CN203641146U - Direct-acting hydraulic threaded cartridge buffering overflow valve - Google Patents
Direct-acting hydraulic threaded cartridge buffering overflow valve Download PDFInfo
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- CN203641146U CN203641146U CN201320804814.1U CN201320804814U CN203641146U CN 203641146 U CN203641146 U CN 203641146U CN 201320804814 U CN201320804814 U CN 201320804814U CN 203641146 U CN203641146 U CN 203641146U
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- valve
- main valve
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- plug
- valve plug
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Abstract
The utility model discloses a direct-acting hydraulic threaded cartridge buffering overflow valve. The direct-acting hydraulic threaded cartridge buffering overflow valve comprises a main valve core, a main valve core spring, a main valve core guide sleeve, a one-way valve core, a one-way valve spring seat, a piston, an upper valve sleeve, a lower valve sleeve, a plug screw and an adjusting gasket. The direct-acting hydraulic threaded cartridge buffering overflow valve has the advantages of achieving two-stage pressure control through the same oil port of the same valve and integrating a piston cavity, a piston and a one-way valve into a single valve, thereby being compact in structure and simple in valve block machining.
Description
Technical field
The utility model relates to a kind of plug-in type buffer overflow valve of Hydraulic Power Transmission System, particularly a kind of direct moving type hydraulic thread cartridge buffer overflow valve.
Background technique
Buffer overflow valve is a kind of 2-level hydraulic pressure controlled valve, mainly plays level pressure overflow, eliminates pulsating pressure, voltage stabilizing, system unloaded and safety protection in hydraulic equipment, and its working principle as shown in Figure 1.Set it as especially a necessary condition of technology upgrading in farm machinery, engineering machinery etc.For example, in excavator walking device, buffer overflow valve is the crucial hydraulic element of this type systematic, and the quality of buffer overflow valve directly affects the performance of main frame.Existing buffer overflow valve is divided into two kinds of board-like buffer overflow valve and plug-in type buffer overflow valves by Placement, in system, in order to reduce installing space, improves the reliability of system, generally adopts plug-in type buffer overflow valve.
Existing plug-in type buffer overflow valve has the following disadvantages: first, realize secondary pressure control and realize by two identical valves, different hydraulic fluid port oil-feeds, must support the use, its working principle as shown in Figure 2; Secondly, on valve piece, must increase plunger cavity, piston, one-way valve and support the use, cause valve piece processed complex.
Model utility content
Model utility object: for the problems referred to above, the purpose of this utility model is to provide a kind of compact structure, valve piece is processed simple plug-in type buffer overflow valve, realizes the control of secondary pressure on same valve.
Technological scheme: a kind of direct moving type hydraulic thread cartridge buffer overflow valve, comprises main valve plug, main valve plug spring, main valve plug guide sleeve, nonreturn valve core, check valve spring, check valve spring seat, piston, upper valve sleeve, lower valve sleeve, plug screw, adjustment pad;
Nonreturn valve core, check valve spring, check valve spring seat are housed in main valve plug front end, on nonreturn valve core, offer damping hole;
Main valve plug and main valve plug guide sleeve pack in lower valve sleeve, main valve plug spring is housed between main valve plug and main valve plug guide sleeve and adjusts pad, upper valve sleeve is connected with lower valve sleeve and carries out spacing to main valve plug guide sleeve, on lower valve sleeve, offer and be positioned at the pressure port A of front end and the pressure port B of both sides, under the effect of main valve plug spring, main valve plug front end and pressure port A form cone mouth sealing;
Piston is housed in upper valve sleeve, and plug screw is to the shutoff of upper valve sleeve tail end, and piston and upper valve sleeve, main valve plug guide sleeve, main valve plug, nonreturn valve core form piston cavity.
Adjust the initial compression amount of the THICKNESS CONTROL main valve plug spring of pad by change, to regulate cracking pressure and the rated pressure of main valve plug.
The utility model is to utilize the active force of main valve plug internal check valve spring to realize one-way throttle function, realizes the first class pressure of buffer overflow valve by the variation of piston cavity, realizes the secondary pressure of buffer overflow valve in the time that piston cavity is increased to maximum.
When pressure port A place pressure starts to increase, pressure port A enters the flow of piston cavity by the damping hole control on nonreturn valve core, promoting piston slowly moves, when pressure port A place oil pressure active force is increased to when equally large with main valve plug spring force, buffer overflow valve is realized first class pressure control function, and pressure port A is to pressure port B release.
When piston moves to behind top, can not exchange pressure balance for by flow of fluid again, just there is not flow of fluid in piston cavity and pressure port A, and in inactive liquid, the suffered pressure of any point all equates in all directions, now main valve plug is closed, and pressure port A cannot be to pressure port B release.
When pressure port A place oil pressure active force continues to be increased to can overcome main valve plug spring force and piston cavity and act on the active force on main valve plug time, buffer overflow valve is realized secondary pressure control function, and pressure port A is to pressure port B release.
Beneficial effect: compared with prior art, the utility model has the advantages that the same hydraulic fluid port on same valve realizes the control of secondary pressure, can use by a valve, piston cavity, piston, one-way valve are integrated on valve, compact structure, the processing of valve piece is simple.
Accompanying drawing explanation
Fig. 1 is the fundamental diagram of buffer overflow valve;
Fig. 2 is the fundamental diagram of existing plug-in type buffer overflow valve;
Fig. 3 is that the utility model partly cuts open structural representation piston in initial position;
Fig. 4 is that the utility model partly cuts open structural representation first class pressure enable possition;
Fig. 5 is that the utility model partly cuts open structural representation first class pressure and secondary pressure position when excessive;
Fig. 6 is that the utility model partly cuts open structural representation secondary pressure enable possition;
Fig. 7 partly cuts open structural representation while starting to walk with the running motor of the utility model buffer overflow valve;
Fig. 8 partly cuts open structural representation while normally working with the running motor of the utility model buffer overflow valve;
Fig. 9 starts to stop operating with the running motor of the utility model buffer overflow valve partly to cut open structural representation while being low pressure release;
Figure 10 partly cuts open structural representation while being high pressure release with the running motor maximum brake pressure of the utility model buffer overflow valve.
Embodiment
Below in conjunction with the drawings and specific embodiments, further illustrate the utility model, should understand these embodiments and only be not used in restriction scope of the present utility model for the utility model is described, after having read the utility model, those skilled in the art all fall within the application's claims limited range to the modification of the various equivalent form of values of the present utility model.
As shown in Figure 3, a kind of direct moving type hydraulic thread cartridge buffer overflow valve, comprises main valve plug 1, main valve plug spring 2, main valve plug guide sleeve 3, nonreturn valve core 4, check valve spring 5, check valve spring seat 6, piston 7, upper valve sleeve 8, lower valve sleeve 9, plug screw 10, adjusts pad 11.
Main valve plug 1 and main valve plug guide sleeve 3 pack in lower valve sleeve 9, main valve plug spring 2 is housed between main valve plug 1 and main valve plug guide sleeve 3 and adjusts pad 11, by adjusting the initial compression amount of THICKNESS CONTROL main valve plug spring 2 of pad 11, upper valve sleeve 8 is threaded connection and carries out spacing to main valve plug guide sleeve 3 with lower valve sleeve 9, on lower valve sleeve 9, offer and be positioned at the pressure port A13 of front end and the pressure port B14 of both sides, under the effect of main valve plug spring 2, main valve plug 1 front end and pressure port A13 form cone mouth sealing;
Piston 7 is housed in upper valve sleeve 8, and piston 7 can be free to slide in upper valve sleeve 8, and plug screw 10 is to upper valve sleeve 8 tail end shutoff, and piston 7 forms piston cavity with upper valve sleeve 8, main valve plug guide sleeve 3, main valve plug 1, nonreturn valve core 4.
Main valve plug is through-flow, and diameter is d1, and main valve plug guiding diameter is d2, and one-way valve is through-flow, and diameter is d3.P
gfor piston cavity pressure, P
1for working as pressure port A place pressure, F
sfor main valve plug spring force.
As shown in Figure 4, when pressure port A place pressure starts to increase, pressure port A enters the flow of piston cavity by the damping hole control on nonreturn valve core, promote piston and slowly move right, P
g≈ 0, when pressure port A place oil pressure active force is increased to when equally large with main valve plug spring force, i.e. P
1× π (d1)
2/ 4=F
s, buffer overflow valve is realized first class pressure control function, hydraulic oil by pressure port A to pressure port B release.
As shown in Figure 5, when piston moves to behind right top, can not exchange pressure balance for by flow of fluid again, just there is not flow of fluid in piston cavity and pressure port A, and in inactive liquid, the suffered pressure of any point all equates in all directions, therefore P
1=P
g, according to main valve plug equation of equilibrium P
1× π (d1)
2/ 4 < F
s+ P
g× π (d2)
2/ 4, now main valve plug is closed, and hydraulic oil cannot be by pressure port A to pressure port B release.
As shown in Figure 6, when pressure port A place oil pressure active force continues to be increased to can overcome main valve plug spring force and piston cavity and act on the active force on main valve plug time, P
1× π (d1)
2/ 4=F
s+ P
g× π (d2)
2/ 4, P
1=P
g, i.e. P
1× π ［ (d1)
2-(d2)
2］/4=F
s, buffer overflow valve is realized secondary pressure control function, hydraulic oil by pressure port A to pressure port B release.
Enter high pressure oil as example take the running motor A chamber with the utility model buffer overflow valve below, introduce the application of the utility model buffer overflow valve on running motor.
As shown in Figure 7, when high pressure oil is entered in A chamber, when running motor starts to walk, buffer overflow valve I 15 realizes first class pressure release, and when the piston of buffer overflow valve I 15 moves to after end, main valve plug is closed.Now, buffer overflow valve I 15 has played and has started effect stably on running motor.
As shown in Figure 8, when high pressure oil is entered in A chamber, when running motor is normally walked, buffer overflow valve I 15 and buffer overflow valve II 16 are all inoperative.
When high pressure oil is entered in A chamber, in the time that running motor is braked, because B chamber is connected with brake chamber, B cavity pressure and brake chamber pressure equate, just can control running motor retardation pressure therefore control B cavity pressure.
As shown in Figure 9, in the time that running motor just starts to stop operating, B cavity pressure raises rapidly, and buffer overflow valve II 16 realizes first class pressure release, and when the piston of buffer overflow valve II 16 moves on to after end, main valve plug is closed.Now, buffer overflow valve II 16 has been eliminated the pulsating pressure in B chamber in the time that running motor is braked, and has prevented that the suction of A chamber is empty.
As shown in Figure 10, in the time that motor is braked, follow-up height of continuing rising is closed in the pressure process first class pressure release in B chamber, until buffer overflow valve is realized secondary release.Now, the secondary pressure of buffer overflow valve is exactly the maximum brake pressure of running motor.
Claims (2)
1. a direct moving type hydraulic thread cartridge buffer overflow valve, is characterized in that: comprise main valve plug (1), main valve plug spring (2), main valve plug guide sleeve (3), nonreturn valve core (4), check valve spring (5), check valve spring seat (6), piston (7), upper valve sleeve (8), lower valve sleeve (9), plug screw (10), adjust pad (11);
Nonreturn valve core (4), check valve spring (5), check valve spring seat (6) are housed in main valve plug (1) front end, on nonreturn valve core (4), offer damping hole (12);
Main valve plug (1) and main valve plug guide sleeve (3) pack in lower valve sleeve (9), main valve plug spring (2) is housed between main valve plug (1) and main valve plug guide sleeve (3) and adjusts pad (11), upper valve sleeve (8) is connected with lower valve sleeve (9) and carries out spacing to main valve plug guide sleeve (3), lower valve sleeve is offered the pressure port A(13 that is positioned at front end on (9)) and the pressure port B(14 of both sides), under the effect of main valve plug spring (2), main valve plug (1) front end and pressure port A(13) sealing of formation cone mouth;
Piston (7) is housed in upper valve sleeve (8), and plug screw (10) is to upper valve sleeve (8) tail end shutoff, and piston (7) forms piston cavity with upper valve sleeve (8), main valve plug guide sleeve (3), main valve plug (1), nonreturn valve core (4).
2. direct moving type hydraulic thread cartridge buffer overflow valve according to claim 1, is characterized in that: the initial compression amount of adjusting the THICKNESS CONTROL main valve plug spring (2) of pad (11) by change.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320804814.1U CN203641146U (en) | 2013-12-09 | 2013-12-09 | Direct-acting hydraulic threaded cartridge buffering overflow valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320804814.1U CN203641146U (en) | 2013-12-09 | 2013-12-09 | Direct-acting hydraulic threaded cartridge buffering overflow valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203641146U true CN203641146U (en) | 2014-06-11 |
Family
ID=50872394
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320804814.1U Withdrawn - After Issue CN203641146U (en) | 2013-12-09 | 2013-12-09 | Direct-acting hydraulic threaded cartridge buffering overflow valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203641146U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103615424A (en) * | 2013-12-09 | 2014-03-05 | 怀特(中国)驱动产品有限公司 | Direct-operated-type hydraulic threaded insertion buffer overflow valve |
| CN108626193A (en) * | 2018-05-18 | 2018-10-09 | 宁波真格液压科技有限公司 | A kind of cartridge valve |
| WO2022222252A1 (en) * | 2021-04-20 | 2022-10-27 | 宁波万安股份有限公司 | Fuel gas pressure-stabilizing apparatus |
-
2013
- 2013-12-09 CN CN201320804814.1U patent/CN203641146U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103615424A (en) * | 2013-12-09 | 2014-03-05 | 怀特(中国)驱动产品有限公司 | Direct-operated-type hydraulic threaded insertion buffer overflow valve |
| CN103615424B (en) * | 2013-12-09 | 2015-12-30 | 怀特(中国)驱动产品有限公司 | Direct moving type hydraulic thread cartridge buffer overflow valve |
| CN108626193A (en) * | 2018-05-18 | 2018-10-09 | 宁波真格液压科技有限公司 | A kind of cartridge valve |
| WO2022222252A1 (en) * | 2021-04-20 | 2022-10-27 | 宁波万安股份有限公司 | Fuel gas pressure-stabilizing apparatus |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20140611 Effective date of abandoning: 20151230 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |