WO2005098205A1 - Cartridge valve, especially for a camshaft regulator - Google Patents
Cartridge valve, especially for a camshaft regulator Download PDFInfo
- Publication number
- WO2005098205A1 WO2005098205A1 PCT/EP2005/002349 EP2005002349W WO2005098205A1 WO 2005098205 A1 WO2005098205 A1 WO 2005098205A1 EP 2005002349 W EP2005002349 W EP 2005002349W WO 2005098205 A1 WO2005098205 A1 WO 2005098205A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cartridge valve
- valve according
- connection
- cartridge
- recess
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
Definitions
- the invention relates to a cartridge valve, in particular for camshaft adjusters, according to the preamble of claim 1.
- Cartridge valves are used, for example, in camshaft adjusters to control the pressure medium supply to the camshaft adjuster.
- the cartridge valves have as drive part a magnetic part to which a valve part is connected.
- the valve member is installed in a receiving block, which may be the cylinder head, the engine block or a special valve block.
- the valve member has a bush which is provided on the outside with circumferentially extending depressions, which are formed either as annular grooves or Operaringnuten. In these recesses opens at least one passage opening.
- the valve member must be installed in the receiving block so that provided in the receiving block supply bores for the pressure medium reach the corresponding wells.
- Valve parts of cartridge valves are also known, which instead of the recesses have through holes which must be exactly aligned with the supply holes when installing the cartridge valve.
- the distance between the depressions or these position-oriented bores largely depends on the construction of the piston located in the bush or the volume flow of the pressure medium to be realized.
- the invention is based on the object, the generic cartridge valve in such a way that it is used for different installation situations. can be set, in which the distance between the supply holes of the receiving block for the cartridge valve is different.
- the recess has a length and / or width dimension which is greater than the cross section of the terminal.
- the recess forms an oil distribution channel that can be created by machining or casting the socket. Through a passage opening in this recess, a line connection can be made with inner ring channels on the inside of the socket.
- the bushing has a plurality of depressions corresponding to the number of connections of the cartridge valve.
- FIG. 1 is a side view of an inventive cartridge valve, 2 partially in axial section along the line AA in Fig. 4 and partly in side view of the inserted into a receiving block cartridge valve of FIG. 1,
- FIG. 7 is a side view of a second embodiment of a cartridge valve according to the invention.
- FIG. 12 shows a section along the line E-E in FIG. 8.
- the cartridge valve is provided for phaser and has a solenoid part 1 and a valve part 2.
- the cartridge valve is inserted with the valve part 2 into a receiving block 12, which may be a cylinder head, an engine block, a valve receiving block or the like.
- the magnet part 1 has a cylindrical housing 3 which has a plug connection 4 at its end remote from the valve part 2.
- a tab 5 is fixed, which projects transversely from the housing and with which the cartridge valve is mounted on the receiving block.
- the magnet part 1 contains in a known manner at least one coil, in whose energization an armature is displaced axially, which is connected to a plunger 6. With it, a piston 7 can be moved in the valve member 2 against the force of at least one compression spring 8.
- the valve member 2 has a sleeve 9 which engages with one end in a central recess 10 in the valve part side end face 1 1 of the housing 3 and is secured there in a suitable manner.
- the bush 9 is sealed relative to the housing 3 by at least one seal which is provided in the bottom of the recess 10.
- the bush 9 is provided near the magnet part 1 with an annular groove 13 which receives a ring seal 14, with which the valve member 2 is sealed in the receiving space of the receiving block.
- the piston 7 is axially displaceable in the sleeve 9 and has a closed bottom 15 against which the plunger 6 of the magnetic part 1 is applied.
- the opposite end of the hollow piston 7 is open.
- the compression spring 8 which is supported at one end to a radial annular shoulder 16 in the inner wall of the piston 7.
- the other end of the compression spring 8 bears against a ring 17, which is advantageously screwed into the free end of the bushing 9.
- the bias of the compression spring 8 can be optimally adjusted continuously.
- the sleeve 9 has on the inside two annular grooves 18 and 19, which have axial distance from each other.
- the piston 7 has near the bottom 15 on the circumference evenly distributed through holes 20. Adjacent to the free end of the hollow piston 7 is provided with further, uniformly distributed over the circumference arranged through holes 21.
- the distance between the passage openings 20 and 21 is greater than the distance between the annular grooves 18 and 19th
- the sleeve 9 has on its outer side at the level of the inner annular grooves 18, 19 each have a distribution channel 22, 23 (Fig. 1), is reliably achieved by the hydraulic medium through holes in the receiving block to the annular grooves 18, 19 and the Through openings 20, 21 can get.
- the two distribution channels 22, 23 are the same design, but arranged in mirror image to each other. As shown in FIG. 1, the distribution channels 22, 23 each have a U-shape.
- the two legs 24, 25 of the magnetteil documenten distribution channel 22 extend axially in the direction of the magnetic part 3.
- the legs 26, 27 of the distribution channel 23 are also axially and at the same height with the legs 24, 25 of the distribution channel 22.
- the two legs 24th , 25 and 26, 27 are connected to each other by a perpendicular to them and in the circumferential direction of the housing extending transverse part 28, 29 with each other.
- the two cross members 28, 29 are at a distance from each other.
- Between the transverse parts 28, 29 of the distribution channels 22, 23 remains a web 34 which extends in the circumferential direction of the bushing 9 and has constant width.
- the distribution channels 22, 23 are provided so that their legs 24, 25 and 26, 27 each extend to the level of the annular grooves 18, 19 in the inner wall of the bush 9. As is apparent from Figs. 1 and 3, the legs 24, 25 extend; 26, 27 of the distribution channels 22, 23 approximately over half its length in the region of the annular grooves 18, 19.
- the transverse parts 28, 29 are outside the range of the annular grooves 18, 19th
- passage openings 30, 31 are provided which connect the distribution channels 22, 23 with the inner ring grooves 18, 19 (Fig. 1 and 3).
- the passage openings 30, 31 are advantageously formed as diaphragms.
- the legs 24, 25; 26, 27 are at an angle to the axial direction or, for example, also have a V-shaped design.
- the distribution channels 22, 23 are designed in any case so that also different distances between Zutechnischsboh- ments in the receiving block with the corresponding inner ring grooves 18, 19 and the through holes 20, 21 can be brought into connection.
- the free ends of the legs 24, 25, 26, 27 of the two distribution channels 22, 23 have the distance a from each other (Fig. 1).
- the legs 24, 25, 26, 27 have a length b.
- the receiving block 12 has two working ports A, B and a pressure port P, which are each formed as radial bores (Fig. 4 to 6).
- the axis of the working connection A has the axial distance d from the longitudinal axis of the web 34 (FIG. 2).
- the working port B has the axial distance e from the longitudinal axis of the web 34.
- the two distances d, e are advantageously the same.
- the distances d, e are greater than the length b of the legs 24, 25, 26, 27 of the distribution channels 22, 23, but smaller than the distance a of the free ends of the legs 24, 25, 26, 27 from each other.
- the axes of the two working ports A, B have the axial distance c from each other, which corresponds to the sum of the distances d and e, but is smaller than the distance a.
- optimum position of the socket 9 in the receiving block 12 cover the terminals A, B, the cross members 28, 29 of the distribution channels 22, 23 about halfway.
- the radial working ports A, B is in each case assigned to one of the two distribution channels 22, 23.
- the valve member 2 is provided with the radial pressure port P, via which the hydraulic medium is supplied under pressure to the cartridge valve.
- the magnetic member 1 is not energized, so that the plunger 6 is withdrawn and the piston. 7 under the force of the compression spring 8 assumes its one end position.
- the pressure port P which is formed by at least one radial bore 33 in the bush 9 (FIG. 3), is in this position of the piston 7 with an annular groove 32 in the outer circumferential surface of the piston 7 in connection.
- the pressure port P can be connected to the inner ring channel 18 or 19 of the bushing 9, which has a line connection with the distribution channel 22 and 23, depending on the position of the piston 7.
- the hydraulic medium can thus via the pressure port P, the annular groove 32, the inner ring channel 18 or 19 and the distribution channel 22 or 23 to the working port A or B flow.
- the other working port is separated from the pressure port P by the piston 7.
- the magnetic part 1 is energized, so that the plunger 6 is moved in Figs. 2 and 3 to the right.
- the working connection A or B not connected to the pressure connection P is connected to an axial tank connection T, so that the hydraulic medium displaced via the working connection A or B can flow through the piston 7 to the tank T.
- the hydraulic medium flows through the open piston end and the ring 17th
- angles x, y, z between the axes of the connections A, B, P and the distribution channels 22, 23 indicated in FIGS. 4 to 6 can be variable.
- the two working ports A, B are connected to the corresponding pressure chambers of the camshaft adjuster. It has a stator with radially inwardly projecting vanes, which are provided at a distance from one another along the circumference of the stator and bear sealingly against the lateral surface of a cylindrical main body of a rotor. He sits non-rotatably on the camshaft and has from its base radially outwardly projecting wings. They engage in the area between each two adjacent stator blades and are sealingly against the inner wall of the stator. Between each rotor blade and the adjacent stator blades a pressure chamber is formed in each case, which is connected to the working ports A and B of the cartridge valve.
- the stator is non-rotatable with a drive wheel connected, which is drivingly connected via a chain or a belt with a crankshaft of the internal combustion engine. Sn of an end position of the rotor are its wings on a side wall of the stator at. From this end position of the rotor can be rotated relative to the maximum maximum so that the rotor blades abut the opposite stator blades. This relative rotation of the rotor with respect to the stator takes place in that, depending on the desired direction of rotation of the working port A or B of the cartridge valve is connected to the respective pressure chamber of the camshaft adjuster. In the relative rotation of the rotor located in the non-pressurized pressure chamber hydraulic medium is displaced in the manner described to the tank T via the cartridge valve.
- the pressure port P may also be provided axially and the tank port T radially.
- the radial pressure or tank connection P, T is advantageously also associated with a distribution channel 22.
- the embodiment according to FIGS. 7 to 12 differs from the previous embodiment only in that the bush 9 has no inner ring channels or annular grooves.
- the distribution channels 22, 23 are in line connection with the working ports A, B in the receiving block 12.
- the bushing 9 receives the piston 7, which has the annular groove 35 in its outer circumferential surface.
- the pressure port P can be conductively connected depending on the position of the piston 7 to the working port A or B.
- the distances a to e are equal to each other in relation to the previous embodiment.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
- Magnetically Actuated Valves (AREA)
- Lift Valve (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE502005000069T DE502005000069D1 (en) | 2004-04-02 | 2005-03-05 | CARTRIDGE VALVE, ESPECIALLY FOR CAMSHAFT ADJUSTERS |
EP05715769A EP1623099B1 (en) | 2004-04-02 | 2005-03-05 | Cartridge valve, especially for a camshaft regulator |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004017790A DE102004017790A1 (en) | 2004-04-02 | 2004-04-02 | Cartridge valve, in particular for camshaft adjuster |
DE102004017790.2 | 2004-04-02 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005098205A1 true WO2005098205A1 (en) | 2005-10-20 |
Family
ID=34961128
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2005/002349 WO2005098205A1 (en) | 2004-04-02 | 2005-03-05 | Cartridge valve, especially for a camshaft regulator |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1623099B1 (en) |
AT (1) | ATE337473T1 (en) |
DE (2) | DE102004017790A1 (en) |
WO (1) | WO2005098205A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011051656A1 (en) | 2011-07-07 | 2013-01-10 | Hydraulik-Ring Gmbh | Slew motor adjuster for internal combustion engine, has rotor rotatably connected with camshaft, where rotor is pivotable in opposite set pivot direction against stator and hydraulic piston that is displaceable within guide bore |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5247965A (en) * | 1990-11-05 | 1993-09-28 | Aisin Aw Co., Ltd. | Linear solenoid valve apparatus |
US6089575A (en) * | 1997-03-15 | 2000-07-18 | Ina Walzlager Schaeffler Ohg | Sealed seat for a hydraulic switching element in a mounting space for a direct-controlled cartridge valve in an insertion bore |
-
2004
- 2004-04-02 DE DE102004017790A patent/DE102004017790A1/en not_active Withdrawn
-
2005
- 2005-03-05 AT AT05715769T patent/ATE337473T1/en not_active IP Right Cessation
- 2005-03-05 EP EP05715769A patent/EP1623099B1/en active Active
- 2005-03-05 WO PCT/EP2005/002349 patent/WO2005098205A1/en not_active Application Discontinuation
- 2005-03-05 DE DE502005000069T patent/DE502005000069D1/en active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5247965A (en) * | 1990-11-05 | 1993-09-28 | Aisin Aw Co., Ltd. | Linear solenoid valve apparatus |
US6089575A (en) * | 1997-03-15 | 2000-07-18 | Ina Walzlager Schaeffler Ohg | Sealed seat for a hydraulic switching element in a mounting space for a direct-controlled cartridge valve in an insertion bore |
Also Published As
Publication number | Publication date |
---|---|
DE102004017790A1 (en) | 2005-10-20 |
ATE337473T1 (en) | 2006-09-15 |
EP1623099A1 (en) | 2006-02-08 |
DE502005000069D1 (en) | 2006-10-05 |
EP1623099B1 (en) | 2006-08-23 |
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