CN206708120U - A kind of hydraulic auxiliary driving system of integrated hydraulic starter - Google Patents

Abstract

The utility model discloses a hydraulic auxiliary drive system integrated with a hydraulic starter, which aims to solve the problems of unnecessary fuel consumption caused by the idling of the engine when the traditional heavy vehicle is parked, and the inability of the starter to start the engine under extreme conditions such as failure. Problems, including hydraulic control unit, power take-off device, hydraulic pump assembly, control valve group, accumulator, hydraulic starter motor, one-way clutch, oil storage tank, hydraulic hub motor and detachable hydraulic hand pump, etc. The hydraulic control unit realizes switching of the vehicle in different working modes by controlling the working position of each valve group element according to the current vehicle state and the driver's demand. The system provided by the utility model can not only improve the dynamic performance of the whole vehicle, but also realize the fast idle start-stop function of the vehicle, and reduce the fuel consumption of the engine at the same time; and it is easy to realize in engineering and has good application prospects.

Description

A Hydraulic Auxiliary Drive System Integrated with Hydraulic Starter

technical field

The utility model relates to a vehicle hydraulic auxiliary drive system, more precisely, the utility model relates to a hydraulic auxiliary drive system which integrates a hydraulic starter and can realize the function of fast idle start and stop.

Background technique

The driving conditions of heavy-duty commercial vehicles and engineering transport vehicles are complex and changeable, and they often need to work on muddy, sandy and other low adhesion coefficient roads, which are prone to the problem of driving wheel slipping due to insufficient driving force. To solve this problem, hydraulic auxiliary drive technology can be used to change the vehicle from rear drive to all-wheel drive by installing a hydraulic hub motor in the front wheel hub of a traditional rear drive vehicle. At the same time, such commercial vehicles and engineering transport vehicles often need to load and unload goods and frequently start and stop vehicles. Considering that the engine idle speed is automatically turned off when the vehicle is parked, it can effectively reduce fuel consumption and achieve the effect of energy saving and emission reduction.

In the 1970s, some car companies in Japan, Europe and the United States proposed hydraulic auxiliary drive systems and successfully applied them to real vehicles. For example, companies such as Rexroth, Poclain, and MAN successively launched their own hydraulic auxiliary drive vehicles. In recent years, in order to meet the needs of engineering applications and consider the outstanding advantages of hydraulic drive systems, domestic scholars have also carried out related research on hydraulic auxiliary drive systems. The Chinese patent publication number is CN104859424A, and the publication date is 2015-08-26, which discloses a hydraulic hub motor auxiliary drive system. The system uses a closed circuit composed of a hydraulic pump, a hydraulic control valve group, and a hydraulic motor to assist in driving the vehicle, which can improve the power of the vehicle on low-adhesion roads, but cannot recover the braking energy of the system, and cannot achieve fuel saving. . The Chinese patent publication number is CN105459978A, and the publication date is 2016-04-06, which discloses a hydraulic auxiliary drive and braking energy recovery system. This system not only improves the dynamic performance of the vehicle, but also realizes the recovery of braking energy. At the same time, it can realize more working modes by controlling the hydraulic valve group. However, the existing hydraulic auxiliary drive system patents have not taken into account the vehicle starting device, and these patents generally use a starter motor for the starting device of the vehicle. In addition, the existing engine starting device will not be able to start the engine under extreme conditions such as failure. In the hydraulic auxiliary drive system, the hydraulic starter is used to realize the idling start and stop of the engine, which not only reduces the idling fuel consumption of the engine, but also can effectively utilize the energy recovered by braking. There is no related invention in this field. At the same time, the detachable hydraulic manual pump is used as a backup pump, which can ensure the normal starting of the engine when the hydraulic accumulator is insufficiently charged.

Contents of the invention

The technical problem to be solved by the utility model is to overcome the problem of unnecessary fuel consumption caused by the idling of the engine at idle speed in the prior art; To solve the problem, a hydraulic auxiliary drive system that integrates a hydraulic starter and can realize the function of quick idle start and stop is provided.

In order to solve the above technical problems, the utility model is realized by adopting the following technical scheme: the hydraulic auxiliary driving system of an integrated hydraulic starter includes a hydraulic control unit, a power take-off device, a hydraulic pump assembly, a No. 1 control valve group, No. 1 accumulator, hydraulic starter motor, one-way clutch, engine, oil storage tank, No. 2 accumulator, No. 2 control valve group, No. 1 hydraulic hub motor, No. 2 hydraulic hub motor, load mass of No. 1 hydraulic motor Body, load quality body of No. 2 hydraulic motor and detachable hydraulic manual pump.

The output shaft of the engine and the input shaft of the power take-off device are connected by a spline pair, and the output shaft of the power take-off device and the input shaft of the hydraulic pump assembly are connected by a universal joint or a spline pair. The valve groups are connected by pipelines, the No. 1 control valve group is connected with the oil port of the No. 1 accumulator through the external port S3, and the No. 1 control valve group is connected with the hydraulic starter motor through the external port S4. Pipeline connection, the output shaft of the hydraulic starter motor is mechanically connected with the input shaft of the one-way clutch, the output shaft of the one-way clutch is mechanically connected with the engine crankshaft, the hydraulic pump assembly and the No. The valve group is connected with the oil port of the No. 2 accumulator through the external port Acc, and the port D2 and port D3 of the No. 2 control valve group are sequentially connected with the two inlet and outlet ports of the No. 1 hydraulic hub motor. Port D4 and port D5 of the No. 2 control valve group are sequentially connected to the two inlet and outlet pipelines of the No. 2 hydraulic hub motor, and the connection between the No. 1 hydraulic hub motor and the load mass body of the No. 1 hydraulic motor is a spline connection or The two are coaxially connected, the No. 2 hydraulic hub motor and the load mass body of No. 2 hydraulic motor are connected by a spline pair or the two are coaxially connected. The hydraulic pump assembly, No. 1 control valve group, hydraulic starter motor and The No. 2 control valve group is connected with the oil storage tank by pipelines, the hydraulic control unit and the hydraulic pump assembly, the No. 1 control valve group and the No. 2 control valve group are connected by signal lines; The pipeline connection is adopted between the detachable hydraulic manual pump and the oil port of the No. 1 accumulator.

A hydraulic auxiliary drive system integrated with a hydraulic starter described in the technical solution is characterized in that the hydraulic pump assembly and the No. 1 control valve group are connected by pipelines, and the hydraulic pump assembly is connected to the No. The pipeline connection between the control valve groups refers to:

The hydraulic pump assembly includes a hydraulic pump, a charge pump, a No. 1 check valve, a No. 1 overflow valve, a No. 2 check valve, a No. 2 overflow valve, a No. 3 overflow valve, and a No. 1 two-position two-way solenoid valve. Reversing valve; the external port M1 of the hydraulic pump assembly is connected to the external port S1 of the No. 1 control valve group, and the external port M2 of the hydraulic pump assembly is connected to the external port S2 of the No. 1 control valve group; the hydraulic pump assembly The external port M1 is connected to the external port MA of the No. 2 control valve group, the external port M2 of the hydraulic pump component is connected to the external port MB of the No. 2 control valve group, and the external port M3 of the hydraulic pump component is connected to the No. 2 control valve. The external port of the group is connected to the MG pipeline.

A hydraulic auxiliary drive system integrated with a hydraulic starter described in the technical solution is characterized in that the No. 1 control valve group includes a three-position three-way electromagnetic reversing valve, a No. 1 stop valve, and a No. 4 overflow valve. , No. 2 two-position two-way electromagnetic reversing valve, No. 3 check valve, No. 4 check valve, No. 5 check valve and No. 1 accumulator pressure sensor Pacc1. The oil inlet of No. 3 check valve is connected with the external port S1 of No. 1 control valve group, the oil inlet of No. 4 check valve is connected with the external port S2 of No. 1 control valve group. The oil outlet of the valve is connected to the port A pipeline of the three-position three-way electromagnetic reversing valve, the oil outlet of the No. 4 check valve is connected to the port B pipeline of the three-position three-way electromagnetic reversing valve, and the three-position three-way The port P of the electromagnetic reversing valve is connected with the external port S3 of the No. 1 control valve group, the oil inlet of the No. 1 stop valve, the oil inlet of the No. 4 relief valve and the oil inlet of the No. 5 one-way valve. No. 1 accumulator pressure sensor Pacc1 is installed between it and external port S3, the oil outlet of No. 5 check valve is connected with port A of No. The port P of the reversing valve is connected to the external port S4 of the No. 1 control valve group, and the No. 1 stop valve is connected to the oil outlet of the No. 4 overflow valve and the oil storage tank pipeline.

A hydraulic auxiliary drive system integrated with a hydraulic starter described in the technical solution is characterized in that the No. 2 control valve group includes a No. 3 two-position two-way electromagnetic reversing valve, a No. Stop valve, No. 5 relief valve, No. 4 two-position two-way electromagnetic directional valve, No. 2 two-way hydraulic directional valve, No. 7 one-way valve, No. 1 two-position four-way electromagnetic directional valve, No. 5 two-position Two-way electromagnetic directional valve, No. 6 two-position two-way electromagnetic directional valve, No. 6 overflow valve, No. 8 one-way valve, three-position three-way hydraulic directional valve, No. 7 overflow valve, No. 1 two-position four-way valve Hydraulic directional valve, two-position three-way electromagnetic directional valve, No. 2 two-position four-way electromagnetic directional valve, No. 3 two-position four-way electromagnetic directional valve, No. 2 two-position four-way hydraulic directional valve Two-position four-way hydraulic reversing valve, No. 8 relief valve and No. 2 accumulator pressure sensor Pacc2. The control port X of the three-position three-way hydraulic directional valve and its port A, the external port MA of the second control valve group, the port P of the three-position two-way electromagnetic directional valve, the oil outlet of the seventh one-way valve, Port P of No. 1 two-position four-way hydraulic directional valve, port P of No. 1 two-position four-way electromagnetic directional valve, external port MG of No. 2 control valve group, port P of two-position three-way electromagnetic directional valve, Port P of No. 2 2/4-way electromagnetic directional valve and port P of No. 3 2/4-way electromagnetic directional valve are connected by pipelines, port A of No. The oil inlet pipeline connection of the No. 6 check valve is connected with the No. 2 stop valve, the oil inlet of the No. 5 relief valve, the external port Acc of the No. 2 control valve group, and the No. 4 two-position two-way solenoid The port P of the reversing valve is connected to the pipeline, and the No. 2 accumulator pressure sensor Pacc2 is installed between the port P and the external port Acc, the No. 2 stop valve, the oil outlet of the No. 5 overflow valve and the oil storage tank pipeline connection, port A of the No. Oil port pipeline connection, the control port X of the two-position two-way hydraulic directional valve is connected to the port A of the No. 1 two-position four-way electromagnetic directional valve, and the control port Y of the two-position two-way hydraulic directional valve Port B pipeline connection of No. 2/4-way solenoid directional valve.

The port T of the three-position three-way hydraulic reversing valve is connected to the oil inlet pipeline of the No. 7 relief valve, the oil outlet of the No. 7 relief valve is connected to the oil storage tank pipeline, and the Port A is connected to the control port of the No. 1 two-position four-way hydraulic directional valve, port T of the two-position three-way electromagnetic directional valve is connected to the port T of the No. The port T of the four-way electromagnetic reversing valve is connected to the pipeline of the oil storage tank, the port T of the No. Port P of the electromagnetic reversing valve, control port Y of the three-position three-way hydraulic reversing valve and its port B are connected by pipelines, and port A of the No. 1 two-position four-way hydraulic reversing valve is connected to the No. Port P of the directional valve and port P of the No. and port T of the No. The oil inlet port of the flow valve is connected with the external port D1 of the No. 2 control valve group, the oil outlet port of the No. The control port Y of the No. 2 two-position four-way hydraulic directional valve is connected with the pipeline, and the port A of the third two-position four-way electromagnetic directional valve is connected with the control port X of the No. 3 two-position four-way hydraulic directional valve. Port B of the No. 3 2/4-way electromagnetic directional valve is connected to the control port Y of the No. 3 2/4-way hydraulic directional valve, and port A of the No. The external port D2 of the No. 2 two-position four-way hydraulic reversing valve is connected with the pipeline, the port B of the No. The external port D4 of the No. 2 control valve group is connected to the pipeline, and the port B of the No. 3 two-position four-way hydraulic reversing valve is connected to the external port D5 of the No. 2 control valve group. Port P of the No. 5 two-position two-way electromagnetic directional valve is connected with the external port MB of the No. 2 control valve group and the oil inlet pipeline of the No. It is connected with the oil inlet pipeline of the No. 8 check valve, and the oil outlet of the No. 6 overflow valve and the oil outlet of the No. 8 check valve are connected with the oil storage tank pipeline.

The connection between the hydraulic control unit and the hydraulic pump assembly, the No. 1 control valve group and the No. 2 control valve group by signal lines refers to: the hydraulic control unit adjusts the control signal input end, No. 1 through the electric signal line and the displacement of the hydraulic pump Two-position two-way electromagnetic directional valve, three-position three-way electromagnetic directional valve, No. two two-way two-way electromagnetic directional valve, three-position two-way electromagnetic directional valve, No. , No. 1, two-position, four-way electromagnetic directional valve, No. 5, two-position, two-way electromagnetic directional valve, No. 6, two-position, two-way electromagnetic directional valve, two-position, three-way electromagnetic directional valve, No. 2, two-position, four-way electromagnetic directional valve The reversing valve and the control signal input end of the No. 3 two-position four-way electromagnetic reversing valve are connected, and the hydraulic control unit is connected with the hydraulic pump displacement sensor S, the No. 1 accumulator pressure sensor Pacc1 and the No. 2 accumulator through the electric signal line. Output connection of pressure sensor Pacc2.

A hydraulic auxiliary drive system integrated with a hydraulic starter described in the technical solution is characterized in that a two-position two-way hydraulic directional valve and a two-position four-way electromagnetic directional valve are connected to the second control valve group , its function is to determine whether the No. 2 accumulator is drained or keep the No. 2 accumulator in the state of draining through the opening or closing of the charging pump when the No. 4 two-position two-way electromagnetic reversing valve is in the II position. Regardless of whether the charge pump is turned on or not; when the No. 1 two-position four-way electromagnetic directional valve is in position I, the port P of the No. 1 two-position four-way electromagnetic directional valve is connected to port A, and port B is connected to port T. If the charging pump is not turned on at this time, the two-position two-way hydraulic directional valve remains at position I, and the No. 2 accumulator is in the liquid discharge state. When the No. 1 two-position four-way electromagnetic directional valve is in the II position, the No. 1 two-position four-way electromagnetic directional valve is connected to port A, port B and port T of the No. 1 two-position four-way electromagnetic directional valve. If the port P is connected, the port P is cut off. At this time, regardless of whether the charge pump is turned on or not, the two-position two-way hydraulic reversing valve remains at the I position, and the No. 2 accumulator is always in the liquid discharge state.

Compared with the prior art, the beneficial effects of the utility model are:

1. The hydraulic auxiliary drive system integrated with the hydraulic starter described in the utility model can realize the idling start-stop function of the vehicle, reduce the idling time of the engine, reduce the fuel consumption of the whole vehicle, and achieve the effect of energy saving and emission reduction;

2. The hydraulic auxiliary drive system of an integrated hydraulic starter described in the utility model has a compact structure, the structure size of the whole system is small, and the layout and installation are simple and convenient;

3. The hydraulic auxiliary drive system integrated with a hydraulic starter described in this utility model can switch the state according to the driving demand when the vehicle starts, and turn on the creep mode of the accumulator when necessary, so as to compensate for the possibility of starting the engine in a hydraulic way. The filling delay of the incoming fluid can realize the rapid start of the vehicle and start driving, and it can also reduce the working time of the engine in the low-speed area with high fuel consumption;

4. The hydraulic auxiliary drive system of the integrated hydraulic starter described in the utility model can realize the recovery of braking energy, and the recovered energy can be used to boost the vehicle by the accumulator to improve the power performance of the vehicle, and can also be used to Provide power to the hydraulic starter when starting the engine next time, reducing engine fuel consumption and improving energy utilization;

5. The hydraulic auxiliary drive system of the integrated hydraulic starter described in the utility model is equipped with a detachable hydraulic manual pump. When the vehicle is in normal operation, the hydraulic manual pump is removed to save the layout space of the hydraulic auxiliary drive system. When the accumulator is insufficiently charged due to system failure or other reasons, the hydraulic manual pump can be installed to manually charge the accumulator manually to ensure that the engine can be started normally.

Description of drawings

Below in conjunction with accompanying drawing, the utility model is further described:

Fig. 1 is a schematic structural principle diagram of a hydraulic auxiliary drive system of an integrated hydraulic starter described in the utility model;

Fig. 2 is a schematic diagram of the structural composition of the hydraulic auxiliary drive system control valve group of an integrated hydraulic starter described in the present invention and the connection relationship of each reversing valve in the parking mode;

Fig. 3 is a schematic diagram of the connection relationship of the reversing valves of the hydraulic auxiliary drive system of the integrated hydraulic starter described in the utility model under the in-situ starting mode;

Fig. 4 is a schematic diagram of the connection relationship of the reversing valves of the hydraulic auxiliary drive system of the integrated hydraulic starter described in the present invention in the open state of the creep start mode;

Fig. 5 is a schematic diagram of the connection relationship of the reversing valves of the hydraulic auxiliary drive system of the integrated hydraulic starter described in the utility model under the automatic stop state of the creep start mode;

Fig. 6 is a schematic diagram of the connection relationship of the reversing valves in the driving charging mode or the braking energy recovery mode of the hydraulic auxiliary drive system of the integrated hydraulic starter described in the present invention;

Fig. 7 is a schematic diagram of the connection relationship of the reversing valves in the hydraulic auxiliary drive system of the integrated hydraulic starter described in the utility model under the power-assisted mode of the driving accumulator;

In the figure: 1. Hydraulic control unit, 2. Power take-off device, 3. Hydraulic pump assembly, 4. No. 1 control valve group, 5. No. 1 accumulator, 6. Hydraulic starting motor, 7. One-way clutch, 8 .Engine, 9. Oil storage tank, 10. No. 2 accumulator, 11. No. 2 control valve group, 12. No. 1 hydraulic hub motor, 13. No. 2 hydraulic hub motor, 14. Load mass body of No. 1 hydraulic motor , 15. Load mass body of No. 2 hydraulic motor, 16. Detachable hydraulic hand pump, 17. Three-position three-way electromagnetic reversing valve, 18. Hydraulic pump, 19. Charge pump, 20. No. 1 one-way valve, 21. No. 1 overflow valve, 22. No. 2 one-way valve, 23. No. 2 overflow valve, 24. No. 3 overflow valve, 25. No. 1 two-position two-way electromagnetic reversing valve, 26. No. 1 cut-off valve Valve, 27. No. 4 overflow valve, 28. No. 2 two-position two-way electromagnetic reversing valve, 29. No. 3 one-way valve, 30. No. 4 one-way valve, 31. No. 5 one-way valve, 32. Three No. 2, 2-way electromagnetic directional valve, 33. No. 6 one-way valve, 34. No. 2 stop valve, 35. No. 5 overflow valve, 36. No. 4, 2-position, 2-way electromagnetic directional valve, 37. Two-position Two-way hydraulic directional valve, 38. No. 7 one-way valve, 39. No. 1, two-position, four-way electromagnetic directional valve, 40. No. 5, two-position, two-way electromagnetic directional valve, 41. No. 6, two-position, two-way electromagnetic directional valve Reversing valve, 42. No. 6 overflow valve, 43. No. 8 one-way valve, 44. Three-position three-way hydraulic reversing valve, 45. No. 7 overflow valve, 46. No. 1, two-position four-way hydraulic reversing valve Valve, 47. Two-position three-way electromagnetic directional control valve, 48. No. 2 two-position four-way electromagnetic directional control valve, 49. No. 3 two-position four-way electromagnetic directional control valve, 50. No. 2 two-position four-way hydraulic directional control valve Valve, 51. No. 3 two-position four-way hydraulic reversing valve, 52. No. 8 relief valve, S. Hydraulic pump displacement sensor, Pacc1. No. 1 accumulator pressure sensor, Pacc2. No. 2 accumulator pressure sensor .

detailed description

Below in conjunction with accompanying drawing, the utility model is described in detail:

Referring to Fig. 1, a hydraulic auxiliary drive system for an integrated hydraulic starter described in the present invention includes a hydraulic control unit 1, a power take-off device 2, a hydraulic pump assembly 3, a No. 1 control valve group 4, and a No. 1 accumulator 5 , hydraulic starter motor 6, one-way clutch 7, engine 8, oil storage tank 9, No. 2 accumulator 10, No. 2 control valve group 11, No. 1 hydraulic hub motor 12, No. 2 hydraulic hub motor 13, No. 1 hydraulic motor The load mass body 14, the load mass body 15 of the No. 2 hydraulic motor and the detachable hydraulic manual pump 16.

Referring to Fig. 2, the hydraulic pump assembly 3 includes a hydraulic pump 18, a charge pump 19, a No. 1 check valve 20, a No. 1 overflow valve 21, a No. 2 check valve 22, a No. 2 overflow valve 23, and a No. 3 overflow valve. 24. No. 1 two-position two-way electromagnetic reversing valve 25. The hydraulic pump 18 is a two-way plunger type variable pump, which provides high-pressure oil for the No. 1 hydraulic hub motor 12 , the No. 2 hydraulic hub motor 13 , the No. 1 accumulator 5 and the No. 2 accumulator 10 . The hydraulic control unit 1 issues a PWM control command to control the opening of the swash plate of the hydraulic pump 18 to achieve the purpose of adjusting the displacement. At the same time, the signal output terminal of the hydraulic pump displacement sensor S is connected to the pin wire of the hydraulic control unit 1 to obtain The actual displacement of the hydraulic pump 18. The charge pump 19 is a one-way quantitative pump, which is coaxial with the hydraulic pump 18, and absorbs oil from the oil storage tank 9 to replenish stable oil for the oil circuit. The oil outlet of the charge pump 19 and the oil inlet of No. 1 check valve 20, the oil inlet of No. 1 overflow valve 21, the oil inlet of No. 2 check valve 22, the oil inlet of No. 2 overflow valve 23, and the oil inlet of No. The oil inlet of the relief valve 24 is connected to the port P of the No. 1 two-position two-way electromagnetic reversing valve 25 through a pipeline. No. 1 check valve 20 and No. 2 check valve 22 only allow oil to flow from charge pump 19 to the main oil circuit of the system, and No. 1 overflow valve 21 and No. 2 overflow valve 23 are used to limit the maximum pressure of the main oil circuit. The third relief valve 24 is used to limit the outlet pressure of the charge pump. The No. 1 two-position two-way electromagnetic reversing valve 25 is an electromagnetic reversing valve, operated by an electromagnet, and reset by a spring. Its control signal input end is connected with the pin of the hydraulic control unit 1 through a wire, and its port A is connected to the pin of the hydraulic pump assembly 3. The external port M3 is connected to the pipeline, and its function is to control the switch of the oil supply circuit. The two oil ports of the hydraulic pump 18 are respectively connected with the M1 and M2 pipelines.

Referring to Fig. 1 and Fig. 2, the power take-off device 2 can be one or more sets of speed change gears, and the installation position of the power take-off device 2 can be the power output end of the engine or the power output end of the transmission according to the actual situation. Said technical scheme takes the power output end of the engine as an embodiment here. The output shaft of the engine 8 and the input shaft of the power take-off device 2 are connected by a spline pair, and the output shaft of the power take-off device 2 and the input shaft of the hydraulic pump assembly 3 are connected by a universal joint or a spline pair. The hydraulic pump 18 and charge oil pump 19 are coaxial pumps, and the power take-off device 2 provides power for hydraulic pump 18 and charge oil pump 19 . The external port M1 of the hydraulic pump assembly 3 is connected to the external port S1 of the first control valve group 4 , and the external port M2 of the hydraulic pump assembly 3 is connected to the external port S2 of the first control valve group 4 . The external port M1 of the hydraulic pump assembly 3 is connected to the external port MA of the second control valve group 11, the external port M2 of the hydraulic pump assembly 3 is connected to the external port MB of the second control valve group 11, and the hydraulic pump assembly 3 The external connection port M3 of the control valve group 11 is connected with the external connection port MG pipeline of the second control valve group 11. Port D2 and port D3 of No. 2 control valve group 11 are sequentially connected to the two oil inlet and outlet pipelines of No. 1 hydraulic hub motor 12, and port D4 and port D5 of No. 2 control valve group 11 are sequentially connected to No. 2 hydraulic hub motor 13 The two inlet and outlet pipelines are connected. The No. 1 hydraulic hub motor 12 and the No. 2 hydraulic hub motor 13 are both radial piston type bidirectional quantitative motors, and splines are used between the load mass body 14 of the No. 1 hydraulic motor and the load mass body 15 of the No. 2 hydraulic motor respectively. The secondary connection or the two are coaxially connected, and the casing drain ports of the No. 1 hydraulic hub motor 12 and the No. 2 hydraulic hub motor 13 are connected to the external port D1 of the No. 2 control valve group 11 through pipelines. The detachable hydraulic manual pump 16 is installed between the oil port of the No. 1 accumulator 5 and the oil storage tank 9 with a pipeline when in use. At this time, the system is in the parking mode, and the No. 1 accumulator 5 is disconnected from the hydraulic circuit. ; When not in use, remove the detachable hydraulic hand pump 16 to save layout space.

Referring to Fig. 2, the No. 1 control valve group 4 of the hydraulic auxiliary drive system of an integrated hydraulic starter described in the utility model includes a three-position three-way electromagnetic reversing valve 17, a No. 1 stop valve 26, and a No. 4 overflow valve. 27. No. 2 two-position two-way electromagnetic reversing valve 28, No. 3 check valve 29, No. 4 check valve 30, No. 5 check valve 31 and No. 1 accumulator pressure sensor Pacc1. Port S1 , port S2 , port S3 and port S4 shown in the figure are the external ports of the No. 1 control valve group 4 . The hydraulic control unit 1 is connected to the control signal input ends of the three-position three-way electromagnetic reversing valve 17 and the second two-position two-way electromagnetic reversing valve 28 through electric signal lines.

Referring to Fig. 2, the oil inlet of No. 3 check valve 29 is connected with the external port S1 of No. 1 control valve group 4, and the oil inlet of No. 4 check valve 30 is connected with the external port S2 of No. 1 control valve group 4. Pipeline connection, the oil outlet of the third check valve 29 is connected with the port A of the three-position three-way electromagnetic reversing valve 17, the oil outlet of the fourth check valve 30 is connected with the three-position three-way electromagnetic reversing valve 17 for the port B tubing connection. The three-position three-way electromagnetic reversing valve 17 is a normally closed electromagnetic reversing valve. When it is necessary to charge the No. 1 accumulator 5, if the oil at the input port A is high-pressure oil at this time, the three-position three-way The electromagnetic reversing valve 17 is switched to the I position, and its port A and port P are connected. On the contrary, if the oil in the input port B is high-pressure oil at this time, the three-position three-way electromagnetic reversing valve 17 is switched to III. position, its port B and port P are connected to realize the filling of No. 1 accumulator 5 . The port P of the three-position three-way electromagnetic reversing valve 17 and the external port S3 of the No. 1 control valve group 4, the oil inlet of the No. 1 stop valve 26, the oil inlet of the No. 4 relief valve 27, and the oil inlet of the No. 5 one-way valve 31 The port is connected with the pipeline, and a No. 1 accumulator pressure sensor Pacc1 is installed between the port P and the external port S3. The No. 1 control valve group 4 is connected with the oil port of the No. 1 accumulator 5 through the external port S3 by a pipeline. The No. 1 accumulator 5 is a gas-isolated accumulator. The hydraulic control unit 1 is connected to the output end of the No. 1 accumulator pressure sensor Pacc1 through an electrical signal line to collect the pressure signal of the No. 1 accumulator, which is used to judge the pressure of the No. 1 accumulator. Whether the liquid filling and discharging of the device 5 meet the conditions. The oil outlet of No. 5 one-way valve 31 is connected with port A of No. 2 two-position two-way electromagnetic directional valve 28, and the port P of No. two two-position two-way electromagnetic directional valve 28 is connected with No. 1 control valve group 4 The external port S4 is connected with the pipeline, and the No. 1 shut-off valve 26 is connected with the oil outlet of the No. 4 relief valve 27 and the oil storage tank 9 with pipelines. The No. 4 overflow valve 27 is used to limit the maximum pressure of the No. 1 accumulator 5 discharge oil circuit. The No. 2 two-position two-way electromagnetic reversing valve 28 is used to control the discharge of the No. one accumulator 5. When the No. two two-position two-way electromagnetic reversing valve 28 is switched to the II position, the second two-position two-way electromagnetic The port A of the reversing valve 28 is connected to the port P, and the oil in the No. 1 accumulator 5 enters the hydraulic starter motor 6 to drive the hydraulic starter motor 6 to output power. The output shaft of the hydraulic starter motor 6 is mechanically connected to the input shaft of the one-way clutch 7, and the output shaft of the one-way clutch 7 is mechanically connected to the crankshaft of the engine.

Referring to Fig. 2, the No. 2 control valve group 11 of the hydraulic auxiliary drive system of an integrated hydraulic starter described in the utility model includes a No. 3 two-position two-way electromagnetic reversing valve 32, a No. Stop valve 34, No. 5 overflow valve 35, No. 4 2-position 2-way electromagnetic directional valve 36, 2-position 2-way hydraulic directional valve 37, No. 7 one-way valve 38, No. 1 2-position 4-way electromagnetic directional valve 39. No. 5, 2-position, 2-way electromagnetic directional valve 40, No. 6, 2-position, 2-way electromagnetic directional valve 41, No. 6 overflow valve 42, No. 8 one-way valve 43, three-position, 3-way hydraulic directional valve 44, No. 7 overflow valve 45, No. 1 two-position four-way hydraulic directional control valve 46, two-position three-way electromagnetic directional control valve 47, No. 2 two-position four-way electromagnetic directional control valve 48, No. 3 two-position four-way electromagnetic directional control valve Valve 49, No. 2 two-position four-way hydraulic directional valve 50, No. 3 two-position four-way hydraulic directional valve 51, No. 8 overflow valve 52 and No. 2 accumulator pressure sensor Pacc2. The hydraulic control unit 1 connects the electric signal line and the No. 3 two-position two-way electromagnetic directional valve 32, the No. four two-position two-way electromagnetic directional valve 36, the No. Pass electromagnetic reversing valve 40, No. 6 two-position, two-way electromagnetic reversing valve 41, two-position, three-way electromagnetic reversing valve 47, No. 2, two-position, four-way electromagnetic reversing valve 48, and No. 3, two-position, four-way electromagnetic reversing valve The control signal input terminal of the valve 49 is connected.

Referring to Fig. 2, the control port X of the three-position three-way hydraulic reversing valve 44 and its port A, the external port MA of the second control valve group 11, the port P of the third two-position two-way electromagnetic reversing valve 32, the single port of the seventh The oil outlet of the directional valve 38, the port P of the No. 1 two-position four-way hydraulic directional valve 46, the port P of the No. 1 two-position four-way electromagnetic directional valve 39, the external port MG of the No. 2 control valve group 11, two The port P of the three-position electromagnetic directional valve 47, the port P of the second two-position four-way electromagnetic directional valve 48, and the port P of the third two-position four-way electromagnetic directional valve 49 are connected by pipelines, The port A leading to the electromagnetic reversing valve 32 is connected with the oil inlet pipeline of the No. 6 check valve 33 . The No. 3 two-position two-way electromagnetic reversing valve 32 is used as the on-off valve for the liquid filling of the No. 2 accumulator 10 . When the No. 3 two-position two-way electromagnetic reversing valve 32 is switched to the II position, the port A and the port P are connected, and the No. 2 accumulator 10 is filled with liquid; otherwise, when it is switched to the I position, the liquid filling is stopped. The oil outlet of No. 6 one-way valve 33 and the oil inlet of No. 2 stop valve 34, No. 5 overflow valve 35, the oil port of No. 2 accumulator 10 and the port of No. 4 two-position two-way electromagnetic reversing valve 36 The port P is connected to the pipeline, and the No. 2 accumulator pressure sensor Pacc2 is installed between the port P and the external port Acc. The oil outlets of the No. 2 stop valve 34 and the No. 5 overflow valve 35 are connected with the oil storage tank 9. . The No. 5 overflow valve 35 is used to limit the maximum pressure of the No. 2 accumulator 10 filling oil circuit. The No. 2 accumulator 10 is a gas-isolated accumulator. The hydraulic control unit 1 is connected to the output end of the pressure sensor Pacc2 of the No. 2 accumulator through an electric signal line. The pressure sensor Pacc2 detects the pressure of the accumulator so as to judge the Whether the charging and discharging of the accumulator 10 meets the conditions. The port A of the No. 4 two-position two-way electromagnetic selector valve 36 is connected to the port P of the two-position two-way hydraulic selector valve 37 by pipeline. No. four two-position two-way electromagnetic reversing valve 36 is used as the on-off valve of No. two accumulator 10 discharging liquid. Port A of the two-position two-way hydraulic reversing valve 37 is connected with the oil inlet pipeline of the No. 7 one-way valve 38 .

Referring to Fig. 2, the control port X of the two-position two-way hydraulic directional control valve 37 is connected to the port A of the No. The port B of the No. 1 two-position four-way electromagnetic reversing valve 39 is connected to the pipeline. A two-position, two-way hydraulic directional valve 37 and a No. 1, two-position, four-way electromagnetic directional valve 39 are connected to the No. 2 control valve group 11. , whether the No. 2 accumulator 10 is drained or whether the No. 2 accumulator 10 is always in the liquid discharge state regardless of whether the charge pump 19 is turned on or not by opening or closing the charge pump 19 . Specifically, when the No. 1 two-position, four-way electromagnetic reversing valve 39 is controlled to be in the I position, the port P and port A of the No. one two-position, four-way electromagnetic reversing valve 39 are connected, and port B is connected with port T. If the oil charge pump 19 is not turned on at this time, the two-position two-way hydraulic directional control valve 37 remains at the I position, and the No. 2 accumulator 10 is in the state of discharging liquid. The dynamic reversing valve 37 is switched to the II position, and the second accumulator 10 stops discharging liquid; when the No. A. Port B and port T are connected, and port P is cut off. At this time, regardless of whether the charging pump 19 is turned on or not, the two-position two-way hydraulic reversing valve 37 is always kept at the I position, and the second accumulator 10 is always in the liquid discharge state . Using the above method, during the process of starting the engine by the hydraulic starter motor 6, the No. 2 accumulator 10 can be drained as needed, that is, the creep mode of the accumulator is turned on. If the engine 8 is started to the target speed, the charge pump 19 is opened, the No. 2 accumulator 10 stops draining, that is, the creep mode of the accumulator is closed, and the vehicle enters a normal driving state. If the driver still needs to turn on the creep mode of the accumulator at this time, then the No. 1 two-position four-way electromagnetic selector valve 39 can be in the II position by controlling the two-position two-way hydraulic selector valve 37 to remain at the I position. No. 2 accumulator 10 is in the state of discharging liquid all the time.

Referring to Fig. 2, the port T of the three-position three-way hydraulic reversing valve 44 is connected to the oil inlet pipeline of the No. 7 overflow valve 45, and the oil outlet of the No. 7 overflow valve 45 is connected to the oil storage tank 9 pipeline. When there is a large pressure difference between the two control ports of the three-position three-way hydraulic reversing valve 44, the low-pressure oil flows into the oil storage tank 9 from the port T of the three-position three-way hydraulic reversing valve 44 through the No. 7 relief valve 45 , No. 7 relief valve 45 is used as a back pressure valve. The three-position three-way hydraulic reversing valve 44 and the No. 7 overflow valve 45 form a cooling circuit. Port A of the two-position three-way electromagnetic reversing valve 47 is connected to the control port of the No. The port T of the electromagnetic reversing valve 48, the port T of the No. 3 two-position four-way electromagnetic reversing valve 49 are connected to the pipeline of the oil storage tank 9, and the port T of the No. 1 two-position four-way hydraulic reversing valve 46 is connected to the No. 5 two-position Port A of the two-way electromagnetic reversing valve 40, port P of the No. The port A of the four-position hydraulic directional valve 46 is connected to the port P of the No. 2 two-position four-way hydraulic directional valve 50 and the port P of the No. three two-position four-way hydraulic directional valve 51. The port B of the hydraulic reversing valve 46 is connected with the port T of the No. 2 two-position four-way hydraulic reversing valve 50 and the port T of the No. three two-position four-way hydraulic reversing valve 51. The port A of the reversing valve 48 is connected with the control port X of the No. 2 two-position four-way hydraulic reversing valve 50, the oil inlet port of the No. 8 relief valve 52, and the external port D1 of the No. 2 control valve group 11. The oil outlet of the No. 2 overflow valve 52 is connected to the pipeline of the oil storage tank 9, and the port B of the No. 2 two-position four-way electromagnetic reversing valve 48 is connected to the control port Y of the No. , the port A of the No. 3 two-position four-way electromagnetic reversing valve 49 is connected to the control port X of the No. three two-position four-way hydraulic reversing valve 51, and the port B of the No. The control port Y of the No. 2 two-position four-way hydraulic reversing valve 51 is connected to the pipeline, and the port A of the No. two two-position four-way hydraulic reversing valve 50 is connected to the external port D2 of the No. Port B of the two-position four-way hydraulic reversing valve 50 is connected to the external port D3 of the second control valve group 11, and port A of the third two-position four-way hydraulic reversing valve 51 is connected to the external connection The port D4 is connected to the pipeline, and the port B of the No. 3 two-position four-way hydraulic reversing valve 51 is connected to the external port D5 of the No. 2 control valve group 11. The port P of No. 5 two-position two-way electromagnetic reversing valve 40 is connected with the external port MB of No. two control valve group 11 and the oil inlet pipeline of No. six relief valve 42, and the No. six two-position two-way electromagnetic reversing valve Port A of 41 is connected with the oil inlet pipeline of No. eight check valve 43, and the oil outlet of No. six relief valve 42 and the oil outlet of No. eight check valve 43 are connected with oil storage tank 9 pipelines. No. 5, two-position, two-way electromagnetic directional valve 40 and No. six, two-position, two-way electromagnetic directional valve 41 are used for switching the hydraulic circuit between an open circuit and a closed circuit. When No. five two-position two-way electromagnetic selector valve 40 and No. six two-position two-way electromagnetic selector valve 41 are all in position I, it is an open circuit; when No. five two-position two-way electromagnetic selector valve 40 and No. When the two-position two-way electromagnetic reversing valve 41 is located at the II position, it is a closed circuit.

Referring to Figures 2 to 7, the following describes in detail the switching of each valve in the system in the parking mode, in-situ start mode, creep start mode, driving charging mode, braking energy recovery mode and driving accumulator boosting mode locations and the functions they fulfill. The working path in the figure is marked by a thick solid line with an arrow.

Referring to Fig. 2, a hydraulic auxiliary drive system integrated with a hydraulic starter according to the present invention works in the parking mode. In this mode, the engine 8 is turned off, and all components of the system do not work. At this time, No. 1 two-position two-way electromagnetic directional valve 25, No. two two-position two-way electromagnetic directional valve 28, No. three two-position two-way electromagnetic directional valve 32, and No. four two-position two-way electromagnetic directional valve 36 , No. 1 two-position four-way hydraulic directional valve 46, two-position three-way electromagnetic directional valve 47, No. 2 two-position four-way electromagnetic directional valve 48, No. 3 two-position four-way electromagnetic directional valve 49, No. 2 two-way The four-position hydraulic directional valve 50, the three-position four-way hydraulic directional valve 51, the fifth two-position two-way electromagnetic directional valve 40, and the sixth two-position two-way electromagnetic directional valve 41 are all in position I, and the three-position The three-way electromagnetic reversing valve 17 is in the II position. No. 1, two-position, four-way electromagnetic reversing valve 39 is in position I. At this time, since the engine 8 is turned off and the charge pump 19 is closed, there is no pressure difference between port P and port T of No. 1, two-position, four-way electromagnetic reversing valve 39. The two-way hydraulic reversing valve 37 is in the I position due to the effect of the back-moving spring. There is no pressure difference between the upper and lower ports of the three-position three-way hydraulic reversing valve 44, which is in position II.

Referring to Fig. 3, a hydraulic auxiliary drive system integrated with a hydraulic starter described in the present invention works in the in-situ starting mode. The hydraulic control unit 1 issues an instruction, the No. 2 two-position two-way electromagnetic reversing valve 28 is switched to the II position, the No. 1 accumulator 5 provides hydraulic energy for the hydraulic starter motor 6, and the hydraulic starter motor 6 drives the engine to start in situ. The working positions of the remaining valve group components remain unchanged with the parking mode.

Referring to Fig. 4 and Fig. 5, a hydraulic auxiliary drive system of an integrated hydraulic starter described in the utility model works in the creep start mode, wherein Fig. 4 shows that the system is in the creep start mode open state, and Fig. 5 shows that the system is in the automatic stop state of creep start mode.

Referring to FIG. 4 , during the in-situ starting mode, the hydraulic control unit 1 can be selected to issue an instruction to control the No. 4 two-position two-way electromagnetic reversing valve 36 to switch to the II position. Here, as an example, the input control signal of the No. 4 two-position two-way electromagnetic reversing valve 36 may be a signal for the driver to release the service brake pedal. Simultaneously, three-position three-way hydraulic reversing valve 44 is switched to 1 position because there is pressure difference between the upper and lower ports. No. 2, two-position, four-way electromagnetic directional valve 48 and No. three, two-position, four-way electromagnetic directional valve 49 switch to the II position, then No. two, two-position, four-way hydraulic directional control valve 50 and No. The pressure at the control port Y of the valve 51 is greater than that at the control port X, and is switched to position II. The working positions of the rest of the valve group components remain the same as in the original starting mode. At this time, the No. 2 accumulator 10 enters the liquid discharge state, and the No. 2 accumulator 10, the No. 4 two-position two-way electromagnetic reversing valve 36, the two-position two-way hydraulic reversing valve 37, the seventh one-way valve 38, No. 1, two-position, four-way hydraulic directional valve 46, No. 2, two-position, four-way hydraulic directional valve 50, No. 3, two-position, four-way hydraulic directional valve 51, No. 1 hydraulic hub motor 12, No. 2 hydraulic hub motor 13, The No. 6 two-position two-way electromagnetic reversing valve 41 and the oil storage tank 9 form an open circuit, which drives the No. 1 hydraulic hub motor 12 and the No. 2 hydraulic hub motor 13 to rotate, and drives the vehicle into creep mode.

Referring to Fig. 5, when the creep start mode is in progress, when the engine 8 is started to the target speed by the hydraulic starter motor 6, the No. 2 two-position two-way solenoid valve 28 switches back to the I position, and the No. 1 accumulator 5 stops discharging. liquid, the hydraulic starter motor 6 stops working. Since the engine 8 has been started, the charge oil pump 19 coaxial with it is turned on to replenish oil in the oil circuit. When the pressure of the control port X of the two-way hydraulic reversing valve 37 is greater than its control port Y, the two-position two-way hydraulic reversing valve 37 switches to the II position, and the discharge of the second accumulator 10 stops, and the accumulator is in creep mode. stop. The working positions of the rest of the valve group components are kept unchanged from the open state of the creep start mode. Thereafter, the control valve group returns to its original position, and the vehicle enters a normal driving state.

Referring to FIG. 6 , a hydraulic auxiliary drive system integrated with a hydraulic starter described in the present invention works in the driving charging mode. In the driving charging mode, No. 1 two-position two-way electromagnetic directional valve 25, No. two two-position two-way electromagnetic directional valve 28, No. 1 two-position four-way electromagnetic directional valve 39, No. Dynamic reversing valve 46, 2-position, 3-way electromagnetic directional valve 47, No. 2, 2-position, 4-way electromagnetic directional valve 48, No. 3, 2-position, 4-way electromagnetic directional valve 49, No. 2, 2-position, 4-way hydraulic directional valve 50 , No. three two-position four-way hydraulic directional control valve 51 is in the I position, No. five two-position two-way electromagnetic directional control valve 40, No. six two-position two-way electromagnetic directional control valve 41, three-position three-way hydraulic directional control valve 44 , No. 4 two-position two-way electromagnetic directional control valve 36 and two-position two-way hydraulic directional control valve 37 are all in the II position. The three-position three-way electromagnetic reversing valve 17 receives the control command and switches to the I position, the No. three two-position two-way electromagnetic reversing valve 32 switches to the II position, and the oil flows from the oil storage tank 9 through the hydraulic pump 18 and the No. three one-way valve 29 , three-position three-way electromagnetic reversing valve 17 and No. three two-position two-way electromagnetic reversing valve 32 and No. six check valve 33 are charged into No. 1 accumulator 5 and No. 2 accumulator 10 respectively.

When the vehicle needs to take non-emergency braking during normal driving, the system enters the braking energy recovery mode. At this time, the working positions of each valve of the system are the same as the driving charging mode, as shown in Figure 6.

Referring to Fig. 7, a hydraulic auxiliary drive system integrated with a hydraulic starter described in the present invention works in the power-assisted mode of the driving accumulator. When the vehicle was running normally, the No. two two-position two-way electromagnetic reversing valve 28 was switched to the 1 position, and the hydraulic starter motor did not work. When the driver presses the booster switch of the accumulator, the hydraulic control unit 1 sends a control command, and the No. 1 two-position four-way electromagnetic reversing valve 39 is switched to the II position, and its port A and port B are both connected to the oil storage tank 9 . At this time, regardless of whether the charging pump 19 is turned on or not, there is no pressure difference between the control port X and the control port Y of the two-position two-way hydraulic directional control valve 37. Under the action of the return spring, the two-position two-way hydraulic directional control valve 37 is always Stay in I position. The working positions of the remaining valve group components are consistent with the creep start mode.

The parts not mentioned in the utility model and other achievable working modes can be realized by adopting or referring to existing disclosed patent schemes.

The working position of each reversing valve in each working mode is shown in Table 1 below.

The principle and characteristics of the hydraulic auxiliary drive system of the integrated hydraulic starter:

1. The hydraulic auxiliary drive system equipped with this integrated hydraulic starter can change the traditional rear-drive vehicle into a full-drive vehicle according to the driver's needs, improving the power of the vehicle; in the parking mode, the engine stops working, reducing fuel consumption. consume.

2. The system determines the vehicle working mode according to the current vehicle driving state and the driver's operation intention, including the vehicle speed, engine speed, accumulator pressure, accelerator pedal opening, brake pedal opening and other signals. By switching the working position of each valve To realize the switching of the system between the parking mode, the in-situ starting mode, the creeping starting mode, the driving charging mode, the braking energy recovery mode, the driving accumulator assisting mode and other modes.

3. The vehicle starts the engine with a hydraulic starter motor. During this process, according to the driver’s needs, if the driver is in a hurry to drive at this time, the creep assist mode can be turned on. When the engine is started, the creep power will The driving mode is automatically turned off, and the vehicle enters the normal driving state; if the driver is not in a hurry to drive, the engine can be started on the spot, and then the vehicle enters the normal driving state. Through the above method, it is ensured that the vehicle can quickly restart and start running without delay.

4. When the vehicle is in non-emergency braking, according to the brake pedal signal, the system reasonably distributes the braking torque, and at the same time enters the braking energy recovery mode, converting the kinetic energy of the vehicle into hydraulic energy and storing it in the accumulator, so that it can be restarted next time. It is used when starting the engine or using the accumulator to power the vehicle, which improves the energy utilization rate of the vehicle and achieves the effect of energy saving.

5. When the accumulator of the hydraulic starter motor is insufficiently charged due to failure or other reasons, a detachable hydraulic manual pump can be installed to manually charge the accumulator by manpower to ensure that the engine can start normally. When the detachable hydraulic hand pump is not in use, it can be removed to save layout space.

According to the principle and characteristics of the above-mentioned system, it can be seen that the utility model integrates a hydraulic starter and its supporting control valve group system on the basis of the hydraulic front wheel auxiliary drive system, and increases the vehicle working mode, including parking mode, in-situ Starting mode, creeping starting mode, driving charging mode, braking energy recovery mode and driving accumulator boosting mode, etc. The utility model can not only improve the power performance of the whole vehicle, but also effectively reduce the fuel consumption at idling speed of the engine; through the hydraulic auxiliary drive system of the integrated hydraulic starter, the vehicle can be quickly restarted and start running; through the recovery of braking energy, the energy It can be effectively utilized to further realize energy saving and environmental protection; it has a certain failure emergency response capability; it is easy to implement in engineering and has a good application prospect.

Claims (4)

1. A hydraulic auxiliary drive system with an integrated hydraulic starter, characterized in that: the hydraulic auxiliary drive system with an integrated hydraulic starter includes a hydraulic control unit (1), a power take-off device (2), a hydraulic pump assembly (3), No. 1 control valve group (4), No. 1 accumulator (5), hydraulic starter motor (6), one-way clutch (7), engine (8), oil storage tank (9), No. 2 accumulator energy device (10), No. 2 control valve group (11), No. 1 hydraulic hub motor (12), No. 2 hydraulic hub motor (13), load mass body (14) of No. 1 hydraulic motor, and No. 2 hydraulic motor Load mass body (15) and detachable hydraulic manual pump (16); The output shaft of the engine (8) and the input shaft of the power take-off device (2) are connected by a spline pair, and the output shaft of the power take-off device (2) and the input shaft of the hydraulic pump assembly (3) are connected by a universal joint or The spline pair is connected, the hydraulic pump assembly (3) and the No. 1 control valve group (4) are connected by pipelines, and the No. 1 control valve group (4) is connected to the oil of the No. 1 accumulator (5) through the external port S3. The ports are connected by pipelines, the No. 1 control valve group (4) is connected with the hydraulic starter motor (6) through the external port S4, and the output shaft of the hydraulic starter motor (6) is connected with the one-way clutch (7). The input shaft is mechanically connected, the output shaft of the one-way clutch (7) is mechanically connected to the engine crankshaft, the hydraulic pump assembly (3) is connected to the No. 2 control valve group (11) by pipeline, and the No. 2 control valve group (11) Through the connection between the external port Acc and the oil port of the No. 2 accumulator (10), the port D2 and port D3 of the No. 2 control valve group (11) are connected with the two ports of the No. 1 hydraulic hub motor (12) The oil inlet and outlet pipelines are connected, the port D4 and the port D5 of the second control valve group (11) are connected with the two oil inlet and outlet pipelines of the second hydraulic hub motor (13) in turn, and the first hydraulic hub motor (12) and the The load mass body (14) of the No. 1 hydraulic motor is connected by a spline pair or the two are coaxially connected, and the load mass body (15) of the No. 2 hydraulic hub motor (13) and the No. 2 hydraulic motor is connected by a spline. The key pairs are connected or both are coaxially connected. The hydraulic pump assembly (3), the No. 1 control valve group (4), the hydraulic starting motor (6) and the No. 2 control valve group (11) adopt pipelines and oil storage tanks (9 ), the hydraulic control unit (1) is connected with the hydraulic pump assembly (3), the No. 1 control valve group (4) and the No. 2 control valve group (11) with signal lines; The oil tanks (9) are connected by pipelines, and the detachable hydraulic manual pump (16) is connected with the oil port of the No. 1 accumulator (5). 2. A hydraulic auxiliary drive system integrating a hydraulic starter according to claim 1, characterized in that the hydraulic pump assembly (3) and the No. 1 control valve group (4) are connected by pipelines, The pipeline connection between the hydraulic pump assembly (3) and the second control valve group (11) refers to: The hydraulic pump assembly (3) includes a hydraulic pump (18), a charge pump (19), a No. 1 check valve (20), a No. 1 overflow valve (21), a No. 2 check valve (22), and a No. 2 check valve (22). No. 1 overflow valve (23), No. 3 overflow valve (24), No. 1 two-position two-way electromagnetic reversing valve (25); the external port M1 of the hydraulic pump assembly (3) and the No. 1 control valve group (4) The external port S1 of the hydraulic pump assembly (3) is connected to the external port S2 of the hydraulic pump assembly (3) and the external port S2 of the first control valve group (4); the external port M1 of the hydraulic pump assembly (3) is connected to the second control valve The external port MA of group (11) is connected to the pipeline, the external port M2 of the hydraulic pump assembly (3) is connected to the external port MB of the second control valve group (11), and the external port M3 of the hydraulic pump assembly (3) is connected to The external port MG pipeline of No. 2 control valve group (11) is connected. 3. The hydraulic auxiliary drive system of an integrated hydraulic starter according to claim 1, wherein said No. 1 control valve group (4) includes a three-position three-way electromagnetic reversing valve (17), a No. globe valve (26), No. 4 overflow valve (27), No. 2 two-position two-way electromagnetic reversing valve (28), No. 3 check valve (29), No. 4 check valve (30), No. 5 The check valve (31) is connected to the No. 1 accumulator pressure sensor (Pacc1); the oil inlet of the No. 3 check valve (29) is connected to the external port S1 of the No. 1 control valve group (4), and the No. 4 single The oil inlet of the directional valve (30) is connected to the external port S2 of the No. 1 control valve group (4), and the oil outlet of the No. 3 check valve (29) is connected to the three-position three-way electromagnetic reversing valve (17). The port A pipeline connection of the No. 4 check valve (30) is connected with the port B pipeline of the three-position three-way electromagnetic reversing valve (17), and the oil outlet of the three-position three-way electromagnetic reversing valve (17) Port P and the external port S3 of the No. 1 control valve group (4), the oil inlet of the No. 1 stop valve (26), the oil inlet of the No. 4 relief valve (27), and the oil inlet of the No. 5 one-way valve (31) connection, and a No. 1 accumulator pressure sensor (Pacc1) is installed between the port P and the external port S3, and the oil outlet of the No. 5 check valve (31) is connected to the No. ), the port P of the No. 2 two-position two-way electromagnetic reversing valve (28) is connected with the external port S4 of the No. No. overflow valve (27) oil outlet and oil storage tank (9) pipeline connection; The No. 2 control valve group (11) includes No. 3 two-position two-way electromagnetic reversing valve (32), No. 6 check valve (33), No. 2 stop valve (34), No. 5 overflow valve (35 ), No. 4, two-position, two-way electromagnetic directional valve (36), two-position, two-way hydraulic directional valve (37), No. 7 check valve (38), No. 1, two-position, four-way electromagnetic directional valve (39) , No. 5, two-position, two-way electromagnetic directional valve (40), No. 6, two-position, two-way electromagnetic directional valve (41), No. 6 overflow valve (42), No. 8 one-way valve (43), three-position three-way valve Through hydraulic directional valve (44), No. 7 relief valve (45), No. 1 two-position four-way hydraulic directional valve (46), two-position three-way electromagnetic directional valve (47), No. 2 two-position four-way Electromagnetic reversing valve (48), No. 3 two-position, four-way electromagnetic reversing valve (49), No. 2, two-position, four-way hydraulic reversing valve (50), No. 3, two-position, four-way hydraulic reversing valve (51), The No. 8 relief valve (52) and the No. 2 accumulator pressure sensor (Pacc2); the control port X of the three-position three-way hydraulic reversing valve (44) and its port A, and the external port of the No. 2 control valve group (11) Port P of MA, No. three two-position two-way electromagnetic directional valve (32), oil outlet of No. seven check valve (38), port P of No. one two-position four-way hydraulic directional valve (46), one Port P of No. 2 two-position four-way electromagnetic directional valve (39), external port MG of No. 2 control valve group (11), port P of No. 2 two-position four-way electromagnetic directional valve (47), The port P of the electromagnetic reversing valve (48) is connected to the port P of the No. The oil inlet pipeline of the check valve (33) is connected, the oil outlet of the No. 6 check valve (33) is connected with the oil inlet of the No. The external port Acc of the control valve group (11) is connected to the port P of the No. 4 two-position two-way electromagnetic reversing valve (36), and the No. 2 accumulator pressure sensor is installed between the port P and the external port Acc (Pacc2), No. 2 cut-off valve (34), No. 5 overflow valve (35) oil outlet is connected with oil storage tank (9) pipeline, port A of No. 4 two-position two-way electromagnetic reversing valve (36) It is connected with the port P pipeline of the two-position two-way hydraulic reversing valve (37), and the port A of the two-position two-way hydraulic reversing valve (37) is connected with the oil inlet pipeline of the No. 7 one-way valve (38), The control port X of the two-position two-way hydraulic directional valve (37) is connected to the port A of the No. 1 two-position four-way electromagnetic directional valve (39), and the control port of the two-position two-way hydraulic directional valve (37) Y is connected with the port B pipeline of the No. 1 two-position four-way electromagnetic reversing valve (39); Port T of the three-position three-way hydraulic reversing valve (44) is connected to the oil inlet pipeline of the No. 7 relief valve (45), and the oil outlet of the No. 7 relief valve (45) is connected to the oil storage tank (9) pipe The port A of the two-position three-way electromagnetic directional valve (47) is connected to the control port of the No. Port T is connected to port T of No. 2 two-position four-way electromagnetic directional valve (48), port T of No. 3 two-position four-way electromagnetic directional valve (49) and the pipeline of the oil storage tank (9). Port T of the four-way hydraulic reversing valve (46) and port A of the No. 5 two-position two-way electromagnetic reversing valve (40), port P of the No. The control port Y of the hydraulic reversing valve (44) and its port B are connected by pipelines, and the port A of the No. 1 two-position four-way hydraulic reversing valve (46) is connected to the No. The port P of the No. 3 two-position four-way hydraulic directional control valve (51) is connected with the port P pipeline, and the port B of the No. 1 two-position four-way hydraulic directional control valve (46) is connected with the No. The port T of the valve (50) is connected to the port T of the No. The control port X of the hydraulic reversing valve (50), the oil inlet port of the No. 8 relief valve (52) and the external port D1 of the No. 2 control valve group (11) are connected by pipelines. The oil outlet is connected to the oil storage tank (9) pipeline, the port B of the No. 2 two-position four-way electromagnetic directional valve (48) is connected to the control port Y pipeline of the No. Connection, the port A of the No. 3 two-position four-way electromagnetic directional valve (49) is connected to the control port X of the No. 3 two-position four-way hydraulic directional valve (51), and the No. Port B of (49) is connected to the control port Y of No. 3 two-position four-way hydraulic directional valve (51), and port A of No. The external port D2 of (11) is connected with the pipeline, the port B of the No. The port A of the hydraulic directional control valve (51) is connected with the external port D4 of the No. 2 control valve group (11), and the port B of the No. 11) to the external port D5 pipeline connection; the port P of No. 5 two-position two-way electromagnetic reversing valve (40) is connected with the external port MB of No. 2 control valve group (11) and the inlet port of No. 6 overflow valve (42). The oil port pipeline connection, the port A of the No. 6 two-position two-way electromagnetic reversing valve (41) is connected with the oil inlet pipeline of the No. 8 check valve (43), and the oil outlet of the No. 6 overflow valve (42) The oil outlet of port and No. eight check valve (43) is connected with oil storage tank (9) pipeline; The hydraulic control unit (1) is connected with the hydraulic pump assembly (3), the No. 1 control valve group (4) and the No. 2 control valve group (11) by signal lines. Line and hydraulic pump (18) displacement adjustment control signal input end, No. 1 two-position two-way electromagnetic reversing valve (25), three-position three-way electromagnetic reversing valve (17), No. two two-position two-way electromagnetic reversing valve Directional valve (28), No. 3, two-position, two-way electromagnetic directional valve (32), No. 4, two-position, two-way electromagnetic directional valve (36), No. 1, two-position, four-way electromagnetic directional valve (39), fifth Two-position two-way electromagnetic directional valve (40), No. six two-position two-way electromagnetic directional valve (41), two-position three-way electromagnetic directional valve (47), No. two two-position four-way electromagnetic directional valve (48 ) and the control signal input terminal of the No. 3 two-position four-way electromagnetic reversing valve (49), the hydraulic control unit (1) is connected with the hydraulic pump displacement sensor (S) and the No. 1 accumulator pressure sensor ( Pacc1) and the output end of the second accumulator pressure sensor (Pacc2). 4. The hydraulic auxiliary drive system of an integrated hydraulic starter according to claim 3, characterized in that a two-position two-way hydraulic reversing valve (37) and a No. 2, 4-way electromagnetic directional valve (39), its function is to determine the energy storage of No. 2 through the opening or closing of the charging pump (19) when the No. device (10) whether to discharge liquid or make the No. 2 accumulator (10) always in the state of discharging liquid regardless of whether the charge pump (19) is opened; When in position, port P and port A of the No. 1 two-position four-way electromagnetic reversing valve (39) are connected, and port B is connected with port T. If the charging pump (19) is not turned on at this time, the two-position two-way The hydraulic reversing valve (37) is kept at the I position, and the No. 2 accumulator (10) is in the liquid discharge state. If the charge pump (19) is turned on at this time, the two-position two-way hydraulic reversing valve (37) is switched to the II position. position, the No. 2 accumulator (10) stops discharging liquid; when the No. 1 two-position, four-way electromagnetic directional valve (39) is in the II position, the port A of the No. 1, two-position, four-way electromagnetic directional valve (39) , port B and port T are connected, and port P is cut off. At this time, regardless of whether the charge pump (19) is turned on or not, the two-position two-way hydraulic directional valve (37) remains at the I position, and the No. 2 accumulator (10) Has been in the liquid state.