WO2018113836A1 - Débrayeur central pneumatique - Google Patents

Débrayeur central pneumatique Download PDF

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Publication number
WO2018113836A1
WO2018113836A1 PCT/DE2017/101060 DE2017101060W WO2018113836A1 WO 2018113836 A1 WO2018113836 A1 WO 2018113836A1 DE 2017101060 W DE2017101060 W DE 2017101060W WO 2018113836 A1 WO2018113836 A1 WO 2018113836A1
Authority
WO
WIPO (PCT)
Prior art keywords
pneumatic
sleeve
actuating piston
guide sleeve
fixed
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.)
Ceased
Application number
PCT/DE2017/101060
Other languages
German (de)
English (en)
Inventor
Frank Frietsch
Massimo Merola
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to DE112017006363.9T priority Critical patent/DE112017006363A5/de
Publication of WO2018113836A1 publication Critical patent/WO2018113836A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

Definitions

  • the present invention relates to a pneumatic Gottausschreiber with improved resistance to contamination.
  • the present invention further relates to a pneumatic clutch system comprising such a central release.
  • Actuation systems for motor vehicles are widely known. These can be actuated hydraulically or pneumatically depending on the field of application.
  • pneumatic Gottausschreiber are known that are part of a release system as an actuation system. These are often used in trucks. In particular, in harsh applications, such as in trucks, problems may occur with regard to a dirt entry into the actuation system. A dirt entry can lead to damage to the actuation system or malfunction thereof. This often causes a service effort that must be avoided. To prevent a dirt entry, solutions are known. However, these still offer room for improvement.
  • the object of the present invention to at least partially overcome the disadvantages known from the prior art.
  • a pneumatic Gottitzer for an actuating system of a vehicle clutch, comprising a guide sleeve and an at least partially limited by the guide sleeve pressure chamber, wherein in the pressure chamber, an actuating piston for driving a bearing for actuating the vehicle clutch is axially displaceable axially relative to the guide sleeve, wherein the Monaus - scaffolder having a cover with variable length, wherein the envelope is fixed to the guide sleeve and the actuating piston is such that the length of the envelope changes with an axial displacement of the actuating piston.
  • a prescribed Gottitzer can be easily produced while having a significantly improved resistance to contamination.
  • the above-described pneumatic Gottitzer thus serves for use in an actuating system, in particular release system, a vehicle clutch, and in particular the operation of a clutch of a motor vehicle, such as a truck.
  • the Gottausschreiber is controlled pneumatically, as is generally known for such systems.
  • the pneumatic Gottitzer is designed in particular as a so-called CPCA (Concentric Pneumatic Clutch Actuator) and is named, for example, as a pneumatic cylinder. It comprises a guide sleeve, which can serve in a conventional manner radially inwardly receiving a transmission shaft. Further, the Monausschreiber comprises an at least partially delimited by the guide sleeve pressure chamber, wherein in the pressure chamber, an actuating piston for driving a bearing for actuating the vehicle clutch axially with respect to the guide sleeve is pneumatically displaceable. In other words, a pressure chamber is provided with
  • Compressed air can be acted upon, and can be arranged for example in the guide sleeve or as a wall, the cylinder sleeve.
  • the actuating piston By acting on the pressure chamber with compressed air, the actuating piston can be displaced axially. Due to the axial displacement of the actuating piston can be a bearing, in particular, drive a clutch or release bearing, which acts on the vehicle clutch.
  • the compressed air acts directly on the actuating piston or indirectly, via interposition of other components.
  • a pneumatic piston is provided in the pressure chamber, which is radially sealed against the Druckraumwandungen, ie approximately against the guide sleeve and can be displaced by the entry of compressed air and so, about with the interposition of another, such as plastic manufactured piston, act on the actuating piston and so can move it axially.
  • the actuating piston can be designed as an aluminum piston.
  • this has a sheath with variable length, wherein the sheath is fixed to the guide sleeve and the actuating piston such that changes the length of the sheath at an axial displacement of the actuating piston.
  • the envelope can be fixed in particular sealingly and / or immovably to the guide sleeve. In particular, this configuration can prevent the entry of dirt into sensitive zones of the central release.
  • an enclosure which can also be designated as a dirt protection, with a variable length, ie a length which is variable or changeable in the axial direction with respect to the guide sleeve
  • the enclosure can be secured to the guide sleeve and furthermore to the actuating piston at any time. be xiert.
  • the ingress of dirt can be prevented particularly sure.
  • Due to the fact that the length of the casing changes with an axial displacement of the actuating piston an axial movability of the piston can furthermore remain unimpaired or it can be made possible that the casing does not disturb the displacement of the actuating piston. As a result, a safe and reliable or stable working system can be made possible.
  • a prescribed Gottscher is thus particularly robust against the entry of dirt particles, which can prevent damage or malfunction caused by dirt entry or at least reduce significantly. It may be particularly preferred if the envelope seals the area between the guide sleeve and the actuating piston or protects against dirt entry. In particular, in this embodiment, it can be reliably prevented that dirt in the area radially between the actuating piston and the guide sleeve, in particular in the front, ie the clutch facing area, the guide sleeve, passes, which may be particularly advantageous. For it has been found that, in particular, this position can be prone to registered dirt or registered dirt can have a disadvantageous effect in this position.
  • abrasion can cause increased wear, for example on the front sliding belt or piston sliding ring, or seals due to dirt particles can be damaged.
  • this can be prevented by a previously described central release mechanism or the risk for this significantly reduced, because in particular at the position of the sliding band or the seal to the guide tube or the guide sleeve can protect the enclosure.
  • the envelope is configured as a two-part sleeve with a first sleeve member and a first sleeve member coaxially formed second sleeve member, wherein the first sleeve member is fixed to the guide sleeve and wherein the second sleeve member to the Actuating piston is fixed, and wherein the first sleeve member is fixed to the second sleeve member axially movable thereto
  • two sleeve members are provided, which are movable relative to each other to compensate for the axial movement of the piston or to change the length of the sheath.
  • the sleeve members are sealed to each other to allow no dirt entry at the connecting position of the sleeve elements.
  • a dirt entry over the entire stroke of the actuating piston can be prevented in a simple manner.
  • it can be allowed by a sleeve or by sleeve elements that the enclosure has a high stability, which can guarantee a long-term stable operation.
  • an immovable or backlash-free fixation of the first sleeve element to the guide sleeve can make it possible to prevent a dirt entry from being particularly secure there.
  • An attachment of the second sleeve member to the actuating piston can also be made free of play or axially play, the latter can increase the possible stroke.
  • the first sleeve element that is to say the sleeve element fixed to the guide sleeve
  • the second sleeve element that is to say the sleeve element fixed to the actuating piston
  • the sleeve elements can be particularly advantageous fixed to the guide sleeve or on the actuating piston.
  • the first sleeve member is fixed to the guide sleeve by a press fit, such as is pressed at the end portion of the guide sleeve.
  • This fixation can be particularly advantageous using a metal and allow in a simple way that the sleeve member engages around the guide sleeve and is fixed to this particular clearance, so that a dirt entry between the guide sleeve and sleeve member can be prevented.
  • the second sleeve element it may be provided that this has a radially arranged projection as an axially acting stop, which is arranged axially between two stops of the actuating piston, or vice versa. In other words, a stop of the actuating piston can be positioned axially between two stops of the sleeve element be.
  • the stop of the sleeve element interact with the stops of the actuating piston and thus prevent or limit an axial movement of the sleeve element, so that the second sleeve element can be fixed to the actuating piston with axial play or also without clearance.
  • first sleeve member is fixed to the second sleeve member by axially interacting corresponding stops in the axial direction.
  • first and the second sleeve member may each have an axially acting stop, whereby an axial sliding out of the second sleeve member from the first sleeve member or vice versa can be prevented.
  • a secure fixation of the two sleeve elements can be made possible and yet a smooth axial movement of the sleeve members are made possible relative to each other, which can allow a large and about the positioning of the stops easily adjustable stroke of the actuating piston.
  • the second sleeve member is axially movable and the first sleeve member is axially fixed so as to provide a protection against dirt and equally to be able to compensate for the stroke of the actuating piston.
  • the enclosure is designed as a telescopic spring, wherein a first axial end of the telescopic spring is fixed to the guide sleeve and wherein a second axial end of the telescopic spring is fixed to the actuating piston.
  • Telescopic springs are a simple and cost-effective design, to allow for a varying length a secure seal, as the Teleskopfederemia can be pushed into each other or can be pulled apart, so as to respond to a stroke of the actuating piston. In this case, the entry of soiling is certainly prevented because of a possible possible secure fixation of the axially outer telescopic spring elements on the guide sleeve or on the actuating piston despite different strokes.
  • the first axial end of the telescopic spring is fixed to the guide sleeve with a centering flange is and / or that the second axial end of the telescopic spring is fixed to the actuating piston with a centering flange.
  • This embodiment enables a defined and well sealing fixation on the guide sleeve or on the actuating piston.
  • the position and orientation of the axial ends of the Teleskopfeder or the Teleskopfeder be specifically defined as such. As a result, it can be prevented that the telescopic spring tilted in its orientation, whereby a telescoping or pulling apart of the telescopic spring can be ensured without great effort. This in turn allows a low-force axial displacement of the actuating piston and thereby a safe and stable operation of the central release.
  • a centering flange for example made of steel
  • a centering flange for example made of steel
  • the flange By means of the flange, a particular axial and radial fixing of the telescopic spring to the actuating piston or guide sleeve is made possible.
  • the telescopic spring can increase or decrease its length.
  • Another way of fixing the telescopic spring on the actuating piston can be seen to fix it via a stop on the actuating piston, or on an undercut or a stop thereof.
  • the telescopic spring can be made of steel, such as stainless spring steel or steel C70 or C70S, which has the advantage that the telescopic spring radially requires little space, as about small spring thicknesses of, for example, 0.2-0.8mm are possible and high axial paths can be covered.
  • telescopic springs offer the advantage of great adaptability in their dimensions and a high level of sophistication.
  • the envelope is designed as a bellows.
  • Bellows have been considered in the past Dirt protection in other applications already claimed and require no complex additional components for fixation. These are also available inexpensively and can be designed wear. In order to prevent the radial expansion of the bellows, it may be advantageous to adjust the venting accordingly.
  • the guide sleeve may have a radially aligned ring arranged in a groove, which interacts with an undercut or a recess of the bellows and / or that the bellows on the actuating piston by means of a hook connection or latching connection connected is.
  • fixations are easy to train and also provide a secure axial fixation, which can reliably prevent the ingress of contaminants.
  • the guide sleeve anyway such a ring about to mount the guide sleeve, which can be used in this embodiment in a simple way for fixing the bellows use.
  • the subject matter of the present invention is furthermore a pneumatic clutch system comprising a motor vehicle clutch and a pneumatic central release which can actuate the motor vehicle clutch, the pneumatic central release being designed as described above in detail.
  • a pre-described clutch system may be, in particular, a release system for a vehicle clutch, such as a truck.
  • a «37.00 a «39.0, a
  • a «40%.00 a «40%.00
  • a clutch plate such as a plate spring
  • FIG. 1 is a sectional view through a portion of a first embodiment of a pneumatic Gottaus Wegers in fully disengaged state.
  • Figure 2 is a sectional view through part of the first embodiment of a pneumatic Gottaus Wegers in central position.
  • Fig. 3 is a sectional view through part of the first embodiment of a pneumatic Gottaus Wegers in fully engaged condition
  • FIG. 4 shows a sectional view through a part of a further embodiment of a pneumatic central release in the middle position
  • Figure 5 is a sectional view through part of another embodiment of a pneumatic Gottaus Wegers in central position.
  • FIG. 5th is a detail view of Fig. 5th
  • FIG. 1 shows an embodiment of a pneumatic central release 10, also referred to as a pneumatic cylinder, for an actuation system of a vehicle clutch.
  • the central release 10 comprises a guide sleeve 12 and a at least partially limited by the guide sleeve 12 pressure chamber 14, wherein in the pressure chamber 14, an actuating piston 16 for driving a bearing 18 for actuating the vehicle clutch axially with respect to the guide sleeve 12 is pneumatically displaced.
  • an inlet 20 is arranged for compressed air, wherein the compressed air initially to a by a Seal 22 against the pressure chamber 14 and against the guide sleeve 12 sealed pneumatic piston 24 acts and the pneumatic piston 24 can move axially.
  • the pneumatic piston 24 acts on an aluminum piston 26, which in turn acts on the actuating piston 16 for an axial displacement.
  • the actuating piston 16 can then drive the bearing 18, so as to act on the clutch.
  • spring retaining plate 28 is shown in which a preload spring 30 is arranged for a spring preload.
  • the central disengager 10 has a variable length enclosure 32, the enclosure 32 being fixed to the guide sleeve 12 and the actuating piston 16 such that the length of the enclosure 32 varies with axial displacement of the actuating piston 16.
  • the envelope 32 is fixed on the side of the actuating piston 16 which is radially remote from the guide sleeve 12.
  • dirt such as clutch wear
  • the envelope 32 may be an additional protection, for example to a dirt protection arranged in the actuating piston 16, such as a sealing ring 38.
  • the envelope 32 is designed as a two-part sleeve or double sleeve, which can be preassembled approximately during assembly, with a first sleeve element 40 and a second sleeve element 42 coaxial with the first sleeve element 40, wherein the first sleeve member 40 is fixed to the guide sleeve 12 and wherein the second sleeve member 42 is fixed to the actuating piston 16, and wherein the first sleeve member 40 is fixed to the second sleeve member 42 axially movable to this.
  • first and second sleeve member With respect to an axial fixation of first and second sleeve member, it is further provided that the first sleeve member 40 is fixed to the second sleeve member 42 by axially interacting corresponding stops 44, 46 of the guide sleeve 12 and the actuating piston 14 in the axial direction, but with an axial displaceability of the second sleeve member 42 is given relative to the first sleeve member 40 for compensating the stroke of the actuating piston 16.
  • the first sleeve member 40 is further formed of a metal and fixed to the guide sleeve with a press fit.
  • the second sleeve element 42 is formed from a plastic and has a second stop 48 arranged axially opposite the stop 46 and axially fixed between two stops 50, 52 of the actuating piston 16 with axial play.
  • the second sleeve member 42 is axially movable and the first sleeve member 40 is axially fixed.
  • the second sleeve member 42 is fixed axially on the stops 50, 52 on the movable actuating piston 16 and thus can reach any operating position.
  • the stops 50, 52 on the actuating piston 16 ensure that the plastic sleeve is moved downwards, ie in the direction of minimum disengagement or also upwards in the direction of maximum disengagement.
  • FIG. 1 shows a position with the actuating piston 16 completely disengaged
  • FIG. 2 shows a middle position
  • FIG. 3 shows a position with fully engaged actuating piston 16.
  • the maximum stroke can be exemplary and in no way limiting at 122mm, whereas the center position can be at 104mm and the fully engaged state at 84mm can lie. These distances can be easily compensated by the configured as a double sleeve enclosure 32.
  • FIG. 4 shows a further embodiment of a central release 10 in a central position.
  • the central release 10 differs from the embodiment of Figures 1 to 3 in particular in the embodiment of the envelope 32, wherein with respect to the figures 1 to 3 the same or similar components are provided with the same reference numerals.
  • the envelope 32 is configured as a telescopic spring 54, a first axial end of the telescopic spring 54 being fixed to the guide sleeve 12, and a second axial end of the telescopic spring 54 being fixed to the actuating piston 16.
  • the first axial end of the telescopic spring 54 is fixed to the guide sleeve 12 with a centering flange 56, such as steel, which is fixed to the guide sleeve 12 and this embraces.
  • the second axial end of the telescopic spring 54 is also fixed to the actuating piston 16 with a Zentrierflansch, such as steel, which is fixed to the actuating piston 16, such as a stop 59.
  • a Zentrierflansch such as steel
  • FIG. 5 shows a further embodiment of a central release device 0 in a middle position, FIG. 6 showing a detailed view thereof.
  • the central release 10 differs from the embodiment of Figures 1 to 4 in particular in the embodiment of the envelope 32, wherein with respect to the figures 1 to 4 the same or similar components are provided with the same reference numerals.
  • the envelope 32 is designed as a bellows 62, wherein the guide sleeve 12 has a radially aligned ring 64 arranged in particular in a groove, which interacts with an undercut or a recess of the bellows 62 and / or the bellows is connected to the actuating piston 16 by means of a hook connection or latching connection 68.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

La présente invention concerne un débrayeur central (10) pneumatique pour un système d'actionnement d'un embrayage de véhicule. Le débrayeur comprend un manchon de guidage (12) et une chambre de pression (14) délimitée au moins en partie par le manchon de guidage (12). Dans la chambre de pression (14), un piston d'actionnement (16) destiné à commander un palier (18) pour l'actionnement de l'embrayage du véhicule peut être déplacé axialement de manière pneumatique par rapport au manchon de guidage (12). Le débrayeur central (10) présente une enveloppe (32) de longueur variable, l'enveloppe (32) étant fixée au manchon de guidage (12) et au piston d'actionnement (16) de telle manière que la longueur de l'enveloppe (32) varie lors d'un déplacement axial du piston d'actionnement (16).
PCT/DE2017/101060 2016-12-19 2017-12-12 Débrayeur central pneumatique Ceased WO2018113836A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112017006363.9T DE112017006363A5 (de) 2016-12-19 2017-12-12 Pneumatischer Zentralausrücker

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016124815.0A DE102016124815A1 (de) 2016-12-19 2016-12-19 Pneumatischer Zentralausrücker
DE102016124815.0 2016-12-19

Publications (1)

Publication Number Publication Date
WO2018113836A1 true WO2018113836A1 (fr) 2018-06-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2017/101060 Ceased WO2018113836A1 (fr) 2016-12-19 2017-12-12 Débrayeur central pneumatique

Country Status (2)

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DE (2) DE102016124815A1 (fr)
WO (1) WO2018113836A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115917174A (zh) * 2020-09-03 2023-04-04 采埃孚商用车系统欧洲有限公司 气动致动器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021201096A1 (de) * 2021-02-05 2022-08-11 Zf Friedrichshafen Ag Zentralausrücker

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009030974A1 (de) * 2008-07-14 2010-01-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Doppelkupplung
EP2626582A2 (fr) * 2008-08-22 2013-08-14 Schaeffler Technologies AG & Co. KG Embrayage double
DE102013221841A1 (de) * 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Ausrücksystem
DE102013223653A1 (de) * 2012-12-19 2014-06-26 Schaeffler Technologies Gmbh & Co. Kg Deckelfestes Ausrücksystem

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009030974A1 (de) * 2008-07-14 2010-01-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Doppelkupplung
EP2626582A2 (fr) * 2008-08-22 2013-08-14 Schaeffler Technologies AG & Co. KG Embrayage double
DE102013221841A1 (de) * 2012-11-22 2014-05-22 Schaeffler Technologies Gmbh & Co. Kg Ausrücksystem
DE102013223653A1 (de) * 2012-12-19 2014-06-26 Schaeffler Technologies Gmbh & Co. Kg Deckelfestes Ausrücksystem

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115917174A (zh) * 2020-09-03 2023-04-04 采埃孚商用车系统欧洲有限公司 气动致动器

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Publication number Publication date
DE102016124815A1 (de) 2018-06-21
DE112017006363A5 (de) 2019-09-05

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