CN111271334B - Hydraulic valve with bidirectional braking buffering and oil supplementing functions - Google Patents
Hydraulic valve with bidirectional braking buffering and oil supplementing functions Download PDFInfo
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- CN111271334B CN111271334B CN202010303037.7A CN202010303037A CN111271334B CN 111271334 B CN111271334 B CN 111271334B CN 202010303037 A CN202010303037 A CN 202010303037A CN 111271334 B CN111271334 B CN 111271334B
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- valve
- valve core
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- main valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a hydraulic valve with two-way braking buffering and oil supplementing functions, which comprises a valve block and two one-way overflow valves, wherein the two one-way overflow valves are arranged on the valve block and have the same components and symmetrical structural layout; the invention has simple structure and convenient processing, and is mainly used for overload overflow protection and reverse oil supplement protection caused by inertia effect when the hydraulic cylinder brakes positively and reversely.
Description
Technical Field
The invention relates to the technical field of pressure control elements of hydraulic systems, in particular to a hydraulic valve with bidirectional braking buffering and oil supplementing functions, which is mainly used for overload overflow protection and reverse oil supplementing protection caused by inertia effect when a hydraulic cylinder brakes in the forward and reverse directions.
Background
In the process of pushing the load to move by the hydraulic cylinder, if braking is carried out under the conditions of heavy load and high running speed, the load can drive the piston of the hydraulic cylinder to continuously move forwards due to the inertia effect, so that the pressure in one cavity of the hydraulic cylinder is suddenly increased, a high pressure peak value is generated, and the instantaneous pressure impact can not only cause vibration and noise, but also damage a sealing device, a pipeline and a hydraulic element; the effective acting area of the other cavity of the hydraulic cylinder is increased, but because the oil supply is stopped, the cavity forms negative pressure, and cavitation is caused.
Therefore, in order to avoid the above situation, it is necessary to smoothly change the hydraulic cylinder from the moving state to the stationary state in response to the abnormally high pressure and the negative pressure occurring in the oil passage.
Disclosure of Invention
Aiming at the problems, the invention provides the hydraulic valve with the functions of bidirectional braking buffering and oil supplementing, which is mainly used for overload overflow protection and reverse oil supplementing protection caused by inertia effect when the hydraulic cylinder brakes forwards and backwards.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a hydraulic valve with two-way brake buffering and oil supplementing functions comprises a valve block, and a one-way overflow valve I and a one-way overflow valve II which are arranged on the valve block, have the same components and are symmetrical in structural layout;
the valve block is in a cuboid shape, and a first oil port, a second oil port, a third oil port and a fourth oil port are formed in the valve block;
the one-way overflow valve I comprises a valve sleeve, an adjusting screw, a first locking nut, a main valve core, a first spring, a clamp spring, a one-way valve core, an adjusting nut and a second locking nut;
wherein the valve sleeve is fixed in the valve block in a thread fit mode, the adjusting screw is fixed in the valve sleeve in a thread fit mode, the first locking nut is connected to the outer peripheral surface of the adjusting screw in a threaded fit manner, one end of the main valve core extends into the blind hole of the adjusting screw and is positioned by the first spring, the other end of the main valve core extends into the valve sleeve, can move in the valve sleeve and is limited by the clamp spring, the one-way valve core is positioned in the main valve core hole, can move in the main valve core, the contact surface of the right end of the one-way valve core and the main valve core is a conical surface, the adjusting nut is connected to the left end of the one-way valve core in a threaded fit mode, a second spring with weak elasticity is arranged between the adjusting nut and the main valve core, and the second locking nut is connected to the outer peripheral face of the valve sleeve in a threaded fit mode.
Preferably, a first sealing ring and a second sealing ring are installed between the valve block and the valve sleeve, the first sealing ring adopts a combination mode of an O-shaped ring and a rubber check ring, and the second sealing ring is an O-shaped ring.
Preferably, a third sealing ring is installed between the valve sleeve and the adjusting screw, a fourth sealing ring is installed between the valve sleeve and the main valve element, a fifth sealing ring is installed between the main valve element and the one-way valve element, and the third sealing ring, the fourth sealing ring and the fifth sealing ring are all sliding sealing rings.
Preferably, the main valve core is provided with a radial hole b and a radial hole c, and the radial hole b is communicated with the first oil port through the hole in the main valve core and the internal passage of the valve block.
Preferably, the valve sleeve is provided with a radial hole d, and the radial hole d is communicated with the third oil port through the valve block passage.
Preferably, a cavity a is formed between the main valve element and the check valve element, the effective acting area of the check valve element can be changed by changing the size of the cavity a, and in addition, the cavity a is communicated with a radial hole c on the main valve element.
In a preferable scheme, the adjusting screw is provided with an inner hexagonal hole.
The invention has simple structure and convenient processing, and is mainly used for overload overflow protection and reverse oil supplement protection caused by inertia effect when the hydraulic cylinder brakes positively and reversely.
Drawings
FIG. 1 is a schematic structural diagram of an embodiment of the present invention;
fig. 2 is an application example of the embodiment of the present invention.
Detailed Description
In order to facilitate an understanding of the invention, the invention is described in more detail below with reference to the accompanying drawings and specific examples. Preferred embodiments of the present invention are shown in the drawings. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete.
The invention is further described below with reference to the accompanying drawings.
As shown in fig. 1, a hydraulic valve with two-way brake buffering and oil supplementing functions comprises a valve block 22, and a one-way overflow valve I and a one-way overflow valve II which are arranged on the valve block 22 and have consistent components and symmetrical structural layouts;
the valve block 22 is rectangular, and is internally provided with a first oil port A, a second oil port B, a third oil port T1 and a fourth oil port T2;
the one-way overflow valve I comprises a valve sleeve 1, an adjusting screw 2, a first locking nut 3, a main valve core 4, a first spring 5, a clamp spring 6, a one-way valve core 7, an adjusting nut 8 and a second locking nut 10;
wherein, the valve housing 1 is fixed in the valve block 22 by a thread fit mode, the adjusting screw 2 is fixed in the valve housing 1 by a thread fit mode, the first lock nut 3 is connected on the outer peripheral surface of the adjusting screw 2 by a thread fit, one end of the main valve core 4 extends into the blind hole 201 of the adjusting screw 2 and is positioned by the first spring 5, the other end extends into the valve housing 1 and can move in the valve housing 1 and is limited by the clamp spring 6, the one-way valve core 7 is positioned in the hole of the main valve core 4 and can move in the main valve core, the contact surface of the right end of the one-way valve core 7 and the main valve core 4 is a conical surface, the adjusting nut 8 is connected with the left end of the one-way valve core 5 by a thread fit, a second spring 9 with weaker elasticity is arranged between the adjusting nut 8 and the main valve core 4, the second lock nut 10 is connected to the outer peripheral surface of the valve housing 1 through thread fit;
a first sealing ring 23 and a second sealing ring 24 are arranged between the valve block 22 and the valve sleeve 4, the first sealing ring 23 adopts a combination mode of an O-shaped ring and a rubber check ring, and the second sealing ring is an O-shaped ring;
a third sealing ring 25 is arranged between the valve sleeve 1 and the adjusting screw 2, a fourth sealing ring 26 is arranged between the valve sleeve 1 and the main valve element 4, a fifth sealing ring 27 is arranged between the main valve element 4 and the one-way valve element 7, and the third sealing ring 25, the fourth sealing ring 26 and the fifth sealing ring 27 are all sliding sealing rings;
a radial hole b and a radial hole c are formed in the main valve element 4, and the radial hole b is communicated with the first oil port A through a hole 401 in the main valve element 4 and an internal passage of the valve block 22;
a radial hole d is formed in the valve sleeve 1 and is communicated with the third oil port T1 through a channel of the valve block 22;
a cavity a is formed between the main valve core 4 and the one-way valve core, the effective acting area of the one-way valve core 5 can be changed by changing the size of the cavity a, and in addition, the cavity a is communicated with a radial hole c on the main valve core 4;
the adjusting screw 2 is provided with an inner hexagonal hole 202.
Fig. 2 is an application example of the embodiment of the present invention. In the application example, the first oil port a is connected to the rodless cavity oil passage of the hydraulic cylinder, the second oil port B is connected to the rod cavity oil passage of the hydraulic cylinder, and the third oil port T1 and the fourth oil port T2 are both connected to the oil tank.
For example, when the hydraulic cylinder normally moves forward, oil acts on the main valve element 4 and the check valve element 7 of the check relief valve I through the first oil port a and the internal passage of the valve block 22, and at this time, because the oil pressure is insufficient to overcome the acting force of the first spring 5 on the main valve element 4, the main valve port is closed, and the oil cannot flow back to the oil tank through the radial hole b, the radial hole d and the third oil port T1. Similarly, the second port B and the fourth port T2 do not communicate with each other.
If the reversing valve is suddenly reversed to be in a middle position and the work load is large, due to the inertia effect, the load drives the hydraulic cylinder piston to continue to perform forward stroke, the pressure of the second oil port B rises sharply to cause large pressure impact, at the moment, the oil force overcomes the acting force of the first spring 5 of the one-way overflow valve II to push the main valve core 4 of the one-way overflow valve II to drive the one-way valve core 7 to move leftwards together, the main valve port is opened, the oil flows back to the oil tank through the radial hole c and the radial hole d of the one-way overflow valve II, the pressure impact caused by inertia during load braking is absorbed, effective buffering during load braking is realized, the oil flows away, the pressure of the second oil port B is reduced, the main valve core 4 recovers under the action of the first spring 5, and the passage between the second oil port B and the fourth oil port T2 is cut off.
Meanwhile, in the process that the load drives the piston of the hydraulic cylinder to continue to move forwards, the area of a rodless cavity of the hydraulic cylinder is increased to form negative pressure, oil must be supplemented, otherwise cavitation is easily caused, and a hydraulic element is damaged. At this time, because the pressure of the first port a is a negative value, the oil of the third port T1 flows into the cavity a through the radial hole d and the radial hole c of the one-way relief valve I, acts on the one-way valve core 7 of the cavity a, overcomes the elastic force of the second spring 9, and moves rightward, at this time, the cavity a is communicated with the hole 401 of the main valve core 4, and the oil effectively replenishes the rodless cavity of the hydraulic cylinder through the internal passage of the valve block 22 and the first port a, so as to prevent cavitation.
For example, when the hydraulic cylinder normally moves backward, the oil acts on the main valve element 4 and the check valve element 7 of the check relief valve II through the second port a and the internal passage of the valve block 22, and at this time, because the oil pressure is insufficient to overcome the acting force of the first spring 5 on the main valve element 4, the main valve port is closed, and the oil cannot flow back to the oil tank through the radial hole b, the radial hole d and the fourth port T2. Similarly, the first port a and the third port T1 do not communicate with each other.
If the reversing valve is suddenly reversed to be in a middle position and the work load is large, due to the inertia effect, the load drives the hydraulic cylinder piston to continue to perform backward flushing, the pressure of the first oil port A rises sharply to cause large pressure impact, at the moment, the oil force overcomes the acting force of the first spring 5 of the one-way overflow valve I to push the main valve core 4 of the one-way overflow valve I to drive the one-way valve core 7 to move leftwards together, the main valve port is opened, the oil flows back to the oil tank through the radial hole c and the radial hole d of the one-way overflow valve I, the pressure impact caused by the inertia during load braking is absorbed, effective buffering during load braking is realized, the oil flows away, the pressure of the first oil port A is reduced, the main valve core 4 recovers under the action of the first spring 5, and the first oil port A and the third oil port T1 channel is cut off.
Meanwhile, in the process that the load drives the piston of the hydraulic cylinder to continue to perform backward flushing, the area of a rod cavity of the hydraulic cylinder is increased to form negative pressure, oil must be supplemented, otherwise cavitation is easily caused, and a hydraulic element is damaged. At this time, since the pressure of the second port B is a negative value, the oil in the fourth port T2 flows into the cavity a through the radial hole d and the radial hole c of the relief valve II, acts on the check valve core 7 of the cavity a, overcomes the elastic force of the second spring 9, and moves rightward, at this time, the cavity a is communicated with the hole 401 of the main valve core 4, and the oil effectively replenishes the rod cavity of the hydraulic cylinder through the internal passage of the valve block 22 and the second port B, so as to prevent cavitation.
In addition, it should be noted that, according to actual conditions, all the parts of the relief check valve I and the relief check valve II can be changed in size, especially the size of the diameter of the first spring 5.
Furthermore, it should be noted that all equivalent or simple changes made to the structure, features and principles described in the present patent concept are included in the protection scope of the present patent.
Claims (6)
1. A hydraulic valve with two-way braking buffering and oil supplementing functions is characterized by comprising a valve block (22), and a one-way overflow valve I and a one-way overflow valve II which are arranged on the valve block (22) and have consistent components and symmetrical structural layout;
the valve block (22) is cuboid, and is internally provided with a first oil port (A), a second oil port (B), a third oil port (T1) and a fourth oil port (T2);
the one-way overflow valve I comprises a valve sleeve (1), an adjusting screw (2), a first locking nut (3), a main valve core (4), a first spring (5), a clamp spring (6), a one-way valve core (7), an adjusting nut (8) and a second locking nut (10);
wherein the valve sleeve (1) is connected in the valve block (22) through threads, the adjusting screw (2) is connected in the valve sleeve (1) through threads, the first locking nut (3) is connected on the outer peripheral surface of the adjusting screw (2) through thread fit, one end of the main valve core (4) extends into a blind hole (201) of the adjusting screw (2) and is positioned through the first spring (5), the other end of the main valve core extends into the valve sleeve (1) and can move in the valve sleeve (1) and is limited through the snap spring (6), the one-way valve core (7) is positioned in the hole of the main valve core (4) and can move in the main valve core, the contact surface of the right end of the one-way valve core (7) and the main valve core (4) is a conical surface, and the adjusting nut (8) is connected at the left end of the one-way valve core (7) through thread fit, a second spring (9) with weak elasticity is arranged between the adjusting nut (8) and the main valve core (4), and the second locking nut (10) is connected to the outer peripheral surface of the valve sleeve (1) in a threaded fit manner;
the valve barrel (1) with install third sealing washer (25) between adjusting screw (2), valve barrel (1) with install fourth sealing washer (26) between main valve core (4), main valve core (4) with install fifth sealing washer (27) between one-way valve core (7), third sealing washer (25), fourth sealing washer (26), fifth sealing washer (27) are the slip sealing washer.
2. The hydraulic valve with the functions of bidirectional braking buffering and oil supplementing according to claim 1, wherein a first sealing ring (23) and a second sealing ring (24) are installed between the valve block (22) and the valve sleeve (1), the first sealing ring (23) adopts a combination mode of an O-shaped ring and a rubber check ring, and the second sealing ring is an O-shaped ring.
3. The hydraulic valve with the functions of bidirectional braking buffering and oil supplementing according to claim 1, wherein a radial hole (b) and a radial hole (c) are formed in the main valve core (4), and the radial hole (b) is communicated with the first oil port (a) through a hole (401) in the main valve core (4) and an internal passage of the valve block (22).
4. The hydraulic valve with the functions of bidirectional braking, buffering and oil supplementing as claimed in claim 1, wherein said valve housing (1) is provided with a radial hole (d), and said radial hole (d) is communicated with said third oil port (T1) through said valve block (22) channel.
5. The hydraulic valve with the functions of bidirectional braking buffering and oil supplementing according to claim 1, characterized in that a cavity (a) is formed between the main valve core (4) and the check valve core, the effective acting area of the check valve core (7) can be changed by changing the size of the cavity (a), and in addition, the cavity (a) is communicated with a radial hole (c) on the main valve core (4).
6. The hydraulic valve with the functions of bidirectional braking, buffering and oil supplementing according to claim 1, characterized in that the adjusting screw (2) is provided with an inner hexagonal hole (202).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010303037.7A CN111271334B (en) | 2020-04-17 | 2020-04-17 | Hydraulic valve with bidirectional braking buffering and oil supplementing functions |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010303037.7A CN111271334B (en) | 2020-04-17 | 2020-04-17 | Hydraulic valve with bidirectional braking buffering and oil supplementing functions |
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| CN111271334A CN111271334A (en) | 2020-06-12 |
| CN111271334B true CN111271334B (en) | 2022-01-25 |
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Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201671899U (en) * | 2010-05-19 | 2010-12-15 | 西安邮电学院 | Hydraulic overflow buffer circuit for mechanical arm |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2746857B2 (en) * | 1995-05-18 | 1998-05-06 | 仁科工業株式会社 | Shockless valve |
| CN1593789A (en) * | 2004-07-12 | 2005-03-16 | 山西潞安矿业(集团)有限责任公司 | Pump controlled motor hydraulic excitation device |
| CN102444686B (en) * | 2010-10-11 | 2013-10-09 | 伊卡路斯(苏州)车辆系统有限公司 | Variable damping control and buffering system |
| CN203023554U (en) * | 2012-11-19 | 2013-06-26 | 安徽金达利液压有限公司 | Multipurpose one-way overflow valve |
| CN107939767A (en) * | 2017-12-28 | 2018-04-20 | 邵立坤 | A kind of oil supplementation buffer valve |
| CN208416674U (en) * | 2018-04-27 | 2019-01-22 | 山推工程机械股份有限公司 | Intelligent temperature control fan radiating system |
| CN110219847A (en) * | 2019-04-13 | 2019-09-10 | 湖南鹏翔星通汽车有限公司 | A kind of switch valve revolution buffer protection system for wet-spraying machine |
| CN110905888A (en) * | 2019-12-24 | 2020-03-24 | 苏州嘉诺环境工程有限公司 | Hydraulic system and double-shaft crusher |
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2020
- 2020-04-17 CN CN202010303037.7A patent/CN111271334B/en active Active
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201671899U (en) * | 2010-05-19 | 2010-12-15 | 西安邮电学院 | Hydraulic overflow buffer circuit for mechanical arm |
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Effective date of registration: 20230612 Address after: Room 101, No.16 Industrial Road, Miaotou Siheha, Huangpu District, Guangzhou City, Guangdong Province, 510000 Patentee after: Yanchuang Hydraulic Technology (Guangzhou) Co.,Ltd. Address before: 230000 b-1018, Woye Garden commercial office building, 81 Ganquan Road, Shushan District, Hefei City, Anhui Province Patentee before: HEFEI WISDOM DRAGON MACHINERY DESIGN Co.,Ltd. Effective date of registration: 20230612 Address after: 230000 b-1018, Woye Garden commercial office building, 81 Ganquan Road, Shushan District, Hefei City, Anhui Province Patentee after: HEFEI WISDOM DRAGON MACHINERY DESIGN Co.,Ltd. Address before: Weidu District Bayi Road Xuchang city Henan province 461000 No. 88 Patentee before: XUCHANG University |