CN1756917A - Directly controlled pressure control valve - Google Patents
Directly controlled pressure control valve Download PDFInfo
- Publication number
- CN1756917A CN1756917A CNA2003801100030A CN200380110003A CN1756917A CN 1756917 A CN1756917 A CN 1756917A CN A2003801100030 A CNA2003801100030 A CN A2003801100030A CN 200380110003 A CN200380110003 A CN 200380110003A CN 1756917 A CN1756917 A CN 1756917A
- Authority
- CN
- China
- Prior art keywords
- piston
- seat
- director element
- valve
- relief valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0433—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with vibration preventing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
- F16K17/065—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure with differential piston
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
- G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Fluid Mechanics (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Safety Valves (AREA)
Abstract
The invention relates to a directly controlled pressure control valve comprising a seat piston (6) in a longitudinal borehole (8) of a valve housing (4), said piston being radially guided in the longitudinal borehole, in its guiding region, by means of two peripheral interspaced guiding elements (36).
Description
Technical field
The present invention relates to a kind of as described in the preamble direct control relief valve according to claim 1.
Background technique
A kind of such relief valve (DBV) is shown in Figure 1.The DBV shown in the there produces from applicant's record chart RD 18 016-3.01/01.98.Fig. 1 illustrates DBV 2, is included in the seat piston 6 that is directed in the valve pocket 4.Seat piston 6 is received in vertical boring 8 and by spring 10 bias voltages and leans against valve seat 12, so that the hydraulic oil that blocks from inflow side working interface A to outflow side working interface B connects.Seat piston 6 vertically is being provided with radial clearance in the boring 8.Receive seal ring 34 in the circumferential groove 38 of present piston 6, it leans against on the inner peripheral wall of vertical boring 8 hermetically.
Shortcoming in this solution is that the seat piston is rotated or pivot movement along the longitudinal direction around seal ring in open position.
Owing to the contact chatter that wherein produces, a seat piston bears high mechanical stress, thereby reduces the working life of this DBV.
And this contact chatter is converted into the operation such as the noise beastly and the prevention low noise of flute song.
Summary of the invention
Task of the present invention is, a kind of direct control relief valve is provided, and it can eliminate above-mentioned shortcoming and can be with the low cost manufacturing.
This task is by having the direct control relief valve solution according to the feature of claim 1.
The valve pocket that has the working interface that has inflow side and outflow side according to relief valve of the present invention (DBV).In valve pocket, seat piston bias voltage leans against on the valve seat.According to the present invention the seat piston in guiding area at least by two apart from one another by the circumference of present piston on the circular director element that is provided with of annular be supported in the valve pocket.
In solution of the present invention advantageously, at least---two director elements---are directed in vertical boring of valve pocket the seat piston by two " bearings ", so the seat piston can not cause being rotated or pivot movement around its longitudinal shaft, and does not therefore cause vibration when opening DBV.Suppress contact chatter.
And be according to the advantage of DBV of the present invention, realized the damping in axial direction of seat piston by two director elements.
The seat piston does not have the axial stop that axial restraint seat piston is opened stroke.The maximum stroke of opening is determined by the compression of spring.In order to protect director element; vertically boring is radially being widened by flat inclined-plane in the exit region of spring chamber; make the director element that enters not be damaged when return course, described director element enters spring chamber and turns back to during shutoff stroke in vertical boring in favourable modification.
Director element is the O V-shaped ring in a preferred embodiment, for example has shear strength A in 90 scope.
In one embodiment, pressure oil can turn back to spring chamber from the outflow side working interface through the boring in the present piston, so the pressure that exists in spring chamber is basically corresponding to the pressure of outflow side working interface.At least one is opened by matching gap or by cross section towards the lateral bore of the working interface of outflow side in the bias voltage position of rest in this case, yet the cross section that it is opened can controllably be closed according to the stroke of opening of seat piston, so pressure oil stream no longer passes lateral bore, but only crosses the annular space.
For the stable base piston, director element is apart from one another by far away as much as possible, and wherein preferably first director element is arranged near the lateral bore and second director element is arranged on vertical boring near the exit region of spring chamber.
In order to reduce retardation phenomenon, be provided with the turning circular groove between the director element of the present piston of another embodiment, so can the seat piston not carried out grinding.
In another embodiment,, on the outflow side, form reservoir in order to obtain the response characteristic that DBV improves, its form be have the hoop end face the seat piston radially to returning ladder.Reservoir is limited by valve seat and annular end face in the axial direction.In position of rest, pressure oil can be present and be flowed along the direction towards the outflow side working interface from reservoir on the piston.Explanation in the German patent application 102 60 662.5 of such reservoir before the claimant.
Other favourable structural types are themes of other dependent claims.
Description of drawings
Explain the preferred embodiment of the invention according to schematic figures below.Wherein:
Fig. 1 illustrates the longitudinal sectional view of the known solution of passing relief valve;
Fig. 2 illustrates the longitudinal sectional view that passes the preferred embodiments of the present invention;
Fig. 3 illustrates the longitudinal sectional view of seat piston according to the present invention among Fig. 2;
Fig. 4 illustrates the zoomed-in view of the regional X of Fig. 2.
Embodiment
Fig. 2 illustrates the cutaway side sectional view according to the preferred embodiment of directly actuated relief valve of the present invention (DBV) 2.DBV 2 has the valve pocket of being made up of many parts 4 that comprises vertical boring 8, received block piston 6 slidably in above-mentioned boring.Seat piston 6 is biased into its position of rest by spring 10, leans against on the valve seat 12.Spring 10 is arranged in the spring chamber 14 and passes through biased member 16 can regulate bias voltages.
Valve pocket 4 has spring chamber shell 18 and seat piston shell 20.18 restrictions of spring chamber shell are used to receive the spring chamber 14 of spring 10 and are threadably engaged with seat piston shell 20 and link to each other.In spring chamber 14, spring 10 supports by the end portion 72 on the bias voltage lid 60 of biased member 16.Second end portion, 62 springs by it are on the spring cup 24 of a piston 6.
In the present piston shell 20, the outflow side that is formed with vertical boring 8 and and be positioned at the axial working interface A of inflow side when observing and is used to be connected the service line (not shown) from valve seat 12 is working interface B radially.Vertical boring 8 direction of working interface A is vertically opened.Vertically boring 8 is connected with the star drill hole structure with working interface B radially by a plurality of equally distributed radial bores 22.Valve seat 12 is formed in the seat piston shell 20 in vertical boring 8 between working interface A, B.
Vertically boring 8 is radially widened by four ladders 26,28,30,32 along the direction of spring chamber 16.First ladder 26 forms and is used as formation valve seat 12 between two working interface A, B.In the position of rest of the bias voltage of the present piston 8 of second ladder, 28 usefulness, the impact spring that is used to receive spring cup 24 and spring 10 covers the end portion 62 of 18 back.Third and fourth ladder 30,32 is used to receive spring chamber shell 18.
By use at least two apart from one another by director element 36, guarantee by two " bearing " on the stroke in vertical boring 8 guide seat piston 6 like this, thereby stop or reduce to a certain extent the rotation and the pivot movement of a piston 6, and the more difficult basically piston 6 that makes vibrates.In this case, the distance between director element 36 is big more, and the radially-directed of seat piston 6 is good more so.Except support function radially, director element 36 also has axial damping function.The material of director element 36 is so selected, and on the one hand reaches optimum support effect and damping, yet on the other hand by the frictional force minimum on the present piston 6 of director element 36 effects, makes the response characteristic optimum of DBV 2.In the above-described embodiment, select to have the fluorine rubber of shear strength A in 90 scope as material.
In the inflow side or when radially working interface B upstream observes, pedestal 6 is radially to back-shaped one-tenth ladder, so that form reservoir 44 (Fig. 4) between seat piston 6 in vertical boring 8 and the seat piston shell 22.This forwards the conical surface 68 of end face side to the staircase areas of returning, and it is located on the valve seat 12 in the position of rest of bias voltage.Reservoir 44 by valve seat 12 and by seat piston 6 radially to returning annular end face 52 restrictions that ladder produces, this annular end face constitutes seat piston edge 46 or guiding valve edge.Reservoir 44 (Fig. 4) 22 is opened to radially holing by the fan-shaped flow section 48 between present piston edge 46 and seat piston shell 20 radial bores 22 internal edges in closed position.Advantageously, seat piston edge 46 and radial bore 22 make to face toward hydraulic oil appears discharging in annular end face 52 (Fig. 3) along seat piston 6 axial flow apart from valve seat 12 or the axial certain distance of working interface A.
When seat piston 6 rose from valve seat 12, reservoir 44 and annular end face 52 be together as being used for a piston 6 stroke auxiliary devices, thus can realize the response characteristic of DBV most of with open stroke and therefore with the spring path independence.For the detailed explanation of reservoir 44 operations, please refer to the applicant's German patent application 102 60 662.5 in the past.
In the present piston 6, constitute the axial drilling 54 (Fig. 3) of blind hole mode, it is opened and feeds at least one lateral bore 56 in the valve seat side to spring chamber 14.Therefore the pressure that exists at working interface B place, outflow side can be drawn and be present in the spring chamber 14.Preferably, lateral bore forms as the star drill hole.In the position of rest of bias voltage, lateral bore 56 is opened to outflow side working interface B, yet along with the increase of opening stroke, it closes (Fig. 4) towards the open cross-section of working interface B by the control edge 58 of vertical boring 8.Form fan-shaped in the section part of control edge 58 by radial bore 22 and the vertical boring 8 present piston shells 20.After closing, hydraulic oil between radial bore 22 and lateral bore 56 only flows by narrow annular space 80, so strengthened the damping of seat piston 6, extended to the control edge 58 of vertical boring 8 between the excircle 84 of the present piston 6 in described annular space and 8 the inner circumference 78 of vertically holing from the director element 36 facing to outflow side working interface B of seat piston 6 always.
Illustrate that as top in order to improve the stability of a piston 6, director element 36 is apart from one another by far away as much as possible.Preferably, a director element 36 is provided with near lateral bore 56 and the close vertically boring of another director element---in position of rest---8 exit regions towards spring chamber 14.
Disclosed is a kind of direct control relief valve, have in vertical boring of valve pocket the seat piston, described piston in its guiding area by two circles apart from one another by director element radially be guided in vertical boring.
Reference numeral
2 overflow valves
4 valve pockets
6 pistons
8 longitudinal drillings
10 springs
12 valve seats
14 spring chambers
16 biased members
18 spring chamber shells
20 piston shells
22 radial bores
24 spring cups
26 first ladders
28 second ladders
30 the 3rd ladders
32 four-steps
34 seal rings
36 director elements
38 circumferential grooves
40 inner circumferential portion
42 turning circular grooves
44 reservoir
46 piston edges
48 flow sections
50 internal edges
52 annular end faces
54 axial drillings
56 lateral bores
58 control edges
60 bias voltages lid
62 end portion
64 bias voltage screws
66 lock nuts
68 conical surfaces
70 inner circumference area
72 end portion
74 annular chambers
76 outer circumferential area
78 inner circumferences
80 annular spaces
82 inclined-planes
84 excircles
Claims (10)
1. directly control relief valve for one kind, has the biased seat piston (6) that leans against on the valve seat (12) in valve pocket, the pressure oil that is used to open and close between inflow side working interface A and outflow side working interface A, B connects, it is characterized in that, seat piston (6) in guiding area, comprise at least two apart from one another by, the circular director element (36) that is provided with on the present piston circumference side, a seat piston (6) radially is supported in the valve pocket (4) by this director element.
2. direct control relief valve as claimed in claim 1, wherein director element (36) is the O V-shaped ring.
3. direct control relief valve as claimed in claim 1 or 2, wherein director element (36) has the shear strength A in 90 scopes.
4. as claim 1,2 or 3 described direct control relief valves, wherein at the turning circular groove that forms between the director element (36) on the present piston (6).
5. direct control relief valve as claimed in claim 1, wherein be used for forming in the present piston (6) in the boring (54,56) that spring chamber (14) is exerted pressure, wherein at least one lateral bore (56) is opened to outflow side working interface B under the closed condition of valve, and it can be according to the Stroke Control of opening of seat piston (6) to the opening cross-section of working interface B.
6. each described direct control relief valve in the claim as described above, wherein vertically boring (8) is radially being widened by inclined-plane (82) in the exit region of spring chamber (14).
7. each described direct control relief valve in the claim as described above, wherein director element (36) is apart from one another by very big, and wherein first director element is provided with near lateral bore (56) and second director element close vertically exit region towards spring chamber (14) of boring (8) in position of rest.
8. each described direct control relief valve in the claim as described above wherein forms reservoir (44) in the outflow side, and it has annular end face (52) to constitute the stroke auxiliary device.
9. direct control relief valve as claimed in claim 8, wherein reservoir (44) forms by the ladder that radially returns of seat piston (6), and wherein reservoir (44) axially limits by the annular end face (52) of valve seat (12) and seat piston (6).
10. directly control relief valve as claimed in claim 8 or 9, wherein have such axial distance between valve seat (12) and outflow side working interface B, feasible appearance is along the axial flow of the pressure oil of the discharge of seat piston (6).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10308487 | 2003-02-26 | ||
DE10308487.8 | 2003-02-26 | ||
DE10312672.4 | 2003-03-21 |
Publications (2)
Publication Number | Publication Date |
---|---|
CN1756917A true CN1756917A (en) | 2006-04-05 |
CN100532899C CN100532899C (en) | 2009-08-26 |
Family
ID=32841965
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CNB2003801100030A Expired - Fee Related CN100532899C (en) | 2003-02-26 | 2003-11-14 | Directly controlled relief valve |
Country Status (3)
Country | Link |
---|---|
CN (1) | CN100532899C (en) |
AT (1) | ATE434144T1 (en) |
DE (2) | DE10312672A1 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102884349A (en) * | 2010-05-06 | 2013-01-16 | 伊利诺斯工具制品有限公司 | Multi-mode pressure relief valve |
CN103244498A (en) * | 2013-05-17 | 2013-08-14 | 浙江科技学院 | Precision pressure regulating type direct-acting overflow valve |
CN103291983A (en) * | 2013-06-28 | 2013-09-11 | 三一重型装备有限公司 | Safety valve and hydraulic support with same |
CN103775438A (en) * | 2013-12-31 | 2014-05-07 | 江苏南铸科技股份有限公司 | Overload protective valve and overload valve comprising same |
CN104141813A (en) * | 2013-05-06 | 2014-11-12 | 北京华德液压工业集团有限责任公司 | Direct-acting overflow valve |
CN105299254A (en) * | 2015-12-08 | 2016-02-03 | 大连海事大学 | Overflow valve of oil supply system of transmission device |
CN104302907B (en) * | 2012-05-16 | 2017-03-01 | 福士汽车配套部件责任有限公司 | Pressure limiting valve |
CN107504302A (en) * | 2016-06-14 | 2017-12-22 | 保时捷股份公司 | For with air conduit can reverse connection pressure holding valve |
CN108679031A (en) * | 2018-05-18 | 2018-10-19 | 东莞海特帕沃液压科技有限公司 | A kind of hydraulic air compressor |
CN113983342A (en) * | 2021-10-29 | 2022-01-28 | 中国航发沈阳发动机研究所 | Pressure regulating valve structure with anti-pollution capability |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013131886A1 (en) * | 2012-03-08 | 2013-09-12 | Robert Bosch Gmbh | Hydrostatic displacement machine |
EP2728229B1 (en) * | 2012-11-05 | 2015-06-24 | Magna Steyr Fahrzeugtechnik AG & Co KG | Pressure storage valve unit for a pressure storage container |
EP2728228B1 (en) | 2012-11-05 | 2015-06-17 | Magna Steyr Fahrzeugtechnik AG & Co KG | Sealing valve for a pressure storage container |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1095611B (en) * | 1957-12-24 | 1960-12-22 | Zentrale Entwicklung Und Konst | Spring-loaded safety valve with high-lift piston |
DE4037905A1 (en) * | 1990-11-28 | 1992-06-04 | Herion Werke Kg | SAFETY VALVE |
DE4206210A1 (en) * | 1992-02-28 | 1993-09-02 | Rexroth Mannesmann Gmbh | Electromagnetically actuated, proportional pressure regulating, hydraulic fluid power valve - has armature displaced with control coil by magnetic force with in line mechanical spring opposing action |
-
2003
- 2003-03-21 DE DE10312672A patent/DE10312672A1/en not_active Withdrawn
- 2003-11-14 AT AT03785514T patent/ATE434144T1/en not_active IP Right Cessation
- 2003-11-14 CN CNB2003801100030A patent/CN100532899C/en not_active Expired - Fee Related
- 2003-11-14 DE DE50311620T patent/DE50311620D1/en not_active Expired - Lifetime
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102884349A (en) * | 2010-05-06 | 2013-01-16 | 伊利诺斯工具制品有限公司 | Multi-mode pressure relief valve |
CN104302907B (en) * | 2012-05-16 | 2017-03-01 | 福士汽车配套部件责任有限公司 | Pressure limiting valve |
CN104141813A (en) * | 2013-05-06 | 2014-11-12 | 北京华德液压工业集团有限责任公司 | Direct-acting overflow valve |
CN104141813B (en) * | 2013-05-06 | 2017-02-15 | 北京华德液压工业集团有限责任公司 | Direct-acting overflow valve |
CN103244498A (en) * | 2013-05-17 | 2013-08-14 | 浙江科技学院 | Precision pressure regulating type direct-acting overflow valve |
CN103291983A (en) * | 2013-06-28 | 2013-09-11 | 三一重型装备有限公司 | Safety valve and hydraulic support with same |
CN103291983B (en) * | 2013-06-28 | 2015-06-10 | 三一重型装备有限公司 | Safety valve and hydraulic support with same |
CN103775438A (en) * | 2013-12-31 | 2014-05-07 | 江苏南铸科技股份有限公司 | Overload protective valve and overload valve comprising same |
CN105299254A (en) * | 2015-12-08 | 2016-02-03 | 大连海事大学 | Overflow valve of oil supply system of transmission device |
CN105299254B (en) * | 2015-12-08 | 2017-07-11 | 大连海事大学 | A kind of direct-acting overflow valve of transmission device oil supply system |
CN107504302A (en) * | 2016-06-14 | 2017-12-22 | 保时捷股份公司 | For with air conduit can reverse connection pressure holding valve |
US10394258B2 (en) | 2016-06-14 | 2019-08-27 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Pressure maintaining valve for a reversible connection to an air line |
CN107504302B (en) * | 2016-06-14 | 2019-12-03 | 保时捷股份公司 | For with air conduit can reverse connection pressure holding valve |
CN108679031A (en) * | 2018-05-18 | 2018-10-19 | 东莞海特帕沃液压科技有限公司 | A kind of hydraulic air compressor |
CN113983342A (en) * | 2021-10-29 | 2022-01-28 | 中国航发沈阳发动机研究所 | Pressure regulating valve structure with anti-pollution capability |
Also Published As
Publication number | Publication date |
---|---|
DE10312672A1 (en) | 2004-09-09 |
ATE434144T1 (en) | 2009-07-15 |
DE50311620D1 (en) | 2009-07-30 |
CN100532899C (en) | 2009-08-26 |
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C06 | Publication | ||
PB01 | Publication | ||
C10 | Entry into substantive examination | ||
SE01 | Entry into force of request for substantive examination | ||
C14 | Grant of patent or utility model | ||
GR01 | Patent grant | ||
C17 | Cessation of patent right | ||
CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090826 Termination date: 20121114 |