Differential one-way overflow valve

Abstract

The differential type one-way overflow valve comprises a valve body, a valve seat and a one-way valve element, an overflow valve element is connected to the middle of the valve body in an inserted mode, and a load oil port is formed in the middle of the valve body; the valve seat is connected with the end, away from the gland, of the valve body, and an oil inlet and outlet is formed in one side of the valve seat. The one-way valve element is installed in the valve body, a surrounding type oil inlet channel is formed in the end face, close to the pressure adjusting screw, of the valve seat, and a one-way spring is installed at the other end of the one-way valve element. When pressure oil enters from the load oil port, due to the fact that the diameter D2 is larger than the diameter D1, the pressure oil acts on the annular zone area of D2-D1, when the pressure of the load oil port is enough to overcome the pre-compression force of the pressure adjusting spring, the load oil port is communicated with the oil inlet and outlet to form a differential overflow valve loop, and in the process, the load can be controlled to be reduced; and in addition, the descending process can be slowly carried out, load jitter is reduced, and the purpose of finely controlling working conditions is achieved.

Description

Technical Field

[0001] The present invention relates to the technical field of overflow valves, and particularly relates to a differential one-way overflow valve. Background Art

[0002] In a circuit for controlling the lifting, lowering, and pressure holding of a load, a hydraulic control one-way valve is often used. When oil enters from the oil port end of the one-way valve, the load can be controlled to rise. At this time, when the oil supply stops, the one-way valve can keep the load at a certain position. When pressure is applied to the hydraulic control oil port, the one-way valve can be opened, and the load can be controlled to lower. Due to the structural limitations of the hydraulic control one-way valve, during the process of controlling the load to lower, there will always be a problem of load jitter. In some fine control working conditions, the hydraulic control one-way valve cannot meet the usage requirements. Therefore, there is an urgent need for a differential one-way overflow valve. Summary of the Invention

[0003] Based on this, in view of the above technical problems, it is necessary to provide a differential one-way overflow valve.

[0004] In order to achieve the above object, the present invention adopts the following technical solutions: A differential one-way overflow valve, comprising: A valve body, in the middle of which an overflow valve core is inserted. A radial hole 1 is provided through the middle of the overflow valve core. A pressure regulating screw is provided at the end of the valve body. A pressure regulating spring is provided between the pressure regulating screw and the overflow valve core in the valve body. A load oil port is opened in the middle of the valve body, and the load oil port is communicated with the outer ring space of the overflow valve core; A valve seat, which is connected to the end of the valve body away from the gland. The end of the overflow valve core is inserted into the inner cavity of the valve seat, and the end of the overflow valve core abuts against the end of the valve seat through the valve core end face fixed by the outer ring. An oil inlet and outlet is opened on one side of the valve seat, and the oil inlet and outlet is communicated with the outer ring space of the overflow valve core in the valve seat; A one-way valve core, which is installed in the valve body and sleeved on the outer ring of the overflow valve core. A circumferential oil inlet passage is opened on the end face of the valve seat close to the pressure regulating screw, and the oil inlet passage is communicated with the oil inlet and outlet. The end of the one-way valve core abuts against the oil inlet passage on the valve seat, and a one-way spring is installed at the other end of the one-way valve core; The outer ring diameter of the corresponding ends of the overflow valve core and the valve seat is D1, and the outer ring diameter of the corresponding ends of the overflow valve core and the valve body is D2, and D2 is greater than D1.

[0005] As a preferred embodiment of the differential one-way relief valve provided by the present invention, a piston sleeve is inserted into the end of the valve seat away from the valve body, the inner cavity of the piston sleeve is connected to the cavity in the valve body which is connected to the inlet and outlet oil ports, a piston is installed in the piston sleeve, and the corresponding inner diameter of the piston sleeve and the piston is D3, and D3 is larger than D1. The ratio of the area of the piston to the area of the annulus D2-D1 is the control ratio, and the control ratio can be changed by changing the diameter of D3.

[0006] As a preferred embodiment of the differential one-way relief valve provided by the present invention, the outer ring of the pressure-adjusting screw is provided with a pressure cover, and the pressure cover is installed with the end of the relief valve core, wherein the pressure cover and the valve body, the pressure cover and the pressure-adjusting screw are all connected by threads, so that the position of the pressure-adjusting screw can be adjusted by rotating the pressure cover, thereby adjusting the compression force on the pressure-adjusting spring.

[0007] As a preferred embodiment of the differential one-way relief valve provided by the present invention, a spring seat is arranged between the end of the relief valve core and the pressure regulating spring, and the spring seat is penetrated by a radial hole 2 which is connected with the radial hole 1. The elastic force of the pressure regulating spring acts on the relief valve core through the spring seat, thereby reducing the damage of the end of the pressure regulating spring to the end of the relief valve core and better protecting the relief valve core. The relief valve core and the spring seat are matched with an outer spherical surface and an inner cone angle, and can automatically adjust the center alignment.

[0008] As a preferred embodiment of the differential one-way relief valve provided by the present invention, the end face of the one-way valve core adopts an inner cone angle to hard-seal with the oil inlet channel on the valve seat.

[0009] As a preferred embodiment of the differential one-way relief valve provided by the present invention, a piston is installed in the middle of the piston sleeve, and a control oil port is arranged through the middle of the piston. When the pressure of the control oil port increases, the piston is pushed to move to the left, and the left end of the piston and the right end of the relief valve core begin to contact. When the piston thrust is sufficient to overcome the pre-compression force of the pressure regulating spring, the relief valve core is pushed to move to the left, opening the hard sealing point between the relief valve core and the left end of the valve seat, and the load oil port and the inlet and outlet oil ports are connected to form a throttle valve circuit.

[0010] As a preferred embodiment of the differential one-way overflow valve provided by the present invention, a secondary pressure mechanism is provided at the input end of the piston. The secondary pressure mechanism includes a hydraulic control cylinder communicated with the control oil port on the piston and a pressure storage cylinder communicated with the inner cavity of the hydraulic control cylinder. A hydraulic pressure gauge is installed on the pressure storage cylinder. By setting the secondary pressure mechanism, hydraulic oil enters the hydraulic control cylinder and is injected into the control oil port. During the injection process, the hydraulic oil is introduced into the pressure storage cylinder, and the hydraulic state in the pressure storage cylinder is viewed through the hydraulic pressure gauge. When it is necessary to quickly increase the pressure in the control oil port, the hydraulic oil with a certain pressure in the pressure storage cylinder is quickly introduced into the hydraulic control cylinder and injected into the control oil port to achieve the purpose of quickly adjusting the pressure.

[0011] As a preferred embodiment of the differential one-way overflow valve provided by the present invention, a central shaft is horizontally inserted in the middle of the hydraulic control cylinder. An end of the central shaft close to the output end of the hydraulic control cylinder is provided with a middle shaft, and the middle shaft abuts against the inner ring of the output end of the hydraulic control cylinder. A movable piston plate slidably connected to the inner wall of the hydraulic control cylinder is fixed in the middle of the middle shaft. A blocking block placed at the communication part of the pressure storage cylinder and the hydraulic control cylinder is fixed on the movable piston plate. A through hole 1 is opened on the movable piston plate. The oil pump injects hydraulic oil into the hydraulic control cylinder. The high-pressure hydraulic oil pushes the blocking valve to move. The blocking valve drives the movable piston plate and the blocking block to move synchronously, thereby opening the communication port between the pressure storage cylinder and the hydraulic control cylinder. The hydraulic oil enters the pressure storage cylinder to increase the pressure in the pressure storage cylinder. The hydraulic oil entering the hydraulic control cylinder is injected into the control oil port through the through hole 1 on the movable piston plate to increase the pressure in the control oil port. After the pressure adjustment is completed, the oil pump is closed. At this time, the movable piston plate resets to block the inlet of the hydraulic control cylinder, and at the same time, the blocking block blocks the opening between the pressure storage cylinder and the hydraulic control cylinder to complete the purpose of increasing the pressure inside the pressure storage cylinder. When the hydraulic oil is injected into the hydraulic control cylinder again by the oil pump, as shown in the figure, the blocking valve opens and controls the displacement of the blocking block. At this time, the high-pressure hydraulic oil in the pressure storage cylinder is quickly injected into the hydraulic control cylinder, thereby quickly increasing the pressure in the hydraulic control cylinder, and further quickly increasing the pressure of the hydraulic oil injected into the control oil port to achieve the purpose of quickly adjusting the pressure.

[0012] As a preferred embodiment of the differential one-way overflow valve provided by the present invention, a fixed piston plate is fixed in the middle of the hydraulic control cylinder. The fixed piston plate is located on the side of the moving piston plate close to the piston. The central shaft is inserted into the fixed piston plate. An elastic member is installed between the end of the central shaft and the fixed piston plate. A second through hole is formed on the fixed piston plate. The first through hole and the second through hole are arranged in a staggered manner. An electromagnet corresponding to the moving piston plate is installed on the fixed piston plate. The moving piston plate is made of ferromagnetic metal. A hydraulic sensor is installed in the inner cavity of the pressure storage cylinder. In order to improve the accuracy of regulating the pressure of the control oil port, it is necessary to increase the pressure in the pressure storage cylinder to a preset value, so as to quickly inject the hydraulic oil with the preset pressure in the pressure storage cylinder into the control oil port when the blocking block is opened. At this time, by controlling the operation of the electromagnet, the electromagnet generates magnetism to magnetically attract the moving piston plate, and the moving piston plate abuts. Since the first through hole and the second through hole are arranged in a staggered manner, the inner cavity of the hydraulic control cylinder is blocked by the fixed piston plate and the moving piston plate at this time. The hydraulic oil entering from the input end of the hydraulic control cylinder completely enters the pressure storage cylinder, and the pressure state of the hydraulic oil in the pressure storage cylinder is detected by the hydraulic sensor. The pressure in the pressure storage cylinder is adjusted by continuously injecting hydraulic oil through the operation of the oil pump, so as to achieve the purpose of automatically controlling the pressure of the hydraulic oil in the pressure storage cylinder. And when the pressure in the pressure storage cylinder reaches the preset value, the control electromagnet stops working, and the elastic member is used to push the central shaft to drive the moving piston plate to reset. At the same time, the blocking block blocks the connection between the pressure storage cylinder and the hydraulic control cylinder to seal the pressure storage cylinder.

[0013] As a preferred embodiment of the differential one-way overflow valve provided by the present invention, an auxiliary pressure controller is further provided on the piston. The auxiliary pressure controller includes a detection module and a pressure regulating module. The detection module is respectively connected to the pressure regulating module and the hydraulic sensor in a signal manner. The pressure regulating module is connected to the electromagnet in a signal manner. When it is necessary to control the pressure of the hydraulic oil in the pressure storage cylinder to increase to a preset value, the oil pump works to inject the hydraulic oil into the hydraulic control cylinder. The pressure regulating module controls the operation of the electromagnet, and the moving piston plate fits with the fixed piston plate to block the inner cavity of the hydraulic control cylinder. The hydraulic oil enters the pressure storage cylinder to increase the pressure. The hydraulic sensor sends the detected pressure value to the detection module. The detection module compares the pressure value with the pressure preset value. When it is judged that the pressure value reaches the pressure preset value, the pressure regulating module controls the electromagnet to stop working, and the elastic member is used to push the central shaft to drive the moving piston plate to reset. At the same time, the blocking block blocks the connection between the pressure storage cylinder and the hydraulic control cylinder to seal the pressure storage cylinder.

[0014] Compared with the prior art, the present invention has the following beneficial effects: 1. A differential one-way overflow valve provided by the present invention. Under the action of the compression force of the one-way spring, the one-way valve core is pushed rightward against the valve seat, and the pressure regulating spring presses the overflow valve core, pushing the overflow valve core rightward against the valve seat. At this time, when the pressure oil enters from the oil inlet and outlet, one path passes through the radial hole 1 of the valve seat into the cavity where the pressure regulating spring is located, and the other path acts on the right end face of the one-way valve core through the oil inlet passage on the valve seat. After overcoming the spring force of the one-way spring, the one-way valve core is pushed open, passes through the middle of the overflow valve core and the annular part of the valve body, and then enters the load oil port through the oil inlet passage on the valve body, forming a one-way valve circuit. When the pressure oil enters from the load oil port, since the diameter D2 is greater than the diameter D1, the pressure oil acts on the annular area of D2 - D1. When the pressure at the load oil port is sufficient to overcome the pre-compression force of the pressure regulating spring, the load oil port and the oil inlet and outlet are connected, forming a differential overflow valve circuit. During this process, the load descent can be controlled, and the descent process can be slow, and the load jitter can be reduced, achieving the purpose of fine control of the working condition.

[0015] 2. A differential one-way overflow valve provided by the present invention. In order to improve the accuracy of regulating the pressure of the control oil port, it is necessary to increase the pressure in the pressure storage cylinder to a preset value, so as to quickly inject the hydraulic oil with the preset pressure in the pressure storage cylinder into the control oil port when the plugging block is opened. At this time, by controlling the operation of the electromagnet, the electromagnet generates magnetism to magnetically attract the moving piston plate, and the moving piston plate abuts. Since the through hole 1 and the through hole 2 are arranged in a dislocation manner, at this time, the fixed piston plate and the moving piston plate block the inner cavity of the liquid control cylinder. At this time, the hydraulic oil entering from the input end of the liquid control cylinder completely enters the pressure storage cylinder, and the pressure state of the hydraulic oil in the pressure storage cylinder is detected by the hydraulic sensor. The pressure in the pressure storage cylinder is adjusted by continuously injecting hydraulic oil through the operation of the oil pump, achieving the purpose of automatically controlling the pressure of the hydraulic oil in the pressure storage cylinder. And when the pressure in the pressure storage cylinder reaches the preset value, the control electromagnet is disconnected from the operation, and the middle shaft is driven by the elastic member to drive the moving piston plate to reset. At the same time, the plugging block blocks the connection between the pressure storage cylinder and the liquid control cylinder, sealing the pressure storage cylinder. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the drawings required to be used in the embodiments. Obviously, the following-described drawings are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0017] Figure 1 It is a cross-sectional view provided by the present invention; Figure 2 It is a schematic diagram of the positions of D1, D2 and D3 provided by the present invention; Figure 3 It is a schematic diagram of the structure of the piston and the auxiliary pressure mechanism provided by the present invention; Figure 4 Schematic diagram of the auxiliary pressure mechanism provided by the present invention; Figure 5 Schematic diagram of the displacement of the plugging block driven by the plugging valve in the auxiliary pressure mechanism provided by the present invention; Figure 6 Schematic diagram of the contact between the moving piston plate and the fixed piston plate provided by the present invention; Figure 7 Control principle block diagram of the auxiliary pressure controller provided by the present invention.

[0018] The markings in the figure are explained as follows: 1. Piston; 2. Piston sleeve; 3. Valve seat; 4. Valve body; 5. Check valve core; 6. Check spring; 7. Overflow valve core; 8. Spring seat; 9. Pressure regulating spring; 10. Pressure regulating screw; 11. Gland; 12. Control oil port; 13. Inlet and outlet oil port; 14. Load oil port; 15. Radial hole 1; 16. Oil inlet channel; 17. Radial hole 2; 18. Hydraulic control cylinder; 19. Accumulator cylinder; 20. Plugging valve; 21. Central shaft; 22. Moving piston plate; 23. Plugging block; 24. Fixed piston plate; 25. Electromagnet; 26. Hydraulic sensor; 27. Pressure gauge. Detailed implementation manners

[0019] In order to enable those skilled in the art to better understand the solution of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0020] In order to enable those skilled in the art to better understand the solution of the present invention, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings. It should be noted that, without conflict, the embodiments and features and technical solutions in the embodiments of the present invention can be combined with each other.

[0021] It should be noted that: similar reference numerals and letters denote similar items in the following drawings. Therefore, once an item is defined in one drawing, it does not need to be further defined and explained in subsequent drawings. Embodiment

[0022] Please refer to Figure 1 - Figure 2, A differential unidirectional overflow valve, comprising: a valve body 4, a valve seat 3 and a unidirectional valve core 5. An overflow valve core 7 is inserted in the middle of the valve body 4. A first radial hole 15 is provided through the middle of the overflow valve core 7. A pressure regulating screw 10 is provided at the end of the valve body 4. A pressure regulating spring 9 is provided between the pressure regulating screw 10 and the overflow valve core 7 in the valve body 4. A load oil port 14 is provided in the middle of the valve body 4. The load oil port 14 communicates with the outer ring space of the overflow valve core 7; The valve seat 3 is connected to one end of the valve body 4 away from the gland 11. The end of the overflow valve core 7 is inserted into the inner cavity of the valve seat 3, and the end of the overflow valve core 7 abuts against the end of the valve seat 3 through the end face fixed to the outer ring. An oil inlet and outlet port 13 is provided on one side of the valve seat 3. The oil inlet and outlet port 13 communicates with the outer ring space of the overflow valve core 7 in the valve seat 3; The unidirectional valve core 5 is installed in the valve body 4 and sleeved on the outer ring of the overflow valve core 7. A circumferential oil inlet channel 16 is provided on the end face of the valve seat 3 close to the pressure regulating screw 10. The oil inlet channel 16 communicates with the oil inlet and outlet port 13. The end of the unidirectional valve core 5 abuts against the oil inlet channel 16 on the valve seat 3. A unidirectional spring 6 is installed at the other end of the unidirectional valve core 5; The outer ring diameter of the corresponding end of the overflow valve core 7 and the valve seat 3 is D1, and the outer ring diameter of the corresponding end of the overflow valve core 7 and the valve body 4 is D2, and D2 is greater than D1.

[0023] Through the above structural design, the outer circle of the left end of the valve seat 3 and the inner hole of the right end step of the valve body 4 are in transitional fit. A snap ring groove is provided at the rightmost end of the inner hole of the valve body 4, and a snap ring is installed to limit the valve seat 3; The inside of the valve seat 3 is a stepped through hole. A piston sleeve 2 is arranged with a large diameter at the right end. A piston 1 is arranged inside the piston sleeve 2. The right ends of the piston sleeve 2 and the piston 1 are limited by snap rings, and seals are provided on the outer circles. A ring groove is provided on the left end face of the valve seat 3. Three axial waist-shaped grooves are provided on the ring groove, which are respectively communicated with three radial arc grooves to form the oil inlet and outlet port 13 channel; The left end of the valve seat 3 is the unidirectional valve core 5. The outer circle of the unidirectional valve core 5 and the inner hole of the valve body 4 are in clearance fit and are provided with seals. The inner conical surface at its right end abuts against the obtuse vertex of the small diameter of the ring groove on the right end face of the valve seat 3. Under the action of the compression force of the unidirectional spring 6, a hard seal of the unidirectional valve is formed; An overflow valve core 7 is provided between the valve seat 3 and the inner hole of the valve body 4. The outer circle diameter D2 of the left end of the overflow valve core 7 and the inner hole of the valve body 4 are in clearance fit and are provided with seals. The outer circle of the right end of the overflow valve core 7 and the inner hole of the valve seat 3 are in clearance fit. There is a slightly larger diameter step at the left end of the outer circle, and an outer cone angle is provided. This outer cone angle abuts against the obtuse vertex of the end face diameter D1 of the inner hole at the left end of the valve seat 3 to form the hard seal point of the overflow valve.

[0024] Among them, the initial state of this overflow valve is as Figure 1, under the action of the compression force of the one-way spring 6, the one-way valve core 5 presses against the valve seat 3 to the right, and the pressure regulating spring 9 presses the overflow valve core 7, pushing the overflow valve core 7 to the right against the valve seat 3; at this time, when the pressure oil enters from the inlet and outlet ports 13, one path passes through the radial hole 15 of the valve seat 3 to enter the cavity where the pressure regulating spring 9 is located, and the other path passes through the oil inlet channel 16 on the valve seat 3 to act on the end surface of the one-way valve core 5, overcomes the spring force of the one-way spring 6, pushes the one-way valve core 5 open, passes through the middle of the overflow valve core 7 and the annular part of the valve body 4, and then passes through the oil inlet channel 16 on the valve body 4 to enter the load oil port 14, forming a one-way valve circuit; When the pressure oil enters from the load oil port 14, since the diameter D2 is larger than the diameter D1, the pressure oil acts on the annular area of D2-D1. When the pressure of the load oil port 14 is sufficient to overcome the pre-compression force of the pressure regulating spring 9, the load oil port 14 and the inlet and outlet oil ports 13 are connected to form a differential overflow valve circuit. In this process, the load can be controlled to drop, and the drop process can be carried out slowly, and the load jitter can be reduced, thereby achieving the purpose of fine control of the working conditions.

[0025] In addition, a piston sleeve 2 is inserted into the end of the valve seat 3 away from the valve body 4, the inner cavity of the piston sleeve 2 is connected to the cavity in the valve body 4 which is connected to the inlet and outlet oil ports 13, a piston 1 is installed in the piston sleeve 2, the corresponding inner diameters of the piston sleeve 2 and the piston 1 are D3, D3 is larger than D1, a piston 1 is installed in the middle of the piston sleeve 2, a control oil port 12 is provided through the middle of the piston 1, when the pressure of the control oil port 12 increases, the piston 1 is pushed to move to the left, the left end of the piston 1 and the right end of the overflow valve core 7 begin to contact, when the thrust of the piston 1 is sufficient to overcome the pre-compression force of the pressure regulating spring 9, the overflow valve core 7 is pushed to move to the left, the hard sealing point between the overflow valve core 7 and the left end of the valve seat 3 is opened, the load oil port 14 and the inlet and outlet oil ports 13 are connected, and a throttling valve circuit is formed; wherein, the ratio of the area of the piston 1 to the area of the annulus D2-D1 is the control ratio, and the control ratio can be changed by changing the diameter of D3.

[0026] In this embodiment, the outer ring of the pressure-adjusting screw 10 is provided with a pressure cap 11, and the pressure cap 11 is installed with the end of the overflow valve core 7, wherein the pressure cap 11 and the valve body 4, the pressure cap 11 and the pressure-adjusting screw 10 are all connected by threads, so that the position of the pressure-adjusting screw 10 can be adjusted by rotating the pressure cap 11, thereby adjusting the compression force on the pressure-adjusting spring 9.

[0027] A spring seat 8 is arranged between the end of the overflow valve core 7 and the pressure regulating spring 9. The spring seat 8 is penetrated by a radial hole 2 17 connected with the radial hole 15. The elastic force of the pressure regulating spring 9 acts on the overflow valve core 7 through the spring seat 8, reducing the damage of the end of the pressure regulating spring 9 to the end of the overflow valve core 7, and better protecting the overflow valve core 7. The overflow valve core 7 and the spring seat 8 are both matched with the outer spherical surface and the inner cone angle contact, and can automatically adjust the center alignment. The end face of the one-way valve core 5 adopts the inner cone angle to hard seal with the oil inlet channel 16 on the valve seat 3. Embodiment

[0028] The differential unidirectional overflow valve provided in the first embodiment is further optimized. Different from the first embodiment, when injecting high pressure into the control oil port 12 in the piston 1, a hydraulic pump is usually used to inject hydraulic oil into the control oil port 12. Therefore, it takes a certain amount of time for the hydraulic pump to start and pump the hydraulic oil to the preset hydraulic value, resulting in insufficient speed and sensitivity when pressurizing the control oil port 12, and there is a certain delay. To solve the above problems, as Figure 3 - Figure 7 shown, an auxiliary pressure mechanism is provided at the input end of the piston 1. The auxiliary pressure mechanism includes a hydraulic control cylinder 18 communicated with the control oil port 12 on the piston 1 and a pressure storage cylinder 19 communicated with the inner cavity of the hydraulic control cylinder 18. A hydraulic pressure gauge 27 is installed on the pressure storage cylinder 19. By setting the auxiliary pressure mechanism, the hydraulic oil enters the hydraulic control cylinder 18 and is injected into the control oil port 12. During the injection process, the hydraulic oil is introduced into the pressure storage cylinder 19, and the hydraulic state in the pressure storage cylinder 19 is viewed through the hydraulic pressure gauge 27. When it is necessary to quickly increase the pressure in the control oil port 12, the hydraulic oil with a certain pressure in the pressure storage cylinder 19 quickly enters the hydraulic control cylinder 18 and is injected into the control oil port 12 to achieve the purpose of quickly adjusting the pressure.

[0029] It is worth mentioning that the middle part of the hydraulic control cylinder 18 is horizontally inserted with a central shaft 21. One end of the central shaft 21 close to the output end of the hydraulic control cylinder 18 is provided with a central shaft 21, and the central shaft 21 abuts against the inner ring of the output end of the hydraulic control cylinder 18. A moving piston plate 22 slidably connected to the inner wall of the hydraulic control cylinder 18 is fixed in the middle of the central shaft 21. A blocking block 23 placed at the communication position between the pressure storage cylinder 19 and the hydraulic control cylinder 18 is fixed on the moving piston plate 22. A through hole 1 is opened on the moving piston plate 22. The hydraulic pump injects hydraulic oil into the hydraulic control cylinder 18. The high-pressure hydraulic oil pushes the blocking valve 20 to move. The blocking valve 20 drives the moving piston plate 22 and the blocking block 23 to move synchronously, thereby opening the communication port between the pressure storage cylinder 19 and the hydraulic control cylinder 18. The hydraulic oil enters the pressure storage cylinder 19 to increase the pressure in the pressure storage cylinder 19. The hydraulic oil entering the hydraulic control cylinder 18 is injected into the control oil port 12 through the through hole 1 on the moving piston plate 22 to increase the pressure in the control oil port 12. After the pressure adjustment is completed, the hydraulic pump is closed. At this time, the moving piston plate 22 resets to block the inlet of the hydraulic control cylinder 18, and at the same time, the blocking block 23 blocks the opening between the pressure storage cylinder 19 and the hydraulic control cylinder 18 to complete the purpose of pressurizing the inside of the pressure storage cylinder 19. When the hydraulic oil is injected into the hydraulic control cylinder 18 again by the hydraulic pump, as Figure 5 shown, the blocking valve 20 opens and controls the displacement of the blocking block 23. At this time, the high-pressure hydraulic oil in the pressure storage cylinder 19 is quickly injected into the hydraulic control cylinder 18, thereby quickly increasing the pressure in the hydraulic control cylinder 18, and further quickly increasing the pressure of the hydraulic oil injected into the control oil port 12 to achieve the purpose of quickly adjusting the pressure.

[0030] Moreover, a fixed piston plate 24 is fixed in the middle of the hydraulic control cylinder 18. The fixed piston plate 24 is located on the side of the movable piston plate 22 close to the piston 1. The central shaft 21 is inserted into the fixed piston plate 24. An elastic member is installed between the end of the central shaft 21 and the fixed piston plate 24. A second through hole is provided on the fixed piston plate 24. The first through hole and the second through hole are arranged in a staggered manner. An electromagnet 25 corresponding to the movable piston plate 22 is installed on the fixed piston plate 24. The movable piston plate 22 is made of ferromagnetic metal. A hydraulic sensor 26 is installed in the inner cavity of the pressure storage cylinder 19. In order to improve the accuracy of regulating the pressure of the control oil port 12, it is necessary to increase the pressure in the pressure storage cylinder 19 to a preset value, so as to quickly inject the hydraulic oil with the preset pressure in the pressure storage cylinder 19 into the control oil port 12 when the blocking block 23 is opened. At this time, by controlling the electromagnet 25 to work, the electromagnet 25 generates magnetism to magnetically attract the movable piston plate 22, and the movable piston plate 22 abuts against 4. Since the first through hole and the second through hole are arranged in a staggered manner, at this time, the fixed piston plate 24 and the movable piston plate 22 block the inner cavity of the hydraulic control cylinder 18. At this time, the hydraulic oil entering from the input end of the hydraulic control cylinder 18 completely enters the pressure storage cylinder 19, and the pressure state of the hydraulic oil in the pressure storage cylinder 19 is detected by the hydraulic sensor 26. The pressure in the pressure storage cylinder 19 is adjusted by continuously injecting hydraulic oil through the operation of the oil pump, so as to achieve the purpose of automatically controlling the pressure of the hydraulic oil in the pressure storage cylinder 19. And when the pressure in the pressure storage cylinder 19 reaches the preset value, the electromagnet 25 is controlled to stop working. Under the action of the elastic member, the central shaft 21 is pushed to drive the movable piston plate 22 to reset. At the same time, the blocking block 23 blocks the connection between the pressure storage cylinder 19 and the hydraulic control cylinder 18 to seal the pressure storage cylinder 19.

[0031] In addition, a secondary pressure controller is also provided on the piston 1. The secondary pressure controller includes a detection module and a pressure regulating module. The detection module is respectively connected to the pressure regulating module and the hydraulic sensor 26 in a signal manner. The pressure regulating module is connected to the electromagnet 25 in a signal manner. When it is necessary to control the pressure of the hydraulic oil in the pressure storage cylinder 19 to increase to a preset value, the oil pump works to inject the hydraulic oil into the hydraulic control cylinder 18. The pressure regulating module controls the electromagnet 25 to work. The movable piston plate 22 fits with the fixed piston plate 24 to block the inner cavity of the hydraulic control cylinder 18. The hydraulic oil enters the pressure storage cylinder 19 to increase the pressure. The hydraulic sensor 26 sends the detected pressure value to the detection module. The detection module compares the pressure value with the pressure preset value (the pressure value that needs to increase the pressure in the pressure storage cylinder 19 is preset in the detection module). When it is judged that the pressure value reaches the pressure preset value, the pressure regulating module controls the electromagnet 25 to stop working. Under the action of the elastic member, the central shaft 21 is pushed to drive the movable piston plate 22 to reset. At the same time, the blocking block 23 blocks the connection between the pressure storage cylinder 19 and the hydraulic control cylinder 18 to seal the pressure storage cylinder 19.

[0032] In the present invention, unless otherwise clearly stipulated and defined, terms such as "installation", "connection", "linkage", "fixation", etc. shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection, or an integral body; it may be a mechanical connection, an electrical connection, or communication with each other; it may be directly connected, or indirectly connected through an intermediate medium, and it may be the internal communication of two components or the interaction relationship between two components, unless otherwise clearly defined. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0033] Obviously, the embodiments described above are only a part of the embodiments of the present invention, rather than all embodiments. The preferred embodiments of the present invention are given in the drawings, but do not limit the patent scope of the present invention. The present invention can be implemented in many different forms. On the contrary, the purpose of providing these embodiments is to make the understanding of the disclosed content of the present invention more thorough and comprehensive. Although the present invention has been described in detail with reference to the foregoing embodiments, for those skilled in the art, they can still modify the technical solutions described in the foregoing specific embodiments, or perform equivalent replacements for some of the technical features. Any equivalent structure directly or indirectly using the content of the specification and drawings of the present invention in other related technical fields is equally within the scope of the patent protection of the present invention.

Claims

1. A differential unidirectional overflow valve, characterized in that, Comprising: A valve body (4), in the middle of which an overflow valve core (7) is inserted. A radial hole one (15) is arranged through the middle of the overflow valve core (7). A pressure regulating screw (10) is arranged at the end of the valve body (4). A pressure regulating spring (9) is arranged between the pressure regulating screw (10) and the overflow valve core (7) in the valve body (4). A load oil port (14) is arranged in the middle of the valve body (4), and the load oil port (14) is communicated with the outer ring space of the overflow valve core (7); A valve seat (3), which is connected to the end of the valve body (4) away from the gland (11). The end of the overflow valve core (7) is inserted into the inner cavity of the valve seat (3), and the end of the overflow valve core (7) abuts against the end of the valve seat (3) through the valve core end face fixed by the outer ring. An oil inlet and outlet (13) is arranged on one side of the valve seat (3), and the oil inlet and outlet (13) is communicated with the outer ring space of the overflow valve core (7) in the valve seat (3); A check valve core (5), which is installed in the valve body (4) and sleeved on the outer ring of the overflow valve core (7). A circumferential oil inlet channel (16) is arranged on the end face of the valve seat (3) close to the pressure regulating screw (10), and the oil inlet channel (16) is communicated with the oil inlet and outlet (13). The end of the check valve core (5) abuts against the oil inlet channel (16) on the valve seat (3), and a check spring (6) is installed at the other end of the check valve core (5); The outer ring diameter of the corresponding end of the overflow valve core (7) and the valve seat (3) is D1, and the outer ring diameter of the corresponding end of the overflow valve core (7) and the valve body (4) is D2, and D2 is greater than D1.

2. The differential type one-way overflow valve according to claim 1, characterized in that, A piston sleeve (2) is inserted into the end of the valve seat (3) away from the valve body (4). The inner cavity of the piston sleeve (2) is communicated with the cavity in the valve body (4) that is communicated with the oil inlet and outlet (13). A piston (1) is installed in the piston sleeve (2), and the inner diameter of the piston sleeve (2) corresponding to the piston (1) is D3, and D3 is greater than D1.

3. The differential type one-way overflow valve according to claim 1, characterized in that, A gland (11) is sleeved on the outer circle of the pressure regulating screw (10), and the gland (11) is installed with the end of the overflow valve core (7).

4. A differential unidirectional overflow valve according to claim 1, characterized in that, A spring seat (8) is arranged between the end of the overflow valve core (7) and the pressure regulating spring (9). A radial hole two (17) communicated with the radial hole one (15) is arranged through the spring seat (8).

5. The differential type one-way overflow valve according to claim 1, characterized in that, The end face of the check valve core (5) adopts an inner taper angle for hard sealing with the oil inlet channel (16) on the valve seat (3).

6. The differential type one-way overflow valve according to claim 2, wherein, A piston (1) is installed in the middle of the piston sleeve (2), and a control oil port (12) is arranged through the middle of the piston (1).

7. A differential unidirectional overflow valve according to claim 6, characterized in that, A secondary pressure mechanism is arranged at the input end of the piston (1). The secondary pressure mechanism includes a hydraulic control cylinder (18) communicated with the control oil port (12) on the piston (1), a pressure storage cylinder (19) communicated with the inner cavity of the hydraulic control cylinder (18), and a hydraulic pressure gauge (27) is installed on the pressure storage cylinder (19).

8. The differential unidirectional overflow valve according to claim 7, wherein The middle part of the hydraulic control cylinder (18) is horizontally inserted with a central shaft (21). A central shaft (21) is provided at the end of the central shaft (21) close to the output end of the hydraulic control cylinder (18). The central shaft (21) abuts against the inner ring of the output end of the hydraulic control cylinder (18). A moving piston plate (22) that is slidably connected to the inner wall of the hydraulic control cylinder (18) is fixed in the middle of the central shaft (21). A blocking block (23) placed at the communication part of the pressure storage cylinder (19) and the hydraulic control cylinder (18) is fixed on the moving piston plate (22). A through hole one is formed on the moving piston plate (22).

9. The differential unidirectional overflow valve according to claim 8, wherein, A fixed piston plate (24) is fixed in the middle of the hydraulic control cylinder (18). The fixed piston plate (24) is located on the side of the moving piston plate (22) close to the piston (1). The central shaft (21) is inserted into the fixed piston plate (24). An elastic member is installed between the end of the central shaft (21) and the fixed piston plate (24). A through hole two is formed on the fixed piston plate (24). The through hole one and the through hole two are arranged in a staggered manner. An electromagnet (25) corresponding to the moving piston plate (22) is installed on the fixed piston plate (24). The moving piston plate (22) is made of ferromagnetic metal. A hydraulic sensor (26) is installed in the inner cavity of the pressure storage cylinder (19).

10. A differential unidirectional overflow valve according to claim 9, characterized in that, A secondary pressure controller is further provided on the piston (1). The secondary pressure controller includes a detection module and a pressure regulating module. The detection module is respectively in signal connection with the pressure regulating module and the hydraulic sensor (26). The pressure regulating module is in signal connection with the electromagnet (25).

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