CN117514945A - Control system and harvesting machine - Google Patents

Abstract

The utility model relates to a hydraulic control device discloses a control system and harvester, and this control system includes main oil feed oil circuit and cooling circulation loop, be provided with the main pump mechanism that is used for supplying oil to control module on the main oil feed oil circuit, control module's oil return port is connected with the oil tank, cooling circulation loop with the oil tank links to each other and forms closed loop, in order to right the hydraulic oil of oil tank carries out the circulative cooling. The control system can reduce the length of the oil return pipeline, reduce the oil return pressure and prolong the service life of the hydraulic element.

Description

Control system and harvesting machine

Technical Field

The present application pertains to hydraulic control devices, and in particular, to a control system. Furthermore, a harvesting machine is also disclosed.

Background

The harvester with large feeding quantity belongs to high-end agricultural machinery, and has the characteristics of complex structure and high automation degree, so that a control system of the harvester needs to realize various control functions.

The feeding quantity of the existing harvester is relatively small, so that the control system is simple in composition and function. In the prior art, a cooler is generally arranged on an oil return pipeline to directly cool oil returned by the system, and the design increases the length of the oil return pipeline, increases the oil return pressure of the system and has adverse effect on the service life of hydraulic elements in a control system.

Accordingly, there is a need to design a new control system to overcome or alleviate the above-mentioned technical problems.

Disclosure of Invention

The purpose of this application is to provide a control system, can reduce the oil return pipeline length, reduces oil return pressure, improves hydraulic component life-span.

The utility model provides a harvester, this harvester's control system can reduce the oil return pipeline length, reduces oil return pressure, improves hydraulic component life-span.

In order to achieve the above-mentioned purpose, this application provides a control system on the one hand, including main oil feed oil circuit and cooling circulation loop, be provided with the main pump mechanism that is used for supplying oil to control module on the main oil feed oil circuit, control module's oil return port is connected with the oil tank, cooling circulation loop with the oil tank links to each other and forms closed circuit, in order to right the hydraulic oil of oil tank carries out the circulative cooling.

In some embodiments, a cooling circulation pump and a chiller are disposed on the cooling circulation loop.

In some embodiments, a first filter is also disposed on the cooling circulation loop.

In some embodiments, the main pump mechanism comprises a constant pressure pump, a variable oil cylinder for adjusting the flow rate of the constant pressure pump and a first constant pressure pump control valve, the constant pressure pump is installed on the main oil inlet path, the first constant pressure pump control valve comprises a first oil port connected with the main oil inlet path, a second oil port connected with the oil tank and a third oil port connected with the variable oil cylinder, one end control cavity of the first constant pressure pump control valve is connected with the main oil inlet path, two end control cavities of the first constant pressure pump control valve are respectively connected with a remote control valve, and a first throttle valve is arranged between one end control cavity of the first constant pressure pump control valve connected with the main oil inlet path and the remote control valve.

In some embodiments, the control module comprises a first control module and a second control module, a pressure reducing valve is arranged between the main pump mechanism and the first control module, an oil inlet of the second control module is connected to an oil path between the main pump mechanism and the pressure reducing valve, an oil return port of the first control module is connected with the oil tank, and an oil return port of the second control module is connected with the oil tank through the first filter.

In some embodiments, the first control module includes a first control valve connected to the main pump mechanism, a plurality of first actuators, and a plurality of first actuator control valves, each of the first actuators being connected to the first control valve through a corresponding one of the first actuator control valves.

In some embodiments, a second throttle valve is arranged between the first control valve and the main pump mechanism, an accumulator is connected on an oil path between the second throttle valve and the main pump mechanism, and a second overflow valve is arranged between an oil inlet of the first control valve and an oil return port of each first actuator control valve.

In some embodiments, the first actuators are hydraulic cylinders, each of the first actuator control valves is connected to a corresponding rodless chamber of the first actuator, and each of the rod chambers of the first actuators is connected to an oil path between the first control valve and the second throttle valve.

In some embodiments, the second control module comprises a multi-way valve and a plurality of second execution mechanisms connected with the multi-way valve, an oil inlet of the multi-way valve is connected with an oil inlet of the second control module, and an oil return port of the multi-way valve is connected with an oil return port of the second control module.

In some embodiments, the second control module further comprises a full hydraulic steering gear and a steering cylinder connected with the full hydraulic steering gear, wherein the full hydraulic steering gear is respectively connected with an oil inlet and an oil return port of the second control module.

In some embodiments, the second control module further comprises a brake valve and a brake cylinder connected with the brake valve, wherein the brake valve is respectively connected with the oil inlet and the oil return port of the second control module.

In some embodiments, the fan drive hydraulic pump is connected with the fan, and the fan drive motor is connected with the fan.

In some embodiments, the fan driven hydraulic pump and the main pump mechanism are both connected to a transfer case.

A second aspect of the present application provides a harvesting machine provided with a control system as described above.

Through the technical scheme, the active cooling circulation loop is arranged to carry out circulation cooling on the hydraulic oil in the oil tank, so that the return oil of the system does not pass through the cooler, the length of an oil return pipeline is reduced, the return oil pressure is reduced, and the service life of elements is prolonged.

Additional features and advantages of embodiments of the present application will be set forth in the detailed description which follows.

Drawings

The accompanying drawings are included to provide a further understanding of embodiments of the present application and are incorporated in and constitute a part of this specification, illustrate embodiments of the present application and together with the description serve to explain, without limitation, the embodiments of the present application. Other figures may be made from the structures shown in these figures without inventive effort for a person of ordinary skill in the art. In the drawings:

FIG. 1 is a hydraulic schematic diagram of a control system in an embodiment of the present application;

FIG. 2 is a hydraulic schematic diagram of a first control module in an embodiment of the present application;

fig. 3 is a hydraulic schematic of a second control module in an embodiment of the present application.

Description of the reference numerals

1 main pump mechanism 11 constant pressure pump

12 variable cylinder 13 first constant pressure pump control valve

14 first throttle valve 15 second constant pressure pump control valve

2 pressure reducing valve 3 first overflow valve

4 cooler 5 first check valve

6 remote control valve 7 cooling circulation pump

8 first filter 9 fan drive hydraulic pump

91 hydraulic pump 92 oil supplementing pump

93 fan drive control valve 10 fan drive motor

101 first control module P1 first control module oil inlet

Oil return port 1a of T1 first control module is a first clutch oil cylinder

2a second clutch cylinder 3a third clutch cylinder

4a fourth clutch cylinder 5a first clutch control valve

6a second clutch control valve 7a third clutch control valve

8a fourth clutch control valve 9a first control valve

10a accumulator 11a second overflow valve

12a second throttle valve 102 second control module

Oil inlet of 102b multiway valve P2 second control module

Oil return port 1b of T2 second control module first high-pressure working oil cylinder

2b second high-pressure working cylinder 3b third high-pressure working cylinder

4b fourth high-pressure working cylinder 5b fifth high-pressure working cylinder

6b sixth high-pressure working cylinder 7b first high-pressure control valve

8b second high-pressure control valve 9b third high-pressure control valve

10b fourth high-pressure control valve 11b fifth high-pressure control valve

12b sixth high-pressure control valve 13b seventh high-pressure control valve

14b eighth high-pressure control valve 15b ninth high-pressure control valve

16b tenth high pressure control valve 17b brake cylinder

18b brake valve 19b full hydraulic steering gear

20b steering cylinder 103 transfer case

Detailed Description

The following detailed description of specific embodiments of the present application refers to the accompanying drawings. It should be understood that the detailed description is presented herein for purposes of illustration and explanation only and is not intended to limit the present application.

It should be noted that, the control system of the present application belongs to the hydraulic field, and for those skilled in the art, the substantial technical concept is a hydraulic connection relationship. The relevant hydraulic components, such as reversing valves, non-return valves, relief valves, hydraulic pumps, etc., are well known to those skilled in the art and are also common components in existing hydraulic systems, and therefore only a brief description of these hydraulic components follows. Those skilled in the art, after having known the technical concepts of the present application, may simply replace the oil path or the valve, so as to implement the function of the control system of the present application, which is also within the protection scope of the present application.

As shown in fig. 1, the embodiment of the application provides a control system, which comprises a main oil inlet oil way and a cooling circulation loop, wherein a main pump mechanism 1 is arranged on the main oil inlet oil way, the main pump mechanism 1 is used for supplying oil to a control module, an oil return port of the control module is connected with an oil tank, and the cooling circulation loop is connected with the oil tank to form a closed loop so as to carry out circulating cooling on hydraulic oil of the oil tank. Compared with the existing cooling mode of setting a cooler on an oil return pipeline, the cooling system has the advantages that the temperature of the system is more controllable through setting an active cooling circulation loop, the length of the oil return pipeline can be reduced without the cooler, the oil return pressure is reduced, and the service life of elements is prolonged.

In a specific embodiment, the cooling circulation loop is provided with the cooling circulation pump 7 and the cooler 4, and the cooling circulation pump 7 is started, so that hydraulic oil in the oil tank can circulate through the cooler 4, and the hydraulic oil in the oil tank is cooled in a circulating way.

Further, a first filter 8 may be provided in the cooling circulation circuit to filter the hydraulic oil in the tank.

The radiator 4 may be cooled by air cooling, liquid cooling, or the like. In the embodiment shown in fig. 1, the air cooling mode is adopted to dissipate heat of the cooler 4, specifically, a fan driving hydraulic pump 9 and a fan driving motor 10 are provided, the fan driving motor 10 is connected with the fan driving hydraulic pump 9, the fan driving hydraulic pump 9 can drive the fan driving motor 10 to run forward or backward, and an output shaft of the fan driving motor 10 is connected with a fan for driving the fan to rotate. The fan-driven hydraulic pump 9 comprises a hydraulic pump 91, a supplemental pump 92 and a fan-driven control valve 93, the hydraulic pump 91 and the supplemental pump 92 are coaxially connected in series, two oil ports of the hydraulic pump 91 are respectively connected with the fan-driven control valve 93, the supplemental pump 92 is respectively connected with two oil ports of the hydraulic pump 91 through the fan-driven control valve 93, the supplemental pump 92 is connected with an oil tank, hydraulic oil can be conveyed to the hydraulic pump 91 to supplement the hydraulic pump 91, the hydraulic pump 91 is connected with a pump servo oil cylinder, the pump servo oil cylinder is connected with a proportional valve, the output direction of the hydraulic pump 91 can be controlled through the proportional valve, and the two oil ports of the hydraulic pump 91 are correspondingly connected with the two oil ports of the fan-driven motor 10 one by one, so that the fan-driven motor 10 is controlled to run forward or backward. The fan drive control valve 93 may include, among other things, a relief valve and a check valve arranged in parallel, or other hydraulic valves capable of achieving similar functions.

The fan drive hydraulic pump 9 and the main pump mechanism 1 are both connected with a transfer case 103, and the transfer case 103 is a device for distributing the power of the engine, which is well known to those skilled in the art, and thus will not be described herein.

In some embodiments, the main pump mechanism 1 comprises a constant pressure pump 11, a variable oil cylinder 12 and a first constant pressure pump control valve 13, the variable oil cylinder 12 is connected with the constant pressure pump 11 and is used for adjusting the flow of the constant pressure pump 11, the constant pressure pump 11 is installed on a main oil inlet path, the first constant pressure pump control valve 13 comprises a first oil port, a second oil port and a third oil port, the first oil port of the first constant pressure pump control valve 13 is connected with a main oil inlet path, the second oil port of the first constant pressure pump control valve 13 is connected with an oil tank through a control valve oil return path, the third oil port of the first constant pressure pump control valve 13 is connected with the variable oil cylinder 12, a first pipeline is arranged between an oil port of a rodless cavity of the variable oil cylinder 12 and the control valve oil return path, a throttle valve is arranged on the first pipeline, one end control cavity of the first constant pressure pump control valve 13 is connected with the main oil inlet path, two end control cavities of the first constant pressure pump control valve 13 are connected with the remote control valve 6, and a first throttle valve 14 is arranged between one end control cavity of the first constant pressure pump control valve 13 connected with the main oil inlet path and the remote control valve 6.

When the engine is started, the remote control valve 6 is opened, so that control cavities at two ends of the first constant pressure pump control valve 13 are communicated with the oil tank through the remote control valve 6, meanwhile, a first oil port of the first constant pressure pump control valve 13 is communicated with a third oil port of the first constant pressure pump control valve 13, part of hydraulic oil output by the constant pressure pump 11 flows to a rodless cavity of the variable oil cylinder 12 through the first constant pressure pump control valve 13, the variable oil cylinder 12 controls the displacement of the constant pressure pump 11 to be reduced, and at the moment, the constant pressure pump 11 is in a low-pressure small-displacement state, so that the engine starting load can be reduced. After the engine is started, the remote control valve 6 is closed, so that the pressure of control cavities at two ends of the first constant pressure pump control valve 13 is equal, the first constant pressure pump control valve 13 is reset, a second oil port of the first constant pressure pump control valve 13 is communicated with a third oil port of the first constant pressure pump control valve 13, the displacement of the constant pressure pump 11 is increased until the system reaches constant pressure set pressure, at the moment, the constant pressure pump 11 works in a high-pressure small displacement state, only the flow required by leakage of the system and the hydraulic element is output, and the energy loss is reduced.

When the engine is closed, if the system needs to be depressurized rapidly, the remote control valve 6 can be opened, so that the hydraulic oil output by the constant pressure pump 11 flows through the first constant pressure pump control valve 13, a first pipeline between the oil port of the rodless cavity of the variable oil cylinder 12 and the oil return oil way of the control valve, and the oil return oil way of the control valve is depressurized.

Further, the second constant pressure pump control valve 15 is further provided, and comprises a first oil port, a second oil port and a third oil port, the first oil port of the second constant pressure pump control valve 15 is connected with the main oil inlet oil path, the second oil port of the second constant pressure pump control valve 15 is connected with the third oil port of the first constant pressure pump control valve 13, the third oil port of the second constant pressure pump control valve 15 is connected with the rodless cavity of the variable cylinder 12, a second pipeline is further communicated between the second oil port of the second constant pressure pump control valve 15 and the third oil port of the second constant pressure pump control valve 15, and a throttle valve is also arranged on the second pipeline. The first constant pressure pump control valve 13 and the second constant pressure pump control valve 15 may be two-position three-way valves.

In some embodiments, filters are respectively installed at the positions of the oil inlet and the oil outlet of the main pump mechanism 1.

In some embodiments, the control module includes a first control module 101 and a second control module 102, a pressure reducing valve 2 is disposed between the main pump mechanism 1 and the first control module 101, the pressure reducing valve 2 is connected with an oil inlet P1 of the first control module 101, the oil inlet P2 of the second control module 102 is connected to an oil path between the main pump mechanism 1 and the pressure reducing valve 2, relatively speaking, low pressure oil can be provided to the first control module 101, and high pressure oil can be provided to the second control module 102. The oil return port T1 of the first control module 101 is connected with the oil tank, the oil return port T2 of the second control module 102 is connected with the oil tank through the first filter 8, and the overflow port of the pressure reducing valve 2 and one end control cavity thereof are connected with the oil tank. And an overflow oil path is further arranged, one end of the overflow oil path is connected to an oil path between the main pump mechanism 1 and the pressure reducing valve 2, the other end of the overflow oil path is connected to an oil path between the oil return port T2 of the second control module 102 and the first filter 8, and the overflow oil path is provided with the first overflow valve 3.

As shown in fig. 1 and 2, the first control module 101 includes a first control valve 9a, a plurality of first actuators, and a plurality of first actuator control valves, each first actuator is connected to the first control valve 9a through a corresponding first actuator control valve, and the first control valve 9a is connected to the main pump mechanism 1. When each first actuator needs to act, the main pump mechanism 1 outputs high-pressure oil, the pressure is reduced by the action of the pressure reducing valve 2, and then the high-pressure oil is output to the first control module 101, and the first control valve 9a and the first actuator control valve are opened to realize the corresponding action of the first actuator. The first control valve 9a may be a two-position two-way valve, the first actuator may be a hydraulic cylinder or a hydraulic motor, and the first actuator control valve may be a two-position three-way valve.

Specifically, in the embodiment shown in fig. 2, the first actuator is a clutch cylinder, and may be divided into a first clutch cylinder 1a, a second clutch cylinder 2a, a third clutch cylinder 3a, and a fourth clutch cylinder 4a, and correspondingly, the plurality of first actuator control valves may be divided into a first clutch control valve 5a, a second clutch control valve 6a, a third clutch control valve 7a, and a fourth clutch control valve 8a. The rodless cavity of the first clutch cylinder 1a is connected with the first clutch control valve 5a, the oil inlet of the first clutch control valve 5a is connected with the first control valve 9a, the first clutch cylinder 1a is preferably a plunger cylinder, the rodless cavity of the second clutch cylinder 2a is connected with the second clutch control valve 6a, the oil inlet of the second clutch control valve 6a is connected with the first control valve 9a, the rodless cavity of the third clutch cylinder 3a is connected with the third clutch control valve 7a, the oil inlet of the third clutch control valve 7a is connected with the first control valve 9a, the rodless cavity of the fourth clutch cylinder 4a is connected with the fourth clutch control valve 8a, the oil return port of the first clutch control valve 5a, the oil return port of the second clutch control valve 6a, the oil return port of the third clutch control valve 7a and the oil return port of the fourth clutch control valve 8a are all connected with the oil return port T1 of the first control module 101. A second throttle valve 12a is provided between the first control valve 9a and the main pump mechanism 1, that is, a second throttle valve 12a is provided between the first control valve 9a and the oil inlet P1 of the first control module 101, an accumulator 10a is connected to an oil passage between the second throttle valve 12a and the main pump mechanism 1, a second relief valve 11a is provided between an oil inlet of the first control valve 9a and an oil return port of each first actuator control valve, a rod cavity of the second clutch cylinder 2a, a rod cavity of the third clutch cylinder 3a, and a rod cavity of the fourth clutch cylinder 4a are all connected to an oil passage between the oil inlet of the first control valve 9a and the second throttle valve 12a, and when the first clutch cylinder 1a is a single piston rod cylinder, the rod cavity of the first clutch cylinder 1a may also be connected to an oil passage between the oil inlet of the first control valve 9a and the second throttle valve 12 a. The first actuator is not limited to the cylinder for operating the clutch described above, and may be a cylinder or a hydraulic motor applied to other devices.

As shown in fig. 1 and fig. 3, the second control module 102 includes a multiple-way valve 102b and a plurality of second execution mechanisms, the plurality of second execution mechanisms are connected with the multiple-way valve 102b, an oil inlet of the multiple-way valve 102b is connected with an oil inlet P2 of the second control module 102, and an oil return port of the multiple-way valve 102b is connected with an oil return port T2 of the second control module 102. When each second actuator needs to act, the main pump mechanism 1 outputs high-pressure oil to the second control module 102, and opens the multi-way valve 102b to realize the corresponding second actuator. The second actuator may be a hydraulic cylinder or a hydraulic motor.

Specifically, in the embodiment shown in fig. 3, each of the second actuators may be a hydraulic cylinder, and may be divided into a first high-pressure working cylinder 1b, a second high-pressure working cylinder 2b, a third high-pressure working cylinder 3b, a fourth high-pressure working cylinder 4b, a fifth high-pressure working cylinder 5b, and a sixth high-pressure working cylinder 6b, and the multiple valve 102b includes a first high-pressure control valve 7b, a second high-pressure control valve 8b, a third high-pressure control valve 9b, a fourth high-pressure control valve 10b, a fifth high-pressure control valve 11b, a sixth high-pressure control valve 12b, a seventh high-pressure control valve 13b, an eighth high-pressure control valve 14b, a ninth high-pressure control valve 15b, and a tenth high-pressure control valve 16b, respectively. The first high-pressure working cylinder 1b may be a plunger cylinder, the rod cavity of the first high-pressure working cylinder 1b is connected with the first high-pressure control valve 7b, and the second high-pressure working cylinder 2b may be a plunger cylinder. The rodless chamber of the second high-pressure working cylinder 2b, the third high-pressure control valve 9b, and the second high-pressure control valve 8b are connected in this order. The third high-pressure working cylinder 3b may be a plunger cylinder, and the rodless chamber of the third high-pressure working cylinder 3b, the fifth high-pressure control valve 11b, and the fourth high-pressure control valve 10b are connected in order. The number of the fourth high-pressure working cylinders 4b can be two, the rodless cavities of one fourth high-pressure working cylinder 4b are respectively connected with the sixth high-pressure control valve 12b and the seventh high-pressure control valve 13b, the rodless cavities of the other fourth high-pressure working cylinder 4b are directly connected with the oil return port T2 of the second control module 102, an adjustable throttle valve and a pressure detection device are arranged on an oil way between the rodless cavities of the other fourth high-pressure working cylinder 4b and the oil return port T2 of the second control module 102, and the pressure detection device can be a pressure gauge, a pressure sensor and the like, and the rodless cavities of the fourth high-pressure working cylinder 4b are also connected with an energy accumulator. The fifth high-pressure working cylinder 5b is connected with the eighth high-pressure control valve 14b through a hydraulic lock, and a one-way throttle valve is installed between the rodless cavity of the fifth high-pressure working cylinder 5b and the hydraulic lock. The number of the sixth high-pressure working cylinders 6b is two, rodless cavities of the two sixth high-pressure working cylinders 6b are connected, rod cavities of the two sixth high-pressure working cylinders 6b are connected, and the rodless cavities of the sixth high-pressure working cylinders 6b are respectively connected with the ninth high-pressure control valve 15b and the tenth high-pressure control valve 16b. The oil inlet of the first high-pressure control valve 7b, the oil inlet of the second high-pressure control valve 8b, the oil inlet of the fourth high-pressure control valve 10b, the oil inlet of the seventh high-pressure control valve 13b, the oil inlet of the eighth high-pressure control valve 14b and the oil inlet of the tenth high-pressure control valve 16b are all connected with the oil inlet P2 of the second control module 102, and throttle valves are respectively installed among the oil inlet of the second high-pressure control valve 8b, the oil inlet of the fourth high-pressure control valve 10b, the oil inlet of the seventh high-pressure control valve 13b and the oil inlet P2 of the second control module 102. The oil return port of the first high-pressure control valve 7b, the oil return port of the second high-pressure control valve 8b, the oil return port of the fourth high-pressure control valve 10b, the oil return port of the sixth high-pressure control valve 12b, the oil return port of the eighth high-pressure control valve 14b and the oil return port of the ninth high-pressure control valve 15b are all connected with the oil return port T2 of the second control module 102, a one-way valve is arranged between the oil return port of the first high-pressure control valve 7b and the oil return port T2 of the second control module 102, an accumulator is connected between the oil return port of the first high-pressure control valve 7b and the one-way valve, and a throttling valve is respectively arranged between the oil return port of the second high-pressure control valve 8b, the oil return port of the fourth high-pressure control valve 10b, the oil return port of the sixth high-pressure control valve 12b, the oil return port of the eighth high-pressure control valve 14b and the oil return port T2 of the second control module 102, a one-way valve is also arranged between the oil return port of the sixth high-pressure control valve 12b and the oil return port T2 of the second control module 102, and an oil return port of the ninth high-pressure control valve 15b is provided with a pressure compensation valve 2. The first high-pressure control valve 7b, the second high-pressure control valve 8b, and the fourth high-pressure control valve 10b may be two-position three-way valves, the third high-pressure control valve 9b, the fifth high-pressure control valve 11b, the sixth high-pressure control valve 12b, the seventh high-pressure control valve 13b, the ninth high-pressure control valve 15b, and the tenth high-pressure control valve 16b may be two-position two-way valves, and the eighth high-pressure control valve 14b may be a three-position four-way valve.

In some embodiments, as shown in fig. 3, the second control module further includes a full hydraulic steering gear 19b and a steering cylinder 20b, where the steering cylinder 20b is connected to the full hydraulic steering gear 19b for controlling steering of the apparatus, and the full hydraulic steering gear 19b is connected to the oil inlet P2 and the oil return port T2 of the second control module 102, respectively. The full hydraulic steering gear 19b can achieve a larger steering force control with a smaller steering force, and is safe, reliable, flexible and lightweight in terms of performance, well known to those skilled in the art, and therefore, will not be described in detail herein.

In some embodiments, as shown in fig. 3, the second control module further includes a brake valve 18b and a brake cylinder 17b, where the brake cylinder 17b is connected to the brake valve 18b for implementing device braking, and the brake valve 18b is connected to the oil inlet P2 and the oil return port T2 of the second control module 102, respectively.

For a better understanding of the technical concepts of the present application, the following description is made in connection with relatively comprehensive technical features.

As shown in fig. 1 to 3, the preferred embodiment of the present application provides a control system including a main oil intake passage and a cooling circulation circuit, the main oil intake passage is provided with a main pump mechanism 1, the main pump mechanism 1 is used for supplying oil to a first control module 101 and a second control module 102, the main pump mechanism 1 includes a constant pressure pump 11, a variable cylinder 12, a first constant pressure pump control valve 13 and a second constant pressure pump control valve 15, the variable cylinder 12 is connected with the constant pressure pump 11 for adjusting the flow rate of the constant pressure pump 11, the constant pressure pump 11 is installed on the main oil intake passage, the first constant pressure pump control valve 13 includes a first oil port, a second oil port and a third oil port, the first oil port of the first constant pressure pump control valve 13 is connected with the main oil intake passage, the second oil port of the first constant pressure pump control valve 13 is connected with an oil tank through a control valve oil return passage, the second constant pressure pump control valve 15 comprises a first oil port, a second oil port and a third oil port, the first oil port of the second constant pressure pump control valve 15 is connected with a main oil inlet oil way, the second oil port of the second constant pressure pump control valve 15 is connected with the third oil port of the first constant pressure pump control valve 13, the third oil port of the second constant pressure pump control valve 15 is connected with a rodless cavity of the variable cylinder 12, a first pipeline is arranged between the oil port of the rodless cavity of the variable cylinder 12 and the return oil way of the control valve, a throttle valve is arranged on the first pipeline, a second pipeline is also communicated between the second oil port of the second constant pressure pump control valve 15 and the third oil port of the second constant pressure pump control valve 15, a throttle valve is also arranged on the second pipeline, one end control cavity of the first constant pressure pump control valve 13 is connected with the main oil inlet oil way, and both end control cavities of the first constant pressure pump control valve 13 are connected with the remote control valve 6, a first throttle valve 14 is provided between the remote control valve 6 and an end control chamber of the first constant pressure pump control valve 13 connected to the main oil feed passage. The first control module 101 comprises a first control valve 9a, a first clutch oil cylinder 1a, a second clutch oil cylinder 2a, a third clutch oil cylinder 3a, a fourth clutch oil cylinder 4a, a first clutch control valve 5a, a second clutch control valve 6a, a third clutch control valve 7a and a fourth clutch control valve 8a, wherein the first control valve 9a is connected with the main pump mechanism 1 through a relief valve 2, a rodless cavity of the first clutch oil cylinder 1a is connected with the first clutch control valve 5a, an oil inlet of the first clutch control valve 5a is connected with the first control valve 9a, the first clutch oil cylinder 1a is preferably a plunger cylinder, a rodless cavity of the second clutch oil cylinder 2a is connected with the second clutch control valve 6a, an oil inlet of the second clutch control valve 6a is connected with the first control valve 9a, an oil inlet of the third clutch oil cylinder 3a is connected with the third clutch control valve 7a, an oil inlet of the third clutch control valve 7a is connected with the first control valve 9a, an oil inlet of the fourth clutch oil cylinder 4a is connected with the fourth clutch oil return valve 8a, an oil return port of the fourth clutch oil cylinder 8a is connected with the fourth clutch oil return port of the fourth clutch oil cylinder 6a is connected with the fourth clutch oil return port of the first clutch oil cylinder 6a, the fourth clutch oil cylinder 8a is connected with the fourth clutch control valve 8a, the oil return port of the fourth clutch oil cylinder is connected with the fourth clutch oil valve 8a is connected with the fourth clutch control valve 6 a. A second throttle valve 12a is provided between the first control valve 9a and the main pump mechanism 1, that is, a second throttle valve 12a is provided between the first control valve 9a and the oil inlet P1 of the first control module 101, an accumulator 10a is connected to an oil passage between the second throttle valve 12a and the main pump mechanism 1, a second relief valve 11a is provided between an oil inlet of the first control valve 9a and an oil return port of each first actuator control valve, and a rod cavity of the second clutch cylinder 2a, a rod cavity of the third clutch cylinder 3a, and a rod cavity of the fourth clutch cylinder 4a are all connected to an oil passage between an oil inlet of the first control valve 9a and the second throttle valve 12 a. The second control module 102 includes a multiplex valve 102b, a first high-pressure working cylinder 1b, a second high-pressure working cylinder 2b, a third high-pressure working cylinder 3b, a fourth high-pressure working cylinder 4b, a fifth high-pressure working cylinder 5b, a sixth high-pressure working cylinder 6b, a brake valve 18b, a brake cylinder 17b, a full hydraulic steering 19b, and a steering cylinder 20b, and the multiplex valve 102b includes a first high-pressure control valve 7b, a second high-pressure control valve 8b, a third high-pressure control valve 9b, a fourth high-pressure control valve 10b, a fifth high-pressure control valve 11b, a sixth high-pressure control valve 12b, a seventh high-pressure control valve 13b, an eighth high-pressure control valve 14b, a ninth high-pressure control valve 15b, and a tenth high-pressure control valve 16b. The first high-pressure working cylinder 1b may be a plunger cylinder, the rod cavity of the first high-pressure working cylinder 1b is connected with the first high-pressure control valve 7b, and the second high-pressure working cylinder 2b may be a plunger cylinder. The rodless chamber of the second high-pressure working cylinder 2b, the third high-pressure control valve 9b, and the second high-pressure control valve 8b are connected in this order. The third high-pressure working cylinder 3b may be a plunger cylinder, and the rodless chamber of the third high-pressure working cylinder 3b, the fifth high-pressure control valve 11b, and the fourth high-pressure control valve 10b are connected in order. The number of the fourth high-pressure working cylinders 4b can be two, the rodless cavities of one fourth high-pressure working cylinder 4b are respectively connected with the sixth high-pressure control valve 12b and the seventh high-pressure control valve 13b, the rodless cavities of the other fourth high-pressure working cylinder 4b are directly connected with the oil return port T2 of the second control module 102, an adjustable throttle valve and a pressure detection device are arranged on an oil way between the rodless cavities of the other fourth high-pressure working cylinder 4b and the oil return port T2 of the second control module 102, and the pressure detection device can be a pressure gauge, a pressure sensor and the like, and the rodless cavities of the fourth high-pressure working cylinder 4b are also connected with an energy accumulator. The fifth high-pressure working cylinder 5b is connected with the eighth high-pressure control valve 14b through a hydraulic lock, and a one-way throttle valve is installed between the rodless cavity of the fifth high-pressure working cylinder 5b and the hydraulic lock. The number of the sixth high-pressure working cylinders 6b is two, rodless cavities of the two sixth high-pressure working cylinders 6b are connected, rod cavities of the two sixth high-pressure working cylinders 6b are connected, and the rodless cavities of the sixth high-pressure working cylinders 6b are respectively connected with the ninth high-pressure control valve 15b and the tenth high-pressure control valve 16b. The oil inlet of the first high-pressure control valve 7b, the oil inlet of the second high-pressure control valve 8b, the oil inlet of the fourth high-pressure control valve 10b, the oil inlet of the seventh high-pressure control valve 13b, the oil inlet of the eighth high-pressure control valve 14b and the oil inlet of the tenth high-pressure control valve 16b are all connected with the oil inlet P2 of the second control module 102, and throttle valves are respectively installed among the oil inlet of the second high-pressure control valve 8b, the oil inlet of the fourth high-pressure control valve 10b, the oil inlet of the seventh high-pressure control valve 13b and the oil inlet P2 of the second control module 102. The oil return port of the first high-pressure control valve 7b, the oil return port of the second high-pressure control valve 8b, the oil return port of the fourth high-pressure control valve 10b, the oil return port of the sixth high-pressure control valve 12b, the oil return port of the eighth high-pressure control valve 14b and the oil return port of the ninth high-pressure control valve 15b are all connected with the oil return port T2 of the second control module 102, a one-way valve is arranged between the oil return port of the first high-pressure control valve 7b and the oil return port T2 of the second control module 102, an accumulator is connected between the oil return port of the first high-pressure control valve 7b and the one-way valve, and a throttling valve is respectively arranged between the oil return port of the second high-pressure control valve 8b, the oil return port of the fourth high-pressure control valve 10b, the oil return port of the sixth high-pressure control valve 12b, the oil return port of the eighth high-pressure control valve 14b and the oil return port T2 of the second control module 102, a one-way valve is also arranged between the oil return port of the sixth high-pressure control valve 12b and the oil return port T2 of the second control module 102, and an oil return port of the ninth high-pressure control valve 15b is provided with a pressure compensation valve 2. The brake cylinder 17b is connected with a brake valve 18b for realizing equipment braking, and the brake valve 18b is respectively connected with an oil inlet P2 and an oil return port T2 of the second control module 102. The steering cylinder 20b is connected with a full hydraulic steering gear 19b for controlling equipment steering, and the full hydraulic steering gear 19b is respectively connected with an oil inlet P2 and an oil return port T2 of the second control module 102. Be provided with cooling circulation pump 7, cooler 4 and first filter 8 on the cooling circulation circuit, can adopt the forced air cooling mode to dispel the heat to cooler 4, be provided with fan drive hydraulic pump 9 and fan drive motor 10, fan drive motor 10 is connected with fan drive hydraulic pump 9, fan drive hydraulic pump 9 can drive fan drive motor 10 forward or reverse operation, fan drive motor 10's output shaft is connected with the fan for drive fan is rotatory, dispel the heat to cooler 4.

Based on the technical scheme, the control system of the application works as follows:

when the engine is started, the remote control valve 6 is opened, so that control cavities at two ends of the first constant pressure pump control valve 13 are communicated with the oil tank through the remote control valve 6, meanwhile, a first oil port of the first constant pressure pump control valve 13 is communicated with a third oil port of the first constant pressure pump control valve 13, part of hydraulic oil output by the constant pressure pump 11 flows to a rodless cavity of the variable oil cylinder 12 through the first constant pressure pump control valve 13, the variable oil cylinder 12 controls the displacement of the constant pressure pump 11 to be reduced, and at the moment, the constant pressure pump 11 is in a low-pressure small-displacement state, so that the engine starting load can be reduced. After the engine is started, the remote control valve 6 is closed, so that the pressure of control cavities at two ends of the first constant pressure pump control valve 13 is equal, the first constant pressure pump control valve 13 is reset, a second oil port of the first constant pressure pump control valve 13 is communicated with a third oil port of the first constant pressure pump control valve 13, the displacement of the constant pressure pump 11 is increased until the system reaches constant pressure set pressure, at the moment, the constant pressure pump 11 works in a high-pressure small displacement state, only the flow required by leakage of the system and the hydraulic element is output, and the energy loss is reduced. Moreover, the constant pressure pump 11 can select a hydraulic pump with larger discharge capacity, so that the system can integrate more functions and the high-automation requirement of the harvester is met.

When the engine is closed, if the system needs to be depressurized rapidly, the remote control valve 6 can be opened, so that the hydraulic oil output by the constant pressure pump 11 flows through the first constant pressure pump control valve 13, a first pipeline between the oil port of the rodless cavity of the variable oil cylinder 12 and the oil return oil way of the control valve, and the oil return oil way of the control valve is depressurized.

When each first executing mechanism or each second executing mechanism needs to act, the corresponding first executing mechanism control valve or the corresponding second executing mechanism control valve is opened, so that the main pump mechanism 1 outputs hydraulic oil to the first executing mechanism or the second executing mechanism which needs to act, the flow of the constant pressure pump 11 is increased until the system returns to the set pressure, at the moment, the constant pressure pump 11 only outputs the flow required by the load, and the system has no overflow loss. When the cylinders work simultaneously, as long as the total flow does not exceed the maximum output flow of the constant pressure pump 11, the outlet of the constant pressure pump 11 still keeps the set pressure, and no interference is generated between the actions.

In fig. 1, the high-pressure oil at the outlet of the constant-pressure pump 11 is output to the first control module 101 after being subjected to pressure reduction by the pressure reducing valve 2, so as to provide the pressure required by the operation of each clutch cylinder. The pressure reducing valve 2 is a pressure reducing overflow valve, and can prevent the pressure of the low pressure loop from being blocked. The oil inlet P1 of the first control module 101 is provided with a second relief valve 11a for protecting the hydraulic components and the pipes of the first control module 101 in case of failure of the pressure reducing valve 2.

In fig. 2, when the clutch is off, the rodless cavity of one or some of the first actuators is connected with the oil tank, the rod cavity of the first actuator is connected with the oil inlet P1 of the first control module 101, and the first actuator is retracted under the action of the hydraulic resultant force because the hydraulic pressure of the rod cavity of the first actuator is greater than the hydraulic pressure of the rodless cavity of the first actuator. At this time, the first control valve 9a is closed, and pressure oil is prevented from penetrating into the first actuator, so that the clutch is dithered. When the clutch is combined, the first control valve 9a is opened, and one or more first actuating mechanism control valves are controlled to be opened, so that the rodless cavity of the corresponding first actuating mechanism is communicated with the oil inlet P1 of the first control module 101, and the clutch piston is pushed to extend. In order to keep the clutch combined, the first actuating mechanism control valve needs to be controlled to keep the opening state, so that the corresponding rod cavity and rodless cavity of the first actuating mechanism keep the same pressure, the first actuating mechanism keeps extending to the maximum stroke, compared with the prior art, a one-way valve or a hydraulic lock is adopted to keep the clutch position, the situation that the position of the clutch cylinder is changed due to leakage under the condition of long-time working, the speed is reduced and the like is caused, and the clutch is kept combined by utilizing the hydraulic pressure difference value, so that the clutch is prevented from loosening due to leakage.

Similarly, the multiple-way valve 102b and the plurality of second actuators in the second control module 102 may be operated to implement the actions of the second actuators.

The cooling circulation pump 7 extracts oil from the oil tank, discharges back the oil tank after passing through the cooler 4 and the filter 8, completes the cooling and filtering of the oil in the oil tank, and the circulation flow is controllable, can carry out temperature control relatively accurately by adjusting the cooling air quantity, and the oil in the oil tank is filtered through circulation constantly, thereby improving the cleanliness of the oil, and further improving the service life of the oil. Compared with the prior art, the cooler is used for directly cooling the system oil return, the system oil return pressure is increased, the service life of the hydraulic element is adversely affected, and meanwhile, the technical problem of element arrangement is also not facilitated. The hydraulic system oil return of this application need not pass through the cooler, and direct oil return tank makes things convenient for the pipeline to arrange, reduces system oil return pressure, improves hydraulic component life-span. When the oil temperature is too low and the loop pressure is high, the circulating oil is controlled to return to the oil tank through the first one-way valve 5, so that the cooler shell is protected.

Further, the fan driving hydraulic pump 9 and the fan driving motor 10 are combined into a closed hydraulic system, the fan driving oil pump 9 has a bidirectional stepless variable function, the fan driving motor 10 can be controlled, the rotating speed and the direction of the cooling fan are further controlled, the air quantity and the air direction can be adjusted according to the system requirement, and the temperature control can be accurately performed on the cooler 4 by adjusting the cooling air quantity. The system temperature is more controllable, the system oil return does not pass through a cooler, the length of an oil return pipeline is reduced, the oil return pressure is reduced, and the service life of elements is prolonged.

When the vehicle needs to be braked, the brake valve 18b is adopted to decompress the system pressure and output the system pressure to the brake cylinder 17b, so that compared with a common booster, the operation load is reduced, and the brake pressure is improved.

When the vehicle needs to turn, oil enters the steering oil cylinder 20b through the full-hydraulic steering gear 19b, the steering oil cylinder 20b drives the steering wheel to rotate, the relief valve is not needed for unloading, and the priority valve and the relief valve are omitted.

The application also provides a harvesting machine provided with the control system. The harvesting machine is preferably a harvester, but the harvesting machine is not limited to a harvester, but may be other harvesting devices where the above control system is needed.

In the description of the present application, it should be understood that the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or an implicit indication of the number of technical features being indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "plurality" is at least two, such as two, three, etc., unless explicitly defined otherwise.

In this application, unless specifically stated and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may be in communication with each other; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art as the case may be.

In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present application. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

Although embodiments of the present application have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the application, and that variations, modifications, alternatives, and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the application.

Claims (14)

1. The control system is characterized by comprising a main oil inlet oil way and a cooling circulation loop, wherein a main pump mechanism (1) for supplying oil to a control module is arranged on the main oil inlet oil way, an oil return port of the control module is connected with an oil tank, and the cooling circulation loop is connected with the oil tank to form a closed loop so as to circularly cool hydraulic oil of the oil tank.

2. Control system according to claim 1, characterized in that the cooling circuit is provided with a cooling circulation pump (7) and a cooler (4).

3. Control system according to claim 2, characterized in that the cooling circuit is further provided with a first filter (8).

4. A control system according to claim 3, characterized in that the main pump mechanism (1) comprises a constant pressure pump (11), a variable cylinder (12) for regulating the flow of the constant pressure pump (11), and a first constant pressure pump control valve (13), the constant pressure pump (11) is mounted on the main oil intake passage, the first constant pressure pump control valve (13) comprises a first oil port connected with the main oil intake passage, a second oil port connected with the oil tank, and a third oil port connected with the variable cylinder (12), one end control chamber of the first constant pressure pump control valve (13) is connected with the main oil intake passage, and both end control chambers of the first constant pressure pump control valve (13) are respectively connected with a remote control valve (6), and a first throttle valve (14) is provided between one end control chamber of the first constant pressure pump control valve (13) connected with the main oil intake passage and the remote control valve (6).

5. The control system according to claim 4, characterized in that the control module comprises a first control module (101) and a second control module (102), a pressure reducing valve (2) is arranged between the main pump mechanism (1) and the first control module (101), an oil inlet (P2) of the second control module (102) is connected to an oil path between the main pump mechanism (1) and the pressure reducing valve (2), an oil return port (T1) of the first control module (101) is connected to the oil tank, and an oil return port (T2) of the second control module (102) is connected to the oil tank through the first filter (8).

6. The control system according to claim 5, characterized in that the first control module (101) comprises a first control valve (9 a) connected to the main pump mechanism (1), a number of first actuators and a number of first actuator control valves, each of the first actuators being connected to the first control valve (9 a) by a corresponding first actuator control valve.

7. The control system according to claim 6, characterized in that a second throttle valve (12 a) is arranged between the first control valve (9 a) and the main pump mechanism (1), an accumulator (10 a) is connected to an oil path between the second throttle valve (12 a) and the main pump mechanism (1), and a second overflow valve (11 a) is arranged between an oil inlet of the first control valve (9 a) and an oil return port of each first actuator control valve.

8. The control system according to claim 7, characterized in that the first actuators are hydraulic cylinders, each of the first actuator control valves being connected to a corresponding rodless chamber of the first actuator, each of the first actuator rod chambers being connected to an oil circuit between the first control valve (9 a) and the second throttle valve (12 a).

9. The control system according to claim 5, characterized in that the second control module (102) comprises a multi-way valve (102 b) and a number of second actuators connected to the multi-way valve (102 b), an oil inlet of the multi-way valve (102 b) is connected to an oil inlet (P2) of the second control module (102), and an oil return port of the multi-way valve (102 b) is connected to an oil return port (T2) of the second control module (102).

10. The control system according to claim 9, characterized in that the second control module further comprises a full hydraulic steering gear (19 b) and a steering cylinder (20 b) connected to the full hydraulic steering gear (19 b), the full hydraulic steering gear (19 b) being connected to the oil inlet (P2) and the oil return (T2) of the second control module (102), respectively.

11. The control system according to claim 9, characterized in that the second control module further comprises a brake valve (18 b) and a brake cylinder (17 b) connected to the brake valve (18 b), the brake valve (18 b) being connected to the oil inlet (P2) and the oil return (T2) of the second control module (102), respectively.

12. The control system according to any one of claims 1 to 11, further comprising a fan drive hydraulic pump (9) and a fan drive motor (10) connected to the fan drive hydraulic pump (9), an output shaft of the fan drive motor (10) being connected to the fan.

13. The control system according to claim 12, characterized in that the fan driven hydraulic pump (9) and the main pump mechanism (1) are both connected to a transfer case (103).

14. Harvesting machine, characterized in that a control system according to any of claims 1 to 13 is provided.