CN111441679B - Hydraulic stepless position regulator - Google Patents
Hydraulic stepless position regulator Download PDFInfo
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- CN111441679B CN111441679B CN202010126174.8A CN202010126174A CN111441679B CN 111441679 B CN111441679 B CN 111441679B CN 202010126174 A CN202010126174 A CN 202010126174A CN 111441679 B CN111441679 B CN 111441679B
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- valve seat
- piston
- sliding sleeve
- spring
- flow port
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- 238000007789 sealing Methods 0.000 claims description 30
- 230000036961 partial effect Effects 0.000 claims description 6
- 230000003247 decreasing effect Effects 0.000 claims description 2
- 239000012530 fluid Substances 0.000 claims 1
- 238000000034 method Methods 0.000 description 11
- 230000002829 reductive effect Effects 0.000 description 4
- 101100282111 Caenorhabditis elegans gap-2 gene Proteins 0.000 description 3
- 101100121125 Drosophila melanogaster RasGAP1 gene Proteins 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000007667 floating Methods 0.000 description 3
- 238000002955 isolation Methods 0.000 description 3
- 230000002265 prevention Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
- E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
-
- E—FIXED CONSTRUCTIONS
- E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
- E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
- E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
- E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
Landscapes
- Fluid-Damping Devices (AREA)
Abstract
The invention relates to the technical field of hydraulic pressure, in particular to a hydraulic stepless position regulator, which aims to solve the technical problems that the existing hydraulic structure cannot be automatically unlocked and cannot be automatically unlocked, and the self-locking force and the movement resistance are not ideal; the piston substructure is connected to the end 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, wherein the left spring and the right spring are in a compressed state in a natural state. The hydraulic stepless position regulator provided by the invention can effectively adjust the self-locking force Fsr and effectively adjust 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, the door and window is required to stop at any angle, and when the door and window is started from a rest position, a sufficient resistance, namely, a self-locking force Fsr (wind blowing prevention, gravity load prevention, vibration impact prevention and the like) is required, and the movement resistance Fmr in the opening (closing) process is small enough.
However, the existing hydraulic structure cannot realize automatic switching between static and moving states, and the self-locking force and the moving resistance are not ideal.
Disclosure of Invention
The invention aims to provide a hydraulic stepless position regulator, which solves the technical problems that the existing hydraulic structure cannot realize automatic switching between static and moving states and the self-locking force and the movement resistance are not ideal.
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 substructure 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 in a natural state.
Still further, the method further comprises the steps of,
The piston substructure further comprises a left spring seat positioned on the left side of the valve seat piston and a right spring seat positioned 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.
Still further, the method further comprises the steps of,
The left spring seat and the right spring seat each comprise a head and a handle;
The periphery of the head part is propped against the cylinder barrel;
The handle extends from the head to the valve seat piston until the handle abuts against the valve seat piston, the handle is provided with a step structure with gradually reduced height 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.
Still further, the method further comprises the steps of,
The piston substructure further comprises a right valve seat sliding sleeve;
The right spring is abutted to the outer side of the right valve seat sliding sleeve;
the right side of the valve seat piston is provided with a first flow port, the first flow port is communicated with the left side of the valve seat piston, and the right valve seat sliding sleeve seals the first flow port in a natural state;
the 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 liquid in the first annular gap and the second annular gap forms liquid resistance.
Still further, the method further comprises the steps of,
The right valve seat sliding sleeve is sleeved in a partial area of the 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 at the bulge position.
Still further, the method further comprises the steps of,
The valve seat is characterized in that an annular groove is formed in one side, facing the valve seat piston, of the right valve seat sliding sleeve, a right sealing ring is arranged in the annular groove, and the right sealing ring is used for sealing the first flow port in a natural state.
Still further, the method further comprises the steps of,
The piston substructure further comprises a left valve seat sliding sleeve;
The left spring is abutted to the outer side of the left valve seat sliding sleeve;
the left side of the valve seat piston is provided with a second flow port, and the second flow port is communicated with the right side of the valve seat piston; the left valve seat sliding sleeve is used for sealing the second flow port in a natural state;
A third annular gap is formed 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 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 forms a fourth annular gap.
Still further, the method further comprises the steps of,
The left valve seat sliding sleeve is sleeved in a partial area of the small-diameter section of the handle part of the left spring seat, the left valve seat sliding sleeve is provided with a bulge extending leftwards, and the left spring is sleeved at the bulge position.
Still further, the method further comprises the steps of,
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 seals the second flow port in a natural state;
still further, the method further comprises the steps of,
An external 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 following outline of the technical effects that the hydraulic stepless position regulator provided by the invention can at least realize:
The hydraulic stepless positioner comprises a piston substructure which is arranged in an oil cavity in a floating mode, wherein the piston substructure 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 in a natural state, namely, in the 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.
When the axial pressure power or the thrust applied to the piston rod end causes the left oil cavity pressure or the right oil cavity pressure of the valve seat piston to rise, but the pressure is insufficient to overcome the spring force, the piston rod cannot move, the difference between the hydraulic pressure acting on the left end face and the right end face of the valve seat piston is self-locking force Fsr, and otherwise, when the axial pressure power or the thrust applied to the piston rod end causes the left oil cavity pressure or the right oil cavity pressure of the valve seat piston to rise, the pressure is sufficient to overcome the spring force, the piston rod can be compressed leftwards or stretched rightwards.
From the above analysis, it is clear that the axial compressive force or thrust force applied to the rod end first needs to overcome the spring force, that is, 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 that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of the overall structure of a hydraulic stepless positioner according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a piston sub-structure in a hydraulic stepless positioner provided by 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.
The icons are 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 sliding sleeve, 170-right valve seat sliding sleeve, 101-left sealing ring, 102-right sealing ring, 103-outer sealing ring and 104-inner sealing ring. 200-cylinder barrel, 300-piston rod, 400-isolation piston, 500-guide sealing mechanism, 001-first flow port, 002-second flow port, gap 1-first annular Gap, gap 2-second annular Gap, gap 3-third annular Gap and Gap 4-fourth annular Gap.
Detailed Description
The following description of the embodiments of the present invention will be made apparent and fully in view of the accompanying drawings, in which some, but not all embodiments of the invention are shown. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "left," "right," "third," and the like 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, unless explicitly stated or limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected, mechanically connected, electrically connected, directly connected, indirectly connected via an intervening medium, or in communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Embodiment 1 is described in detail below in conjunction with fig. 1, 2 and 3:
the present embodiment provides a hydraulic stepless positioner,
The hydraulic stepless positioner comprises a cylinder barrel 200, wherein an isolation piston 400 is arranged in the cylinder barrel 200, the inner cavity of the cylinder barrel 200 is divided into an air cavity and an oil cavity by the isolation piston 400, 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 positioner further comprises a piston substructure 100 which is arranged in the oil cavity in a floating manner, and the shape and the structure of the piston substructure 100 are described in detail below:
The piston sub-structure 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 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.
When the axial pressure force or thrust force applied to the end of the piston rod 300 causes the left or right oil chamber pressure of the valve seat piston 110 to rise, but is insufficient to overcome the spring force, the piston rod 300 cannot move, and the difference between the hydraulic forces acting on the left and right end surfaces of the valve seat piston 110 is the self-locking force Fsr, whereas when the axial pressure force or thrust force applied to the end of the piston rod 300 causes the left or right oil chamber pressure of the valve seat piston 110 to rise, the piston rod 300 can be compressed or extended to the left when the spring force is sufficient to overcome. From the above analysis, it is clear that 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.
In an alternative to this embodiment, the first and second embodiments, preferably,
The piston sub-structure 100 also 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 comprises a head portion and a handle portion, the periphery of the head portion abuts against the cylinder barrel 200, the handle portion extends from the head portion to the direction of the valve seat piston 110 to abut against the valve seat piston 110, the handle portion is provided with a step structure with gradually reduced height along the direction pointing to the valve seat piston 110, and the right spring 130 is sleeved on a large-diameter section of the handle portion.
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, the right valve seat sliding sleeve 170 is provided with a bulge extending to the right, and the right spring 130 is sleeved on the bulge.
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 port 001 in a natural state.
In an alternative to this embodiment, the first and second embodiments, preferably,
The piston sub-structure 100 also includes a left spring seat 140 and a left valve seat sliding 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 with an outer periphery abutting against the cylinder tube 200, and a shank portion extending from the head portion toward the valve seat piston 110 to abut against the valve seat piston 110, the shank portion having a stepped structure with a gradually decreasing height in a direction toward the valve seat piston 110, and the left spring 120 being fitted over a large diameter section of the shank portion.
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, the left valve seat sliding sleeve 160 is provided with a bulge extending leftwards, and the left spring 120 is sleeved on the bulge position.
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 seals the second flow port 002 in a natural state.
In an alternative to this embodiment, the first and second embodiments, preferably,
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, the right valve seat sliding sleeve 170 is used for plugging 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 Gap1, 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 forms a second annular Gap2, and oil in the first annular Gap1 and the second annular Gap2 form hydraulic resistance.
The left side of the valve seat piston 110 is provided with a second flow port 002, the second flow port 002 is communicated with the right side of the valve seat piston 110, the left valve seat sliding sleeve 160 is used for plugging the second flow port 002 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 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 Gap4.
In an alternative to this embodiment, the first and second embodiments, preferably,
An outer sealing mechanism is arranged between the valve seat piston 110 and the cylinder barrel 200, specifically, a groove is arranged on the outer peripheral surface of the valve seat piston 110, an outer sealing ring 103 is arranged in the groove, and the outer sealing ring 103 forms an outer sealing structure.
In an alternative to this embodiment, the first and second embodiments, preferably,
An inner sealing mechanism is provided between valve seat piston 110 and piston rod 300. Specifically, a groove is provided in the inner surface of valve seat piston 110, and an inner seal ring 104 is provided in the groove, and inner seal ring 104 abuts against piston rod 300 to form an inner seal mechanism.
The implementation principle of the motion resistance Fmr during the opening (closing) process is described in detail below:
when the left oil pressure of the valve seat piston 110 overcomes the spring force of the right spring 130, after pushing open the right seal ring 102, the left oil of the valve seat piston 110 flows through the first flow port 001 to the right cavity of the right valve seat sliding sleeve 170 through two annular gaps, the 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 Gap1, the 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 forms a second annular Gap2, the two gaps form a hydraulic resistance, the left oil pressure of the valve seat sliding sleeve is greater than the right oil pressure of the valve seat sliding sleeve, the left oil pressure of the valve seat sliding sleeve is greater than the spring force acting on the right end surface of the valve seat sliding sleeve, the valve seat slides rightwards, the hydraulic resistance is reduced, and finally the left oil pressure of the valve seat sliding sleeve and the spring force acting on the right end surface of the valve seat sliding sleeve are balanced, and the acting on the piston substructure 100 is the sum of the hydraulic force acting on the valve seat piston 110 and the spring force exerted on the right spring seat. This is the compression movement resistance Fmr.
When the oil pressure on the right side of the valve seat piston 110 overcomes the spring force of the second spring, after pushing 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 then flows to the left cavity of the left valve seat sliding sleeve 160 through two parts, 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. The two gaps form hydraulic resistance, the oil pressure on the right side of the valve seat sliding sleeve is larger than the oil pressure on the left side of the valve seat sliding sleeve, the oil pressure on the right side of the valve seat sliding sleeve is larger 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, the oil pressure on the right side of the valve seat sliding sleeve is balanced with the spring force acting on the left end face of the valve seat sliding sleeve finally, and the acting force acting on the piston substructure 100 is the difference between the spring force exerted on the left spring seat 140 by the second spring and the hydraulic force acting on the valve seat piston 110, namely the compression movement resistance Fmr.
In addition, it is also necessary to exchange for the explanation:
the first, left air chamber pressure provides hydraulic force on the piston rod 300 as the piston rod 300 compresses;
Secondly, the size of the self-locking force Fsr is determined by the ratio of the end surface area of the valve seat piston 110 to the area of the bulge flow port;
third, the gap and length of each annular gap, the spring force, determine the amount of movement resistance Fmr.
It should be noted that the above embodiments are merely for illustrating the technical solution of the present invention and not for limiting the same, and although the present invention has been described in detail with reference to the above embodiments, it should be understood by those skilled in the art that the technical solution described in the above embodiments may be modified or some or all of the technical features may be equivalently replaced, and these modifications or substitutions do not make the essence of the corresponding technical solution deviate from the scope of the technical solution of the embodiments of the present invention.
Claims (8)
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010126174.8A CN111441679B (en) | 2020-02-28 | 2020-02-28 | Hydraulic stepless position regulator |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010126174.8A CN111441679B (en) | 2020-02-28 | 2020-02-28 | Hydraulic stepless position regulator |
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| CN111441679A CN111441679A (en) | 2020-07-24 |
| CN111441679B true CN111441679B (en) | 2024-12-17 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113513556A (en) * | 2021-08-30 | 2021-10-19 | 潍坊晨雨机械设备有限公司 | A pressure control check valve |
| CN114856338B (en) * | 2022-04-22 | 2024-03-29 | 宁波力品格工业机械有限公司 | Stepless limiter |
| CN118958809B (en) * | 2024-09-29 | 2025-09-09 | 北京吉信气弹簧制品有限公司 | Stepless limiter and automobile |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110714678A (en) * | 2019-09-06 | 2020-01-21 | 上海湘俊气弹簧有限公司 | Hovering type bidirectional balancer with air spring structure |
| CN212359448U (en) * | 2020-02-28 | 2021-01-15 | 天津华壹永创科技合伙企业(有限合伙) | Hydraulic stepless positioner |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2523900Y (en) * | 2002-02-05 | 2002-12-04 | 肯旺车业(深圳)有限公司 | Hydraulic automatic door shutter |
| US6904643B2 (en) * | 2003-02-27 | 2005-06-14 | Tom W. Duffy | Door closer hold-open apparatus |
| DE102010022053A1 (en) * | 2009-12-01 | 2011-06-09 | Dorma Gmbh + Co. Kg | door closers |
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2020
- 2020-02-28 CN CN202010126174.8A patent/CN111441679B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110714678A (en) * | 2019-09-06 | 2020-01-21 | 上海湘俊气弹簧有限公司 | Hovering type bidirectional balancer with air spring structure |
| CN212359448U (en) * | 2020-02-28 | 2021-01-15 | 天津华壹永创科技合伙企业(有限合伙) | Hydraulic stepless positioner |
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