwhile, the comprehensive performance test device for the differential lock control mechanism is compact in structure, a whole vehicle test is not needed, the test cost is low, and the test period is short.
In this embodiment, in order to keep the same with the actual working condition, the differential lock operating mechanism 100 to be tested further includes a reducer housing 102, a fork shaft 103, and a fork return spring 105. Wherein the retarder housing 102 is mounted on the side of the fork 104 facing away from the piston 1012. The shift fork 104 includes a fork rod and a fork foot disposed at one end of the fork rod. The fork shaft 103 is mounted on the end of the fork rod that is not connected to the fork leg, and one end of the fork shaft 103 is fixedly connected to the piston 1012, and the other end of the fork shaft 103 is slidably connected to the inside of the reducer case 102 along the moving direction of the fork 104. The shifting fork 104 is sleeved on the movable gear sleeve 21 through a fork foot. A fork return spring 105 is installed in the reducer case 102, and both ends of the fork return spring 105 are respectively abutted against the reducer case 102 and the fork 104. When the air supply mechanism 1 stops supplying air to the air cylinder 101, the shifting fork 104 can be automatically returned through the elastic force of the shifting fork return spring 105.
Optionally, as shown in fig. 1, the device for testing the comprehensive performance of the differential lock operating mechanism further comprises a pressure sensor 5 and a displacement sensor 6. Wherein a pressure sensor 5 and a displacement sensor 6 are respectively connected to the cylinder 101, the pressure sensor 5 is for measuring the air pressure in the compression chamber 1013, and the displacement sensor 6 is for measuring the displacement of the piston 1012.
Specifically, in the cylinder tightness test, a curve of the change of the air pressure of the compression chamber 1013 with time is obtained by the pressure sensor 5, and then the pressure drop at the measurement point, that is, the tightness of the cylinder 101 is measured, is obtained by the curve.
In the response time test, a time-dependent profile of the air pressure in the compression chamber 1013 (denoted by C1) is obtained by the pressure sensor 5, and a time-dependent profile of the displacement of the piston 1012 (denoted by C2) is obtained by the displacement sensor 6. At this time, the time when the cylinder 101 starts to ventilate can be obtained through the curve C1, which is embodied as the time when the pressure value on the curve C1 starts to rise from zero, and this time is the meshing start time; the time for the moving sleeve 21 to just reach full engagement with the fixed sleeve 22 is obtained by curve C2, which is the time when the displacement value no longer increases on curve C2 and the slope of the curve changes from a non-zero positive value to zero, which is the time when engagement ends. The engagement end time and the engagement start time are differentiated to obtain the engagement response time of the differential lock operating mechanism.
Similarly, the time for starting the gas cut-off of the cylinder 101 can be obtained through the curve C1, which is embodied as the time for the pressure value on the curve C1 to drop from the highest point, and the time is the time for starting the gas cut-off; the time at which the moving toothed sleeve 21 is just completely disengaged from the fixed toothed sleeve 22 can be obtained by means of the curve C2, which is represented by the time at which the displacement value on the curve C2 no longer decreases and the slope of the curve changes from a non-zero negative value to zero, which is the disengagement termination time. The engagement response time of the differential lock operating mechanism can be obtained by subtracting the disengagement termination time and the disengagement start time.
In the axial stiffness test, a P-S curve is obtained when the air pressure (denoted as P) in the compression chamber 1013 is measured by the pressure sensor 5 and the displacement (denoted as S) of the piston 1012 is measured by the displacement sensor 6. The following can be obtained by the P-S curve: when the air pressure in the compression chamber 1013 is the standard pressure P, the displacement of the corresponding piston 1012 is S1; when the gas pressure in the compression chamber 1013 is decreased from P to 0.3P, the displacement of the corresponding piston 1012 is S2. At this time, the ratio of the amount of change in P to the amount of change in S is the axial stiffness value (denoted by K) of the differential lock operating mechanism, that is:
in a whole view, the present embodiment realizes measurement of all parameters required for experiments by providing one pressure sensor 5 and one displacement sensor 6, and is excellent in economical efficiency.
Next, the detailed configuration of the device for testing the overall performance of the differential lock operating mechanism will be described.
Alternatively, as shown in fig. 1, the air supply mechanism 1 includes an air source 11 and an air servo valve 12, and an air outlet end of the air source 11 is communicated with the compression chamber 1013 through the air servo valve 12. In this embodiment, the air source 11 provides compressed air; the air servo valve 12 is used to control the supply of air and to perform the operation of discharging the high-pressure air in the cylinder 101, etc., in accordance with the requirements of the test program. Specifically, the air source 11 may be a compressor or an air tank as long as compressed air can be supplied.
As shown in fig. 1, in the present embodiment, the pressure sensor 5 is provided in a pipe connecting the air servo valve 12 and the compression chamber 1013. Further, a displacement sensor 6 is installed on the cylinder 101, and a sensing end of the displacement sensor 6 extends into the compression chamber 1013 and is disposed toward the piston 1012 to measure the displacement of the piston 1012.
Alternatively, the rotary drive mechanism 3 includes a bearing housing 31, a rotary shaft 32, and a half shaft 34, the rotary shaft 32 being mounted on the bearing housing 31. A first end of the axle shaft 34 is provided with a flange 341 and a second end of the axle shaft 34 is provided with splines. One end of the rotating shaft 32 is in transmission connection with the half shaft 34 through a flange 341, the half shaft 34 is in sliding transmission connection with the movable gear sleeve 21 through a spline, and the half shaft 34 and the movable gear sleeve 21 are coaxially arranged. According to the arrangement, when the half shaft 34 is rotated, the half shaft 34 can drive the movable gear sleeve 21 to rotate; at the same time, the moving sleeve 21 can be made to slide along the half-shaft 34, making the moving sleeve 21 closer to or farther from the fixed sleeve 22.
In this embodiment, the shaft 32 is connected to the flange 341 through the transition piece 33. Transition piece 33 is integrally split in half and includes coaxially disposed and abutting coupling halves 331 and flange 332. Wherein, the half coupling 331 is provided with a mounting hole along the axial direction, and one end of the rotating shaft 32 connected with the half shaft 34 is arranged in the mounting hole in a penetrating way. The flange 332 is abutted against the flange 341, and a receiving groove is further formed on the side of the flange 332 facing the flange 341 to receive the protruding portion of the flange 341.
Optionally, the movable gear sleeve 21 is provided with a ring groove along the circumferential direction. One end of the shifting fork 104 is connected with one side of the piston 1012 departing from the compression chamber 1013, and the other end of the shifting fork 104 is sleeved on the ring groove and is in clearance fit with the bottom wall of the ring groove. According to the arrangement, the shifting fork 104 can drive the shifting gear sleeve 21 to move along the transmission shaft, and the shifting fork 104 can be ensured to relatively shift the gear sleeve 21 to rotate.
Optionally, the moving mechanism 4 comprises a fixed seat 41 and a moving sleeve 42. A fixed seat thread through hole is formed in the fixed seat 41 along the axial direction of the movable gear sleeve 21, the fixed seat 41 is sleeved outside the half shaft 34 through the fixed seat thread through hole at intervals, the movable sleeve 42 is also sleeved outside the half shaft 34 at intervals, the first end of the movable sleeve 42 is connected in the fixed seat thread through hole in a threaded mode, and the second end of the movable sleeve 42 is detachably connected with the movable gear sleeve 21. At this time, the movable sleeve 42 is rotated to drive the movable gear sleeve 21 to move along the self axial direction, so that the movable gear sleeve 21 reaches a preset position; further, stopping the rotation of the traveling sleeve 42 fixes the traveling sleeve 42 at a predetermined position.
In addition, as can be seen from fig. 1, the movable sleeve 42 is sleeved outside the half shaft 34 at intervals, so that the floor area of the test device can be reduced, and the overall structure is very compact. Meanwhile, because the existence of the half shaft 34 does not hinder the rotation of the movable sleeve 42, the half shaft 34 does not need to be disassembled when the air tightness test is carried out, and the disassembling operation in the test process is reduced.
Specifically, the fixing base 41 includes a bracket 411 and a fixing sleeve 412. Wherein, support 411 and ground fixed constraint, fixed sleeve 412 is installed on support 411, and fixing base screw thread through-hole opens promptly and establishes in fixed sleeve 412. It can be understood that the height of the bracket 411 can be adjusted according to actual requirements, and it is sufficient to ensure that the fixed sleeve 412 is coaxial with the movable gear sleeve 21.
As shown in fig. 2, for the movable sleeve 42, from the first end to the second end thereof, the movable sleeve 42 includes a guide sleeve 421, an intermediate sleeve 422 and a connection sleeve 423 which are coaxially arranged and connected in sequence. The guiding sleeve 421 is connected to the fixing base 41. In this embodiment, the guiding sleeve 421 is screwed into the through hole of the fixing seat. When the guiding sleeve 421 rotates, the moving sleeve 42 is driven to move along the axial direction of the moving sleeve 42 as a whole. In this embodiment, the guiding sleeve 421 is connected to the fixing seat 41 by a trapezoidal thread, so as to ensure that the guiding sleeve 421 and the fixing seat 41 have small resistance and operate smoothly when transmitting the axial force therebetween.
Further, one end of the intermediate sleeve 422 is positioned with the guiding sleeve 421 through the seam allowance and fixed by a fastener (which may be a screw) to ensure that the intermediate sleeve 422 and the guiding sleeve 421 are coaxial. Meanwhile, the second end of the intermediate sleeve 422 is rotatably connected to the first end of the connection sleeve 423, and the second end of the connection sleeve 423 is detachably connected to the movable gear sleeve 21. Therefore, the rotation guide sleeve 421 and the intermediate sleeve 422 can be fixed to rotate together and simultaneously, the connecting sleeve 423 can not rotate relative to the intermediate sleeve 422, and finally the connecting sleeve 423 can only drive the movable gear sleeve 21 to move along the self axial direction without causing the connecting sleeve 423 to rotate around the circumferential direction of the movable gear sleeve 21 or driving the movable gear sleeve 21 to rotate, so that the connection reliability of the connecting sleeve 423 and the movable gear sleeve 21 is ensured.
Optionally, the second end of the intermediate sleeve 422 is rotatably connected to the first end of the connecting sleeve 423 by a thrust bearing 43 to reduce friction when the intermediate sleeve 422 rotates relative to the connecting sleeve 423, so that the rotation of the intermediate sleeve 422 is smoother. Further, as shown in fig. 2, the inner wall of the second end of the intermediate sleeve 422 is in clearance fit with the outer wall of the first end of the connecting sleeve 423 to ensure that the intermediate sleeve 422 and the connecting sleeve 423 can move relative to each other during installation and testing, and cannot deflect due to an excessive clearance.
In a specific structure, as shown in fig. 2, a first circular ring 4221 is arranged at the second end of the intermediate sleeve 422 along the circumferential direction, and the first circular ring 4221 is sleeved outside the connecting sleeve 423; at a first end of the connecting sleeve 423, a second ring 4231 is circumferentially arranged, the second ring 4231 being nested within the intermediate sleeve 422. In the axial direction of the connecting sleeve 423 or the intermediate sleeve 422, a mounting space is formed between the first ring 4221 and the second ring 4231, and the thrust bearing 43 is mounted in the mounting space.
Further, in consideration of the fact that there is a gap between the fork 104 and the two side walls of the ring groove, as in the practical case, in this embodiment, two insertion portions 4232 are disposed at the second end of the connecting sleeve 423. The second end of the connecting sleeve 423 can be connected with the gap by two plugging portions 4232 to realize the detachable connection between the connecting sleeve 423 and the movable gear sleeve 21, so that the connecting sleeve 423 can drive the movable gear sleeve 21 to move. Meanwhile, the matching and stress relation among all parts in the differential lock operating mechanism is also kept through the arrangement.
Optionally, a handle 44 is also provided in the moving mechanism 4. In this embodiment, the handle 44 is fixed outside the middle sleeve 422, and the movable sleeve 42 can be rotated by rotating the handle 44, so that the use is very convenient. Further, a plurality of handles 44 may be disposed along the circumferential direction of the movable sleeve 42 according to actual requirements, and will not be described herein.
Optionally, as shown in fig. 1, a measurement and control and electrical mechanism 7 is further provided in the device for testing the comprehensive performance of the differential lock operating mechanism. Specifically, the measurement and control and electrical mechanism 7 includes a power distribution cabinet, a data acquisition card, a PLC controller, and the like. Wherein, the switch board is connected with spare parts that need the power consumption such as air servo valve 12 to supply power. The data acquisition card is simultaneously connected with the pressure sensor 5, the displacement sensor 6 and the PLC. The data measured by the pressure sensor 5 and the displacement sensor 6 can be transmitted to a data acquisition card, and the PLC controller controls the operation of the air servo valve 12 and the like according to the acquired data.
In summary, the present embodiment provides a device for testing the comprehensive performance of a differential lock operating mechanism, by which the cylinder sealing performance, the response time, the axial stiffness, and the like of the differential lock operating mechanism can be tested, so as to obtain the comprehensive performance of the differential lock operating mechanism. On the whole, the comprehensive performance test device for the differential lock control mechanism is compact in structure, does not need to carry out a whole vehicle test, is low in test cost and short in test period, and has good economical efficiency.
Example two
The present embodiment provides a device for testing the comprehensive performance of a differential lock operating mechanism, which has substantially the same structure as the device for testing the comprehensive performance of a differential lock operating mechanism provided in the first embodiment, except for the difference in the arrangement of the moving mechanism 4.
As shown in fig. 3 and 4, the moving mechanism 4 includes a fixed seat 41 and a moving sleeve 42. The fixing seat 41 is provided with a smooth through hole along the axial direction of the movable gear sleeve 21, the fixing seat 41 is sleeved outside the half shaft 34 through the smooth through hole at intervals, the movable sleeve 42 is sleeved outside the half shaft 34 at intervals, the first end of the movable sleeve 42 is slidably connected in the smooth through hole, and the second end of the movable sleeve 42 is detachably connected with the movable gear sleeve 21.
As in the first embodiment, the shifting sleeve 42 also includes, from the first end to the second end of the shifting sleeve 42, a guiding sleeve 421, an intermediate sleeve 422 and a connecting sleeve 423, which are coaxially arranged and connected in sequence. However, in a slight difference from the embodiment, the guide sleeve 421 is slidably connected in the smooth through hole in the present embodiment. The connection structure between the guide sleeve 421 and the intermediate sleeve 422, the connection structure between the intermediate sleeve 422 and the connection sleeve 423, and the connection structure between the connection sleeve 423 and the movable gear sleeve 21 are the same as those in the first embodiment, and are not described again here.
The moving mechanism 4 further comprises an electric driving assembly 45, the electric driving assembly 45 comprises a driving motor 451, a synchronous belt 452, a driving wheel 453 and a driven wheel 454, two ends of the synchronous belt 452 are respectively sleeved on the driving wheel 453 and the driven wheel 454, the driving motor 451 is in transmission connection with the driving wheel 453 to drive the driving wheel 453 to rotate, a driven wheel threaded through hole is further axially arranged on the driven wheel 454, the driven wheel 454 is in threaded connection with the outside of the moving sleeve 42 through the driven wheel threaded through hole, and the driven wheel 454 is located between two ends of the moving sleeve 42.
With the above arrangement, when the driving motor 451 operates, it can drive the driving wheel 453 to rotate, and further drive the driven wheel 454 to rotate through the timing belt 452. When the driven wheel 454 rotates, since the position of the driven wheel 454 in the axial direction of the movable gear sleeve 21 is relatively fixed, and the driven wheel 454 is in threaded connection with the movable sleeve 42, the driven wheel 454 can drive the movable sleeve 42 to rotate, and the movable sleeve 42 moves along the axial direction of the movable gear sleeve 21, so that the movable gear sleeve 21 is moved to a preset position through the movable sleeve 42. When the motor is stopped immediately after the movable gear sleeve 21 reaches the preset position, the movable gear sleeve 21 can be fixed at the preset position.
In this embodiment, driven wheel 454 is threadably coupled to intermediate sleeve 422 via a driven wheel threaded through-hole.
Preferably, the driving motor 451 is provided as a servo motor, the timing belt 452 is provided as a toothed belt, and the driving wheel 453 and the driven wheel 454 are provided as toothed belt wheels, so that the overall operation is highly accurate, the operation is stable, and the response is timely, the movement of the movable gear sleeve 21 can be more accurately adjusted, and the movable gear sleeve 21 can be rapidly fixed at a preset position. Since the structures of the servo motor, the toothed belt and the toothed belt wheel are all the prior art, the description is omitted.
The above description is only a preferred embodiment of the present invention, and for those skilled in the art, the present invention should not be limited by the description of the present invention, which should be interpreted as a limitation.
Claims (7)
1. The utility model provides a differential lock operating mechanism comprehensive properties test device for the comprehensive properties of the differential lock operating mechanism (100) that awaits measuring, the differential lock operating mechanism (100) that awaits measuring includes cylinder (101) and shift fork (104), cylinder (101) include cylinder body (1011) and piston (1012), piston (1012) with cylinder body (1011) cooperation forms compression chamber (1013), its characterized in that, differential lock operating mechanism comprehensive properties test device includes:
the gas outlet end of the gas supply mechanism (1) is communicated with the compression chamber (1013) to supply gas into the compression chamber (1013);
the differential lock gear sleeve (2) comprises a movable gear sleeve (21) and a fixed gear sleeve (22) which are coaxially and oppositely arranged, a piston (1012) is in transmission connection with the movable gear sleeve (21) through a shifting fork (104) so as to drive the movable gear sleeve (21) to move relative to the fixed gear sleeve (22) along the self axial direction, so that the movable gear sleeve (21) and the fixed gear sleeve (22) are mutually meshed or separated, a ring groove is formed in the movable gear sleeve (21) along the circumferential direction, one end of the shifting fork (104) is connected with one side of the piston (1012) departing from the compression chamber (1013), and the other end of the shifting fork (104) is sleeved on the ring groove and is in clearance fit with the bottom wall of the ring groove;
the rotary driving mechanism (3) is in transmission connection with the movable gear sleeve (21), the rotary driving mechanism (3) is used for driving the movable gear sleeve (21) to rotate, the rotary driving mechanism (3) comprises a bearing seat (31), a rotating shaft (32) and a half shaft (34), the rotating shaft (32) is installed on the bearing seat (31), a flange plate (341) is arranged at the first end of the half shaft (34), a spline is arranged at the second end of the half shaft (34), one end of the rotating shaft (32) is in transmission connection with the half shaft (34) through the flange plate (341), the half shaft (34) is in sliding transmission connection with the movable gear sleeve (21) through the spline, and the half shaft (34) and the movable gear sleeve (21) are coaxially arranged;
the moving mechanism (4) is detachably connected with the moving gear sleeve (21), and the moving mechanism (4) is used for moving the moving gear sleeve (21) to a preset position along the axial direction of the moving gear sleeve and keeping the moving gear sleeve (21) still;
a pressure sensor (5) and a displacement sensor (6), said pressure sensor (5) and said displacement sensor (6) being connected to said cylinder (101), respectively, said pressure sensor (5) being adapted to measure the gas pressure in said compression chamber (1013), said displacement sensor (6) being adapted to measure the displacement of said piston (1012).
2. The device for testing the comprehensive performance of the differential lock operating mechanism according to claim 1, wherein the air supply mechanism (1) comprises an air source (11) and an air servo valve (12), and an air outlet end of the air source (11) is communicated with the compression chamber (1013) through the air servo valve (12).
3. The device for testing the comprehensive performance of the differential lock operating mechanism according to claim 1, wherein the moving mechanism (4) comprises a fixed seat (41) and a moving sleeve (42);
follow on fixing base (41) the axial of removing tooth cover (21) is provided with fixing base screw thread through-hole, fixing base (41) are passed through fixing base screw thread through-hole interval cover is established the outside of semi-axis (34), it establishes also to separate the cover in to remove sleeve (42) the outside of semi-axis (34), just the first end threaded connection that removes sleeve (42) is in the fixing base screw thread through-hole, the second end of removing sleeve (42) with remove tooth cover (21) and can dismantle the connection.
4. The device for testing the comprehensive performance of the differential lock operating mechanism according to claim 1, wherein the moving mechanism (4) comprises a fixed seat (41) and a moving sleeve (42), a smooth through hole is formed in the fixed seat (41) along the axial direction of the moving gear sleeve (21), the fixed seat (41) is sleeved outside the half shaft (34) at intervals through the smooth through hole, the moving sleeve (42) is sleeved outside the half shaft (34) at intervals, the first end of the moving sleeve (42) is slidably connected in the smooth through hole, and the second end of the moving sleeve (42) is detachably connected with the moving gear sleeve (21);
the moving mechanism (4) further comprises an electric driving assembly (45), the electric driving assembly (45) comprises a driving motor (451), a synchronous belt (452), a driving wheel (453) and a driven wheel (454), two ends of the synchronous belt (452) are respectively sleeved on the driving wheel (453) and the driven wheel (454), the driving motor (451) is in transmission connection with the driving wheel (453) to drive the driving wheel (453) to rotate, a driven wheel threaded through hole is further axially arranged on the driven wheel (454), the driven wheel (454) is in threaded connection outside the moving sleeve (42) through the driven wheel threaded through hole, and the driven wheel (454) is located between two ends of the moving sleeve (42).
5. A test device for the comprehensive performance of a differential lock operating mechanism as claimed in claim 4, wherein the driving motor (451) is provided as a servo motor, the timing belt (452) is provided as a toothed belt, and the driving pulley (453) and the driven pulley (454) are provided as toothed pulleys.
6. A differential lock operating mechanism comprehensive performance test device according to any one of claims 3-5, characterized in that, from the first end of the movable sleeve (42) to the second end of the movable sleeve (42), the movable sleeve (42) comprises a guide sleeve (421), an intermediate sleeve (422) and a connecting sleeve (423) which are coaxially arranged and connected in sequence;
the guide sleeve (421) is connected with the fixed seat (41), the first end of the middle sleeve (422) is positioned with the guide sleeve (421) through a spigot and fixed through a fastener, the second end of the middle sleeve (422) is rotatably connected with the first end of the connecting sleeve (423), and the second end of the connecting sleeve (423) is detachably connected with the movable gear sleeve (21).
7. A differential lock operating mechanism combination property test device according to claim 6, characterized in that the moving mechanism (4) further comprises a thrust bearing (43), and the second end of the intermediate sleeve (422) is rotationally connected with the first end of the connecting sleeve (423) through the thrust bearing (43).
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201078748Y (en) * | 2007-05-11 | 2008-06-25 | 李延平 | Dynamic state load test device of overrun clutch |
| CN205808706U (en) * | 2016-06-22 | 2016-12-14 | 南通信达诺测控技术有限公司 | A kind of assay device of the parking shift fork in automatic gearshift automobile vehicle gearbox |
| CN110907199A (en) * | 2019-12-31 | 2020-03-24 | 一汽解放汽车有限公司 | Impact durability test bed and bench test method for differential lock between wheels of drive axle |
| CN210603934U (en) * | 2019-10-29 | 2020-05-22 | 一汽解放汽车有限公司 | Static torsion test device for differential lock |
Family Cites Families (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6389888B1 (en) * | 1998-06-29 | 2002-05-21 | Veri-Tek Inc. | Isolation and loading arrangement for differential gear system under test |
| DE19950171B4 (en) * | 1999-10-19 | 2004-02-05 | Daimlerchrysler Ag | Pneumatically operated differential lock of a motor vehicle |
| JP4591663B2 (en) * | 2004-06-30 | 2010-12-01 | トヨタ自動車株式会社 | Side shim selection method and side shim selection device for differential carrier assembly |
| CN200960856Y (en) * | 2006-10-24 | 2007-10-17 | 青特集团有限公司 | Differential speed lock between wheels for STR axle |
| CN101118005B (en) * | 2007-09-18 | 2010-10-13 | 洪涛 | Basic mode jaw self locking speed differential gear |
| DE102010022119A1 (en) * | 2010-05-20 | 2012-03-01 | Mahle International Gmbh | Differential pressure measuring device and pollution degree monitoring device and filter device |
| IT1403794B1 (en) * | 2011-01-12 | 2013-10-31 | Vhit Spa | DIFFERENTIAL MASTER CYLINDER, BRAKING SYSTEM INCLUDING THE CYLINDER AND METHOD FOR COMMANDING A CYLINDER UTILIZATION DEVICE |
| CN203083816U (en) * | 2013-01-22 | 2013-07-24 | 杭州沃镭科技有限公司 | Device for testing performance of automobile brake master cylinder |
| CN103308307B (en) * | 2013-06-25 | 2016-04-13 | 吉林大学 | Differential speed type power distributor dynamic performance is test bed |
| US20160169360A1 (en) * | 2014-12-03 | 2016-06-16 | Musashi Seimitsu Industry Co., Ltd. | Differential device |
| US9632012B2 (en) * | 2015-07-01 | 2017-04-25 | GM Global Technology Operations LLC | Vehicle differential housing and method of NVH testing |
| JP2017125580A (en) * | 2016-01-14 | 2017-07-20 | トヨタ自動車株式会社 | Differential gear |
| CN105841975B (en) * | 2016-04-29 | 2018-05-08 | 中国第一汽车股份有限公司 | A kind of pneumatic type mechanical differential lock function bench test device |
| JP6648652B2 (en) * | 2016-08-11 | 2020-02-14 | トヨタ自動車株式会社 | Clutch system |
| CN107132053B (en) * | 2017-05-05 | 2019-02-12 | 山东大学 | One kind realizing on-line tuning detection method to differential lock heavy axle shaft |
| CN206695989U (en) * | 2017-05-19 | 2017-12-01 | 远安永安车桥有限责任公司 | Differential lock detection means |
| US10920866B2 (en) * | 2018-06-04 | 2021-02-16 | American Axle & Manufacturing, Inc. | Vehicle driveline component with latching actuator |
| CN209689915U (en) * | 2019-01-28 | 2019-11-26 | 贵阳力科液压技术有限公司 | A kind of gearbox delivery test platform |
-
2021
- 2021-02-26 CN CN202110219704.8A patent/CN113008480B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201078748Y (en) * | 2007-05-11 | 2008-06-25 | 李延平 | Dynamic state load test device of overrun clutch |
| CN205808706U (en) * | 2016-06-22 | 2016-12-14 | 南通信达诺测控技术有限公司 | A kind of assay device of the parking shift fork in automatic gearshift automobile vehicle gearbox |
| CN210603934U (en) * | 2019-10-29 | 2020-05-22 | 一汽解放汽车有限公司 | Static torsion test device for differential lock |
| CN110907199A (en) * | 2019-12-31 | 2020-03-24 | 一汽解放汽车有限公司 | Impact durability test bed and bench test method for differential lock between wheels of drive axle |
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