Hydraulic stepless positioner

Abstract

The present invention relates to the field of hydraulic technology, and in particular to a hydraulic stepless positioner to solve the technical problems that the existing hydraulic structure cannot automatically unlock, cannot automatically open, and the self-locking force and movement resistance are not ideal. The hydraulic stepless positioner includes a piston substructure floatingly arranged in an oil chamber; the piston substructure is connected to the end of the piston rod, including a valve seat piston, a left spring arranged on the left side of the valve seat piston, and a right spring arranged on the right side of the valve seat piston; the left spring and the right spring are in a compressed state in a natural state. The hydraulic stepless positioner provided by the present invention effectively adjusts the self-locking force Fsr and the movement resistance Fmr.

Description

Technical Field

[0001] The invention relates to the field of hydraulic technology, and in particular to a hydraulic stepless positioner. Background Art

[0002] In the design of many door and window opening and closing systems, it is required that the doors and windows can stop at any angle, and a sufficiently large resistance, namely the self-locking force Fsr (to prevent wind, gravity load, vibration and impact, etc.) is required when starting from a static position, and the motion resistance Fmr during the opening (closing) process is small enough.

[0003] However, the existing hydraulic structure cannot realize automatic switching between static and moving states, and the self-locking force and movement resistance are not ideal. Summary of the invention

[0004] The purpose of the present invention is to provide a hydraulic stepless positioner to solve the technical problems that the existing hydraulic structure cannot realize automatic switching between static and moving states, and the self-locking force and movement resistance are not ideal.

[0005] In order to solve the above technical problems, the technical solution provided by the present invention is:

[0006] A hydraulic stepless positioner, comprising a piston substructure floatingly arranged in the oil chamber;

[0007] The piston substructure is connected to the end of the piston rod, and includes a valve seat piston, a left spring arranged on the left side of the valve seat piston, and a right spring arranged on the right side of the valve seat piston;

[0008] The left spring and the right spring are in a compressed state in a natural state.

[0009] Furthermore,

[0010] The piston substructure further includes a left spring seat located on the left side of the valve seat piston and a right spring seat located on the right side of the valve seat piston;

[0011] The left spring is sleeved on the left spring seat, and the right spring is sleeved on the right spring seat.

[0012] Furthermore,

[0013] The left spring seat and the right spring seat each include a head and a handle;

[0014] The outer periphery of the head abuts against the cylinder;

[0015] The handle extends from the head toward the valve seat piston until it abuts against the valve seat piston, and the handle has a step structure with a height gradually decreasing along the direction pointing to the valve seat piston. The left spring and the right spring are both mounted on the large diameter section of the handle.

[0016] Furthermore,

[0017] The piston substructure also includes a right valve seat sliding sleeve;

[0018] The right spring abuts against the outer side of the right valve seat sliding sleeve;

[0019] A first flow port is provided on the right side of the valve seat piston, the first flow port is communicated with the left side of the valve seat piston, and the right valve seat sliding sleeve blocks the first flow port in a natural state;

[0020] The gap between the outer circumferential surface of the valve seat piston and the large inner circumferential surface of the valve seat sleeve constitutes a first annular gap;

[0021] The gap between the small inner circular surface of the valve seat sliding sleeve and the outer sliding sleeve portion of the right spring seat forms a second annular gap;

[0022] The oil in the first annular gap and the second annular gap forms a fluid resistance.

[0023] Furthermore,

[0024] The right valve seat sliding sleeve is sleeved on a partial area of ​​the small diameter section of the handle of the right spring seat, and the right valve seat sliding sleeve has a protrusion extending to the right side, and the right spring is sleeved on the protrusion position.

[0025] Furthermore,

[0026] An annular groove is arranged on one side of the right valve seat sliding sleeve facing the valve seat piston, a right sealing ring is arranged in the annular groove, and the right sealing ring blocks the first flow port in a natural state.

[0027] Furthermore,

[0028] The piston substructure also includes a left valve seat sliding sleeve;

[0029] The left spring abuts against the outer side of the left valve seat sliding sleeve;

[0030] A second flow port is provided on the left side of the valve seat piston, and the second flow port is communicated with the right side of the valve seat piston; the left valve seat sliding sleeve blocks the second flow port in a natural state;

[0031] The gap between the outer cylindrical surface of the valve seat piston and the large inner cylindrical surface of the left valve seat sleeve forms a third annular gap.

[0032] The gap between the small inner circular surface of the left valve seat sliding sleeve and the portion of the left spring seat rod portion extending into the left valve seat sliding sleeve constitutes a fourth annular gap.

[0033] Furthermore,

[0034] The left valve seat sliding sleeve is sleeved on a partial area of ​​the small diameter section of the handle of the left spring seat, and the left valve seat sliding sleeve has a protrusion extending to the left side, and the left spring is sleeved on the protrusion position.

[0035] Furthermore,

[0036] An annular groove is provided on one side of the left valve seat sliding sleeve facing the valve seat piston, a left sealing ring is provided in the annular groove, and the left sealing ring blocks the second flow port in a natural state;

[0037] Furthermore,

[0038] An external sealing mechanism is provided between the valve seat piston and the cylinder;

[0039] An inner sealing mechanism is arranged between the valve seat piston and the piston rod.

[0040] The following briefly describes the technical effects that can be achieved by the hydraulic stepless positioner provided by the present invention:

[0041] The hydraulic stepless positioner provided by the present invention includes a piston substructure floatingly arranged in an oil chamber, the piston substructure includes a valve seat piston, a left spring arranged on the left side of the valve seat piston and a right spring arranged on the right side of the valve seat piston, the left spring and the right spring are in a compressed state in a natural state, that is, in a natural state, the left spring applies an elastic force pointing to the right of the valve seat piston, and the right spring applies an elastic force pointing to the left of the valve seat piston.

[0042] When the axial compressive force or thrust applied to the piston rod end causes the pressure in the left or right oil chamber of the valve seat piston to increase, but it is not enough to overcome the spring force, the piston rod cannot move. At this time, the difference in liquid pressure acting on the left and right end surfaces of the valve seat piston is the self-locking force Fsr; conversely, when the axial compressive force or thrust applied to the piston rod end causes the pressure in the left or right oil chamber of the valve seat piston to increase, which is enough to overcome the spring force, the piston rod can be compressed to the left or extended to the right.

[0043] From the above analysis, it can be seen that the axial compressive force or thrust applied to the piston rod end first needs to overcome the spring force, that is to say, the spring effectively increases the self-locking force Fsr. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0045] Figure 1 A schematic diagram of the overall structure of a hydraulic stepless positioner provided in an embodiment of the present invention;

[0046] Figure 2 A schematic diagram of a piston substructure in a hydraulic stepless positioner provided in an embodiment of the present invention;

[0047] Figure 3 A schematic diagram of the positions of a first annular gap, a second annular gap, a third annular gap and a fourth annular gap in a piston substructure in a hydraulic stepless positioner provided in an embodiment of the present invention.

[0048] Icon: 100-piston substructure; 110-valve seat piston; 120-left spring; 130-right spring; 140-left spring seat; 150-right spring seat; 160-left valve seat sleeve; 170-right valve seat sleeve; 101-left sealing ring; 102-right sealing ring; 103-outer sealing ring; 104-inner sealing ring. 200-cylinder; 300-piston rod; 400-isolation piston; 500-guide sealing mechanism; 001-first flow port; 002-second flow port; Gap1-first annular gap; Gap2-second annular gap; Gap3-third annular gap; Gap4-fourth annular gap. DETAILED DESCRIPTION

[0049] The technical solution of the present invention will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0050] In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship 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 "left", "right", and "third" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance.

[0051] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" 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 it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0052] Combine the following Figure 1 , Figure 2 and Figure 3 Embodiment 1 is described in detail:

[0053] This embodiment provides a hydraulic stepless positioner.

[0054] The hydraulic stepless positioner includes a cylinder 200, in which an isolation piston 400 is arranged. The isolation piston 400 divides the inner cavity of the cylinder 200 into an air cavity and an oil cavity. The piston rod 300 extends into the oil cavity from the end of the oil cavity, and a guide sealing mechanism 500 is arranged at the end of the oil cavity located in the oil cavity and is mounted on the piston rod 300.

[0055] The hydraulic stepless positioner also includes a piston substructure 100 that is floatingly disposed in the oil chamber. The shape and structure of the piston substructure 100 are described in detail below:

[0056] The piston substructure 100 is connected to the end of the piston rod 300, and includes a valve seat piston 110, a left spring 120 disposed on the left side of the valve seat piston 110, and a right spring 130 disposed on the right side of the valve seat piston 110;

[0057] The left spring 120 and the right spring 130 are in a compressed state in a natural state. That is, in a natural state, the left spring 120 applies a rightward elastic force directed toward the valve seat piston 110, and the right spring 130 applies a leftward elastic force directed toward the valve seat piston 110.

[0058] When the axial compressive force or thrust applied to the end of the piston rod 300 causes the pressure of the left or right oil chamber of the valve seat piston 110 to increase, but it is not enough to overcome the spring force, the piston rod 300 cannot move. At this time, the difference in the liquid pressure acting on the left and right end surfaces of the valve seat piston 110 is the self-locking force Fsr; conversely, when the axial compressive force or thrust applied to the end of the piston rod 300 causes the pressure of the left or right oil chamber of the valve seat piston 110 to increase, which is enough to overcome the spring force, the piston rod 300 can be compressed to the left or stretched to the right. From the above analysis, it can be seen that since the axial compressive force or thrust applied to the end of the piston rod 300 first needs to overcome the spring force, that is, the spring effectively increases the self-locking force Fsr.

[0059] In the optional solutions of this embodiment, it is more preferred that:

[0060] The piston substructure 100 further includes a right spring seat 150 and a right valve seat sliding sleeve 170;

[0061] The right spring seat 150 is sleeved on the piston rod 300 and is located on the right side of the valve seat piston 110; the right spring seat 150 includes a head and a handle, and the outer periphery of the head abuts against the cylinder 200; the handle extends from the head toward the valve seat piston 110 until it abuts against the valve seat piston 110, and the handle has a step structure with a height gradually decreasing in the direction pointing to the valve seat piston 110, and the right spring 130 is sleeved on the large diameter section of the handle.

[0062] The right valve seat sliding sleeve 170 is sleeved on a partial area of ​​the small diameter section of the handle of the right spring seat 150 , and the right valve seat sliding sleeve 170 has a protrusion extending to the right side, and the right spring 130 is sleeved on the protrusion.

[0063] An annular groove is provided on one side of the right valve seat sleeve 170 facing the valve seat piston 110 , and a right sealing ring 102 is provided in the annular groove. The right sealing ring 102 blocks the first flow port 001 in a natural state.

[0064] In the optional solutions of this embodiment, it is more preferred that:

[0065] The piston substructure 100 further includes a left spring seat 140 and a left valve seat sliding sleeve 160;

[0066] The left spring seat 140 is mounted on the piston rod 300 and is located on the left side of the valve seat piston 110;

[0067] The left spring seat 140 includes a head and a handle, the outer periphery of the head abuts against the cylinder 200; the handle extends from the head toward the valve seat piston 110 until it abuts against the valve seat piston 110, and the handle has a step structure with a height gradually decreasing in the direction pointing to the valve seat piston 110, and the left spring 120 is mounted on the large diameter section of the handle.

[0068] The left valve seat sliding sleeve 160 is sleeved on a partial area of ​​the small diameter section of the handle of the left spring seat 140 , and the left valve seat sliding sleeve 160 has a protrusion extending to the left side, and the left spring 120 is sleeved on the protrusion.

[0069] An annular groove is provided on one side of the left valve seat sleeve 160 facing the valve seat piston 110 , and a left sealing ring 101 is provided in the annular groove. The left sealing ring 101 blocks the second flow port 002 in a natural state.

[0070] In the optional solutions of this embodiment, it is more preferred that:

[0071] A first flow port 001 is provided on the right side of the valve seat piston 110, and the first flow port 001 is communicated with the left side of the valve seat piston 110, and the right valve seat sleeve 170 blocks the first flow port 001 in a natural state; the gap between the outer circular surface of the valve seat piston 110 and the large inner circular surface of the valve seat sleeve constitutes a first annular gap Gap1; the gap between the small inner circular surface of the valve seat sleeve and the outer sleeve part of the right spring seat 150 constitutes a second annular gap Gap2; the oil in the first annular gap Gap1 and the second annular gap Gap2 forms a liquid resistance.

[0072] A second flow port 002 is provided on the left side of the valve seat piston 110, and the second flow port 002 is communicated with the right side of the valve seat piston 110; the left valve seat sleeve 160 blocks the second flow port 002 in a natural state; the gap between the outer circular surface of the valve seat piston 110 and the large inner circular surface of the left valve seat sleeve 160 constitutes a third annular gap Gap3, and the gap between the small inner circular surface of the left valve seat sleeve 160 and the part of the rod of the left spring seat 140 extending into the left valve seat sleeve 160 constitutes a fourth annular gap Gap4.

[0073] In the optional solutions of this embodiment, it is more preferred that:

[0074] An external sealing mechanism is provided between the valve seat piston 110 and the cylinder 200 ; specifically, a groove is provided on the outer peripheral surface of the valve seat piston 110 , and an external sealing ring 103 is provided in the groove, and the external sealing ring 103 forms an external sealing structure.

[0075] In the optional solutions of this embodiment, it is more preferred that:

[0076] An inner sealing mechanism is provided between the valve seat piston 110 and the piston rod 300. Specifically, a groove is provided on the inner surface of the valve seat piston 110, and an inner sealing ring 104 is provided in the groove. The inner sealing ring 104 abuts against the piston rod 300 to form an inner sealing mechanism.

[0077] The following is a detailed introduction to the realization principle of the motion resistance Fmr during the opening (closing) process:

[0078] When the oil pressure on the left side of the valve seat piston 110 overcomes the spring force of the right spring 130 and pushes open the right sealing ring 102, the oil on the left side of the valve seat piston 110 flows through the first flow port 001 and is divided into two parts and flows through two annular gaps to the right cavity of the right valve seat sleeve 170. The gap between the outer cylindrical surface of the valve seat piston 110 and the large inner cylindrical surface of the valve seat sleeve constitutes the first annular gap Gap1; the gap between the small inner cylindrical surface of the valve seat sleeve and the outer sleeve part of the right spring seat 150 constitutes the second annular gap Gap2. The two gaps form a hydraulic resistance, the oil pressure on the left side of the valve seat sleeve is greater than the oil pressure on the right side of the valve seat sleeve, the oil pressure on the left side of the valve seat sleeve is greater than the spring force acting on the right end face of the valve seat sleeve, the valve seat sleeve slides to the right, the hydraulic resistance decreases, and finally the oil pressure on the left side of the valve seat sleeve and the spring force acting on the right end face of the valve seat sleeve are balanced. At this time, the force acting on the piston substructure 100 is the sum of the hydraulic force acting on the valve seat piston 110 and the spring force applied by the right spring 130 on the right spring seat. This is the compression motion resistance Fmr.

[0079] When the oil pressure on the right side of the valve seat piston 110 overcomes the spring force of the second spring and pushes open the left sealing ring 101, the oil on the left side of the valve seat piston 110 flows through the second flow port 002 and is divided into two parts and flows through two annular gaps to the left cavity of the left valve seat sleeve 160. The gap between the outer circular surface of the valve seat piston 110 and the large inner circular surface of the left valve seat sleeve 160 constitutes the third annular gap Gap3, and the gap between the small inner circular surface of the left valve seat sleeve 160 and the part of the left spring seat 140 rod extending into the left valve seat sleeve 160 constitutes the fourth annular gap. The two gaps form liquid resistance, and the oil pressure on the right side of the valve seat sleeve is greater than the oil pressure on the left side of the valve seat sleeve. The oil pressure on the right side of the valve seat sleeve is greater than the spring force acting on the left end face of the valve seat sleeve. The valve seat sleeve slides to the left, and the liquid resistance decreases. Finally, the oil pressure on the right side of the valve seat sleeve is balanced with the spring force acting on the left end face of the valve seat sleeve. At this time, the force acting on the piston substructure 100 is the difference between the spring force applied by the second spring on the left spring seat 140 and the liquid force acting on the valve seat piston 110, which is the compression motion resistance Fmr.

[0080] In addition, it is necessary to explain:

[0081] First, the pressure in the left air chamber provides the hydraulic force acting on the piston rod 300 when the piston rod 300 is compressed;

[0082] Second, the size of the spring force, the ratio of the end surface area of ​​the valve seat piston 110 to the convex flow port area, determines the size of the self-locking force Fsr;

[0083] Third, the gap and length of each annular gap and the size of the spring force determine the size of the motion resistance Fmr.

[0084] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A hydraulic stepless positioner, It is characterized in that It includes a piston substructure that is floatingly arranged in the oil chamber; The piston substructure is connected to the end of the piston rod, and includes a valve seat piston, a left spring arranged on the left side of the valve seat piston, and a right spring arranged on the right side of the valve seat piston; The left spring and the right spring are in a compressed state in a natural state; The piston substructure further includes a left spring seat located on the left side of the valve seat piston and a right spring seat located on the right side of the valve seat piston; The left spring is sleeved on the left spring seat, and the right spring is sleeved on the right spring seat; The left spring seat and the right spring seat each include a head and a handle; The outer periphery of the head abuts against the cylinder; The handle extends from the head toward the valve seat piston until it abuts against the valve seat piston, and the handle has a step structure with a height gradually decreasing in the direction pointing to the valve seat piston, and the left spring and the right spring are both sleeved on the large diameter section of the handle; The piston substructure also includes a right valve seat sliding sleeve; The right spring abuts against the outer side of the right valve seat sliding sleeve; The piston substructure also includes a left valve seat sliding sleeve; The left spring abuts against the outer side of the left valve seat sliding sleeve.

2. The hydraulic stepless positioner according to claim 1, It is characterized in that A first flow port is provided on the right side of the valve seat piston, the first flow port is communicated with the left side of the valve seat piston, and the right valve seat sliding sleeve blocks the first flow port in a natural state; The gap between the outer circumferential surface of the valve seat piston and the large inner circumferential surface of the valve seat sleeve constitutes a first annular gap; The gap between the small inner circular surface of the right valve seat sliding sleeve and the outer sliding sleeve portion of the right spring seat forms a second annular gap; The oil in the first annular gap and the second annular gap forms a fluid resistance.

3. The hydraulic stepless positioner according to claim 2, It is characterized in that The right valve seat sliding sleeve is sleeved on a partial area of ​​the small diameter section of the handle of the right spring seat, and the right valve seat sliding sleeve has a protrusion extending to the right side, and the right spring is sleeved on the protrusion.

4. The hydraulic stepless positioner according to claim 3, It is characterized in that An annular groove is arranged on one side of the right valve seat sliding sleeve facing the valve seat piston, a right sealing ring is arranged in the annular groove, and the right sealing ring blocks the first flow port in a natural state.

5. The hydraulic stepless positioner according to claim 4, It is characterized in that A second flow port is provided on the left side of the valve seat piston, and the second flow port is communicated with the right side of the valve seat piston; the left valve seat sliding sleeve blocks the second flow port in a natural state; The gap between the outer cylindrical surface of the valve seat piston and the large inner cylindrical surface of the left valve seat sleeve constitutes a third annular gap. The gap between the small inner circular surface of the left valve seat sliding sleeve and the portion of the left spring seat rod portion extending into the left valve seat sliding sleeve constitutes a fourth annular gap.

6. The hydraulic stepless positioner according to claim 5, It is characterized in that The left valve seat sliding sleeve is sleeved on a partial area of ​​the small diameter section of the handle of the left spring seat, and the left valve seat sliding sleeve has a protrusion extending to the left side, and the left spring is sleeved on the protrusion.

7. The hydraulic stepless positioner according to claim 6, It is characterized in that An annular groove is arranged on one side of the left valve seat sliding sleeve facing the valve seat piston, a left sealing ring is arranged in the annular groove, and the left sealing ring blocks the second flow port in a natural state.

8. The hydraulic stepless positioner according to any one of claims 1 to 7, It is characterized in that An external sealing mechanism is provided between the valve seat piston and the cylinder; An inner sealing mechanism is arranged between the valve seat piston and the piston rod.

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