CN209100381U - Pump Valve Integrated Fluidics Module - Google Patents

Abstract

The utility model discloses a pump-valve integrated flow control module, which comprises a confluence element, a two-way pump, an electro-hydraulic servo valve and a pressure sensor which are respectively integrally installed on the confluence element. The inside of the confluence element is provided with a main channel and a branch flow The main channel is used to connect the two-way pump and the controlled object to form an output main channel, and the branch channel is used to connect the electro-hydraulic servo valve and the controlled object to form a throttling bypass. The pressure sensor is communicated with the main channel. The pump-valve integrated fluid control module provided by the utility model realizes the high integration of fluid control elements through the confluence structure, compresses the layout space, reduces the number of pipelines, improves the installation and maintenance efficiency, and reduces the production and maintenance cost.

Description

Pump Valve Integrated Fluidics Module

technical field

The utility model belongs to the field of hydraulic technology, in particular to a pump-valve integrated flow control module.

Background technique

Hydraulic transmission is a transmission method in which liquid is used as the working medium for energy transmission and control. It forms three main types of transmission in parallel with mechanical transmission and electrical transmission. Based on hydraulic transmission technology, hydraulic control systems are widely used in industrial fields.

The hydraulic control system uses the motor to provide the power base, uses the hydraulic pump to convert the mechanical energy into pressure to push the hydraulic oil, and changes the flow direction of the hydraulic oil by controlling various valves, thereby pushing the hydraulic cylinder to achieve different strokes and different directions. Different actions are required. The hydraulic control system has the advantages of easy stepless speed regulation, good dynamic performance, good motion stability, self-lubricating and so on.

At present, hydraulic systems generally need to be connected through pipelines. The pipeline connection process is cumbersome, the pipelines are scattered and complex, and a large layout space is required to increase the layout difficulty. When the system oil circuit is complex, the situation is more serious, which is not conducive to assembly and maintenance, and greatly increases production and maintenance costs.

Utility model content

In order to overcome the deficiencies of the prior art, the utility model provides a pump-valve integrated fluid control module, which realizes the high integration of fluid control elements with a confluence structure, compresses the layout space, reduces the number of pipelines, improves installation and maintenance efficiency, and reduces production and maintenance costs. .

The purpose of the present utility model is achieved through the following technical solutions:

A pump-valve integrated flow control module includes a confluence element, a bidirectional pump, an electro-hydraulic servo valve and a pressure sensor integrally installed on the confluence element, wherein the confluence element has a main flow channel and a branch flow channel inside the main flow channel. The channel is used to connect the two-way pump and the controlled object to form an output main path, the branch channel is used to connect the electro-hydraulic servo valve and the controlled object to form a throttling bypass, and the pressure sensor is connected to the main channel.

As an improvement of the above technical solution, the main flow channel and the branch flow channel respectively have a plurality of commutation ends, and the commutation ends are opened on the surface of the confluence element.

As a further improvement of the above technical solution, the bidirectional pump, the electro-hydraulic servo valve, the pressure sensor and the quick connector are respectively installed at different commutation ends, and the quick connector is used to realize the external pipeline connection.

As a further improvement of the above technical solution, a drive motor for driving the two-way pump is installed on the two-way pump.

As a further improvement of the above technical solution, the controlled object is a hydraulic cylinder, the main flow channel includes a first flow channel and a second flow channel, and the first flow channel is used to connect an oil port of the two-way pump and the A cavity of the hydraulic cylinder, and the second flow channel is used to connect an oil port at one end of the bidirectional pump and the other cavity of the hydraulic cylinder.

As a further improvement of the above technical solution, one end of the first flow channel and the second flow channel are communicated with each other and are jointly connected to the fuel supply tank.

As a further improvement of the above technical solution, the branch channels are arranged in pairs and are respectively connected to the two cavities of the hydraulic cylinder, and the electro-hydraulic servo valves are arranged in a one-to-one correspondence with the branch channels.

As a further improvement of the above technical solution, the branch channel includes a drainage section and a drainage section isolated from each other: one end of the drainage section is connected to the controlled object, and the other end is connected to the oil inlet of the electro-hydraulic servo valve ; One end of the discharge section is respectively connected to the control oil port of the electro-hydraulic servo valve, and the other end is connected to the oil return tank.

As a further improvement of the above technical solution, one end of the drainage section away from the oil inlet of the electro-hydraulic servo valve is communicated with the main channel.

As a further improvement of the above technical solution, a one-way valve is provided at one end of the main channel for connecting with the fuel supply tank.

The beneficial effects of the present utility model are:

The two-way pump, electro-hydraulic servo valve and pressure sensor are integrated with the confluence element. The confluence element has a main channel and a branch channel. The main channel is used to connect the two-way pump and the controlled object to form the main output path, and the branch channel is used to connect the electro-hydraulic channel. The servo valve and the controlled object form a throttling bypass, and the pressure sensor is connected to the main channel to form a highly integrated pump valve integrated flow control module, which can be assembled and disassembled for maintenance, compress the layout space, reduce the number of pipelines, and improve the installation and maintenance efficiency. Reduce production and maintenance costs.

In order to make the above-mentioned objects, features and advantages of the present utility model more obvious and easy to understand, preferred embodiments are given below, and are described in detail as follows in conjunction with the accompanying drawings.

Description of drawings

In order to illustrate the technical solutions of the embodiments of the present invention more clearly, the accompanying drawings that need to be used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention. Therefore, it should not be regarded as a limitation of the scope. For those of ordinary skill in the art, other related drawings can also be obtained from these drawings without any creative effort.

1 is a first axonometric schematic view of a pump-valve integrated fluid control module provided in Embodiment 1 of the present invention;

2 is a second axonometric schematic diagram of the pump-valve integrated fluid control module provided in Embodiment 1 of the present invention;

3 is a partial schematic front view of the pump-valve integrated fluid control module provided in Embodiment 1 of the present invention;

Fig. 4 is the A-A sectional schematic diagram of the pump-valve integrated fluid control module in Fig. 3;

Fig. 5 is the B-B sectional schematic diagram of the pump-valve integrated fluid control module in Fig. 3;

6 is a schematic diagram of the system principle of the pump-valve composite control system provided in Embodiment 2 of the present invention;

7 is a schematic diagram of the control principle of the pump-valve composite control system provided in Embodiment 2 of the present invention;

8 is a control principle block diagram of the first controller of the pump-valve composite control system provided in Embodiment 2 of the present invention;

9 is a block diagram of the control principle of the second controller of the pump-valve composite control system provided in Embodiment 2 of the present invention;

10 is a block diagram of the control principle of the third controller of the pump-valve composite control system provided in Embodiment 2 of the present invention.

Description of main component symbols:

1-Pump-valve compound control system, 10-Pump-valve integrated fluid control module, 11-Converging element, 111-Main channel, 111a-First channel, 111b-Second channel, 112-Sub channel, 112a-Drainage section, 112b-discharge section, 113-commutation end, 12-bidirectional pump, 121-first oil port, 122-second oil port, 13-drive motor, 141-first pressure sensor, 142-second pressure sensor, 151- The first electro-hydraulic servo valve, 152- The second electro-hydraulic servo valve, 161- The first one-way valve, 162- The second one-way valve, 17- Quick connector, 20- Displacement sensor, 31- The first controller , 32- the second controller, 33- the third controller, 40- oil supply tank, 50- oil return tank, 60- oil cooler, 70- asymmetric hydraulic cylinder.

Detailed ways

In order to facilitate the understanding of the present invention, a more comprehensive description of the pump-valve integrated fluid control module will be given below with reference to the related drawings. A preferred embodiment of the pump-valve integrated fluidics module is shown in the accompanying drawings. However, the pump valve integrated fluidics module may be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided so that the disclosure of the pump valve integrated fluidics module will be thorough and complete.

It should be noted that when an element is referred to as being "fixed to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. In contrast, when an element is referred to as being "directly on" another element, there are no intervening elements present. The terms "vertical," "horizontal," "left," "right," and similar expressions are used herein for illustrative purposes only.

Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the technical field to which the present invention belongs. The terms used herein in the description of the pump-valve integrated fluid control module are for the purpose of describing specific embodiments only, and are not intended to limit the present invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.

Example 1

Please refer to FIGS. 1 to 5 , this embodiment discloses a pump-valve integrated fluid control module 10 , which includes a confluence element 11 , a bidirectional pump 12 , an electro-hydraulic servo valve and a pressure sensor integrally mounted on the confluence element 11 , for use in A highly integrated pump-valve compound control device is provided, which compresses layout space, reduces the number of pipelines, improves installation and maintenance efficiency, and reduces production and maintenance costs.

The confluence element 11 is used to realize the integrated installation of the pump valve fluid control elements in the fluid circuit, and make these pump valve fluid control elements correspond to the fluid connection to form the required fluid control circuit. Based on this, the pump-valve integrated fluid control module 10 forms an integral unit that is highly intensive and can be quickly disassembled and assembled. There is no need to communicate through pipelines between the pump-valve fluid control components in the module, which eliminates the trouble of complicated pipeline winding, and is very convenient for installation and maintenance. . The confluence element 11 can take various structural forms, such as plate-like, block-like, and the like. Exemplarily, the confluence element 11 is a confluence block structure.

The inside of the confluence element 11 has a main flow channel 111 and a branch flow channel 112, which are used to realize the flow communication between the corresponding pump valve flow control elements. Among them, the main channel 111 is used to connect the two-way pump 12 and the controlled object to form the main output path, providing the main driving force required for the controlled object to work; the branch channel 112 is used to connect the electro-hydraulic servo valve and the controlled object to form a joint The flow bypass is used to realize the throttling adjustment of the controlled object; the pressure sensor is connected to the main channel 111 to realize the pressure monitoring of the output main channel.

Exemplarily, the main channel 111 and the branch channel 112 respectively have a plurality of commutation ends 113 , and the commutation ends 113 are opened on the surface of the bus element 11 . The commutating end 113 is used to realize the fluid exchange between the confluence element 11 and other fluid elements, and realize the communication of the fluid path. The commutating end 113 can be implemented in various forms, including threaded holes, through holes, joints, and the like.

Exemplarily, two-way pumps 12, electro-hydraulic servo valves, pressure sensors and quick connectors 17 are respectively installed on different commutating ends 113, and the quick connectors 17 are used to realize external pipeline connection. Among them, the quick connector 17 is used to realize the quick connection between the pump valve integrated fluid control module 10 and the controlled object, the fuel supply tank 40, the fuel return tank 50 and other fluid components. Exemplarily, the quick connector 17 is a hinged connector, which can realize convenient rotation adjustment, make it in a better connection position and ensure the compactness of the pipeline.

Controlled objects are selected according to actual needs and used to perform corresponding actions. Exemplarily, the controlled object is a hydraulic cylinder, and the main flow channel 111 includes a first flow channel 111a and a second flow channel 111b. The first flow channel 111a is used to connect one end of the oil port of the two-way pump 12 and a cavity of the hydraulic cylinder, and the other end of the oil port is used to connect the oil supply tank 40 to input hydraulic oil; the second flow channel 111b is used to connect the two-way pump 12. One end of the oil port is connected to the other cavity of the hydraulic cylinder, and the other end of the oil port is used to connect the oil supply tank 40 to input hydraulic oil. Correspondingly, the first oil port 121 of the bidirectional pump 12 is connected to the first flow passage 111a, and the second oil port 122 is connected to the second flow passage 111b.

Exemplarily, one end of the first flow channel 111a and the second flow channel 111b communicate with each other and are jointly connected to the fuel supply tank 40 , which further simplifies the structure of the main flow channel 111 . Exemplarily, one end of the main flow channel 111 for connecting with the oil supply tank 40 is provided with a one-way valve to prevent the hydraulic oil from returning to the oil supply tank 40 unexpectedly. For example, one end of the first flow channel 111 a is used for connecting to the fuel supply tank 40 and the first check valve 161 is installed, and one end of the second flow channel 111 b is used for connecting the end of the fuel supply tank 40 to install the second one-way valve 162 . Exemplarily, the first pressure sensor 141 is installed on the first flow channel 111a, and the second pressure sensor 142 is installed on the second flow channel 111b.

Exemplarily, the branch channel 112 includes a drainage section 112a and a drainage section 112b isolated from each other. One end of the drainage section 112a is connected to the controlled object, and the other end is connected to the oil inlet (P port) of the electro-hydraulic servo valve; one end of the drain section 112b is respectively connected to the control oil port (A port or B port) of the electro-hydraulic servo valve. port), and the other end is connected to the return tank 50. Thus, the electro-hydraulic servo valve can realize throttling control. It can be understood that the discharge section 112b has the commutation ends 113 corresponding to the T (oil outlet)/A/B ports of the electro-hydraulic servo valve, respectively.

It can be understood that the main channel 111 and the branch channel 112 can be communicated with the controlled object through different commutation terminals 113 , or can also share the same commutation end 113 and communicated with the controlled object. Exemplarily, one end of the drainage section 112a away from the oil inlet of the electro-hydraulic servo valve is communicated with the main channel 111 , so that the main channel 111 and the branch channel 112 share the commutating end 113 , reducing the number of the commutating ends 113 and simplifying the confluence element 11 . Structure.

Exemplarily, the branch channels 112 are arranged in pairs and are respectively connected to the two chambers of the hydraulic cylinder, and the electro-hydraulic servo valves are arranged in a one-to-one correspondence with the branch channels 112 . In other words, the number of the branch channels 112 is at least two. An electro-hydraulic servo valve is respectively installed in each branch flow channel 112 for realizing bypass throttling of a cavity of the hydraulic cylinder. Since the hydraulic cylinder has two chambers, the first electro-hydraulic servo valve 151 is used to realize the bypass throttling of the first chamber, and the second electro-hydraulic servo valve 152 is used to realize the bypass throttling of the second chamber.

Exemplarily, the bidirectional pump 12 is mounted with a drive motor 13 for driving its operation. The drive motor 13 can be directly mounted on the bidirectional pump 12 through a coupling, and has an integral fastening structure.

Example 2

Please refer to FIGS. 1 to 7 , this embodiment discloses a pump-valve composite control system 1, including the pump-valve integrated fluid control module 10, the displacement sensor 20 and the control unit described in The pump valve compound control of the cylinder 70 (controlled object). First of all, it is explained that the inner cavity of the asymmetric hydraulic cylinder 70 is divided into a rod cavity and a rodless cavity by the piston, and the piston rod is located in the rod cavity.

Among them, the bidirectional pump 12 and the drive motor 13 are used to achieve the purpose of volume control. One end of the bidirectional pump 12 is connected to the rodless cavity of the asymmetric hydraulic cylinder 70 through the first flow channel 111a oil circuit, and the other end is connected to the rod cavity of the asymmetric hydraulic cylinder 70 through the second flow channel 111b oil circuit.

The bidirectional pump 12 has two rotation directions, and achieves different output purposes by switching forward and reverse. Driven by the rotational output in different directions, the asymmetric hydraulic cylinder 70 realizes the telescopic reciprocating motion. Exemplarily, the two-way pump 12 is a two-way variable pump with variable displacement, which realizes displacement adjustment through volume change, and has a volume control characteristic. There are many types of bidirectional pumps 12, and may be, for example, bidirectional gear pumps. It can be understood that, through the driving control of the driving motor 13, the bidirectional pump 12 can realize rapid direction switching and displacement adjustment.

The pressure sensor is used to monitor the real-time pressure of the two chambers of the asymmetric hydraulic cylinder 70 respectively. In other words, the number of pressure sensors is at least two, wherein the first pressure sensor 141 is used to monitor the real-time pressure of the rodless cavity, and the second pressure sensor 142 is used to monitor the real-time pressure of the rod cavity. Exemplarily, the first pressure sensor 141 is installed on the oil port oil circuit (such as the first flow channel 111a) without the rod cavity, and the second pressure sensor 142 is installed on the oil port oil circuit with the rod cavity (such as the second flow channel 111b). )superior.

The displacement sensor 20 is used to monitor the real-time displacement of the piston movement of the asymmetric hydraulic cylinder 70 . There are many types of displacement sensors 20 , including linear displacement sensors, magnetostrictive displacement sensors 20 , LVDT displacement sensors, pull-string displacement sensors, and the like. Exemplarily, the displacement sensor 20 is a magnetostrictive displacement sensor.

Exemplarily, the displacement sensor 20 is integrated on the asymmetric hydraulic cylinder 70 to measure the displacement of the piston in real time along with the piston movement of the piston rod of the asymmetric hydraulic cylinder 70 . It can be understood that, according to the measurement value of the displacement sensor 20, the movement parameters such as the piston movement speed and the acceleration of the asymmetric hydraulic cylinder 70 can be calculated.

The electro-hydraulic servo valve is used to respectively realize the bypass pressure relief of the two chambers of the asymmetric hydraulic cylinder 70 , so as to solve the problem of asymmetric flow characteristics existing in the asymmetric hydraulic cylinder 70 . Specifically, due to the flow asymmetry caused by the asymmetric area of the two chambers of the asymmetric hydraulic cylinder 70, when oil is discharged from the rodless chamber and oil is fed into the rod chamber, the excess oil forces the pressure in the two chambers to rise, generating pressure The force control accuracy of the system decreases due to the position disturbance. The electro-hydraulic servo valve discharges the excess oil in the two cavities in real time from the bypass valve to realize bypass throttling adjustment, eliminate the pressure disturbance and position disturbance of the rodless cavity and the rod cavity, thereby ensuring the ideal force control accuracy.

Among them, the first electro-hydraulic servo valve 151 is arranged on one side bypass of the asymmetric hydraulic cylinder 70 (the branch channel 112 on one side) to release the excess oil in the rodless cavity of the asymmetric hydraulic cylinder 70; The hydraulic servo valve 152 is arranged on the other side of the bypass (the branch channel 112 on the other side) of the asymmetric hydraulic cylinder 70 , and is used to release the excess oil in the rod cavity of the asymmetric hydraulic cylinder 70 .

Exemplarily, the pump-valve composite control system 1 further includes a return oil tank 50 for receiving excess oil released by the first electro-hydraulic servo valve 151 and the second electro-hydraulic servo valve 152 . In other words, the oil inlet (P port) of the first electro-hydraulic servo valve 151 is connected to the rodless cavity of the asymmetric hydraulic cylinder 70 through the drain section 112a, and the control port (A port or B port) is connected to the return through the drain section 112b. The oil tank 50; the oil inlet (P port) of the second electro-hydraulic servo valve 152 is connected to the rod cavity of the asymmetric hydraulic cylinder 70 through the drainage section 112a, and the control port (A port or B port) is connected to the asymmetric hydraulic cylinder 70 through the drainage section 112b. Return to tank 50. Exemplarily, the return tank 50 is an atmospheric pressure tank. Exemplarily, the first electro-hydraulic servo valve 151 and the second electro-hydraulic servo valve 152 are respectively connected to the oil return tank 50 via the oil cooler 60 .

The control unit is used to control the output torque of the drive motor 13, the first electro-hydraulic servo valve 151 and the second electro-hydraulic servo valve 152 according to the monitoring value of the pressure sensor, the monitoring value of the displacement sensor 20 and the target parameter of the asymmetric hydraulic cylinder 70 pressure relief flow. The target parameter of the asymmetric hydraulic cylinder 70 refers to its expected dynamic target value, including different motion parameters such as target output force, target velocity and target displacement of the piston movement.

According to the aforementioned parameter values, the control unit correspondingly implements the feedforward control and feedback control of the drive motor 13 (indirectly to the bidirectional pump 12 ), the first electro-hydraulic servo valve 151 and the second electro-hydraulic servo valve 152 , reducing the rigidity of the force control and reducing the Enhance flexibility, suppress the influence of position disturbance on force control accuracy, reduce time lag and improve control sensitivity.

Please refer to FIGS. 7 to 10 in conjunction. Exemplarily, the control unit includes a first controller 31 , a second controller 32 and a third controller 33 . The first controller 31 is used to control the output torque of the drive motor 13 according to the target parameters of the asymmetric hydraulic cylinder 70 and the real-time pressure of the two chambers, and the second controller 32 is used to control the output torque of the driving motor 13 according to the target parameters of the asymmetric hydraulic cylinder 70, The real-time pressure of the two chambers and the real-time displacement of the piston movement control the opening of the first electro-hydraulic servo valve 151, and the third controller 33 is used to control the real-time pressure of the two chambers and the real-time piston movement according to the target parameters of the asymmetric hydraulic cylinder 70, the real-time pressure of the two chambers and the real-time displacement of the piston movement. The displacement controls the opening degree of the second electro-hydraulic servo valve 152 .

Exemplarily, the pump-valve composite control system 1 further includes an oil supply tank 40 for supplying the hydraulic oil required to be pumped by the bidirectional pump 12 . One end of the fuel supply tank 40 is connected to the rodless cavity, and the other end is connected to the rod cavity. Under the pumping action of the bidirectional pump 12, the hydraulic oil of the oil supply tank 40 is output to the rodless cavity or the rod cavity correspondingly. Exemplarily, the oil supply tank 40 is a pressurized oil tank, which ensures that the oil circuit of the system is filled with oil when the two-way pump 12 stops working, prevents air from mixing in, and provides oil when the two-way pump 12 is working.

Exemplarily, one end of the oil output port of the fuel supply tank 40 is connected to the rodless cavity of the asymmetric hydraulic cylinder 70 through the first one-way valve 161 and the first flow passage 111a, and the other end is connected to the rodless cavity of the asymmetric hydraulic cylinder 70 through the second one-way valve 162 and the second one-way valve 162. The oil path of the flow channel 111b is connected to the rod cavity of the asymmetric hydraulic cylinder 70 to prevent the oil in the system from flowing back to the oil supply tank 40 .

In all examples shown and described herein, any specific value should be construed as merely exemplary and not as limiting, as other examples of exemplary embodiments may have different values.

It should be noted that like numerals and letters refer to like items in the following figures, so once an item is defined in one figure, it does not require further definition and explanation in subsequent figures.

The above-mentioned embodiments only represent several embodiments of the present invention, and the descriptions thereof are specific and detailed, but should not be construed as limiting the scope of the present invention. It should be pointed out that for those of ordinary skill in the art, some modifications and improvements can be made without departing from the concept of the present invention, which all belong to the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the appended claims.

Claims (10)

1. A pump-valve integrated fluid control module, characterized in that it comprises a confluence element and a two-way pump, an electro-hydraulic servo valve and a pressure sensor that are respectively integrated and installed on the confluence element, and the interior of the confluence element has a main channel and a pressure sensor. a branch channel, the main channel is used to connect the two-way pump and the controlled object to form an output main channel, the branch channel is used to connect the electro-hydraulic servo valve and the controlled object to form a throttling bypass, The pressure sensor is communicated with the main channel. 2 . The pump-valve integrated fluid control module according to claim 1 , wherein the main flow channel and the branch flow channel respectively have a plurality of flow exchange ends, and the flow exchange ends are opened on the surface of the confluence element. 3 . . 3 . The pump-valve integrated fluid control module according to claim 2 , wherein the two-way pump, the electro-hydraulic servo valve, the pressure sensor and the quick connector are respectively installed at different commutating ends, and the quick The joint is used to realize the external pipeline connection. 4 . The pump-valve integrated fluid control module according to claim 1 , wherein a driving motor for driving the bidirectional pump is installed on the bidirectional pump. 5 . 5 . The pump-valve integrated fluid control module according to claim 1 , wherein the controlled object is a hydraulic cylinder, the main flow channel includes a first flow channel and a second flow channel, and the first flow channel is used for An oil port at one end of the bidirectional pump is connected with a cavity of the hydraulic cylinder, and the second flow passage is used for connecting an oil port at one end of the bidirectional pump with another cavity of the hydraulic cylinder. 6 . The pump-valve integrated fluid control module according to claim 5 , wherein one end of the first flow passage and the second flow passage communicate with each other and are jointly connected to the fuel supply tank. 7 . 7 . The pump-valve integrated fluid control module according to claim 5 , wherein the branch channels are arranged in pairs and are respectively connected to the two cavities of the hydraulic cylinder, and the electro-hydraulic servo valve is connected to the branch channel. 8 . set accordingly. 8 . The pump-valve integrated fluid control module according to claim 1 , wherein the branch channel comprises a drainage section and a drainage section isolated from each other: one end of the drainage section is connected to the controlled object, and the other end is connected to the controlled object. 9 . It is connected to the oil inlet of the electro-hydraulic servo valve; one end of the discharge section is respectively connected to the control oil port of the electro-hydraulic servo valve, and the other end is connected to the oil return tank. 9 . The pump-valve integrated fluid control module according to claim 8 , wherein one end of the drainage section away from the oil inlet of the electro-hydraulic servo valve is communicated with the main channel. 10 . 10 . The pump-valve integrated fluid control module according to claim 1 , wherein a one-way valve is provided at one end of the main channel for connecting with the fuel supply tank. 11 .