Bidirectional two-way hydraulic control one-way valve

Abstract

The utility model relates to the technical field of hydraulic control, and particularly discloses a two-way two-way hydraulic control one-way valve which comprises a valve seat, a first valve body, a second valve body and a valve element, the first valve body is connected to the valve seat, the second valve body is connected to the first valve body, and a first oil inlet cavity and a second oil inlet cavity are formed in the first valve body. A first oil inlet and a second oil inlet are formed in the first valve body, a first oil return cavity, a second oil return cavity and a control oil cavity are formed in the second valve body, an oil return opening and a control oil opening are formed in the second valve body, the valve element is arranged in the first valve body, and a plugging seat and a ball seal seat are arranged in the first oil return cavity. And a second reset spring is arranged between the plugging seat and the first valve body. Control hydraulic oil is introduced through the control oil port to push the ball seal seat and the valve element to move to relieve sealing, the first oil inlet and the second oil inlet are communicated with the oil return port, the first oil inlet and the second oil inlet lose pressure, response is rapid and reliable, simultaneous control is achieved, and harm caused by asynchronous control is eliminated.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic control technology, and in particular to a bidirectional two-way hydraulic control check valve. Background Technology

[0002] In large logistics vehicles or engineering vehicles, multi-axle steering is often required to ensure vehicle flexibility. Currently, centering hydraulic cylinders are commonly used to achieve wheel steering and centering, ensuring the stability of the vehicle at high speeds.

[0003] Chinese invention patent application (publication number CN102910202A) discloses an automatic steering wheel centering unit, a vehicle including the unit, and an automatic centering method. The automatic centering unit also includes a bidirectional hydraulic lock disposed in an electro-hydraulic proportional valve group. When the steering cylinder of the rear axle reaches the neutral position, the electro-hydraulic proportional valve group remains de-energized, and the rear axle cylinder is locked by the bidirectional hydraulic lock to ensure driving safety. This technical solution controls the steering cylinder through two hydraulic locks, requiring the two hydraulic locks to maintain a high degree of synchronization to maintain the stability of the steering system. However, in actual operation, the two hydraulic locks often cannot achieve synchronization within the specified range, thus affecting the stability of vehicle handling and posing a significant safety hazard.

[0004] Therefore, it is necessary to propose an improved bidirectional two-way hydraulic control check valve to overcome the shortcomings of the existing technology. Utility Model Content

[0005] The purpose of this invention is to solve the problems in the prior art and provide a bidirectional, two-way hydraulic control check valve.

[0006] The technical solution of this utility model is:

[0007] A bidirectional, two-way hydraulically controlled check valve includes a valve seat, a first valve body, a second valve body, and a valve core. One end of the first valve body is threaded onto the valve seat, and the second valve body is threaded onto the other end of the first valve body. The first valve body has a first inlet chamber and a second inlet chamber, and a first inlet port and a second inlet port are provided on the first valve body. The first inlet port communicates with the first inlet chamber, and the second inlet port communicates with the second inlet chamber. The second valve body has a first return chamber, a second return chamber, and a control chamber, and a return port is provided on the second valve body. A control port is provided at the end of the second valve body, and the return port communicates with the second return chamber. The valve core passes through the first inlet chamber and the second inlet chamber in sequence and extends into the first return chamber. A first return spring is provided between the valve core and the valve seat. A sealing seat is provided in the first return chamber, and a ball seal is provided at the end of the sealing seat facing away from the valve core. A second return spring is provided between the sealing seat and the first valve body. A plunger is slidably provided in the control chamber, and one end of the plunger extends into the second return chamber.

[0008] Preferably, the valve core includes a sealing section, a contraction section and a guide section. The sealing section has a sealing cone surface on its outer circumference, the guide section has an oil outlet hole, and the valve core has a through oil passage inside, with the oil outlet hole communicating with the oil passage.

[0009] Preferably, the inner diameter of the first oil inlet chamber is larger than the inner diameter of the second oil inlet chamber, and the first oil inlet chamber and the second oil inlet chamber form a first sealing step surface, with sharp corners retained at the edges of the first sealing step surface.

[0010] Preferably, the inner diameter of the first oil return chamber is larger than the inner diameter of the second oil return chamber, and the first oil return chamber and the second oil return chamber form a second sealing step surface, with sharp corners retained at the edges of the second sealing step surface.

[0011] Preferably, the sealing seat is fitted with a clearance fit to the inner wall of the first return oil chamber.

[0012] Preferably, the oil port threaded connection has a limit stop.

[0013] Preferably, the valve seat is provided with an external thread for connection.

[0014] Preferably, a first sealing ring is provided between the valve core and the inner wall of the second oil inlet chamber.

[0015] Preferably, a number of second sealing rings are provided between the plunger and the inner wall of the control oil chamber.

[0016] Preferably, a plurality of first grooves are provided at intervals on the outer wall of the first valve body, and a plurality of second grooves are provided at intervals on the outer wall of the second valve body.

[0017] Compared with the prior art, the beneficial effects of this utility model are:

[0018] This invention achieves a seal between the valve core and the first sealing step surface through the pre-tightening force of the first return spring on the valve core, preventing the first and second oil inlets from communicating. Similarly, the pre-tightening force of the second return spring on the sealing seat achieves a seal between the ball seal seat and the second sealing step surface, preventing both the first and second oil inlets from communicating with the return port. The first and second oil inlets can function as two separate high-pressure control oil circuits. By connecting control hydraulic oil through the control port, the plunger pushes the ball seal seat and valve core to move, releasing the seal. Simultaneously, the first and second oil inlets communicate with the return port, resulting in simultaneous pressure loss. This design provides a fast and reliable response, enabling simultaneous control with high synchronization, eliminating the hazards caused by asynchronous control. The overall structure is compact, occupies little space, eliminates the need for two control systems, saves costs, and offers high safety. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the structure of this utility model;

[0020] Figure 2This is a schematic diagram of the valve core structure of this utility model.

[0021] The components are as follows: 1. Valve seat; 11. Connecting external thread; 2. First valve body; 21. First oil inlet chamber; 22. Second oil inlet chamber; 23. First oil inlet; 24. Second oil inlet; 25. First sealing step surface; 26. First groove; 27. First return spring; 3. Second valve body; 31. First return oil chamber; 32. Second return oil chamber; 33. Control oil chamber; 34. Return oil port; 35. Control oil port; 36. Second sealing step surface; 37. Second groove; 38. Second return spring; 4. Valve core; 41. Sealing section; 42. Contraction section; 43. Guide section; 44. Sealing cone surface; 45. Oil outlet; 46. Oil passage; 5. Sealing seat; 6. Ball seal seat; 7. Plunger; 8. Limiting block; 9. First sealing ring; 10. Second sealing ring. Detailed Implementation

[0022] To make the technical means, technical features, utility model purpose and technical effects of this utility model easier to understand, the present utility model will be further described below with reference to specific illustrations.

[0023] like Figure 1 and Figure 2 As shown, a bidirectional, two-way hydraulically controlled check valve includes a valve seat 1, a first valve body 2, a second valve body 3, a valve core 4, a sealing seat 5, a plunger 7, a limit stop 8, a first return spring 27, and a second return spring 38. The valve seat 1, the first valve body 2, and the second valve body 3 are installed sequentially via a threaded connection. Specifically, one end of the first valve body 2 is threaded onto the valve seat 1, and the second valve body 3 is threaded onto the other end of the first valve body 2. This threaded, detachable connection facilitates processing and assembly. The valve core 4 is slidably installed within the first valve body 2 and extends into the second valve body 3 to achieve a first-stage seal. The sealing seat 5 slides... A ball seal seat 6 is installed inside the second valve body 3 at the end of the sealing seat 5 facing away from the valve core 4 to achieve a second-stage seal. A plunger 7 is slidably installed inside the second valve body 3, and the ball seal seat 6, the sealing seat 5, and the valve core 4 can be moved to release the seal by sliding the plunger 7. A limit stop 8 is threaded to the end of the first valve body 2 to limit the plunger 7. A first return spring 27 is installed between the valve seat 1 and the valve core 4 to maintain the sealing effect of the valve core 4. A second return spring 38 is installed between the first valve body 2 and the sealing seat 5 to maintain the seal of the ball seal seat 6.

[0024] like Figure 1 and Figure 2As shown, the valve core 4 includes a sealing section 41, a contraction section 42 and a guide section 43 that are integrally machined. A sealing cone surface 44 is machined on the outer circumference of the sealing section 41. Oil outlet holes 45 are uniformly distributed on the end circumference of the guide section 43. An oil passage 46 is machined inside the valve core 4 that runs through its axis. The oil outlet holes 45 are connected to the oil passage 46.

[0025] like Figure 1 and Figure 2 As shown, a first oil inlet chamber 21 and a second oil inlet chamber 22 are machined inside the first valve body 2. A first oil inlet port 23 and a second oil inlet port 24 are machined on the first valve body 2. The first oil inlet port 23 is connected to the first oil inlet chamber 21, and the second oil inlet port 24 is connected to the second oil inlet chamber 22. The inner diameter of the first oil inlet chamber 21 is larger than the inner diameter of the second oil inlet chamber 22, so that a first sealing step surface 25 is formed between the first oil inlet chamber 21 and the second oil inlet chamber 22. During machining, the sharp corner of the edge of the first sealing step surface 25 transitioning from the first oil inlet chamber 21 to the second oil inlet chamber 22 is retained. The sealing section 41 of the valve core 4 is located in the first oil inlet chamber 21. Under the action of the first return spring 27, the sealing cone surface 44 of the sealing section 41 of the valve core 4 cooperates with the sharp corner of the first sealing step surface 25 to achieve a line seal, so that the first oil inlet port 23 and the second oil inlet port 24 are not connected, so that the first oil inlet port 23 and the second oil inlet port 24 can be used as two separate high-pressure oil circuits.

[0026] The contraction section 42 of the valve core 4 is located inside the second oil inlet chamber 22. The diameter of the contraction section 42 is smaller than the inner diameter of the second oil inlet chamber 22, which facilitates the flow of hydraulic oil in the second oil inlet 24. The guide section 43 of the valve core 4 is located inside the second oil inlet chamber 22 to guide the sliding of the valve core 4. The end of the guide section 43 of the valve core 4 extends through the second oil inlet chamber 22 into the interior of the second valve body 3. A first sealing ring 9 is installed between the guide section 43 of the valve core 4 and the inner wall of the second oil inlet chamber 22 to prevent hydraulic oil in the second oil inlet 24 from leaking from the valve core 4 and the second oil inlet chamber 22 into the second valve body 3. The first sealing ring 9 is an O-ring.

[0027] like Figure 1As shown, a first return oil chamber 31, a second return oil chamber 32, and a control oil chamber 33 are machined inside the second valve body 3. A return oil port 34 is machined on the second valve body 3, connecting to the second return oil chamber 32. The inner diameter of the first return oil chamber 31 is larger than the inner diameter of the second return oil chamber 32, forming a second sealing step surface 36 between the first and second return oil chambers 31 and 32. During machining, the sharp corner of the edge of the second sealing step surface 36 transitioning from the first return oil chamber 31 to the second return oil chamber 32 is retained. The sealing seat 5 is fitted with a clearance fit inside the first return oil chamber 31. Under the action of the second return spring 38, the sealing seat 5 drives the ball seal seat 6 to engage with the sharp corner of the second sealing step surface 36 to achieve a line seal, ensuring that neither the first oil inlet 23 nor the second oil inlet 24 is connected to the return oil port 34. The second valve body 3 has a control port 35 machined at its end. A limit stop 8 is threaded into the control port 35, which can limit the plunger 7 and connect to the external control oil circuit. The plunger 7 is located in the control oil chamber 33 and can slide in the control oil chamber 33 under the action of the control hydraulic oil. The end of the plunger 7 extends towards the ball seal seat 6 towards the valve core 4. The sliding of the plunger 7 can push the ball seal seat 6, the sealing seat 5 and the valve core 4 to overcome the action of the second return spring 38 and the first return spring 27 respectively, and release the two-stage seal, so that the first oil inlet 23 and the second oil inlet 24 are simultaneously connected to the return oil port 34. Several second sealing rings 10 are installed between the plunger 7 and the inner wall of the control oil chamber 33 to prevent internal leakage. The second sealing rings 10 are O-rings.

[0028] like Figure 1 As shown, an external thread 11 is machined on the valve seat 1 to realize the installation connection of the valve seat 1. Several first grooves 26 are machined on the outer circumference of the first valve body 2, and several second grooves 37 are machined on the outer circumference of the second valve body 3. O-rings are installed in both the first grooves 26 and the second grooves 37 to achieve sealing after the first valve body 2 and the second valve body 3 are installed, and to prevent internal leakage.

[0029] When in use, when the control oil port 35 is not connected to the control hydraulic oil, under the action of the first return spring 27, the sealing cone surface 44 of the sealing section 41 of the valve core 4 seals with the sharp corner of the first sealing step surface 25, so that the first oil inlet 23 and the second oil inlet 24 are not connected to each other. Under the action of the second return spring 38, the sealing seat 5 drives the ball seal seat 6 to seal with the sharp corner of the second sealing step surface 36, so that neither the first oil inlet 23 nor the second oil inlet 24 is connected to the return oil port 34. The first oil inlet 23 and the second oil inlet 24 work as separate high-pressure control oil circuits.

[0030] When the control port 35 is connected to the control hydraulic oil, the plunger 7 slides under the action of the control hydraulic oil, pushing the ball seal seat 6 and the valve core 4 to move against the preload of the second return spring 38 and the first return spring 27. At the same time, the sealing effect between the ball seal seat 6 and the second sealing step surface 36, and between the sealing cone surface 44 of the valve core 4 and the first sealing step surface 25 is released, so that the first oil inlet 23 and the second oil inlet 24 are connected to the return oil port 34 at the same time. The high pressure oil circuits of the first oil inlet 23 and the second oil inlet 24 are depressurized at the same time, realizing synchronous control. The response speed is fast, the synchronization is high, and the safety of use is high.

[0031] The above description is merely a preferred embodiment of this utility model and is not intended to limit the scope of this utility model. All equivalent changes and modifications made in accordance with the scope of the claims of this utility model should fall within the technical scope of this utility model.

Claims

1. A bidirectional two-way pilot operated check valve, characterized by: The valve comprises a valve seat (1), a first valve body (2), a second valve body (3) and a valve core (4), one end of the first valve body (2) is threadedly connected to the valve seat (1), the second valve body (3) is threadedly connected to the other end of the first valve body (2), the first valve body (2) is provided with a first oil inlet cavity (21) and a second oil inlet cavity (22), the first valve body (2) is provided with a first oil inlet port (23) and a second oil inlet port (24), the first oil inlet port (23) is communicated with the first oil inlet cavity (21), the second oil inlet port (24) is communicated with the second oil inlet cavity (22), the second valve body (3) is provided with a first oil return cavity (31), a second oil return cavity (32) and a control oil cavity (33), the second valve body (3) is provided with an oil return port (34), the end of the second valve body (3) is provided with a control oil port (35), the oil return port (34) is communicated with the second oil return cavity (32), the valve core (4) extends into the first oil return cavity (31) through the first oil inlet cavity (21) and the second oil inlet cavity (22) in sequence, the first reset spring (27) is arranged between the valve core (4) and the valve seat (1), the first oil return cavity (31) is provided with a blocking seat (5), the end of the blocking seat (5) away from the valve core (4) is provided with a ball sealing seat (6), the second reset spring (38) is arranged between the blocking seat (5) and the first valve body (2), the plunger (7) is slidably arranged in the control oil cavity (33), one end of the plunger (7) extends into the second oil return cavity (32).

2. The bidirectional two-way pilot operated check valve of claim 1, wherein: The valve core (4) comprises a sealing section (41), a contraction section (42) and a guide section (43), the sealing section (41) is provided with a sealing taper surface (44) on the outer circumference, the guide section (43) is provided with an oil outlet hole (45), the valve core (4) is internally provided with a through oil channel (46), the oil outlet hole (45) is communicated with the oil channel (46).

3. The bidirectional two-way pilot operated check valve of claim 1, wherein: The inner diameter of the first oil inlet cavity (21) is larger than the inner diameter of the second oil inlet cavity (22), a first sealing step surface (25) is formed between the first oil inlet cavity (21) and the second oil inlet cavity (22), and the edge of the first sealing step surface (25) retains an acute angle.

4. The bidirectional two-way pilot operated check valve of claim 1, wherein: The inner diameter of the first oil return cavity (31) is larger than the inner diameter of the second oil return cavity (32), a second sealing step surface (36) is formed between the first oil return cavity (31) and the second oil return cavity (32), and the edge of the second sealing step surface (36) retains an acute angle.

5. The bidirectional two-way pilot operated check valve of claim 1, wherein: The blocking seat (5) is gap-fitted with the inner side wall of the first oil return cavity (31).

6. The bidirectional two-way pilot operated check valve of claim 1, wherein: The control oil port (35) is threadedly connected with a limiting block (8).

7. The bidirectional two-way pilot operated check valve of claim 1, wherein: The valve seat (1) is provided with a connecting external thread (11).

8. The bidirectional two-way pilot operated check valve of claim 1, wherein: The valve core (4) is provided with a first sealing ring (9) between the inner side wall of the second oil inlet cavity (22).

9. The bidirectional two-way pilot operated check valve of claim 1, wherein: The plunger (7) is provided with a plurality of second sealing rings (10) between the inner side wall of the control oil cavity (33).

10. The bidirectional two-way pilot operated check valve of claim 1, wherein: A plurality of first grooves (26) are arranged on the outer side wall of the first valve body (2) at intervals, and a plurality of second grooves (37) are arranged on the outer side wall of the second valve body (3) at intervals.

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