A direct-acting, high-pressure, high-flow three-way proportional pressure reducing valve

Abstract

This invention provides a direct-acting, high-pressure, high-flow-rate three-way proportional pressure reducing valve, comprising a valve sleeve, a valve core, a proportional electromagnet, and a push rod. The valve core is installed inside the valve sleeve and can slide within the valve sleeve. One end of the valve core contacts the end face of the push rod, which is installed inside the proportional electromagnet. The proportional electromagnet is connected to the valve sleeve. The valve sleeve has an inlet port P and an outlet port T. The valve core has a first annular groove and a second annular groove. The areas between the two ends of the valve core and the valve sleeve form a first control cavity and a second control cavity. This invention changes the pressure at the working port A by altering the excitation current, thereby achieving proportional control of the output pressure of the proportional pressure reducing valve. The diameters of the inlet and outlet ports are equal to the large-diameter end face diameter of the valve core. By increasing the large-diameter end face diameter of the valve core, the flow rate at the inlet or outlet port can be increased, thus achieving high-flow-rate control and decoupling control of the output pressure and flow rate of the three-way proportional pressure reducing valve.

Description

Technical Field

[0001] This invention relates to the field of pressure reducing valve technology, and in particular to a direct-acting, high-pressure, high-flow three-way proportional pressure reducing valve. Background Technology

[0002] The direct-acting three-way proportional pressure reducing valve is mainly composed of a proportional electromagnet, a valve core, and a valve sleeve. It is mainly used to convert the input excitation current into a proportional control pressure output. It is one of the core control components for realizing electro-hydraulic conversion and has a wide range of applications in fields such as engineering machinery and automobiles.

[0003] Most existing direct-acting proportional pressure reducing valves on the market directly feed back the output pressure, which means they cannot simultaneously increase output flow and output pressure, severely limiting the performance improvement of three-way proportional pressure reducing valves. Summary of the Invention

[0004] To address the shortcomings of existing technologies, this invention provides a direct-acting, high-pressure, high-flow three-way proportional pressure reducing valve.

[0005] The technical solution of the present invention is as follows: a direct-acting high-pressure, high-flow three-way proportional pressure reducing valve, comprising a valve sleeve, a valve core, a proportional electromagnet, and a push rod. The valve core is installed inside the valve sleeve and can slide within the valve sleeve. One end of the valve core is in contact with the end face of the push rod. The push rod is installed inside the proportional electromagnet, which is connected to the valve sleeve. The valve sleeve is provided with an oil inlet P and an oil return port T. The valve core is provided with a first annular groove and a second annular groove. The annular groove forms a throttling orifice with the oil inlet P and the oil return port T. The areas between the two ends of the valve core and the valve sleeve form a first control cavity and a second control cavity.

[0006] Preferably, the valve sleeve is provided with a stepped through hole that extends through both ends, and the valve core is installed in the stepped through hole, with the end away from the proportional electromagnet serving as the working oil port A.

[0007] Preferably, the return port T is located on the valve sleeve near the proportional electromagnet, the inlet port P is located on the valve sleeve away from the proportional electromagnet, the first control chamber is located away from the proportional electromagnet, and the second control chamber is located near the proportional electromagnet.

[0008] Preferably, the valve sleeve is further provided with multiple annular grooves, and a corresponding sealing ring is fitted inside the annular grooves.

[0009] Preferably, the valve sleeve is also provided with a plurality of first connection holes, and the two ends of each first connection hole are respectively connected to the corresponding oil return port T and the internal cavity of the proportional electromagnet.

[0010] Preferably, the valve core has a blind hole along its length, and the valve core at the first control cavity position also has a first through hole along the vertical direction, the first through hole communicating with the first annular groove, and the valve core at the second control cavity position also has a second through hole along the vertical direction, the second through hole communicating with the second annular groove.

[0011] Preferably, the valve core at the first annular groove position is provided with multiple third through holes, and the valve core at the second annular groove position is provided with multiple fourth through holes, and the third through holes and fourth through holes are all connected to blind holes.

[0012] Preferably, a return spring is also fitted on one end of the valve core near the push rod. The other end of the return spring abuts against the end of the valve core, and the other end abuts against the T-groove of the positioning sleeve fitted on the valve core. The positioning sleeve can abut against the stepped groove inside the valve sleeve.

[0013] Preferably, the valve sleeve and the proportional electromagnet are connected by rolling.

[0014] Preferably, a sealing ring is also provided at the connection between the valve sleeve and the proportional electromagnet.

[0015] The beneficial effects of this invention are as follows:

[0016] 1. This invention changes the pressure at the working port A by changing the excitation current, thereby achieving proportional control of the output pressure of the proportional pressure reducing valve.

[0017] 2. The diameter of the oil inlet P and the oil return port of this invention is the large diameter end face diameter D of the valve core. By increasing the large diameter end face diameter D of the valve core, the flow rate at the oil inlet P or the oil return port T can be increased, thereby achieving high flow rate control. Since the diameter D and the diameter d are not related to each other, the output pressure and flow rate of the three-way proportional pressure reducing valve can be decoupled and controlled. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the pressure reducing valve of the present invention;

[0019] Figure 2 This is a cross-sectional schematic diagram of the pressure reducing valve of the present invention;

[0020] Figure 3 This is a schematic diagram of the valve sleeve of the present invention;

[0021] Figure 4 This is a schematic diagram of the structure of the present invention after the valve sleeve is concealed;

[0022] Figure 5 This is a schematic diagram of the valve core structure of the present invention;

[0023] Figure 6 This is a partially enlarged view of the valve core of the present invention;

[0024] Figure 7 This is a partial enlarged view of the positioning sleeve and the return spring of the present invention;

[0025] Figure 8 This is a schematic diagram of the working position of the pressure reducing valve of the present invention;

[0026] In the diagram, 1-valve sleeve, 2-valve core, 3-proportional electromagnet, 4-push rod;

[0027] 10-First control chamber; 11-Second control chamber; 12-Oil inlet P; 13-Oil return port T; 14-Stepped through hole; 15-Working oil port A; 16-Annular groove; 17-Sealing ring; 18-First connecting hole;

[0028] 21-Reset spring, 22-Positioning sleeve, 23-First annular groove, 24-Blind hole, 25-First through hole, 26-Second through hole, 27-Third through hole, 28-Fourth through hole, 29-Second annular groove. Detailed Implementation

[0029] The specific embodiments of the present invention will be further described below with reference to the accompanying drawings:

[0030] like Figure 1 and 2 As shown, this embodiment provides a direct-acting high-pressure, high-flow three-way proportional pressure reducing valve, including a valve sleeve 1, a valve core 2, a proportional electromagnet 3, and a push rod 4. The valve core 2 is installed inside the valve sleeve 1 and can slide inside the valve sleeve 1. One end of the valve core 2 is in contact with the end face of the push rod 4. The push rod 4 is installed inside the proportional electromagnet 3. The proportional electromagnet 3 is connected to the valve sleeve 1. The valve sleeve 1 is provided with multiple oil inlets P12 and multiple oil return ports T13. The valve core 2 is provided with a first annular groove 23 and a second annular groove 29. The first annular groove 23 and the second annular groove 29 form a throttling orifice with the oil inlets P12 and the oil return ports T13. The area between the two ends of the valve core 2 and the valve sleeve 1 forms a first control cavity 10 and a second control cavity 11.

[0031] As a preferred embodiment, such as Figure 3 As shown, the valve sleeve 1 is provided with a stepped through hole 14 that runs through both ends. The valve core 2 is installed in the stepped through hole 14, and the end away from the proportional electromagnet 3 serves as the working oil port A15.

[0032] As a preferred embodiment, such as Figure 2 , 3As shown, the return port T13 is located on the valve sleeve 1 near the proportional electromagnet 3, the inlet port P12 is located on the valve sleeve 1 away from the proportional electromagnet 3, the first control chamber 10 is located away from the proportional electromagnet 3, and the second control chamber 11 is located near the proportional electromagnet 3.

[0033] As a preferred embodiment, such as Figure 2 , 3 As shown, the valve sleeve 1 is also provided with a plurality of annular grooves 16, and a corresponding sealing ring 17 is fitted inside the annular grooves 16.

[0034] As a preferred embodiment, such as Figure 2 , 3 As shown, the valve sleeve 1 is also provided with a plurality of first connection holes 18, and the two ends of each first connection hole 18 are respectively connected to the corresponding oil return port T13 and the internal cavity of the proportional electromagnet 3.

[0035] As a preferred embodiment, such as Figure 2 , 4 As shown in Figure 5, the valve core 2 has a blind hole 24 along its length. The valve core 2 at the position of the first control cavity 10 also has a first through hole 25 along the vertical direction. The first through hole 25 communicates with the first annular groove 23. The valve core 2 at the position of the second control cavity 11 also has a second through hole 26 along the vertical direction. The second through hole 26 communicates with the second annular groove 29.

[0036] As a preferred embodiment, such as Figure 2 , 4 As shown in Figure 5, the valve core 2 at the position of the first annular groove 23 is provided with multiple third through holes 27, and the valve core 2 at the position of the second annular groove 29 is provided with multiple fourth through holes 28. The third through holes 27 and the fourth through holes 28 are all connected to the blind hole 24.

[0037] As a preferred embodiment, such as Figure 2 , 6 As shown in Figure 7, a return spring 21 is also sleeved on one end of the valve core 2 near the push rod 4. The other end of the return spring 21 abuts against the end of the valve core 2, and the other end abuts against the T-shaped groove of the positioning sleeve 22 sleeved on the valve core 2. The positioning sleeve 22 can abut against the stepped groove inside the valve sleeve 1.

[0038] As a preferred embodiment, such as Figure 1 , 2 As shown, the valve sleeve 1 and the proportional electromagnet 3 are connected by rolling.

[0039] As a preferred embodiment, such as Figure 1 , 2 As shown, a sealing ring 17 is also fitted at the connection between the valve sleeve 1 and the proportional electromagnet 3.

[0040] In a preferred embodiment, the diameter of the first control cavity 10 and the second control cavity 11 is D, and the diameter of the blind hole 24 is d.

[0041] Working principle:

[0042] When the proportional electromagnet 3 is not energized, the valve core 2 is located on the far right under the action of the return spring 21. The return port T13 is connected to the working port A15 through the second annular groove 29, the fourth through hole 28, and the blind hole 24. The first control cavity 10 is connected to the working port A15 through the first through hole 25, the first annular groove 23, the third through hole 27, and the blind hole 24. The second control cavity 11 is connected to the working port A15 through the second through hole 26, the second annular groove 29, the fourth through hole 28, and the blind hole 24. Since the large end face diameter and the small end face diameter of the first control cavity 10 and the second control cavity 11 are equal, the forces on both sides of the valve core 2 at the first control cavity 10 and the second control cavity 11 cancel each other out. At this time, the pressure at the working port A15 is the minimum, which is equal to the pressure at the return port T13.

[0043] When a proportional electromagnet 3 receives an input current, it generates an electromagnetic force. Under the action of this electromagnetic force, the valve core 2 overcomes the spring force of the return spring 21 and moves to the left. The first oil passage of the working oil port A15 is connected to the oil inlet P12 through the blind hole 24 and the third through hole 27. The second oil passage of the working oil port A15 is connected to the first control cavity 10 through the blind hole 24, the third through hole 27, and the first through hole 25. The third oil passage of the working oil port A15 is connected to the second control cavity 11 through the blind hole 24, the fourth through hole 28, and the second through hole 26. The return oil port T13 is in a closed state. At this time, the pressure in the working port A15, the second control chamber 11, and the first control chamber 10 will increase under the action of the high-pressure inlet P12. When the pressure increases to a certain level, the valve core 2 moves to the right, and the return port T13 opens. At this time, the pressure in the working port A15, the second control chamber 11, and the first control chamber 10 will be partially relieved at the return port T13. By continuously repeating the above process, the spring force of the reset spring 21, the electromagnetic force of the proportional electromagnet 3, the feedback fluid pressure at the working port A15, the feedback fluid pressure at the second control chamber 11, and the feedback fluid pressure at the first control chamber 10 will eventually reach a new equilibrium at their new positions. Figure 8 As shown.

[0044] At this point, the force balance equation for valve core 2 is:

[0045]

[0046] In the formula, F s The spring force F is the return spring 21. e p is the electromagnetic force output by proportional electromagnet 3. A The pressure at the working oil port A15 is denoted by D; the diameter of the large diameter end face of valve core 2 is denoted by d; and the diameter of the small diameter end face of valve core 2 is denoted by d.

[0047] The electromagnetic force F generated by the proportional electromagnet 3 is described above. e The approximate relationship with the excitation current i is:

[0048] F e =k*i;

[0049] In the formula, k is the proportionality coefficient between the output electromagnetic force of the proportional electromagnet 3 and the excitation current, and its value is positive; i is the excitation current in the proportional electromagnet 3.

[0050] The spring force F of the reset spring 21 s for:

[0051] F s =k s *Δx2;

[0052] In the formula, k s Δx2 represents the spring stiffness of the return spring 21; Δx2 represents the compression of the return spring 21.

[0053] Therefore, the pressure at the working oil port A15 can be expressed as:

[0054]

[0055] Since the structures of valve core 2 and valve sleeve 1 are fixed, the major diameter D and minor diameter d of valve core 2 are constants. The compression Δx2 and stiffness k of return spring 21 are also constants. s The force is very small, so the spring force of the return spring 21 can be approximated as constant.

[0056] Therefore, as the excitation current i of the proportional electromagnet 3 continuously increases, the pressure p at the working oil port A15 increases. A The pressure is increased proportionally, thereby achieving proportional control of the output pressure of the proportional pressure reducing valve.

[0057] As can be seen from the above, the pressure p at the working oil port A15 is... A The pressure p at the working port A15 is inversely proportional to the small diameter end face diameter d of valve core 2. By reducing the small diameter end face diameter d of valve core 2, the pressure p can be increased. A This achieves high-voltage control. From Figure 2 as well as Figure 8As can be seen, the diameters at the inlet and return throttling ports are equal to the large diameter end face diameter D of valve core 2. By increasing the large diameter end face diameter D of valve core 2, the flow rate at the inlet port P12 or the return port T13 can be increased, thereby achieving high flow rate control. Since diameter D and diameter d are independent of each other, decoupled control of the output pressure and flow rate of the three-way proportional pressure reducing valve can be achieved.

[0058] The embodiments and descriptions above are merely illustrative of the principles and preferred embodiments of the present invention. Various changes and modifications may be made to the present invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the present invention as claimed.

Claims

1. A direct-acting, high-pressure, high-flow-rate three-way proportional pressure reducing valve, characterized in that: The system includes a valve sleeve (1), a valve core (2), a proportional electromagnet (3), and a push rod (4). The valve core (2) is installed inside the valve sleeve (1) and can slide inside the valve sleeve (1). One end of the valve core (2) is in contact with the end face of the push rod (4). The push rod (4) is installed inside the proportional electromagnet (3). The proportional electromagnet (3) is connected to the valve sleeve (1). The valve sleeve (1) is provided with multiple oil inlets P (12) and multiple oil return ports T (13). The valve core (2) is provided with a first annular groove (23) and a second annular groove (29). The first annular groove (23) and the second annular groove (29) form a throttling port between the oil inlet P (12) and the oil return port T (13). The area between the two ends of the valve core (2) and the valve sleeve (1) forms a first control cavity (10) and a second control cavity (11). The valve core (2) is provided with a blind hole (24) along its length. The valve core (2) at the position of the first control cavity (10) is also provided with a first through hole (25) along the vertical direction. The first through hole (25) is connected to the first annular groove (23). The valve core (2) at the position of the second control cavity (11) is also provided with a second through hole (26) along the vertical direction. The second through hole (26) is connected to the second annular groove (29). The valve core (2) at the first annular groove (23) is provided with multiple third through holes (27), and the valve core (2) at the second annular groove (29) is provided with multiple fourth through holes (28). The third through holes (27) and the fourth through holes (28) are connected to the blind hole (24). The valve sleeve (1) is provided with a stepped through hole (14) that runs through both ends. The valve core (2) is installed in the stepped through hole (14) and the end away from the proportional electromagnet (3) serves as the working oil port A (15). The return port T (13) is located on the valve sleeve (1) near the end of the proportional electromagnet (3), and the inlet port P (12) is located on the valve sleeve (1) away from the end of the proportional electromagnet (3). The first control cavity (10) is located at the end away from the proportional electromagnet (3), and the second control cavity (11) is located at the end close to the proportional electromagnet (3). The diameter of the first control cavity (10) and the second control cavity (11) is D, and the diameter of the blind hole (24) is d; A return spring (21) is also fitted on one end of the valve core (2) near the push rod (4). The other end of the return spring (21) abuts against the end of the valve core (2) and the other end abuts against the T-groove of the positioning sleeve (22) fitted on the valve core (2). The positioning sleeve (22) can abut against the stepped groove inside the valve sleeve (1).

2. The direct-acting high-pressure, high-flow three-way proportional pressure reducing valve according to claim 1, characterized in that: The valve sleeve (1) is also provided with a plurality of annular grooves (16), and a corresponding sealing ring (17) is fitted inside the annular grooves (16).

3. The direct-acting high-pressure, high-flow three-way proportional pressure reducing valve according to claim 2, characterized in that: The valve sleeve (1) is also provided with a plurality of first connection holes (18), and the two ends of each first connection hole (18) are respectively connected to the corresponding oil return port T (13) and the internal cavity of the proportional electromagnet (3).

4. The direct-acting high-pressure, high-flow three-way proportional pressure reducing valve according to claim 1, characterized in that: The valve sleeve (1) and the proportional electromagnet (3) are connected by rolling.

5. A direct-acting high-pressure, high-flow three-way proportional pressure reducing valve according to claim 4, characterized in that: A sealing ring (17) is also provided at the connection between the valve sleeve (1) and the proportional electromagnet (3).

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