A damping regulating valve

Abstract

The present invention provides a damping control valve, comprising: a coil, a housing, a valve sleeve, a sealing ring, an outer valve seat, a movable valve core, a movable valve core spring, a spring seat, a slider, a valve stem, an inner valve seat, a reed, an armature spring, an armature, a ball bracket, a steel ball, and a retaining spring. The damping control valve has a simple structure and an ingenious design. Through the design of the structure and flow path of the damping control valve, only a small operating current is required to generate the driving force required to overcome the oil pressure resistance and drive the valve stem downward. The small operating current minimizes the hysteresis of the current rise from initial energization to the minimum damping operating current caused by the coil inductance suppressing current changes. Furthermore, the flow path damping of the damping control valve can be adjusted and controlled by applying a corresponding solenoid valve operating current according to different operating conditions.

Description

Technical Field

[0001] The present invention relates to the technical field of regulating valves, and in particular to a damping regulating valve with a large working flow. Background Art

[0002] Traditional vehicle shock absorbers have fixed damping characteristics, providing fixed cushioning performance during the shock absorber's expansion and contraction process, and have poor adaptability to operating conditions. With the continuous development of automotive technology, adjustable damping shock absorbers have been used in vehicles, improving vehicle comfort, maneuverability, and safety. Adjustable damping shock absorbers require a damping control valve to control the shock absorber's damping. However, existing adjustable damping control valves have complex structures, difficult damping control operations, and low damping control accuracy. Furthermore, the upper and lower axial holes of the valve stem of the current damping control valve are not connected. The electromagnetic force driving the valve stem downward must overcome not only the elastic force of the armature spring but also the oil pressure resistance in the spring seat valve hole to drive the valve stem downward. As a result, the damping control valve has a significant response hysteresis. Summary of the Invention

[0003] In view of the deficiencies in the prior art, the present invention proposes a damping regulating valve with a simple structure, high damping control accuracy and small response hysteresis.

[0004] In order to realize the above technical solution, the present invention provides a damping regulating valve, comprising: a coil, a shell, a valve sleeve, a sealing ring, an outer valve seat, a movable valve core, a movable valve core spring, a spring seat, a slider, a valve stem, an inner valve seat, a reed, an armature spring, an armature, a ball bracket, a steel ball and a retaining spring, wherein the coil is installed in the upper hole of the shell, the upper part of the valve sleeve passes through the axial hole of the shell and extends into the hole of the coil, a sealing ring mounting groove is provided on the outer side of the valve sleeve, the valve sleeve is provided with a radial flow hole communicating with the inside and outside of the valve sleeve, the sealing ring is installed in the sealing ring mounting groove on the outer side of the valve sleeve, and the outer valve seat is tightly fitted The outer valve seat is fixed to the bottom of the valve sleeve, an axial through hole is provided on the outer valve seat, a radial flow hole connecting the inner and outer sides of the outer valve seat is provided on the side of the outer valve seat, a flow notch is provided on the outer side of the outer valve seat, a moving valve core is installed in the outer valve seat, a throttle hole is provided at the axis of the bottom of the moving valve core, a moving valve core spring is installed in the inner cavity of the moving valve core, the spring seat is fixed in the axial hole of the valve sleeve with a tight fit, the slider is installed in the slider mounting hole of the spring seat, a flow hole is provided on the slider that passes through the upper and lower end faces of the slider, the bottom of the valve stem is fixed in the axial hole of the slider with a tight fit, a countersunk hole is provided at the bottom of the valve stem, and the valve stem axis is fixed in the axial hole of the slider with a tight fit. The center is provided with an axial through hole that passes through the upper and lower ends of the valve stem. The inner valve seat and the reed are installed in the stop at the lower end of the spring seat. The bottom surface of the reed rests on the top surface of the inner valve seat. The axis of the reed is provided with a through hole. The periphery of the axial hole of the reed is provided with a flow groove. An armature spring is provided on the spring seat. The upper part of the valve stem passes through the axial through hole of the spring seat and extends into the axial hole of the armature. The upper part of the valve stem is tightly fitted with the bottom axial hole of the armature. The bottom surface of the armature rests on the top surface of the armature spring. The ball bracket is fixed to the top of the armature. The axis of the ball bracket is provided with an axial through hole that passes through the upper and lower ends of the ball bracket. A steel ball that constrains the radial displacement of the top of the armature is provided between the top surface of the armature and the flange of the ball bracket. The retaining spring is clamped in the clamping groove of the coil and the clamping groove of the outer shell to fix the coil in the outer shell. An overflow gap δ1 is provided between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the movable valve core. An overflow gap δ2 is provided between the outer circle of the slider and the slider mounting hole in the spring seat. An overflow gap δ3 is provided between the bottom surface of the valve stem and the top surface of the reed. An overflow gap δ4 is provided between the top surface of the slider and the top surface of the overflow groove in the spring seat. An overflow gap δ5 is provided between the bottom surface of the slider and the bottom surface of the valve stem.

[0005] In the above technical solution, when the damping regulating valve is not energized, the elastic force of the armature spring pushes the armature upward, and the armature drives the valve stem and the slider to move upward so that the top surface of the slider rests on the top surface of the flow groove in the spring seat and closes the flow gap δ4 between the top surface of the slider and the top surface of the flow groove in the spring seat. After the oil pressure in the axial hole of the outer valve seat increases, the oil in the inner cavity of the movable valve core leaks to the oil cavity at the bottom of the shell through the bypass regulating flow channel. The throttling effect of the axial throttling hole at the bottom of the movable valve core causes a pressure difference to be generated between the inner cavity of the movable valve core and the bottom surface of the movable valve core. The axial force generated by the pressure difference acting on the movable valve core overcomes the elastic force of the movable valve core spring to push the movable valve core upward and open the gap between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the movable valve core. The high-pressure oil in the axial hole of the outer valve seat leaks from the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the movable valve core and the radial flow hole on the side of the outer valve seat to the oil chamber at the bottom of the shell. Under this working condition, the damping of the bypass regulating flow channel of the damping regulating valve is in an intermediate damping state between the minimum damping and the maximum damping. Correspondingly, the damping of the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the movable valve core is in an intermediate damping state between the minimum damping and the maximum damping. The flow gap δ3 between the bottom surface of the valve stem and the top surface of the reed decreases with the increase of the flow gap δ4 between the top surface of the slider and the top surface of the flow groove in the spring seat, showing an opposite trend. After the damping regulating valve is energized, the electromagnetic force overcomes the elastic force of the armature spring to drive the armature to drive the valve stem and the slider to move downward, thereby opening the flow gap δ4 between the top surface of the slider and the top surface of the flow groove in the spring seat, and at the same time reducing the flow gap δ3 between the bottom surface of the valve stem and the top surface of the reed. After the damping regulating valve applies the minimum damping working current, the electromagnetic force overcomes the elastic force of the armature spring to drive the armature to drive the valve stem and the slider to move downward, thereby opening the flow gap δ4 between the top surface of the slider and the top surface of the flow groove in the spring seat, and the flow cross-sectional area of ​​the additional flow channel, the flow cross-sectional area of ​​the flow gap δ2 between the outer circle of the slider and the slider mounting hole in the spring seat, and the flow cross-sectional area of ​​the flow gap δ3 between the bottom surface of the valve stem and the top surface of the reed, thereby minimizing the damping of the bypass regulating flow channel of the damping regulating valve, and the oil in the inner cavity of the moving valve core passes through The damping of the bypass regulating flow channel leaking to the oil chamber at the bottom of the shell is minimal. The throttling effect of the axial throttling hole at the bottom of the moving valve core maximizes the pressure difference between the inner cavity of the moving valve core and the bottom surface of the moving valve core, and maximizes the pressure difference acting on the inner cavity and the bottom of the moving valve core. The axial force generated by the pressure difference between the inner cavity and the bottom of the moving valve core overcomes the elastic force of the moving valve core spring to push the moving valve core upward and open the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the moving valve core to a fully open state. The damping of the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the moving valve core is in a minimum damping state. The axial through hole passing through the upper and lower ends of the valve stem and the axial through hole passing through the upper and lower ends of the ball bracket are connected to the oil chamber at the bottom of the valve stem and the oil chamber at the top of the ball bracket. The axial resultant force of the oil pressure acting on the valve stem is always zero, thereby eliminating the back pressure resistance of the valve stem movement caused by the oil pressure.

[0006] Preferably, the spring seat is provided with an axial through hole, a slider mounting hole is provided inside the spring seat, a stop is provided at the lower end of the spring seat, an inner flow groove is provided inside the spring seat, an outer flow groove is provided outside the spring seat, a radial flow hole connecting the inner and outer flow grooves is provided on the spring seat, and a countersunk hole is provided on the top surface of the inner flow groove of the spring seat.

[0007] Preferably, a throttling hole is provided at the bottom of the inner valve seat, and a countersunk hole connected to the throttling hole at the bottom of the inner valve seat is provided at the center of the top of the inner valve seat. The hole diameter of the central countersunk hole at the top of the inner valve seat is the same as the outer circle diameter of the valve stem installed in the axial through hole of the spring seat, and a flow groove is provided around the central countersunk hole at the top of the inner valve seat.

[0008] Preferably, the flow gap between the bottom surface of the valve stem and the top surface of the reed decreases as the flow gap between the top surface of the slider and the top surface of the flow groove in the spring seat increases.

[0009] Preferably, the axial throttling hole at the bottom of the moving valve core, the inner cavity of the moving valve core, the throttling hole at the bottom of the inner valve seat, the central countersunk hole at the top of the inner valve seat, the axial hole of the reed, the flow gap between the bottom surface of the valve stem and the top surface of the reed, the flow gap between the bottom surface of the slider and the bottom surface of the valve stem, the flow gap between the outer circle of the slider and the slider mounting hole in the spring seat, the inner flow groove inside the spring seat, the radial flow hole connecting the inner and outer flow grooves of the spring seat, the outer flow groove outside the spring seat, the radial flow hole connecting the inside and outside of the valve sleeve, and the flow notch on the outside of the outer valve seat constitute the bypass regulating flow channel of the damping regulating valve.

[0010] Preferably, the flow gap between the bottom surface of the slider and the bottom surface of the valve stem, the flow hole passing through the upper and lower end surfaces of the slider, the countersunk hole on the top surface of the flow groove in the spring seat at the top of the slider, and the flow gap between the top surface of the slider and the top surface of the flow groove in the spring seat to the flow groove in the spring seat constitute an additional bypass regulating flow channel.

[0011] Preferably, the slider and the valve stem are an integrated structure.

[0012] The damping control valve provided by the present invention has the following beneficial effects: The damping control valve has a simple structure and ingenious design. Through the design of the structure and flow path of the damping control valve, only a small operating current is required to generate the driving force required to overcome the oil pressure resistance to drive the valve stem downward. This small operating current reduces the hysteresis of the current rise from initial energization to the minimum damping operating current, caused by the coil inductance suppressing the current change. Furthermore, the diameter of the countersunk hole on the top surface of the flow groove in the spring seat is much larger than the stem shaft diameter of conventional damping control valves. This allows the slider of the damping control valve of the present invention to achieve a sufficiently large flow cross-sectional area of ​​the flow gap δ4 between the top surface of the slider and the top surface of the flow groove in the spring seat with a small downward movement stroke. This small movement stroke reduces the hysteresis of the moving part's motion response. The combination of the small current rise hysteresis of the applied operating current and the small motion response hysteresis of the moving part results in a small hysteresis in the energized operation of the damping control valve of the present invention. During actual operation, when the damping regulating valve is not energized, the damping of the flow channel of the damping regulating valve is in the intermediate damping state. After the minimum damping working current is applied to the damping regulating valve, the flow channel damping of the damping regulating valve is the smallest. After the maximum working current is applied to the damping regulating valve, the flow channel damping of the damping regulating valve is the largest. The flow channel damping of the damping regulating valve can be adjusted and controlled by applying the corresponding solenoid valve working current according to different working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 This is a structural view of the damping regulating valve of the present invention in the intermediate damping state.

[0014] Figure 2 This is a structural view of the spring seat of the damping regulating valve of the present invention.

[0015] Figure 3 This is a structural view of the damping regulating valve of the present invention in the minimum damping state.

[0016] Figure 4 This is a structural view of the damping regulating valve of the present invention in the maximum damping state. DETAILED DESCRIPTION

[0017] The following will provide a clear and complete description of the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. All other embodiments obtained by ordinary persons in this field without creative work are within the scope of protection of the present invention.

[0018] Embodiment: A damping regulating valve.

[0019] like Figure 1As shown, a damping regulating valve includes a coil 1, a shell 2, a valve sleeve 3, a sealing ring 4, an outer valve seat 5, a movable valve core 6, a movable valve core spring 7, a spring seat 8, a slider 9, a valve stem 10, an inner valve seat 11, a reed 12, an armature spring 13, an armature 14, a ball bracket 15, a steel ball 16 and a retaining spring 17, wherein the coil 1 is installed in the upper hole of the shell 2, the upper part of the valve sleeve 3 passes through the axial hole of the shell 2 and extends into the hole of the coil 1, a sealing ring mounting groove is provided on the outside of the valve sleeve 3, the valve sleeve 3 is provided with a radial flow hole connecting the inside and outside of the valve sleeve, the sealing ring 4 is installed in the sealing ring mounting groove on the outside of the valve sleeve 3, the outer valve seat 5 is tightly fixed to the bottom of the valve sleeve 3, the outer valve seat 5 is provided with an axial through hole, and the side of the outer valve seat 5 is provided with a hole connecting the outer valve seat Inside and outside radial flow holes, the outside of the outer valve seat 5 is provided with a flow notch, the dynamic valve core 6 is installed in the outer valve seat 5, the bottom axis of the dynamic valve core 6 is provided with a throttle hole, the dynamic valve core spring 7 is installed in the inner cavity of the dynamic valve core 6, the spring seat 8 is tightly fixed in the axial hole of the valve sleeve 3, the spring seat 8 is provided with an axial through hole 8-1, the spring seat 8 is provided with a slider mounting hole 8-2, the lower end of the spring seat 8 is provided with a stop 8-3, the spring seat 8 is provided with an inner flow groove 8-4, the spring seat 8 is provided with an outer flow groove 8-5 outside the spring seat 8, the spring seat 8 is provided with a radial flow hole 8-6 connecting the inner and outer flow grooves, the top surface of the flow groove 8-4 in the spring seat 8 is provided with a countersunk hole 8-7, the slider 9 is installed in the slider mounting hole 8-2 of the spring seat 8, and the slider 9 is provided with a stopper 8-3. A flow hole is provided through the upper and lower end surfaces of the slider 9, and the bottom of the valve stem 10 is tightly fixed in the axial hole of the slider 9. A countersunk hole is provided at the bottom of the valve stem 10, and the axis of the valve stem 10 is provided with an axial through hole through the upper and lower ends of the valve stem 10. The slider 9 and the valve stem 10 can also be an integrated structure. The inner valve seat 11 and the reed 12 are installed in the stop 8-3 at the lower end of the spring seat 8. The bottom surface of the reed 12 abuts against the top surface of the inner valve seat 11. A throttle hole 11-1 is provided at the bottom of the inner valve seat 11, and a countersunk hole 11-2 is provided at the top center of the inner valve seat 11, which is connected to the throttle hole 11-1 at the bottom of the inner valve seat 11. The hole diameter of the central countersunk hole 11-2 on the top of the inner valve seat 11 is the same as the outer diameter of the valve stem 10 installed in the axial through hole 8-1 of the spring seat 8. , a flow groove 11-3 is provided on the periphery of the central countersunk hole 11-2 at the top of the inner valve seat 11, a through hole 12-1 is provided on the axis of the reed 12, and a flow groove 12-2 is provided on the periphery of the axial hole 12-1 of the reed 12. An armature spring 13 is provided on the spring seat 8. The upper part of the valve stem 10 passes through the axial through hole 8-1 of the spring seat 8 and extends into the axial hole of the armature 14. The upper part of the valve stem 10 is tightly fitted with the bottom axial hole of the armature 14. The bottom surface of the armature 14 rests on the top surface of the armature spring 13. The ball bracket 15 is fixed to the top of the armature 14. The axis of the ball bracket 15 is provided with an axial through hole that passes through the upper and lower ends of the ball bracket 15. A steel ball 16 that constrains the radial displacement of the top of the armature 14 is provided between the top surface of the armature 14 and the flange of the ball bracket 15.The retaining spring 17 is clamped in the groove of the coil 1 and the groove of the housing 2 to fix the coil 1 in the housing 2. A flow gap δ1 is provided between the bottom surface of the inner cavity of the outer valve seat 5 and the bottom surface of the movable valve core 6. A flow gap δ2 is provided between the outer circle of the slider 9 and the slider mounting hole 8-2 in the spring seat 8. A flow gap δ3 is provided between the bottom surface of the valve stem 10 and the top surface of the reed 12. A flow gap δ4 is provided between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8. A flow gap δ5 is provided between the bottom surface of the slider 9 and the bottom surface of the valve stem 10. When the damping regulating valve is not energized, the elastic force of the armature spring 13 pushes the armature 1 upward. 4, the armature 14 drives the valve stem 10 and the slider 9 to move upward so that the top surface of the slider 9 abuts against the top surface of the flow groove 8-4 in the spring seat 8 and closes the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8, the axial throttle hole at the bottom of the movable valve core 6, the inner cavity of the movable valve core 6, the throttle hole 11-1 at the bottom of the inner valve seat 11, the central countersunk hole 11-2 at the top of the inner valve seat 11, the axial hole 12-1 of the reed 12, the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12, the flow gap δ5 between the bottom surface of the slider 9 and the bottom surface of the valve stem 10, the outer circle of the slider 9 and the slider mounting hole 8 in the spring seat 8 -2, the internal flow groove 8-4 inside the spring seat 8, the radial flow hole 8-6 connecting the internal and external flow grooves of the spring seat 8, the external flow groove 8-5 outside the spring seat 8, the radial flow holes connecting the inside and outside of the valve sleeve and the flow notch on the outside of the outer valve seat 5 constitute the bypass regulating flow channel of the damping regulating valve. After the oil pressure in the axial hole of the outer valve seat 5 increases, the oil in the inner cavity of the moving valve core 6 leaks to the oil cavity at the bottom of the shell 2 through the bypass regulating flow channel. The throttling effect of the axial throttling hole at the bottom of the moving valve core 6 generates a pressure difference between the inner cavity of the moving valve core 6 and the bottom surface of the moving valve core 6. The axial force generated by the pressure difference acting on the moving valve core 6 overcomes the The elastic force of the movable valve core spring 7 pushes the movable valve core 6 upward, opening the flow gap δ1 between the inner bottom surface of the outer valve seat 5 and the bottom surface of the movable valve core 6. The high-pressure oil in the axial hole of the outer valve seat 5 leaks through the flow gap δ1 between the inner bottom surface of the outer valve seat 5 and the bottom surface of the movable valve core 6 and the radial flow holes on the side of the outer valve seat 5 into the oil chamber at the bottom of the housing 2. Under this operating condition, the damping of the bypass regulating flow channel of the damping regulating valve is in an intermediate damping state between minimum and maximum damping. Correspondingly, the damping of the flow gap δ1 between the inner bottom surface of the outer valve seat 5 and the bottom surface of the movable valve core 6 is in an intermediate damping state between minimum and maximum damping.

[0020] like Figure 2 As shown, a damping regulating valve is provided with an axial through hole 8-1 on its spring seat 8, a slider mounting hole 8-2 is provided inside the spring seat 8, a stop 8-3 is provided at the lower end of the spring seat 8, an inner flow groove 8-4 is provided inside the spring seat 8, an outer flow groove 8-5 is provided outside the spring seat 8, a radial flow hole 8-6 connecting the inner and outer flow grooves is provided on the spring seat 8, and a countersunk hole 8-7 is provided on the top surface of the inner flow groove 8-4 of the spring seat 8.

[0021] like Figure 3As shown, a damping regulating valve is shown, in which the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12 increases and decreases with the increase of the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8, showing an opposite trend. After the damping regulating valve is energized, the electromagnetic force overcomes the elastic force of the armature spring 13 to drive the armature 14 to drive the valve stem 10 and the slider 9 to move downward, so that the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8 is opened, and at the same time, the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12 is reduced. The bypass regulating flow channel of the damping regulating valve is increased by the flow gap δ5 between the bottom surface of the slider 9 and the bottom surface of the valve stem 10, the flow hole penetrating the upper and lower end surfaces of the slider 9, and the spring seat 8 at the top of the slider 9. The countersunk hole 8-7 on the top surface of the flow groove 8-4, the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8, and the flow gap δ4 in the flow groove 8-4 in the spring seat 8 form an additional bypass regulating flow channel. After the damping regulating valve applies the minimum damping working current, the electromagnetic force overcomes the elastic force of the armature spring 13 to drive the armature 14 to drive the valve stem 10 and the slider 9 to move downward, thereby opening the additional flow channel of the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8, the flow cross-sectional area of ​​the additional flow channel, the flow cross-sectional area of ​​the flow gap δ2 between the outer circle of the slider 9 and the slider mounting hole 8-2 in the spring seat 8, and the flow cross-sectional area of ​​the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12 are equal, so that the bypass regulating valve of the damping regulating valve is closed. The damping of the throttling passage is minimal, and the damping of the oil in the inner cavity of the moving valve core 6 leaking to the oil cavity at the bottom of the housing 2 through the bypass regulating flow channel is minimal. The throttling effect of the axial throttling hole at the bottom of the moving valve core 6 maximizes the pressure difference between the inner cavity of the moving valve core 6 and the bottom surface of the moving valve core, and maximizes the pressure difference between the inner cavity and the bottom of the moving valve core 6. The axial force generated by the pressure difference between the inner cavity and the bottom of the moving valve core 6 overcomes the elastic force of the moving valve core spring 7 to push the moving valve core 6 upward and open the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat 5 and the bottom surface of the moving valve core 6 to a fully open state. The damping of the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat 5 and the bottom surface of the moving valve core 6 is in a minimum damping state. The axial through hole passing through the upper and lower ends of the valve stem 10 and the axial through hole passing through the upper and lower ends of the ball bracket 15 are connected to the valve stem 1 0 and the oil chamber at the top of the ball bracket 15. The resultant axial force exerted by the oil pressure on the valve stem 10 is always zero, eliminating the back pressure resistance to valve stem movement caused by the oil pressure. The damping control valve of the present invention only needs to apply a small operating current to obtain the driving force required to overcome the oil pressure resistance to drive the valve stem downward. The small operating current reduces the hysteresis of the current rise from initial energization to the minimum damping operating current caused by the coil inductance suppressing the current change. At the same time, the diameter of the countersunk hole 8-7 on the top surface of the flow groove 8-4 in the spring seat 8 is much larger than the valve stem shaft diameter of existing damping control valves. This allows the slider 9 of the damping control valve of the present invention to move downwardly for a sufficiently large flow cross-sectional area of ​​δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8.The small movement stroke makes the movement response hysteresis of the moving part small. The small current rise hysteresis of the applied working current and the small movement response hysteresis of the moving part make the energized operation response hysteresis of the damping control valve of the present invention small.

[0022] like Figure 4As shown, a damping regulating valve is provided. After the maximum working current is applied to the damping regulating valve, the electromagnetic force overcomes the elastic force of the armature spring 13 to drive the armature 14 to drive the valve stem 10 to move downward so that the bottom surface of the valve stem 10 is pressed against the top surface of the reed 12, thereby closing the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12. The oil in the inner cavity of the movable valve core 6 can only flow through the throttle hole 11-1 at the bottom of the inner valve seat 11, the central countersunk hole 11-2 at the top of the inner valve seat 11, the axial hole 12-1 of the reed 12, the axial through hole passing through the upper and lower ends of the valve stem 10, the axial through hole passing through the upper and lower ends of the ball bracket 15, the oil chamber at the top of the ball bracket 15, the gap between the valve sleeve 3 and the outer circle of the armature 14, the bottom of the armature 14 The bypass regulating flow channel composed of the oil chamber at the bottom of the housing 2, the sliding fit gap between the outer circle of the valve stem 10 and the axial through hole 8-1 of the spring seat 8, the countersunk hole 8-7 on the top surface of the flow groove 8-4 in the spring seat 8, the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8, the inner flow groove 8-4 inside the spring seat 8, the radial flow hole 8-6 connecting the inner and outer flow grooves of the spring seat 8, the outer flow groove 8-5 outside the spring seat 8, the radial flow hole connecting the inside and outside of the valve sleeve and the flow notch outside the outer valve seat 5, leaks to the oil chamber at the bottom of the housing 2. The sliding fit gap between the outer circle of the valve stem 10 and the axial through hole 8-1 of the spring seat 8 is small, which makes the bypass regulating flow channel of the damping regulating valve The damping of the flow channel is in the maximum damping state, the axial throttle hole at the bottom of the dynamic valve core 6 connects the inner cavity of the dynamic valve core 6 and the bottom of the dynamic valve core, so that the pressure difference between the oil pressure in the inner cavity of the dynamic valve core 6 and the oil pressure at the bottom of the dynamic valve core is small, and the downward axial force of the oil pressure on the dynamic valve core 6 is small. The downward thrust of the dynamic valve core spring 7 presses the bottom surface of the dynamic valve core 6 on the bottom surface of the inner cavity of the outer valve seat 5 and closes the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat 5 and the bottom surface of the dynamic valve core 6. The high-pressure oil in the axial hole of the outer valve seat 5 cannot leak to the oil chamber at the bottom of the shell 2 through the flow gap δ1 between the bottom surface of the inner cavity of the outer valve seat 5 and the bottom surface of the dynamic valve core 6, so that the flow channel damping of the damping regulating valve is in the maximum damping state. When the inner cavity of the outer valve seat 5 is When the oil pressure produces an instantaneous jump fluctuation, the pressure wave is transmitted to the oil chamber at the top of the ball bracket 15 through the axial throttle hole at the bottom of the movable valve core 6, the inner cavity of the movable valve core 6, the throttle hole 11-1 at the bottom of the inner valve seat 11, the central countersunk hole 11-2 at the top of the inner valve seat 11, the axial hole 12-1 of the reed 12, the axial through hole passing through the upper and lower ends of the valve stem 10, and the axial through hole passing through the upper and lower ends of the ball bracket 15. When the pressure wave reaches the central countersunk hole 11-2 at the top of the inner valve seat 11, the pressure differential axial force generated between the bottom surface of the reed 12 and the top surface of the ball bracket 15 acts on the bottom surface of the reed 12, causing the middle part of the reed 12 to deform upward, thereby opening the gap between the bottom surface of the reed 12 and the top surface of the inner valve seat 11.The high-pressure oil in the central countersunk hole 11-2 at the top of the inner valve seat 11 flows out from the gap between the bottom surface of the open reed 12 and the top surface of the inner valve seat 11, the flow groove 11-3 at the top of the inner valve seat 11, the flow groove 12-2 of the reed 12, the flow gap δ5 between the bottom surface of the slider 9 and the bottom surface of the valve stem 10, the flow holes penetrating the upper and lower end surfaces of the slider 9, the flow gap δ4 between the top surface of the slider 9 and the top surface of the flow groove 8-4 in the spring seat 8, the inner flow groove 8-4 inside the spring seat 8, and the radial flow hole 8-6 connecting the inner and outer flow grooves of the spring seat 8. The bypass regulating flow channel formed by the external flow groove 8-5 on the outside of the spring seat 8, the radial flow holes connecting the inside and outside of the valve sleeve, and the flow notch on the outside of the outer valve seat 5 leaks to the oil chamber at the bottom of the shell 2. The downward electromagnetic driving force acting on the valve stem 10 and the downward deformation elastic force generated by the upward deformation of the middle part of the reed 12 quickly reset the reed 12 and press it tightly against the top surface of the inner valve seat 11 after the pressure difference axial force between the bottom surface of the reed 12 and the top surface of the ball bracket 15 is reduced. The reed 12 is fixed around and the upward deformation of the middle part of the reed 12 is constrained. The amount of displacement of the valve stem 10 pressed against the top surface of the reed 12 due to the impact of the pressure wave is limited. The combined effect of the electromagnetic driving force and the deformation elastic force of the reed 12 makes the reed 12 reset hysteresis small. The aperture of the central countersunk hole 11-2 on the top of the inner valve seat 11 is the same as the axial diameter of the valve stem 10. The axial resultant force of the oil pressure on the valve stem 10 is zero, thereby eliminating the back pressure resistance of the valve stem movement caused by the oil pressure. The damping regulating valve can bypass the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12 with a small maximum working current. The regulating flow passage is closed. When the power is turned off from the energized state, the low operating current causes the coil inductance to suppress the current change, resulting in a small hysteresis from the operating current decreasing to zero. The elastic force of the armature spring 13 pushes the armature 14 upward, driving the valve stem 10 upward, opening the flow gap δ3 between the bottom surface of the valve stem 10 and the top surface of the reed 12, thereby opening the bypass regulating flow passage of the damping regulating valve. The hysteresis is small, which reduces the hysteresis of the damping regulating valve's power-off response. According to different operating conditions, the corresponding solenoid valve operating current can be applied to adjust the flow passage damping of the damping regulating valve.

[0023] The above description is only a preferred embodiment of the present invention, but the present invention should not be limited to the contents disclosed in the embodiment and the drawings. Therefore, any equivalent or modification completed without departing from the spirit disclosed in the present invention shall fall within the scope of protection of the present invention.

Claims

1. A damping regulating valve, characterized in that include: Coil, shell, valve sleeve, sealing ring, outer valve seat, movable valve core, movable valve core spring, spring seat, slider, valve stem, inner valve seat, reed, armature spring, armature, ball bracket, steel ball and retaining spring, wherein the coil is installed in the upper hole of the shell, the upper part of the valve sleeve passes through the axial hole of the shell and extends into the hole of the coil, a sealing ring mounting groove is provided on the outside of the valve sleeve, the valve sleeve is provided with a radial flow hole communicating with the inside and outside of the valve sleeve, the sealing ring is installed in the sealing ring mounting groove on the outside of the valve sleeve, the outer valve seat is fixed to the bottom of the valve sleeve in a tight fit, and an axial through hole is provided on the outer valve seat. The outer valve seat is provided with a radial flow hole connecting the inner and outer sides of the outer valve seat, and the outer side of the outer valve seat is provided with a flow notch. The movable valve core is installed in the outer valve seat, and the axis of the bottom of the movable valve core is provided with a throttle hole. The movable valve core spring is installed in the inner cavity of the movable valve core. The spring seat is tightly fixed in the axis hole of the valve sleeve, and the slider is installed in the slider mounting hole of the spring seat. The slider is provided with a flow hole that passes through the upper and lower end faces of the slider. The bottom of the valve stem is tightly fixed in the axis hole of the slider, and the bottom of the valve stem is provided with a countersunk hole. The axis of the valve stem is provided with an axis that passes through the upper and lower ends of the valve stem. The inner valve seat and the reed are installed in the stop at the lower end of the spring seat, the bottom surface of the reed abuts against the top surface of the inner valve seat, the axis of the reed is provided with a through hole, the outer periphery of the axis hole of the reed is provided with a flow groove, an armature spring is provided on the spring seat, the upper part of the valve stem passes through the axial through hole of the spring seat and extends into the axial hole of the armature, the upper part of the valve stem is tightly fitted with the bottom axial hole of the armature, the bottom surface of the armature abuts against the top surface of the armature spring, the ball bracket is fixed to the top of the armature, the axis of the ball bracket is provided with an axial through hole that passes through the upper and lower ends of the ball bracket, and the top surface of the armature is connected to the axial through hole of the armature. A steel ball is provided between the flanges of the ball bracket to constrain the radial displacement of the top of the armature. The retaining spring is clamped in the retaining grooves of the coil and the retaining grooves of the housing to fix the coil in the housing. An overflow gap δ1 is provided between the bottom surface of the inner cavity of the outer valve seat and the bottom surface of the movable valve core. An overflow gap δ2 is provided between the outer circle of the slider and the slider mounting hole in the spring seat. An overflow gap δ3 is provided between the bottom surface of the valve stem and the top surface of the reed. An overflow gap δ4 is provided between the top surface of the slider and the top surface of the overflow groove in the spring seat. An overflow gap δ5 is provided between the bottom surface of the slider and the bottom surface of the valve stem. The spring seat is provided with an axial through hole, a slider mounting hole is provided inside the spring seat, a stop is provided at the lower end of the spring seat, an inner flow groove is provided inside the spring seat, an outer flow groove is provided outside the spring seat, a radial flow hole connecting the inner and outer flow grooves is provided on the spring seat, and a countersunk hole is provided on the top surface of the inner flow groove of the spring seat; A throttling hole is provided at the bottom of the inner valve seat, and a countersunk hole connected to the throttling hole at the bottom of the inner valve seat is provided at the center of the top of the inner valve seat. The diameter of the central countersunk hole at the top of the inner valve seat is the same as the outer diameter of the valve stem installed in the axial through hole of the spring seat, and a flow groove is provided around the central countersunk hole at the top of the inner valve seat.

2. The damping regulating valve according to claim 1, characterized in that: The flow gap between the bottom surface of the valve stem and the top surface of the reed is reduced as the flow gap between the top surface of the slider and the top surface of the flow groove in the spring seat increases.

3. The damping regulating valve according to claim 2, characterized in that: The axial throttle hole at the bottom of the moving valve core, the inner cavity of the moving valve core, the throttle hole at the bottom of the inner valve seat, the central countersunk hole on the top of the inner valve seat, the axial hole of the reed, the flow gap between the bottom surface of the valve stem and the top surface of the reed, the flow gap between the bottom surface of the slider and the bottom surface of the valve stem, the flow gap between the outer circle of the slider and the slider mounting hole in the spring seat, the inner flow groove inside the spring seat, the radial flow hole connecting the inner and outer flow grooves of the spring seat, the outer flow groove outside the spring seat, the radial flow holes connecting the inside and outside of the valve sleeve and the flow notch on the outside of the outer valve seat constitute the bypass regulating flow channel of the damping regulating valve.

4. The damping regulating valve according to claim 3, characterized in that: The flow gap between the bottom surface of the slider and the bottom surface of the valve stem, the flow hole running through the upper and lower end surfaces of the slider, the countersunk hole on the top surface of the flow groove in the spring seat at the top of the slider, and the flow gap between the top surface of the slider and the top surface of the flow groove in the spring seat to the flow groove in the spring seat constitute an additional bypass regulating flow channel.

5. The damping regulating valve according to claim 1, characterized in that: The slider and the valve stem are an integrated structure.

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