Armature clearance adjustment assembly, differential pressure servo control valve and plunger pump

Abstract

The present invention discloses an armature clearance adjustment component, a differential pressure servo control valve and a plunger pump. The armature clearance adjustment component includes a seal fit and clearance adjustment member, an armature, a pendulum and an elastic support component. The seal fit and clearance adjustment member, the armature and the pendulum have the same central axis. The elastic support component includes a connecting component and two elastic support rib structures. The two elastic support rib structures are symmetrically arranged around the central axis and the movement direction is perpendicular to the central axis. The seal fit and clearance adjustment member include a sealing body and a stopper located below the sealing body. The length of the armature extends on the central axis and the lower end is connected to the sealing body. The length of the pendulum extends on the central axis and the lower end is connected to the armature. The elastic support component is used to elastically adjust the amplitude of the armature clearance adjustment component. The present invention solves the problems of difficulty in manufacturing the spring tube of the traditional pressure servo control valve, high cost and difficulty in mass production.

Description

Technical Field

[0001] The invention belongs to the technical field of pressure servo control valves, and in particular relates to an armature clearance adjustment component, a differential pressure servo control valve and a plunger pump. Background Art

[0002] The traditional pressure servo control valve includes an armature baffle assembly. In order to meet the dynamic characteristics of the servo control valve, the stiffness of the spring tube in the armature baffle assembly has strict requirements. The wall thickness of the spring tube is usually designed to be very thin, about 0.05-0.07 mm. It needs to undergo multiple heat treatments and use precision special processing tools and precision grinders to be processed to the specified contour size accuracy. If the surface finish of the spring tube is poor or there are processing defects, the traditional pressure servo control valve is prone to oil leakage and fatigue fracture. Therefore, the manufacturing of the spring tube of the traditional pressure servo control valve is difficult, costly, and has a low pass rate, making it difficult to achieve mass production. Summary of the invention

[0003] In view of the above-mentioned deficiencies in the prior art, the present invention provides an armature clearance adjustment assembly, a differential pressure servo control valve and a plunger pump.

[0004] The objective of the present invention is achieved through the following technical solutions:

[0005] In a first aspect, an armature gap adjustment assembly is provided, comprising: a seal fit and gap adjustment member, an armature, a swing member and an elastic support assembly, wherein the seal fit and gap adjustment member, the armature and the swing member have the same central axis, and the elastic support assembly comprises a connecting assembly and two elastic support rib structures, wherein the two elastic support rib structures are symmetrically arranged around the central axis and move in a direction perpendicular to the central axis;

[0006] The sealing fitting and clearance adjusting member comprises a sealing main body and a stopper located below the sealing main body and extending along the central axis;

[0007] The length of the armature extends on the central axis and the lower end is connected to the sealing body;

[0008] The length of the pendulum extends on the central axis and the lower end is connected to the armature;

[0009] The elastic support assembly is used to elastically adjust the amplitude of the deflection of the armature gap adjustment assembly;

[0010] When the armature of the armature gap adjustment assembly is in the middle position, the magnetic forces on both sides of the armature are equal, and the direction of the central axis is used as the first direction;

[0011] When the magnetic forces on both sides of the armature gap adjustment component are unequal, the central axis oscillates on a plane around a oscillation point. At this time, the central axis is not parallel to the first direction, and at least a part of the elastic support component is in a state of increased compression;

[0012] The armature gap adjustment assembly does not undergo yaw motion when the magnetic forces on both sides are equal. At this time, the central axis is parallel to the first direction, and the elastic support assembly is in a state of constant compression.

[0013] In a second aspect, a differential pressure servo control valve is provided, which, in addition to the armature clearance adjustment assembly, further comprises:

[0014] A base assembly is sealingly connected to the armature gap adjustment assembly and controls the inlet and outlet of liquid through the armature gap adjustment assembly;

[0015] A sway control component for controlling the sway state of the armature gap adjustment component;

[0016] a zeroing assembly connected to the armature gap adjustment assembly to restore the central axis of the armature gap adjustment assembly to be parallel to the first direction; and

[0017] A housing component connected to the base component, wherein the housing component and the base component form an outer protection portion of the differential pressure servo control valve.

[0018] In some embodiments, the base assembly includes:

[0019] A base having a cavity sealingly matched with the armature gap adjustment assembly and a liquid inlet hole and a liquid outlet hole communicating with the cavity;

[0020] Two injection parts are symmetrically arranged in the cavity of the base around the central axis of the blocking part, and are respectively recorded as a first injection part and a second injection part, a first gap is formed between the first injection part and the outer wall of the blocking part, and a second gap is formed between the second injection part and the outer wall of the blocking part, and the first gap and the second gap are both located in the area directly above the liquid outlet hole of the base;

[0021] The filter unit for preventing impurities in the oil from entering the injection part is arranged in the cavity of the base. In some embodiments, the yaw control component adopts a coil magnet component.

[0022] In some embodiments, the yaw control component includes:

[0023] A pressure plate, symmetrically arranged on the top surface of the elastic support assembly along the central axis of the armature;

[0024] a solenoid, symmetrically arranged on the top surface of the pressure plate along the central axis of the armature;

[0025] A magnetic conductor is symmetrically arranged on the top surface of the pressure plate along the central axis of the armature;

[0026] The permanent magnet is arranged at the end of the magnetic conductor, and the gaps between the two magnetic poles of the permanent magnet and the corresponding armature are respectively the third gap and the fourth gap.

[0027] In some embodiments, the zeroing assembly includes:

[0028] A spring seat, disposed on the top of the armature;

[0029] A zero adjustment seat, arranged on the housing assembly;

[0030] a spring, disposed between the spring seat and the zero adjustment seat; and

[0031] An adjusting screw for adjusting the compression amount of the spring is arranged on the zero adjustment seat.

[0032] In some embodiments, the housing assembly comprises:

[0033] A housing, disposed on the top of the base assembly;

[0034] an electrical plug disposed on a side wall of the housing; and

[0035] A manual knob for driving the armature gap adjustment assembly to swing is arranged at the center of the top surface of the shell.

[0036] In some embodiments, when a positive electrical signal is input to the differential pressure servo control valve, the deflection control component generates a current change, the electromagnetic force of the magnetic pole at the third gap is greater than the electromagnetic force of the magnetic pole at the fourth gap, so that the armature deflects counterclockwise, the elastic support component is deformed by force, and the second gap is smaller than the first gap;

[0037] The pressure value at a position in the cavity of the base close to the first injection part is a first load pressure, and the pressure value at a position in the cavity of the base close to the second injection part is a second load pressure, the second load pressure is greater than the first load pressure, and the second load pressure changes proportionally with the size of the forward electrical signal.

[0038] In some embodiments, when a negative electrical signal is input to the differential pressure servo control valve, the deflection control component generates a current change, the electromagnetic force of the magnetic pole at the third gap is smaller than the electromagnetic force of the magnetic pole at the fourth gap, so that the armature deflects clockwise, the elastic support component is deformed by force, and the second gap is larger than the first gap;

[0039] The pressure value at a position in the cavity of the base close to the first injection part is a first load pressure, and the pressure value at a position in the cavity of the base close to the second injection part is a second load pressure. The first load pressure is greater than the second load pressure, and the first load pressure changes proportionally with the size of the negative electrical signal.

[0040] In a third aspect, a plunger pump is provided, comprising the differential pressure servo control valve.

[0041] The beneficial effects of the present invention are as follows: the elastic support assembly used in the armature gap adjustment assembly of the present invention replaces the precise and costly spring tube in the traditional servo valve. In order to adapt to the elastic support assembly and ensure the role of the armature gap adjustment assembly in the entire differential pressure servo control valve, the present invention configures a sealing fit and gap adjustment part, an armature and a pendulum in the armature gap adjustment assembly, and constructs the positional relationship and connection relationship of the elastic support assembly, the sealing fit and gap adjustment part, the armature and the pendulum in the armature gap adjustment assembly. The elastic support assembly uses two elastic support rib structures to replace the thin-wall structure of the traditional servo valve. The elastic support rib structure of the elastic support assembly is easy to process and can be formed by a stamping process without the need for a high-precision grinder. The manufacturing cost is much lower than that of the traditional pressure servo valve. The permanent magnets are symmetrically arranged on both sides of the armature, so that the magnetic resistance of the entire magnetic circuit is minimized, and a stronger initial magnetic force is generated for the armature, that is, the initial magnetic stiffness coefficient is large. Therefore, the present invention has better dynamic performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0043] Figure 1 is a cross-sectional view of a differential pressure servo control valve provided in one embodiment of the present invention;

[0044] Figure 2 is a structural principle diagram of a differential pressure servo control valve provided in one embodiment of the present invention;

[0045] Figure 3 It is a working principle diagram of the differential pressure servo control valve provided in one embodiment of the present invention when no electricity is supplied;

[0046] Figure 4 This is a working principle diagram of a differential pressure servo control valve provided in one embodiment of the present invention when a positive electrical signal is introduced;

[0047] Figure 5 It is a working principle diagram of a differential pressure servo control valve provided in one embodiment of the present invention when a negative electrical signal is introduced;

[0048] Figure 6 is a structural schematic diagram of a portion of an armature gap adjustment assembly provided in one embodiment of the present invention;

[0049] Figure 7 is a schematic structural diagram of a portion of an elastic support assembly provided in one embodiment of the present invention;

[0050] Figure 8 1 is an exploded view of a differential pressure servo control valve provided in one embodiment of the present invention. DETAILED DESCRIPTION

[0051] In order to better understand the technical solution of the present application, the embodiments of the present application are described in detail below with reference to the accompanying drawings.

[0052] The present invention provides an armature clearance adjustment component, which solves the problem that the spring tube of a conventional pressure servo control valve is difficult to manufacture, has high cost and is difficult to mass produce. The present invention also provides a differential pressure servo control valve implemented by using the armature clearance adjustment component, and a plunger pump implemented by using the differential pressure servo control valve.

[0053] like Figure 1 , Figure 6 and Figure 7 As shown, in one embodiment, an armature gap adjustment assembly is provided, the armature gap adjustment assembly 20 comprising a seal fit and gap adjustment member 201, an armature 202, a pendulum member 203 and an elastic support assembly 204;

[0054] The sealing and clearance adjustment member 201, the armature 202 and the pendulum 203 all have the same central axis Y1, and the elastic support assembly 204 includes a connecting assembly 2041 and two elastic support rib structures 2042, and the two elastic support rib structures 2042 are symmetrically arranged around the central axis Y1 and move in a direction perpendicular to the central axis Y1;

[0055] The sealing fitting and clearance adjusting member 201 comprises a sealing main body 2011 and a stopper 2012 located below the sealing main body and extending along the central axis Y1; in one embodiment, the sealing fitting and clearance adjusting member 201 is plate-shaped, wherein a sealing groove arranged circumferentially is provided on the side wall of the sealing main body 2011 and a sealing ring is embedded in the sealing groove of the sealing main body 2011, an embedding groove is provided on the top of the sealing main body 2011, and the cross section of the stopper 2012 is rectangular;

[0056] The length of the armature 202 extends on the central axis Y1 and the lower end is connected to the sealing body 2011 of the sealing fitting and gap adjusting member; in one embodiment, the lower end of the armature 202 passes through the elastic support assembly 204 and is embedded in the embedding groove connected to the top of the sealing body 2011 of the sealing fitting and gap adjusting member;

[0057] The length of the swing member 203 extends on the central axis Y1 and the lower end is connected to the armature 202; in one embodiment, the swing member 203 is a cylindrical pin;

[0058] The elastic support assembly 204 is used to elastically adjust the amplitude of the deflection of the armature gap adjustment assembly;

[0059] In one embodiment, if Figure 6 and Figure 7 As shown, the elastic support assembly 204 includes a connecting assembly 2041 and two elastic support rib structures 2042, the two elastic support rib structures 2042 are symmetrically arranged around the central axis Y1 and the movement direction is perpendicular to the central axis Y1; the connecting assembly 2041 includes a first plate 2041a and a second plate 2041b, the first plate 2041a and the second plate 2041b both have a hollow structure, wherein specifically, the second plate 2041b is roughly in the shape of a cube and has a loading hole in the middle, and the second plate 2041b is arranged at On the top surface of the base 101; the first plate 2041a is roughly annular and is arranged in the loading hole of the second plate 2041b, the bottom surface of the first plate 2041a is located on the top surface of the sealing body 2011, and the lower end of the armature 202 passes through the middle hole of the first plate 2041a and is connected to the sealing body 2011; in one embodiment, the elastic support rib structure 2042 is plate-shaped, and the two elastic support rib structures 2042 are symmetrically arranged around the central axis Y1 between the first plate 2041a and the second plate 2041b.

[0060] When the armature of the armature gap adjustment assembly 20 is in the middle position, the magnetic forces on both sides of the armature are equal, the direction of the central axis Y1 is taken as the first direction Y, and the direction perpendicular to the first direction Y is taken as the second direction X.

[0061] When the magnetic forces on both sides of the armature gap adjustment component 20 are uneven, the central axis Y1 undergoes a swing motion on the horizontal plane around a swing point, for example, the swing amplitude is ±1°, at this time, at least a portion of the elastic support component 204 is in a state of increased compression, and the central axis of the armature gap adjustment component 20 is not parallel to the first direction; when the central axis Y1 of the armature gap adjustment component 20 is not parallel to the first direction Y, due to the different swing directions of the central axis Y1 of the armature gap adjustment component 20, the gaps between the two side walls of the blocking portion 2012 and the corresponding injection portion 102 are different; for example, in one embodiment, the gap between the right side wall of the blocking portion 2012 and the corresponding injection portion 102 is greater than the gap between the left side wall of the blocking portion 2012 and the corresponding injection portion 102; in another embodiment, the gap between the right side wall of the blocking portion 2012 and the corresponding injection portion 102 is smaller than the gap between the left side wall of the blocking portion 2012 and the corresponding injection portion 102.

[0062] The armature gap adjustment assembly 20 will not undergo yaw motion when the magnetic forces on both sides are equal. At this time, the elastic support assembly 204 is in a constant compression state, and the central axis Y1 of the armature gap adjustment assembly 20 is parallel to the first direction Y; when the central axis Y1 of the armature gap adjustment assembly 20 is parallel to the first direction Y, the gaps between the two side walls of the blocking portion 2012 and the injection portion 102 are the same.

[0063] like Figure 8 As shown, in one embodiment, a differential pressure servo control valve is provided. In addition to the armature clearance adjustment assembly 20 mentioned in the above embodiment, the differential pressure servo control valve also includes a base assembly 10, a yaw control assembly 30, a zero adjustment assembly 40 and a housing assembly 50.

[0064] The base assembly 10 is sealingly connected with the armature gap adjustment assembly 20 and the inlet and outlet of the liquid are regulated by the armature gap adjustment assembly 20;

[0065] In one embodiment, if Figure 1As shown, the base assembly 10 includes: a base 101, two injection parts 102 and a filter unit 103 for preventing impurities in the oil from entering the injection part 102, which solves the problem that the nozzle diameter of the conventional pressure servo control valve is about 0.5-1.0 mm, and when the oil is contaminated, it is easy to cause the nozzle to be blocked, thereby causing functional failure; wherein, the base 101 has a cavity that is sealed with the armature gap adjustment assembly 20 and a liquid inlet hole 107 and a liquid outlet hole 108 that are connected to the cavity; in one embodiment, a sealing ring is provided between the base 101 and the sealing body 2011 at the sealing groove of the sealing body 2011; in one embodiment, the cavity of the base 101 includes a first through hole 1011 extending in a first direction Y and two second through holes extending in a second direction X and symmetrically arranged along the central axis of the first through hole 1011, the two second through holes are respectively a second through hole 1012a and a second through hole 2 1012b, and the outer opening ends of the two second through holes are installed with screw plugs 104; in one embodiment, the liquid inlet hole 1 There are two 07 and they are symmetrically arranged around the central axis of the first through hole 1011 and are located at the bottom of the base 101. The liquid inlet hole 107 of the base is tightly connected to the oil pipe through a sealing ring; the liquid outlet hole 108 is located directly below the first through hole 1011 and is set at the bottom of the base 101. The liquid outlet hole 108 of the base is tightly connected to the oil pipe through a sealing ring; the two injection parts 102 are symmetrically arranged around the central axis of the blocking part 2012 in the cavity of the base 101, respectively, the first injection part 1021 and the second injection part 1 022, a first gap 105 is defined between the first injection portion 1021 and the outer wall of the blocking portion 2012, a second gap 106 is defined between the second injection portion 1022 and the outer wall of the blocking portion 2012, and both the first gap 105 and the second gap 106 are located directly above the liquid outlet 108 of the base; in one embodiment, the first injection portion 1021 and the second injection portion 1022 are interference fit and are respectively embedded in the inner opening ends of the second through hole of the base, and in one embodiment, the two injection portions 102 use nozzles.

[0066] In one embodiment, the base assembly 10 further includes a filtering unit 103 for preventing impurities in the oil from entering the injection portion 102 ; the filtering unit 103 includes two filters, which are symmetrically arranged around the central axis of the first through hole 1011 inside the second through hole of the base.

[0067] The deflection control component 30 is used to control the deflection state of the armature gap adjustment component 20;

[0068] In one embodiment, the yaw control component 30 adopts a coil magnet component, including: a pressure plate 301, a solenoid 302, a wire 303, a magnet 304, a permanent magnet 305 and a screw 306; wherein the pressure plate 301 is symmetrically arranged on the top surface of the elastic support component 204 along the central axis Y1 of the armature, the solenoid 302 is placed on the top of the pressure plate 301 and symmetrically arranged along the central axis Y1 of the armature, and the bottom of the solenoid 302 is connected to the wire 303; the magnet 304 is symmetrically arranged along the central axis Y1 of the armature, and the vertical extension part of the magnet 304 is fixed on On the pressing plate 301, the horizontal extension part of the magnet 304 has an opening along the second direction X, and the opening on the horizontal extension part of the magnet 304 has a thread inside; the permanent magnet 305 is a ring-shaped component with a circular opening in the middle, and the permanent magnet 305 is arranged at the end of the horizontal extension part of the magnet 304. The permanent magnet 305 has two magnetic poles, and the magnet 304 and the permanent magnet 305 are fixedly connected by screws 306. The gaps between the two magnetic poles of the permanent magnet 305 and the armature 202 are the third gap 307 and the fourth gap 308. Only when the solenoid 302 has an electrical signal, the magnetic field on both sides changes, and the magnetic force will be uneven.

[0069] The zero adjustment assembly 40 is connected to the armature gap adjustment assembly 20 to restore the central axis Y1 of the armature gap adjustment assembly 20 to a position parallel to the first direction Y;

[0070] In one embodiment, the zero adjustment assembly 40 includes: a spring seat 401, a spring 402, a zero adjustment seat 403 and an adjusting screw 404; wherein the spring seat 401 is embedded in the top of the armature 202 and is symmetrically arranged on the outer wall of the pendulum 203, the zero adjustment seat 403 is fixed on the housing assembly 50, the adjusting screw 404 is threadedly connected to the zero adjustment seat 403, the adjusting screw 404 can adjust the compression amount of the spring 402, the spring 402 is arranged between the spring seat 401 and the adjusting screw 404 along the second direction X, one end of the spring 402 is connected to the spring seat 401 and the other end is connected to the adjusting screw 404.

[0071] The housing assembly 50 and the base assembly 10 are combined to form an outer protection portion of the differential pressure servo control valve.

[0072] In one embodiment, the housing assembly 50 includes: a housing 501, a manual knob 502, an electrical plug 503 and a bolt 504; wherein the housing 501 is a component having a roughly rectangular cavity inside, and the bottom of the housing 501 is connected to the top of the base 101 by bolts; the electrical plug 503 is fixed to the left side wall of the housing 501 by screws, and the wiring port of the electrical plug 503 is connected to the wire 303; the manual knob 502 is fixed to the center of the outer top surface of the housing 501 by a retaining spring, and the upper end of the pendulum 203 is embedded in the bottom groove of the manual knob 502, and the movement of the manual knob 502 can drive the pendulum 203 and the armature 202 to swing; the bolt 504 is fixed to the right side wall of the housing 501 to facilitate the later maintenance of the differential pressure servo control valve.

[0073] like Figure 2 and Figure 3 As shown, the pressure value of a position near the first injection part 1021 in the second through hole 1012a of the base is the first load pressure C1, and the pressure value of a position near the second injection part 1022 in the second through hole 1012b of the base is the second load pressure C2; ​​in one embodiment, when the electrical signal input to the differential pressure servo control valve is 0, the magnetic flux lines on the magnet 304 will not change, the gap between the magnetic pole of the permanent magnet 305 and the armature 202 will not change, and the armature gap adjustment assembly 20 will not deflect. At this time, oil flows into the liquid inlet 107, reaches the first injection part 1021 through the second through hole 1012a and flows back to the liquid outlet 108 from the first gap 105, and reaches the second injection part 1022 through the second through hole 1012b and flows back to the liquid outlet 108 from the second gap 106. Since the blocking part 2012 is in the neutral position, the third gap 307 and the fourth gap 308 are equal, the first gap 105 and the second gap 106 are equal, and the first load pressure C1 and the second load pressure C2 are equal.

[0074] like Figure 4 As shown, in one embodiment, when a positive electrical signal is introduced into the differential pressure servo control valve, the positive electrical signal is transmitted to the solenoid 302 along the wire 303, and the change of the internal current of the solenoid 302 will cause a positive signal magnetic flux 601 to be generated between the magnetic poles of the permanent magnet 305 (i.e., N is the north pole of the magnet, and S is the south pole of the magnet), so that the electromagnetic force of the magnetic pole at the third gap 307 is greater than the electromagnetic force of the magnetic pole at the fourth gap 308, so that the armature 202 deflects counterclockwise, the elastic support rib structure 2042 on the elastic support assembly 204 is deformed by force, the second gap 106 is smaller than the first gap 105, the second load pressure C2 is greater than the first load pressure C1, and the second load pressure C2 changes in proportion to the size of the positive electrical signal.

[0075] like Figure 5As shown, in one embodiment, when a negative electrical signal is introduced into the differential pressure servo control valve, the negative electrical signal is transmitted along the wire 303 to the solenoid 302, and the change of the current inside the solenoid 302 will cause a negative signal magnetic flux 602 to be generated between the magnetic poles of the permanent magnet 305 (i.e., N is the north pole of the magnet, and S is the south pole of the magnet), so that the electromagnetic force of the magnetic pole at the third gap 307 is smaller than the electromagnetic force of the magnetic pole at the fourth gap 308, so that the armature 202 deflects clockwise, the elastic support rib structure 2042 on the elastic support assembly 204 is deformed by force, the second gap 106 is larger than the first gap 105, the first load pressure C1 is larger than the second load pressure C2, and the first load pressure C1 changes in proportion to the size of the negative electrical signal.

[0076] The elastic support assembly 204 used in the armature gap adjustment assembly 20 of the present invention replaces the spring tube in the traditional servo control valve, solving the problems of the difficulty in manufacturing the spring tube, high cost, and difficulty in mass production. In order to adapt to the elastic support assembly 204 and ensure the role of the armature gap adjustment assembly 20 in the entire differential pressure servo control valve, the present invention configures a sealing fit and gap adjustment member 201, an armature 202, and a pendulum 203 in the armature gap adjustment assembly 20, and constructs the positional relationship and connection relationship of the elastic support assembly 204, the sealing fit and gap adjustment member 201, the armature 202, and the pendulum 203 in the armature gap adjustment assembly 20. The elastic support assembly 204 uses two elastic support rib structures 2042 to replace the thin-walled structure of the traditional servo control valve. The elastic support assembly 204 is easy to process and can be formed using a stamping process without the need for a high-precision grinder. The manufacturing cost is much lower than that of the traditional pressure servo control valve. The two elastic support rib structures 2042 provide elastic force for the elastic support component 204. The width and thickness of each elastic support rib structure are design parameters for controlling the elastic force. The size of the elastic support component 204 can be stamped by a precision stamping die, which is easy to ensure the manufacturing accuracy and consistency of parts manufacturing. It has the advantages of easy processing, low manufacturing cost, not easy fatigue fracture, and easy mass production. The permanent magnets 305 are symmetrically arranged on both sides of the armature 202, so that the magnetic resistance of the entire magnetic circuit is minimized, and a strong initial magnetic force is generated for the armature 202, that is, the initial magnetic stiffness coefficient is large. Therefore, the present invention has better dynamic performance.

[0077] The differential pressure servo control valve provided by the present invention has differential pressure servo control characteristics, zero dead zone, large pressure gain, and a pressure hysteresis loop of less than 5%. It can accurately control the displacement of the plunger pump so that the displacement of the plunger pump is proportional to the electrical signal applied at both ends of the armature gap adjustment component of the present invention.

[0078] The above description is merely a preferred embodiment of one or more embodiments of the present specification and is not intended to limit one or more embodiments of the present specification. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of one or more embodiments of the present specification shall be included in the scope of protection of one or more embodiments of the present specification.

Claims

1. A differential pressure servo control valve, characterized in that: It includes an armature gap adjustment component, a base component, a yaw control component, a zero adjustment component and a housing component; The armature gap adjustment assembly includes a seal fit and gap adjustment member, an armature, a pendulum member and an elastic support assembly; The sealing fit and clearance adjustment member, the armature and the pendulum member have the same central axis; The elastic support component includes a connecting component and two elastic support rib structures, the two elastic support rib structures are symmetrically arranged around the central axis and the movement direction is perpendicular to the central axis; the connecting component includes a first plate and a second plate, the first plate and the second plate both have a hollow structure, the second plate is in a cube shape and has a loading hole in the middle, the second plate is arranged on the top surface of the base, the first plate is in a circular ring shape and is arranged in the loading hole of the second plate, the bottom surface of the first plate is located on the top surface of the sealing body, and the lower end of the armature passes through the hole in the middle of the first plate to connect with the sealing body; the elastic support rib structure is in a plate shape, and the two elastic support rib structures are symmetrically arranged between the first plate and the second plate around the central axis; the elastic support rib structure provides elastic force for the elastic support component, and the width and thickness of each elastic support rib structure are design parameters for controlling the elastic force; the elastic support rib structure is formed by a stamping process; The sealing fitting and gap adjusting member comprises a sealing main body and a stopper located below the sealing main body and extending along the central axis; the sealing fitting and gap adjusting member is in the shape of a plate, a sealing groove arranged circumferentially is provided on the side wall of the sealing main body, a sealing ring is embedded in the sealing groove of the sealing main body, an embedding groove is provided on the top of the sealing main body, and the cross section of the stopper is in the shape of a rectangle; The length of the armature extends on the central axis and the lower end thereof passes through the elastic support assembly and is embedded in an embedding groove connected to the top of the sealing main body of the sealing fitting and clearance adjusting member; The length of the swing member extends on the central axis and the lower end is connected to the armature; the swing member adopts a cylindrical pin; The elastic support assembly is used to elastically adjust the amplitude of the deflection of the armature gap adjustment assembly; When the armature of the armature gap adjustment assembly is in the middle position, the magnetic forces on both sides of the armature are equal, the direction of the central axis is taken as the first direction, and the direction perpendicular to the first direction is taken as the second direction; When the magnetic forces on both sides of the armature gap adjustment component are unequal, the central axis oscillates on a plane around a oscillation point. At this time, the central axis is not parallel to the first direction, and at least a portion of the elastic support component is in a state of increased compression. When the central axis of the armature gap adjustment component is not parallel to the first direction, due to the different oscillation directions of the central axis of the armature gap adjustment component, the gaps between the two side walls of the blocking portion and the corresponding injection portion are different. The armature gap adjustment assembly does not yaw when the magnetic forces on both sides are equal. At this time, the central axis is parallel to the first direction, and the elastic support assembly is in a state of constant compression; When the central axis of the armature gap adjustment assembly is parallel to the first direction, the gaps between the two side walls of the blocking portion and the injection portion are the same; The base assembly is sealingly connected with the armature gap adjustment assembly and regulates the inflow and outflow of liquid through the armature gap adjustment assembly; The deflection regulating component is used to regulate the deflection state of the armature gap regulating component; The zero adjustment assembly is connected to the armature gap adjustment assembly to restore the central axis of the armature gap adjustment assembly to be parallel to the first direction; The housing assembly is connected to the base assembly, and the housing assembly and the base assembly form an outer protection portion of the differential pressure servo control valve; The base assembly comprises: A base, having a cavity that seals with the armature gap adjustment assembly and a liquid inlet and a liquid outlet that communicate with the cavity; a sealing ring is provided between the base and the sealing body and is located at the sealing groove of the sealing body; the cavity of the base includes a first through hole that extends in a first direction and two second through holes that extend in a second direction and are symmetrically arranged along the central axis of the first through hole, the two second through holes are respectively the second through hole one and the second through hole two, and screw plugs are installed at the outer opening ends of the two second through holes; the number of the liquid inlet holes is two and they are symmetrically arranged around the central axis of the first through hole and are located at the bottom of the base, and the liquid inlet of the base is tightly connected to the oil pipe through a sealing ring; the liquid outlet is located directly below the first through hole and is provided at the bottom of the base, and the liquid outlet of the base is tightly connected to the oil pipe through a sealing ring; Two injection parts are symmetrically arranged in the cavity of the base around the central axis of the stopper, and are respectively recorded as a first injection part and a second injection part. A first gap is provided between the first injection part and the outer wall of the stopper, and a second gap is provided between the second injection part and the outer wall of the stopper. The first gap and the second gap are both located in the area directly above the liquid outlet hole of the base. The first injection part and the second injection part are interference fit and are respectively embedded in the inner opening end of the second through hole of the base; A filter unit for preventing impurities in the oil from entering the injection portion is disposed in the cavity of the base; the filter unit comprises two filters, which are symmetrically arranged inside the second through hole of the base around the central axis of the first through hole; The deflection control component adopts a coil magnet component; the deflection control component includes: A pressure plate, symmetrically arranged on the top surface of the elastic support assembly along the central axis of the armature; A solenoid is symmetrically arranged on the top surface of the pressure plate along the central axis of the armature; a wire is connected to the bottom of the solenoid; The magnetizer is symmetrically arranged along the central axis of the armature; the vertical extension portion of the magnetizer is fixed on the pressure plate, the horizontal extension portion of the magnetizer has an opening along the second direction, and the opening on the horizontal extension portion of the magnetizer has a thread inside; A permanent magnet, which is an annular component with a circular opening in the middle, is arranged at the end of the horizontal extension part of the magnetizer, and is symmetrically arranged on both sides of the armature. The permanent magnet has two magnetic poles. The magnetizer and the permanent magnet are fixedly connected by screws. The gaps between the two magnetic poles of the permanent magnet and the corresponding armature are the third gap and the fourth gap respectively. Only when the solenoid has an electrical signal, the magnetic field on both sides changes, and the magnetic force will be unequal; The zeroing component comprises: A spring seat, embedded in the top of the armature and symmetrically arranged on the outer side wall of the pendulum; A zero adjustment seat, arranged on the housing assembly; a spring arranged between the spring seat and the adjusting screw along the second direction; and An adjusting screw for adjusting the compression amount of the spring, which is threadedly connected to the zero adjustment seat; The housing assembly comprises: A housing, disposed on the top of the base assembly; an electrical plug disposed on a side wall of the housing; and The manual knob is fixed at the center of the outer top surface of the housing through a retaining spring, the upper end of the pendulum is embedded in the bottom groove of the manual knob, and the movement of the manual knob can drive the pendulum and the armature to swing; The pressure value at a position near the first injection part in the second through hole 1 of the base is the first load pressure, and the pressure value at a position near the second injection part in the second through hole 2 of the base is the second load pressure; when the electric signal passed into the differential pressure servo control valve is 0, the magnetic flux lines on the magnetic conductor will not change, the gap between the magnetic pole of the permanent magnet and the armature will not change, and the armature gap adjustment component will not deflect; at this time, oil is passed into the liquid inlet hole, the oil reaches the first injection part through the second through hole 1 and flows back to the liquid outlet hole from the first gap, the oil reaches the second injection part through the second through hole 2 and flows back to the liquid outlet hole from the second gap, and because the blocking part is in the neutral position, the third gap and the fourth gap are equal, the first gap and the second gap are equal, and the first load pressure and the second load pressure are equal; When a positive electrical signal is introduced into the differential pressure servo control valve, the positive electrical signal is transmitted to the solenoid along the wire, and the change of the current inside the solenoid will generate a positive signal magnetic flux between the magnetic poles of the permanent magnet, so that the electromagnetic force of the magnetic poles at the third gap is greater than the electromagnetic force of the magnetic poles at the fourth gap, thereby causing the armature to deflect counterclockwise, the elastic support rib structure of the elastic support assembly is deformed by force, and the second gap is smaller than the first gap; the second load pressure is greater than the first load pressure, and the second load pressure changes in proportion to the size of the positive electrical signal; When a negative electrical signal is passed into the differential pressure servo control valve, the negative electrical signal is transmitted along the wire to the solenoid. The change of the current inside the solenoid will cause a negative signal magnetic flux to be generated between the magnetic poles of the permanent magnet, so that the electromagnetic force of the magnetic poles at the third gap is smaller than the electromagnetic force of the magnetic poles at the fourth gap, thereby causing the armature to deflect clockwise, and the elastic support rib structure of the elastic support assembly is deformed by force, and the second gap is larger than the first gap; the first load pressure is larger than the second load pressure, and the first load pressure changes proportionally with the size of the negative electrical signal.

2. A plunger pump, characterized in that: It includes the differential pressure servo control valve as claimed in claim 1.

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