Feedback type pressure adjusting device

Abstract

The invention provides a feedback type pressure adjusting device. The feedback type pressure adjusting device comprises an armature assembly, a power supply assembly and a valve seat. The armature assembly comprises a shell, a movable iron core, a push rod and a pin. The power supply assembly is powered on, magnetic force is generated in the armature assembly, the magnetic force controls the movable iron core to do axial movement along the shell, the movable iron core drives the push rod to approach or make contact with the end face of the valve seat, the pressure of the pilot cavity is increased, meanwhile, a pin is used for being in small clearance fit with the movable iron core, and therefore the valve seat can be opened or closed. Oil pressure of the pilot cavity is introduced into the first high-pressure cavity of the magnetic circuit, a small pilot feedback area is formed, and pilot-level pressure control and adjustment are achieved. The device is simple in structure and easy to prepare, and the preparation cost is reduced. Furthermore, the precise control of the fluid flow can be realized by controlling the pressure of the pilot cavity, so that the damping effect of the damper is more stable.

Description

Technical Field

[0001] This invention relates to the field of hydraulic or pneumatic control design, and in particular to a feedback pressure regulating device. Background Technology

[0002] In the field of hydraulic or pneumatic control, achieving high pressure or flow control usually requires controlling or adjusting the pressure and flow damping effect of the pilot chamber based on the amplification principle of the pilot device. This adjustment device can reduce the demand on the output force of the electromagnetic device, that is, to achieve higher pressure and flow control with a smaller electromagnetic force device.

[0003] One application of this type of hydraulic or pneumatic regulating device is in vibration damper applications. By adjusting the relationship between the flow rate of the fluid flowing through the proportional valve and the residual pressure difference, i.e., the damping characteristics, the vibration damper can be adjusted to meet different operating conditions. This application, similar to a proportional relief valve, requires a large pressure and flow rate, and needs to meet the stable damping force output requirements of the vibration damper. That is, without increasing the electromagnetic force, the effective feedback area of ​​the pilot stage needs to be very small to achieve the pressure amplification effect.

[0004] To achieve pressure amplification, prior art (CN102803782A) discloses a pressure regulator; please refer to that. Figure 1 This pressure regulator uses a relatively long armature rod with a bearing sleeve at each end to guide and introduce the high-pressure channel, and uses additional sealing gaskets to seal the high-pressure oil. However, this pressure regulator has a complex structure, many parts, and a complicated assembly process, resulting in high production costs. Summary of the Invention

[0005] The purpose of this invention is to provide a feedback pressure regulating device that achieves pressure amplification effect using a simpler and easier-to-manufacture structure, thereby reducing manufacturing costs.

[0006] The armature assembly includes: a housing, a moving iron core, a push rod, and a pin;

[0007] The moving iron core is placed inside the housing and can reciprocate axially along the housing. The push rod is fixed in the moving iron core. A first flow gap is provided inside the push rod.

[0008] The pin and the moving iron core are fitted with a clearance, and the pin can reciprocate axially along the moving iron core.

[0009] The valve seat is provided with a pilot chamber;

[0010] When the power supply component is powered on, a magnetic force is generated in the armature assembly. The magnetic force controls the moving iron core to move axially along the housing. The moving iron core drives the push rod to approach or contact the end face of the valve seat, thereby controlling and adjusting the pilot chamber pressure. The pilot chamber pressure is transmitted along the first flow gap to the first end face of the pin, forming a first high-pressure chamber between the pin and the push rod.

[0011] Furthermore, the armature assembly also includes a magnetic coil, which is fixed inside the housing and has a clearance fit with the outer circle of the push rod.

[0012] Furthermore, a second flow gap is formed between the pin and the moving iron core; a third flow gap is provided inside or on the side of the moving iron core; and a fourth flow gap is formed between the magnetic ring and the push rod.

[0013] Furthermore, the size of the second flow gap is 0-0.05 mm.

[0014] Furthermore, the armature assembly also includes a first elastic element disposed between the valve seat and the push rod.

[0015] Furthermore, when the power supply component is powered on, the push rod contacts the first elastic element, causing the first elastic element to undergo axial elastic deformation toward the valve seat and approach or contact the end face of the valve seat.

[0016] Furthermore, stepped protrusions are respectively provided on both sides of the outer circle of the bottom of the push rod near the valve seat end face; when the power supply component is powered on, the stepped protrusions and the push rod approach or contact the valve seat end face.

[0017] Furthermore, the first elastic element and the second elastic element are leaf springs or coil springs.

[0018] Furthermore, the power supply component includes a coil disposed within the housing.

[0019] Furthermore, a second low-pressure cavity is formed between the moving iron core, the pin, and the housing; a third low-pressure cavity is formed between the moving iron core and the magnetic ring.

[0020] Furthermore, a fourth low-pressure chamber is provided between the outer edge of the valve seat end face, the housing, and the leaf spring.

[0021] Compared with the prior art, the present invention has at least the following technical effects:

[0022] The feedback pressure regulating device provided by this invention includes an armature assembly comprising a housing, a moving iron core, a push rod, and a pin. After power is supplied to the armature assembly, the moving iron core is controlled to reciprocate axially along the housing. The moving iron core drives the push rod to approach or contact the valve seat, thereby controlling and regulating the pilot stage pressure. The pilot chamber oil pressure is introduced into the first high-pressure chamber of the magnetic circuit through a first flow gap, forming a smaller pilot feedback area and amplifying the pressure in the pilot chamber. This device has a simple structure, is easy to manufacture, and reduces manufacturing costs.

[0023] Furthermore, the present invention reduces the pressure in the first high-pressure chamber and the leakage of fluid by using a small gap between the pin and the moving iron core, thereby maintaining the pressure in the feedback pressure regulating device.

[0024] Furthermore, the present invention achieves precise control of fluid flow rate by controlling the pressure in the pilot chamber, thereby making the damping effect of the damper more stable. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of a pressure regulator;

[0026] Figure 2 This is a schematic diagram of the feedback pressure regulating device in this invention;

[0027] Figure 3 This is another structural schematic diagram of the feedback pressure regulating device in this invention;

[0028] Figure 4 This is another structural schematic diagram of the feedback pressure regulating device in this invention. Detailed Implementation

[0029] The following description, in conjunction with schematic diagrams, illustrates a feedback pressure regulating device of the present invention, which represents a preferred embodiment. It should be understood that those skilled in the art can modify the invention described herein while still achieving its advantageous effects. Therefore, the following description should be understood as being of general knowledge to those skilled in the art and is not intended to limit the invention.

[0030] The invention is described more specifically by way of example in the following paragraphs with reference to the accompanying drawings. The advantages and features of the invention will become clearer from the following description. It should be noted that the drawings are in a very simplified form and use non-precise proportions, and are only used to facilitate and clarify the illustration of the embodiments of the invention.

[0031] Please refer to Figures 1-3 This embodiment provides a feedback pressure regulating device, including: an armature assembly, a power supply assembly, and a valve seat 7.

[0032] The armature assembly includes: a housing 1, a moving iron core 3, a push rod 4, and a pin 2.

[0033] The moving iron core 3 is fixed inside the housing 1, the push rod 4 is fixed in the moving iron core 3, and the push rod can move axially along the housing;

[0034] The pin 2 and the moving iron core 3 are fitted with a small gap, the size of which is 0-0.05mm; the pin 2 can move axially relative to the moving iron core 1.

[0035] The two ends of the first elastic element are fixed inside the housing 1 on both sides, between the valve seat 7 and the moving iron core.

[0036] The valve seat 7 is provided with a pilot cavity R1.

[0037] When the power supply component is powered on, the generated magnetic force controls the moving iron core 3 to move axially along the housing 1. The moving iron core 3 drives the push rod 4 to approach or contact the end face of the valve seat 7, controlling and adjusting the pressure of the pilot chamber R1. The pilot chamber pressure is transmitted along the first flow gap to the first end face 12 of the pin 2, forming a first high-pressure chamber between the pin 2 and the push rod 4.

[0038] It is understandable that the clearance between pin 2 and moving iron core 3 in this embodiment can also be set according to the actual situation.

[0039] In this example, two moving iron cores 3 are included, and a push rod 4 is fixed between the two moving iron cores 3. When the power supply component is powered on, a magnetic field is generated. Under the action of magnetic force, the moving iron core 3 can move axially in the housing 11 along the direction of the housing 1 toward the valve seat 7, which drives the push rod 4 to move axially in the direction of the valve seat 7, controls and adjusts the pilot cavity pressure, and makes the pilot cavity pressure transmitted along the first flow gap to the first end face 12 of the pin 2, forming a first high pressure cavity R2 between the pin 2 and the push rod 4.

[0040] In one specific example, the power supply component is a coil 8, which is disposed inside the housing.

[0041] In summary, after the power supply component is powered on, it provides magnetic force to the armature assembly, controlling the moving iron core 3 to move axially along the housing 1. The moving iron core 3 drives the push rod 4 to approach or contact the valve seat 7, realizing the control and adjustment of the pilot stage pressure. After the pilot cavity pressure is transmitted to the first end face of the pin 2 along the first flow gap, a first high-pressure cavity R2 is formed between the pin 2 and the push rod 4. The small clearance fit between the pin 2 and the moving iron core 3 reduces the pressure leakage of the first high-pressure cavity R1 introduced into the magnetic circuit by the pilot cavity oil pressure, forming a smaller pilot feedback area A2, thereby amplifying the pressure of the pilot cavity R1. Moreover, the device has a simple structure, is easy to manufacture, and reduces manufacturing costs.

[0042] Furthermore, the armature assembly also includes a first elastic element. When the power supply assembly is powered on, the push rod 4 contacts the first elastic element, causing the first elastic element to undergo axial elastic deformation toward the valve seat 7, approaching or contacting the end face of the valve seat 7.

[0043] Alternatively, stepped protrusions 11 can be provided on both sides of the outer circle of the bottom of the push rod 4 near the end face of the valve seat 7. When the power supply component is powered on, the stepped protrusions 11 and one end face of the push rod 4 approach or contact the end face of the valve seat. At the same time, the stepped protrusions 11 and one end face of the push rod 4 are in contact with the end face of the valve seat, which can increase the contact area and thus improve the sealing performance and stability of the device.

[0044] In one specific example, the first elastic element is a leaf spring 6, but elastic elements made of different materials can also be selected according to the actual situation, such as a coil spring.

[0045] Furthermore, the armature assembly in this invention also includes a magnetic coil 5, which is located between the moving iron core 3 and the first elastic element.

[0046] In one specific example, two magnetic coils 5 are included, with each side of the outer circumference of the push rod 4 respectively fitted with one of the magnetic coils 5 with a clearance. The magnetic coils 5 are used to generate a magnetic field, thereby forming a magnetic force to control the movement of the moving iron core 3 and the push rod 4.

[0047] Furthermore, the armature assembly of the present invention also includes a second elastic element, which is disposed on both sides of the push rod 4 and between the magnetic coil 5 and the moving iron core 3.

[0048] In this example, when the magnetic force fails, the second elastic element pushes the moving iron core 3 to move axially away from the valve seat 7. The moving iron core 3 drives the push rod 4 and pin 2 to retract in the same direction, so that the push rod 4 no longer contacts the surface of the leaf spring 6, or so that the push rod 4 and the stepped protrusion 11 no longer contact the end face of the valve seat.

[0049] In one specific example, the second elastic element is spring 10. Elastic elements made of different materials can also be selected according to actual needs, such as helical springs.

[0050] Furthermore, a second flow gap is formed between the pin 2 and the moving iron core 3; a third flow gap is provided inside or on the side of the moving iron core 3; and a fourth flow gap is formed between the magnetic ring 5 and the push rod 4.

[0051] In this example, the push rod 4 has a through hole inside, thereby forming a first flow gap; the outer circle of the pin 2 and the inner hole of the moving iron core 3 form a second flow gap; the moving iron core 3 has a through hole inside (or both moving iron cores can have through holes), thereby forming a third flow gap; the inner hole of the magnetic ring 5 and the outer circle of the push rod 4 form a fourth flow gap.

[0052] In one specific example, the second flow gap is smaller than the first flow gap, the third flow gap, and the fourth flow gap, in order to control fluid leakage and reduce leakage of pressure in the first high-pressure chamber R2.

[0053] Furthermore, in this example, a certain distance is provided between the pin 1 and the push rod 4 to form a first high-pressure chamber R2. When the first elastic element undergoes axial deformation toward the valve seat 7, and the distance between it and the valve seat 7 decreases, the pressure in the pilot chamber R1 increases, and the pressure in the first high-pressure chamber R2 also increases. Furthermore, a second low-pressure chamber R3 is formed between the moving iron core 3 and the pin 1, and a third low-pressure chamber R4 is formed between the moving iron core 3 and the magnetic ring 5. A fourth low-pressure chamber R5 is also included between the valve seat 7, the housing 1, and the leaf spring 6. The second low-pressure chamber R3, the third low-pressure chamber R4, and the fourth low-pressure chamber R5 are still at low pressure. At this time, the force on the leaf spring 6 is P1*(A1-A2)+Fs=Fm, where P1 is the pressure in the pilot chamber R1, A1 is the magnetic circuit feedback area, which is the area of ​​the top end face of the push rod, A2 is the pilot feedback area, Fs is the deformation spring force of the leaf spring 6, and Fm is the electromagnetic force.

[0054] By calculating the force on the leaf spring 6, the degree of deformation of the leaf spring 6 is determined, thereby achieving accurate control of the pressure in the pilot chamber R1 of the valve seat 7.

[0055] When coil 8 is energized, the fluid flows through pilot cavity R1, sequentially into the first flow gap, the first high-pressure cavity R2, the second flow gap, the second low-pressure cavity R3, the third flow gap, the third low-pressure cavity R4, and the fourth flow gap, before flowing into the fourth low-pressure cavity R5. Since pilot cavity R1 and the first high-pressure cavity R2 are at high pressure, and the second low-pressure cavity R3, the third low-pressure cavity R4, and the fourth low-pressure cavity R5 are all at low pressure, precise control of the fluid flow rate can be achieved by controlling the pressure in pilot cavity R1, thereby making the damping effect of the damper more stable.

[0056] In summary, this embodiment achieves pilot stage pressure control and regulation by having the moving iron core 3 drive the push rod 4 to approach or contact the valve seat end face. After the pilot chamber pressure is transmitted along the first flow gap to the first end face of the pin 2, a first high-pressure chamber R2 is formed between the pin 2 and the push rod 4. The small clearance between the pin 2 and the moving iron core 3 reduces pressure leakage from the pilot chamber oil pressure introduced into the magnetic circuit's first high-pressure chamber R1, resulting in a smaller pilot feedback area A2 and amplifying the pilot chamber pressure. This device has a simple structure, is easy to manufacture, and reduces manufacturing costs. Furthermore, this feedback pressure regulating device has fewer sliding moving parts, optimizing friction and increasing the robustness of pressure amplification and damping regulation performance.

[0057] Furthermore, by controlling the pressure in the pilot chamber R1, precise control of the fluid flow rate can be achieved, thereby making the damping effect of the damper more stable.

[0058] Obviously, those skilled in the art can make various modifications and variations to this invention without departing from its spirit and scope. Therefore, if these modifications and variations fall within the scope of the claims of this invention and their equivalents, this invention also intends to include these modifications and variations.

Claims

1. A feedback pressure regulating device, characterized in that, include: Armature assembly, power supply assembly, and valve seat; The armature assembly includes: a housing, a moving iron core, a push rod, and a pin; The moving iron core is placed inside the housing and can reciprocate axially along the housing. The push rod is fixed in the moving iron core. A first flow gap is provided inside the push rod. The pin and the moving iron core are fitted with a clearance, and the pin can reciprocate axially along the moving iron core. The valve seat is provided with a pilot chamber; When the power supply component is powered on, a magnetic force is generated in the armature assembly. The magnetic force controls the moving iron core to move axially along the housing. The moving iron core drives the push rod to approach or contact the end face of the valve seat, thereby controlling and adjusting the pilot chamber pressure. The pilot chamber pressure is transmitted along the first flow gap to the first end face of the pin, forming a first high-pressure chamber between the pin and the push rod.

2. The feedback pressure regulating device as described in claim 1, characterized in that, The armature assembly also includes a magnetic coil, which is fixed inside the housing and has a clearance fit with the outer circle of the push rod.

3. The feedback pressure regulating device as described in claim 2, characterized in that, A second flow gap is formed between the pin and the moving iron core; a third flow gap is provided inside or on the side of the moving iron core; a fourth flow gap is formed between the magnetic ring and the push rod.

4. The feedback pressure regulating device as described in claim 3, characterized in that, The size of the second flow gap is 0-0.05 mm.

5. The feedback pressure regulating device as described in claim 1, characterized in that, The armature assembly further includes a first elastic element disposed between the valve seat and the push rod.

6. The feedback pressure regulating device as described in claim 5, characterized in that, When the power supply component is powered on, the push rod contacts the first elastic element, causing the first elastic element to undergo axial elastic deformation toward the valve seat, approaching or contacting the end face of the valve seat.

7. The feedback pressure regulating device as described in claim 1, characterized in that, The bottom of the push rod is provided with stepped protrusions on both sides of the outer circle near the valve seat end face; when the power supply component is powered on, the stepped protrusions and the push rod approach or contact the valve seat end face.

8. The feedback pressure regulating device as described in claim 1, characterized in that, The armature assembly further includes a second elastic element, which is respectively disposed on both sides of the outer circle of the push rod, between the magnetic ring and the moving iron core.

9. The feedback pressure regulating device as described in claim 5 or 8, characterized in that, The first elastic element and the second elastic element are leaf springs or helical springs.

10. The feedback pressure regulating device as described in claim 1, characterized in that, The power supply component includes a coil disposed within the housing.

11. The feedback pressure regulating device as described in claim 1, characterized in that, A second low-pressure cavity is formed between the moving iron core, the pin, and the housing; a third low-pressure cavity is formed between the moving iron core and the magnetic ring.

12. The feedback pressure regulating device as described in claim 1, characterized in that, A fourth low-pressure chamber is also provided between the outer edge of the valve seat end face, the housing, and the leaf spring.

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