WO2004015271A1 - Nicht-proportionales stromregelventil für eine flügelzellenpumpe - Google Patents
Nicht-proportionales stromregelventil für eine flügelzellenpumpe Download PDFInfo
- Publication number
- WO2004015271A1 WO2004015271A1 PCT/EP2003/006091 EP0306091W WO2004015271A1 WO 2004015271 A1 WO2004015271 A1 WO 2004015271A1 EP 0306091 W EP0306091 W EP 0306091W WO 2004015271 A1 WO2004015271 A1 WO 2004015271A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- spring
- valve
- length
- length range
- valve according
- Prior art date
Links
- 238000004804 winding Methods 0.000 claims description 9
- 239000012530 fluid Substances 0.000 description 13
- 230000000694 effects Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000000704 physical effect Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/20—Flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/58—Valve parameters
Definitions
- the invention relates to a valve for a pump with a spring according to the preamble of claim 1.
- DE 199 48 446 A1 describes a spring for a pump valve, in particular for a suction valve of a pump of a controlled brake system.
- the spring for controlling the opening times of the suction valve of a piston pump has a small spring stiffness in the work area in which the valve opens, while a large spring stiffness of the spring is used in the work area in which the spring begins to close the valve. The effect of this is that the valve can close quickly.
- a control piston is preferably axially displaceably mounted in a valve bore in a housing of a vane cell pump.
- the flow control valve is designed in the manner of a pressure compensator, with the control piston on one side at the operating pressure of the vane cell pump and at a consumer, such as at a
- a channel for guiding fluid which is under pressure from the vane cell pump, opens into the valve bore.
- the fluid reaches a consumer via a throttle opening in a valve screw within the valve bore.
- the cross-section of the throttle opening is changed depending on the path of an extension of the control piston which projects through it.
- the control piston is acted upon on its other side facing away from the extension by a spring, the spring force of which acts on a guide pin of the control piston and presses the control piston against the throttle opening.
- the spring is positioned in a control chamber which is pressurized with fluid under pressure by a pressure compensation bore.
- the spring has a constant spring rate, which means a compromise between a force necessary to open the throttle opening and a spring force to regulate the throttle cross section at high volume flows of the fluid through the flow control valve.
- the degree of filling of such a power steering pump is not optimal at high volume flows and the characteristic curve of the power steering pump in this volume flow speed range is not linear. In addition, the power requirement for smaller volume flows is increased.
- the invention has for its object to provide a valve designed as a flow control valve for a power steering pump, which enables a uniform volume flow of a fluid over a large volume flow range.
- the spring which applies a compressive force to the guide pin of the control piston, has a length range with a first spring constant and a length range with a second spring constant, the second spring constant being greater than the first spring constant, has the effect that an optimal response to the Characteristic curve of the respective wing cell pump adapted opening force for the throttle of the flow control valve and such a spring force, in particular at high volume flows and speeds of the wing cell pump, is present on the control piston such that a high fluid pressure is present on the pressure side of the wing cell pump. This results in a high degree of filling of the wing cell pump.
- control piston which is provided with a short guide length and is arranged in the valve bore at risk of tipping, is guided well through the tight-fitting turns of the soft length of the spring and centered during stroke movements.
- a control piston is at open state of the throttle is additionally stabilized by the spring itself.
- the spring may be expedient to provide the spring with a third length range, which has a different spring constant than the first and second length ranges.
- the third length range of the spring can follow the first length range.
- the spring can be represented in the axial direction with the first and third length ranges arranged symmetrically to the second length range, so that they can be installed in a direction-independent manner during assembly.
- the spring has eight resilient turns, the first length range 2.6, the second length range 1, 8 and the third length range 2.6 having resilient turns.
- the flow control valve is dimensioned such that the spring is about 25.5 mm long in a contact position of the control piston at the throttle opening of the flow control valve. In contrast, in a block position in which the guide pin of the control piston rests on a housing wall, the spring length is still approximately 13.5 mm.
- the maximum spring force is approximately 68 N and the spring force in the "open position" of the control piston is approximately 35 N.
- the spring constant of the first and / or third length range of the spring is preferably approximately 2.0 N / mm and the spring constant of the second length range of the spring is approximately 5.7 N / mm.
- FIG. 1 shows a cross section through a vane cell pump with the flow control valve according to the invention
- FIG. 2 shows a cross section through the flow control valve in FIG. 1 in the closed state
- 2 a shows a cross section through the flow control valve in Fig. 1 in the open state
- 2 b shows a cross section through the flow control valve in Fig. 1 in kink length
- FIG. 2 c shows a cross section through the flow control valve in FIG. 1 in the block length position
- Fig. 4 shows the spring force of a spring for the flow control valve in Fig. 1 plotted against the spring length.
- a valve 1 designed as a flow control valve 10 extends across approximately the entire width of a housing 23 of the air cell pump 11 across a shaft axis 22 of the air cell pump 11.
- the housing 23 is provided with a valve bore 15, in which a control piston 14 is provided an extension 24 is axially displaceable.
- the valve bore 15 is closed on one side by a housing wall 25 and provided at its opposite end with a valve screw 26 to which a consumer, such as a steering gear, can be connected.
- a pressure channel (not shown) opens into a pressure chamber 27 between the valve screw 26 and a pressure compensator surface 28 of the control piston 14, via which the pressurized fluid 29 generated by the vane cell pump 11 flows into the valve bore 15.
- the housing 23 has a throttle channel 30, which fluidly connects the pressure chamber 27 to a control chamber 17 on the rear side 32 of the control piston 14 via a pressure compensation bore 16 (throttle bore) from the pressure chamber 27 and a pressure compensation bore 16 'of the control chamber 17.
- the control piston 14 is acted upon by a spring 3 in the form of a compression coil spring 33 on an axial section 13 in the form of a guide pin 12.
- the spring 3 is supported on the housing wall 25 and on the guide mandrel 12 of the control piston 14, the spring force 5 causing the pressure compensator surface 28 of the control piston 14 to close the throttle opening 21 in the valve screw 26 when the flow control valve 10 is in the idle state.
- the pressure present in the control chamber 17 between the control piston 14 and the housing wall 25 causes a force which is in the same direction as the spring force 5 and which counteracts the pressure prevailing in the pressure chamber 27, the throttle opening 21 starting from a matched pressure of the fluid flowing into the valve bore 29 opens.
- the control piston thus forms a pressure compensator.
- a spring equipped in a known manner with at least two length ranges 6, 8 with different spring constants 7, 9 is used.
- the second length range 8 is followed by a third length range 18 of the spring 3 with the same spring constant 7 as the first length range 6.
- the number of resilient turns 20 of the third length range 18 is 2.6.
- the distance between the turns is the same as in the first length range (see FIG. 3).
- the second length range of the spring 3 changes its axial position to the pressure equalization bore 16 'little. With a further stroke of the control piston 14 beyond a kink length position (cf. " FIGS. 2 b and 4), the second length region 8 of the spring 3 is compressed. This results in a disproportionate increase in the spring force 5 on the control piston, whereby the pressure in the pressure chamber 27 and thus also the pressure in the wing cell pump is kept at a high level, and the degree of filling of the wing cell pump is improved at high volume flows and the characteristic curve of the wing cell pump is kept linear by the use of the spring 3 according to the invention.
- the length 4 of the spring 3 in a position of the control piston 14 in which its pressure compensator surface 28 bears against the throttle opening 21 of the valve screw 26 is a contact position - approximately 25.5 mm.
- the spring force 5 in this position is approximately 29 N (see FIG. 4).
- the length 4 of the spring 3 is approximately 22.5 mm and the spring force 5 is approximately 35 N.
- the length 4 of the spring 3 is approximately 17.5 mm and the spring force 5 is approximately 45 N.
- the spring has a wire diameter of 1.5 mm and a winding diameter of about 15 mm.
- the largest mandrel diameter D d is 13 mm and the smallest sleeve diameter D h is approximately 17 mm.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
- Safety Valves (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03735598A EP1523623B1 (de) | 2002-07-24 | 2003-06-11 | Nicht proportionales stromregelventil für eine flügelzellenpumpe |
DE50309423T DE50309423D1 (de) | 2002-07-24 | 2003-06-11 | Nicht proportionales stromregelventil für eine flügelzellenpumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10233579.6 | 2002-07-24 | ||
DE2002133579 DE10233579A1 (de) | 2002-07-24 | 2002-07-24 | Ventil für eine Pumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004015271A1 true WO2004015271A1 (de) | 2004-02-19 |
Family
ID=30010333
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/006091 WO2004015271A1 (de) | 2002-07-24 | 2003-06-11 | Nicht-proportionales stromregelventil für eine flügelzellenpumpe |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1523623B1 (de) |
DE (2) | DE10233579A1 (de) |
ES (1) | ES2301804T3 (de) |
WO (1) | WO2004015271A1 (de) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0528254A2 (de) * | 1991-08-08 | 1993-02-24 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Regeleinrichtung für Verdrängerpumpen |
DE19915555A1 (de) * | 1999-04-07 | 2000-10-12 | Zahnradfabrik Friedrichshafen | Verdrängerpumpe |
DE19948446A1 (de) * | 1999-10-08 | 2001-04-12 | Continental Teves Ag & Co Ohg | Progressive Saugventilfeder, insbesondere für Pumpen eines geregelten Bremssystems |
WO2001059301A1 (de) * | 2000-02-11 | 2001-08-16 | Zf Lenksysteme Gmbh | Regeleinrichtung für verdrängerpumpen |
-
2002
- 2002-07-24 DE DE2002133579 patent/DE10233579A1/de not_active Withdrawn
-
2003
- 2003-06-11 EP EP03735598A patent/EP1523623B1/de not_active Expired - Fee Related
- 2003-06-11 DE DE50309423T patent/DE50309423D1/de not_active Expired - Lifetime
- 2003-06-11 WO PCT/EP2003/006091 patent/WO2004015271A1/de active IP Right Grant
- 2003-06-11 ES ES03735598T patent/ES2301804T3/es not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0528254A2 (de) * | 1991-08-08 | 1993-02-24 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Regeleinrichtung für Verdrängerpumpen |
DE19915555A1 (de) * | 1999-04-07 | 2000-10-12 | Zahnradfabrik Friedrichshafen | Verdrängerpumpe |
DE19948446A1 (de) * | 1999-10-08 | 2001-04-12 | Continental Teves Ag & Co Ohg | Progressive Saugventilfeder, insbesondere für Pumpen eines geregelten Bremssystems |
WO2001059301A1 (de) * | 2000-02-11 | 2001-08-16 | Zf Lenksysteme Gmbh | Regeleinrichtung für verdrängerpumpen |
Also Published As
Publication number | Publication date |
---|---|
DE10233579A1 (de) | 2004-02-05 |
EP1523623B1 (de) | 2008-03-19 |
EP1523623A1 (de) | 2005-04-20 |
DE50309423D1 (de) | 2008-04-30 |
ES2301804T3 (es) | 2008-07-01 |
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