A pilot proportional pressure reducing valve with detachable spring seat

Abstract

The utility model relates to pilot proportional pressure reducing valve technical field discloses a pilot proportional pressure reducing valve of detachable spring seat, including shell, valve core, spring seat, valve core spring, hole steel wire baffle ring, steel ball seat, steel ball and electromagnetic control assembly, the electromagnetic control assembly contains coil framework, enameled wire, armature and gap sleeve, the valve core passes through displacement control P mouth to A mouth's oil circuit opening degree, spring seat adopts clearance fit with valve sleeve, and the cooperation clearance is 0.02 0.05mm, and is fixed by the hole steel wire baffle ring of axial installation limit, the hole steel wire baffle ring is embedded in the annular groove of shell inner wall, and the detachable type constraint spring seat axial displacement is established, be equipped with third O ring between steel ball seat and shell, the outside of P mouth is connected with filter screen, through setting spring seat, valve sleeve and hole steel wire baffle ring, spring seat adopts clearance fit (0.02 0.05mm) plus hole steel wire baffle ring limit with valve sleeve, thoroughly avoid the hole deformation caused by traditional interference pressurization.

Description

Technical Field

[0001] This utility model relates to the technical field of pilot proportional pressure reducing valves, specifically a pilot proportional pressure reducing valve with a detachable spring seat. Background Technology

[0002] Pilot-operated pressure reducing valves regulate the flow of the medium by controlling the opening degree of the opening and closing elements within the valve body, thereby reducing the pressure of the medium. At the same time, they adjust the opening degree of the opening and closing elements by using the downstream pressure to keep the downstream pressure within a certain range. Even when the inlet pressure changes continuously, the outlet pressure is kept within the set range, protecting downstream household and production equipment.

[0003] Traditional proportional pressure reducing valves suffer from problems such as deformation, complex assembly, and difficult maintenance. Therefore, a pilot-operated proportional pressure reducing valve with a detachable spring seat is proposed to solve these problems. Summary of the Invention

[0004] The purpose of this invention is to provide a pilot proportional pressure reducing valve with a detachable spring seat to solve the problems mentioned in the background art.

[0005] To achieve the above objectives, this utility model provides the following technical solution: a pilot-operated proportional pressure reducing valve with a detachable spring seat, comprising a housing, a valve core, a spring seat, a valve core spring, a wire retaining ring for the bore, a steel ball seat, a steel ball, and an electromagnetic control assembly; the electromagnetic control assembly includes a coil frame, enameled wire, an armature, and a magnetic shielding sleeve; the valve core controls the oil circuit opening from port P to port A through displacement.

[0006] The spring seat and valve sleeve are fitted with a clearance of 0.02-0.05mm, and are fixed by a wire retaining ring through an axially installed hole. The wire retaining ring is embedded in the annular groove on the inner wall of the outer shell, which can be detachably constrained from axial displacement of the spring seat. A third O-ring is provided between the steel ball seat and the outer shell, and a filter screen is snapped onto the outside of the P port.

[0007] Furthermore, the clearance mating surface between the spring seat and the valve sleeve is provided with a guide chamfer, the chamfer angle is 15°±2°, and the chamfer depth is 0.5mm.

[0008] Furthermore, the electromagnetic control assembly also includes an armature spring and a push rod. The armature is elastically connected to the magnetic shielding sleeve through the armature spring. One end of the push rod abuts against the armature, and the other end is linked to the steel ball through the first composite bearing and the second composite bearing. A fourth O-ring and a fifth O-ring are provided between the first composite bearing and the outer shell, and a sixth O-ring is provided between the first composite bearing and the magnetic shielding sleeve.

[0009] Furthermore, a first O-ring and a second O-ring are provided between the valve core and the outer shell, respectively located at the two ends of the valve core sealing cavity, and are made of fluororubber with a hardness of 75±5 Shore A.

[0010] Furthermore, the coil frame of the electromagnetic control component is fixed to the front yoke by laser welding, the number of turns of the enameled wire is 1500±50, and the wire diameter is 0.25mm.

[0011] Furthermore, the opening degree of the steel ball is negatively correlated with the coil current. For every 100mA increase in current, the pressure at port T increases by 5.2±0.3 bar, and the displacement of the valve core increases by 0.15mm.

[0012] Furthermore, the inner hole of the outer shell has a roundness of ≤0.003mm, a cylindricity of ≤0.005mm, and a surface roughness Ra≤0.4μm. A plug is snapped into the right end of the outer shell, a seventh O-ring is provided between the plug and the outer shell, and a pin is fixedly connected to the right end of the plug.

[0013] Compared with the prior art, the beneficial effects of this utility model are:

[0014] By incorporating a spring seat, valve sleeve, and wire retaining ring for the bore, valve sleeve deformation is easily eliminated. The spring seat and valve sleeve are fitted with a clearance fit (0.02-0.05mm), and the wire retaining ring for the bore provides limiting, completely avoiding internal bore deformation caused by traditional interference fits, effectively improving structural accuracy. The wire retaining ring allows for easy replacement of the spring seat or valve core by axially removing it (removal force only 15-20N), reducing maintenance time from ≥30 minutes (destructive disassembly) to ≤5 minutes, facilitating rapid disassembly and assembly. With the inclusion of seven O-rings (first to seventh), seven sets of O-rings and valve core components are independently encapsulated, eliminating the need to disassemble the electromagnetic control components (coil frame, armature, etc.) during maintenance, reducing the risk of misoperation. Furthermore, two sets of fluororubber O-rings (hardness 75±5 Shore) are used. A) With the valve core split at both ends, the sealing life is increased by 40%, the leakage rate is ≤0.1ml / min, and the steel ball is set. The opening degree of the steel ball is negatively correlated with the coil current. The pressure output range is 0-33bar. For every 100mA increase in current, the pressure at port T increases by 5.2±0.3bar. The linearity error is ≤±1.5%. By setting the first composite bearing and the second composite bearing, the composite bearing and the armature spring work together to reduce frictional resistance and shorten the response time to 20ms. It is suitable for high dynamic hydraulic systems. Attached Figure Description

[0015] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort. In all drawings, similar elements or parts are generally identified by similar reference numerals. In the drawings, the elements or parts are not necessarily drawn to scale.

[0016] Figure 1 This is a schematic diagram of the cross-sectional structure of the main body of this utility model;

[0017] Figure 2 This utility model Figure 1 Enlarged structural diagram at point A in the middle.

[0018] In the diagram: 1. Valve core spring; 2. Spring seat; 3. Valve sleeve; 4. Valve core; 5. Fifth O-ring; 6. Sixth O-ring; 7. Seventh O-ring; 8. Wire retaining ring for the hole; 9. Steel ball seat; 10. Steel ball; 11. First O-ring; 12. Second O-ring; 13. T-port; 14. Outer shell; 15. Coil frame; 16. Enamelled wire; 17. Third O-ring; 18. Front yoke; 19. First composite bearing; 20. Plug; 21. Pin; 22. Fourth O-ring; 23. Armature spring; 24. Armature; 25. Filter screen; 26. Magnetic shielding sleeve; 27. Second composite bearing; 29. ​​Push rod; 30. P-port; 31. A-port. Detailed Implementation

[0019] In the description of this utility model, it should be noted that the terms "upper," "lower," "inner," "outer," "front end," "rear end," "both ends," "one end," and "the other end," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. In addition, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0020] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installed," "equipped with," and "connected," etc., should be interpreted broadly. For example, "connected" can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0021] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0022] Please see Figure 1-2 This utility model provides a pilot proportional pressure reducing valve with a detachable spring seat, including a housing 14, a valve core 4, a spring seat 2, a valve sleeve 3, and a wire retaining ring 8 for the bore, which facilitates the elimination of deformation of the valve sleeve 3. The spring seat 2 and the valve sleeve 3 are fitted with a clearance fit (0.02-0.05mm), and the wire retaining ring 8 for the bore limits the movement, completely avoiding the inner bore deformation caused by traditional interference fit, effectively improving structural accuracy. The valve core spring 1 and the wire retaining ring 8 for the bore allow for easy replacement of the spring seat 2 or the valve core 4 by axially removing the wire retaining ring 8 (removal force is only 15-20N), reducing maintenance time from ≥30 minutes (destructive disassembly) to ≤5 minutes, facilitating quick disassembly and assembly. The valve also includes a steel ball seat 9, a steel ball 10, and an electromagnetic control assembly. The steel ball 10 is negatively correlated with the coil current, and the pressure... The output range is 0-33 bar. For every 100mA increase in current, the pressure at port T13 increases by 5.2±0.3 bar. The linearity error is ≤±1.5%. The electromagnetic control assembly includes a coil frame 15, enameled wire 16, armature 24, and magnetic shielding sleeve 26. The valve core 4 controls the oil circuit opening from port P30 to port A31 through displacement. The spring seat 2 and valve sleeve 3 are in clearance fit with a clearance of 0.02-0.05mm. They are fixed by a wire retaining ring 8 through an axially installed hole. The wire retaining ring 8 is embedded in the annular groove on the inner wall of the outer shell 14, which can be detachably constraining the axial displacement of the spring seat. A third O-ring 17 is provided between the steel ball seat 9 and the outer shell 14. A filter screen 25 is snapped onto the outside of port P30. The clearance fit surface between the spring seat 2 and the valve sleeve 3 is provided with a guide chamfer with a chamfer angle of 15°±2° and a chamfer depth of 0.5mm.

[0023] The electromagnetic control assembly also includes an armature spring 23 and a push rod 29. The armature 24 is elastically connected to the magnetic shielding sleeve 26 via the armature spring 23. One end of the push rod 29 abuts against the armature 24, and the other end is linked to the steel ball 10 via the first composite bearing 19 and the second composite bearing 27. By setting the first composite bearing 19 and the second composite bearing 27, the composite bearing and the armature spring 23 work together to reduce frictional resistance, shortening the response time to 20ms, which is suitable for high-dynamic hydraulic systems. A fourth O-ring 22 and a fifth O-ring 5 are provided between the first composite bearing 19 and the housing 14, and a sixth O-ring 6 is provided between the first composite bearing 19 and the magnetic shielding sleeve 26. A first O-ring 11 and a second O-ring 12 are provided between the valve core 4 and the housing 14. By setting the first O-ring 11 to the seventh O-ring 7, the seven sets of O-rings, valve core 4 and other key components are independently packaged, so that the electromagnetic control assembly (coil frame 15, armature 24, etc.) does not need to be disassembled during maintenance, reducing the risk of misoperation. The two sets of fluororubber O-rings (hardness 75±5 Shore) A) The valve core 4 is separated at both ends, improving the sealing life by 40% and the leakage rate ≤0.1ml / min. The sealing cavities at both ends of the valve core 4 are made of fluororubber with a hardness of 75±5 Shore A. The coil frame 15 of the electromagnetic control component is fixed to the front yoke 18 by laser welding. The enameled wire 16 has 1500±50 turns and a wire diameter of 0.25mm. The opening of the steel ball 10 is negatively correlated with the coil current. For every 100mA increase in current, the pressure at port 13 increases by 5.2±0.3bar, and the displacement of the valve core 4 increases by 0.15mm. The inner hole of the outer shell 14 is precision machined with a roundness ≤0.003mm, a cylindricity ≤0.005mm, and a surface roughness Ra≤0.4μm. The right end of the outer shell 14 is connected to a plug 20. A seventh O-ring 7 is provided between the plug 20 and the outer shell 14. The right end of the plug 20 is fixedly connected to a pin 21.

[0024] In use, this utility model's pressure reducing valve regulates oil pressure through electromagnetic control and mechanical linkage. The working process can be divided into two scenarios: energized and de-energized.

[0025] 1. Power-on state: Dynamic pressure adjustment

[0026] Electromagnetic drive trigger: After being energized, the enameled wire 16 generates a magnetic field, which attracts the armature 24 to move towards the coil against the resistance of the armature spring 23, thereby driving the push rod 29 to push the steel ball 10 to reduce the opening.

[0027] Pressure transmission and valve spool response:

[0028] The pressure at port T13 increases because the reduced opening of the steel ball obstructs the oil drain at port T. The pressure at port T increases linearly with the current; for every 100mA increase in current, the pressure rises by 5.2±0.3 bar.

[0029] Valve core 4 displacement control: The pressure at port T is transmitted to valve core 4 through composite bearings 19 and 27, pushing it to move towards port P 30, so that the high-pressure oil at port P is proportionally distributed to port A 31 through the valve core opening, with an output pressure range of 0-33 bar.

[0030] 2. Power failure state: System reset and oil circuit interruption

[0031] Electromagnetic force disappears: After power is cut off, armature spring 23 pushes armature 24 to reset, steel ball 10 returns to maximum opening, and T port 13 quickly releases pressure to the oil tank.

[0032] Valve core reset: When the pressure at port T returns to zero, valve core spring 1 drives valve core 4 to reset, closing the oil circuit from port P to port A and blocking pressure output.

[0033] 3. Key component coordination mechanism

[0034] Clearance fit and retaining ring limit: The clearance fit between the spring seat and the valve sleeve is 0.02-0.05mm to avoid deformation of the inner hole. The hole is axially limited by a steel wire retaining ring 8 to ensure the valve core movement accuracy and roundness ≤0.003mm;

[0035] Sealing and anti-interference: Two sets of fluororubber O-rings 5 ​​and 6 are placed at both ends of the valve core for sealing, and composite bearings 19 and 27 reduce friction, with a response time ≤20ms.

[0036] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A pilot proportional pressure reducing valve with a detachable spring seat, comprising a housing (14), a valve core (4), a spring seat (2), a valve core spring (1), a wire retaining ring (8) for the bore, a steel ball seat (9), a steel ball (10), and an electromagnetic control assembly; the electromagnetic control assembly comprises a coil frame (15), enameled wire (16), an armature (24), and a magnetic shielding sleeve (26); the valve core (4) controls the oil passage opening from port P (30) to port A (31) by displacement, characterized in that: The spring seat (2) and the valve sleeve (3) are fitted with a clearance of 0.02-0.05mm. The spring seat (2) is fixed by a wire retainer (8) installed in the axial direction. The wire retainer (8) is embedded in the annular groove on the inner wall of the outer shell (14) to detachably constrain the axial displacement of the spring seat. A third O-ring (17) is provided between the steel ball seat (9) and the outer shell (14). A filter screen (25) is snapped onto the outside of the P port (30).

2. The pilot-operated proportional pressure-reducing valve with a detachable spring seat according to claim 1, characterized in that: The spring seat (2) and valve sleeve (3) have a guide chamfer on their clearance mating surface. The chamfer angle is 15°±2° and the chamfer depth is 0.5mm.

3. The pilot-operated proportional pressure-reducing valve with a detachable spring seat according to claim 2, characterized in that: The electromagnetic control assembly also includes an armature spring (23) and a push rod (29). The armature (24) is elastically connected to the magnetic shielding sleeve (26) through the armature spring (23). One end of the push rod (29) abuts against the armature (24), and the other end is linked with the steel ball (10) through the first composite bearing (19) and the second composite bearing (27). A fourth O-ring (22) and a fifth O-ring (5) are provided between the first composite bearing (19) and the outer shell (14), and a sixth O-ring (6) is provided between the first composite bearing (19) and the magnetic shielding sleeve (26).

4. The pilot-operated proportional pressure-reducing valve with a detachable spring seat according to claim 3, characterized in that: The valve core (4) and the outer shell (14) are provided with a first O-ring (11) and a second O-ring (12), which are respectively located at the two ends of the valve core (4) sealing cavity. The material is fluororubber with a hardness of 75±5 Shore A.

5. The pilot-operated pressure-reducing valve of claim 4, wherein: The coil frame (15) of the electromagnetic control component is fixed to the front yoke (18) by laser welding. The number of turns of the enameled wire (16) is 1500±50, and the wire diameter is 0.25mm.

6. The pilot-operated pressure-reducing valve of claim 5, wherein: The opening of the steel ball (10) is negatively correlated with the coil current. For every 100mA increase in current, the pressure at port T (13) increases by 5.2±0.3bar, and the displacement of the drive valve core (4) increases by 0.15mm.

7. The pilot-operated pressure-reducing valve of claim 6, wherein: The outer shell (14) has a precision machined inner hole with a roundness of ≤0.003mm, a cylindricity of ≤0.005mm, and a surface roughness Ra≤0.4μm. The right end of the outer shell (14) is connected to a plug (20). A seventh O-ring (7) is provided between the plug (20) and the outer shell (14). The right end of the plug (20) is fixedly connected to a pin (21).

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