A high-precision synchronous valve group

Abstract

The present invention relates to the technical field of synchronous valves, and specifically to a high-precision synchronous valve group, including a valve body, on which a plurality of closed-loop control circulation flow channel groups are arranged, the closed-loop control flow channel group includes a medium flow channel connected to a hydraulic actuator; the medium flow channel includes a plurality of distribution start flow channels connected to a throttling damping flow channel, the throttling damping flow channel is connected to a flow compensation flow channel through at least two channels, and a throttling assembly and a damping member are arranged in the throttling damping flow channel; the flow compensation flow channels are respectively connected to independent pressure compensation flow channels, and the pressure compensation flow channels are connected to the hydraulic actuator through the distribution end flow channels; the distribution end flow channels are also unidirectionally connected to the throttling damping flow channels through the return flow channels. By performing flow compensation and pressure compensation on the medium guide, the medium transported backward can be kept to have the same flow rate for a plurality of different hydraulic actuators, the action consistency of the hydraulic actuators can be maintained, and the control accuracy of the synchronous valve group can be improved.

Description

Technical Field

[0001] The invention relates to the technical field of synchronous valves, and in particular to a high-precision synchronous valve group. Background Art

[0002] When controlling different hydraulic actuators through a hydraulic system, it is necessary to adjust the flow in each hydraulic actuator. When the flow rates of each hydraulic actuator are different, the execution force is also different, and the final execution effect is also different. When it is necessary to complete the execution action with high precision, the hydraulic medium is delivered to each hydraulic actuator by setting a synchronous valve group and the flow rate of each hydraulic actuator is kept equal, so that the hydraulic actuators can keep the same action after being stressed and reach the set accuracy range. However, when controlling multiple hydraulic actuators, the traditional hydraulic system mainly optimizes the delivery rate of the hydraulic medium and maintains the stability of the delivery pressure to achieve synchronous control of multiple hydraulic actuators. The synchronous valve group only plays a role of diversion in the hydraulic system. This control system relies on the hydraulic driving force provided by the hydraulic source, and the control accuracy value provided is low. When the pressure and flow rate of the hydraulic medium change along the process, the synchronous valve group cannot be adjusted autonomously to improve the control accuracy of the hydraulic actuator, which will affect the synchronization of multiple hydraulic actuators. In addition, in the prior art, a closed-loop control system is used to improve the control accuracy, but the traditional closed-loop control system has the problems of complex structure and high cost, and the effect is not ideal when used specifically.

[0003] It can be seen that the current structure of the synchronous valve group still has room for improvement, and should be optimized to achieve autonomous adjustment of the synchronous valve group structure. Even if there is an unbalanced pressure load, the flow and force of the hydraulic actuator can be quickly balanced through autonomous adjustment to maintain control accuracy. Therefore, it is necessary to propose a more reasonable technical solution to solve the technical problems existing in the prior art. Summary of the invention

[0004] In order to overcome at least one of the defects mentioned above, the present invention proposes a high-precision synchronous valve group, which adjusts the valve body structure and first uses a damping structure to maintain the hydraulic equality after the throttle valve is diverted, and performs flow compensation and pressure compensation on the control oil circuit to adjust the output hydraulic load, keeping the loads of multiple hydraulic actuators the same, thereby achieving high-precision synchronous control.

[0005] In order to achieve the above purpose, the synchronous valve group disclosed in the present invention can adopt the following technical solutions:

[0006] A high-precision synchronous valve group comprises a valve body, on which a plurality of closed-loop control circulation flow channel groups are arranged, the closed-loop control flow channel group comprises an even number of medium flow channels and each medium flow channel is used to connect to a hydraulic actuator; the medium flow channels comprise a plurality of distribution start flow channels, each distribution start flow channel is connected to a separate throttling damping flow channel and the throttling damping flow channel is connected to a flow compensation flow channel through at least two channels, a throttling assembly and a damping member are arranged in the throttling damping flow channel, and a flow compensation assembly is arranged in the flow compensation flow channel; each flow compensation flow channel is connected to the distribution end flow channel and to the hydraulic actuator through a separate pressure compensation assembly; the hydraulic actuator is connected through the pressure compensation flow channel and feedback controls the opening of the pressure compensation assembly; the distribution end flow channel is also unidirectionally connected to the throttling damping flow channel through the return flow channel; when the medium flow channel supplies oil to the hydraulic actuator, the return flow channel is closed, and when the medium flow channel returns oil from the hydraulic actuator, the return flow channel is opened.

[0007] The high-precision synchronous valve group disclosed above, the compensation of the medium by the medium flow channel in the valve body, can maintain the same flow and pressure of the medium in multiple medium flow channels when conveying to the hydraulic actuator, so as to maintain high precision and synchronization of control.

[0008] Furthermore, the structure of the throttling damping flow channel of the high-precision synchronous valve group disclosed above can be constructed in various forms and is not limited to a single one. Here, an optimization is made and one feasible option is proposed: a throttling valve is arranged at one end of the throttling damping flow channel, and a damping member is arranged at the other end of the throttling damping flow channel. The throttling damping flow channel is connected to the flow compensation flow channel through the throttling valve and the damping member respectively. When the above scheme is adopted, the damping member and the throttling valve can be used to control the flow, thereby adjusting the medium flow delivered to the flow compensation flow channel, which is convenient for correction to maintain the consistency of the medium flow.

[0009] Furthermore, the specific connection position of the distribution start flow channel is not limited to a single one. Here, an optimization is made and one of the feasible options is proposed: the distribution start flow channel is connected to the middle of the throttling damping flow channel. When the above solution is adopted, the distribution start flow channel can disperse the conveying medium from the middle of the throttling damping flow channel to both ends, thereby maintaining the uniformity of the medium distribution.

[0010] Furthermore, the flow compensation channel is used to adjust the medium flow in multiple channels to keep the medium flow transported backwards consistent. The structure of the flow compensation channel can be constructed in various forms, which are not limited to a single one. Here, an optimization is made and one of the feasible options is proposed: the flow compensation channel includes at least two flow compensation sections, and the flow compensation component is located in each flow compensation section. When the above scheme is adopted, each flow compensation section corresponds to a medium channel, so the structure of the flow compensation channel can be in various forms, which is convenient for realizing the simultaneous adjustment and compensation of the flow of multiple channels.

[0011] Furthermore, in order to more conveniently realize flow compensation and simplify the structure of the flow compensation channel, optimization is performed here and one of the feasible options is proposed: the flow compensation channel is a straight channel that passes through the valve body, and two flow compensation sections are formed in the flow compensation channel; the flow compensation assembly includes a flow compensation valve core located in the flow compensation channel, and a compensation hole connecting the flow compensation section and the pressure compensation channel is formed on the flow compensation valve core; the oil in the flow compensation section applies force to the flow compensation valve core and pushes the flow compensation valve core in opposite directions to change the opening of the compensation hole, thereby balancing the oil flow of the two oil compensation sections entering the pressure compensation assembly. When the above scheme is adopted, the compensation hole of the flow compensation valve core can also be constructed as a compensation groove; the flow compensation valve core is displaced between the two compensation ends and reaches balance through the oil medium of the compensation sections on both sides. When the medium pressure at one end is larger, the flow compensation valve core is pushed to the compensation section on the other side, so that the opening of the compensation hole of the compensation section on this side is reduced, and the opening of the compensation hole of the compensation end on the other side is increased, thereby realizing balanced flow regulation.

[0012] Furthermore, pressure compensation provides another compensation scheme, which acts on the medium flow channel at the front end through pressure feedback of the hydraulic actuator to feedback and adjust the opening of the medium flow channel. Its structure can be constructed in various forms and is not limited to a single form. It is optimized here and one of the feasible options is proposed: the pressure compensation flow channel includes a pressure compensation chamber formed in the valve body for setting a pressure compensation component, the pressure compensation chamber includes a lower chamber, a middle chamber and an upper chamber, the lower chamber is connected to the flow compensation flow channel, the middle chamber is connected to the distribution end flow channel, and the upper chambers are connected to each other; the pressure compensation component includes a pressure compensation valve core arranged in the pressure compensation chamber, when the pressure compensation valve core is in the closed position, the lower chamber is separated from the middle chamber, and when the pressure compensation valve core is in the open position, the lower chamber and the middle chamber are connected. When the above scheme is adopted, the load pressures of multiple hydraulic actuators are fed back to the corresponding pressure compensation components. The path with the largest load pressure pushes open the valve of the control component and enters into multiple upper chambers, and the load pressure acts on each pressure compensation valve core, thereby ensuring that each pressure compensation valve core is subjected to the same feedback force, providing the same pressure compensation for each medium flow channel, thereby improving the accuracy of synchronous control.

[0013] Furthermore, the structure of the pressure compensation valve can adopt a variety of schemes, which are not limited to the only one. Here, an optimization is made and one of the feasible options is proposed: the pressure compensation valve core extends from the lower chamber to the upper chamber, and a flow structure connecting the lower chamber and the middle chamber is formed on the pressure compensation valve core. When the above scheme is adopted, the flow structure is used to pass the medium. The larger the opening of the flow structure, the greater the flow rate of the medium. The medium entering the lower chamber can push the pressure compensation valve core to open the flow structure and enter the middle chamber.

[0014] Furthermore, the control component can cooperate with the pressure compensation valve to realize the output pressure of the medium output to the outside. The structure of the control component can be constructed in various forms, which is not limited to a single one. Here, optimization is made and one of the feasible options is proposed: the control component includes a control valve, the control valve includes a control flow channel of the upper chamber connecting all pressure compensation chambers, and a control valve core for adjusting the on-off of the control flow channel is arranged in the control flow channel. The control valve core is used to receive the feedback pressure of each hydraulic actuator and deliver the hydraulic medium with the largest feedback pressure to the upper chamber to form a consistent pressure compensation. When the above scheme is adopted, the control valve core acts in the control flow channel and is used to connect the upper chamber. The pressure of the medium entering the upper chamber is equal and provides corresponding pressure to the pressure compensation valve core, thereby achieving consistent pressure flow of the medium delivered to the outside.

[0015] Furthermore, the control flow channel is used to feedback the pressure of the hydraulic actuator and is connected to the hydraulic actuator. The specific structure is not limited to the only one. Here, an optimization is made and one of the feasible options is proposed: the control flow channel extends from the distribution end channel to the upper chamber. When the above solution is adopted, the distribution end flow channel can extend to the side wall surface of the main body.

[0016] Furthermore, when the medium flows back, it flows back to the throttling damping flow channel through the return flow channel. The structure of the return flow channel may not be limited to a single one. Here, an optimization is made and one of the feasible options is proposed: a one-way valve is provided at the return flow channel, and the one-way valve limits the one-way return of the medium from the hydraulic actuator to the throttling damping flow channel. When the above solution is adopted, after the medium enters the throttling damping flow channel through the one-way valve, it can reversely enter the flow channel at the start of the distribution.

[0017] Compared with the prior art, some beneficial effects of the technical solution disclosed in the present invention include:

[0018] The present invention optimizes the medium flow channel in the valve body, maintains the guidance of the medium, and after flow compensation and pressure compensation, can maintain the same flow rate of the medium transported backward when entering multiple different hydraulic actuators, thereby maintaining the consistency of the actions of the hydraulic actuators and improving the control accuracy of the synchronous valve group over multiple hydraulic actuators. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for use in the embodiments are briefly introduced below. It should be understood that the following drawings only represent some embodiments of the present invention and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without creative work.

[0020] Figure 1 It is the overall structural diagram of the synchronous valve group.

[0021] Figure 2 This is a schematic diagram of the overall structure of the synchronous valve group from another perspective.

[0022] Figure 3 The figure is a schematic diagram of the overall structure of a medium flow channel set in a synchronous valve group.

[0023] Figure 4 The figure is a schematic diagram of the flow channel structure of a medium flow channel set in a synchronous valve group.

[0024] Figure 5 for Figure 3 Schematic diagram from another perspective.

[0025] Figure 6 for Figure 4 Schematic diagram from another perspective.

[0026] Figure 7 for Figure 3 Schematic diagram of the structure from above.

[0027] Figure 8 for Figure 7 Schematic cross-sectional view of section AA (isometric).

[0028] Fig. 9 for Figure 7 Schematic cross-sectional view of section AA (front view).

[0029] Fig.10 This is a schematic cross-sectional view of section AA in 7 (the isometric view only shows the medium flow channel).

[0030] Fig.11 for Figure 7 Schematic cross-sectional view of the BB section (isometric).

[0031] Fig.12 for Figure 7 Schematic cross-sectional view of the BB section (front view).

[0032] Fig.13 for Figure 7 Schematic cross-sectional view of the BB section (the isometric view only shows the medium flow channel).

[0033] Fig.14 for Figure 7 Schematic cross-sectional view of the CC section (isometric).

[0034] Fig.15 for Figure 7 Schematic cross-sectional view of the CC section (the isometric view only shows the flow channel).

[0035] Fig.16 for Figure 7 Schematic diagram of half section of the FF section (isometric).

[0036] Fig.17 for Figure 7 Schematic diagram of half section of the DD section (isometric).

[0037] Fig.18 for Figure 7 Schematic diagram of half section of section EE (isometric).

[0038] Fig.19 for Figure 7 Schematic diagram of half section of section GG (isometric).

[0039] Fig. 20 This is a schematic diagram of the principle of the synchronous valve group.

[0040] In the above drawings, the meanings of the symbols are as follows:

[0041] 1. Valve body; 101. Throttling damping flow channel; 102. Flow compensation flow channel; 103. Pressure compensation flow channel; 103a. Lower chamber; 103b. Middle chamber; 103c. Upper chamber; 104. Return flow channel; 105. Distribution end flow channel; 106. Control flow channel; 2. Distribution start flow channel; 3. Pressure compensation component; 301. Pressure compensation valve core; 302. Flow-through structure; 4. Distribution end flow channel; 5. Damping element; 6. One-way valve; 7. Flow compensation component; 701. Flow compensation valve core; 702. Return spring; 703. Compensation hole; 8. Throttle valve; 9. Control valve core. DETAILED DESCRIPTION

[0042] The present embodiment is further explained below in conjunction with the accompanying drawings and specific embodiments.

[0043] In view of the many deficiencies in the prior art, the following embodiments are optimized and overcome the defects in the prior art.

[0044] Example

[0045] like Figure 1 to Figure 19As shown, this embodiment provides a high-precision synchronous valve group, including a valve body 1, on which a plurality of closed-loop control circulation flow channel groups are arranged, the closed-loop control flow channel 106 group includes an even number of medium flow channels and each medium flow channel is used to connect a hydraulic actuator; the medium flow channel includes a plurality of distribution start flow channels 2, each of which is connected to a separate throttling damping flow channel 101 and the throttling damping flow channel 101 is connected to a flow compensation flow channel 102 through at least two channels, and a throttling component and a damping member 5 are arranged in the throttling damping flow channel 101, and the flow compensation flow channel 102 is connected to the throttling damping flow channel 101. A flow compensation component 7 is arranged in the compensation flow channel 102; each flow compensation flow channel 102 is connected to the distribution end flow channel 105 and the hydraulic actuator through a separate pressure compensation component 3; the hydraulic actuator is connected through the pressure compensation flow channel 103 and feedback controls the opening of the pressure compensation component 3; the distribution end flow channel 105 is also unidirectionally connected to the throttling damping flow channel 101 through the return flow channel 104; when the medium flow channel supplies oil to the hydraulic actuator, the return flow channel 104 is closed, and when the medium flow channel returns oil from the hydraulic actuator, the return flow channel 104 is opened.

[0046] The high-precision synchronous valve group disclosed in this embodiment, the medium flow channel in the valve body 1 compensates for the medium, which can maintain the same flow and pressure of the medium in multiple medium flow channels when conveying to the hydraulic actuator, so as to maintain high precision and synchronization of control.

[0047] The high-precision synchronous valve group disclosed in this embodiment, the structure of the throttling damping channel 101 can be constructed in various forms and is not limited to a single form. This embodiment is optimized and adopts one of the feasible options: Figure 1~Figure 3 , Figure 5~Figure 8 As shown, a throttle valve 8 is provided at one end of the throttle damping flow channel 101, and a damping member 5 is provided at the other end of the throttle damping flow channel 101. The throttle damping flow channel 101 is connected to the flow compensation flow channel 102 through the throttle valve 8 and the damping member 5 respectively. When the above scheme is adopted, the damping member 5 and the throttle valve 8 can be used to control the flow, thereby adjusting the medium flow delivered to the flow compensation flow channel 102, which is convenient for correction to maintain the consistency of the medium flow.

[0048] Preferably, in this embodiment, Fig. 20 As shown, the hydraulic actuator can adopt a hydraulic cylinder; a set of closed-loop control circulation flow channels can be arranged in a valve body 1, and include two groups of medium flow channels, one group of medium flow channels is connected to the front cylinder body of the hydraulic cylinder, and the other group of medium flow channels is connected to the rear cylinder body of the hydraulic cylinder; the cooperation of the two groups of medium flow channels can realize the synchronous action of the hydraulic cylinder, including synchronous extension, synchronous retraction, etc.

[0049] Preferably, the medium flow channel in the valve body 1 can cooperate with multiple hydraulic cylinders, that is, by providing multiple distribution terminal flow channels 105, multiple hydraulic cylinders can be connected respectively, thereby realizing synchronous control of multiple hydraulic cylinders.

[0050] The specific connection position of the distribution start flow channel 2 is not limited to a single one. This embodiment optimizes and adopts one of the feasible options: the distribution start flow channel 2 is connected to the middle of the throttling damping flow channel 101. When the above solution is adopted, the distribution start flow channel 2 can disperse the conveying medium from the middle of the throttling damping flow channel 101 to both ends, maintaining the uniformity of the medium distribution.

[0051] The flow compensation channel 102 is used to adjust the medium flow in multiple channels to keep the medium flow delivered backwards consistent. The structure of the flow compensation channel 102 can be constructed in various forms, which are not limited to the only one. This embodiment is optimized and adopts one of the feasible options: Figure 8~Figure 10 As shown, the flow compensation channel 102 includes at least two flow compensation sections, and the flow compensation component 7 is located in each flow compensation section. When the above scheme is adopted, each flow compensation section corresponds to a medium channel, so the structure of the flow compensation channel can be in various forms, which is convenient for realizing simultaneous flow adjustment and compensation of multiple channels.

[0052] In order to more conveniently realize flow compensation and simplify the structure of the flow compensation channel 102, this embodiment is optimized and adopts one of the feasible options: the flow compensation channel 102 is a straight channel that passes through the valve body 1, and two flow compensation sections are formed in the flow compensation channel 102; Figure 11~Figure 13 , Fig.17 As shown, the flow compensation assembly 7 includes a flow compensation valve core 701 located in the flow compensation flow channel 102, and a compensation hole 703 is formed on the flow compensation valve core 701 to connect the flow compensation section and the pressure compensation flow channel 103; the oil in the flow compensation section applies force to the flow compensation valve core 701 and pushes the flow compensation valve core 701 in the opposite direction to change the opening of the compensation hole 703, thereby balancing the oil flow of the two oil compensation sections entering the pressure compensation assembly 3. When the above scheme is adopted, the compensation hole 703 of the flow compensation valve core 701 can also be constructed as a compensation groove; through the pressure of the oil medium of the compensation sections on both sides, the flow compensation valve core 701 is displaced between the two compensation ends and reaches a balance. When the medium pressure at one end is larger, the flow compensation valve core 701 is pushed to move to the compensation section on the other side, so that the opening of the compensation hole 703 of the compensation section on this side is reduced, and the opening of the compensation hole 703 of the compensation end on the other side is increased, thereby achieving balanced flow regulation.

[0053] Preferably, a return spring 702 is provided on the flow compensation valve core 701 , and the return spring 702 is symmetrically arranged at both ends of the flow compensation valve core 701 .

[0054] Pressure compensation provides another compensation solution. Through the pressure feedback of the hydraulic actuator, it acts on the medium flow channel at the front end to feedback and adjust the opening of the medium flow channel. Its structure can be constructed in various forms and is not limited to a single form. This embodiment optimizes and adopts one of the feasible options: Figure 11~Figure 13 , Fig.18 As shown, the pressure compensation channel 103 includes a pressure compensation chamber formed in the valve body 1 for setting the pressure compensation component 3, the pressure compensation chamber includes a lower chamber 103a, a middle chamber 103b and an upper chamber 103c, the lower chamber 103a is connected to the flow compensation channel 102, the middle chamber is connected to the distribution end channel 105, and the upper chambers are connected to each other; the pressure compensation component 3 includes a pressure compensation valve core 301 arranged in the pressure compensation chamber, when the pressure compensation valve core 301 is in the closed position, the lower chamber 103a is separated from the middle chamber 103b, and when the pressure compensation valve core 301 is in the open position, the lower chamber 103a is connected to the middle chamber 103b. When the above scheme is adopted, the load pressures of multiple hydraulic actuators are fed back to the corresponding pressure compensation components 3. The path with the largest load pressure pushes open the valve of the control valve and enters into multiple upper chambers 103c, and the load pressure acts on each pressure compensation valve core 301, thereby ensuring that each pressure compensation valve core 301 is subjected to the same feedback force, providing the same pressure compensation for each medium flow channel, thereby improving the accuracy of synchronous control.

[0055] The structure of the pressure compensation valve can adopt a variety of schemes, which are not limited to the only one. This embodiment is optimized and adopts one of the feasible options: Figure 11~Figure 13 , Fig.18 As shown, the pressure compensation valve core 301 extends from the lower chamber 103a to the upper chamber 103c, and a flow structure 302 connecting the lower chamber 103a and the middle chamber 103b is formed on the pressure compensation valve core 301. When the above solution is adopted, the flow structure 302 is used to pass the medium. The larger the opening of the flow structure 302, the larger the flow rate of the medium. The medium entering the lower chamber 103a can push the pressure compensation valve core 301 to open the flow structure 302 and enter the middle chamber 103b.

[0056] The control component can cooperate with the pressure compensation valve to realize the output pressure of the medium output to the outside. The structure of the control component can be constructed in various forms, which are not limited to the only one. This embodiment is optimized and adopts one of the feasible options: Fig.18 , Fig.19As shown, the control assembly includes a control valve, and the control valve includes a control flow channel 106 of the upper chamber 103c connected to all pressure compensation chambers, and a control valve core 9 for adjusting the on-off of the control flow channel 106 is arranged in the control flow channel 106. The control valve core 9 is used to receive the feedback pressure of each hydraulic actuator and deliver the hydraulic medium with the largest feedback pressure to the upper chamber 103c to form a consistent pressure compensation. When the above scheme is adopted, the control valve core 9 acts in the control flow channel 106 and is used to connect the upper chamber 103c. The pressure of the medium entering the upper chamber 103c is equal and provides corresponding pressure to the pressure compensation valve core 301, so as to achieve consistent pressure flow of the medium delivered to the outside.

[0057] The control channel 106 is used to feedback the pressure of the hydraulic actuator and is connected to the hydraulic actuator. The specific structure is not limited to the specific structure. This embodiment is optimized and adopts one of the feasible options: Fig.18 , Fig.19 As shown, the control channel 106 extends from the flow distribution end channel to the upper chamber 103c. When the above solution is adopted, the flow distribution end channel 105 can extend to the side wall surface of the main body.

[0058] When the medium flows back, it flows back to the throttling damping channel 101 through the return channel 104. The structure of the return channel 104 is not limited to a single one. This embodiment is optimized and adopts one of the feasible options: Figure 8~Figure 9 As shown, the return flow channel 104 is provided with a one-way valve 6, which limits the medium from unidirectionally returning from the hydraulic actuator to the throttling damping flow channel 101. When the above scheme is adopted, after the medium enters the throttling damping flow channel 101 through the one-way valve, it can reversely enter the distribution start flow channel 2.

[0059] The above are the implementation methods listed in this embodiment, but this embodiment is not limited to the above optional implementation methods. Those skilled in the art can arbitrarily combine the above methods to obtain other various implementation methods. Anyone can derive other various implementation methods under the inspiration of this embodiment. The above specific implementation methods should not be understood as limiting the protection scope of this embodiment. The protection scope of this embodiment should be based on the definition in the claims.

Claims

1. A high-precision synchronous valve group, characterized in that: The invention comprises a valve body (1), wherein a plurality of closed-loop control circulation flow channel groups are arranged on the valve body (1), wherein the closed-loop control flow channel (106) group comprises an even number of medium flow channels and each medium flow channel is used to connect to a hydraulic actuator; the medium flow channel comprises a plurality of distribution start flow channels (2), each distribution start flow channel (2) is connected to a separate throttling damping flow channel (101), and the throttling damping flow channel (101) is connected to a flow compensation flow channel (102) through at least two channels, a throttling assembly and a damping element (5) are arranged in the throttling damping flow channel (101), and a flow compensation flow channel (102) is arranged in the There is a flow compensation component (7); each flow compensation flow channel (102) is connected to the distribution end flow channel (105) and the hydraulic actuator through a separate pressure compensation component (3); the hydraulic actuator is connected through the pressure compensation flow channel (103) and feedback controls the opening of the pressure compensation component (3); the distribution end flow channel (105) is also unidirectionally connected to the throttling damping flow channel (101) through the return flow channel (104); when the medium flow channel supplies oil to the hydraulic actuator, the return flow channel (104) is closed, and when the medium flow channel returns oil from the hydraulic actuator, the return flow channel (104) is opened; A throttle valve (8) is disposed at one end of the throttle damping flow channel (101), and a damping member (5) is disposed at the other end of the throttle damping flow channel (101); the throttle damping flow channel (101) is connected to the flow compensation flow channel (102) via the throttle valve (8) and the damping member (5) respectively; The distribution start end flow channel (2) is connected to the middle of the throttling damping flow channel (101); The flow compensation channel (102) comprises at least two flow compensation sections, and the flow compensation component (7) is located in each flow compensation section; The flow compensation channel (102) is a straight channel that passes through the valve body (1), and two flow compensation sections are formed in the flow compensation channel (102); the flow compensation assembly (7) comprises a flow compensation valve core (701) located in the flow compensation channel (102), and a compensation hole (703) that connects the flow compensation section and the pressure compensation channel (103) is formed on the flow compensation valve core (701); the oil in the flow compensation section exerts force on the flow compensation valve core (701) and pushes the flow compensation valve core (701) in opposite directions to change the opening of the compensation hole (703), thereby balancing the oil flow of the two oil compensation sections entering the pressure compensation assembly (3); The pressure compensation flow channel (103) comprises a pressure compensation chamber formed in the valve body (1) and used to set the pressure compensation assembly (3), the pressure compensation chamber comprising a lower chamber (103a), a middle chamber (103b) and an upper chamber (103c), the lower chamber (103a) being connected to the flow compensation flow channel (102), the middle chamber being connected to the flow distribution end flow channel (105), and the upper chambers being connected to each other; the pressure compensation assembly (3) comprises a pressure compensation valve core (301) arranged in the pressure compensation chamber, the lower chamber (103a) being isolated from the middle chamber (103b) when the pressure compensation valve core (301) is in a closed position, and the lower chamber (103a) being connected to the middle chamber (103b) when the pressure compensation valve core (301) is in an open position; The pressure compensation valve core (301) extends from the lower chamber (103a) to the upper chamber (103c), and a flow structure (302) connecting the lower chamber (103a) and the middle chamber (103b) is formed on the pressure compensation valve core (301).

2. The high-precision synchronous valve group according to claim 1, characterized in that: The invention also includes a control component, wherein the control component includes a control channel (106) of an upper chamber (103c) connected to all pressure compensation chambers, and a control valve core (9) for adjusting the on-off state of the control channel (106) is arranged in the control channel (106). The control valve core (9) is used to receive the feedback pressure of each hydraulic actuator and transport the hydraulic medium with the maximum feedback pressure to the upper chamber (103c) to form a consistent pressure compensation.

3. The high-precision synchronous valve group according to claim 2, characterized in that: The control flow channel (106) extends from the flow distribution terminal channel to the upper chamber (103c).

4. The high-precision synchronous valve group according to claim 1, characterized in that: The return flow channel (104) is provided with a one-way valve (6), and the one-way valve (6) limits the one-way return flow of the medium from the hydraulic actuator to the throttling damping flow channel (101).

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