EP2501905A2 - Switchable pressure supply device - Google Patents
Switchable pressure supply deviceInfo
- Publication number
- EP2501905A2 EP2501905A2 EP10779801A EP10779801A EP2501905A2 EP 2501905 A2 EP2501905 A2 EP 2501905A2 EP 10779801 A EP10779801 A EP 10779801A EP 10779801 A EP10779801 A EP 10779801A EP 2501905 A2 EP2501905 A2 EP 2501905A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- switching
- pressure supply
- supply according
- housing
- 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
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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
-
- 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
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/04—Accumulators
-
- 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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0475—Hollow camshafts
-
- 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
- F01L1/3442—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 using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34446—Fluid accumulators for the feeding circuit
-
- 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
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- 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
- F15B2201/00—Accumulators
- F15B2201/20—Accumulator cushioning means
- F15B2201/21—Accumulator cushioning means using springs
-
- 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
- F15B2201/00—Accumulators
- F15B2201/30—Accumulator separating means
- F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
Definitions
- the invention relates to the technical field of internal combustion engines and relates to a switchable device for supplying pressure to at least one consumer of an internal combustion engine.
- German patent application DE 102007056684 A1 of the applicant shows a pressure accumulator with its own housing.
- German patent application DE 10228354 A1 describes an integrated in an inner cavity of a camshaft pressure accumulator, which space can be saved in the internal combustion engine.
- the object of the present invention is to further develop conventional pressure accumulators for supplying pressure to consumers in an internal combustion engine in an advantageous manner.
- a switchable device for supplying pressure (switchable pressure accumulator) to at least one consumer of an internal combustion engine.
- the consumer may in particular be a hydraulic camshaft adjuster for adjusting the phase angle between crankshaft and camshaft.
- the device is used for example in an electro-hydraulic valve actuating device of the internal combustion engine.
- the pressure supply device comprises a housing with a cavity.
- the cavity may, for example, be an internal cavity of a camshaft so that the camshaft forms the housing of the switchable device.
- a different from the hollow camshaft housing may be provided with a cavity, which is then inserted into an inner cavity of the camshaft.
- the device for pressure supply furthermore comprises a displacement element arranged in the housing cavity, which can be displaced between a first end position and a second end position.
- the displacement element has a pressure surface which, together with a wall of the housing cavity, at least partially delimits a reservoir which can be connected or connected to the load in a fluid-conducting manner.
- the pantry is with a Druck L. Pressure medium source fluidly connected or connected.
- the storage space is connected to the lubricating oil circuit of the internal combustion engine, wherein an oil pump serves as a pressure source and oil of the lubricating oil circuit is used as a pressure medium.
- the displacement element can For example, be formed in the form of a piston with a frontal pressure surface.
- the device according to the invention further comprises a force accumulator which cooperates with the displacement element so that the displacement element can be displaced from the first end position into the second end position by pressurizing the reservoir against the force of the force accumulator.
- the energy accumulator is designed for example as a spring element, in particular in the form of a compression spring, wherein any other suitable spring type can be used.
- the device according to the invention further comprises a locking mechanism, by means of which the displacement element can be releasably locked in the second end position in which the force accumulator is tensioned. In a different position of the displacement element from the second end position, in particular in the first end position, the displacement element can not be locked by the locking mechanism.
- the device according to the invention comprises an actuated by an actuator switching mechanism with a switching element, which can be brought into at least two switching positions, wherein the switching element cooperates with the locking mechanism, that the displacement element in a first switching position of the switching element from both an unlocked state locked is unlocked from a locked state and in a second switching position of the switching element in the unlocked state neither locked nor unlocked in the locked state.
- the inventive device allows for a comparatively small space requirement, a reliable and secure pressure supply to consumers of an internal combustion engine, which is independent of the pressure in the lubrication circuit of the internal combustion engine available.
- this includes a ball carrier element rigidly connected to the housing with a carrier cavity in which the switching element is at least partially accommodated.
- the ball carrier element has a plurality of openings, in each of which a ball is received radially movable. The balls are applied to an outer circumferential surface formed by the switching element.
- the device furthermore comprises a locking element which is rigidly connected to the displacement element and which is provided with a locking portion which, in the second end position of the displacement element, can engage with the balls, for example by engaging them behind, thereby forming the displacement element to lock on the housing.
- the locking element can not engage with the balls, so that the displacement element is not locked.
- a restoring element is further provided, which is arranged so that the switching element is displaceable relative to the force of the restoring element by the actuator from the first switching position to the second switching position relative to the ball carrier element.
- the first return element is formed, for example, as a spring element, in particular in the form of a compression spring, wherein any other suitable spring type can be used.
- the outer circumferential surface of the switching element is provided with at least one recess associated with the balls, which is formed and arranged so that the balls can be at least partially received in the recess in the second switching position of the switching element, so that the locking portion disengaged arrives with the balls and the locking of the displacement element is released.
- the balls are not received by the recess of the support surface in the first switching position of the switching element, so that the locking of the displacement element is maintained.
- a rigidly connected to the ball carrier element securing element is arranged, which forms a stop for a radially outward movement of the balls, such that the balls are taken secured against loss in the openings.
- this is cup-shaped and applied from one side to the ball carrier element.
- the securing element and the ball carrier element can be rigidly connected to one another by pressing, for example.
- the latter is provided with a closing element closing off the cavity to the outside, on which the force accumulator of the displacement element is supported.
- the closure element can serve in particular for securing the position of the force accumulator.
- the ball carrier element is rigidly connected to the closure element.
- the closure element is provided with a passage opening in which a cooperating with the switching element, actuated by the actuator switch body is received displaceably.
- the storage space can be fluidly connected or connected to the pressure source and possibly the consumer with the interposition of at least one outlet safety device.
- the leakage protection is designed so that it allows the flow of pressurized pressure medium, whereas it blocks the flow of non-pressurized, only the hydrostatic pressure underlying the pressure medium.
- the leakage protection can serve as a limitation of the storage space and can in particular form a stop for the displacement element in the first end position. The construction of such a leakage protection is known per se to a person skilled in the art and described in the patent literature, for example in DE 19615076.
- the pressure source via a blocking in the direction of the pressure source check valve with the reservoir space fluidly connected or connected.
- the invention further extends to an internal combustion engine which is equipped with at least one switchable device as described above for supplying pressure to at least one consumer.
- FIG. 1 is a schematic axial sectional view with enlarged detail of an embodiment of the inventive device for pressure supply
- FIG. 2 shows a schematic overview representation, with reference to which the connection of the device for supplying pressure to FIG. 1 to the lubricating oil circuit of an internal combustion engine is illustrated;
- 3A-3C are enlarged axial sectional views for illustrating the
- Locking the device for supplying pressure of Fig. 1; 4A-4C are enlarged axial sectional views illustrating the unlocking of the pressure supply apparatus of FIG. 1.
- Fig. 1 and Fig. 2 considered, wherein an embodiment of the inventive device for supplying pressure to consumers of an internal combustion engine, and the connection of the device to the lubricating oil circuit of an internal combustion engine are illustrated.
- the device generally designated by the reference numeral 1 can be inserted into a camshaft cavity 5 of a hollow camshaft 6.
- the camshaft 6 constructed here, for example, which is provided on its outer peripheral surface with a plurality of cams 25, can be rotated about a central axis of rotation 7. Equally, however, it would also be conceivable that the camshaft 6 is produced in the forging process.
- the device 1 for supplying pressure to consumers of an internal combustion engine comprises a hollow cylindrical housing 2 ("cartridge"), which is formed in a manner adapted to the camshaft cavity 5, so that the device 1 can be easily integrated into the camshaft 6 by the housing 2 in the camshaft cavity 5 is introduced and firmly connected to the camshaft 6.
- the housing 2 forms a housing cavity 3, in which a displacement element designed in the form of a piston 4 is received in an axially displaceable manner.
- a stepped cylinder closure body 7 is pressed, which extends from one end of the housing 2 ago in the housing cavity 3 inside. It may be divided into a larger diameter terminal first section 8 and an adjoining second smaller diameter section 9, thereby forming an annular step 10.
- a force storage spring serving as an energy accumulator (screw pressure spring) 1 1 with its one end, which abuts the piston 4 with its other end.
- the closure body 7 fixedly connected to the housing 2 is provided with a central axial bore 12 in which a switching rod 13 is received in an axially displaceable manner.
- the shift rod 13 can be actuated by an electromagnetic actuator 14, for which purpose a non-illustrated plunger engages a front-side abutment surface of the shift rod 13.
- the shift rod 12 is part of a switching mechanism for locking and releasing a locking mechanism for the piston 4, which will be explained in more detail below.
- the piston 4 has an end-face pressure surface 15 which, together with a housing cavity wall 16 of the housing cavity 3, at least partially delimits a reservoir 17 for pressurized oil.
- a hydraulic camshaft adjuster 18 is fastened to the end face of the camshaft 6, for example, by means of a central screw (not shown).
- the hydraulic camshaft adjuster 18 comprises a driving part which is drivingly connected to the crankshaft via a drive wheel and a camshaft-fixed drive part, as well as a hydraulic actuator connected between drive and driven part, which transmits the torque from the to the driven part and a Adjustment and fixation of the rotational position between these allows.
- the hydraulic actuator is provided with at least one oppositely acting pressure chamber pair, which can be targeted beaufschlagbar with pressure oil to bring about by creating a pressure gradient across the two pressure chambers, a change in the rotational position between the input and output part.
- Hydraulic camshaft adjusters as such are well known to the person skilled in the art and described in detail for example in the publications DE 202005008264 U1, EP 1596040 A2, DE 102005013141 A1, DE 19908934 A1 and WO 2006/039966 by the applicant, so that they need not be discussed in more detail here.
- the hydraulic camshaft adjuster 18 and the reservoir 17 are fluid-conductively connected via a pressure line 19 to a pressure or pressure medium source designed in the form of an oil pump 20.
- the pressure line 19 is connected to opening into the camshaft cavity 5 radial openings 26 of the camshaft 6.
- a non-return valve 22 arranged in the pressure line 19, which blocks in the direction of the oil pump 20, prevents a return of pressure oil at a reduced or missing delivery rate of the oil pump 20.
- a not-shown control valve for controlling the oil flows is arranged, through which the pressure chambers of the camshaft adjuster 18 can optionally be fluid-conductively connected to the oil pump 20 or to the oil tank 21.
- control valves are well-known to those skilled in the art as such and described in detail for example in the German patent DE 19727180 C2, the German patent DE 19616973 C2, the European patent application EP 1 596 041 A2 and the German patent application DE 102 39 207 A1 of the applicant, so that here does not need to be discussed further.
- the storage space 17 communicates with the hydraulic camshaft adjuster 18 or its control valve.
- other consumers are connected to the lubricating oil circuit, such as support members 23 and bearings 24 of the camshaft 6, which must be supplied with pressure oil.
- a leakage protection for limiting the storage space 17 may be provided, which may serve in particular as a stop for the piston 4.
- the piston 4 can be displaced axially by pressurizing the storage space 17 against the spring force of the energy storage spring 1 1 by pressure oil from the oil pump 20 via the pressure line 19 in the storage space 17 is promoted. In this case, the piston 4 is moved from a first end position to a second end position in which the energy storage spring 1 1 is stretched or more tensioned in the presence of a bias. About not shown ring seals the reservoir 17 is closed to the outside oil-tight.
- the locking mechanism comprises a sleeve-shaped ball carrier 31, which is pressed into a cup-shaped end section 27 of the closure body 7 and has a plurality of radial bores 29 distributed in the circumferential direction, in each of which a ball 30 is accommodated.
- the holes 29 each have a larger diameter than the balls 30, so that they are radially freely movable in the holes 29.
- the ball carrier 28 is rigidly connected to the closure body 7.
- a cup-shaped fuse body 31 consisting of a bottom wall 33 and a hollow cylindrical sleeve member 32, pressed.
- the sleeve part 32 of the securing body 31 is dimensioned such that it partially covers the radial bores 29 with a certain projection, so that only a certain radially outward movement of the balls 30 is made possible. Beyond that, radially outwardly directed movement of the balls 30 is blocked by the sleeve part 32, so that the balls 30 each remain received in the bores 29.
- switching pin 35 is received axially displaceable.
- the switching pin 35 has a first end face 36, which is coupled to a front end of the shift rod 35.
- a return spring 39 is further included, with one end to one of the first end face 37 opposite the second end face 37 of the switch pin 35 and with its other end to an inner surface 38 of Bottom wall 33 of the fuse body 31 is supported.
- the return spring 39 is formed here, for example, as a helical compression spring, but may also be of any other suitable spring type. The switching pin 35 can thus be displaced axially by moving the switching rod 13 by the plunger of the actuator 14 against the spring force of the return spring 39.
- the plunger acts on the front-side abutment surface of the shift rod 13, wherein the plunger is rigidly secured to a magnet armature of an electromagnet of the actuator 14 and can be moved axially by energizing the magnet armature. If the magnet armature is not energized, the switching pin 35 is reset by the spring force of the return spring 39.
- An outer circumferential surface 40 of the switching pin 35 is provided with a circumferential annular groove 41, which is assigned to the balls 30 and formed in a fit to the balls 30.
- the switching pin 35 can be moved back and forth between two end positions by the counteracting forces of actuator 14 and return spring 39. In a first end position without energization of the actuator 14, the balls 30 are outside of the annular groove 41st In a second end position with energized actuator 14, the balls 30 can dip into the annular groove 41. Always the balls 30 of the outer circumferential surface 40 of the switch pin 35, so that they are taken in connection with the fuse body 31 secured against loss in their holes 29.
- a locking body 42 is pressed on the piston 4, a locking body 42 is pressed.
- the locking body 42 is provided with a hollow-cylindrical sleeve section 43, which is applied to the cup-shaped piston 4, and is adjoined by a locking section 44.
- the sleeve portion 43 serves for axial guidance of the piston 4 within the housing cavity 3.
- the locking portion 44 tapers stepwise in the direction of the actuator 14 back.
- a first step 45 tapering towards the actuator 14 forms an annular support surface 47 for the energy storage spring 11.
- An adjoining second stage 46 tapering towards the actuator 14 forms an annular seating surface 48 for the balls 30.
- An integrally formed on the second step 46 Collar 52 which widens radially with respect to the second step 46, forms a contact surface 49 for the balls 30.
- FIGS. 3A-3E A locking or unlocking of the piston 4 of the device 1 will now be described, reference being made to FIGS. 3A-3E.
- the shift rod 13 is moved against the force of the return spring 39 by the plunger acting on the face-side abutment surface.
- the shift pin 35 is brought by the shift rod 13 into a position in which annular groove 41 is radially inwardly of the holes 29 and balls 30, so that the balls 30 can dip into the annular groove 41.
- the balls 30, urged by the locking portion 44 are pressed into the annular groove 41.
- the depth of the annular groove 41 is dimensioned such that the piston 4 or the locking portion 44 rigidly connected to the piston 4 can be displaced even further against the spring force of the energy storage spring 11.
- the balls 30 are completely received within the holes 29 and close at least approximately flush with an outer circumferential surface of the ball carrier 28 from. This situation is shown in Fig. 3B.
- Second end position An end position (referred to in the introduction as "second end position") of the piston 4 is defined, in which the storage space 17 is filled to the maximum with pressure oil. If the actuator 14 is no longer actuated, that is, the energization of the electromagnet is terminated, the shift pin 35 is axially displaced by the spring force of the return spring 39 relative to the ball carrier 28, wherein the balls 30 are pressed from the annular groove 41 against the seat surface 48 of the locking portion 44 , In this position, the locking portion 43 engages behind the balls 30, so that the piston 4 is axially fixed. This situation is shown in Fig. 3C.
- the piston 4 can thus be locked against the spring force of the return spring 39 from the first switching position to the second switching position in its second end position only by pressing the plunger to move the switching pin 35. Without displacement of the switching pin 35 in the second switching position, the piston 4 can not be locked.
- the piston 4 can thus be unlocked by pressing the plunger to move the switch pin 35 against the spring force of the return spring 39 from the first switching position to the second switching position. Without displacement of the switching pin 35 in the second switching position, the piston 4 can not be unlocked.
- the piston 4 In the device according to the invention can thus be biased by a separate housing in a cavity of the camshaft piston by the pressure of the oil pump with the internal combustion engine running against the power storage spring up to a fixed stroke. In this position, the piston engages by a short energizing the radially decoupled actuator, which is mounted outside the camshaft, in a holding mechanism (ball lock). When the engine is switched off, the oil pressure in the oil galleries drops to ambient pressure, as does the pressure in the accumulator.
- An optional leakage protection means that the "pressure-free" lubricating oil can not run back from the storage room into the oil galleries or via the camshaft bearing points into the cylinder head.
- a leakage protection for example, a lamellar labyrinth leakage protection, consisting of three sheets, each with a bore in the axial direction on the outer diameter. The sheets are rotated by 120 ° to each other. The pressure accumulator has no pressure loss due to leaks. Expensive high-pressure seals are eliminated. As a result, the system friction is reduced and stored more usable energy in the energy storage spring.
- the locking mechanism of the piston can be released.
- the prestressed energy storage spring For example, the oil from the reservoir is forced back into the oil circuit of the cylinder head and the phaser, provided that the supply oil pressure in the oil galleries is less than the pressure achievable with the accumulator (spring element force multiplied by piston pressure area).
- a non-return valve in the direction of the oil pump is provided between the oil pump and the consumers, which are to be acted upon by oil pressure from the pressure accumulator.
- the piston is guided axially in the housing and is supported by a spring element (eg tension or compression spring) on the closure body, which is pressed into the housing. In the closure body of the ball carrier is pressed.
- the shift rod is coupled to the shift pin and mounted axially displaceable in the closure body.
- the actuator is screwed, for example, in the cylinder head and presses in the energized state on the shift rod against the return spring of the switch pin.
- the fuse body serves as a captive for the balls.
- the arrangement in the cavity of the camshaft results in a space advantage over externally arranged camshaft pressure accumulators.
- the device according to the invention enables a reliable pressure supply of consumers of an internal combustion engine, wherein pressure oil is independent of the engine oil supply (lubricating oil circuit) of the internal combustion engine available through the pressure accumulator integrated in the camshaft.
- pressure oil is independent of the engine oil supply (lubricating oil circuit) of the internal combustion engine available through the pressure accumulator integrated in the camshaft.
- consumers can be supplied with pressurized oil even when the oil supply on the engine side is insufficient, for example when starting the engine and when the oil pressure is very high in conjunction with a low flow rate of the oil pump (hot idling).
- an adjustment of the camshaft adjuster in basic position (late, middle, early position) take place, which is particularly suitable in connection with Start / stop systems is.
- the adjustment speed of the camshaft adjuster can be improved, in particular when the internal combustion engine is idling.
- the device of the invention can be realized by relatively few components, which costs in the industrial mass production assembly and material can be saved.
- a particular advantage of the device results from the fact that the piston can be locked or unlocked by briefly energizing the actuator (current pulses). A permanent energization of the actuator in the locked or unlocked state of the piston is not required. This allows a particularly energy-saving operation of the device for pressure supply.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009054055A DE102009054055A1 (en) | 2009-11-20 | 2009-11-20 | Switchable device for pressure supply |
PCT/EP2010/067658 WO2011061217A2 (en) | 2009-11-20 | 2010-11-17 | Switchable pressure supply device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2501905A2 true EP2501905A2 (en) | 2012-09-26 |
EP2501905B1 EP2501905B1 (en) | 2014-09-17 |
Family
ID=43902038
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10779801.9A Not-in-force EP2501905B1 (en) | 2009-11-20 | 2010-11-17 | Switchable pressure supply device |
Country Status (5)
Country | Link |
---|---|
US (1) | US8813709B2 (en) |
EP (1) | EP2501905B1 (en) |
CN (1) | CN102667073B (en) |
DE (1) | DE102009054055A1 (en) |
WO (1) | WO2011061217A2 (en) |
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DE102009054052B4 (en) * | 2009-11-20 | 2018-08-23 | Schaeffler Technologies AG & Co. KG | Switchable device for pressure supply |
DE102011114894B4 (en) * | 2010-10-08 | 2013-05-16 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Accumulator arrangement |
DE102010063390A1 (en) | 2010-12-17 | 2012-06-21 | Schaeffler Technologies Gmbh & Co. Kg | Pressure accumulator unit for supporting e.g. camshaft for supporting during starting engine of vehicle, has guide comprising hollow-cylinder-shaped base element and ring-shaped bearing element that is arranged between base element and rod |
DE102012210795B3 (en) * | 2012-06-26 | 2013-09-19 | Schaeffler Technologies AG & Co. KG | Pressure accumulator for e.g. balancing operational pressure fluctuation in line system of internal combustion engine, has locking device that is provided with locking pipe which is connected with piston |
DE102013111617B4 (en) | 2013-10-22 | 2021-12-23 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Changeover valve and internal combustion engine with such a changeover valve |
DE102013111616B4 (en) | 2013-10-22 | 2021-12-23 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Changeover valve and internal combustion engine with such a changeover valve |
DE102014226150A1 (en) * | 2014-12-17 | 2016-06-23 | Zf Friedrichshafen Ag | Hydraulic system for an automatic transmission |
CN110088430A (en) * | 2016-09-09 | 2019-08-02 | Jp领域股份有限公司 | Route-variable valve equipment for internal combustion engine |
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DE19615076C2 (en) | 1995-12-15 | 1999-01-07 | Schaeffler Waelzlager Ohg | Pressure medium supply for a variable camshaft adjustment |
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DE19908934A1 (en) | 1999-03-02 | 2000-09-07 | Schaeffler Waelzlager Ohg | Device for adjusting the angle of rotation of a camshaft |
DE10050225A1 (en) | 2000-10-11 | 2002-04-25 | Hydraulik Ring Gmbh | Actuating device for fixing a camshaft of a drive engine of a vehicle, preferably a motor vehicle, in a starting position |
US6782856B2 (en) * | 2002-04-09 | 2004-08-31 | Ford Global Technologies, Llc | Camshaft accumulator |
DE10228354B4 (en) | 2002-06-25 | 2017-06-22 | Daimler Ag | Device for supplying pressure to a camshaft adjusting device |
DE10239207A1 (en) | 2002-08-27 | 2004-03-11 | Ina-Schaeffler Kg | Electromagnetic hydraulic valve, in particular a proportional valve for controlling a device for adjusting the angle of rotation of a camshaft relative to a crankshaft of an internal combustion engine |
DE102004035035B4 (en) * | 2003-07-24 | 2022-04-14 | Daimler Ag | Camshaft adjusters for internal combustion engines |
DE10337430A1 (en) | 2003-08-13 | 2005-03-17 | Fev Motorentechnik Gmbh | Internal combustion engine with shift cam |
CN2746125Y (en) * | 2004-03-25 | 2005-12-14 | 周晓仪 | Electromagnetic valve stopping device of single overhead cam shaft motor |
EP1596040B1 (en) | 2004-05-14 | 2010-10-13 | Schaeffler KG | Camshaft phaser |
DE102004038252A1 (en) | 2004-05-14 | 2005-12-15 | Ina-Schaeffler Kg | Control valve for a device for changing the timing of an internal combustion engine |
DE102004049123A1 (en) | 2004-10-07 | 2006-04-13 | Ina-Schaeffler Kg | Device for changing the timing of gas exchange valves of an internal combustion engine |
DE102005013141B4 (en) | 2005-03-22 | 2017-10-19 | Schaeffler Technologies AG & Co. KG | Device for adjusting the camshaft of an internal combustion engine |
DE202005008264U1 (en) | 2005-05-23 | 2005-08-25 | Ina-Schaeffler Kg | Device for variable adjustment of gas exchange valve timing in IC engines has housing projecting into radial profile of on outer stator jacket surface for positive connection |
DE102005037480A1 (en) * | 2005-08-09 | 2007-02-15 | Schaeffler Kg | Control valve and method of making the same |
WO2008067935A2 (en) * | 2006-12-04 | 2008-06-12 | Daimler Ag | Regulating device |
FI121895B (en) | 2007-01-03 | 2011-05-31 | Waertsilae Finland Oy | Reciprocating Engine |
WO2008140897A1 (en) | 2007-05-14 | 2008-11-20 | Borgwarner Inc. | Cam mounted accumulator |
DE102007056684B4 (en) | 2007-11-24 | 2016-02-18 | Schaeffler Technologies AG & Co. KG | accumulator |
FR2933471B1 (en) * | 2008-07-03 | 2013-02-15 | Vianney Rabhi | BALANCED ELECTRO-HYDRAULIC VALVE FOR A VARIABLE COMPRESSION RATE MOTOR HYDRAULIC CONTROL UNIT |
DE102010045358A1 (en) * | 2010-04-10 | 2011-10-13 | Hydraulik-Ring Gmbh | Schwenkmotornockenwellenversteller with a hydraulic valve |
-
2009
- 2009-11-20 DE DE102009054055A patent/DE102009054055A1/en not_active Withdrawn
-
2010
- 2010-11-17 CN CN201080052599.3A patent/CN102667073B/en not_active Expired - Fee Related
- 2010-11-17 US US13/510,702 patent/US8813709B2/en not_active Expired - Fee Related
- 2010-11-17 WO PCT/EP2010/067658 patent/WO2011061217A2/en active Application Filing
- 2010-11-17 EP EP10779801.9A patent/EP2501905B1/en not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2011061217A2 * |
Also Published As
Publication number | Publication date |
---|---|
DE102009054055A1 (en) | 2011-05-26 |
CN102667073B (en) | 2015-05-06 |
US20120304953A1 (en) | 2012-12-06 |
US8813709B2 (en) | 2014-08-26 |
EP2501905B1 (en) | 2014-09-17 |
WO2011061217A2 (en) | 2011-05-26 |
WO2011061217A3 (en) | 2011-07-21 |
CN102667073A (en) | 2012-09-12 |
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