CN107607329A - Series parallel type hydraulic hybrid dynamic automobile simulation test stand - Google Patents

Abstract

The present invention provides a kind of series parallel type hydraulic hybrid dynamic automobile simulation test stand, is related to automobile technical field, including stand in kind and real-time emulation system.By controlling the combination that clutch, brake are different in stand in kind, single planetary row configuration can be simulated respectively and preceding planet row+heel row motor increases the series parallel type hydraulic hybrid dynamic automobile for turning round configuration, and every kind of configuration can be achieved engine and open machine pattern, pure hydraulic-driven pattern, joint drive pattern, braking mode and reversing mode.Testing stand provided by the invention can reduce research and development testing expense and the time of series parallel type hydraulic hybrid dynamic automobile, improve simulation accuracy, while can also improve the versatility of hydraulic hybrid dynamic automobile testing stand, reduce integrated cost.

Description

Hybrid hydraulic hybrid vehicle simulation test bench

technical field

The invention relates to an automobile test bench, more precisely, the invention relates to a simulation test bench for a hybrid hydraulic hybrid vehicle.

Background technique

Hybrid technology is an energy-saving solution that has been widely recognized at present. According to different power sources, hybrid vehicles are divided into oil-electric hybrid and hydraulic hybrid. Hybrid vehicle energy storage devices require the ability to recover and release a large amount of power in a short period of time. Due to the low power density of the battery, the application of the battery with a large mass such as passenger cars and trucks is limited; the power density of the hydraulic accumulator is high. It is widely used in passenger cars, heavy commercial vehicles and other fields. The hybrid hydraulic hybrid electric vehicle can achieve double decoupling of the torque and speed of the engine and the wheel through the planetary gear coupling mechanism, flexibly adjust the working point of the power source according to the working conditions, and has a high overall efficiency. Therefore, the research on this hybrid form Gradually increasing, the results are also increasingly rich. For example, the Chinese patent publication number is CN 102514474 A, and the publication date is 2012-06-27, which discloses a hybrid hydraulic hybrid vehicle power system, which combines the advantages of series and parallel systems, and can be adjusted by a power split device The engine operating point is stable in the economic zone, achieving the goals of low emissions and low fuel consumption.

The hydraulic hybrid electric vehicle is a relatively complex electromechanical-hydraulic integrated system. In the early stage of vehicle development, if the vehicle is directly built for real vehicle test, the cost and development cycle will be greatly increased; it is difficult to fully reflect the full use of computer simulation. Due to the characteristics of system components, the results are quite different from the actual ones. Therefore, in the preliminary research and development of hybrid electric vehicles, it is very necessary to develop a method that integrates computer technology for hardware-in-the-loop test simulation. In the semi-physical test simulation, the key components of the system that need to explore some characteristics are used in kind, and the known characteristics or performance of the components that have little influence on the test results are replaced by simulation software to build mathematical models or graphical physical models. The real-time simulator is used as a carrier to download the model into it, and at the same time, the controller is used to control the physical components of the system and collect system status signals. Therefore, it is of great practical application value to develop a simulation test bench suitable for hybrid hydraulic hybrid vehicles. The Chinese patent publication number is CN104535337 A, and the publication date is 2015-04-22, which discloses a hydraulic hybrid power simulation test bench, which can simulate road loads in different working conditions, by controlling the state of valve group and pump/motor , to realize the switching of various modes such as hydraulic drive, combined drive, and regenerative braking. The test cost is low and it is not limited by environmental conditions. However, the test bench can only simulate a series hydraulic hybrid vehicle, and the test bench uses a large number of hydraulic valves. Group, the structure is complex, and the efficiency of the hydraulic system is relatively low.

Contents of the invention

The invention provides a simulation test bench for a hybrid hydraulic hybrid vehicle, which can overcome the disadvantages of high cost, time-consuming and inaccurate computer simulation in the development and testing of a hybrid hydraulic hybrid vehicle in the prior art. The power system configuration that can be simulated by the hydraulic hybrid vehicle simulation test bench in the prior art is single and has the disadvantages of poor versatility.

In order to solve the above problems, the present invention adopts the following technical solution: the simulation test bench for hybrid hydraulic hybrid electric vehicle includes a physical bench and a real-time simulation system.

The physical platform includes a motor, a first two-position two-way electromagnetic directional valve, a second two-position two-way electromagnetic directional valve, a third two-position two-way electromagnetic directional valve, a front planetary row, a rear planetary row, Front planetary input shaft, front planetary input gear, rear planetary input shaft, rear planetary input gear, first hydraulic pump/motor, second hydraulic pump/motor, DC dynamometer, high pressure accumulator, low pressure accumulator energy, the first coupling, the second coupling, the third coupling, the fourth coupling, the fifth coupling, the sixth coupling, the seventh coupling, the eighth coupling , C1 clutch, C2 clutch, C3 brake, first meshing gear, second meshing gear, hydraulic control check valve, first hydraulic pipeline, second hydraulic pipeline, first pressure sensor, second pressure sensor, first speed A torque sensor, a second rotational speed torque sensor, a third rotational speed torque sensor, a fourth rotational speed torque sensor, and a torsional shock absorber.

The front planetary row is set on the front planetary row input shaft. The front planetary row includes the front planetary row sun gear, the front planetary row carrier, the front planetary row ring gear and four front planetary row planetary gears with the same structure. The front planetary row The sun gear is integrated with the input gear of the front planetary row, and the input gear of the front planetary row is constantly meshed with the second meshing gear; the rear planetary row is set on the input shaft of the rear planetary row, and the rear planetary row includes the rear planetary row sun wheel, rear planetary planet carrier, rear planetary ring gear and four rear planetary planetary gears with the same structure, the rear planetary sun gear and the rear planetary input gear are integrated, and the rear planetary input gear and the first meshing gear Constant mesh connection.

The a-end of the C1 clutch is coaxially connected with the rear planetary row input shaft, and the b-end is coaxially fixedly connected with the rear planetary row carrier; the a-end of the C2 clutch is coaxially fixedly connected with the rear planetary row input gear , the b end is coaxially connected with the rear planetary row input shaft; the fixed end of the C3 brake is fixedly connected with the frame, and the rotating end is coaxially connected with the rear planetary row ring gear.

The P port and the A port of the first two-position two-way electromagnetic reversing valve are respectively connected with the second hydraulic pipeline and the K port (control port) of the hydraulic control check valve; The P port and A port of the reversing valve are respectively connected with the second hydraulic pipeline and the P2 port of the hydraulic control check valve, and the P1 port of the hydraulic control check valve is connected with the a port of the second hydraulic pump/motor; The P port and the A port of the three-two-two-way electromagnetic reversing valve are respectively connected with the second hydraulic pipeline and the a port of the first hydraulic pump/motor; the oil outlet of the high-pressure accumulator is connected with the second hydraulic pipeline , the oil outlet of the low-pressure accumulator is connected to the first hydraulic pipeline; the b port of the first hydraulic pump/motor and the b port of the second hydraulic pump/motor are both connected to the first hydraulic pipeline.

The real-time simulation system is composed of a controller, a dSPACE simulator and an upper computer; the controller is connected to the physical platform through wires, the controller is connected to the dSPACE simulator through wires, and the upper computer is connected to the dSPACE simulator through an Ethernet cable.

The connection between the controller and the physical platform through wires described in the technical solution refers to:

The first pressure sensor, the second pressure sensor, the first rotational speed torque sensor, the second rotational speed torque sensor, the third rotational speed torque sensor, and the fourth rotational speed torque sensor are respectively connected with the controller through electric wires in the described physical platform. EAD00 terminal, EAD01 terminal, EAD02 terminal, EAD03 terminal, EAD04 terminal, EAD05 terminal connection; the control terminal of the motor in the physical bench, the displacement control terminal of the first hydraulic pump/motor, the second hydraulic pump/motor Displacement control terminal, C1 clutch control terminal, C2 clutch control terminal, C3 brake control terminal, control terminal of the first two two-way electromagnetic reversing valve, control of the second two two-way electromagnetic reversing valve terminal, the control terminal of the third two-position two-way electromagnetic reversing valve and the control terminal of the DC dynamometer are respectively connected to the LA00 terminal, LA01 terminal, LA02 terminal, LA03 terminal, LA04 terminal, LA05 terminal and LA06 terminal of the controller through wires. , LA07 terminal, LA08 terminal, LA09 terminal connection.

The left and right ends of the first rotational speed torque sensor described in the technical solution are coaxially connected with the motor and the torsional damper respectively through the first coupling and the second coupling, and the torsional damper is connected with the front planetary planet carrier The input shaft of the front planetary row is connected coaxially; the left and right ends of the second rotational speed torque sensor are respectively coaxially connected with the rear planetary row carrier and the DC dynamometer through the third coupling and the fourth coupling; The left and right ends of the speed torque sensor are coaxially connected with the first hydraulic pump/motor and the first meshing gear respectively through the fifth coupling and the sixth coupling; the left and right ends of the fourth speed torque sensor are connected through the eighth coupling The device and the seventh coupling are respectively coaxially connected with the second hydraulic pump/motor and the second meshing gear.

The first pressure sensor described in the technical solution is installed on the second hydraulic pipeline, and the second pressure sensor is installed on the first hydraulic pipeline; the input shaft of the front planetary row is vertically coaxial with the circumferential surface of the front planetary row carrier Fixed connection; the front planetary ring gear is coaxially fixed with the rear planetary row input shaft.

Compared with prior art, the beneficial effects of the present invention are:

1. The hybrid hydraulic hybrid vehicle simulation test bench of the present invention is used in the research and development stage of the hybrid hydraulic hybrid vehicle, which can improve the research and development efficiency and shorten the research and development cycle.

2. The hybrid hydraulic hybrid vehicle simulation test bench of the present invention is suitable for development tests of hybrid hydraulic hybrid vehicles with different planetary gear coupling mechanism structures, has certain versatility, and can reduce test costs.

3. The hybrid hydraulic hybrid vehicle simulation test bench of the present invention can simulate the operating conditions of the real vehicle and the different operating states of the hybrid hydraulic hybrid vehicle. Compared with pure software simulation, the authenticity of the test is improved with accuracy.

Description of drawings

The present invention will be further described below in conjunction with accompanying drawing:

Fig. 1 is a schematic composition diagram of the structure of a hybrid hydraulic hybrid vehicle simulation test bench according to the present invention;

Fig. 2 is a schematic composition diagram of the physical bench structure in the hybrid hydraulic hybrid vehicle simulation test bench of the present invention;

Fig. 3 is the state diagram of C1 clutch, C2 clutch, C3 brake when the parallel hydraulic hybrid vehicle simulation test bench of the present invention simulates the single planetary row configuration of the hybrid hydraulic hybrid vehicle;

Fig. 4 is the C3 brake state diagram when the parallel hydraulic hybrid electric vehicle simulation test bench of the present invention simulates the parallel hydraulic hybrid electric vehicle of the front planetary row + rear row motor torque increasing configuration;

In Fig. 1, Ⅰ. physical platform, Ⅱ. real-time simulation system, 37. controller, 42. dSPACE simulator, 43. upper computer;

In Fig. 2, 1. motor, 2. first shaft coupling, 3. first rotational speed torque sensor, 4. second shaft coupling, 5. torsional shock absorber, 6. front planetary row input gear, 7. Front planetary sun gear, 8. Front planetary carrier, 9. Front planetary ring gear, 10. Front planetary input shaft, 11. Rear planetary input shaft, 12. Rear planetary input gear, 13. Rear planet Sun gear, 14. Rear planetary planetary gear, 15. Rear planetary ring gear, 16. Rear planetary planet carrier, 17. C1 clutch, 18. C2 clutch, 19. Third coupling, 20. Second Speed torque sensor, 21. Fourth coupling, 22. DC dynamometer, 23. First hydraulic pump/motor, 24. Fifth coupling, 25. Third speed torque sensor, 26. Sixth Coupling, 27. First meshing gear, 28. Second meshing gear, 29. Seventh coupling, 30. Fourth rotational speed torque sensor, 31. Eighth coupling, 32. Second hydraulic pump/ Motor, 33. High pressure accumulator, 34. Low pressure accumulator, 35. First hydraulic pipeline, 36. Second hydraulic pipeline, 37. Controller, 38. Hydraulic control check valve, 39. The first two two Through electromagnetic reversing valve, 40. The first pressure sensor, 41. The second pressure sensor, 44. Front planetary planetary gear, 45. C3 brake, 46. The second two-position two-way electromagnetic reversing valve, 47. The third Two-position two-way electromagnetic reversing valve.

detailed description

The present invention is described in detail below in conjunction with accompanying drawing:

Referring to accompanying drawing 1, the parallel type hydraulic hybrid vehicle simulation test bench of the present invention comprises physical bench I and real-time simulation system II; Described real-time simulation system II is composed of controller 37, dSPACE simulator 42 and host computer 43 poses.

The dSPACE simulator 42 is a multifunctional platform integrating control system design, performance testing and hardware-in-the-loop simulation, including hardware and software. Among them, the hardware part mainly refers to the data information processing board and hardware interface, which is mainly used for the operation of the real-time simulation program, signal transmission, and interrupts when necessary; the software part includes the control software ControlDesk and the analog hardware interface RTI. ControlDesk is installed in the host computer 43, and is used for registering the control board and visually managing the system, and real-time regulation of the vehicle physical model in the dSPACE simulator 42. RTI converts the connection relationship between the control algorithm in the simulation model and the vehicle mathematical model into the I/O relationship in the RTI library, and sets its corresponding parameters.

The model of the controller 37 is HY-TTC200-CD-538K-2.4M-WD00-000. This controller is 32 controllers, has 448KBFLASH, 26KBRAM, two-way CAN, one-way LIN and RS-232 interface; The software part MPC555 of controller 37 and TTCDownloader are installed in host computer 43 together with simulation software MATLAB/Simulink, in MATLAB The test bench control algorithm built in /Simulink is compiled to generate a .s19 format code file, which is burned into the controller 37 through TTCDownloader. The AD port of the controller 37 is connected with the DA port of the dSPACE simulator 42 through wires, so that the analog signal of the vehicle physical model in the dSPACE simulator 42 is transmitted to the controller 37 and the output control signal of the controller 37 is accepted.

Referring to accompanying drawing 2, described physical platform 1 comprises motor 1, the first two-position two-way electromagnetic reversing valve 39, the second two-position two-way electromagnetic reversing valve 46, the third two-position two-way electromagnetic reversing valve 47. Front planetary row, rear planetary row, front planetary row input shaft 10, front planetary row input gear 6, rear planetary row input shaft 11, rear planetary row input gear 12, first hydraulic pump/motor 23, second hydraulic pump / Motor 32, DC dynamometer 22, high-voltage accumulator 33, low-pressure accumulator 34, first coupling 2, second coupling 4, third coupling 19, fourth coupling 21, Fifth coupling 24, sixth coupling 26, seventh coupling 29, eighth coupling 31, C1 clutch 17, C2 clutch 18, C3 brake 45, first meshing gear 27, second meshing gear 28. Hydraulic control check valve 38, first hydraulic pipeline 35, second hydraulic pipeline 36, first pressure sensor 40, second pressure sensor 41, first rotational speed torque sensor 3, second rotational speed torque sensor 20, first The third rotational speed torque sensor 25 , the fourth rotational speed torque sensor 30 , and the torsional shock absorber 5 .

Referring to accompanying drawing 2, described controller 37 monitors and sends control commands to the running state of physical platform I, and is used to control the torque speed of motor 1, the combination and separation of C1 clutch 17, C2 clutch 18 and C3 brake 45, The displacement values of the first hydraulic pump/motor 23 and the second hydraulic pump/motor 32, the load or loading torque and the rotational speed of the DC dynamometer 22, the first two-position two-way electromagnetic reversing valve 39, the second two-position two-way The opening and closing of the electromagnetic reversing valve 46 and the second two-position two-way electromagnetic reversing valve 47. The first pressure sensor 40, the second pressure sensor 41, the first rotational speed torque sensor 3, the second rotational speed torque sensor 20, the 3rd rotational speed torque sensor 25, the 4th rotational speed torque sensor in the described physical platform I 30 are respectively connected with the EAD00 terminal, EAD01 terminal, EAD02 terminal, EAD03 terminal, EAD04 terminal, EAD05 terminal of the controller 37 through wires; the control terminal of the motor 1, the displacement control terminal of the first hydraulic pump/motor 11, the second hydraulic pressure The displacement control terminal of the pump/motor 16, the control terminal of the C1 clutch 17, the control terminal of the C2 clutch 18, the control terminal of the C3 brake 45, the control terminal of the first two-position two-way electromagnetic reversing valve 39, the second two-position The control terminal of the two-way electromagnetic reversing valve 46, the control terminal of the third two-position two-way electromagnetic reversing valve 47 and the control terminal of the DC dynamometer 22 are respectively connected with the LA00 terminal, LA01 terminal, LA02 terminal, LA03 terminal, LA04 terminal, LA05 terminal, LA06 terminal, LA07, LA08, LA09 terminal connection.

Referring to accompanying drawing 2, the front planetary row is set on the front planetary row input shaft 10, and the front planetary row includes the front planetary row sun gear 7, the front planetary row carrier 8, the front planetary row ring gear 9 and four front planetary rows with the same structure Planetary gear 44, four front planetary planetary gears 44 with the same structure are evenly distributed on the circumference of the equiradius apart from the axis of rotation of the front planetary planet carrier 8, the two are connected in rotation, and the axis of rotation of each front planetary planetary gear 44 Parallel to the rotation axis of the front planetary planet carrier 8, the outer sides of each front planetary planetary gear 44 mesh with the internal teeth of the front planetary ring gear 9, and the inner sides of each front planetary planetary gear 44 engage with the front planetary sun gear 7 Engagement: the front planetary row sun gear 7 is integrated with the front planetary row input gear 6, and the front planetary row input gear 6 is constantly meshed with the second meshing gear 28. The rear planetary row is set on the rear planetary row input shaft 11. The rear planetary row includes a rear planetary row sun gear 13, a rear planetary row carrier 16, a rear planetary row ring gear 15 and four rear planetary row planetary gears 14 with the same structure. Four rear planetary row planet wheels 14 with the same structure are evenly distributed on the circumference of the equiradius apart from the rear planetary row planet carrier 16 axis of rotation, and the two are connected in rotation. The axis of rotation of the frame 16 is parallel, the outer side of each rear planetary row planetary gear 14 meshes with the internal teeth of the rear planetary row ring gear 15, and the inner side of each rear planetary row planetary wheel 14 meshes with the rear planetary row sun gear 13; The sun gear 13 is integrated with the rear planetary input gear 12 , and the rear planetary input gear 12 is in constant mesh connection with the first meshing gear 27 . The front planetary row input shaft 10 is vertically coaxially connected with the peripheral surface of the front planetary row carrier 8 , and the front planetary row ring gear 9 is coaxially fixedly connected with the rear planetary row input shaft 11 .

Referring to accompanying drawing 2, the a end of C1 clutch 17 is coaxially connected with the rear planetary row input shaft 11, and the b end is coaxially fixedly connected with the rear planetary row carrier 16; the a end of C2 clutch 18 is connected with the rear planetary row input gear 12 The coaxial fixed connection, the b end is coaxially fixed with the rear planetary row input shaft 11; The rear planetary input shaft 11 and the rear planetary carrier 16 are fixedly connected or completely separated through the C1 clutch 17, and the rear planetary input shaft 11 and the rear planetary input gear 12 are fixedly connected or completely separated through the C2 clutch 18. The rear planetary The ring gear 15 and the frame are fixedly connected or completely separated through the C3 brake 45 .

Referring to accompanying drawing 2, the P port, the A port of the first two-position two-way electromagnetic reversing valve 39 are respectively connected with the second hydraulic pipeline 36, the K port (control port) of the hydraulic control check valve 38; The P port and the A port of the electromagnetic reversing valve 46 are respectively connected with the second hydraulic pipeline 36 and the P2 port of the hydraulic control check valve 38, and the P1 port of the hydraulic control check valve 38 is connected with the a port of the second hydraulic pump/motor 32. port connection; the P port and the A port of the third two-position two-way electromagnetic reversing valve 47 are respectively connected with the second hydraulic pipeline 36 and the a port of the first hydraulic pump/motor 23; the oil outlet of the high-pressure accumulator 33 is connected with the The second hydraulic pipeline 36 is connected, and the oil outlet of the low pressure accumulator 34 is connected with the first hydraulic pipeline 35; the b port of the first hydraulic pump/motor 23 and the b port of the second hydraulic pump/motor 32 are all connected with the first hydraulic pressure The pipe 35 is connected.

Referring to accompanying drawing 2, the left and right ends of the first rotation speed torque sensor 3 are respectively coaxially connected with the motor 1 and the torsional vibration damper 5 through the first shaft coupling 2 and the second shaft coupling 4, and the torsional vibration damper 5 and the The front planetary planetary carrier 8 is coaxially connected through the front planetary row input shaft 10; the left and right ends of the second rotational speed torque sensor 20 are respectively connected to the rear planetary row planetary carrier 16 through the third coupling 19 and the fourth coupling 21. , DC dynamometer 22 are coaxially connected; the left and right ends of the third rotational speed torque sensor 25 are connected with the first hydraulic pump/motor 23 and the first meshing gear 27 respectively through the fifth coupling 24 and the sixth coupling 26 Shaft connection: the left and right ends of the fourth rotational speed torque sensor 30 are coaxially connected with the second hydraulic pump/motor 32 and the second meshing gear 28 through the eighth coupling 31 and the seventh coupling 29 respectively. The first pressure sensor 40 is installed on the second hydraulic pipeline 36 , and the second pressure sensor 41 is installed on the first hydraulic pipeline 35 .

Referring to accompanying drawing 2, according to the control signal of the controller 37, the DC dynamometer 22 can not only provide external loads to simulate the road input of the car in the driving mode, but also provide external power to simulate the road input of the car in the braking mode. .

The hybrid hydraulic hybrid vehicle simulation test bench of the present invention can simulate the working states of the hybrid hydraulic hybrid vehicles with different planetary gear configurations in different modes, and will be described in detail below in conjunction with accompanying drawing 3:

Referring to accompanying drawing 3, the simulation test bench of the series hydraulic hybrid electric vehicle according to the present invention can be used for simulating the working states of the series hybrid electric vehicle with single planetary row configuration in different modes.

C1 clutch 17 and C2 clutch 18 are combined, C3 brake 45 is disengaged, and the rear planetary row as a whole is connected to the front planetary row ring gear 9 through the rear planetary row input shaft 11, so the whole test bench is regarded as a simulated single planetary row configuration.

1. Engine start mode

Referring to accompanying drawing 3, the simulation test bench of the hybrid hydraulic vehicle according to the present invention is used for simulating the working state of the hybrid hydraulic hybrid vehicle with a single planetary row configuration in the stop-start mode. Under this mode, the controller 37 sends a control signal to make the displacement of the first hydraulic pump/motor 23 be zero, and the displacement of the second hydraulic pump/motor 32 is positive (0, 1) and works in a motor state. The two-position two-way electromagnetic directional valve 39 is in the left position, the hydraulic control check valve 38 is in the two-way flow state, the second two-position two-way electromagnetic directional valve 46 is in the left position, and the third two-position two-way electromagnetic directional valve 47 is in the left position. in a superior position. The high-pressure oil stored in the high-pressure accumulator 33 enters the a port of the second hydraulic pump/motor 32 through the second hydraulic pipeline 36, the second two-position two-way electromagnetic reversing valve 46, and the hydraulic control check valve 38 in sequence, and passes through Port b of the second hydraulic pump/motor 32 enters the first hydraulic conduit 35 , which eventually flows into the low pressure accumulator 34 . The hydraulic energy is converted into mechanical energy through the second hydraulic pump/motor 32, and the power transmission sequentially passes through the eighth coupling 31, the seventh coupling 29, the second meshing gear 28, the front planetary row input gear 6, and the front planetary row sun gear 7. The front planetary row carrier 8, the front planetary row input shaft 10, the torsional shock absorber 5, the second coupling 4, and the first coupling 2 reach the input shaft of the motor 1. Simultaneously, the rotational speed and the torque value of the input shaft of the motor 1 and the output shaft of the second hydraulic pump/motor 32 are respectively recorded in real time by the first rotational speed torque sensor 3 and the fourth rotational speed torque sensor 30; the first pressure sensor 40, the second The pressure sensor 41 records the hydraulic oil pressure in the high-pressure accumulator 33 and the low-pressure accumulator 34 respectively in real time. The controller 37 outputs a signal to control the load moment of the DC dynamometer 22 to provide sufficient load to the front planetary ring gear 9 . The starting characteristics of different engines can be simulated by controlling the working point of the motor 1 through the output signal of the controller 37 .

2. Pure hydraulic drive mode

Referring to accompanying drawing 3, the simulation test bench of the hybrid hydraulic vehicle according to the present invention is used for simulating the working state of the hybrid hydraulic hybrid vehicle with a single planetary row configuration in the pure hydraulic drive mode. In this mode, the controller 37 sends a control signal, so that the displacement of the first hydraulic pump/motor 23 is positive (0,1) and works in the motor state, the displacement of the second hydraulic pump/motor 32 is zero, and the displacement of the first hydraulic pump/motor 23 is zero. The two-position two-way electromagnetic reversing valve 39 is in the right position, the hydraulic control check valve 38 is in the one-way flow state (only from the P1 port to the P2 port), and the second two-position two-way electromagnetic reversing valve 46 is in the right position, The third two-position two-way electromagnetic reversing valve 47 is in the down position. The high-pressure oil stored in the high-pressure accumulator 33 enters the a port of the first hydraulic pump/motor 23 through the second hydraulic pipeline 36 and the third two-position two-way electromagnetic reversing valve 47, and passes through the first hydraulic pump/motor 23 The b port enters the first hydraulic line 35 and finally flows into the low-pressure accumulator 34 . The hydraulic energy is converted into mechanical energy through the first hydraulic pump/motor 23, and the power passes through the fifth coupling 24, the sixth coupling 26, the first meshing gear 27, the rear planetary row input gear 12, the C2 clutch 18, and the C1 clutch 17. The rear planetary planet carrier 16, the third coupling 19, and the fourth coupling 21 reach the DC dynamometer 22. Simultaneously, the rotational speed and the torque value of the input shaft of the DC dynamometer 22 and the output shaft of the first hydraulic pump/motor 23 are respectively recorded in real time by the second rotational speed torque sensor 20 and the third rotational speed torque sensor 25; the first pressure sensor 40 1. The second pressure sensor 41 records the hydraulic oil pressure in the high-pressure accumulator 33 and the low-pressure accumulator 34 respectively in real time. The load torque and rotational speed of the DC dynamometer 22 are controlled by the output signal of the controller 37 to simulate different road surface condition inputs to obtain different pure hydraulic drive characteristics. In this mode, the controller 37 does not output a control signal to the motor 1, and the motor 1 runs idly. The second hydraulic pump/motor 32 is also in an idle state.

3. Joint drive mode

Referring to accompanying drawing 3, the simulation test bench of the hybrid hydraulic vehicle according to the present invention is used for simulating the working state of the hybrid hydraulic hybrid vehicle with a single planetary row configuration in the combined drive mode. In this mode, the controller 37 sends a control signal so that the displacement values of the first hydraulic pump/motor 23 and the second hydraulic pump/motor 32 are both positive (0-1), and the first hydraulic pump/motor 23 works in the motor state, the first two two-way electromagnetic reversing valve 39 is in the left position, the hydraulic control check valve 38 is in the two-way flow state, the second two two-way electromagnetic reversing valve 46 is in the left position, and the third two two-way electromagnetic reversing valve is in the left position. Reversing valve 47 is in down position. At this time, there are two power transmission paths: in path one, the power passes through the motor 1, the first coupling 2, the second coupling 4, the torsional shock absorber 5, the front planetary row input shaft 10, and the front planetary row planets in turn. Frame 8, front planetary row planetary gear 44, front planetary row ring gear 9, rear planetary row input shaft 11, C1 clutch 17, rear planetary row planet carrier 16 reach DC dynamometer 22; in path 2, power passes through motor 1 in sequence , the first coupling 2, the second coupling 4, the torsional shock absorber 5, the front planetary row input shaft 10, the front planetary row carrier 8, the front planetary row planetary gear 44, the front planetary row ring gear 7, the front The planetary input gear 6, the second meshing gear 29, the seventh coupling 29, and the eighth coupling 31 reach the input shaft of the second hydraulic pump/motor 32, and the second hydraulic pump/motor 32 converts mechanical energy into hydraulic energy , the high-pressure oil enters the second hydraulic pipeline 36 from the a port of the second hydraulic pump/motor 32, forms a coupling with the pressure oil in the high-pressure accumulator 33, and enters the first hydraulic pressure through the third two-position two-way electromagnetic reversing valve 47. The a port of the pump/motor 23 enters the first hydraulic pipeline 35 through the b port of the first hydraulic pump/motor 23 , and finally flows into the low pressure accumulator 34 . The hydraulic energy is converted into mechanical energy through the first hydraulic pump/motor 23, and then passes through the fifth coupling 24, the sixth coupling 26, the first meshing gear 27, the rear planetary input gear 12, the C2 clutch 18, and the C1 clutch 17 , the rear planetary planet carrier 16 , the third coupling 19 , and the fourth coupling 21 reach the DC dynamometer 22 . At the same time, the first rotational speed torque sensor 3, the second rotational speed torque sensor 20, the third rotational speed torque sensor 25, and the fourth rotational speed torque sensor 30 respectively record the output shaft of the motor 1, the input shaft of the DC dynamometer 22, the The rotational speed and torque value of the input shaft of a hydraulic pump/motor 23 and the input shaft of the second hydraulic pump/motor; the first pressure sensor 40 and the second pressure sensor 41 respectively record the hydraulic pressure in the high pressure accumulator 33 and the low pressure accumulator 34 in real time. oil pressure. The output signal of the controller 37 controls the load torque and rotational speed of the DC dynamometer 22 to simulate different road surface condition inputs, so that different combined driving characteristics can be obtained.

In the combined drive mode, the second hydraulic pump/motor 32 may work in the motor state according to the change of the rotational speed and torque of the front planetary planet carrier 8 and the front planetary ring gear 9, so the controller 37 makes the first two bits two The electromagnetic reversing valve 39 is in the left position, and the hydraulic control check valve 38 is in a two-way flow state. Whether the second hydraulic pump/motor 32 will work in the motor state is related to the control strategy used by the simulated vehicle, which will not be described in detail in the present invention.

4. Regenerative braking mode

Referring to accompanying drawing 3, the simulation test bench of the series hydraulic hybrid electric vehicle according to the present invention is used to simulate the working state of the single planetary row configuration of the series hydraulic hybrid electric vehicle in the regenerative braking mode. In this mode, the controller 37 sends a control signal, so that the displacement of the first hydraulic pump/motor 23 is positive (0,1) and works in the pump state, the displacement of the second hydraulic pump/motor 32 is zero, and the displacement of the first hydraulic pump/motor 23 is zero. The two-position two-way electromagnetic reversing valve 39 is in the right position, the hydraulic control check valve 38 is in the one-way flow state (only from the P1 port to the P2 port), and the second two-position two-way electromagnetic reversing valve 46 is in the right position, The third two-position two-way electromagnetic reversing valve 47 is in the down position. The power sequentially passes through the DC dynamometer 22, the fourth coupling 21, the third coupling 19, the rear planetary planet carrier 16, the C1 clutch 17, the C2 clutch 18, the rear planetary input gear 12, and the first meshing gear 27 , the sixth coupling 26 and the fifth coupling 24 reach the first hydraulic pump/motor 23 . The first hydraulic pump/motor 23 converts mechanical energy into hydraulic energy and stores it in a high pressure accumulator 33 . Simultaneously, the second rotating speed torque sensor 20, the third rotating speed torque sensor 25 record the rotating speed torque values of the DC dynamometer 22 output shaft and the first hydraulic pump/motor 23 input shaft in real time respectively; Two pressure sensors 41 respectively record the hydraulic oil pressure in the high-pressure accumulator 33 and the low-pressure accumulator 34 in real time. Different regenerative braking characteristics can be obtained by controlling the loading torque and rotational speed of the DC dynamometer 22 through the output signal of the controller 37 to simulate different road surface condition inputs. In this mode, the controller 37 does not output a control signal to the motor 1, and the motor 1 runs idly. The second hydraulic pump/motor 32 is also in an idle state.

5. Reversing mode

Referring to accompanying drawing 3, the simulation test bench of the series hydraulic hybrid vehicle according to the present invention is used to simulate the working state of the series hydraulic hybrid vehicle with a single planetary row configuration in reverse mode. In this mode, the controller 37 sends a control signal to make the displacement of the first hydraulic pump/motor 23 negative (-1, 0) and work in the motor state, the displacement of the second hydraulic pump/motor 32 is zero, and the displacement of the first hydraulic pump/motor 23 is zero. The one-two-two-way electromagnetic reversing valve 39 is in the right position, the hydraulic control check valve 38 is in the one-way flow state (only from the P1 port to the P2 port), and the second two-two-way electromagnetic reversing valve 46 is in the right position , the third two-way electromagnetic reversing valve 47 is in the lower position. Compared with the pure hydraulic driving mode, in the reversing mode, the first hydraulic pump/motor 23 is in the reverse state, and the oil flow path, power transmission path, recording status of each sensor, and the control mode of the DC dynamometer 22 are similar to those of the pure hydraulic The driving mode is exactly the same, so I won't repeat them here.

The working state and power transmission path of each hydraulic valve in different modes when simulating the single planetary row configuration:

Note: When simulating single planetary row configuration, C1 clutch 17 and C2 clutch 18 are always engaged, and C3 brake is always disengaged. The numerical symbols of the coupling and the speed torque sensor are omitted in the power transmission path.

Referring to accompanying drawing 4, the hybrid hydraulic hybrid vehicle simulation test bench of the present invention can be used for simulating the working state of a hybrid hydraulic hybrid vehicle with single planetary row + rear motor torque increasing configuration in different modes. The C3 brake 45 is combined to lock the rear planetary ring gear 15, and the entire system simulates the front planetary + rear motor torque increasing configuration. The C1 clutch 17 and the C2 clutch 18 work in different states to achieve different torque increasing effects.

1. Engine start mode

Referring to accompanying drawing 4, the hybrid hydraulic hybrid vehicle simulation test bench of the present invention is used for simulating the working state of a hybrid hydraulic hybrid vehicle with a single planetary row + motor torque increase configuration in the engine start-up mode. The controller 37 sends out a control signal, so that the displacement value of the first hydraulic pump/motor 23 is zero, the displacement value of the second hydraulic pump/motor 32 is positive (0-1) and works in the motor state, and the C1 clutch 17 is disengaged state, the C2 clutch 18 is in the combined state, the first two-position two-way electromagnetic reversing valve 39 is in the left position, the hydraulic control check valve 38 is in the two-way flow state, and the second two-position two-way electromagnetic reversing valve 46 is in the left position. The third two-position two-way electromagnetic reversing valve 47 is in the upper position. The flow route of hydraulic oil, the power transmission route, the recording state of each sensor and the control mode of DC dynamometer 22 under this mode are used for simulating single planetary row The cross-connected hydraulic hybrid vehicles of the configuration are completely the same in the engine start-up mode, and will not be repeated here.

2. Pure hydraulic drive mode

Referring to accompanying drawing 4, the hybrid hydraulic hybrid vehicle simulation test bench of the present invention is used to simulate the working state of a hybrid hydraulic hybrid vehicle with a single planetary row + motor torque increasing configuration in a purely hydraulic drive mode. The controller 37 sends a control signal, so that the displacement value of the first hydraulic pump/motor 23 is positive (0～1) and works in the motor state, the displacement of the second hydraulic pump/motor 32 is zero, and the C1 clutch 17 and C2 The clutches 18 are all in the disengaged state, the first two-position two-way electromagnetic reversing valve 39 is in the right position, the hydraulic control check valve 38 is in the one-way flow state (only from P1 port to P2 port), the second two-position two-way The electromagnetic reversing valve 46 is in the right position, and the third two-position two-way electromagnetic reversing valve 47 is in the down position. In this mode, the high-pressure oil stored in the high-pressure accumulator 33 enters the port a of the first hydraulic pump/motor 23 through the second hydraulic pipeline 36 and the third two-position two-way electromagnetic reversing valve 47, and passes through the first hydraulic The b-port of the pump/motor 23 enters a first hydraulic line 35 which eventually flows into a low pressure accumulator 34 . The hydraulic energy is converted into mechanical energy through the first hydraulic pump/motor 23, and the power passes through the fifth coupling 24, the sixth coupling 26, the first meshing gear 27, the rear planetary row input gear 12, and the rear planetary row sun gear 13 in sequence , the rear planetary row planet wheel 14, the rear planetary row carrier 16, the third coupling 19, and the fourth coupling 21 reach the DC dynamometer 22. Simultaneously by the second rotation speed torque sensor 20, the 3rd rotation speed torque sensor 25 respectively real-time record the rotation speed, the torque value of DC dynamometer 22 input shafts and first hydraulic pump/motor 23 output shafts; First pressure sensor 40, The second pressure sensor 41 respectively records the hydraulic oil pressure in the high-pressure accumulator 33 and the low-pressure accumulator 34 in real time. The load torque and rotational speed of the DC dynamometer 22 are controlled by the output signal of the controller 37 to simulate different road surface condition inputs to obtain different pure hydraulic drive characteristics.

3. Joint drive mode

Referring to accompanying drawing 4, the hybrid hydraulic hybrid vehicle simulation test bench of the present invention is used for simulating the working state of a hybrid hydraulic hybrid vehicle with a single planetary row + rear row motor torque increasing configuration in the combined drive mode . The controller 37 sends a control signal so that the displacement values of the first hydraulic pump/motor 23 and the second hydraulic pump/motor 32 are positive (0-1), the first hydraulic pump/motor 23 works in the motor state, and the first hydraulic pump/motor 23 works in a motor state. The two-position two-way electromagnetic directional valve 39 is in the left position, the hydraulic control check valve 38 is in the two-way flow state, the second two-position two-way electromagnetic directional valve 46 is in the left position, and the third two-position two-way electromagnetic directional valve 47 is in the left position. in the lower position. By making the C1 clutch 17 and the C2 clutch 18 in different engagement states, two combined drive modes can be simulated, namely, the HVT1 mode and the HVT2 mode.

When the C1 clutch 17 is in the disengaged state and the C2 clutch 18 is in the engaged state, the test bench simulates the HVT1 mode, or the low-speed HVT mode. At this time, there are two power transmission paths: in path one, the power passes through the motor 1, the first coupling 2, the second coupling 4, the torsional shock absorber 5, the front planetary row input shaft 10, the front planetary row Star frame 8, front planetary row planetary gear 44, front planetary row ring gear 9, rear planetary row input shaft 11, C2 clutch 18, rear planetary row sun gear 13, rear planetary row planetary gear 14, rear planetary row carrier 16, The third coupling 19 and the fourth coupling 21 reach the DC dynamometer 22; in the second path, the power passes through the motor 1, the first coupling 2, the second coupling 4, the torsional shock absorber 5, Front planetary row input shaft 10, front planetary row carrier 8, front planetary row planetary gear 44, front planetary row ring gear 7, front planetary row input gear 6, second meshing gear 29, seventh coupling 29, eighth The shaft coupling 31 reaches the input shaft of the second hydraulic pump/motor 32, the second hydraulic pump/motor 32 converts mechanical energy into hydraulic energy, and the high-pressure oil enters the second hydraulic pipeline 36 from port a of the second hydraulic pump/motor 32, It is coupled with the pressure oil in the high-pressure accumulator 33, enters the a port of the first hydraulic pump/motor 23 through the third two-position two-way electromagnetic reversing valve 47, and enters the first hydraulic pump/motor 23 through the b port of the first hydraulic pump/motor 23. A hydraulic line 35 ultimately flows into a low pressure accumulator 34 . The hydraulic energy is converted into mechanical energy by the first hydraulic pump/motor 23, and passes through the fifth coupling 24, the sixth coupling 26, the first meshing gear 27, the rear planetary row input gear 12, the rear planetary row sun gear 13, The rear planetary row planet wheel 14 , the rear planetary row carrier 16 , the third coupling 19 and the fourth coupling 21 reach the DC dynamometer 22 .

When the C1 clutch 17 is in the engaged state and the C2 clutch 18 is in the disengaged state, the test bench simulates the EVT2 mode, or the low-speed HVT mode. At this time, there are also two power transmission paths: in path one, the power transmission sequentially passes through the motor 1, the first coupling 2, the second coupling 4, the torsional shock absorber 5, the front planetary row input shaft 10, the front Planetary carrier 8, front planetary gear 44, front planetary ring gear 9, rear planetary input shaft 11, C1 clutch 17, rear planetary carrier 16, third coupling 19, fourth coupling 21 reaches the DC dynamometer 22; the second path is a compound transmission path, and its power transmission path is the same as the HVT1 mode path two, and will not be repeated here.

At the same time, the first rotational speed torque sensor 3, the second rotational speed torque sensor 20, the third rotational speed torque sensor 25, and the fourth rotational speed torque sensor 30 respectively record the output shaft of the motor 1, the input shaft of the DC dynamometer 22, the A hydraulic pump/motor 23 input shaft, the rotational speed torque value of the second hydraulic pump/motor input shaft, the first pressure sensor 40, the second pressure sensor 41 records the hydraulic pressure in the high pressure accumulator 33 and the low pressure accumulator 34 respectively in real time. oil pressure. The load torque and rotational speed of the DC dynamometer 22 are controlled by the output signal of the controller 37 to simulate different road surface condition inputs to obtain different combined driving characteristics.

In the joint drive mode, the second hydraulic pump/motor 32 may work in the motor state according to the change of the rotational speed and torque of the front planetary planetary carrier 8 and the front planetary ring gear 9, so the controller 37 makes the third two bits two The electromagnetic reversing valve 39 is in the left position, and the hydraulic control check valve 38 is in a two-way flow state. Whether the second hydraulic pump/motor 32 will work in the motor state is related to the control strategy used by the simulated vehicle, which will not be described in detail in the present invention.

4. Regenerative braking mode

Referring to accompanying drawing 4, the hybrid hydraulic hybrid vehicle simulation test bench of the present invention is used to simulate the working state of a hybrid hydraulic hybrid vehicle with a single planetary row + motor torque increase configuration in regenerative braking mode. The controller 37 sends a control signal so that the displacement of the first hydraulic pump/motor 23 is positive (0-1) and works in the pump state, the displacement value of the second hydraulic pump/motor 32 is zero, and the C1 clutch 17 and C2 The clutches 18 are all in the disengaged state, the first two-position two-way electromagnetic reversing valve 39 is in the right position, the hydraulic control check valve 38 is in the one-way flow state (only from P1 port to P2 port), the second two-position two-way The electromagnetic reversing valve 46 is in the right position, and the third two-position two-way electromagnetic reversing valve 47 is in the down position. The power sequentially passes through the DC dynamometer 22, the fourth coupling 21, the third coupling 19, the rear planetary row carrier 16, the rear planetary row planetary gear 14, the rear planetary row sun gear 13, and the rear planetary row input gear 12 , the first meshing gear 27 , the sixth coupling 26 , and the fifth coupling 24 reach the first hydraulic pump/motor 23 . The first hydraulic pump/motor 23 converts mechanical energy into hydraulic energy and stores it in a high pressure accumulator 33 . Simultaneously, the second rotating speed torque sensor 20, the third rotating speed torque sensor 25 record the rotating speed torque values of the DC dynamometer 22 output shaft and the first hydraulic pump/motor 23 input shaft in real time respectively; Two pressure sensors 41 respectively record the hydraulic oil pressure in the high-pressure accumulator 33 and the low-pressure accumulator 34 in real time. Different regenerative braking characteristics can be obtained by controlling the loading torque and rotational speed of the DC dynamometer 22 through the signal output of the controller 37 to simulate different road surface condition inputs.

5. Reversing mode

Referring to accompanying drawing 4, the hybrid hydraulic hybrid vehicle simulation test bench of the present invention is used for simulating the working state of a hybrid hydraulic hybrid vehicle with single planetary row + rear row motor torque increasing configuration in reverse mode. The controller 37 sends a control signal to make the displacement value of the first hydraulic pump/motor 23 negative (-1~0) and work in a motor state, and the displacement of the second hydraulic pump/motor 32 is zero. Both the C1 clutch 17 and the C2 clutch 18 are in the disengaged state, the first two-position two-way electromagnetic reversing valve 39 is in the right position, the hydraulic control check valve 38 is in the one-way flow state (only from the P1 port to the P2 port), the second The second two-two-way electromagnetic directional valve 46 is in the right position, and the third two-two-way electromagnetic directional valve 47 is in the lower position. Compared with the pure hydraulic drive mode, in the reversing mode, the first hydraulic pump/motor 23 is in the reverse state, and the oil flow path, power transmission path, and control method of the DC dynamometer 22 are exactly the same as those of the pure hydraulic drive mode. I won't repeat them here.

Simulate the working status of hydraulic valves, clutches and power transmission paths in different modes when the front planetary row + rear row motor increase torque configuration:

Note: When simulating a single planetary row + rear motor torque increase configuration, the C3 brake is always engaged. Couplings and speed torque sensor numerals are ignored in the power transmission path.

The hybrid hydraulic hybrid vehicle simulation test bench of the present invention can not only be used to simulate the working states of hybrid hydraulic hybrid vehicles with different planetary gear configurations in different modes, but also perform performance tests on hydraulic components.

1. Hydraulic pump displacement response and accumulator charging characteristics test

Through the controller, the first two-two-way electromagnetic reversing valve 39 is in the right position, the second two-two-way electromagnetic reversing valve 46 is in the right position, the third two-two-way electromagnetic reversing valve 47 is in the lower position, and the C1 clutch 17 and C2 clutch 18 are combined, C3 clutch is disengaged, the dynamometer 22 outputs a constant speed or constant torque, and the first hydraulic pump/motor 23 works in a pump state. The controller 37 controls the displacement change of the first hydraulic pump/motor 23, while the third rotational speed torque sensor 25 records the rotational speed torque change of the input shaft of the first hydraulic pump/motor 23 in real time, the first pressure sensor 40, the second pressure The sensor 41 respectively records the pressure changes of port a (high pressure accumulator) and port b (low pressure accumulator) of the first hydraulic pump/motor 23 in real time.

2. Hydraulic motor response and accumulator discharge characteristics test

Through the controller, the first two-two-way electromagnetic reversing valve 39 is in the right position, the second two-two-way electromagnetic reversing valve 46 is in the right position, the third two-two-way electromagnetic reversing valve 47 is in the lower position, and the C1 clutch 17 and C2 clutch 18 are combined, C3 clutch is disengaged, and the first hydraulic pump/motor 23 works in the motor state. The controller 37 controls the load speed and torque changes of the DC dynamometer 22, while the third speed torque sensor 25 records the speed and torque changes of the input shaft of the first hydraulic pump/motor 23 in real time, the first pressure sensor 40, the second The pressure sensor 41 respectively records the pressure changes of port a (high pressure accumulator) and port b (low pressure accumulator) of the first hydraulic pump/motor 23 in real time.

The above-mentioned system components have already been produced, and the specific selection needs to be determined in combination with design parameters and design requirements.

Claims (4)

1. A kind of 1. series parallel type hydraulic hybrid dynamic automobile simulation test stand：Including stand in kind (I) and real-time emulation system (II), It is characterized in that：

   Described stand in kind (I) includes motor (1), the first 2/2-way solenoid directional control valve (39), the second 2/2-way electromagnetism It is reversal valve (46), the 3rd 2/2-way solenoid directional control valve (47), preceding planet row, rear planet row, preceding planet row input shaft (10), preceding Planet row input gear (6), rear planet row input shaft (11), rear planet row input gear (12), the first hydraulic pump/motor (23), the second hydraulic pump/motor (32), direct current dynamometer (22), high pressure accumulator (33), low pressure accumulator (34), first Axle device (2), second shaft coupling (4), the 3rd shaft coupling (19), the 4th shaft coupling (21), the 5th shaft coupling (24), the 6th shaft coupling (26), the 7th shaft coupling (29), the 8th shaft coupling (31), C1 clutches (17), C2 clutches (18), C3 brakes (45), One meshing gear (27), the second meshing gear (28), hydraulic control one-way valve (38), the first hydraulic pipeline (35), the second hydraulic pipeline (36), first pressure sensor (40), second pressure sensor (41), the first torque and speed sensorses (3), the second rotational speed and torque Sensor (20), the 3rd torque and speed sensorses (25), the 4th torque and speed sensorses (30), torsional vibration damper (5)；

   Described preceding planet row be sleeved on before on planet row input shaft (10), preceding planet row includes preceding planet row sun gear (7), preceding Planet rows of planetary wheel (44) before planet row planet carrier (8), preceding planet toothrow circle (9) and four structure identicals, preceding planet row Sun gear (7) is integral with preceding planet row input gear (6), preceding planet row input gear (6) and the second meshing gear (28) Often engagement connection；Described rear planet row is sleeved on rear planet row input shaft (11), and rear planet row includes the rear planet row sun Planet row planetary gear after wheel (13), rear planet row planet carrier (16), rear planet row gear ring (15) and four structure identicals (14), rear planet row sun gear (13) is integral with rear planet row input gear (12), rear planet row input gear (12) with First meshing gear (27) often engagement connection；

   The a ends of described C1 clutches (17) are coaxial connected with rear planet row input shaft (11), b ends and rear planet row planet carrier (16) it is coaxial to be connected；The a ends of described C2 clutches (18) are coaxial connected with rear planet row input gear (12), b ends and rear row Star row's input shaft (11) is coaxially connected；The fixing end of described C3 brakes (45) is connected with frame, turning end and rear planet row Gear ring (15) is coaxially connected；

   The P ports of the first described 2/2-way solenoid directional control valve (39), A ports respectively with the second hydraulic pipeline (36), hydraulic control K ports (control port) connection of check valve (38)；P ports, the A ports of the second described 2/2-way solenoid directional control valve (46) The P2 ports with the second hydraulic pipeline (36), hydraulic control one-way valve (38) are connected respectively, the P1 ports of hydraulic control one-way valve (38) and the The a ports connection of two hydraulic pump/motors (32)；P ports, the A ports point of the 3rd described 2/2-way solenoid directional control valve (47) A ports not with the second hydraulic pipeline (36), the first hydraulic pump/motor (23) are connected；Described high pressure accumulator (33) go out Hydraulic fluid port is connected with the second hydraulic pipeline (36), and the oil-out of low pressure accumulator (34) is connected with the first hydraulic pipeline (35)；It is described The b ports of the first hydraulic pump/motor (23), the b ports of the second hydraulic pump/motor (32) with the first hydraulic pipeline (35) even Connect；

   Described real-time emulation system (II) is made up of controller (37), dSPACE simulators (42) and host computer (43)；Control Device (37) is connected with stand in kind (I) by electric wire, and controller (37) is connected with dSPACE simulators (42) by electric wire, upper Machine (43) is connected with dSPACE simulators (42) by ethernet line.
2. 2. according to the series parallel type hydraulic hybrid dynamic automobile simulation test stand described in claim 1, it is characterised in that described control Device (37) processed is connected with stand in kind (I) by electric wire to be referred to：

   First pressure sensor (40), second pressure sensor (41), the first rotational speed and torque sensing in described stand in kind (I) Device (3), the second torque and speed sensorses (20), the 3rd torque and speed sensorses (25), the 4th torque and speed sensorses (30) are logical Cross EAD00 terminal of the electric wire respectively with controller (37), EAD01 terminals, EAD02 terminals, EAD03 terminals, EAD04 terminals, EAD05 terminals connect；The control terminal of motor (1), the discharge capacity of the first hydraulic pump/motor (23) in described stand in kind (I) Control terminal, the displacement control terminal of the second hydraulic pump/motor (32), the control terminal of C1 clutches (17), C2 clutches (18) control terminal, the control terminal of C3 brakes (45), the control terminal of the first 2/2-way solenoid directional control valve (39), The control terminal of two 2/2-way solenoid directional control valves (46), the control terminal of the 3rd 2/2-way solenoid directional control valve (47) and straight Flow dynamometer machine (22) control terminal by electric wire respectively the LA00 terminals with controller (37), LA01 terminals, LA02 terminals, LA03 terminals, LA04 terminals, LA05 terminals, LA06 terminals, LA07 terminals, LA08 terminals, the connection of LA09 terminals.
3. 3. according to the series parallel type hydraulic hybrid dynamic automobile simulation test stand described in claim 1, it is characterised in that described The left and right ends of one torque and speed sensorses (3) by first shaft coupling (2), second shaft coupling (4) respectively with motor (1), turn round It is coaxially connected to turn shock absorber (5), torsional vibration damper (5) is same by preceding planet row input shaft (10) with front planetary line (8) Axis connection；The left and right ends of second torque and speed sensorses (20) pass through the 3rd shaft coupling (19), the 4th shaft coupling (21) difference It is coaxially connected with rear planet row planet carrier (16), direct current dynamometer (22)；3rd torque and speed sensorses (25) left and right ends lead to It is coaxial with the first hydraulic pump/motor (23), the first meshing gear (27) respectively to cross the 5th shaft coupling (24), the 6th shaft coupling (26) Connection；4th torque and speed sensorses (30) left and right ends are by the 8th shaft coupling (31), the 7th shaft coupling (29) respectively with Two hydraulic pump/motors (32), the second meshing gear (28) are coaxially connected.
4. 4. according to the series parallel type hydraulic hybrid dynamic automobile simulation test stand described in claim 1, it is characterised in that described One pressure sensor (40) is arranged on the second hydraulic pipeline (36), and second pressure sensor (41) is arranged on the first hydraulic pipeline (35) on；Described preceding planet row input shaft (10) is vertical with the periphery of front planetary line (8) to be coaxially connected；Described Preceding planet toothrow circle (9) is coaxial connected with rear planet row input shaft (11).