Hydraulic-mechanical continuously variable transmission test device and test method thereof

Abstract

The application discloses a machine-fluid hybrid continuously variable transmission testing device and a testing method thereof. The testing device is mainly composed of a box body, a machine-fluid hybrid transmission part, an oil supplement pump station, a power input part, a servo control device, a load driving part and a control system. The testing method comprises zero load basic parameter testing, inertia load acceleration and deceleration dynamic characteristic testing, constant power output dynamic characteristic testing, constant speed output dynamic characteristic testing and constant torque output dynamic characteristic testing. The control system controls the oil supplement pump station, the power input part, the servo control device and the load driving part to perform various tests and collect relevant data, so that the oil stirring resistance moment, the transmission efficiency and the dynamic characteristics under various working conditions are finally obtained.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of mechanical-hydraulic hybrid transmission, and in particular to a device and a method for testing a mechanical-hydraulic hybrid continuously variable transmission. BACKGROUND

[0002] The cylinder-opposed radial flow mechanical-hydraulic hybrid continuously variable transmission has the advantages of high transmission efficiency, small size, high integration, good controllability, etc., and integrates pure mechanical transmission, mechanical-hydraulic parallel flow real-time synchronous transmission, can reduce transmission, constant speed transmission, and can also increase transmission. However, due to its high integration characteristics, its transmission characteristics cannot be comprehensively and effectively tested, and there are mainly the following problems: 1. The built-in closed hydraulic circuit is integrated and has no open port, so it cannot be externally tested, and it is impossible to detect the volumetric efficiency under different working conditions, which leads to the fact that the mechanical efficiency of the transmission device cannot be obtained, and there is no test data as a basis, which ultimately leads to the fact that design improvement cannot be carried out; 2. Different lubrication oil invasion depths during the transmission process of the mechanical-hydraulic hybrid continuously variable transmission will bring different oil stirring resistance torques, and improper control will bring large power loss, so it is necessary to detect the minimum oil stirring resistance torque under the condition of meeting the lubrication effect, and there is currently no corresponding device and effective detection method; 3. Under the conditions of inertial load or controllable load, there is no effective control and testing scheme for the driving of the mechanical-hydraulic hybrid continuously variable transmission. At present, a testing device and a corresponding testing method are urgently needed to solve the above problems. SUMMARY

[0003] The technical problem solved by the present application is to provide a mechanical-hydraulic hybrid continuously variable transmission testing device and a testing method thereof to solve the problems in the background.

[0004] The technical problem solved by the present application is solved by adopting the following technical solutions:

[0005] The mechanical-hydraulic hybrid continuously variable transmission testing device mainly comprises a box, a mechanical-hydraulic hybrid transmission part, an oil supplement pump station, a power input part, a servo control device, a load driving part and a control system. The mechanical-hydraulic hybrid transmission part is arranged in the box, the servo control device is arranged on the box, the oil supplement pump station supplements the leaked hydraulic oil of the mechanical-hydraulic hybrid transmission part through a pipeline, the leaked oil of the mechanical-hydraulic hybrid transmission part flows through the box and then returns to the oil tank of the oil supplement pump station through a pipeline, the power input part drives the mechanical-hydraulic hybrid transmission part to output power, the servo control device controls the output speed of the mechanical-hydraulic hybrid transmission part, the power output by the mechanical-hydraulic hybrid transmission part drives the load driving part, and the control system feedback controls the power input part and the servo control device according to the collected data of the power input part and the load driving part, so as to obtain different transmission effects.

[0006] In the application, the box is mainly composed of a left end plate, a right end plate, a bottom plate, a cover plate, a servo side plate, an oil discharging side plate, a lifting screw, and a box pin shaft. The left end plate, the right end plate, the bottom plate, the cover plate, the servo side plate, and the oil discharging side plate are cuboids. The servo side plate and the oil discharging side plate are arranged in parallel and opposite to each other and fastened perpendicularly on the bottom plate. The left end plate and the right end plate are arranged in parallel and opposite to each other and fastened perpendicularly on the bottom plate. The left end plate is in contact with one end of the servo side plate and the oil discharging side plate respectively and is fastened by the box pin shaft. The right end plate is in contact with the other end of the servo side plate and the oil discharging side plate respectively and is fastened by the box pin shaft. The left end plate, the right end plate, the servo side plate, and the oil discharging side plate have the same height. The cover plate is fastened on the upper plane formed by the left end plate, the right end plate, the servo side plate, and the oil discharging side plate. The left end plate, the right end plate, the servo side plate, the oil discharging side plate, and the cover plate form an internal cavity. The hydraulic-mechanical transmission part is arranged in the internal cavity. The lifting screw passes through the cover plate and is arranged on the left end plate and the right end plate respectively. The screws arranged in the side holes of the bottom plate are screwed into the servo bottom plate screw holes and the oil discharging bottom plate screw holes respectively and are fastened. The screws arranged in the end holes of the bottom plate are screwed into the left bottom plate screw holes and the right bottom plate screw holes respectively and are fastened. The cover plate is arranged at the upper end of the box. The screws pass through the cover plate screw holes and are screwed into the left cover plate screw holes, the right cover plate screw holes, the servo cover plate screw holes, and the oil discharging cover plate screw holes respectively and are fastened. The connecting thread part of the lifting screw passes through the cover plate lifting hole and is screwed into the left lifting screw hole and the right lifting screw hole respectively. After the box is assembled, the left bearing cavity and the right large bearing cavity are coaxial. The box with a plate type distribution is convenient for disassembly and assembly and can eliminate the cumulative error of machining through assembly.

[0007] In the application, the machine-oil hybrid transmission part is mainly composed of a motor swash bracket, a motor eccentric bracket, a bracket pin shaft, a bearing check ring, a motor ball socket tray, a motor cylinder, a motor eccentric ring, a pump cylinder, a drive gear, a drive spindle, a drive housing, a pump ball socket tray, a pump plunger, a pump flow distribution valve, a pump eccentric ring, a flow distribution cylinder, a motor flow distribution valve, a motor plunger and a motor swash plate. One end of the flow distribution cylinder is tightly connected with the pump cylinder, and the other end is tightly connected with the motor cylinder. The flow distribution cylinder, the motor cylinder and the pump cylinder are coaxially fixed on the drive spindle. The pump plunger is axially arranged in the plunger hole of the pump cylinder. The motor plunger is axially arranged in the plunger hole of the motor cylinder. Two rows of valve holes are radially arranged on the flow distribution cylinder. The pump flow distribution valve is arranged in the valve hole close to the pump cylinder. The motor flow distribution valve is arranged in the valve hole close to the motor cylinder. The motor swash bracket and the motor eccentric bracket are assembled by limiting with a pin and then fastened by a screw. The motor swash plate is rotatably arranged on the motor swash bracket. The motor swash plate is matched with the motor swash bracket through spherical surface contact. The motor swash plate is limited by contact with the upper and lower circular arc structures of the motor eccentric bracket. The center line of the upper and lower circular arcs passes through the center of the contact spherical surface of the motor swash plate and the motor swash bracket, so as to limit the relative position of the motor swash plate relative to the motor swash bracket and the motor eccentric bracket, and then the motor swash plate can only rotate around the center line of the upper and lower circular arcs. The motor ball socket tray is arranged in the motor swash plate through a bearing. The bearing check ring is sleeved on the drive spindle and is limited by the check ring arranged on the drive spindle. The bearing check ring is arranged on the motor swash bracket through a bearing. The bearing boss of the bearing check ring and the bearing boss of the motor swash bracket are located on both sides of the bearing. The motor cylinder is arranged on the motor eccentric bracket through a bearing. The ball head of the motor plunger is in contact with the ball socket of the motor ball socket tray. The motor eccentric bracket is provided with a cavity eccentric to the rotation axis of the motor cylinder. The motor eccentric ring is arranged in the cavity. The axial position of the motor eccentric ring is located at the axial position of the motor flow distribution valve. One end of the drive housing is arranged on the pump cylinder through a bearing. The other end of the drive housing is arranged on the drive spindle through a bearing. The bearing is limited by the check ring arranged on the drive spindle. The pump ball socket tray is arranged in the drive housing through a bearing. The rotation axis of the pump ball socket tray is at an angle with the rotation axis of the drive spindle. The ball head of the pump plunger is in contact with the ball socket of the pump ball socket tray. The drive housing is provided with a cavity eccentric to the rotation axis of the pump cylinder. The pump eccentric ring is arranged in the cavity. The axial position of the pump eccentric ring is located at the axial position of the pump flow distribution valve. The drive housing is provided with a drive gear. The drive housing and the drive gear are limited and driven by a pin shaft and then fastened by a screw.The driving shell is rotatably arranged on the right end plate through a bearing in the right large bearing cavity, the driving spindle is rotatably arranged on the right end plate through a bearing in the right small bearing cavity, the motor swash plate support is positioned on the left end plate through the left bearing cavity and is limited in circumferential rotation through the support pin shaft, and the motor swash plate support and the left end plate are fastened through the screws arranged in the left support mounting hole.

[0008] In the application, the oil supplement pump station comprises an oil supplement joint, a pipe joint, a flow meter and a pressure sensor, the oil supplement joint is rotatably and tightly arranged on the right end plate, the pipe joint on the oil supplement pump station is connected with the oil supplement joint, and then the pressure oil of the oil supplement pump station is delivered to the inner cavity of the driving spindle through the pressure sensor and the flow meter, and the output pressure oil of the oil supplement pump station is a constant pressure oil source.

[0009] The power input part comprises a driving gear, a driving shaft, a power motor, a shaft coupling and an input torque and speed sensor, the driving shaft is rotatably arranged on the right end plate through a bearing, an oil seal is arranged between the driving shaft and the right end plate, one end of the driving shaft is provided with the driving gear, the driving shaft transmits power through the driving gear, the driving gear is engaged with the driving gear to drive, the other end of the driving shaft is connected with one end of the input torque and speed sensor through the shaft coupling to drive, and the other end of the input torque and speed sensor is connected with the power motor through the shaft coupling to drive.

[0010] In the application, the servo control device comprises an optical encoder, an encoder support, a servo sub-shaft, a sub-bevel gear, a servo main shaft, a main-bevel gear, a servo nut, a servo carrier, an outer ring positioning pin, a servo sun gear, a servo motor, a servo planetary gear, a servo outer ring, the servo sub-shaft is arranged on the servo side plate through a bearing, the bearing is located in the sub-shaft cavity, an oil seal is arranged between the servo sub-shaft and the servo side plate, a manual control mechanism is arranged at one end of the servo sub-shaft, the optical encoder is fixedly arranged on the servo side plate through the encoder support, the shaft of the optical encoder is connected with the servo sub-shaft, a sub-bevel gear is arranged at the other end of the servo sub-shaft, the relative position of the sub-bevel gear on the servo sub-shaft can be adjusted, one end of the servo main shaft is arranged on the motor eccentric support through a bearing, the other end of the servo main shaft is arranged on the motor swash plate support through a bearing, the servo nut is movably arranged on the servo main shaft between the two bearings, the servo nut is connected with the rocker arm on the motor swash plate for transmission, a main-bevel gear is arranged at one end of the servo main shaft, the axial position of the main-bevel gear on the servo main shaft is adjusted by changing the thickness of the stop washer, a servo carrier is arranged at the other end of the servo main shaft, an oil seal is arranged between the servo main shaft and the motor swash plate support, an outer ring positioning pin is arranged in the servo variable speed cavity, and the outer ring positioning pin is arranged in the limiting pin slot of the servo variable speed cavity to limit the circumferential rotation of the servo outer ring, a servo planetary gear is arranged on the servo carrier, the servo motor is arranged on the left end plate and is fastened through the screw arranged in the motor screw hole, the rotation center of the driving shaft of the servo motor and the rotation center of the servo main shaft are coaxially arranged, a servo sun gear is arranged on the driving shaft of the servo motor, the servo motor drives the servo planetary gear to drive the servo carrier to rotate through the servo sun gear, and the servo main shaft is driven to rotate, the rotating servo main shaft drives the servo nut to move, the moving servo nut drives the motor swash plate to rotate, the servo main shaft drives the main-bevel gear to drive the sub-bevel gear and then drives the servo sub-shaft to rotate, and the rotation amount of the servo sub-shaft is collected by the optical encoder and then fed back to the control system, so that the inclination angle of the motor swash plate is obtained; after the servo motor is powered off, the servo sub-shaft can be manually operated to drive the servo main shaft to rotate through the sub-bevel gear and the main-bevel gear, and then the servo nut is driven to move.

[0011] In the application, the load driving part comprises a main flange, a transmission pin, a slave flange, an output torque and speed sensor, and a load device, one end of the main flange is connected with the driving main shaft for transmission, the other end of the main flange is connected with one end of the slave flange for transmission, a transmission pin is arranged between the main flange and the slave flange, the transmission pin is cut off when the transmission is overloaded, so as to prevent the transmission device from being damaged, the other end of the slave flange is connected with one end of the output torque and speed sensor for transmission, and the other end of the output torque and speed sensor is connected with the load device for transmission.

[0012] In the present application, the oil supplement pump station supplies oil to the inner cavity of the driving main shaft of the machine-oil hybrid transmission part. Part of the oil enters the motor cylinder, pump cylinder body and flow distribution cylinder body to compensate for internal leakage. Another part of the oil flows out through the flow channel provided on the driving main shaft to flush each mechanism of the machine-oil hybrid transmission part. The flushed oil and the oil after internal leakage flow through the tank body, and then flow back to the oil supplement pump station through the oil discharge hole and the oil return pipeline. The oil return pipeline is connected to different oil discharge holes to obtain different oil storage heights in the tank body.

[0013] In the application, the power motor drives the driving gear through the input torque speed sensor, the driving shaft and the driving gear, and then drives the driving shell to rotate; when the support ball socket end surface of the motor ball socket tray is perpendicular to the rotation axis of the driving main shaft controlled by the motor swash plate, the state is recorded as zero position, the power of the driving shell drives the pump plunger through the pump ball socket tray, and then drives the pump cylinder body to rotate, the power of the pump cylinder body is directly output by the pure mechanical transmission of the driving main shaft, at this time, the pump plunger, the motor plunger, the motor ball socket tray, the pump flow distribution valve and the motor flow distribution valve move circumferentially with the pump cylinder body, the motor cylinder and the flow distribution cylinder body, at this time, the pump plunger and the motor plunger have no axial movement, the pump flow distribution valve has no radial movement, and the motor flow distribution valve simultaneously moves radially under the action of the motor eccentric ring, and oil is distributed to the plunger hole where the motor plunger is located which alternately enters the high pressure oil area, when the support ball socket end surface is perpendicular to the axis, the pure mechanical transmission is constant speed transmission, in the actual transmission process, affected by internal leakage, especially when the load is large, the pure mechanical transmission of the zero position state is non-full constant speed transmission, and speed difference is generated due to leakage, in order to compensate for internal leakage, the support ball socket end surface of the motor ball socket tray and the rotation axis of the driving main shaft are in a certain angle state of self-adaptive leakage compensation; when the support ball socket end surface of the motor ball socket tray and the rotation axis of the driving main shaft are in a positive angle state controlled by the motor swash plate, the power of the driving shell drives the pump plunger through the pump ball socket tray, and then drives the pump cylinder body to rotate, at the same time, the pump ball socket tray drives the pump plunger to move axially, the driving shell and the pump eccentric ring generate circumferential relative motion with the pump cylinder body, under the action of the pump eccentric ring, the pump flow distribution valve moves radially while moving circumferentially with the flow distribution cylinder body, under the action of the motor eccentric ring, the motor flow distribution valve moves radially while moving circumferentially with the flow distribution cylinder body, a hydraulic closed circuit is formed under the joint action of the pump flow distribution valve and the motor flow distribution valve, the pressure oil pushed by the pump plunger enters the plunger hole of the motor cylinder, and then drives the motor plunger to move axially, under the inclination of the motor ball socket tray, the motor plunger generates circumferential thrust, at this time, the mechanical driving speed of the pump cylinder body and the flow distribution cylinder body driven by the pump plunger is consistent with the hydraulic driving speed of the motor cylinder and the flow distribution cylinder body driven by the motor plunger, and the two are coupled and superimposed and then output through the driving main shaft, since part of the speed of the driving shell is output through the pump ball socket tray to drive the pressure oil, therefore, at this positive angle, the mechanical and hydraulic mixed transmission part is speed reduction transmission, and the larger the positive angle is, the larger the speed reduction transmission ratio is.When the motor swash plate controls the support ball socket end face of the motor ball socket tray to form a negative angle with the rotation axis of the driving main shaft, a new closed system is formed. Compared with the closed system when the angle is positive, the high and low pressure circuits remain unchanged, but the original pump executes the function of the motor and the original motor executes the function of the pump. On the basis of pure mechanical transmission, the motor plunger pushes the pump plunger to do axial movement along the original high pressure circuit to the plunger hole of the pump cylinder body, under the action of the inclined pump ball socket tray, the pump cylinder body, together with the matching flow cylinder body and the motor cylinder, is further driven to rotate, that is, the pump cylinder body, together with the matching flow cylinder body and the motor cylinder, generates movement relative to the driving shell at this time, the direction of the movement is consistent with the running direction of the driving shell, that is, speed increase is generated at this time, and the greater the negative angle, the greater the speed increase; when the power motor is decelerated and the driving main shaft is subjected to load reverse dragging, the machine and liquid mixed transmission part can be reversely dragged and decelerated in three cases of pure mechanical transmission, deceleration transmission and speed increase transmission.

[0014] In the application, the machine and liquid mixed continuously variable transmission test method comprises the following tests: zero load basic parameter test, inertia load acceleration and deceleration dynamic characteristic test, constant power output dynamic characteristic test, constant speed output dynamic characteristic test and constant torque output dynamic characteristic test.

[0015] The test of zero load basic parameters, the control system controls the load device to be in zero load state, and controls the constant pressure oil supply of the oil supplement pump station to the machine-oil mixed transmission part. When the oil is supplied, the data feedback of the pressure sensor is collected to correct the output pressure of the oil supplement pump station to the set pressure of the control system. After the oil supplement fills the pump cylinder body, the flow cylinder body and the motor cylinder, there is no load and the oil supplement pressure is low, so the internal leakage is very low and can be ignored. The supplemented oil flows out through the flow channel arranged on the driving main shaft. The control system records the oil supplement flow through the flowmeter when the power motor is not driven, which is recorded as oil supplement flow L1. The control system controls the servo control device to make the machine-oil mixed transmission part in constant speed transmission state. The control system controls the power motor to rotate and output until the rated speed N1 of the machine-oil mixed transmission part in constant speed transmission state. During the acceleration process, the control system records the change of the oil supplement amount through the flowmeter, and records the oil supplement amount at the rated speed, which is recorded as oil supplement flow L2. During the acceleration process of the control motor, the control system collects the data feedback of the input torque speed sensor and the output torque speed sensor, and then obtains the transmission resistance torque at the rated speed, which is recorded as no-load transmission resistance torque M1. At this time, the oil return position at the bottom of the box body is in the lowest state, and the machine-oil mixed transmission part at this time can be regarded as no stirring oil resistance torque. Change the oil return pipeline to connect different oil discharge holes, and then obtain different oil return positions at the bottom of the box body, and collect the data feedback of the input torque speed sensor and the output torque speed sensor at different oil return positions. Thus, the stirring oil resistance torque M2 at different oil return positions is obtained. And in each different oil return position state, the control system controls the servo control device to change the inclination state of the motor swash plate from the maximum positive angle to the maximum negative angle. The control system collects the data feedback of the optical encoder, the input torque speed sensor and the output torque speed sensor in real time, and then records the dynamically changing stirring oil resistance torque M3 in the change process.

[0016] In the present application, the test of the acceleration and deceleration characteristics of the inertial load, the load device is set as the inertial load, the control system controls the servo control device to change the tilt state of the motor swash plate to the maximum positive angle, that is, the machine-hydraulic hybrid transmission part is in the maximum transmission deceleration ratio state, the control system sets different linear acceleration slope and nonlinear acceleration mode of the power motor, and then drives the inertial load to accelerate, after the acceleration is completed in the maximum positive angle state, the control system controls the servo control device to rotate the motor swash plate from the maximum positive angle to the zero position state, and then rotates from the zero position state to the maximum negative angle, and the change mode of the motor swash plate from the maximum positive angle to the zero position and from the zero position to the maximum negative angle is adjustable, and the reverse is done, the control system controls the servo control device to rotate the motor swash plate from the maximum negative angle to the zero position state, and then rotates from the zero position state to the maximum positive angle, after the servo control device completes the deceleration of the inertial load, the control system sets different linear deceleration slope and nonlinear deceleration mode of the power motor, and then drives the inertial load to decelerate, in this process, the control system collects the data feedback of the photoelectric encoder, the flowmeter, the input torque speed sensor and the output torque speed sensor in real time, records the data and analyzes the transmission characteristics under different inertial load conditions and different acceleration and deceleration conditions, such as transmission total efficiency, dynamic acceleration and deceleration characteristics, and volume efficiency and mechanical efficiency of the machine-hydraulic hybrid transmission part.

[0017] In the present application, the test of the constant power output state characteristics, the control system controls the power motor to output drive the machine-hydraulic hybrid transmission part to obtain the rated speed and rated power in the zero position state, the control system controls the load device to change linearly or nonlinearly at different slopes, when the load increases, the control system dynamically adjusts the output speed of the machine-hydraulic hybrid transmission part through the servo control device according to the data feedback of the input torque speed sensor and the output torque speed sensor, and then increases the deceleration transmission ratio of the machine-hydraulic hybrid transmission part or reduces the acceleration transmission ratio of the machine-hydraulic hybrid transmission part, so as to output the driving torque corresponding to the load, so that the current speed and load torque correspond to the constant output power of the power motor, when the load decreases, the control system dynamically adjusts the output speed of the machine-hydraulic hybrid transmission part through the servo control device according to the data feedback of the input torque speed sensor and the output torque speed sensor, and then reduces the deceleration transmission ratio of the machine-hydraulic hybrid transmission part or increases the acceleration transmission ratio of the machine-hydraulic hybrid transmission part, so as to output the driving torque corresponding to the load, so that the current speed and load torque correspond to the constant output power of the power motor, and then analyze the dynamic characteristics according to the collected data records;

[0018] The test of constant speed output dynamic characteristic is that the control system controls the power motor and the servo control device to make the machine-oil hybrid transmission part output at a constant speed with optimal matching power loss, controls the load of the load device to change linearly or nonlinearly with different slopes, and when the load increases, the control system dynamically adjusts the servo control device and the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, increases the output power and speed of the power motor, and increases the reduction transmission ratio of the machine-oil hybrid transmission part or reduces the step-up transmission ratio of the machine-oil hybrid transmission part through the servo control device, so as to balance the speed rise caused by the increase of the output power of the power motor, and to obtain the optimal matching power loss constant speed output driving with the load increasing. When the load decreases, the control system dynamically adjusts the servo control device and the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, reduces the output power and speed of the power motor, and reduces the reduction transmission ratio of the machine-oil hybrid transmission part or increases the step-up transmission ratio of the machine-oil hybrid transmission part through the servo control device, so as to balance the speed drop caused by the reduction of the output power of the power motor, and to obtain the optimal matching power loss constant speed output driving with the load decreasing. Then the dynamic characteristic is analyzed according to the collected data records.

[0019] The test of constant torque output dynamic characteristic is that the control system controls the power motor and the servo control device to make the machine-oil hybrid transmission part output at a constant torque with optimal matching power loss, controls the servo control device to make the speed of the machine-oil hybrid transmission part change linearly or nonlinearly with different slopes, and when the reduction transmission ratio of the machine-oil hybrid transmission part reduces or the step-up transmission ratio of the machine-oil hybrid transmission part increases, the control system dynamically adjusts the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, and increases the output power and speed of the power motor, and the increased power of the power motor corresponds to the sum of the rising speed of the power motor and the increasing speed of the machine-oil hybrid transmission part, so as to obtain the optimal matching power loss constant torque output driving with the speed increasing. When the reduction transmission ratio of the machine-oil hybrid transmission part increases or the step-up transmission ratio of the machine-oil hybrid transmission part reduces, the control system dynamically adjusts the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, and reduces the output power and speed of the power motor, and the reduced power of the power motor corresponds to the sum of the reducing speed of the power motor and the reducing speed of the machine-oil hybrid transmission part, so as to obtain the optimal matching power loss constant torque output driving with the speed reducing. Then the dynamic characteristic is analyzed according to the collected data records. Beneficial effects

[0020] 1. The box for testing in the present application can accurately obtain different oil invasion depths of the machine-fluid hybrid continuously variable transmission during transmission, including obtaining a non-oil invasion state, after setting zero load, first measuring the no-load non-oil invasion transmission resistance torque by the input torque speed sensor in the non-oil invasion state, and then setting the oil invasion depth in multiple stages through the oil discharge holes distributed on the box, respectively obtaining the comprehensive resistance torque at different oil invasion depths, and the difference between the comprehensive resistance torque and the no-load non-oil invasion transmission resistance torque is the oil stirring resistance torque, the testing device and testing method of the present application can accurately obtain the oil stirring resistance torque of the machine-fluid hybrid continuously variable transmission under different working conditions, and the structure can be modified according to the test data to optimize and reduce the oil stirring resistance torque;

[0021] 2. The present application can accurately measure the volumetric efficiency under different working conditions without opening the port of the hydraulic closed system, and the mechanical efficiency of the machine-fluid hybrid continuously variable transmission can be calculated by combining the measured total efficiency, and the structure configuration can be modified according to the test data to optimize and improve the transmission efficiency;

[0022] 3. The present application can configure different working conditions according to the test requirements, complete the acceleration and deceleration dynamic characteristic test of the inertial load, and complete the constant power output dynamic characteristic test, constant speed output dynamic characteristic test and constant torque output dynamic characteristic test under controllable load;

[0023] 4. The box for testing in the present application adopts a plate type distribution mechanism, which is convenient for disassembly and assembly precision adjustment, and can eliminate the cumulative error of machining through assembly, so as to obtain the highest assembly precision and eliminate the influence on transmission efficiency;

[0024] 5. The servo control device can be electrically controlled or manually controlled, which is convenient for adjusting the relative zero position, the full constant speed transmission leakage compensation angle in actual operation can be obtained by feedback of the photoelectric encoder, the internal leakage amount can be obtained through calculation, so as to verify the volumetric efficiency obtained by the change of oil supplementing amount, and realize multi-dimensional transmission efficiency test. BRIEF DESCRIPTION OF DRAWINGS

[0025] Figure 1 It is a whole schematic view of the testing device of the preferred embodiment of the present application;

[0026] Figure 2 It is a schematic view of the servo control part of the preferred embodiment of the present application;

[0027] Figure 3 It is a schematic view of the machine-fluid hybrid transmission part of the preferred embodiment of the present application;

[0028] Figure 4 It is a schematic view of the power input part of the preferred embodiment of the present application;

[0029] Figure 5 It is a schematic view of the load driving part of the preferred embodiment of the present application;

[0030] Figure 6 Partial view of the oil replenishing transmission of the preferred embodiment of the present application;

[0031] Figure 7 Right side view of the left side plate of the preferred embodiment of the present application;

[0032] Figure 8 Right side view of the left side plate of the preferred embodiment of the present application;

[0033] Figure 9 Left side view of the left side plate of the preferred embodiment of the present application;

[0034] Figure 10 Right side view of the right side plate of the preferred embodiment of the present application;

[0035] Figure 11 Right side view of the right side plate of the preferred embodiment of the present application;

[0036] Figure 12 Right side view of the right side plate of the preferred embodiment of the present application;

[0037] Figure 13 Front view of the oil discharge side plate of the preferred embodiment of the present application;

[0038] Figure 14 Top view of the oil discharge side plate of the preferred embodiment of the present application;

[0039] Figure 15 Front view of the servo side plate of the preferred embodiment of the present application;

[0040] Figure 16 Top view of the servo side plate of the preferred embodiment of the present application;

[0041] Figure 17 Front view of the bottom plate of the preferred embodiment of the present application;

[0042] Figure 18 Front view of the cover plate of the preferred embodiment of the present application;

[0043] Figure 19 Front view of the tank of the preferred embodiment of the present application;

[0044] Figure 20 Top view of the tank of the preferred embodiment of the present application;

[0045] Figure 21 Left view of the tank of the preferred embodiment of the present application;

[0046] Figure 22 Sectional view of the tank of the preferred embodiment of the present application;

[0047] Figure 23The box without cover plate is a top view of the preferred embodiment of the present application. Embodiment

[0048] In order to make the technical means, creative features, purposes and effects of the present application easy to understand, the present application is further described below in combination with specific drawings.

[0049] Reference Figures 1-23 The test device of the machine-oil mixed continuously variable transmission mainly consists of a box 1, a machine-oil mixed transmission part 2, an oil supplement pump station 3, a power input part 4, a servo control device 5, a load driving part 6 and a control system 7.

[0050] The machine-oil mixed transmission part 2 is arranged in the box 1, the servo control device 5 is arranged on the box 1, the oil supplement pump station 3 supplements the leaked hydraulic oil for the machine-oil mixed transmission part 2 through a pipeline, the leaked oil of the machine-oil mixed transmission part 2 flows through the box 1 and then returns to the oil tank of the oil supplement pump station 3 through a pipeline, the power input part 4 drives the machine-oil mixed transmission part 2 to output power, the servo control device 5 controls the output speed of the machine-oil mixed transmission part 2, the power output by the machine-oil mixed transmission part 2 drives the load driving part 6, and the control system 7 performs feedback control on the power input part 4 and the servo control device 5 according to the collected data of the power input part 4 and the load driving part 6 to obtain different transmission effects.

[0051] In the embodiment, the box 1 mainly consists of a left end plate 11, a right end plate 12, a bottom plate 13, a cover plate 14, a servo side plate 15 and an oil discharge side plate 16, lifting screws 17 and a box pin shaft 18.

[0052] The left end plate 11, the right end plate 12, the bottom plate 13, the cover plate 14, the servo side plate 15 and the oil discharge side plate 16 are cuboids, the servo side plate 15 and the oil discharge side plate 16 are arranged in parallel and vertically fastened on the bottom plate 13, the left end plate 11 and the right end plate 12 are arranged in parallel and vertically fastened on the bottom plate 13, the left end plate 11 is in contact with one end of the servo side plate 15 and the oil discharge side plate 16 respectively and is fastened by the box pin shaft 18, the right end plate 12 is in contact with the other end of the servo side plate 15 and the oil discharge side plate 16 respectively and is fastened by the box pin shaft 18, the left end plate 11, the right end plate 12, the servo side plate 15 and the oil discharge side plate 16 have the same height, the cover plate 14 is fastened on the upper plane formed by the left end plate 11, the right end plate 12, the servo side plate 15 and the oil discharge side plate 16, the left end plate 11, the right end plate 12, the servo side plate 15, the oil discharge side plate 16 and the cover plate 14 form an internal cavity, the machine-oil mixed transmission part 2 is arranged in the internal cavity, and the lifting screws 17 pass through the cover plate 14 and are arranged on the left end plate 11 and the right end plate 12 respectively.

[0053] In the embodiment, the geometric elements provided on the left end plate 11 include the left side plate mounting hole 111, the left oil sealing cavity 112, the servo variable speed cavity 113, the left support mounting hole 114, the left side plate positioning hole 115, the servo shaft hole 116, the support positioning hole 117, the left bearing cavity 118, the left cover plate screw hole 119, the left bottom plate screw hole 1110, the left lifting screw hole 1111, and the motor screw hole 1112.

[0054] The bottom end of the left end plate 11 is provided with the left bottom plate screw hole 1110, the upper end opposite to the bottom end is provided with the left cover plate screw hole 119 and the left lifting screw hole 1111, the contact end of the left end plate 11 with the servo side plate 15 is provided with the left side plate mounting hole 111 and the left side plate positioning hole 115, and the contact end of the left end plate 11 with the oil discharging side plate 16 is also provided with the left side plate mounting hole 111 and the left side plate positioning hole 115, the left support mounting hole 114, the support positioning hole 117, and the motor screw hole 1112 are distributed and provided on the left end plate 11, the left oil sealing cavity 112 and the left bearing cavity 118 are coaxially provided on the left end plate 11, the left oil sealing cavity 112 is provided with a through hole on one side, and an oil passing cavity is provided between the other side of the left oil sealing cavity 112 and the left bearing cavity 118, the servo variable speed cavity 113 and the servo shaft hole 116 are coaxially provided on the left end plate 11, and the rotation axis of the left oil sealing cavity 112 and the rotation axis of the servo variable speed cavity 113 are parallel, and the servo variable speed cavity 113 is provided with a limit pin slot.

[0055] In the embodiment, the geometric elements provided on the right end plate 12 include the right side plate positioning hole 121, the right large bearing cavity 122, the oil supplementing joint 123, the right small bearing cavity 124, the power bearing cavity 125, the main shaft sealing cavity 126, the right side plate mounting hole 127, the right cover plate screw hole 128, the right lifting screw hole 129, and the right bottom plate screw hole 1210.

[0056] The bottom end of the right end plate 12 is provided with a right bottom plate screw hole 1210, the upper end opposite to the bottom end is provided with a right cover plate screw hole 128 and a right lifting screw hole 129, the contact end of the right end plate 12 with the servo side plate 15 is provided with a right side plate positioning hole 121 and a right side plate mounting hole 127, and the contact end of the right end plate 12 with the oil discharge side plate 16 is also provided with a right side plate positioning hole 121 and a right side plate mounting hole 127, a right large bearing cavity 122, an oil supplement connection 123 and a right small bearing cavity 124 are coaxially arranged on the right end plate 12, the right small bearing cavity 124 is located between the large bearing cavity 122 and the oil supplement connection 123, an oil passing cavity is arranged between the large bearing cavity 122 and the right small bearing cavity 124, a power bearing cavity 125 and a driving shaft seal cavity 126 are coaxially arranged on the right end plate 12, and the rotary axis of the power bearing cavity 125 is parallel to the rotary axis of the large bearing cavity 122, and a limiting stop ring groove is arranged in each of the power bearing cavity 125 and the driving shaft seal cavity 126.

[0057] In the embodiment, the geometric elements arranged on the bottom plate 13 include a bottom plate end hole 131, a bottom plate side hole 132 and a bottom plate U-shaped groove 133.

[0058] The bottom plate end hole 131 is arranged at the left and right ends of the bottom plate 13, the bottom plate side hole 132 is arranged at the upper and lower sides of the bottom plate 13, and the bottom plate U-shaped groove 133 is arranged at the periphery of the upper and lower sides of the bottom plate 13.

[0059] In the embodiment, the geometric elements arranged on the cover plate 14 include a cover plate screw hole 141 and a cover plate lifting hole 142.

[0060] The cover plate screw hole 141 is arranged on the cover plate 14 along the circumference, and the cover plate lifting hole 142 is arranged at the two ends of the cover plate 14.

[0061] In the embodiment, the geometric elements arranged on the servo side plate 15 include a servo cover plate screw hole 151, a servo bottom plate screw hole 152, a secondary shaft cavity 153, a servo side plate positioning hole 154 and a servo side plate screw hole 155.

[0062] The bottom end of the servo side plate 15 is provided with the servo bottom plate screw hole 152, the upper end opposite to the bottom end is provided with the servo cover plate screw hole 151, the contact end of the servo side plate 15 with the right end plate 12 and the left end plate 11 is respectively provided with the servo side plate positioning hole 154 and the servo side plate screw hole 155, and the servo side plate 15 is provided with the secondary shaft cavity 153.

[0063] In the embodiment, the geometric elements arranged on the oil discharge side plate 16 include an oil discharge cover plate screw hole 161, an oil discharge bottom plate screw hole 162, an oil discharge hole 163, an oil discharge side plate positioning hole 164 and an oil discharge side plate screw hole 165.

[0064] The bottom end of the oil discharge side plate 16 is provided with an oil discharge bottom plate screw hole 162, and the upper end opposite to the bottom end is provided with an oil discharge cover plate screw hole 161. The contact end of the oil discharge side plate 16 with the right end plate 12 and the left end plate 11 is respectively provided with an oil discharge side plate positioning hole 164 and an oil discharge side plate screw hole 165. The servo side plate 15 is provided with an oil discharge hole 163.

[0065] In the embodiment, a part of the box pin shaft 18 is arranged in the left side plate positioning hole 115 on one end of the left end plate 11, and another part of the box pin shaft 18 is arranged in the oil discharge side plate positioning hole 164 on one end of the oil discharge side plate 16 in contact with the left end plate 11, so as to limit the relative position of the left end plate 11 and the oil discharge side plate 16. The screw arranged in the left side plate mounting hole 111 is screwed into the oil discharge side plate screw hole 165 on one end of the oil discharge side plate 16 in contact with the left end plate 11, so as to fasten the relative position of the left end plate 11 and the oil discharge side plate 16.

[0066] A part of the box pin shaft 18 is arranged in the right side plate positioning hole 121 on one end of the right end plate 12, and another part of the box pin shaft 18 is arranged in the oil discharge side plate positioning hole 164 on one end of the oil discharge side plate 16 in contact with the right end plate 12, so as to limit the relative position of the right end plate 12 and the oil discharge side plate 16. The screw arranged in the right side plate mounting hole 127 is screwed into the oil discharge side plate screw hole 165 on one end of the oil discharge side plate 16 in contact with the right end plate 12, so as to fasten the relative position of the right end plate 12 and the oil discharge side plate 16.

[0067] A part of the box pin shaft 18 is arranged in the left side plate positioning hole 115 on one end of the left end plate 11, and another part of the box pin shaft 18 is arranged in the servo side plate positioning hole 154 on one end of the servo side plate 15 in contact with the left end plate 11, so as to limit the relative position of the left end plate 11 and the servo side plate 15. The screw arranged in the left side plate mounting hole 111 is screwed into the servo side plate screw hole 155 on one end of the servo side plate 15 in contact with the left end plate 11, so as to fasten the relative position of the left end plate 11 and the servo side plate 15.

[0068] A part of the box pin shaft 18 is arranged in the right side plate positioning hole 121 on one end of the right end plate 12, and another part of the box pin shaft 18 is arranged in the servo side plate positioning hole 154 on one end of the servo side plate 15 in contact with the right end plate 12, so as to limit the relative position of the right end plate 12 and the servo side plate 15. The screw arranged in the right side plate mounting hole 127 is screwed into the servo side plate screw hole 155 on one end of the servo side plate 15 in contact with the right end plate 12, so as to fasten the relative position of the right end plate 12 and the servo side plate 15.

[0069] In the embodiment, the left end plate 11, the right end plate 12, the servo side plate 15, and the oil discharge side plate 16 are vertically arranged on the bottom plate 13, the screws arranged in the side holes 132 of the bottom plate are screwed into the servo bottom plate screw holes 152 and the oil discharge bottom plate screw holes 162 respectively to fasten, the screws arranged in the end holes 131 of the bottom plate are screwed into the left bottom plate screw holes 1110 and the right bottom plate screw holes 1210 respectively to fasten, the cover plate 14 is arranged on the upper end of the box body, the screws pass through the cover plate screw holes 141 and are screwed into the left cover plate screw holes 119, the right cover plate screw holes 128, the servo cover plate screw holes 151, and the oil discharge cover plate screw holes 161 respectively to fasten, the connecting threaded parts of the lifting screws 17 pass through the cover plate lifting holes 142 and are screwed into the left lifting screw holes 1111 and the right lifting screw holes 129 respectively, and after the box body is assembled, the left bearing cavity 118 and the right large bearing cavity 122 are coaxial.

[0070] In the embodiment, the machine-oil mixed transmission part 2 mainly comprises a motor swash plate support 21, a motor eccentric support 22, a support pin shaft 23, a bearing check ring 24, a motor ball socket tray 25, a motor cylinder 26, a motor eccentric ring 27, a pump cylinder body 28, a drive gear 29, a drive main shaft 210, a drive shell 211, a pump ball socket tray 212, a pump plunger 213, a pump flow distribution valve 214, a pump eccentric ring 215, a flow distribution cylinder body 216, a motor flow distribution valve 217, a motor plunger 218, and a motor swash plate 219.

[0071] The flow distribution cylinder 216 is fixedly connected with the pump cylinder 28 at one end, and is fixedly connected with the motor cylinder 26 at the other end. The flow distribution cylinder 216, the motor cylinder 26 and the pump cylinder 28 are coaxially arranged on the driving main shaft 210. The pump plunger 213 is arranged in the plunger hole of the pump cylinder 28 in an axial direction. The motor plunger 218 is arranged in the plunger hole of the motor cylinder 26 in an axial direction. Two rows of valve holes are arranged on the flow distribution cylinder 216 in a radial direction. The pump flow distribution valve 214 is arranged in the valve hole close to the pump cylinder 28. The motor flow distribution valve 217 is arranged in the valve hole close to the motor cylinder 26. The motor swash plate support 21 and the motor eccentric support 22 are assembled by limiting with a pin and fastened by a screw. The motor swash plate 219 is rotatably arranged on the motor swash plate support 21. The motor swash plate 219 is in surface contact with the motor swash plate support 21. The motor swash plate 219 is in contact with the motor eccentric support 22 through the upper and lower circular arc structures. The center line of the upper and lower circular arcs passes through the center of the spherical surface of the motor swash plate 219 and the motor swash plate support 21, so as to limit the relative position of the motor swash plate 219 relative to the motor swash plate support 21 and the motor eccentric support 22, and thus the motor swash plate 219 can only rotate around the center line of the upper and lower circular arcs. The motor ball socket tray 25 is arranged in the motor swash plate 219 through a bearing. The load check ring 24 is arranged on the driving main shaft 210 and is limited by the check ring arranged on the driving main shaft 210. The load check ring 24 is arranged on the motor swash plate support 21 through a bearing. The load boss on the load check ring 24 and the load boss of the bearing on the motor swash plate support 21 are located on both sides of the bearing. The motor cylinder 26 is arranged on the motor eccentric support 22 through a bearing. The ball head on the motor plunger 218 is in contact with the ball socket on the motor ball socket tray 25. The motor eccentric support 22 is provided with a cavity eccentric to the rotation axis of the motor cylinder 26. The motor eccentric ring 27 is arranged in the cavity. The axial position of the motor eccentric ring 27 is located at the axial position of the motor flow distribution valve 217. One end of the driving housing 211 is arranged on the pump cylinder 28 through a bearing. The other end of the driving housing 211 is arranged on the driving main shaft 210 through a bearing. The bearing is limited by the check ring arranged on the driving main shaft 210. The pump ball socket tray 212 is arranged in the driving housing 211 through a bearing. The rotation axis of the pump ball socket tray 212 is at an angle to the rotation axis of the driving main shaft 210. The ball head on the pump plunger 213 is in contact with the ball socket on the pump ball socket tray 212. The driving housing 211 is provided with a cavity eccentric to the rotation axis of the pump cylinder 28. The pump eccentric ring 215 is arranged in the cavity. The axial position of the pump eccentric ring 215 is located at the axial position of the pump flow distribution valve 214. The driving housing 211 is provided with a driving gear 29. The driving housing 211 and the driving gear 29 are limited and driven by a pin shaft and fastened by a screw.The driving housing 211 is rotatably arranged on the right end plate 12 through a bearing located in the right large bearing cavity 122, and the driving spindle 210 is rotatably arranged on the right end plate 12 through a bearing located in the right small bearing cavity 124, the motor swash bracket 21 is arranged on the left end plate 11 through the left bearing cavity 118, and the circumferential rotation of the motor swash bracket 21 is limited through the bracket pin shaft 23, and the motor swash bracket 21 and the left end plate 11 are fastened through the screws arranged in the left bracket mounting hole 114, the driving spindle 210 passes through the left end plate 11, and the oil seal is arranged between the left end plate 11 and the driving spindle 210, and the oil seal is arranged in the left oil seal cavity 112.

[0072] In the embodiment, the oil supplement pump station 3 comprises an oil supplement joint 31, a pipe joint 32, a flow meter 33, and a pressure sensor 34.

[0073] The oil supplement joint 31 is rotatably fastened in the oil supplement connecting port 123 on the right end plate 12, and the outer circle of the oil supplement joint 31 is in clearance fit with the inner hole of the driving spindle 210, the fit clearance and the fit length can be adjusted according to the requirement, the pipe joint 32 on the oil pipeline of the oil supplement pump station 3 is connected with the oil supplement joint 31, and then the pressure oil of the oil supplement pump station 3 is delivered to the inner cavity of the driving spindle 210 through the pressure sensor 34 and the flow meter 33, the oil return pipeline joint of the oil supplement pump station 3 is connected with one of the oil discharge holes 163 on the oil discharge side plate 16, and the remaining oil discharge holes 163 on the oil discharge side plate 16 are provided with plugs, and the output pressure oil of the oil supplement pump station 3 is a constant pressure oil source.

[0074] In the embodiment, the power input part 4 comprises a driving gear 41, a driving shaft 42, a power motor 43, a shaft coupling 44, and an input torque and rotating speed sensor 45.

[0075] The driving shaft 42 is rotatably arranged on the right end plate 12 through a bearing located in the power bearing cavity 125, and the oil seal is arranged between the driving shaft 42 and the right end plate 12, and the oil seal is arranged in the driving shaft seal cavity 126, one end of the driving shaft 42 is provided with the driving gear 41, the driving shaft 42 transmits power through the driving gear 41, the driving gear 41 is in meshing transmission with the driving gear 29, the other end of the driving shaft 42 is connected with one end of the input torque and rotating speed sensor 45 through the shaft coupling 44 for transmission, and the other end of the input torque and rotating speed sensor 45 is connected with the power motor 43 through the shaft coupling 44 for transmission.

[0076] In the embodiment, the servo control device 5 comprises an optical encoder 51, an encoder bracket 52, a servo sub-shaft 53, a servo pinion 54, a servo spindle 55, a servo bevel gear 56, a servo nut 57, a servo planet carrier 58, an outer ring positioning pin 59, a servo sun gear 510, a servo motor 511, a servo planet gear 512, and a servo outer ring 513.

[0077] The servo countershaft 53 is arranged on the servo side plate 15 through a bearing located in the countershaft cavity 153, and an oil seal is arranged between the servo countershaft 53 and the servo side plate 15. The servo countershaft 53 is provided with a manual control mechanism at one end, and an optical encoder 51 is also arranged at the end. The optical encoder 51 is fixedly arranged on the servo side plate 15 through an encoder support 52. The shaft of the optical encoder 51 is connected with the servo countershaft 53. The other end of the servo countershaft 53 is provided with a secondary bevel gear 54. The relative position of the secondary bevel gear 54 on the servo countershaft 53 can be adjusted and fastened through a screw. One end of the servo main shaft 55 is arranged on the motor eccentric support 22 through a bearing. The other end of the servo main shaft 55 is arranged on the motor swash plate support 21 through a bearing. A servo nut 57 is movably arranged on the servo main shaft 55 between the two bearings. The servo nut 57 is connected with a rocker arm on the motor swash plate 219 for transmission. The one end of the servo main shaft 55 is provided with a main bevel gear 56. The axial position of the main bevel gear 56 on the servo main shaft 55 can be adjusted by changing the thickness of a retainer. The other end of the servo main shaft 55 is provided with a servo carrier 58. An oil seal is arranged between the servo main shaft 55 and the motor swash plate support 21. A servo outer ring 513 is arranged in the servo transmission cavity 113. The circumferential rotation of the servo outer ring 513 is limited by an outer ring positioning pin 59 arranged in a limiting pin slot of the servo transmission cavity 113. The servo carrier 58 is provided with a servo planetary gear 512. The servo motor 511 is arranged on the left end plate 11 and fastened by a screw screwed into a motor screw hole 1112. The rotation center of the driving shaft of the servo motor 511 and the rotation center of the servo main shaft 55 are coaxially arranged. The servo sun gear 510 is arranged on the driving shaft of the servo motor 511. The servo motor 511 drives the servo planetary gear 512 through the servo sun gear 510 to drive the servo carrier 58 to rotate and in turn drive the servo main shaft 55 to rotate. The rotating servo main shaft 55 drives the servo nut 57 to move, and the moving servo nut 57 drives the motor swash plate 219 to rotate. The servo main shaft 55 drives the secondary bevel gear 54 through the main bevel gear 56 to in turn drive the servo countershaft 53 to rotate. The rotation amount of the servo countershaft 53 is collected by the optical encoder 51 and fed back to the control system, so as to obtain the inclination angle of the motor swash plate 219.

[0078] After the servo motor 511 is powered off, the servo countershaft 53 can be manually operated to drive the servo main shaft 55 to rotate through the secondary bevel gear 54 and the main bevel gear 56, and in turn drive the servo nut 57 to move.

[0079] In the embodiment, the load driving part 6 includes a main flange plate 61, a transmission pin 62, a slave flange plate 63, an output torque and speed sensor 64, and a load device 65.

[0080] The main flange 61 is connected to the driving main shaft 210 at one end, and is connected to the slave flange 63 at the other end. The transmission pin 62 is arranged between the main flange 61 and the slave flange 63, and is cut off when the transmission is overloaded, so as to prevent damage to the transmission. The slave flange 63 is connected to the output torque and speed sensor 64 at the other end, and is connected to the load device 65 at the other end. The load device 65 can be an inertial load or a controllable load.

[0081] In the embodiment, the oil supplement pump station 3 supplies oil to the inner cavity of the driving main shaft 210 of the machine-oil mixed transmission part 2. Part of the oil enters the motor cylinder 26, the pump cylinder body 28 and the flow distribution cylinder body 216 to compensate for internal leakage. Another part of the oil flows out through the flow channel arranged on the driving main shaft 210 to flush the mechanisms of the machine-oil mixed transmission part 2. The flushed oil and the oil after internal leakage flow through the tank and then flow back to the oil supplement pump station 3 through the oil discharge hole 163 and the oil return pipeline. The oil return pipeline is connected to different oil discharge holes 163 to obtain different oil storage heights in the tank.

[0082] The power motor 43 drives the driving gear 29 through the input torque and speed sensor 45, the driving shaft 42 and the driving gear 41, and then drives the driving shell 211 to rotate.

[0083] When the motor swash plate 219 controls the support ball socket end face of the motor ball socket tray 25 to be perpendicular to the rotation axis of the driving main shaft 210, the state is recorded as zero position. The power of the driving shell 211 drives the pump plunger 213 through the pump ball socket tray 212, and then drives the pump cylinder body 28 to rotate. The power of the pump cylinder body 28 is directly output by the pure mechanical transmission of the driving main shaft 210. At this time, the pump plunger 213, the motor plunger 218, the motor ball socket tray 25, the pump flow distribution valve 214 and the motor flow distribution valve 217 move circumferentially with the pump cylinder body 28, the motor cylinder 26 and the flow distribution cylinder body 216. At this time, the pump plunger 213 and the motor plunger 218 have no axial movement, the pump flow distribution valve 214 has no radial movement, and the motor flow distribution valve 217 simultaneously performs radial movement under the action of the motor eccentric ring 27. The motor flow distribution valve 217 performs oil distribution on the plunger hole where the motor plunger 218 is located which alternately enters the high-pressure oil area. When the support ball socket end face is perpendicular to the axis, the pure mechanical transmission is a theoretical constant speed transmission. In the actual transmission process, the pure mechanical transmission of the zero position is a non-constant speed transmission due to internal leakage, especially when the load is large. A speed difference is generated due to leakage. In order to compensate for the internal leakage and realize the theoretical constant speed transmission, the support ball socket end face of the motor ball socket tray 25 is at an adaptive leakage compensation angle state with the rotation axis of the driving main shaft 210.

[0084] When the motor swash plate 219 controls the support ball socket end face of the motor ball socket tray 25 to be positive angle with the rotation axis of the drive spindle 210, the power of the drive housing 211 drives the pump plunger 213 through the pump ball socket tray 212, and then drives the pump cylinder 28 to rotate, at the same time, the pump ball socket tray 212 drives the pump plunger 213 to move axially, the drive housing 211 and the pump eccentric ring 215 generate circumferential relative motion with the pump cylinder 28, under the action of the pump eccentric ring 215, the pump flow valve 214 generates radial motion while following the circumferential motion of the flow cylinder 216, under the action of the motor eccentric ring 27, the motor flow valve 217 generates radial motion while following the circumferential motion of the flow cylinder 216, under the joint action of the pump flow valve 214 and the motor flow valve 217, a hydraulic closed loop is formed, the pressure oil pushed by the pump plunger 213 enters the plunger hole of the motor cylinder 26, and then drives the motor plunger 218 to move axially, under the action of the motor ball socket tray 25, the motor plunger 218 generates circumferential thrust, at this time, the mechanical drive speed of the pump cylinder 28, the flow cylinder 216 and the motor cylinder 26 driven by the pump ball socket tray 212 through the pump plunger 213 is consistent with the hydraulic drive speed of the motor cylinder 26, the flow cylinder 216 and the pump cylinder 28 driven by the motor plunger 218, the two are coupled and superimposed, and then output through the drive spindle 210, since part of the speed of the drive housing 211 is output through the pump ball socket tray 212 to drive the pressure oil, therefore, when the positive angle is greater, the speed reduction transmission ratio is greater;

[0085] When the motor swash plate 219 controls the support ball socket end face of the motor ball socket tray 25 to be negative angle with the rotation axis of the drive spindle 210, a new closed system is formed, compared with the closed system when the positive angle is, the high and low pressure circuits are unchanged, but the original pump executes the function of the motor, and the original motor executes the function of the pump, on the basis of pure mechanical transmission, the motor plunger 218 pushes the pump plunger 213 to move axially along the original high pressure circuit to push the pressure oil into the plunger hole of the pump cylinder 28, under the action of the inclined pump ball socket tray 212, the pump cylinder 28, the flow cylinder 216 and the motor cylinder 26 are further driven to rotate, that is, the pump cylinder 28, the flow cylinder 216 and the motor cylinder 26 generate motion relative to the drive housing 211 at this time, the direction of the motion is consistent with the running direction of the drive housing 211, that is, speed increasing is generated at this time, and the greater the negative angle is, the greater the speed increasing is;

[0086] When the power motor 43 is reduced in speed and the drive spindle 210 is dragged by the load, the machine liquid hybrid transmission part 2 can be dragged in speed in three cases of pure mechanical transmission, speed reduction transmission and speed increasing transmission.

[0087] Referring to Figures 1-23The test method of the machine-oil hybrid continuously variable transmission includes the test of zero load basic parameters, the test of inertia load acceleration and deceleration characteristics, the test of constant power output state characteristics, the test of constant speed output dynamic characteristics and the test of constant torque output dynamic characteristics.

[0088] In the embodiment, the test of zero load basic parameters, the control system 7 controls the load device 65 to be in the zero load state, and controls the constant pressure oil supply of the oil supplement pump station 3 to the machine-oil hybrid transmission part 2. When the oil is supplied, the output pressure of the oil supplement pump station 3 is corrected to the set pressure of the control system by collecting the data feedback of the pressure sensor 34. After the oil supplement fills the pump cylinder body 28, the flow cylinder body 216 and the motor cylinder 26, there is no load and the oil supplement pressure is low, so the internal leakage is extremely low and can be ignored. The oil supplement amount flows out through the flow channel arranged on the driving main shaft 210. The control system 7 records the oil supplement flow through the flowmeter 33 when the power motor 43 is not driven, and records the oil supplement flow L1. The control system 7 controls the servo control device 5 to make the machine-oil hybrid transmission part 2 in the constant speed transmission state. The control system 7 controls the power motor 43 to rotate and output until the rated speed N1 of the machine-oil hybrid transmission part 2 in the constant speed transmission state. During the acceleration process, the control system 7 records the change of the oil supplement amount through the flowmeter 33, and records the oil supplement amount at the rated speed, which is recorded as the oil supplement flow L2. During the acceleration process of the power motor 43, the control system 7 collects the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then obtains the transmission resistance torque at the rated speed, which is recorded as the empty load transmission resistance torque M1. At this time, the oil return position at the bottom of the tank body 1 is in the lowest state, and the machine-oil hybrid transmission part 2 at this time can be regarded as having no oil stirring resistance torque. The oil return pipeline is connected to different oil discharge holes 163, and then the oil return position at the bottom of the tank body 1 is obtained, and the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64 is collected and recorded at different oil return positions, so as to obtain the oil stirring resistance torque M2 at different oil return positions. In the state of each different oil return position, the control system 7 controls the servo control device 5 to change the inclination state of the motor swash plate 219, from the maximum positive angle to the maximum negative angle. The control system 7 collects the data feedback of the photoelectric encoder 51, the input torque speed sensor 45 and the output torque speed sensor 64 in real time, and then records the dynamically changing oil stirring resistance torque M3 in the change process.

[0089] In this embodiment, the test of the inertia load acceleration and deceleration characteristics, the load device 65 is set as the inertia load, the control system 7 controls the servo control device 5 to change the tilt state of the motor swash plate 219 to the maximum positive angle, that is, the machine-fluid hybrid transmission part 2 is in the maximum transmission deceleration ratio state, and then the power motor 43 is set to different linear acceleration slope and nonlinear acceleration mode by the control system 7, thereby driving the inertia load to accelerate. After the acceleration is completed at the maximum positive angle, the control system 7 controls the servo control device 5 to rotate the motor swash plate 219 from the maximum positive angle to the zero position state, and then rotates from the zero position state to the maximum negative angle after the zero position state is stalled. The change mode of the motor swash plate 219 from the maximum positive angle to the zero position and from the zero position to the maximum negative angle is adjustable. Conversely, the control system 7 controls the servo control device 5 to rotate the motor swash plate 219 from the maximum negative angle to the zero position state, and then rotates from the zero position state to the maximum positive angle after the zero position state is stalled. After the servo control device 5 completes the deceleration of the inertia load, the control system 7 sets different linear deceleration slope and nonlinear deceleration mode of the power motor 43, thereby driving the inertia load to decelerate. In this process, the control system 7 collects the data feedback of the photoelectric encoder 51, the flowmeter 33, the input torque speed sensor 45 and the output torque speed sensor 64 in real time. In the acceleration process, the oil supplement flow corresponding to each state is recorded as L3, the input torque is recorded as M4, the output torque is recorded as M5, the input speed is recorded as N2, and the output speed is recorded as N3. Thus, the data is recorded and combined with the data in the aforementioned basic parameter test to analyze the transmission characteristics under different inertia load conditions and different acceleration and deceleration conditions. The total transmission efficiency can be calculated from M4, M5, N2 and N3. The volumetric efficiency can be calculated from L2, L3 and N3. The mechanical efficiency can be calculated from the total efficiency and the volumetric efficiency. Conversely, the calculation method of the deceleration process is also the same. The dynamic characteristics of the inertia load acceleration and deceleration can be analyzed from the data acquisition curve.

[0090] In this embodiment, the test of constant power output dynamic characteristics, the control system 7 controls the power motor 43 to output the drive machine liquid hybrid transmission part 2 to obtain the rated speed and rated power in the zero position state, the control system 7 controls the load device 65 to change linearly or nonlinearly with different slopes, when the load increases, the control system 7 dynamically adjusts the servo control device 5 to control the output speed of the machine liquid hybrid transmission part 2 according to the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then increases the speed reduction transmission ratio of the machine liquid hybrid transmission part 2 or reduces the speed increase transmission ratio of the machine liquid hybrid transmission part 2, so as to output the drive torque corresponding to the load, so that the current speed and the load torque correspond to the constant output power of the power motor 43, when the load decreases, the control system 7 dynamically adjusts the servo control device 5 to control the output speed of the machine liquid hybrid transmission part 2 according to the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then reduces the speed reduction transmission ratio of the machine liquid hybrid transmission part 2 or increases the speed increase transmission ratio of the machine liquid hybrid transmission part 2, so as to output the drive torque corresponding to the load, so that the current speed and the load torque correspond to the constant output power of the power motor 43, and then analyze the dynamic characteristics according to the collected data records.

[0091] In this embodiment, the test of constant power output dynamic characteristics, the control system 7 controls the power motor 43 to output the drive machine liquid hybrid transmission part 2 to obtain the rated speed and rated power in the zero position state, the control system 7 controls the load device 65 to change linearly or nonlinearly with different slopes, when the load increases, the control system 7 dynamically adjusts the servo control device 5 to control the output speed of the machine liquid hybrid transmission part 2 according to the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then increases the speed reduction transmission ratio of the machine liquid hybrid transmission part 2 or reduces the speed increase transmission ratio of the machine liquid hybrid transmission part 2, so as to output the drive torque corresponding to the load, so that the current speed and the load torque correspond to the constant output power of the power motor 43, when the load decreases, the control system 7 dynamically adjusts the servo control device 5 to control the output speed of the machine liquid hybrid transmission part 2 according to the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then reduces the speed reduction transmission ratio of the machine liquid hybrid transmission part 2 or increases the speed increase transmission ratio of the machine liquid hybrid transmission part 2, so as to output the drive torque corresponding to the load, so that the current speed and the load torque correspond to the constant output power of the power motor 43, and then analyze the dynamic characteristics according to the collected data records.

[0092] In the present embodiment, the test of constant torque output dynamic characteristics, the control system 7 controls the power motor 43 and the servo control device 5 to make the machine fluid hybrid transmission part 2 output constant torque with optimal matching power loss, the control system 7 controls the servo control device 5 to make the speed of the machine fluid hybrid transmission part 2 change linearly or nonlinearly with different slopes, when the speed reduction transmission ratio of the machine fluid hybrid transmission part 2 decreases or the speed increasing transmission ratio of the machine fluid hybrid transmission part 2 increases, the control system 7 dynamically adjusts the power motor 43 according to the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then increases the output power and speed of the power motor 43, the increased power of the power motor 43 corresponds to the sum of the increased speed of the power motor 43 and the increased speed of the machine fluid hybrid transmission part 2, so as to obtain constant torque output driving with optimal matching power loss when the speed increases, when the speed reduction transmission ratio of the machine fluid hybrid transmission part 2 increases or the speed increasing transmission ratio of the machine fluid hybrid transmission part 2 decreases, the control system 7 dynamically adjusts the power motor 43 according to the data feedback of the input torque speed sensor 45 and the output torque speed sensor 64, and then reduces the output power and speed of the power motor 43, the reduced power of the power motor 43 corresponds to the sum of the reduced speed of the power motor 43 and the reduced speed of the machine fluid hybrid transmission part 2, so as to obtain constant torque output driving with optimal matching power loss when the speed decreases, and then analyzes the dynamic characteristics according to the collected data records.

[0093] The basic principles and main features of the present application and the advantages of the present application are shown and described above. It should be understood by those skilled in the art that the present application is not limited by the above embodiments, the above embodiments and the description in the specification are only to illustrate the principles of the present application, and various changes and improvements can be made to the present application without departing from the spirit and scope of the present application, and these changes and improvements all fall within the scope of the present application. The scope of protection of the present application is defined by the appended claims and their equivalents.

Claims

1. A test device for a mechanical-hydraulic continuously variable transmission, comprising a housing, a mechanical-hydraulic transmission section, an oil make-up pump station, a power input section, a servo control device, a load drive section, a control system, characterized in that The machine-oil hybrid transmission part is arranged in the box, the servo control device is arranged on the box, the oil supplement pump station supplements the leaked hydraulic oil to the machine-oil hybrid transmission part through the pipeline, the leaked oil of the machine-oil hybrid transmission part flows through the box and then returns to the oil tank of the oil supplement pump station through the pipeline, the power input part drives the machine-oil hybrid transmission part to output power, the servo control device controls the output speed of the machine-oil hybrid transmission part, the power output by the machine-oil hybrid transmission part drives the load driving part, and the control system performs feedback control on the power input part and the servo control device according to the collected data of the power input part and the load driving part; different oil storage heights in the box can be obtained by connecting different oil discharge holes on the box through the oil return pipeline; the motor swash plate of the machine-oil hybrid transmission part is rotatably arranged on the motor swash plate support, is transmitted by the servo nut of the servo control device and the rocker arm on the motor swash plate, so as to control the rotation of the motor swash plate and make the motor swash plate and the driving main shaft have different included angle states, so that the machine-oil hybrid transmission part realizes different transmission effects; the control system controls the load driving part to output the required load form in the test, and provides zero load, variable load and inertial load.

2. The test apparatus for a machine-fluid continuously variable transmission according to claim 1, characterized by, The oil supplement pump station comprises an oil supplement joint, a pipe joint, a flowmeter and a pressure sensor, the oil supplement joint is rotatably and tightly arranged in the oil supplement connecting port on the right end plate, and the outer circle of the oil supplement joint is matched with the inner hole of the driving main shaft in a clearance fit, the matching clearance and the matching length can be adjusted according to requirements, the pipe joint on the oil pipeline of the oil supplement pump station is connected with the oil supplement joint, so that the pressure oil of the oil supplement pump station is transmitted to the inner cavity of the driving main shaft through the pressure sensor and the flowmeter, the oil return pipeline joint of the oil supplement pump station is connected with one of the oil discharge holes on the oil discharge side plate, and the remaining oil discharge holes on the oil discharge side plate are provided with plugs, and the output pressure oil of the oil supplement pump station is a constant pressure oil source.

3. The machine-fluid hybrid continuously variable transmission test device according to claim 1 or 2, characterized in that The oil supplement pump station supplements the oil to the inner cavity of the driving main shaft, part of the oil enters the motor cylinder, the pump cylinder and the flow distribution cylinder to compensate for the internal leakage, and the other part of the oil flows out through the flow channel arranged on the driving main shaft to flush the mechanisms of the machine-oil hybrid transmission part, and the flushed oil and the oil after the internal leakage flow through the box, the oil discharge holes and the oil return pipeline to return to the oil supplement pump station.

4. The test apparatus for a machine-fluid continuously variable transmission according to claim 1, characterized by, The power input part comprises a driving gear, a driving shaft, a power motor, a shaft coupling and an input torque and speed sensor, the driving shaft is rotatably arranged on the right end plate through a bearing, the bearing is arranged in the power bearing type cavity, an oil seal is arranged between the driving shaft and the right end plate, and the oil seal is arranged in the driving shaft sealing type cavity, one end of the driving shaft is provided with the driving gear, the driving shaft transmits power through the driving gear, the driving gear is engaged with the driving gear to transmit power, the other end of the driving shaft is connected with one end of the input torque and speed sensor through the shaft coupling to transmit power, and the other end of the input torque and speed sensor is connected with the power motor through the shaft coupling to transmit power.

5. The test apparatus for a machine-fluid continuously variable transmission according to claim 1, wherein The load driving part comprises a main flange, a transmission pin, a slave flange, an output torque and speed sensor, and a load device, one end of the main flange is connected with the driving main shaft, the other end of the main flange is connected with one end of the slave flange, the transmission pin is arranged between the main flange and the slave flange, the other end of the slave flange is connected with one end of the output torque and speed sensor, the other end of the output torque and speed sensor is connected with the load device, and the load device can be an inertial load or a controllable load.

6. The machine-fluid hybrid continuously variable transmission test device of claim 1, wherein the housing is mainly composed of a left end plate, a right end plate, a bottom plate, a cover plate, a servo side plate, an oil discharge side plate, a lifting screw, and a housing pin shaft. The left end plate, the right end plate, the bottom plate, the cover plate, the servo side plate and the oil discharging side plate are cuboids, the servo side plate and the oil discharging side plate are arranged in parallel and vertically opposite on the bottom plate, the left end plate and the right end plate are arranged in parallel and vertically opposite on the bottom plate, the left end plate is positioned and fastened with one end of the servo side plate and the oil discharging side plate through the box shaft, the right end plate is positioned and fastened with the other end of the servo side plate and the oil discharging side plate through the box shaft, the left end plate, the right end plate, the servo side plate and the oil discharging side plate have the same height, the cover plate is fastened on the upper plane formed by the left end plate, the right end plate, the servo side plate and the oil discharging side plate, the left end plate, the right end plate, the servo side plate, the oil discharging side plate and the cover plate form an internal cavity, the hydraulic-mechanical transmission part is arranged in the internal cavity, and the lifting screws pass through the cover plate and are arranged on the left end plate and the right end plate.

7. The machine-fluid hybrid continuously variable transmission test device of claim 6, wherein, The geometric elements arranged on the left end plate comprise a left side plate mounting hole, a left oil sealing cavity, a servo shifting cavity, a left support mounting hole, a left side plate positioning hole, a servo shaft hole, a support positioning hole, a left bearing cavity, a left cover plate screw hole, a left bottom plate screw hole, a left lifting screw hole and a motor screw hole, the bottom end of the left end plate is provided with the left bottom plate screw hole, the upper end opposite to the bottom end is provided with the left cover plate screw hole and the left lifting screw hole, the contact end of the left end plate with the servo side plate is provided with the left side plate mounting hole and the left side plate positioning hole, and the contact end of the left end plate with the oil discharging side plate is also provided with the left side plate mounting hole and the left side plate positioning hole, the left support mounting hole, the support positioning hole and the motor screw hole are arranged on the left end plate, the left oil sealing cavity and the left bearing cavity are coaxially arranged on the left end plate, one side of the left oil sealing cavity is provided with a through hole, an oil passing cavity is arranged between the other side of the left oil sealing cavity and the left bearing cavity, the servo shifting cavity and the servo shaft hole are coaxially arranged on the left end plate, the rotation axis of the left oil sealing cavity is parallel to the rotation axis of the servo shifting cavity, and a limit pin slot is arranged on the servo shifting cavity.

8. The test apparatus for a machine-fluid continuously variable transmission according to claim 6, wherein The geometric elements provided on the right end plate include a right side plate positioning hole, a right large bearing cavity, an oil supplement interface, a right small bearing cavity, a power bearing cavity, a driving shaft seal cavity, a right side plate mounting hole, a right cover plate screw hole, a right lifting screw hole, and a right bottom plate screw hole. The bottom end of the right end plate is provided with the right bottom plate screw hole, the bottom end is in contact with the bottom plate, the upper end opposite to the bottom end is provided with the right cover plate screw hole and the right lifting screw hole, the contact end of the right end plate with the servo side plate is provided with the right side plate positioning hole and the right side plate mounting hole, and the contact end of the right end plate with the oil discharge side plate is also provided with the right side plate positioning hole and the right side plate mounting hole. The right large bearing cavity, the oil supplement interface and the right small bearing cavity are coaxially arranged on the right end plate, the right small bearing cavity is located between the large bearing cavity and the oil supplement interface, an oil passing cavity is arranged between the large bearing cavity and the right small bearing cavity, the power bearing cavity and the driving shaft seal cavity are coaxially arranged on the right end plate, the rotary axis of the power bearing cavity is parallel to the rotary axis of the large bearing cavity, and a limiting stop ring groove is arranged in the power bearing cavity and the driving shaft seal cavity.

9. The test apparatus for a machine-fluid continuously variable transmission according to claim 6, wherein The geometric elements provided on the bottom plate include a bottom plate end hole, a bottom plate side hole and a bottom plate U-shaped groove. The bottom plate end hole is arranged at the left and right ends of the bottom plate, the bottom plate side hole is arranged at the upper and lower sides of the bottom plate, and the bottom plate U-shaped groove is arranged at the periphery of the upper and lower sides of the bottom plate. The geometric elements provided on the cover plate include a cover plate screw hole and a cover plate lifting hole. The cover plate screw hole is arranged along the circumference of the cover plate, and the cover plate lifting hole is arranged at the two ends of the cover plate.

10. The test apparatus for a machine-fluid continuously variable transmission according to claim 6, wherein The geometric elements provided on the servo side plate include a servo cover plate screw hole, a servo bottom plate screw hole, a secondary shaft cavity, a servo side plate positioning hole and a servo side plate screw hole. The bottom end of the servo side plate is provided with the servo bottom plate screw hole, the bottom end is in contact with the bottom plate, the upper end opposite to the bottom end is provided with the servo cover plate screw hole, the contact end of the servo side plate with the right end plate and the left end plate is respectively provided with the servo side plate positioning hole and the servo side plate screw hole, and the servo side plate is provided with the secondary shaft cavity. The geometric elements provided on the oil discharge side plate include an oil discharge cover plate screw hole, an oil discharge bottom plate screw hole, an oil discharge hole, an oil discharge side plate positioning hole and an oil discharge side plate screw hole. The bottom end of the oil discharge side plate is provided with the oil discharge bottom plate screw hole, the bottom end is in contact with the bottom plate, the upper end opposite to the bottom end is provided with the oil discharge cover plate screw hole, the contact end of the oil discharge side plate with the right end plate and the left end plate is respectively provided with the oil discharge side plate positioning hole and the oil discharge side plate screw hole, and the servo side plate is provided with the oil discharge hole.

11. The test apparatus for a machine-fluid continuously variable transmission according to claim 6, wherein One part of the box pin shaft is arranged in the left side plate positioning hole at one end of the left end plate, the other part of the box pin shaft is arranged in the oil discharge side plate positioning hole at one end of the oil discharge side plate in contact with the left end plate, and the screw arranged in the left side plate mounting hole is screwed into the oil discharge side plate screw hole at one end of the oil discharge side plate in contact with the left end plate. One part of the box pin shaft is arranged in the right side plate positioning hole at one end of the right end plate, the other part of the box pin shaft is arranged in the oil discharge side plate positioning hole at one end of the oil discharge side plate in contact with the right end plate, and the screw arranged in the right side plate mounting hole is screwed into the oil discharge side plate screw hole at one end of the oil discharge side plate in contact with the right end plate. The box pin shaft is partly installed in the left side plate positioning hole on one end of the left end plate, and the other part of the box pin shaft is installed in the servo side plate positioning hole on one end of the servo side plate in contact with the left end plate, and the screw installed in the left side plate mounting hole is screwed into the servo side plate screw hole on one end of the servo side plate in contact with the left end plate at the same time. The box pin shaft is partly installed in the right side plate positioning hole on one end of the right end plate, and the other part of the box pin shaft is installed in the servo side plate positioning hole on one end of the servo side plate in contact with the right end plate, and the screw installed in the right side plate mounting hole is screwed into the servo side plate screw hole on one end of the servo side plate in contact with the right end plate at the same time.

12. The test apparatus for a machine-fluid continuously variable transmission according to claim 6, wherein The screws installed in the side holes of the bottom plate are respectively screwed into the servo bottom plate screw holes and the oil discharge bottom plate screw holes to be fastened, the screws installed in the end holes of the bottom plate are respectively screwed into the left bottom plate screw holes and the right bottom plate screw holes to be fastened, the cover plate is arranged on the upper end of the box, the screws pass through the cover plate screw holes and are respectively screwed into the left cover plate screw holes, the right cover plate screw holes, the servo cover plate screw holes and the oil discharge cover plate screw holes to be fastened, the connecting thread parts of the lifting screws pass through the cover plate lifting holes and are respectively screwed into the left lifting screw holes and the right lifting screw holes, and after the box is assembled, the left bearing cavity and the right large bearing cavity are coaxial.

13. The machine-fluid hybrid continuously variable transmission test device of claim 1, the machine-fluid hybrid transmission portion consisting essentially of a motor swash plate support, a motor eccentric support, a support pin, a load retainer, a motor ball socket tray, a motor cylinder, a motor eccentric ring, a pump cylinder block, a drive gear, a drive spindle, a drive housing, a pump ball socket tray, a pump plunger, a pump flow divider valve, a pump eccentric ring, a flow divider cylinder block, a motor flow divider valve, a motor plunger, a motor swash plate, wherein, One end of the distribution cylinder body is fastened and connected with the pump cylinder body, the other end of the distribution cylinder body is fastened and connected with the motor cylinder, the distribution cylinder body, the motor cylinder and the pump cylinder body are coaxially and fixedly arranged on the driving main shaft, the pump plunger shaft is arranged in the plunger hole of the pump cylinder body in an axial direction, the motor plunger shaft is arranged in the plunger hole of the motor cylinder in an axial direction, two rows of valve holes are arranged on the distribution cylinder body in a radial direction, the pump distribution valve is arranged in the valve hole close to the pump cylinder body, and the motor distribution valve is arranged in the valve hole close to the motor cylinder; The motor swash plate support and the motor eccentric support are assembled by limiting through a pin and fastened by screws, the motor swash plate is matched with the motor swash plate support through spherical surface contact, the motor swash plate is limited in contact with the motor eccentric support through the upper and lower circular arc structures, the center line of the upper and lower circular arcs passes through the ball center of the contact spherical surface of the motor swash plate and the motor swash plate support, and the motor swash plate can only rotate around the center line of the upper and lower circular arcs; The motor ball socket tray is arranged in the motor swash plate through a bearing, the bearing retainer is sleeved on the driving main shaft and limited by the bearing retainer arranged on the driving main shaft, the bearing retainer is arranged on the motor swash plate support through a bearing, and the bearing retainer on the bearing retainer and the bearing retainer on the motor swash plate support are located on both sides of the bearing; The motor cylinder is arranged on the motor eccentric support through a bearing, the ball head on the motor plunger is in contact with the ball socket on the motor ball socket tray, the motor eccentric support is provided with a cavity eccentric to the rotation axis of the motor cylinder, the motor eccentric ring is arranged in the eccentric cavity, and the axial position of the motor eccentric ring is located at the axial position of the motor distribution valve. One end of the drive housing is arranged on the pump cylinder body through a bearing, and the other end of the drive housing is arranged on the drive spindle through a bearing, the bearing is limited by a check ring arranged on the drive spindle, the pump ball socket tray is arranged in the drive housing through a bearing, and the rotary axis of the pump ball socket tray is at an angle with the rotary axis of the drive spindle, the ball head on the pump plunger is in contact with the ball socket on the pump ball socket tray, a cavity eccentric to the rotary axis of the pump cylinder body is arranged on the drive housing, the pump eccentric ring is arranged in the eccentric cavity, and the axial position of the pump eccentric ring is located at the axial position of the pump distribution valve, a drive gear is arranged on the drive housing, the drive housing and the drive gear are limited and driven through a pin shaft, and then fastened through a screw; The drive housing is rotatably arranged on the right end plate through a bearing, and the bearing is located in the right large bearing cavity; the drive spindle is rotatably arranged on the right end plate through a bearing, and the bearing is located in the right small bearing cavity; the motor swash plate support is positioned and arranged on the left end plate through the left bearing cavity, and the circumferential rotation of the motor swash plate support is limited through a support pin shaft, and then the motor swash plate support and the left end plate are fastened through a screw arranged in the left support mounting hole; the drive spindle passes through the left end plate, and an oil seal is arranged between the left end plate and the drive spindle, and the oil seal is arranged in the left oil seal cavity.

14. The hydromechanical continuously variable transmission test apparatus according to claim 1, wherein the servo control device comprises an optical encoder, an encoder bracket, a servo countershaft, a servo pinion, a servo main shaft, a servo bevel gear, a servo nut, a servo carrier, an outer ring positioning pin, a servo sun gear, a servo motor, a servo planet gear, and a servo outer ring. The servo countershaft is arranged on the servo side plate through a bearing, the bearing is located in the countershaft cavity, an oil seal is arranged between the servo countershaft and the servo side plate, a manual control mechanism is arranged at one end of the servo countershaft, and an optical encoder is also arranged at the end, the optical encoder is fixedly arranged on the servo side plate through an encoder support, the shaft of the optical encoder is connected with the servo countershaft, a countershaft bevel gear is arranged at the other end of the servo countershaft, the relative position of the adjustable countershaft bevel gear on the servo countershaft can be adjusted and fastened through a screw, one end of the servo main shaft is arranged on the motor eccentric support through a bearing, the other end of the servo main shaft is arranged on the motor swash plate support through a bearing, a servo nut is movably arranged on the servo main shaft between the two bearings, a main bevel gear is arranged at one end of the servo main shaft, the axial position of the main bevel gear on the servo main shaft can be adjusted by changing the thickness of a check ring, a servo carrier is arranged at the other end of the servo main shaft, an oil seal is arranged between the servo main shaft and the motor swash plate support, a servo outer gear ring is arranged in the servo gear cavity, and the circumferential rotation of the servo outer gear ring is limited by an outer gear ring positioning pin arranged in a limiting pin slot of the servo gear cavity, a servo planetary gear is arranged on the servo carrier, a servo motor is arranged on the left end plate and fastened through a screw screwed into a motor screw hole, the rotation center of the driving shaft of the servo motor and the rotation center of the servo main shaft are coaxially arranged, a servo sun gear is arranged on the driving shaft of the servo motor, the servo motor drives the servo planetary gear to rotate through the servo sun gear, thereby driving the servo main shaft to rotate, the rotating servo main shaft drives the servo nut to move, the moving servo nut drives the motor swash plate to rotate, the servo main shaft drives the countershaft bevel gear through the main bevel gear, thereby driving the servo countershaft to rotate, the rotation amount of the servo countershaft is collected by the optical encoder and fed back to the control system, so that the inclination angle of the motor swash plate is obtained; after the servo motor is powered off, the servo countershaft can be manually operated to drive the servo main shaft to rotate through the countershaft bevel gear and the main bevel gear, thereby driving the servo nut to move.

15. The hydromechanical continuously variable transmission test apparatus according to claim 1, characterized by The power motor drives the driving gear through the input torque speed sensor, the driving shaft and the driving gear, thereby driving the driving shell to rotate. When the motor swash plate controls the support ball socket end surface of the motor ball socket tray to be perpendicular to the rotation axis of the drive spindle, it is recorded as zero position state, the power of the drive housing drives the pump plunger through the pump ball socket tray, and then drives the pump cylinder body to rotate, the power of the pump cylinder body is directly output by pure mechanical transmission of the drive spindle, at this time, the pump plunger, motor plunger, motor ball socket tray, pump flow distribution valve, motor flow distribution valve move circumferentially with the pump cylinder body, motor cylinder and flow distribution cylinder body, the pump plunger and motor plunger have no axial movement, the pump flow distribution valve has no radial movement, the motor flow distribution valve moves radially under the action of the motor eccentric ring, and the motor plunger in the plunger hole in the high pressure oil area is simultaneously oil distributed, when the support ball socket end surface is perpendicular to the axis, the pure mechanical transmission is theoretical constant speed transmission, in the actual transmission process, affected by internal leakage, the pure mechanical transmission of the zero position state is non-full constant speed transmission, and speed difference will be generated due to leakage, in order to make up for internal leakage and realize theoretical constant speed transmission, the support ball socket end surface of the motor ball socket tray and the rotation axis of the drive spindle form a certain angle state of self-adaptive leakage compensation; When the motor swash plate controls the support ball socket end surface of the motor ball socket tray to be perpendicular to the rotation axis of the drive spindle, it is recorded as zero position state, the power of the drive housing drives the pump plunger through the pump ball socket tray, and then drives the pump cylinder body to rotate, the power of the pump cylinder body is directly output by pure mechanical transmission of the drive spindle, at this time, the pump plunger, motor plunger, motor ball socket tray, pump flow distribution valve, motor flow distribution valve move circumferentially with the pump cylinder body, motor cylinder and flow distribution cylinder body, the pump plunger and motor plunger have no axial movement, the pump flow distribution valve has no radial movement, the motor flow distribution valve moves radially under the action of the motor eccentric ring, and the motor plunger in the plunger hole in the high pressure oil area is simultaneously oil distributed, when the support ball socket end surface is perpendicular to the axis, the pure mechanical transmission is theoretical constant speed transmission, in the actual transmission process, affected by internal leakage, the pure mechanical transmission of the zero position state is non-full constant speed transmission, and speed difference will be generated due to leakage, in order to make up for internal leakage and realize theoretical constant speed transmission, the support ball socket end surface of the motor ball socket tray and the rotation axis of the drive spindle form a certain angle state of self-adaptive leakage compensation; When the motor swash plate controls the support ball socket end surface of the motor ball socket tray to be perpendicular to the rotation axis of the drive spindle, it is recorded as zero position state, the power of the drive housing drives the pump plunger through the pump ball socket tray, and then drives the pump cylinder body to rotate, the power of the pump cylinder body is directly output by pure mechanical transmission of the drive spindle, at this time, the pump plunger, motor plunger, motor ball socket tray, pump flow distribution valve, motor flow distribution valve move circumferentially with the pump cylinder body, motor cylinder and flow distribution cylinder body, the pump plunger and motor plunger have no axial movement, the pump flow distribution valve has no radial movement, the motor flow distribution valve moves radially under the action of the motor eccentric ring, and the motor plunger in the plunger hole in the high pressure oil area is simultaneously oil distributed, when the support ball socket end surface is perpendicular to the axis, the pure mechanical transmission is theoretical constant speed transmission, in the actual transmission process, affected by internal leakage, the pure mechanical transmission of the zero position state is non-full constant speed transmission, and speed difference will be generated due to leakage, in order to make up for internal leakage and realize theoretical constant speed transmission, the support ball socket end surface of the motor ball socket tray and the rotation axis of the drive spindle form a certain angle state of self-adaptive leakage compensation; When the motor swash plate controls the support ball socket end surface of the motor ball socket tray to be perpendicular to the rotation axis of the drive spindle, it is recorded as zero position state, the power of the drive housing drives the pump plunger through the pump ball socket tray, and then drives the pump cylinder body to rotate, the power of the pump cylinder body is directly output by pure mechanical transmission of the drive spindle, at this time, the pump plunger, motor plunger, motor ball socket tray, pump flow distribution valve, motor flow distribution valve move circumferentially with the pump cylinder body, motor cylinder and flow distribution cylinder body, the pump plunger and motor plunger have no axial movement, the pump flow distribution valve has no radial movement, the motor flow distribution valve moves radially under the action of the motor eccentric ring, and the motor plunger in the plunger hole in the high pressure oil area is simultaneously oil distributed, when the support ball socket end surface is perpendicular to the axis, the pure mechanical transmission is theoretical constant speed transmission, in the actual transmission process, affected by internal leakage, the pure mechanical transmission of the zero position state is non-full constant speed transmission, and speed difference will be generated due to leakage, in order to make up for internal leakage and realize theoretical constant speed transmission, the support ball socket end surface of the motor ball socket tray and the rotation axis of the drive spindle form a certain angle state of self-adaptive leakage compensation; When the power motor is reduced in speed and the driving main shaft is dragged by load, the machine-oil hybrid transmission part can be dragged in reverse at three speeds, namely, pure mechanical transmission, reduced speed and increased speed.

16. A test method of a machine-fluid hybrid continuously variable transmission, which is used for the machine-fluid hybrid continuously variable transmission test device according to claim 1, characterized by, The test of zero load basic parameters, the control system controls the load device to be in a zero load state, and controls the constant pressure oil supply of the oil supplement pump station to the machine-oil hybrid transmission part. When the oil is supplied, the data feedback of the pressure sensor is collected to correct the output pressure of the oil supplement pump station to the set pressure of the control system. After the oil is supplemented to the pump cylinder, the flow cylinder and the motor cylinder, the supplemented oil flows out through the flow channel arranged on the driving main shaft. The control system records the supplemented oil flow through the flowmeter when the power motor is not driven, which is recorded as the supplemented oil flow L1. The control system controls the servo control device to make the machine-oil hybrid transmission part in the constant speed transmission state. The control system controls the power motor to rotate and output until the rated speed N1 of the machine-oil hybrid transmission part in the constant speed transmission state. During the acceleration process, the control system records the change of the supplemented oil flow through the flowmeter and records the supplemented oil flow at the rated speed, which is recorded as the supplemented oil flow L2. During the acceleration process of the control motor, the control system collects the data feedback of the input torque speed sensor and the output torque speed sensor, and then obtains the transmission resistance torque at the rated speed, which is recorded as the empty load transmission resistance torque M1. The oil return position at the bottom of the box is in the lowest state, and the machine-oil hybrid transmission part can be regarded as having no stirring oil resistance torque. The oil return pipeline is connected to different oil discharge holes, and then different oil return positions at the bottom of the box are obtained. The data feedback of the input torque speed sensor and the output torque speed sensor is collected and recorded at different oil return positions, so that the stirring oil resistance torque M2 at different oil return positions is obtained. In the state of each different oil return position, the control system controls the servo control device to change the inclination state of the motor swash plate from the maximum positive angle to the maximum negative angle. The control system collects the data feedback of the optical encoder, the input torque speed sensor and the output torque speed sensor in real time, and then records the dynamically changing stirring oil resistance torque M3 in the change process.

17. A test method of a machine-fluid hybrid continuously variable transmission, which is used for the machine-fluid hybrid continuously variable transmission test device according to claim 1, characterized by, The test of inertia load acceleration and deceleration characteristics sets the load device as an inertia load, the control system controls the servo control device to change the tilt state of the motor swash plate to the maximum positive angle, and the machine and liquid hybrid transmission part is in the maximum deceleration transmission ratio state. The control system sets different linear acceleration and non-linear acceleration of the power motor, and then drives the inertia load to accelerate. After the acceleration is completed at the maximum positive angle, the control system controls the servo control device to rotate the motor swash plate from the maximum positive angle to zero position, and then rotates from zero position to the maximum negative angle. The change mode of the motor swash plate from the maximum positive angle to zero position and from zero position to the maximum negative angle is adjustable. Conversely, the control system controls the servo control device to rotate the motor swash plate from the maximum negative angle to zero position, and then rotates from zero position to the maximum positive angle. After the servo control device completes the deceleration of the inertia load, the control system sets different linear deceleration and non-linear deceleration of the power motor, and then drives the inertia load to decelerate. In this process, the control system collects the data feedback of the photoelectric encoder, flowmeter, input torque speed sensor and output torque speed sensor in real time. In the acceleration process, the oil supplement flow corresponding to each state is recorded as L3, the input torque is recorded as M4, the output torque is recorded as M5, the input speed is recorded as N2, and the output speed is recorded as N3. The data is recorded and analyzed in combination with the data in the zero load basic parameter test to analyze the transmission characteristics under different inertia load conditions and different acceleration and deceleration conditions. The total transmission efficiency can be calculated from M4, M5, N2 and N3. The volume efficiency can be calculated from L2, L3 and N3. The mechanical efficiency can be calculated from the total efficiency and the volume efficiency. Conversely, the calculation method of the deceleration process is also the same.

18. A test method of a machine-fluid hybrid continuously variable transmission, which is used for the machine-fluid hybrid continuously variable transmission test device according to claim 1, characterized by, The test of constant power output dynamic characteristics controls the power motor to output the drive machine and liquid hybrid transmission part to obtain the rated speed and rated power in zero position. When the load increases, the control system dynamically adjusts the servo control device to control the output speed of the machine and liquid hybrid transmission part according to the data feedback of the input torque speed sensor and the output torque speed sensor, and then increases the deceleration transmission ratio or reduces the acceleration transmission ratio of the machine and liquid hybrid transmission part to output the corresponding load driving torque, so that the current speed and load torque correspond to the constant output power of the power motor. When the load decreases, the control system dynamically adjusts the servo control device to control the output speed of the machine and liquid hybrid transmission part according to the data feedback of the input torque speed sensor and the output torque speed sensor, and then reduces the deceleration transmission ratio or increases the acceleration transmission ratio of the machine and liquid hybrid transmission part to output the corresponding load driving torque, so that the current speed and load torque correspond to the constant output power of the power motor. Then, the dynamic characteristics are analyzed according to the collected data.

19. A test method of a machine-fluid hybrid continuously variable transmission, which is used for the machine-fluid hybrid continuously variable transmission test device according to claim 1, characterized by, The test of constant speed output dynamic characteristic is as follows: the control system controls the power motor and the servo control device to make the machine fluid hybrid transmission part output at a constant speed with optimal matching power loss, controls the load of the load device to linearly or nonlinearly change at different slopes, when the load increases, the control system dynamically adjusts the servo control device and the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, increases the output power and speed of the power motor, and increases the reduction transmission ratio of the machine fluid hybrid transmission part or reduces the step-up transmission ratio of the machine fluid hybrid transmission part through the servo control device, so as to balance the speed rise caused by the increase of the output power of the power motor, and to obtain the optimal matching power loss constant speed output driving when the load increases; when the load decreases, the control system dynamically adjusts the servo control device and the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, reduces the output power and speed of the power motor, and reduces the reduction transmission ratio of the machine fluid hybrid transmission part or increases the step-up transmission ratio of the machine fluid hybrid transmission part through the servo control device, so as to balance the speed drop caused by the reduction of the output power of the power motor, and to obtain the optimal matching power loss constant speed output driving when the load decreases, and then the dynamic characteristic is analyzed according to the collected data record.

20. A test method of a machine-fluid hybrid continuously variable transmission, which is used for the machine-fluid hybrid continuously variable transmission test device according to claim 1, characterized by, The test of constant torque output dynamic characteristic is as follows: the control system controls the power motor and the servo control device to make the machine fluid hybrid transmission part output at a constant torque with optimal matching power loss, controls the servo control device to make the speed of the machine fluid hybrid transmission part linearly or nonlinearly change at different slopes, when the reduction transmission ratio of the machine fluid hybrid transmission part reduces or the step-up transmission ratio of the machine fluid hybrid transmission part increases, the control system dynamically adjusts the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, and increases the output power and speed of the power motor, the increased power of the power motor corresponds to the sum of the rising speed of the power motor and the increasing speed of the machine fluid hybrid transmission part, so as to obtain the optimal matching power loss constant torque output driving when the speed increases; when the reduction transmission ratio of the machine fluid hybrid transmission part increases or the step-up transmission ratio of the machine fluid hybrid transmission part reduces, the control system dynamically adjusts the power motor according to the data feedback of the input torque speed sensor and the output torque speed sensor, and reduces the output power and speed of the power motor, the reduced power of the power motor corresponds to the sum of the reducing speed of the power motor and the reducing speed of the machine fluid hybrid transmission part, so as to obtain the optimal matching power loss constant torque output driving when the speed reduces, and then the dynamic characteristic is analyzed according to the collected data record.

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