Pressure adjusting device and damper damping valve

Abstract

The invention provides a pressure adjusting device and a damper damping valve, and relates to the technical field of damper damping valves. The device comprises a valve seat, a valve, a moving part, a first elastic part and a second elastic part, the valve is located in the moving part and can axially move relative to the moving part, the moving part is located in the valve seat and can axially move relative to the valve seat, and the first elastic part and the second elastic part are arranged on the valve seat. The first elastic piece is arranged between the moving part and the valve seat, the outer side of the second elastic piece is connected with the moving part, the inner side of the second elastic piece can make contact with the valve, an annular step is arranged on the inner side of the end of the valve seat, and the annular step is connected with the moving part. And the end part of the annular step can be in contact with the middle part of the second elastic piece.

Description

Technical Field

[0001] The invention relates to the technical field of shock absorber damping valves, and in particular to a pressure regulating device and a shock absorber damping valve. Background Art

[0002] In the technical scope of electronically controlled damping of shock absorbers, the original stepper motor has been used to drive the valve opening to change and control the medium damping change, and the stage of pursuing fast response has been changed. Therefore, the solenoid valve that directly drives the valve has gradually become the mainstream, and the controllable pressure range is required to be adjustable and as large as possible. Therefore, the structure of the pilot proportional valve has become an important structural form of the shock absorber damping regulating valve.

[0003] The solenoid valve structure includes a main stage and a pilot stage. Under the action of pressure, a throttling opening is formed in the pilot stage to form a pilot control of the main stage back pressure. A very small part of the oil medium flows out from the flat gap on one side of the pilot stage. This is the pilot flow channel, which is a small flow channel path for the pilot back pressure control of the main stage pressure. However, the function of the existing pilot stage is relatively simple. Summary of the invention

[0004] The object of the present invention is to provide a pressure regulating device and a shock absorber damping valve. The preferred technical solutions among the many technical solutions provided by the present invention can produce many technical effects as described in detail below.

[0005] To achieve the above object, the present invention provides the following technical solutions:

[0006] A pressure regulating device provided by the present invention comprises a valve seat, a valve, a moving part, a first elastic part and a second elastic part, wherein the valve is located in the moving part and can move axially relative to the moving part, the moving part is located in the valve seat and can move axially relative to the valve seat, the first elastic part is arranged between the moving part and the valve seat, the outer side of the second elastic part is connected to the moving part, the inner side of the second elastic part can contact the valve, and an annular step is arranged on the inner side of the end of the valve seat, and the end of the annular step can contact the middle part of the second elastic part.

[0007] Optionally, the first elastic member is a spring structure or a valve plate structure, and the second elastic member is a valve plate structure;

[0008] The ratio of the stiffness constant of the first elastic member to the variable stiffness constant of the second elastic member is in the range of 1:10 to 1:100.

[0009] Optionally, the second elastic member includes an inner ring spring piece, a middle ring spring piece, an outer ring spring piece, an inner ring spring piece beam and an outer ring spring piece beam, the inner ring spring piece, the middle ring spring piece and the outer ring spring piece are arranged from inside to outside in sequence, the inner ring spring piece is connected to the middle ring spring piece through the inner ring spring piece beam and the inner ring spring piece can move axially relative to the middle ring spring piece, the middle ring spring piece and the outer ring spring piece are connected through the outer ring spring piece beam and the middle ring spring piece can move axially relative to the outer ring spring piece.

[0010] Optionally, the inner ring spring piece, the middle ring spring piece and the outer ring spring piece are all annular structures, the outer ring spring piece is connected to the moving part, the middle ring spring piece can contact the annular step, and the inner ring spring piece can contact the valve.

[0011] Optionally, there are multiple inner ring spring fragment beams and multiple outer ring spring fragment beams, all of the inner ring spring fragment beams are distributed along the circumferential direction of the inner ring spring fragment, and all of the outer ring spring fragment beams are distributed along the circumferential direction of the middle ring spring fragment.

[0012] Optionally, a first flow opening is formed between the inner ring spring sheet, the middle ring spring sheet and two adjacent inner ring spring sheet beams, a second flow opening is formed between the middle ring spring sheet, the outer ring spring sheet and two adjacent outer ring spring sheet beams, and a flow hole is arranged inside the inner ring spring sheet.

[0013] Optionally, a variable flow opening is provided between the valve seat and the valve.

[0014] The present invention provides a shock absorber damping valve, which comprises a main stage, a driving assembly and a pressure regulating device, wherein two ends of the pressure regulating device are respectively connected to the main stage and the driving assembly.

[0015] The present invention provides a pressure regulating device, the core of which is a spring arrangement composed of a first elastic member and a second elastic member. The first elastic member and the second elastic member use a moving part to realize displacement series connection and elastic force transmission, which work in the entire working process. The special design of the second elastic member forms two working displacement areas, corresponding to the main target functions of displacement connection and throttling control. With the help of the second elastic member and other components, 0A protection of the moving part and damping ratio adjustment within the working range of the valve are realized, and finally the design requirements and goals of the damping valve are met. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] 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 or the description of the prior art 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 work.

[0017] Figure 1 It is a principle schematic diagram of the pilot stage spring arrangement in the undeformed state (two-valve plate type);

[0018] Figure 2 It is a principle schematic diagram of the initial deformation state of the pilot stage spring arrangement (two valve plate type);

[0019] Figure 3 It is a principle schematic diagram of the deformation state of the pilot stage spring arrangement after contacting the valve seat step (two-valve plate type);

[0020] Figure 4 It is a principle schematic diagram of the deformation state of the pilot stage spring arrangement after contacting the valve seat throttle (two valve plate type);

[0021] Figure 5 It is a principle schematic diagram of the pilot stage spring arrangement in the undeformed state (one spring type, one valve plate type);

[0022] Figure 6 It is a principle schematic diagram of the initial deformation state of the pilot stage spring arrangement (one spring type, one valve plate type);

[0023] Figure 7 It is a principle schematic diagram of the deformation state of the pilot stage spring arrangement after contacting the valve seat step (one spring type, one valve plate type);

[0024] Figure 8 It is a principle schematic diagram of the deformation state of the pilot stage spring arrangement after contacting the valve seat throttle (one spring type, one valve plate type);

[0025] Fig. 9 It is a schematic diagram of the overall structure of the shock absorber damping valve (without the solenoid);

[0026] Fig.10 is a schematic diagram of the structure of the second elastic member in the spring arrangement;

[0027] Fig.11 It is a schematic diagram of the structure of the pilot stage spring arrangement in an undeformed state;

[0028] Fig.12 It is a schematic diagram of the structure of the initial deformation state of the pilot stage spring arrangement;

[0029] Fig.13It is a structural schematic diagram of the pilot stage spring arrangement in a deformed state after contacting the valve seat step;

[0030] Fig.14 It is a structural schematic diagram of the pilot stage spring arrangement in a deformed state after contacting the throttle opening of the valve seat;

[0031] Fig.15 This is a schematic diagram of the pilot stage structure after the valve is removed;

[0032] Fig.16 is a schematic diagram of a structure in which a second elastic member is installed on a moving part;

[0033] Fig.17 The second elastic member is Fig.16 Another installation arrangement schematic diagram is shown.

[0034] In the figure, 1, pressure regulating device; 11, main valve seat; 12, main valve; 13, main spring; 15, pilot stage;

[0035] 3. Valve seat; 31. Annular step;

[0036] 4. Valve;

[0037] 5. a first elastic member;

[0038] 6. second elastic member; 61. inner ring spring piece; 611. flow hole; 62. middle ring spring piece; 63. outer ring spring piece; 64. inner ring spring piece beam; 65. outer ring spring piece beam; 66. first flow opening; 67. second flow opening;

[0039] 7. Moving parts; 71. Spring base; 72. Spring pressure seat;

[0040] 8. Drive components. DETAILED DESCRIPTION

[0041] To make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be described in detail below. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other implementation methods obtained by ordinary technicians in this field without creative work belong to the scope of protection of the present invention.

[0042] In the description of the present invention, it should be noted that, unless otherwise specified, the meaning of "plurality" is two or more; the orientations or positional relationships indicated by the terms "upper", "lower", "left", "right", "inner", "outer", "front end", "rear end", "head", "tail", etc. are based on the orientations or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", "third", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0043] In the description of the present invention, it is also necessary to explain that, unless otherwise clearly specified and limited, the terms "installation", "connection", and "connection" should be understood in a broad sense, for example, it 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. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0044] Figure 1-4 and Figure 5-8 The first and second embodiments of the present invention are respectively shown, wherein the pressure regulating device 1 is mainly used to regulate the pressures P1 to P4 of the shock absorbing damping medium flows Q1 to Q4 in the shock absorber. The pressure regulating device 1 comprises a valve seat 3, a valve 4, a moving part 7, a first elastic member 5 and a second elastic member 6, wherein the valve 4 is located in the moving part 7 and the valve 4 can move axially relative to the moving part 7, the moving part 7 is located in the valve seat 3 and the moving part 7 can move axially relative to the valve seat 3, the first elastic member 5 is arranged between the moving part 7 and the valve seat 3, the outer side of the second elastic member 6 is connected to the moving part 7, the inner side of the second elastic member 6 can contact the valve 4, and an annular step 31 is arranged on the inner side of the end of the valve seat 3, and the end of the annular step 31 can contact the middle part of the second elastic member 6.

[0045] When the pressure regulating device 1 is opened, the shock absorber oil medium flows into the variable flow opening s provided between the valve 4 and the valve seat 3 at Q1-Q4. When the medium Q increases from zero, the driving force F pushes the axially movable valve 4, and after contacting the second elastic member 6, the elastic deformation force of the second elastic member 6 acts on the moving part 7 and forms a force balance with the first elastic member 5. The driving force F in the variation range F1-F4 will affect the size of the counter-support force R1-R4 and the effect of the elastic member arrangement at different stages. Among them, the elastic member arrangement includes a first elastic member 5 with a stiffness constant k1 and a second elastic member 6 with a variable stiffness constant k2.

[0046] When the driving force F is small, the corresponding working state is shown in FIG. 1. Figure 1 When S2 ≥ 0, the total counter-support force R1 is only formed by the driving force F1 acting on the valve 4. At this time, the first elastic member 5 and the second elastic member 6 have not officially started to deform, and the valve 4 has not officially started to work.

[0047] When S2 = 0, the corresponding stroke S1 is the maximum effective stroke of valve 4. When the driving force F continues to increase, Figure 2 In the state shown, the valve 4 is in contact with the second elastic member 6, and under the series action of the moving part 7, the first elastic member 5 and the second elastic member 6 are deformed. This process always requires S4 ≥ S3. This is the first working principle of the second elastic member 6.

[0048] When the second elastic member 6 contacts the annular step 31 on the valve seat 3, the pressure regulating device 1 enters Figure 3 In the working state shown in FIG. 1 , the deformation amount of the first elastic member 5 reaches t1, and the deformation amount of the outer side of the second elastic member 6 reaches t2. As the driving force F continues to increase, the inner side of the second elastic member 6 continues to deform until reaching the value shown in FIG. Figure 4 In the position shown, the pressure regulating device 1 is completely closed, and the inner deformation of the second elastic member 6 reaches the maximum and is t3. In the entire effective stroke range of the valve 4, the first elastic member 5 and the second elastic member 6 act together, and there is no order of action.

[0049] The working range is defined by the relevant structural characteristic dimensions of the first elastic member 5, the second elastic member 6, the moving part 7 and the valve seat 3, and the deformation capacity of the first elastic member 5 and the second elastic member 6 has the largest influence. The variable flow opening s between the valve 4 and the valve seat 3 is affected by the throttle outlet flow Q and the pressure P, and there is a critical opening s'. When s ≥ s', the variable flow opening s increases, and the throttle damping no longer changes, that is, the damping opening is saturated, and s' is affected by the maximum flow Qmax.

[0050] In Figure 1-4, Figure 5-8 and Figure 11-14 In the embodiment, the driving forces F1-F4 increase sequentially, so the corresponding damping P increases sequentially. The first elastic member 5 is a spring structure or a valve plate structure, and the first elastic member 5 of FIG. 1-4 is a valve plate structure, Figure 5-8 as well as Figure 11-14 The first elastic member 5 is a spring-type structure and the second elastic member 6 is a valve plate-type structure. Figure 1 Except for / 5 / 11, the two elastic members in other figures are in a deformed working state.

[0051] The valve 4 moves axially in the valve seat 3 within the range of stroke S, and the stroke S can be divided into S1, S3 and S5. The stroke S depends on the force balance relationship acting on the valve 4, which is composed of the driving force F, the regulating device force R, the first elastic member 5, and the second elastic member 6, and will be affected by the flow Q. The stroke S1 with S2=0 can be regarded as the starting position of the total stroke, which is defined as the axial distance from the valve 4 to the throttle of the valve seat 3 when the valve 4 contacts the second elastic member 6, and the valve 4 does not start working when S2>0. When the valve 4 does not contact the second elastic member 6, it is considered that the second elastic member 6 is not activated and is in the basic position, that is, the reference zero position of the effective deformation of the spring. The minimum stiffness k2 of the second elastic member 6 with two stiffnesses is greater than the stiffness k1 of the first elastic member 5. The ratio between the stiffness constant of the first elastic member 5 and the variable stiffness constant of the second elastic member 6 is in the range of 1:10 to 1:100. In the spring arrangement, the low stiffness of the first elastic member 5 is mainly intended to achieve the return of the moving part 7, realize the 0A curve characteristics and the stability of the valve 4; the variable stiffness of the second elastic member 6 is mainly intended to achieve the opening control of the valve 4 and the valve seat 3, and ultimately realize the pressure proportional control function of the pilot stage to the main stage.

[0052] exist Figure 2 In the figure, after the driving force F2 reaches a certain value, it overcomes the regulating device force R and the spring force, so that the valve 4 is effectively displaced and approaches the valve seat 3, the variable flow opening s is reduced, and a higher regulating pressure P2 and reaction force R2 are obtained. In addition, the pressure P2 is determined by the flow Q2, and the force R2 is determined by the gradually increasing driving force F2 and the spring arrangement. The premise for meeting this condition is that the driving force F2 ≥ the resultant force of the spring arrangement.

[0053] exist Figure 3 In the embodiment, the second elastic member 6 has already contacted the annular step 31 of the valve seat 3 under the action of the driving force F3, and is configured to be externally limited. At this time, the pressure P3 formed by the flow Q3 is greater than P2, and the second elastic member 6 and the valve 4 formally enter the second stage of the second elastic member 6: the proportional adjustment stage. The deformation of the outer part of the second elastic member 6 and the deformation of the first elastic member 5 almost no longer change, and are fixed at t2 and t1 respectively.

[0054] exist Figure 4 In the figure, the valve 4 has been axially hard-limited by the throttle port of the valve seat 3, and the inner deformation of the second elastic member 6 reaches t3. At this time, the overall deformation of the second elastic member 6 reaches the maximum, that is, the deformation is t2+t3. At this time, the opening pressure of the valve 4 is used to overcome the combined force of the driving force F4 and the spring arrangement. The pressure P4 at the throttle inlet ≥ the opening pressure will cause the valve 4 to move and then open the throttle port s (s≥0).

[0055] It is worth noting that Figure 1 / 5 / 11, Figure 2 / 6 / 12, Figure 3 / 7 / 13 and Figure 4 / 8 / 14 are of the same structural form, the difference is that the implementation structure type and the specific implementation structure of the first elastic member 5 and the moving part 7 are different, and there is almost no difference other than that.

[0056] exist Figure 1-4 In the first embodiment, the first elastic member 5 and the second elastic member 6 are both valve sheet structures, which are generally manufactured by punching or etching an annular sheet less than 0.5 mm, and the greater the thickness, the greater the rigidity.

[0057] In all embodiments, the second elastic member 6 is as follows Fig.10 The valve spring shown includes an inner ring spring piece 61, a middle ring spring piece 62, an outer ring spring piece 63, an inner ring spring piece beam 64 and an outer ring spring piece beam 65. The inner ring spring piece 61, the middle ring spring piece 62 and the outer ring spring piece 63 are arranged from the inside to the outside in sequence. The inner ring spring piece 61 and the middle ring spring piece 62 are connected by the inner ring spring piece beam 64 and the inner ring spring piece 61 can move axially relative to the middle ring spring piece 62. The middle ring spring piece 62 and the outer ring spring piece 63 are connected by the outer ring spring piece beam 65 and the middle ring spring piece 62 can move axially relative to the outer ring spring piece 63.

[0058] The inner ring spring piece 61, the middle ring spring piece 62 and the outer ring spring piece 63 are all annular structures. The outer ring spring piece 63 is connected to the moving component 7. The outer ring spring piece 63 is fixed to the moving component 7 in the form of riveting deformation. The middle ring spring piece 62 can contact the annular step 31, and the inner ring spring piece 61 can contact the valve 4. The valve 4 is used to drive the axial displacement of the second elastic member 6, thereby realizing two-stage functions at different positions and forming two-stage spring stiffness within the entire working range.

[0059] There are multiple inner ring spring fragment beams 64 and outer ring spring fragment beams 65 . All inner ring spring fragment beams 64 are distributed along the circumferential direction of the inner ring spring fragment 61 , and all outer ring spring fragment beams 65 are distributed along the circumferential direction of the middle ring spring fragment 62 .

[0060] A first flow opening 66 is formed between the inner ring spring piece 61 , the middle ring spring piece 62 and two adjacent inner ring spring piece beams 64 , a second flow opening 67 is formed between the middle ring spring piece 62 , the outer ring spring piece 63 and two adjacent outer ring spring piece beams 65 , and a flow hole 611 is arranged inside the inner ring spring piece 61 .

[0061] The existence of the inner ring spring sheet beam 64 and the outer ring spring sheet beam 65 allows the spring sheets on both sides to bounce relative to each other. The first flow port 66 will have a damping effect to a certain extent, that is, it will limit the flow of oil medium entering the valve 4 cavity. The inner ring spring sheet 61 of the second elastic member 6 will rest on the step of the valve 4 that moves axially and is acted upon by the driving force F, achieving plane contact and forming a flat surface seal. And within the entire effective working area, the valve 4 and the second elastic member 6 interact and connect with each other without separation.

[0062] exist Figure 5-8 In the figure, a second embodiment is shown, in which the first elastic member 5 is changed from a valve plate type to a conventional spiral spring, one end of which abuts against the moving part 7 and the other end abuts against the valve seat 3 in a fixed position, and steps or other structural features are respectively provided for the top end of the spring to abut.

[0063] The present invention provides a shock absorber damping valve, comprising a main stage, a drive assembly 8 and a pressure regulating device 1, wherein both ends of the pressure regulating device 1 are connected to the main stage and the drive assembly 8 respectively. Fig. 9 In FIG. 1 , the entire structure of the shock absorber damping valve is shown, and the main and secondary flow passages are marked. In general, the flow Q is the active input quantity, which is passively divided into the main and secondary flows of large flow Qp and small flow Qs by the damping of the main and secondary flow passages of the shock absorber damping valve. In general, Qp is significantly greater than Qs. Under the combined action of the pressure Pin generated by the flow Q, the annular groove pressure Pp between the main valve seat 11 and the main valve 12, the rear back pressure Pb through the middle throttle hole of the main valve 12, and the main spring 13, the main flow passage gap between the main valve seat 11 and the main valve 12 increases, and the corresponding main flow Qp increases accordingly. A small part of the secondary flow Qs flows out from the side after passing through the throttle hole of the main valve 12, the throttle hole of the valve seat 3, and the throttling action of the pilot stage 15. The main function of the pilot stage 15, that is, the pressure regulating device 1, is to control the size of the pressure Pb, and then control the opening of the main valve 12, and finally form the inlet feedback pressure Pin under the active flow Q.

[0064] The damping valve is a two-stage hydraulic control valve, which is divided into a main stage and a pilot stage. The pilot stage 15 is the pressure regulating device 1 mentioned above, and the main stage is mainly composed of a main valve seat 11, a main valve 12 and a main spring 13. This means that the pressure Pin of the liquid medium that opens the main valve 12 depends on the pressure Pb at the rear end of the main valve 12, and the pressure Pb is determined by the pressure Ps generated by the small flow Qs flowing into the pilot stage 15.

[0065] Generally speaking, the control characteristics of the shock absorber damping valve are mainly reflected in the pressure Ps control of the pilot stage 15 pressure regulating device 1. This pressure is adjusted by the size of the variable flow opening between the valve 4 and the valve seat 3. In this case, the valve 4 slides in the pilot chamber. The process state is shown in Figure 11-14 .

[0066] The structure and size of the second elastic member 6, a key component of the pressure regulating device 1, need to be specially designed. The second elastic member 6 has a thin sheet structure, and the stiffness is designed by taking advantage of the elastic characteristics of the thin sheet material itself. The design requires that the spring sheet be configured with two working processes of displacement pulling and throttling damping adjustment.

[0067] Working process 1: displacement traction, that is, before the second elastic member 6 contacts the annular step 31 of the valve seat 3, the outer edge of the step of the valve 4 contacts the inner ring spring piece 61 of the second elastic member 6 under the push of the driving force F. The displacement of the valve 4 will be constrained by the deformation formed by the internal force balance of the spring arrangement, realizing the displacement traction of the constraint point, driving its deformation and movement.

[0068] Working process two: throttling damping adjustment, that is, in this stage, the second elastic member 6 has the damping capacity of regulating the pressure regulating device 1. The middle ring spring piece 62 of the second elastic member 6 contacts the annular step 31 of the valve seat 3, thereby being restricted, and the position and deformation of the outer part of the second elastic member 6 are almost fixed, while the inner part can continue to deform and displace. Under the action of the driving force F, after forming a force balance with other forces, a new valve 4 position is formed, and the oil medium flow Qs forms a feedback pressure Ps, which will indirectly affect the main stage pressure Pb, so that the main valve 12 forms a new equilibrium position, and finally transmits to the inlet pressure Pin. This process is called throttling damping adjustment of the damping valve, and its regulating effect is related to the strength of the control current. The larger the current, the greater the regulating effect, which is proportional to the current size. The input of the control current depends on the adjustment target of the damping valve. The larger the damping Pin, the greater the current input.

[0069] Fig.15 The pressure regulating device 1 shown is another arrangement, that is, the pressure regulating device 1 is cancelled. Fig.14 The middle valve 4 and the lengthened valve stem directly act on the second elastic member 6. Compared with the previous arrangement, the matching installation of the valve 4 and the moving part 7 is reduced, and the assembly difficulty is reduced.

[0070] Fig.16 and Fig.17 There are two arrangements for installing the second elastic member 6. The former is to close the edge of the movable member 7 after the second elastic member 6 is installed. This method requires closing tooling, and due to the thin wall at the closing point, the connection is additionally strengthened. The latter uses an interference fit between the spring base 71 and the spring pressure seat 72 to axially press the second elastic member 6. Compared with the former, the ease of assembly and the connection strength are improved.

[0071] When the regulating pressure is relatively low, that is, the control current is relatively small, the force balance is mainly dominated by the driving force F and the force Fs from the spring arrangement, and this dominant state is referred to as the motion state; when the regulating pressure is relatively high, that is, the control current is relatively large, the force balance is dominated by the driving force F and the anti-support force R of the valve seat 3, and this dominant state is referred to as the static state.

[0072] The outer side of the moving part 7 is matched with the radial clearance of the valve seat 3, and the inner side of the moving part 7 is matched with the clearance of the valve 4, so it is installed between the valve seat 3 and the valve 4. A step is provided for placing the first elastic member 5 and the second elastic member 6. In addition, after the second elastic member 6 is installed, it needs to be closed to fix its position to prevent the second elastic member 6 from separating from the moving part 7 during the movement. The moving part 7 is used for guiding and realizing the function of 0A protection.

[0073] The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. A pressure regulating device, characterized in that: It comprises a valve seat (3), a valve (4), a moving component (7), a first elastic member (5) and a second elastic member (6), wherein: The valve (4) is located in the movable component (7) and the valve (4) can move axially relative to the movable component (7); the movable component (7) is located in the valve seat (3) and the movable component (7) can move axially relative to the valve seat (3); the first elastic component (5) is arranged between the movable component (7) and the valve seat (3); the outer side of the second elastic component (6) is connected to the movable component (7); the inner side of the second elastic component (6) can contact the valve (4); an annular step (31) is arranged on the inner side of the end of the valve seat (3); the end of the annular step (31) can contact the middle part of the second elastic component (6).

2. The pressure regulating device according to claim 1, characterized in that: The first elastic member (5) is a spring-type structure or a valve-type structure, and the second elastic member (6) is a valve-type structure; The ratio between the stiffness constant of the first elastic member (5) and the variable stiffness constant of the second elastic member (6) is in the range of 1:10 to 1:

100.

3. The pressure regulating device according to claim 1 or 2, characterized in that: The second elastic member (6) comprises an inner ring spring piece (61), a middle ring spring piece (62), an outer ring spring piece (63), an inner ring spring piece beam (64) and an outer ring spring piece beam (65); the inner ring spring piece (61), the middle ring spring piece (62) and the outer ring spring piece (63) are arranged in sequence from the inside to the outside; the inner ring spring piece (61) and the middle ring spring piece (62) are connected via the inner ring spring piece beam (64) and the inner ring spring piece (61) can move axially relative to the middle ring spring piece (62); the middle ring spring piece (62) and the outer ring spring piece (63) are connected via the outer ring spring piece beam (65) and the middle ring spring piece (62) can move axially relative to the outer ring spring piece (63).

4. The pressure regulating device according to claim 3, characterized in that: The inner ring spring piece (61), the middle ring spring piece (62) and the outer ring spring piece (63) are all annular structures. The outer ring spring piece (63) is connected to the moving component (7), the middle ring spring piece (62) can contact the annular step (31), and the inner ring spring piece (61) can contact the valve (4).

5. The pressure regulating device according to claim 3, characterized in that: The number of the inner ring spring fragment beams (64) and the outer ring spring fragment beams (65) are both multiple, all of the inner ring spring fragment beams (64) are distributed along the circumferential direction of the inner ring spring fragment (61), and all of the outer ring spring fragment beams (65) are distributed along the circumferential direction of the middle ring spring fragment (62).

6. The pressure regulating device according to claim 3, characterized in that: A first flow opening (66) is formed between the inner ring spring piece (61), the middle ring spring piece (62) and two adjacent inner ring spring piece beams (64); a second flow opening (67) is formed between the middle ring spring piece (62), the outer ring spring piece (63) and two adjacent outer ring spring piece beams (65); and a flow hole (611) is arranged inside the inner ring spring piece (61).

7. The pressure regulating device according to claim 1, characterized in that: A variable flow opening is provided between the valve seat (3) and the valve (4).

8. A shock absorber damping valve, characterized in that: It comprises a main stage, a driving assembly (8) and a pressure regulating device (1) as claimed in any one of claims 1 to 7, wherein two ends of the pressure regulating device (1) are respectively connected to the main stage and the driving assembly (8).

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