A pump-controlled balancing valve

Abstract

The present invention discloses a pump-controlled balancing valve. It comprises a valve body, a valve core, a one-way cone valve, a cone valve spring, a two-way pump and an actuator oil cylinder; the valve body is provided with a valve core, a one-way cone valve and a cone valve spring arranged in sequence along the axial direction; two left and right oil ports are provided at both ends of the valve body to respectively connect the two chambers of the actuator oil cylinder; two pairs of oil ports are symmetrically provided below the valve body to respectively connect the oil outlet of the two-way pump and the oil tank, and internal oil ports are provided above the valve body to communicate with each other; the valve core is symmetrical on the left and right and is processed into three sections of cylinders with different outer diameters, and slides left and right in the valve body to open and close the throttle port. The pump-controlled balancing valve of the present invention has a simple structure, low cost, good reliability, is insensitive to oil temperature and cleanliness, and can effectively ensure equal control or proportional control of input oil and output oil.

Description

Technical Field

[0001] The invention relates to a hydraulic component belonging to the technical field of hydraulic control components and systems, and in particular to a direct-drive pump-controlled balancing valve. Background Art

[0002] Hydraulic technology is a widely used transmission and control technology in modern industrial technology, with many advantages such as high power density and fast system response. In practical applications, in order to accurately control the position of the actuator in the system, it is necessary to accurately control the input or output flow of the actuator. It is necessary to set a servo valve or a proportional valve in the system, and then adjust the opening of the servo valve or the proportional valve instead of adjusting the speed of the system motor to achieve precise control of the flow of the system actuator. However, the servo proportional valve is not only expensive, but also has high requirements for the cleanliness of the oil. It also has a greater impact on the temperature rise of the system due to throttling. In comparison, it has certain requirements for the use environment of the system, so there are certain restrictions on its use. Summary of the invention

[0003] In order to solve the problems existing in the background technology, the present invention proposes a pump-controlled balancing valve, which can accurately control the output flow of the system directly by controlling the input flow of the system; and can realize proportional setting of input and output by processing the throttling groove on the valve core into different proportions, thereby realizing stable and accurate input and output control of both symmetrical cylinders and asymmetrical cylinders.

[0004] In order to achieve the above technical features, the present invention adopts the following technical solutions:

[0005] The present invention comprises a valve body, a valve core, a one-way cone valve, a cone valve spring, a two-way pump and an actuator oil cylinder; the valve body is provided with a valve core, a one-way cone valve and a cone valve spring which are arranged in sequence along the axial direction; two left and right oil ports are provided at both ends of the valve body to respectively connect the two chambers of the actuator oil cylinder; two pairs of oil ports are symmetrically provided below the valve body to respectively connect the oil outlet of the two-way pump and the oil tank, and internal oil ports are provided above the valve body to communicate with each other; the valve core is symmetrical on the left and right and is processed into three sections of cylinders with different outer diameters, and slides left and right in the valve body to open and close the throttle port.

[0006] The present invention comprises a valve body, a valve core, a left one-way cone valve, a right one-way cone valve, a left cone valve spring and a right cone valve spring; a left one-way valve cavity, a left valve cavity, a right valve cavity and a right one-way valve cavity are sequentially opened in the valve body along the axial direction, a valve core hole is opened in the valve body along the central axis, and the valve core hole is axially connected to the left one-way valve cavity, the left valve cavity, the right valve cavity and the right one-way valve cavity; a left one-way cone valve and a left cone valve spring are installed in the left one-way valve cavity, one end of the left one-way cone valve is used to be connected to the step between the left one-way valve cavity and the valve core hole, and the other end is connected through the left cone valve spring and the inner wall of the axial outward end of the left one-way valve cavity; a right one-way cone valve and a right cone valve spring are installed in the right one-way valve cavity, one end of the right one-way cone valve is used to be connected to the step between the right one-way valve cavity and the valve core hole, and the other end is connected through the right cone valve spring and the inner wall of the axial outward end of the right one-way valve cavity;

[0007] A valve core is installed in the valve core hole, and the valve core as a whole slides freely axially in the valve core hole of the valve body; an annular groove is provided on the outer periphery of one end face of the valve core close to the left one-way valve cavity to form a small cylinder on the left end of the valve core, and the small cylinder on the left end of the valve core is used to be connected to the left one-way cone valve, and an outer convex ring is provided on the outer periphery of the valve core in the left valve cavity to form a large left cylinder of the valve core; an annular groove is provided on the outer periphery of one end face of the valve core close to the right one-way valve cavity to form a small cylinder on the right end of the valve core, and the small cylinder on the right end of the valve core is used to be connected to the right one-way cone valve, and an outer convex ring is provided on the outer periphery of the valve core in the right valve cavity to form a large right cylinder of the valve core; an annular groove is provided on the inner wall of the left valve cavity in the middle along the axial direction as a left countersunk groove, and an annular groove is provided on the inner wall of the right valve cavity in the middle along the axial direction as a right countersunk groove.

[0008] The left large cylinder slides freely along the axial direction in the left valve cavity, but prevents the oil flow between the left cavity of the left valve cavity and the right cavity of the left valve cavity. The right large cylinder slides freely along the axial direction in the right valve cavity, but prevents the oil flow between the left cavity of the right valve cavity and the right cavity of the right valve cavity.

[0009] In a specific implementation, the outer diameters of the left cylinder, the middle cylinder and the right cylinder of the valve core are the same, and are all matched with the inner diameter of the valve core hole to ensure that the left cylinder, the middle cylinder and the right cylinder of the valve core can slide freely in the valve core hole, but form a seal at the same time.

[0010] The outer diameters of the left large cylinder of the valve core and the right large cylinder of the valve core are the same, and are respectively matched with the outer diameters of the left valve cavity and the right valve cavity to ensure that the left large cylinder of the valve core and the right large cylinder of the valve core can slide freely in the left valve cavity and the right valve cavity, while forming a seal at the same time.

[0011] The left one-way cone valve and the right one-way cone valve are respectively in the left one-way valve cavity and the right one-way valve cavity, so that a one-way connection and conduction are formed between the left one-way valve cavity and the right one-way valve cavity and the valve core hole respectively. Specifically, the diameter of the one-way cone valve is larger than the minimum diameter of the step between the one-way valve cavity and the valve core hole, so that the one-way cone valve body is pressed at the step under the pressure of the cone valve spring to form a sealing fit.

[0012] The section where the valve core hole is located between the left one-way valve chamber and the left valve chamber is the left valve core hole section, and the section where the valve core hole is located between the right one-way valve chamber and the right valve chamber is the right valve core hole section; the left valve chamber is divided into a left chamber of the left valve chamber close to the left one-way valve chamber and a right chamber of the left valve chamber close to the right one-way valve chamber by the left large cylinder of the valve core, and the right valve chamber is divided into a left chamber of the right valve chamber close to the left one-way valve chamber and a right chamber of the right valve chamber close to the right one-way valve chamber by the right large cylinder of the valve core.

[0013] It also includes an actuator cylinder, a motor and a bidirectional gear pump. The left one-way valve chamber and the right one-way valve chamber are respectively connected to the two chambers of the actuator cylinder, the left valve core hole section is connected to the right countersunk groove of the right valve chamber, and the right valve core hole section is connected to the left countersunk groove of the left valve chamber; the left chamber of the left valve chamber and the right chamber of the right valve chamber are directly connected to the oil tank, the right chamber of the left valve chamber and the left chamber of the right valve chamber are respectively connected to the two oil ports of the bidirectional gear pump, and the control shaft of the bidirectional gear pump and the output shaft of the motor are synchronously connected.

[0014] The valve body is provided with a left top oil port communicating with the left one-way valve cavity at one end face close to the left one-way valve cavity in the axial direction, and a right top oil port communicating with the right one-way valve cavity is provided at one end face close to the right one-way valve cavity in the axial direction; the valve body is provided with a left small oil port at a side wall corresponding to the outer periphery of the left valve core hole section, and the valve body is provided with a right small oil port at a side wall corresponding to the outer periphery of the right valve core hole section;

[0015] The valve body has a left valve cavity left oil port connected to the left cavity of the left valve cavity on the side wall corresponding to the outer periphery of the left cavity of the left valve cavity, and a left valve cavity right oil port connected to the right cavity of the left valve cavity is opened on the valve body at a corresponding position of the right cavity of the left valve cavity. The valve body has a right valve cavity left oil port connected to the left cavity of the right valve cavity on the side wall corresponding to the outer periphery of the left cavity of the right valve cavity, and a right valve cavity right oil port connected to the right cavity of the right valve cavity is opened on the valve body at a corresponding position of the right cavity of the right valve cavity. The valve body has a left countersunk groove oil port connected to the left countersunk groove on the side wall corresponding to the outer periphery of the left countersunk groove, and a right countersunk groove oil port connected to the right countersunk groove is opened on the side wall corresponding to the outer periphery of the right countersunk groove;

[0016] The left small oil port is connected to the right countersunk groove oil port via a pipeline, and the right small oil port is connected to the left countersunk groove oil port via a pipeline; the left one-way valve chamber is connected to the rod chamber of the actuator cylinder via the left top oil port and the pipeline, and the right one-way valve chamber is connected to the rodless chamber of the actuator cylinder via the right top oil port and the pipeline; the left oil port of the left valve chamber and the right oil port of the right valve chamber are both connected to the system oil tank, and the right oil port of the left valve chamber and the left oil port of the right valve chamber are respectively connected to the two oil ports of the bidirectional gear pump.

[0017] The outer diameters of the small cylinder on the left section of the valve core and the small cylinder on the right end of the valve core are both smaller than the inner diameter of the valve core hole, so that there is an annular gap between the small cylinder on the left section of the valve core and the small cylinder on the right end of the valve core and the valve core hole respectively.

[0018] The left large cylinder of the valve core is provided with a notch groove as the upper left throttling port at the outer edge of the left end face near the left one-way valve cavity, and a notch groove as the lower left throttling port is provided at the outer edge of the right end face near the right one-way valve cavity; the right large cylinder of the valve core is provided with a notch groove as the upper right throttling port at the outer edge of the left end face near the left one-way valve cavity, and a notch groove as the lower right throttling port is provided at the outer edge of the right end face near the right one-way valve cavity; and the ratio between the flow area of ​​the upper left throttling port and the flow area of ​​the upper right throttling port is the same as the ratio between the cross-sectional area of ​​the rodless cavity and the cross-sectional area of ​​the rod cavity of the actuator cylinder, and the ratio between the flow area of ​​the lower left throttling port and the flow area of ​​the lower right throttling port and the cross-sectional area of ​​the rodless cavity of the actuator cylinder is the same.

[0019] The axial cross-sectional areas of the left large cylinder of the valve core and the right large cylinder of the valve core are set to be twice the axial cross-sectional areas of the left cylinder of the valve core, the right cylinder of the valve core and the middle cylinder of the valve core.

[0020] The distance between the left edge of the left countersunk groove close to the left one-way valve cavity and the left edge of the right countersunk groove close to the left one-way valve cavity is exactly equal to the distance between the left end surface of the left large cylinder of the valve core close to the left one-way valve cavity and the left end surface of the right large cylinder of the valve core close to the left one-way valve cavity; the distance between the right edge of the left countersunk groove close to the right one-way valve cavity and the right edge of the right countersunk groove close to the right one-way valve cavity is exactly equal to the distance between the right end surface of the left large cylinder of the valve core close to the right one-way valve cavity and the right end surface of the right large cylinder of the valve core close to the right one-way valve cavity.

[0021] Compared with the prior art, the present invention has the following beneficial effects:

[0022] 1. The designed pump-controlled balancing valve has a simple structure, low cost, and low requirements on oil cleanliness and temperature changes.

[0023] 2. The hydraulic system based on this pump-controlled balancing valve can actively control the output flow of the system by controlling the input flow.

[0024] 3. Whether it is equal output or proportional output of the pump-controlled balancing valve, its equality or proportion is guaranteed by the size of mechanical processing and is almost unaffected by other external interference factors. Therefore, it is easier to achieve equal or proportional control and more reliable.

[0025] 4. Compared with the traditional overflow-based balancing valve or proportional valve, it has small throttling loss and low heat generation, and thus has very high energy utilization efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 A schematic diagram of the structure of a pump-controlled balancing valve provided in an embodiment of the present invention;

[0027] Figure 2 A schematic diagram of the structure of the pump-controlled balancing valve provided in an embodiment of the present invention when in working condition 1.

[0028] Figure 3 A schematic diagram of the structure of the pump-controlled balancing valve provided in an embodiment of the present invention when in working condition 2.

[0029] Figure 4 A schematic diagram of the structure of the pump-controlled balancing valve provided in an embodiment of the present invention when working in working conditions 3 and 4.

[0030] In the figure: valve body 1, valve core 2, left one-way cone valve 3, right one-way cone valve 4, left cone valve spring 3a, right cone valve spring 4a, actuator cylinder 21, motor 6, bidirectional gear pump 5; valve core hole 12, left one-way valve chamber 9a, left valve chamber 10, right valve chamber 11, right one-way valve chamber 9b; small cylinder 13a at the left end of valve core, left cylinder 14a of valve core, left large cylinder 15a of valve core, middle cylinder 16 of valve core, right large cylinder 15b of valve core, right cylinder 14b of valve core, small cylinder 13b at the right end of valve core; left valve chamber 10a , left valve chamber right chamber 10b; right valve chamber left chamber 11a, right valve chamber right chamber 11b; left countersunk groove 19a, right countersunk groove 19b, left upper throttle port 17a, right upper throttle port 17b; left lower throttle port 18a, right lower throttle port 18b; left top oil port 20a, right top oil port 20b; left small oil port 7a, right small oil port 7b; left countersunk groove oil port 8a, right countersunk groove oil port 8b; left valve chamber left oil port 22a, left valve chamber right oil port 23a; right valve chamber left oil port 23b, right valve chamber right oil port 22b. DETAILED DESCRIPTION

[0031] The above and other technical features and advantages of the present invention are clearly and completely described below in conjunction with the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, rather than all embodiments.

[0032] like Figure 1 and Figure 2The figure is a schematic diagram of the structure of the pump-controlled balancing valve in normal state, including a valve body 1, a valve core 2, a left one-way cone valve 3, a right one-way cone valve 4, a left cone valve spring 3a and a right cone valve spring 4a; the valve body 1 is provided with a left one-way valve chamber 9a, a left valve chamber 10, a right valve chamber 11 and a right one-way valve chamber 9b in sequence along the axial direction, the left one-way valve chamber 9a and the right one-way valve chamber 9b are symmetrically arranged on both sides of the valve body 1, the left valve chamber 10 and the right valve chamber 11 are symmetrically arranged on both sides of the valve body 1, a valve core hole 12 is provided in the valve body 1 along the central axis, the valve core hole 12 is axially connected to the left one-way valve chamber 9a, the left valve chamber 10, the right valve chamber 11 and the right one-way valve chamber 9b, and the valve core hole 12 runs through from the left one-way cone valve chamber 9a to the right one-way valve chamber 9b;

[0033] The left one-way valve chamber 9a is equipped with a left one-way cone valve 3 and a left cone valve spring 3a, one end of the left one-way cone valve 3 is used to connect to the step between the left one-way valve chamber 9a and the valve core hole 12, and the other end is connected to the inner wall of the axial outward end of the left one-way valve chamber 9a through the left cone valve spring 3a; the right one-way cone valve 4 and a right cone valve spring 4a are installed in the right one-way valve chamber 9b, one end of the right one-way cone valve 4 is used to connect to the step between the right one-way valve chamber 9b and the valve core hole 12, and the other end is connected to the inner wall of the axial outward end of the right one-way valve chamber 9b through the right cone valve spring 4a; the left and right one-way cone valves are respectively pressed against the steps in the one-way valve chamber of the valve body by the left and right cone valve springs to form a seal.

[0034] The valve core 2 is installed in the valve core hole 12, and the valve core 2 as a whole slides freely in the axial direction in the valve core hole 12 of the valve body 1, that is, slides in the left and right directions in the figure; the valve core 2 is provided with an annular groove on the outer periphery of one end surface close to the left one-way valve cavity 9a to form a small cylinder 13a at the left end of the valve core, and the small cylinder 13a at the left end of the valve core is used to be connected to the left one-way cone valve 3, and an outer convex ring is provided on the outer periphery of the valve core 2 in the left valve cavity 10 to form a large left cylinder 15a of the valve core; the valve core 2 is provided with an annular groove on the outer periphery of one end surface close to the right one-way valve cavity 9b to form a small cylinder 13b at the right end of the valve core, and the valve core is provided with an outer convex ring on the outer periphery of the valve core 2 The small end cylinder 13b is used to be connected to the right one-way cone valve 4, and an outer convex ring is arranged on the outer periphery of the valve core 2 in the right valve chamber 11 to form a right large cylinder 15b of the valve core; an annular groove is opened in the middle of the inner wall of the left valve chamber 10 along the axial direction as the left countersunk groove 19a, and the left large cylinder 15a of the valve core is located at the left countersunk groove 19a and can cover the left countersunk groove 19a during the axial movement; an annular groove is opened in the middle of the inner wall of the right valve chamber 11 along the axial direction as the right countersunk groove 19b, and the right large cylinder 15b of the valve core is located at the right countersunk groove 19b and can cover the right countersunk groove 19b during the axial movement.

[0035] The valve core 2 between the small cylinder 13a at the left end of the valve core and the left large cylinder 15a of the valve core forms a left valve core cylinder 14a, and the diameters of the small cylinder 13a at the left end of the valve core, the left valve core cylinder 14a, and the left large valve core cylinder 15a increase successively. The valve core 2 between the small cylinder 13b at the right end of the valve core and the right large valve core cylinder 15b forms a right valve core cylinder 14b, and the diameters of the small cylinder 13b at the right end of the valve core, the right valve core cylinder 14b, and the right large valve core cylinder 15b increase successively. The valve core 2 between the left large valve core cylinder 15a and the right large valve core cylinder 15b forms a middle valve core cylinder 16. The diameters of the left valve core cylinder 14a, the right valve core cylinder 14b, and the middle valve core cylinder 16 are the same, and all cooperate with the valve core hole 12.

[0036] At this point, the valve core 2 is processed into seven sections of cylinders from left to right, namely: the small cylinder 13a at the left end of the valve core, the left cylinder 14a of the valve core, the left large cylinder 15a of the valve core, the middle cylinder 16 of the valve core, the right large cylinder 15b of the valve core, the right cylinder 14b of the valve core, and the small cylinder 13b at the right end of the valve core. The small cylinder 13a at the left end and the small cylinder 13b at the right end are symmetrical and equal, the left cylinder 14a and the right cylinder 14b are symmetrical and equal and have the same outer diameter as the middle cylinder 16 of the valve core, and the left large cylinder 15a and the right large cylinder 15b are also symmetrical and equal; and the valve core 2 slides in the valve body (left and right directions) as a whole.

[0037] The left large cylinder 15a slides freely along the axial direction in the left valve chamber 10, but prevents the oil flow between the left valve chamber 10a and the right valve chamber 10b. Similarly, the right large cylinder 15b slides freely along the axial direction in the right valve chamber 11, but prevents the oil flow between the left valve chamber 11a and the right valve chamber 11b. In a specific implementation, the inner diameter of the left valve chamber 10 is equal to the outer diameter of the left large cylinder 15a of the valve core, or a small gap is formed to fit the seal, and the inner diameter of the right valve chamber 11 is equal to the outer diameter of the right large cylinder 15b of the valve core, or a small gap is formed to fit the seal.

[0038] The left one-way cone valve 3 and the right one-way cone valve 4 are respectively in the left one-way valve cavity 9a and the right one-way valve cavity 9b, so that the left one-way valve cavity 9a and the right one-way valve cavity 9b are respectively connected and conducted with the valve core hole 12 in a one-way manner. Specifically, the inner diameter of the one-way valve cavity is larger than the inner diameter of the valve core hole to form a step, and the diameter of the one-way cone valve is larger than the minimum diameter of the step between the one-way valve cavity and the valve core hole 12, that is, the aperture of the valve core hole 12, so that the one-way cone valve body is pressed at the step under the pressure of the cone valve spring to form a sealing fit.

[0039] The left and right one-way cone valves 3 and 4 are respectively pressed against the steps in the one-way valve cavity of the valve body by the left and right cone valve springs 3a and 4a by the spring elastic force, forming a conical surface between the sealed one-way cone valve and the step. When pressed, the hydraulic oil in the one-way valve cavity is prevented from flowing toward the valve core cavity; the one-way cone valves 3 and 4 move away from the valve core 2 under the pressure of the cone valve springs 3a and 4a, so that a gap is formed between the one-way cone valve and the step, thereby conducting.

[0040] The section where the valve core hole 12 is located between the left one-way valve chamber 9a and the left valve chamber 10 is the left valve core hole section, the section where the valve core hole 12 is located between the right one-way valve chamber 9b and the right valve chamber 11 is the right valve core hole section, and the section where the valve core hole 12 is located between the left valve chamber 10 and the right valve chamber 11 is the middle valve core hole section; the left valve chamber 10 is divided by the left large cylinder 15a of the valve core into a left valve chamber left chamber 10a close to the left one-way valve chamber 9a and a left valve chamber right chamber 10b close to the right one-way valve chamber 9b, and the right valve chamber 11 is divided by the right large cylinder 15b of the valve core into a right valve chamber left chamber 11a close to the left one-way valve chamber 9a and a right valve chamber right chamber 11b close to the right one-way valve chamber 9b.

[0041] It also includes an actuator cylinder 21, a motor 6 and a bidirectional gear pump 5. The left one-way valve chamber 9a and the right one-way valve chamber 9b are respectively connected to the two chambers of the actuator cylinder 21, and the two chambers are respectively a rod chamber and a rodless chamber. The left valve core hole section is connected to the right countersunk groove 19b of the right valve chamber 11, and the right valve core hole section is connected to the left countersunk groove 19a of the left valve chamber 10; the left chamber 10a of the left valve chamber and the right chamber 11b of the right valve chamber are both directly connected to the oil tank, the right chamber 10b of the left valve chamber and the left chamber 11a of the right valve chamber are respectively connected to the two working oil ports of the bidirectional gear pump 5, and the control shaft of the bidirectional gear pump 5 and the output shaft of the motor 6 are synchronously connected.

[0042] The valve body 1 is provided with a left top oil port 20a communicating with the left one-way valve cavity 9a at one end surface axially close to the left one-way valve cavity 9a, and a right top oil port 20b communicating with the right one-way valve cavity 9b is provided at one end surface axially close to the right one-way valve cavity 9b; the valve body 1 is provided with a left small oil port 7a at the side wall corresponding to the outer periphery of the left valve core hole section, and the valve body 1 is provided with a right small oil port 7b at the side wall corresponding to the outer periphery of the right valve core hole section;

[0043] The valve body 1 has a left valve chamber left oil port 22a in communication with the left valve chamber 10a on the side wall corresponding to the outer periphery of the left valve chamber 10a, a left valve chamber right oil port 23a in communication with the left valve chamber right chamber 10b on the corresponding position of the left valve chamber right chamber 10b, a right valve chamber left oil port 23b in communication with the right valve chamber left chamber 11a on the side wall corresponding to the outer periphery of the right valve chamber 11a, a right valve chamber right oil port 22b in communication with the right valve chamber right chamber 11b on the corresponding position of the right valve chamber 11b, a left countersunk groove oil port 8a in communication with the left countersunk groove 19a on the side wall corresponding to the outer periphery of the left countersunk groove 19a, and a right countersunk groove oil port 8b in communication with the right countersunk groove 19b on the side wall corresponding to the outer periphery of the right countersunk groove 19b;

[0044] The left small oil port 7a is connected as the internal oil port of the valve body through the oil circuit and the right countersunk groove oil port 8b, so that the left valve core hole section and the right countersunk groove 19b of the right valve chamber 11 are connected. The right small oil port 7b is connected as the internal oil port of the valve body through the oil circuit and the left countersunk groove oil port 8a, so that the right valve core hole section and the left countersunk groove 19a of the left valve chamber 10 are connected; the left one-way valve chamber 9a is connected to the rod chamber of the actuator cylinder 21 through the left top oil port 20a and the pipeline, and the right one-way valve chamber 9b is connected to the rodless chamber of the actuator cylinder 21 through the right top oil port 20b and the pipeline; the left valve chamber left oil port 22a and the right valve chamber right oil port 22b are both connected to the system oil tank, and the left valve chamber right oil port 23a and the right valve chamber left oil port 23b are respectively connected to the two high-pressure oil outlets of the bidirectional gear pump 5.

[0045] The outer diameters of the small cylinder 13a on the left section of the valve core and the small cylinder 13b on the right end of the valve core are both smaller than the inner diameter of the valve core hole 12, so that there is an annular gap between the small cylinder 13a on the left section of the valve core and the small cylinder 13b on the right end of the valve core and the valve core hole 12 respectively.

[0046] The left small cylinder 13a and the right small cylinder 13b are symmetrically arranged at both ends of the valve core 2 and have equal cross-sectional diameters. The left cylinder 14a and the right cylinder 14b are symmetrically arranged at both ends of the valve core 2 and have equal cross-sectional diameters as the cylinder 16 in the valve core. The left large cylinder 15a and the right large cylinder 15b are symmetrically arranged at both ends of the valve core 2 and have equal cross-sectional diameters.

[0047] The left large cylinder 15a of the valve core has a notch groove as the left upper throttle port 17a at the outer edge of the left end surface near the left one-way valve chamber 9a, and the left upper throttle port 17a is used to connect the left cavity 10a of the left valve chamber with the left undercut groove 19a. The outer edge of the right end surface near the right one-way valve chamber 9b has a notch groove as the left lower throttle port 18a, and the left lower throttle port 18a is used to connect the right cavity 10b of the left valve chamber with the left undercut groove 19a.

[0048] A notch groove is formed on the outer edge of the left end surface of the valve core 15b near the left one-way valve cavity 9a as a right upper throttle port 17b, and the right upper throttle port 17b is used to connect the left cavity 11a of the right valve cavity with the right undercut groove 19b. A notch groove is formed on the outer edge of the right end surface of the right one-way valve cavity 9b as a right lower throttle port 18b, and the right lower throttle port 18b is used to connect the right cavity 11b of the right valve cavity with the right undercut groove 19b.

[0049] In a specific implementation, a plurality of notch grooves may be arranged at intervals along the circumference of the outer edge.

[0050] The upper left throttle opening 17a and the lower left throttle opening 18a are completely identical in shape, and the upper right throttle opening 17b and the lower right throttle opening 18b are also completely identical in shape.

[0051] The shape of the notch groove can be a regular shape such as a triangle, a trapezoid or a rectangle to ensure the same moving distance and the throttling area of ​​the throttling port is always in a fixed proportion.

[0052] When the valve core moves to the right, the upper left throttle port and the upper right throttle port are in a flow matching working mode (equal or in a fixed ratio); when the valve core moves to the left, the lower left throttle port and the lower right throttle port are in a flow matching working mode.

[0053] The ratio of the flow area of ​​the upper left throttle port 17a to the flow area of ​​the upper right throttle port 17b is the same as the ratio of the cross-sectional area of ​​the rodless chamber and the cross-sectional area of ​​the rod chamber of the actuator cylinder 21, and the ratio of the flow area of ​​the lower left throttle port 18a to the flow area of ​​the lower right throttle port 18b to the cross-sectional area of ​​the rodless chamber and the cross-sectional area of ​​the rod chamber of the actuator cylinder 21 is the same.

[0054] As an implementable embodiment, when the execution cylinder 21 is a symmetrical cylinder, that is, the effective piston areas of the two chambers of the cylinder are equal, the flow area of ​​the upper left throttle port 17a and the flow area of ​​the upper right throttle port 17b are set to be exactly the same, and the flow area of ​​the lower left throttle port 18a and the flow area of ​​the lower right throttle port 18b are set to be exactly the same.

[0055] As an implementation method, when the execution cylinder 21 is an asymmetric cylinder, the effective piston areas of the two chambers of the cylinder are not equal, such as Figure 1-Figure 4For the cylinder shown in the figure, the ratio between the flow area of ​​the upper left throttle port 17a and the flow area of ​​the upper right throttle port 17b is the same as the ratio between the cross-sectional area of ​​the rodless cavity and the cross-sectional area of ​​the rod cavity of the actuator cylinder 21, and the flow area of ​​the lower left throttle port 18a and the flow area of ​​the lower right throttle port 18b are the same as the ratio between the cross-sectional area of ​​the rodless cavity and the cross-sectional area of ​​the rod cavity of the actuator cylinder 21, and are set to a fixed ratio. For example, when the ratio of the rodless cavity area to the rod cavity area of ​​the cylinder is 2:1, the ratio of the flow area of ​​the upper left throttle port 17a (also 18a) to the flow area of ​​the upper right throttle port 17b (also 18b) is also set to 2:1. 17a and 17b work as a combination, and similarly, 18a and 18b work as a combination.

[0056] The axial cross-sectional area of ​​the left large cylinder 15a and the right large cylinder 15b of the valve core is set to twice the axial cross-sectional area of ​​the left cylinder 14a, the right cylinder 14b and the middle cylinder 16 of the valve core, which is ensured by machining; that is, the annular area after deducting the area of ​​the left and right large cylinders 15a and 15b of the valve core from the area of ​​the left and right cylinders 14a and 14b of the valve core or the middle cylinder 16 of the valve core is exactly equal to the area of ​​the left and right cylinders 14a and 14b of the valve core or the middle cylinder 16 of the valve core.

[0057] The distance between the left edge of the left undercut groove 19a close to the left one-way valve cavity 9a and the left edge of the right undercut groove 19b close to the left one-way valve cavity 9a is exactly equal to the distance between the left end face of the left large cylinder 15a of the valve core close to the left one-way valve cavity 9a and the left end face of the right large cylinder 15b of the valve core close to the left one-way valve cavity 9a; similarly, the distance between the right edge of the left undercut groove 19a close to the right edge of the right undercut groove 19b close to the right one-way valve cavity 9b and the distance between the right end face of the left large cylinder 15a of the valve core close to the right one-way valve cavity 9b and the right end face of the right large cylinder 15b of the valve core close to the right one-way valve cavity 9b are exactly equal. In this way, synchronous throttling is ensured, and the throttling area changes synchronously with the displacement of the valve core, but the ratio of the throttling areas remains unchanged.

[0058] Under normal circumstances, Figure 1 , the two ends (top and end) of the valve core 2 just touch the bottom of the left and right one-way cone valves; and under normal conditions, the end of the upper left throttle port 17a just flushes with the left edge of the left countersunk groove 19a, so the end of the upper right throttle port 17b just aligns with the left edge of the right countersunk groove 19b; the top of the lower left throttle port 18a just flushes with the right edge of the left countersunk groove 19a, so the top of the lower right throttle port 18b just aligns with the right edge of the right countersunk groove 19b. The effect is that when the valve core moves and pushes the one-way cone valve to open, the throttle port also opens at the same time.

[0059] The working process of the present invention is:

[0060] Working condition 1, when the system needs to execute the cylinder to move to the right, and the load direction is also to the right (that is, the rod cavity pressure is high, and the rod cavity pressure is zero, that is, the "negative load" working condition), such as Figure 2 As shown, the high-pressure oil P1 of the control system is discharged through the two-way gear pump 5 and enters the left chamber 11a of the right valve chamber through the left oil port 23b of the right valve chamber, and the right chamber 11b of the right valve chamber is connected to the system oil tank (pressure is 0) through the right oil port 22b of the right valve chamber; under this working condition, the pressure PR (high pressure) generated by the load acts on the right one-way cone valve 4, and the high-pressure oil P1 discharged by the gear pump acts on the valve core annular surface corresponding to the left chamber 11a of the right valve chamber (the valve core annular area is the area of ​​the valve core large cylinder minus the valve core cylinder), and this valve core annular area is just equal to the area of ​​the valve core hole, that is, equal to the area of ​​the valve core hole, that is, equal to the seal pressed by the right one-way cone valve 4 step area; when the high-pressure oil P1 discharged by the gear pump is slightly greater than the load pressure PR (the extra pressure comes from the elastic force of the cone valve spring), the valve core 2 is pushed to slide to the right and the right one-way cone valve 4 is pushed open, so that the right small chamber 24b is connected with the right one-way valve chamber 9b, that is, it communicates with the right chamber of the actuator cylinder through the right top oil port 20b; at the same time, because the end of the upper left throttle port 17a is just flush with the left edge of the left countersunk groove 19a, and the end of the upper right throttle port 17b is just aligned with the left edge of the right countersunk groove 19b, the upper left throttle port 17a and the upper right throttle port 17b are also gradually and synchronously opened. The distance between the left edge of the left countersunk groove 19a and the left edge of the right countersunk groove 19b, and the distance between the left end face of the valve core left large cylinder 15a and the left end face of the valve core right large cylinder 15b are completely equal.

[0061] During this process, the oil flows as follows: Figure 3 As shown, the oil P1 discharged by the gear pump is reduced to pressure PA after passing through the left oil port 23b of the right valve chamber, the left chamber 11a of the right valve chamber, and the upper right throttle port 17b. (Because the annular area of ​​the valve core acted by PA is equal to the area of ​​the one-way cone valve acted by the load PA, after the system reaches balance, PA is approximately equal to PR; then the oil enters the left small oil port 7a through the right countersunk groove 19b and the right countersunk groove oil port 8b, so that the pressure oil pressure of the left small chamber 24a rises to PA, and the left one-way valve chamber is connected to the left chamber of the actuator cylinder (the pressure is 0), and the pressure difference on both sides of the left one-way valve (the pressure difference is PA, PA is also slightly Greater than PL, approximately equal, the excess pressure comes from the spring force) so that the left one-way valve 3 is pushed open, so that the left small chamber 24a is connected with the left one-way valve chamber 9a, and the oil flows to the left chamber of the actuator cylinder through the left top oil 20a; the hydraulic oil pressure PL in the left chamber of the cylinder rises to PA, that is, PL=PA=PR; at the same time, the hydraulic oil in the right chamber of the actuator cylinder passes through the right small chamber 24b, the one-way valve chamber 9b, the right small oil port 7b, the left countersunk groove oil port 8a, the left countersunk groove 19a, and then through the upper left throttle port 17a, the left valve chamber 10a, and the left valve chamber left oil port 22a back to the system oil tank.

[0062] Working condition 2, when the system needs to execute the cylinder to move to the right, and the load direction is left (i.e. the rod chamber PL is high pressure, and the rodless chamber PR is no pressure and zero), Figure 3 As shown, at this time, the high-pressure oil P1 of the control system is still discharged through the two-way gear pump 5 and enters the left chamber 11a of the right valve chamber through the left oil port 23b of the right valve chamber. The right chamber 11b of the right valve chamber is connected to the system oil tank (pressure is 0) through the right oil port 22b of the right valve chamber. Under this working condition, the pressure PL (high pressure) generated by the load acts on the left one-way cone valve 3; the pressure PR of the right chamber of the oil cylinder is 0, and the right one-way cone valve 4 is pressed against the step by the right cone valve spring 4a.

[0063] The high-pressure oil P1 discharged by the gear pump enters the left chamber 11a of the right valve chamber through the left oil port 23b of the right valve chamber, pushing the valve core 2 to slide to the right while pushing open the right one-way cone valve 4, so that the right small chamber 24b is connected with the right one-way valve chamber 9b, that is, it communicates with the right chamber of the actuator cylinder through the right top oil port 20b; at the same time, the upper left throttle port 17a and the upper right throttle port 17b are also gradually opened synchronously, so that the high-pressure oil P1 is further discharged through the upper right throttle port 17b (the pressure becomes the pressure PA), the right countersunk groove 19b, and the right countersunk groove oil port 8b enters the left small oil port 7a, causing the pressure oil pressure of the left small chamber 24a to rise to PA, until the pressure PA is approximately equal to PL (PA is slightly greater than PL, and the excess pressure comes from the spring force), pushing open the left one-way cone valve 3, allowing the oil to pass through the left small chamber 24a into the left one-way valve chamber 9a, and then flow to the left chamber of the actuator cylinder through the left top oil 20a. Because the annular area of ​​the valve core acted by PA is equal to the one-way cone valve area acted by load PL, PA is equal to PL after the system reaches balance.

[0064] Obviously, in the above working process, in working conditions 1 and 2, the oil inlet of the left chamber of the cylinder is discharged by the gear pump through 23b, and through the upper right throttle port 17b, the left one-way valve chamber 9a, and finally reaches the left chamber of the cylinder; while the return oil of the right chamber of the cylinder is discharged from the right chamber of the cylinder, through the right one-way valve chamber 9b, and then through the upper left throttle port 17a, the left valve chamber left oil port 22a back to the oil tank; because the opening of the upper right throttle port 17b and the upper left throttle port 17a are always synchronized, and the size of the throttle port is set to be a fixed ratio with the area of ​​the left and right chambers of the cylinder. For example; therefore, under the condition of equal pressure difference (the pressure difference is P1-PA), the amount of oil entering through the upper right throttle port 17b and the amount of oil returning through the upper left throttle port 17a are always in a fixed ratio (completely equal or in a fixed ratio with the area of ​​the two chambers of the cylinder), and the size of the flow rate is only related to the opening of the throttle port, that is, the flow rate of the bidirectional gear pump. The bidirectional gear pump is a fixed displacement pump, and the system can control the flow rate of the system by controlling the speed of the bidirectional gear pump, that is, the speed of the motor, that is, controlling the operating speed of the actuator cylinder.

[0065] Working condition 3, on the contrary, when the system needs to execute the cylinder to move to the left, and the load direction is to the right (i.e. the rodless chamber pressure PR is high pressure, and the rod chamber PL has no pressure and is zero); Figure 4 As shown, the high-pressure oil P2 of the control system is discharged through the two-way gear pump 5 and enters the right chamber 10b of the left valve chamber through the right oil port 23a of the left valve chamber. The left chamber 11b of the left valve chamber is connected to the system oil tank through the left oil port 22a of the left valve chamber. Under this working condition, the pressure PR (high pressure) generated by the load acts on the right chamber of the oil cylinder and the right one-way cone valve 4. The high-pressure oil P2 discharged by the gear pump acts on the annular surface of the valve core corresponding to the right chamber 10b of the left valve chamber. The annular area of ​​the valve core is the area of ​​the large cylinder of the valve core minus the area of ​​the valve core cylinder. This annular area of ​​the valve core is exactly equal to the area of ​​the valve core hole, that is, equal to the area of ​​the valve core hole pressed by the right one-way cone valve 4 Sealed step area; when the high-pressure oil P2 discharged by the gear pump is slightly greater than PL (the extra pressure comes from the elastic force of the cone valve spring), the valve core 2 is pushed to slide to the left and the left one-way cone valve 3 is pushed open at the same time, so that the left small chamber 24a is connected with the left one-way valve chamber 9a, and the oil communicates with the left chamber of the actuator cylinder through the left top oil port 20a; at the same time, because the end of the left lower throttle port 18a is just flush with the right edge of the left countersunk groove 19a, and the end of the right lower throttle port 18b is just aligned with the right edge of the right countersunk groove 19b, the left lower throttle port 18a and the right lower throttle port 18b are also gradually and synchronously opened. The distance between the right edge of the left countersunk groove 19a and the right edge of the right countersunk groove 19b, and the distance between the right end face of the left large cylinder 15a of the valve core and the right end face of the right large cylinder 15b of the valve core are completely equal.

[0066] During this process, the oil flows as follows: Figure 4 As shown, the high-pressure oil P2 discharged by the gear pump pushes the valve core 2 to the left and opens the throttle ports 18a and 18b. After the oil P2 passes through the right oil port 23a of the left valve chamber, the right chamber 10b of the left valve chamber, and the left lower throttle port 18a, the oil pressure drops to PB at this time; then it passes through the left countersunk groove 19a and the left countersunk groove oil port 8a and enters the right small oil port 7b, so that the pressure oil pressure of the right small chamber 24b rises to PB, and the right one-way valve chamber is connected to the right chamber of the actuator cylinder (pressure is PR). Because the annular area of ​​the valve core acted on by PB is equal to the area of ​​the one-way cone valve acted on by the load PR, the system After reaching balance, PB is equal to PR. When PB is slightly greater than PR (the excess pressure comes from the elastic force of the cone valve spring), the oil pushes open the one-way cone valve 4, so that the right small chamber 24b and the one-way valve chamber 9b are connected, and the oil enters the right chamber of the cylinder through the right top oil port 20b; at the same time, the hydraulic oil in the left chamber of the cylinder passes through the left top oil port 20a, the one-way valve chamber 9a, the left small chamber 24a, the left small oil port 7a, the right countersunk groove oil port 8b, the right countersunk groove 19b, and then through the right lower throttle port 18b, the right valve chamber 11b, and the right valve chamber right oil port 22b to return to the system oil tank.

[0067] Condition 4: When the system needs to execute the cylinder to move to the left, and the load direction is to the left (i.e. the rod chamber pressure PL is high pressure, and the rodless chamber PR is zero pressure, which is equivalent to "negative load"); or Figure 4 As shown, the high-pressure oil P2 of the control system is discharged through the bidirectional gear pump 5 and enters the right chamber 10b of the left valve chamber through the right oil port 23a of the left valve chamber. The left chamber 11b of the left valve chamber is connected to the system oil tank through the left oil port 22a of the left valve chamber. Under this working condition, the pressure PL (high pressure) generated by the load acts on the left chamber of the oil cylinder and the left one-way cone valve 3. The high-pressure oil P2 discharged by the gear pump acts on the annular surface of the valve core corresponding to the right chamber 10b of the left valve chamber. The annular area of ​​the valve core is the area of ​​the large cylinder of the valve core minus the area of ​​the valve core cylinder. This annular area of ​​the valve core is just equal to the area of ​​the valve core hole, that is, equal to the area of ​​the platform sealed by the right one-way cone valve 4. Step area; when the high-pressure oil P2 discharged by the gear pump is slightly greater than the load pressure PL (the excess pressure comes from the elastic force of the cone valve spring), the valve core 2 is pushed to slide to the left and the left one-way cone valve 3 is pushed open, so that the left small chamber 24a is connected with the left one-way valve chamber 9a, and the oil (high pressure) communicates with the left chamber of the actuator cylinder through the left top oil port 20a; at the same time, because the end of the left lower throttle port 18a is just flush with the right edge of the left countersunk groove 19a, and the end of the right lower throttle port 18b is just aligned with the right edge of the right countersunk groove 19b, the left lower throttle port 18a and the right lower throttle port 18b are also gradually and synchronously opened. The distance between the right edge of the left countersunk groove 19a and the right edge of the right countersunk groove 19b, and the distance between the right end face of the left large cylinder 15a of the valve core and the right end face of the right large cylinder 15b of the valve core are completely equal.

[0068] During this process, the oil flows as follows: Figure 4 As shown, the oil P2 discharged by the gear pump passes through the right oil port 23a of the left valve chamber, the right chamber 10b of the left valve chamber, and the left lower throttle port 18a, and the oil pressure is reduced to PB at this time; then it enters the right small oil port 7b through the left countersunk groove 19a and the left countersunk groove oil port 8a, so that the pressure oil pressure of the right small chamber 24b rises to PB', and the right one-way valve chamber is connected to the right chamber of the actuator cylinder (pressure is PR = 0), because the annular area of ​​the valve core acted by PB is equal to the one-way cone valve area acted by the load PR, then after the system reaches balance, PB is equal to PR, When PB is slightly larger than PR (the excess pressure comes from the elastic force of the cone valve spring), the oil pushes open the one-way cone valve 4, so that the right small chamber 24b and the one-way valve chamber 9b are connected, and the oil then enters the right chamber of the cylinder through the right top oil port 20b; at the same time, the hydraulic oil in the left chamber of the cylinder passes through the left top oil port 20a, the one-way valve chamber 9a, the left small chamber 24a, the left small oil port 7a, the right countersunk groove oil port 8b, the right countersunk groove 19b, and then through the right lower throttle port 18b, the right valve chamber 11b, and the right valve chamber right oil port 22b to return to the system oil tank.

[0069] Obviously, in the above changing process, in working condition 3 and working condition 4, the oil inlet of the right chamber of the cylinder is discharged by the gear pump through 23a, and then through the lower left throttle port 18a, the right one-way valve chamber 9b, and finally reaches the right chamber of the cylinder; while the oil return of the left chamber of the cylinder is discharged from the left chamber of the cylinder, through the left one-way valve chamber 9a, and then through the lower right throttle port 18b, the right oil port 22b of the right valve chamber back to the oil tank; because the opening of the lower left throttle port 18a and the lower right throttle port 18b are always synchronized, and the size of the throttle port is set to be fixed with the area of ​​the left and right chambers of the cylinder. ratio; therefore, under the condition of equal pressure difference (pressure difference is P2-PB), the amount of oil entering through the lower left throttle port 18a and the amount of oil returning through the lower right throttle port 18b are always in a fixed ratio (completely equal or in a fixed ratio with the area of ​​the two chambers of the cylinder), and the size of the flow rate is only related to the opening of the throttle port, that is, the flow rate of the bidirectional gear pump. The bidirectional gear pump is a fixed displacement pump. The system can control the flow rate of the system by controlling the speed of the bidirectional gear pump, that is, the speed of the motor, that is, controlling the running speed of the actuator cylinder.

[0070] When the actuator cylinder reaches the specified position and needs to stop, the system controls the motor to stop, the pump to stop, so that there is no flow input at the system input end; the left and right one-way cone valves 3, 4 will be closed and locked under the action of the load or cone valve spring, there is no flow inside the pump-controlled balancing valve, and the valve core 2 will return to the initial balanced position again, that is, Figure 1 status.

[0071] It can be seen from the implementation process that the pump-controlled balancing valve of the present invention has a simple structure, low cost, good reliability, is insensitive to oil temperature and cleanliness, and can effectively ensure equal control or proportional control of input oil and output oil.

[0072] The specific embodiments described above further illustrate the purpose, technical solutions and beneficial effects of the present invention. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the scope of protection of the present invention. It is particularly pointed out that for those skilled in the art, any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the scope of protection of the present invention.

Claims

1. A pump-controlled balancing valve, characterized in that: The valve body (1) comprises a valve core (2), a left one-way cone valve (3), a right one-way cone valve (4), a left cone valve spring (3a) and a right cone valve spring (4a); the valve body (1) is provided with a left one-way valve chamber (9a), a left valve chamber (10), a right valve chamber (11) and a right one-way valve chamber (9b) in sequence along the axial direction; the valve body (1) is provided with a valve core hole (12) along the central axis; the valve core hole (12) is connected to the left one-way valve chamber (9a), the left valve chamber (10), the right valve chamber (11) and the right one-way valve chamber (9b) along the axial direction; the left one-way valve chamber (9a) is provided with a left one-way cone valve. A valve (3) and a left cone valve spring (3a), one end of the left one-way cone valve (3) is used to connect to the step between the left one-way valve chamber (9a) and the valve core hole (12), and the other end is connected through the left cone valve spring (3a) and the inner wall of the axially outward end of the left one-way valve chamber (9a); a right one-way cone valve (4) and a right cone valve spring (4a) are installed in the right one-way valve chamber (9b), one end of the right one-way cone valve (4) is used to connect to the step between the right one-way valve chamber (9b) and the valve core hole (12), and the other end is connected through the right cone valve spring (4a) and the inner wall of the axially outward end of the right one-way valve chamber (9b); A valve core (2) is installed in the valve core hole (12). The valve core (2) as a whole freely slides in the axial direction in the valve core hole (12) of the valve body (1). An annular groove is provided on the outer periphery of one end surface of the valve core (2) close to the left one-way valve cavity (9a) to form a small cylinder (13a) at the left end of the valve core. The small cylinder (13a) at the left end of the valve core is used to be connected to the left one-way cone valve (3). An outer convex ring is provided on the outer periphery of the valve core (2) in the left valve cavity (10) to form a large cylinder (15a) at the left end of the valve core. An annular groove is provided on the outer periphery of one end surface of the one-way valve chamber (9b) to form a small cylinder (13b) on the right end of the valve core, and the small cylinder (13b) on the right end of the valve core is used to be connected to the right one-way cone valve (4); an outer convex ring is provided on the outer periphery of the valve core (2) in the right valve chamber (11) to form a large cylinder (15b) on the right end of the valve core; an annular groove is provided on the inner wall of the left valve chamber (10) along the axial middle portion thereof as a left undercut groove (19a), and an annular groove is provided on the inner wall of the right valve chamber (11) along the axial middle portion thereof as a right undercut groove (19b); The left large cylinder (15a) of the valve core slides freely along the axial direction in the left valve chamber (10), but prevents the oil flow between the left chamber (10a) of the left valve chamber and the right chamber (10b) of the left valve chamber; the right large cylinder (15b) of the valve core slides freely along the axial direction in the right valve chamber (11), but prevents the oil flow between the left chamber (11a) of the right valve chamber and the right chamber (11b) of the right valve chamber; The section where the valve core hole (12) is located between the left one-way valve chamber (9a) and the left valve chamber (10) is the left valve core hole section, and the section where the valve core hole (12) is located between the right one-way valve chamber (9b) and the right valve chamber (11) is the right valve core hole section; the left valve chamber (10) is divided by the valve core left large cylinder (15a) into a left valve chamber left chamber (10a) close to the left one-way valve chamber (9a) and a left valve chamber right chamber (10b) close to the right one-way valve chamber (9b), and the right valve chamber (11) is divided by the valve core right large cylinder (15b) into a right valve chamber left chamber (11a) close to the left one-way valve chamber (9a) and a right valve chamber right chamber (11b) close to the right one-way valve chamber (9b); It also includes an actuating cylinder (21), a motor (6) and a bidirectional gear pump (5); a left one-way valve chamber (9a) and a right one-way valve chamber (9b) are respectively connected to two chambers of the actuating cylinder (21); a left valve core hole section is connected to a right recessed groove (19b) of a right valve chamber (11); and a right valve core hole section is connected to a left recessed groove (19a) of a left valve chamber (10); a left chamber (10a) of a left valve chamber and a right chamber (11b) of a right valve chamber are both directly connected to an oil tank; a right chamber (10b) of a left valve chamber and a left chamber (11a) of a right valve chamber are respectively connected to two oil ports of a bidirectional gear pump (5); and a control shaft of the bidirectional gear pump (5) and an output shaft of the motor (6) are synchronously connected; The valve body (1) is provided with a left top oil port (20a) on one end surface axially close to the left one-way valve cavity (9a) and communicated with the left one-way valve cavity (9a), and a right top oil port (20b) on one end surface axially close to the right one-way valve cavity (9b) and communicated with the right one-way valve cavity (9b); the valve body (1) is provided with a left small oil port (7a) on a side wall corresponding to the outer periphery of the left valve core hole section, and the valve body (1) is provided with a right small oil port (7b) on a side wall corresponding to the outer periphery of the right valve core hole section; The valve body (1) is provided with a left valve chamber left oil port (22a) communicating with the left valve chamber left chamber (10a) on a side wall corresponding to the outer periphery of the left valve chamber left chamber (10a), and a left valve chamber right oil port (23a) communicating with the left valve chamber right chamber (10b) is provided on the valve body (1) at a position corresponding to the left valve chamber right chamber (10b), and the valve body (1) is provided with a right valve chamber left oil port (23a) communicating with the right valve chamber left chamber (11a) on a side wall corresponding to the outer periphery of the right valve chamber left chamber (11a). b), the valve body (1) is provided with a right valve chamber right oil port (22b) communicating with the right valve chamber right chamber (11b) at a position corresponding to the right chamber (11b) of the right valve chamber, the valve body (1) is provided with a left countersunk groove oil port (8a) communicating with the left countersunk groove (19a) at a side wall corresponding to the outer periphery of the left countersunk groove (19a), and the valve body (1) is provided with a right countersunk groove oil port (8b) communicating with the right countersunk groove (19b) at a side wall corresponding to the outer periphery of the right countersunk groove (19b); The left small oil port (7a) is connected to the right recessed groove oil port (8b) via a pipeline, and the right small oil port (7b) is connected to the left recessed groove oil port (8a) via a pipeline; the left one-way valve chamber (9a) is connected to the rod chamber of the actuator cylinder (21) via the left top oil port (20a) and the pipeline, and the right one-way valve chamber (9b) is connected to the rodless chamber of the actuator cylinder (21) via the right top oil port (20b) and the pipeline; the left valve chamber left oil port (22a) and the right valve chamber right oil port (22b) are both connected to the system oil tank, and the left valve chamber right oil port (23a) and the right valve chamber left oil port (23b) are respectively connected to the two oil ports of the bidirectional gear pump (5); The left large cylinder (15a) of the valve core has a notch groove as a left upper throttling port (17a) on the outer edge of the left end surface close to the left one-way valve cavity (9a), and has a notch groove as a left lower throttling port (18a) on the outer edge of the right end surface close to the right one-way valve cavity (9b); the right large cylinder (15b) of the valve core has a notch groove as a right upper throttling port (17b) on the outer edge of the left end surface close to the left one-way valve cavity (9a), and has a notch groove as a right lower throttling port (18a) on the outer edge of the right end surface close to the right one-way valve cavity (9b). A notch groove is opened on the outer edge of the surface as the lower right throttle port (18b); and the ratio between the flow area of ​​the upper left throttle port (17a) and the flow area of ​​the upper right throttle port (17b) is the same as the ratio between the cross-sectional area of ​​the rodless cavity and the cross-sectional area of ​​the rod cavity of the actuator cylinder (21), and the ratio between the flow area of ​​the lower left throttle port (18a) and the flow area of ​​the lower right throttle port (18b) and the cross-sectional area of ​​the rodless cavity and the cross-sectional area of ​​the rod cavity of the actuator cylinder (21) is the same.

2. A pump-controlled balancing valve according to claim 1, characterized in that: The left one-way cone valve (3) and the right one-way cone valve (4) are respectively in the left one-way valve cavity (9a) and the right one-way cone valve (9b), so that the left one-way valve cavity (9a) and the right one-way valve cavity (9b) are respectively connected and conducted to the valve core hole (12). Specifically, the diameter of the one-way cone valve is larger than the minimum diameter of the step between the one-way valve cavity and the valve core hole (12), so that the one-way cone valve body is pressed against the step by the pressure of the cone valve spring to form a sealing fit.

3. A pump-controlled balancing valve according to claim 1, characterized in that: The outer diameters of the small cylinder (13a) at the left end of the valve core and the small cylinder (13b) at the right end of the valve core are both smaller than the inner diameter of the valve core hole (12), so that an annular gap is formed between the small cylinder (13a) at the left end of the valve core and the small cylinder (13b) at the right end of the valve core and the valve core hole (12).

4. A pump-controlled balancing valve according to claim 1, characterized in that: The axial cross-sectional areas of the valve core left large cylinder (15a) and the valve core right large cylinder (15b) are set to be twice the axial cross-sectional areas of the valve core left cylinder (14a), the valve core right cylinder (14b) and the valve core middle cylinder (16).

5. A pump-controlled balancing valve according to claim 1, characterized in that: The distance between the left edge of the left recessed groove (19a) close to the left one-way valve cavity (9a) and the left edge of the right recessed groove (19b) close to the left one-way valve cavity (9a) is exactly equal to the distance between the left end surface of the left large cylinder (15a) of the valve core close to the left one-way valve cavity (9a) and the left end surface of the right large cylinder (15b) of the valve core close to the left one-way valve cavity (9a); the distance between the right edge of the left recessed groove (19a) close to the right one-way valve cavity (9b) and the right edge of the right recessed groove (19b) close to the right one-way valve cavity (9b) is exactly equal to the distance between the right end surface of the left large cylinder (15a) of the valve core close to the right one-way valve cavity (9b) and the right end surface of the right large cylinder (15b) of the valve core close to the right one-way valve cavity (9b).

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