CN212359448U - Hydraulic stepless positioner - Google Patents
Hydraulic stepless positioner Download PDFInfo
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- CN212359448U CN212359448U CN202020224415.8U CN202020224415U CN212359448U CN 212359448 U CN212359448 U CN 212359448U CN 202020224415 U CN202020224415 U CN 202020224415U CN 212359448 U CN212359448 U CN 212359448U
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Abstract
本实用新型涉及液压技术领域，尤其是涉及一种液压无级调位器，以解决现有的液压结构不能自动解锁，不能自动开锁，自锁力和运动阻力均不够理想的技术问题，该液压无级调位器包括浮动设置于油腔内的活塞子结构；活塞子结构连接于活塞杆端部，包括阀座活塞、设置于阀座活塞左侧的左弹簧和设置于阀座活塞右侧的右弹簧；左弹簧和右弹簧在自然状态下处于压缩状态。本实用新型提供的液压无级调位器有效调整自锁力Fsr，有效调整运动阻力Fmr。
The utility model relates to the technical field of hydraulics, in particular to a hydraulic stepless positioner, which solves the technical problems that the existing hydraulic structure cannot be automatically unlocked, cannot be automatically unlocked, and the self-locking force and movement resistance are not ideal. The stepless positioner includes a piston substructure floating in the oil cavity; 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 side of the valve seat piston. the right spring; the left and right springs are naturally compressed. The hydraulic stepless positioner provided by the utility model can effectively adjust the self-locking force Fsr and the movement resistance Fmr.
Description
Technical Field
The invention relates to the technical field of hydraulic pressure, in particular to a hydraulic stepless position regulator.
Background
In many door and window opening and closing system designs, it is required that the door and window can be stopped at any angle, a sufficient resistance, i.e., a self-locking force Fsr (wind-proof, anti-gravity load, anti-vibration impact, etc.) is required when the door and window is started from a rest position, and a movement resistance Fmr during opening (closing) is sufficiently small.
However, the existing hydraulic structure can not realize automatic switching between static and moving states, and self-locking force and movement resistance are not ideal.
Disclosure of Invention
The invention aims to provide a hydraulic stepless position regulator to solve the technical problems that the existing hydraulic structure cannot realize automatic switching between a static state and a moving state, and self-locking force and moving resistance are not ideal enough.
In order to solve the technical problems, the technical scheme provided by the invention is as follows:
a hydraulic stepless position regulator comprises a piston substructure which is arranged in an oil cavity in a floating manner;
the piston plug structure is connected to the end part of the piston rod and comprises 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 under a natural state.
Further, in the present invention,
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.
Further, in the present invention,
the left spring seat and the right spring seat each comprise a head and a shank;
the periphery of the head part is abutted against the cylinder barrel;
the handle part extends from the head part to the direction of the valve seat piston to abut against the valve seat piston, the handle part is provided with a step structure with the height gradually reduced along the direction pointing to the valve seat piston, and the left spring and the right spring are sleeved on the large-diameter section of the handle part.
Further, in the present invention,
the piston substructure further comprises a right valve seat sliding sleeve;
the right spring is abutted against the outer side of the right valve seat sliding sleeve;
a first flow port is formed in 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;
a gap between the outer circular surface of the valve seat piston and the large inner circular surface of the valve seat sliding sleeve forms a first annular gap;
a second annular gap is formed by a gap between the small inner circular surface of the valve seat sliding sleeve and the outer sliding sleeve part of the right spring seat;
and oil in the first annular gap and the second annular gap forms a liquid resistance.
Further, in the present invention,
the right valve seat sliding sleeve is sleeved in a partial area of a small-diameter section of the handle of the right spring seat, the right valve seat sliding sleeve is provided with a bulge extending to the right side, and the right spring is sleeved in the bulge.
Further, in the present invention,
the valve seat piston is arranged on the valve seat piston, an annular groove is formed in one side, facing the valve seat sliding sleeve, of the right valve seat sliding sleeve, a right sealing ring is arranged in the annular groove, and the right sealing ring blocks the first flow port in a natural state.
Further, in the present invention,
the piston substructure further comprises a left valve seat sliding sleeve;
the left spring is abutted against the outer side of the left valve seat sliding sleeve;
a second flow port is formed in the left side of the valve seat piston and 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;
a third annular gap is formed by a gap between the outer circular surface of the valve seat piston and the large inner circular surface of the left valve seat sliding sleeve,
and a fourth annular gap is formed by a gap between the small inner circular surface of the left valve seat sliding sleeve and the part of the left spring seat rod part extending into the left valve seat sliding sleeve.
Further, in the present invention,
the left valve seat sliding sleeve is sleeved in a partial area of a small-diameter section of the handle part of the left spring seat, the left valve seat sliding sleeve is provided with a bulge extending towards the left side, and the left spring is sleeved in the bulge.
Further, in the present invention,
an annular groove is formed in one side, facing the valve seat piston, of the left valve seat sliding sleeve, a left sealing ring is arranged in the annular groove, and the left sealing ring blocks the second flow port in a natural state;
further, in the present invention,
an outer sealing mechanism is arranged between the valve seat piston and the cylinder barrel;
an inner sealing mechanism is arranged between the valve seat piston and the piston rod.
The technical effects that the hydraulic stepless position regulator provided by the invention can at least realize are briefly described as follows:
the invention provides a hydraulic stepless position regulator, which comprises a piston substructure, wherein the piston substructure is arranged in an oil cavity in a floating manner and comprises a valve seat piston, a left spring and a right spring, the left spring is arranged on the left side of the valve seat piston, the right spring is arranged on the right side of the valve seat piston, the left spring and the right spring are in a compression state in a natural state, namely, in the natural state, the left spring applies a right elastic force pointing to the valve seat piston, and the right spring applies a left elastic force pointing to the valve seat piston.
When the axial pressure force or thrust applied to the piston rod end causes the pressure of the left oil chamber or the right oil chamber of the valve seat piston to rise but is not enough to overcome the spring force, the piston rod cannot move, and the difference of the hydraulic forces acting on the left end surface and the right end surface of the valve seat piston is self-locking force Fsr; conversely, when the axial compression force or thrust applied to the rod end of the piston causes the left chamber pressure or the right chamber pressure of the valve seat piston to rise enough to overcome the spring force, the piston rod can be compressed leftwards or extended rightwards.
From the above analysis, it can be seen that the axial compressive or thrust force applied to the rod end first needs to overcome the spring force, i.e., the spring effectively increases the self-locking force Fsr.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
Fig. 1 is a schematic overall structural diagram of a hydraulic stepless position regulator provided in an embodiment of the present invention;
FIG. 2 is a schematic diagram of a piston substructure in a hydraulic stepless positioner according to an embodiment of the present invention;
fig. 3 is a schematic position diagram 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 according to an embodiment of the present invention.
Icon: 100-piston substructure; 110-valve seat piston; 120-left spring; 130-right spring; 140-left spring seat; 150-a right spring seat; 160-left valve seat sliding sleeve; 170-right valve seat sliding sleeve; 101-left sealing ring; 102-right sealing ring; 103-an outer sealing ring; 104-inner seal ring. 200-a cylinder barrel; 300-a piston rod; 400-isolating piston; 500-a guide sealing mechanism; 001-first flow port; 002-a second flow port; gap1 — first annular Gap; gap2 — second annular Gap; gap 3-third annular Gap; gap 4-fourth annular Gap.
Detailed Description
The technical solutions of the present invention will be described clearly and completely with reference to the accompanying drawings, and it should be understood that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "left", "right", "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Embodiment 1 is described in detail below with reference to fig. 1, 2 and 3:
the present embodiment provides a hydraulic stepless position regulator,
the hydraulic stepless position regulator comprises a cylinder barrel 200, wherein an isolation piston 400 is arranged in the cylinder barrel 200, the isolation piston 400 divides an inner cavity of the cylinder barrel 200 into an air cavity and an oil cavity, a piston rod 300 extends into the oil cavity from the end part of the oil cavity, and a guide sealing mechanism 500 sleeved on the piston rod 300 is arranged at the end part of the oil cavity, which is positioned in the oil cavity.
The hydraulic stepless position regulator also comprises a piston substructure 100 which is arranged in an oil cavity in a floating way, and the shape and the structure of the piston substructure 100 are explained in detail as follows:
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;
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 an elastic force directed to the right of the valve seat piston 110, and the right spring 130 applies an elastic force directed to the left of the valve seat piston 110.
When the axial pressure force or thrust applied to the end of the piston rod 300 causes the left oil chamber pressure or the right oil chamber pressure of the valve seat piston 110 to rise but is not enough to overcome the spring force, the piston rod 300 cannot move, and the difference between the hydraulic forces acting on the left end surface and the right end surface of the valve seat piston 110 is the self-locking force Fsr; conversely, when the axial compression force or thrust applied to the end of the piston rod 300 causes the left or right chamber pressure of the valve seat piston 110 to rise sufficiently to overcome the spring force, the piston rod 300 can be compressed to the left or extended to the right. From the above analysis, it can be seen that the axial compressive or pushing force applied to the end of the piston rod 300 first needs to overcome the spring force, i.e., the spring effectively increases the self-locking force Fsr.
In an alternative to this embodiment, it is preferable that,
the piston sub-structure 100 further includes a right spring seat 150 and a right valve seat sliding sleeve 170;
the right spring seat 150 is sleeved on the piston rod 300 and is positioned on the right side of the valve seat piston 110; the right spring seat 150 includes a head portion and a shank portion, and the outer periphery of the head portion abuts against the cylinder tube 200; the handle extends from the head to the valve seat piston 110 to abut against the valve seat piston 110, and the handle has a step structure with a height gradually decreasing along the direction pointing to the valve seat piston 110, and the right spring 130 is sleeved on the large diameter section of the handle.
The right valve seat sliding sleeve 170 is sleeved on a partial area of the small diameter section of the handle part of the right spring seat 150, the right valve seat sliding sleeve 170 is provided with a bulge extending towards the right side, and the right spring 130 is sleeved at the bulge position.
An annular groove is formed in one side, facing the valve seat piston 110, of the right valve seat sliding sleeve 170, a right sealing ring 102 is arranged in the annular groove, and the right sealing ring 102 seals the first flow opening 001 in a natural state.
In an alternative to this embodiment, it is preferable that,
the piston substructure 100 further includes a left spring seat 140 and a left sliding seat sleeve 160;
the left spring seat 140 is sleeved on the piston rod 300 and is positioned on the left side of the valve seat piston 110;
the left spring seat 140 includes a head portion and a shank portion, and the outer periphery of the head portion abuts against the cylinder tube 200; the handle extends from the head to the valve seat piston 110 to abut against the valve seat piston 110, and the handle has a step structure with a height gradually decreasing along the direction pointing to the valve seat piston 110, and the left spring 120 is sleeved on the large-diameter section of the handle.
The left valve seat sliding sleeve 160 is sleeved on a partial area of the small diameter section of the handle part of the left spring seat 140, the left valve seat sliding sleeve 160 is provided with a bulge extending towards the left side, and the left spring 120 is sleeved on the bulge.
An annular groove is formed in one side, facing the valve seat piston 110, of the left valve seat sliding sleeve 160, a left sealing ring 101 is arranged in the annular groove, and the left sealing ring 101 blocks the second flow port 002 in a natural state.
In an alternative to this embodiment, it is preferable that,
the right side of the valve seat piston 110 is provided with a first flow port 001, the first flow port 001 is communicated with the left side of the valve seat piston 110, and the right valve seat sliding sleeve 170 blocks the first flow port 001 in a natural state; a Gap between the outer circular surface of the valve seat piston 110 and the large inner circular surface of the valve seat sliding sleeve forms a first annular Gap 1; a second annular Gap2 is formed by a Gap between the small inner circular surface of the valve seat sliding sleeve and the outer sliding sleeve part of the right spring seat 150; the oil in the first and second annular gaps Gap1 and Gap2 forms a hydraulic resistance.
A second flow port 002 is formed in 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 sliding 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 sliding sleeve 160 forms a third annular Gap3, and the Gap between the small inner circular surface of the left valve seat sliding sleeve 160 and the part of the rod part of the left spring seat 140 extending into the left valve seat sliding sleeve 160 forms a fourth annular Gap 4.
In an alternative to this embodiment, it is preferable that,
an outer sealing mechanism is arranged between the valve seat piston 110 and the cylinder barrel 200; specifically, a groove is provided in the outer peripheral surface of the valve seat piston 110, an outer seal ring 103 is provided in the groove, and the outer seal ring 103 forms an outer seal structure.
In an alternative to this embodiment, it is preferable that,
an internal sealing mechanism is arranged between the valve seat piston 110 and the piston rod 300. Specifically, a groove is provided in the inner surface of the valve seat piston 110, an inner seal 104 is provided in the groove, and the inner seal 104 abuts against the piston rod 300 to form an inner seal mechanism.
The following describes in detail the realization principle of the movement resistance Fmr during opening (closing):
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 the right sealing ring 102 open, the oil on the left side of the valve seat piston 110 flows through the first flow port 001, divided into two parts, and flows to the cavity on the right side of the right valve seat sliding sleeve 170 through two annular gaps, and a first annular Gap1 is formed by a Gap between the outer circular surface of the valve seat piston 110 and the large inner circular surface of the valve seat sliding sleeve; a second annular Gap2 is formed by a Gap between the small inner circular surface of the valve seat sliding sleeve and the outer sliding sleeve part of the right spring seat 150; the two gaps form a liquid resistance, the oil pressure on the left side of the valve seat sliding sleeve is greater than that on the right side of the valve seat sliding sleeve, the oil pressure on the left side of the valve seat sliding sleeve is greater than the spring force acting on the right end face of the valve seat sliding sleeve, the valve seat sliding sleeve slides rightwards, the liquid resistance is reduced, finally, the oil pressure on the left side of the valve seat sliding sleeve is balanced with the spring force acting on the right end face of the valve seat sliding sleeve, and the acting force acting on the piston substructure 100 at the moment is the sum of the hydraulic force acting on the. This is the compressive resistance Fmr.
When the right oil pressure of the valve seat piston 110 overcomes the spring force of the second spring, and pushes the left sealing ring 101 open, the left oil of the valve seat piston 110 flows through the second flow port 002 and then flows into the left cavity of the left valve seat sliding sleeve 160 through two annular gaps, a Gap between the outer circular surface of the valve seat piston 110 and the large inner circular surface of the left valve seat sliding sleeve 160 forms a third annular Gap3, and a Gap between the small inner circular surface of the left valve seat sliding sleeve 160 and the part of the rod part of the left spring seat 140 extending into the left valve seat sliding sleeve 160 forms a fourth annular Gap. The two gaps form a hydraulic resistance, the pressure of the right-side oil of the valve seat sliding sleeve is greater than that of the left-side oil of the valve seat sliding sleeve, the pressure of the right-side oil of the valve seat sliding sleeve is greater than the spring force acting on the left end face of the valve seat sliding sleeve, the valve seat sliding sleeve slides leftwards, the hydraulic resistance is reduced, finally, the pressure of the right-side oil of the valve seat sliding sleeve is balanced with the spring force acting on the left end face of the valve seat sliding sleeve, and the acting force acting on the piston substructure 100 at the moment is the difference between the spring force applied to the left spring seat 140.
In addition, it is also necessary to give an alternative explanation that:
the first and left air chamber pressures provide hydrodynamic forces acting on the piston rod 300 when the piston rod 300 is compressed;
secondly, the spring force and the ratio of the area of the end surface of the valve seat piston 110 to the area of the convex flow opening determine the self-locking force Fsr;
thirdly, the gap and length of each annular gap, and the magnitude of the spring force, determine the magnitude of the motion resistance Fmr.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention, and not to limit the same; while the invention has been described in detail and with reference to the foregoing embodiments, it will be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and the modifications or the substitutions do not make the essence of the corresponding technical solutions depart from the scope of the technical solutions of the embodiments of the present invention.
Claims (10)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020224415.8U CN212359448U (en) | 2020-02-28 | 2020-02-28 | Hydraulic stepless positioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202020224415.8U CN212359448U (en) | 2020-02-28 | 2020-02-28 | Hydraulic stepless positioner |
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| CN212359448U true CN212359448U (en) | 2021-01-15 |
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| CN202020224415.8U Withdrawn - After Issue CN212359448U (en) | 2020-02-28 | 2020-02-28 | Hydraulic stepless positioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111441679A (en) * | 2020-02-28 | 2020-07-24 | 天津华壹永创科技合伙企业(有限合伙) | Hydraulic stepless positioner |
-
2020
- 2020-02-28 CN CN202020224415.8U patent/CN212359448U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111441679A (en) * | 2020-02-28 | 2020-07-24 | 天津华壹永创科技合伙企业(有限合伙) | Hydraulic stepless positioner |
| CN111441679B (en) * | 2020-02-28 | 2024-12-17 | 北京吉信气弹簧制品有限公司 | Hydraulic stepless position regulator |
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