WO2015043589A2 - Federanordnung für eine hydraulische betätigungsvorrichtung - Google Patents
Federanordnung für eine hydraulische betätigungsvorrichtung Download PDFInfo
- Publication number
- WO2015043589A2 WO2015043589A2 PCT/DE2014/200441 DE2014200441W WO2015043589A2 WO 2015043589 A2 WO2015043589 A2 WO 2015043589A2 DE 2014200441 W DE2014200441 W DE 2014200441W WO 2015043589 A2 WO2015043589 A2 WO 2015043589A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- spring
- piston
- deflection
- spring arrangement
- arrangement
- Prior art date
Links
- 238000010521 absorption reaction Methods 0.000 claims description 5
- 239000000725 suspension Substances 0.000 abstract description 2
- 238000012986 modification Methods 0.000 abstract 1
- 230000004048 modification Effects 0.000 abstract 1
- 230000000903 blocking effect Effects 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/083—Actuators therefor
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
Definitions
- the invention relates to a spring arrangement for a hydraulic actuating device, in particular for a friction clutch of a motor vehicle.
- Hydraulic actuators are known from the prior art, which comprise a helical spring, with which the piston of the actuating device is supported in the release direction. This prevents that when the piston is moved backwards unsprung and undamped is moved into a stop or that the piston is held in a Wegitzung, without the need for a hydraulic pressure is required.
- a coil spring is permanently under tension and in case of damage to the biasing device or when blocking the coil spring, the piston is pressed into the friction clutch or prevents disengagement of the friction clutch in, for example, an overload, whereby the damage can be large.
- the present invention has the object, at least partially overcome the known from the prior art disadvantages.
- the object is solved by the features of the independent claims.
- Advantageous developments are the subject of the dependent claims.
- the invention relates to a spring arrangement for a hydraulic actuating device, which has at least the following components:
- a stop element which is adapted to a Axialkraftement a
- the deflection device is adapted to, when the piston is moved back from a disengaged position and a predetermined target position is reached, to deflect the spring means only when falling below the predetermined desired position, and so to produce a spring force
- the spring means is adapted to direct the said spring force by means of the stop element in the axial direction to the Axialkraftement.
- the spring arrangement proposed here is set up to prevent excessive force application during the rearward movement of a piston of a hydraulic actuating device or to prevent the piston in a minimal position hold without requiring (large) hydraulic pressure.
- the spring arrangement initially has a stop element which acts in the actuating direction of the piston on an axial force absorption of the piston.
- a stop element may for example be a ring element, which acts against a shoulder of the piston, which forms the Axialkraftfact.
- the stop element can at the same time have the task of at least partially holding the spring arrangement together.
- a deflection device is provided, which is configured to deflect the spring device of the spring arrangement and thus exert a force on the piston.
- the spring force thus generated in the interaction between the deflection device and the spring device is transmitted via the stop element to the axial force absorption of the piston.
- the spring force between the deflection device and the spring device is generated only when it falls below a predetermined desired position. This can be achieved, in particular, in that the deflection device and the spring device are, for example, axially spaced apart from each other as long as the predetermined target position is exceeded. This has the effect on the one hand that the introduction of the spring force takes place in the axial direction on the Axialkraftability only when the piston falls below the predetermined target position and, secondly, the piston can not be driven out by the spring arrangement proposed here in case of damage to the spring assembly from its position and damage parts of the friction clutch.
- the minimum displacement of the piston is assigned a zero path and the maximum piston displacement is assigned a higher numerical value path.
- the piston is in falling below the target position on a path portion between the minimum deflection and the predetermined target position and when exceeding the predetermined target position on a path portion between the maximum deflection and the predetermined target position.
- a minimum stop is furthermore provided, which ensures a minimum deflection of the piston in cooperation with the spring device and / or the deflection device.
- a piston sealing elements are provided, which may be mechanically loaded alone with the hydraulic fluid. To prevent them coming into contact with the back wall or other elements in the pressure chamber, should a minimum stop be provided. It is particularly advantageous to use the spring arrangement proposed here for generating a minimum deflection by providing a minimum stop here. This can, for example, act on the spring device by being deflected in such a way that further movement is not possible, or it can act on the deflection device, so that the deflection device is in contact with the minimum stop and further movement of the piston in this direction not possible.
- a guide is furthermore provided which prevents an uncontrolled rotation of components of the spring arrangement, the guide preferably comprising at least one sheet which forms a guide rail for the spring device and / or for the deflection device.
- the actuating piston communicates with the rotating components of a friction clutch, in which case a bearing is provided, which allows a relative movement between the rotating parts and the actuating piston.
- a rotation can be induced in the actuating piston, which in turn can damage the seal of the actuating piston.
- the coil spring With the use of the coil spring a measure against the rotation in both directions is not possible.
- a rotation can be prevented, which can in particular also prevent a rotation of the piston of the actuating device via the stop element.
- the guide can be designed as at least one sheet, which forms an axial guide rail for the spring device and / or the deflection device.
- the spring device comprises at least one leaf spring and the deflection device has at least one corresponding cam, by means of which the spring device can only be deflected when the predetermined desired position is undershot.
- the spring device is formed by a leaf spring, which is preferably deflected in its axial extent.
- the leaf spring extends in this preferred embodiment, approximately in the axial direction, while it may also be inclined slightly to the axial direction of movement, for example by 5 °, 10 ° or 20 °.
- the leaf spring may also have a diffraction such that the angle changes over the length of the leaf spring with respect to the axial direction of movement of the piston.
- the corresponding cam of the deflection device is preferably transversely to the deflection arranged device, and as soon as the exposed from the stop element exposed tip of the leaf spring reaches the corresponding cam, because the piston falls below the predetermined target position, the leaf spring is deflected, so that a force is generated, which at least over the stop member in an axial force on the piston is implemented.
- no force is exerted on the spring device above the predetermined desired position and thus also exerts the spring means no force on the stop element on the piston.
- the at least one corresponding cam is fixed and only the spring device can be deflected.
- This preferred embodiment allows a particularly simple construction, in which the corresponding cam is fixed, for example by a deformation of a component, which may be, for example, a wall surrounding the spring arrangement or a fixed bolt.
- the spring device is particularly advantageous inclined or curved designed so that it comes into contact with the top in undeflected position falls below the target position with the cam and is deflected at further below the target position due to the cam of the inclined orientation of the spring device.
- a leaf spring is particularly well suited to be guided with a metal sheet or between two sheets, so that rotation of the piston is prevented.
- a plurality of leaf springs are provided, for example, four leaf springs (evenly) distributed over the circumference, which are interconnected via the stop element.
- the spring device comprises at least one cam spring-mounted in a spring direction, wherein the spring direction is arranged inclined to the axial direction of movement of the piston, and wherein the deflection device falls below the predetermined target position, the spring means passes such that the spring means in the spring direction from a relaxed position is deflected into a cocked position, wherein the spring direction is preferably between 45 ° and 135 °, particularly preferably aligned transversely to the axial direction of movement.
- a spring-loaded cam which is deflectable in the spring direction.
- the spring device is arranged inclined to the axial direction of movement of the piston; a deflection of the force takes place via the deflection device which deflects the spring device when it falls below the predetermined desired position.
- the deflection device can preferably also be shaped as described above, the leaf spring, wherein the deflection device has a significantly higher rigidity, so that the corresponding spring force is generated mainly via the spring-loaded cam.
- the cam is formed as a sheet metal sleeve, in which a coil spring is guided and encapsulated, so that the cam is guided, without a transverse load on the coil spring takes place.
- the spring direction of the spring device is adapted to the alignment of the deflection device, so that a simple axial movement of the deflection device leads to a deflection of the spring device as soon as the deflection device deflects the spring device when it falls below the desired position.
- the cam is aligned transversely to the axial direction of movement of the piston and the deflection device is a tilted or bent plate, which acts on falling below the predetermined target position on the cam so that it is deflected laterally.
- a hydraulic actuating device for a friction clutch which has at least the following components:
- At least one piston which is hydraulically reciprocable in the pressure cylinder
- the hydraulic actuator is preferably a Gottausschreiber, which surrounds an output shaft of a friction clutch, so that the piston and the pressure cylinder are formed as a ring body.
- the piston has at its rear side on a seal which seals the hydraulic pressure cylinder and ensures that the piston allows a pressure build-up due to a filling of the pressure cylinder, wherein at the same time the piston due to the pressure build-up is movable back and forth.
- a spring arrangement according to the above description is particularly advantageous.
- the piston Upon return of the piston from a deflected position, an axial force is exerted on the piston with this spring arrangement only when falling below the predetermined desired position, which is arranged above the minimum deflection of the piston.
- the force exerted by the piston alone is dependent on the pressure, so that the adjustment and regulation of the pressure of the piston to the components of Reibkupp- is simplified.
- the piston can not be expelled from the assembly in case of damage to the spring assembly and thus not damage the components of the friction clutch. Also, blocking the spring assembly as proposed herein is very unlikely or impossible.
- the spring arrangement can be made particularly cost compared to a coil spring. Most preferably, can be prevented via the guide, for example by means of sheets on the spring assembly, a rotation of the piston, whereby the seals of the piston are relieved.
- a measuring device is further provided, which detects a deflection of the piston, wherein preferably the spatial position of a geometric expression element of the spring device and / or the deflection device is detected.
- the spring arrangement as proposed herein can be clearly determined in its axial position so that it is well suited to measuring the position of the piston.
- a measuring device can be provided where the actuating device is outside the coupling region, so that the number of components in the coupling region can be reduced and thus the size of the friction clutch can be reduced.
- a malfunction of the piston can be registered via the measuring device if, for example, the applied pressure does not coincide with the actual position as intended.
- Rotary axis for releasably connecting an output shaft proposed with a drive train which has at least the following components:
- At least one hydraulic actuator according to the above description, which can be pressed or released by their operative engagement with the friction pack, the Reibpakte.
- the friction clutch has a friction pack with a pressure plate and at least one corresponding friction disc. If the pressure plate is pressed against the at least one corresponding friction disk, a torque can be transmitted as a result of the frictional force. If the contact pressure is released, no or only a small torque is transmitted.
- the pressing or releasing is done by means of the hydraulic actuator.
- the hydraulic actuator can act directly on the pressure plate or indirectly via, for example, a plate spring with the pressure plate in contact. With the Spring arrangement according to the above description prevents the actuator is blocked or the piston is driven into the Reibb. In addition, only the hydraulic pressure is involved in the power transmission by the actuator, so that the design and operation of the friction clutch is facilitated.
- a motor vehicle which has a drive unit with an output shaft, a drive train and a friction clutch as described above.
- Passenger cars are classified according to vehicle class according to, for example, size, price, weight, power, but this definition is subject to constant change according to the needs of the market.
- vehicles of the class small cars and microcars are classified according to European classification of the class of subcompact car and in the British market they correspond to the class Supermini, for example, the class City Car.
- micro car class are a Volkswagen Fox or a Renault Twingo.
- Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.
- Fig. 1 a hydraulic actuator with conventional coil spring
- Fig. 2 a deflected hydraulic actuator with spring arrangement
- Fig. 3 a retracted hydraulic actuator with spring assembly
- FIG. 6 shows a spring device with a stop element
- Fig. 7 an alternative spring means and deflection device
- Fig. 8 a motor vehicle with friction clutch.
- Fig. 1 shows a hydraulic actuator 2 with a conventional
- Coil spring 38 which permanently biases the piston 5 in the pressure cylinder 25 by the spring support 40 and contributes to the actuation force 39.
- Fig. 2 shows a hydraulic actuator 2, in which the piston 5 is at the predetermined target position 10 and, as shown here, below the hydraulically disengaged position 9. The deflection is still supported in this target position 10 alone via the hydraulic pressure 26 in the pressure cylinder 25 in the direction of movement 6.
- the spring device 8 is curved here and has an inclined tip 41, which ensures that the spring device 8 slides smoothly onto the deflection device 7 when the deflection device 7 and the spring device 8 do not overlap.
- the inclined tip 41 is suitable as a geometric shape element 28 for registering the spatial position of the spring arrangement 1 or of the piston 5 by means of a measuring device 27.
- FIG. 3 shows a similar configuration of the hydraulic actuator 2 with a spring assembly 1 as in FIG. 1.
- the piston 5 according to this illustration, below the predetermined target position 10, so that the spring device 8 is deflected by the deflection device 7 and a spring force 1 1 transmits by means of the stop element 3 on the Axialkraftfact 4 and thus on the piston 5.
- the piston is even in a minimum deflection 42, which is ensured by a minimum stop 12 on the spring device 8.
- two variants are shown, wherein on the left in the illustration, the minimum stop 12 is formed by resting the spring means in a corner 43, and wherein on the right in the illustration, the minimum stop is formed by clamping the spring means 8 between the deflector 8 and a wall 44.
- the actuating force 39 can be generated in this minimum deflection 42 solely by the spring device 8.
- FIG. 4 shows a section of a spring arrangement 1, as shown in an actuating device 2 (here incomplete) according to the preceding figures.
- the spring means 8 and the deflection device 7 in a guide rail 14, which is formed by means of the guide 13, in this example of sheets.
- the stop element 3 can thus not only the spring assembly 1 are protected against uncontrolled rotation, but also the piston 5, not shown here via a rotationally fixed engagement of the stop element 3 in the axial force not shown here. 4
- FIGS. 2 to 4 shows a deflection device 7, as can be used in FIGS. 2 to 4, which are integrated with their first cam 19, second cam 20, third cam 21 and fourth cam 22 into a component of the hydraulic actuating device 2, which is not completely shown here ,
- Fig. 6 shows a corresponding to the cams 19 to 22 in Fig. 5 spring means 8 having a first leaf spring 15, a second leaf spring 16, a third leaf spring 17 and a fourth leaf spring 18, all of which are interconnected via the stop element 3.
- the deflection device 7 shows an alternative spring arrangement 1 in a section of a hydraulic actuating device 2.
- the deflection device 7 is fixedly connected to the stop element 3, while the spring device 8 is designed as a sprung cam and falls below a predetermined desired position 10 (not shown here), is deflected against the spring direction 23.
- the operative relationship is described in this spring arrangement 1 as well as in Figures 2 to 4.
- FIG. 8 shows a motor vehicle 33 with a drive unit 34, which is shown here as an internal combustion engine.
- the drive unit 34 is located in front of the driver's cab 35 of the motor vehicle 33 and with its motor axis 37 transversely to the longitudinal axis 36 of the motor vehicle 33.
- the drive unit 34 can be detachably connected via its output shaft 30 by means of the friction pack 32 about the rotation axis 29 of the friction clutch 24 to a drive train 31 shown here purely schematically.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112014004407.5T DE112014004407A5 (de) | 2013-09-26 | 2014-09-04 | Federanordnung für eine hydraulische Betätigungsvorrichtung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013219350.5 | 2013-09-26 | ||
DE102013219350 | 2013-09-26 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2015043589A2 true WO2015043589A2 (de) | 2015-04-02 |
WO2015043589A3 WO2015043589A3 (de) | 2015-11-26 |
Family
ID=51627172
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2014/200441 WO2015043589A2 (de) | 2013-09-26 | 2014-09-04 | Federanordnung für eine hydraulische betätigungsvorrichtung |
Country Status (2)
Country | Link |
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DE (2) | DE102014217652A1 (de) |
WO (1) | WO2015043589A2 (de) |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1310331A (en) * | 1971-02-04 | 1973-03-21 | Ford Motor Co | Self-centering clutch release bearing assembly |
FR2224019A1 (fr) * | 1973-03-27 | 1974-10-25 | Roulements Soc Nouvelle | Butée d'embrayage à centrage et alignement élastiques |
JP2005163943A (ja) * | 2003-12-03 | 2005-06-23 | Ntn Corp | クラッチレリーズ軸受 |
DE102009018794A1 (de) * | 2009-04-24 | 2010-10-28 | Daimler Ag | Zentralausrücker |
DE102011087101A1 (de) * | 2010-12-23 | 2012-06-28 | Schaeffler Technologies Gmbh & Co. Kg | Ausrücksystem zur hydraulischen Betätigung einer Kupplung |
-
2014
- 2014-09-04 WO PCT/DE2014/200441 patent/WO2015043589A2/de active Application Filing
- 2014-09-04 DE DE201410217652 patent/DE102014217652A1/de not_active Withdrawn
- 2014-09-04 DE DE112014004407.5T patent/DE112014004407A5/de active Pending
Non-Patent Citations (1)
Title |
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None |
Also Published As
Publication number | Publication date |
---|---|
DE112014004407A5 (de) | 2016-06-16 |
DE102014217652A1 (de) | 2015-03-26 |
WO2015043589A3 (de) | 2015-11-26 |
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