EP1831061A2 - Liaison articulee pour un dispositif de debrayage - Google Patents

Liaison articulee pour un dispositif de debrayage

Info

Publication number
EP1831061A2
EP1831061A2 EP05849408A EP05849408A EP1831061A2 EP 1831061 A2 EP1831061 A2 EP 1831061A2 EP 05849408 A EP05849408 A EP 05849408A EP 05849408 A EP05849408 A EP 05849408A EP 1831061 A2 EP1831061 A2 EP 1831061A2
Authority
EP
European Patent Office
Prior art keywords
piston rod
ball head
gleitschutzkappe
joint
spring elements
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.)
Withdrawn
Application number
EP05849408A
Other languages
German (de)
English (en)
Inventor
Markus Heitbaum
Roland Welter
Volker Lang
Urban Panther
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 Buehl Verwaltungs GmbH
LuK Lamellen und Kupplungsbau GmbH
Original Assignee
LuK Lamellen und Kupplungsbau Beteiligungs KG
LuK Lamellen und Kupplungsbau GmbH
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 LuK Lamellen und Kupplungsbau Beteiligungs KG, LuK Lamellen und Kupplungsbau GmbH filed Critical LuK Lamellen und Kupplungsbau Beteiligungs KG
Publication of EP1831061A2 publication Critical patent/EP1831061A2/fr
Withdrawn legal-status Critical Current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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/18—Connection thereof to initiating means
    • 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
    • F16D25/088—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members being distinctly separate from the axis of rotation
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05G—CONTROL DEVICES OR SYSTEMS INSOFAR AS CHARACTERISED BY MECHANICAL FEATURES ONLY
    • G05G1/00—Controlling members, e.g. knobs or handles; Assemblies or arrangements thereof; Indicating position of controlling members
    • G05G1/30—Controlling members actuated by foot
    • 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
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0212—Details of pistons for primary or secondary cylinders especially adapted for fluid control
    • 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
    • F16D2300/12—Mounting or assembling

Definitions

  • the invention relates to a hinge connection between the piston rod of a slave cylinder and a release element of a release device, in particular for a clutch of a motor vehicle.
  • DE 103 20 004 A1 describes a pressure medium drive, which is preferably designed as a hydraulic cylinder with an axially movable piston rod which engages with its free end via a non-slip on a pivotally mounted release element.
  • This anti-slip serves as an adapter between the piston rod and the disengagement, inter alia, to realize a hinge connection between the two components.
  • anti-slip adapter on a plurality of adjacent and circumferentially arranged holding elements which are separated by axial slots and are briefly spread when snapped onto the ball head of the piston rod radially outward from its initial position to thereafter at the smaller of the diameter of the ball head again snap back.
  • This adapter (anti-skid) is designed so that it encloses on the one hand with its inner contour, the end of the piston rod and is received with its outer contour of a correspondingly shaped recess in the release element.
  • the anti-slip device serves to reduce the wear occurring due to the rotational movement between the piston rod and slave cylinder, to produce the articulation between the two elements, and also to realize a connection of the bellows to the piston rod.
  • no axial fixation of the bellows is possible, which can lead to dirt entry within the bellows and thus on the piston rod.
  • a pressure medium drive with an axially movable piston rod is known, which engages at its free end via a non-slip on a pivotally mounted release element.
  • the inner shape of the anti-slip corresponds to the shape of the ball head and the outer with the shape of the release element in the joint area and the anti-slip is made of elastic plastic material. Due to this elastic material, supported by interruptions of its circumference by axial slots in the receiving area to the ball head, it can be snapped or clipped onto a piston rod. A radial extension of the outer contour of the anti-slip, in which a groove is introduced, serves to receive a bellows.
  • the object of the invention is to make the sealing of the ball head relative to the environment so, without restricting the mobility of the joint and also perform the joint connection space-saving.
  • a hinge connection which consists of a ball head of a piston rod and a disengagement, between which an adapter in the form of an anti-slip or a Gleitschutzkappe of elastic material is arranged, which has on its underside on the circumference in the axial direction of spring elements, which with a circumferential groove are provided.
  • This circumferential groove serves to attach a dirt cover.
  • the ball head can essentially be formed from spring elements whose length is determined by the length of the circumference of the ball head arranged axial slots. This length should advantageously be chosen larger than the largest radial extent of the ball head, in order to achieve optimum elasticity of the spring elements during radial compression.
  • the anti-slip cap is not provided with spring elements to increase their elasticity in the overcap area, but in this end, which is provided with a circumferential recess, a seal is used, which may for example be an O-ring.
  • a seal is used, which may for example be an O-ring.
  • this has a transition region between the ball head piston rod, a so-called neck, in which a correspondingly shaped groove is provided. After clipping the anti-slip cap on the piston rod, the anti-slip cap is thereby locked on the piston rod.
  • the ball head of the piston rod is designed as a ball socket, distributed over the circumference of several lugs are provided. These lugs are intended to receive the end of a mudguard. However, instead of the noses, a closed ring can be mounted on the circumference of the ball socket, which performs the same function.
  • the ball head is designed as a ball socket for producing a joint connection
  • the anti-slip cap is produced by molding the ball head of the piston rod.
  • both the outer and the inner shape of the Gleitschkappe can be produced in one operation.
  • the hinge connection is advantageously formed from a ball head of a piston rod which is sealed by a bellows and a release element. Between both joint parts, a lubricant is introduced in this case to reduce the friction. To seal the ball head is at the - A -
  • Piston rod already provided radially and axially fixed dirt protection with a wave-shaped axial extension, which is either supported on the release element or connected to this.
  • the ball head is made of two plastic components.
  • the piston rod is made with a ball head of a sprayable, such as PA 66 GF 35.
  • PA 66 GF 10 TF 25 In the contact area to the recess of the release element of the ball head is provided with a sliding layer of plastic, which has a high proportion of slip-modified components such.
  • PA 66 GF 10 TF 25 In the contact area to the recess of the release element of the ball head is provided with a sliding layer of plastic, which has a high proportion of slip-modified components such.
  • FIG. 3 further possibility of designing the articulated connection
  • FIG. 4 shows a further possibility of designing the joint connection according to the invention
  • FIG. 5 ball head with molded anti-slip
  • FIG. 6 joint connection without anti-slip cap
  • FIG. 6 a joint connection with wear protection integrated in the ball head
  • FIG. 1 shows a slave cylinder 1 with a piston rod 2.
  • a non-slip cap 5 is clipped on the ball head 4 of this piston rod 2.
  • This anti-slip cap 5 is made of a resilient plastic material and surrounds with its lower end the KoI- Rod 2.
  • Piston rod 2 and ball head 4 are preferably made in one piece and are advantageously made of plastic. However, another material, such as aluminum, could equally well be used for it.
  • the anti-slip cap 5 has a hat-like design, wherein the edge 6 serves as a support or stop for the disengagement element 9, not shown in this figure.
  • FIG. 1 Another possibility for producing a clip connection between ball head 4 and anti-slip 5 is shown in FIG.
  • piston rod 2 and ball head 4 are made in one piece and made of elastic material.
  • the ball head 4 is formed as a hollow body and provided with axial slots whose length extends slightly beyond the largest radial diameter of the ball head 4 addition.
  • the body of the anti-slip cap 5 is again made of elastic material and describes a shortened hollow ball whose diameter is adapted to that of the ball head 4. The diameter at the opening of the hollow sphere is smaller than the diameter to choose.
  • a circumferential groove 7 is provided for receiving the bellows 3.
  • FIG. 3 shows a further variant of the production of an articulated connection of and piston rod 2 and disengaging element 9, in which the antiskid cap 5 can likewise be previously clipped.
  • the diameter of the ball head 4 is followed by a constriction in the form of a neck 11, via which the ball head is preferably integrally connected to the piston rod 2.
  • a groove 13 is further provided.
  • a circumferential recess 14 is introduced in the region of its opening, which serves for receiving, for example, an O-ring 12.
  • the inner contour of the anti-slip cap 5 is in the remaining area of the contour of the ball head 4 and its outer contour is adapted to the recess 10 of the disengaging element 9.
  • the anti-slip cap has an edge 6 for receiving the bellows 3.
  • a lubricant 19 can be introduced into the recess 10 of the disengaging element 9.
  • FIG. 4 shows a further possibility of forming a hinge connection according to the invention.
  • the piston rod 2 instead of a ball head 4, a ball socket 15, which is made in one piece with the piston rod 2 made of elastic material.
  • the ball socket 15 has advantageously the shape of a shortened hemisphere whose diameter at the shortened position is slightly smaller than its remaining diameter.
  • the ball socket 15 also has at its periphery in the radial direction a plurality of lugs 16 or a continuous ring.
  • the anti-skid 5 is designed in this case so that it simulates the contour of the release element with its upper side and with its underside the cavity of the ball socket 15 can form-fit fill. Top and bottom are separated by an edge 6, which serves as a stop or support the Gleitschutzkappe 5 on disengagement 9.
  • an edge 6 which serves as a stop or support the Gleitschutzkappe 5 on disengagement 9.
  • several extensions 17 are provided at the bottom of the anti-slip cap 5 distributed over the circumference.
  • a closed ring may also be attached.
  • From Figure 5 is another way of producing a compound of anti-skid 5 and ball head 4 can be seen.
  • the anti-skid 5 is sprayed directly onto the ball head 4 of the piston rod 2 by means of a special manufacturing process. Since ball head 4 and antislip 5 are made of different materials and during the Umsprit- process of the ball head was surrounded with a special release agent, a compound of the two materials is excluded.
  • a radially inwardly directed collar 21 is provided in the region of the piston rod 2, which serves for receiving or fastening of the bellows 3, not shown in this figure.
  • Figure 6 shows a hinge connection according to the invention without anti-slip cap 5.
  • the hinge connection between the release element 9 and the head of the piston rod 2 is made directly.
  • the head of the piston rod 2 is formed substantially cylindrical, wherein it expires hemispherical in the joint region.
  • a lubricant 19 is advantageous.
  • a constriction 22 is provided for fastening the bellows 3, to which the bellows is frictionally connected by a Ringschnappthetic.
  • the bellows 3 has an extension 23 which is molded onto the last bellows shaft. This is supported under pretension on the disengaging element 9 and, due to its elastic material, resembles each Steering movement caused axial distance change from bellows 3 to disengaging 9, so that the head of the piston rod 2 is protected from contamination.
  • FIG. 6a A further possibility to reduce the friction in a hinge connection without antiskid cap 5, can be seen from the figure 6a.
  • the region of the ball head 4, which is exposed during the joint movement of a particularly large friction provided with a plastic layer having a correspondingly high proportion of slip-modified components, such as PA 66 GF 10 TF 25.
  • the remaining part of the ball head 4 and the piston rod 2 can consist of PA 66 GF 35.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

Liaison articulée située entre la tige de piston d'un cylindre récepteur et un élément de débrayage d'un dispositif de débrayage, en particulier pour un embrayage de véhicule à moteur. L'objet de la présente invention est la mise au point d'une solution compacte pour l'étanchéification de la tête sphérique par rapport à l'environnement, sans restriction de la mobilité de la liaison articulée composée d'une tête sphérique de tige de piston et d'un élément de débrayage entre lesquels est placé un adaptateur sous forme d'antidérapant ou de capuchon antidérapant en matière élastique, qui comporte sur sa face inférieure périphérique, dans le sens axial, des éléments ressorts. Selon la présente invention, les éléments ressorts sont pourvus d'une rainure périphérique et la tête sphérique constituée d'une matière élastique est formée de plusieurs éléments ressorts répartis sur sa circonférence.
EP05849408A 2004-12-22 2005-12-09 Liaison articulee pour un dispositif de debrayage Withdrawn EP1831061A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004062985 2004-12-22
PCT/DE2005/002217 WO2006066542A2 (fr) 2004-12-22 2005-12-09 Liaison articulee pour un dispositif de debrayage

Publications (1)

Publication Number Publication Date
EP1831061A2 true EP1831061A2 (fr) 2007-09-12

Family

ID=35985371

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05849408A Withdrawn EP1831061A2 (fr) 2004-12-22 2005-12-09 Liaison articulee pour un dispositif de debrayage

Country Status (6)

Country Link
EP (1) EP1831061A2 (fr)
JP (1) JP2008524528A (fr)
KR (1) KR101230163B1 (fr)
BR (1) BRPI0519196A2 (fr)
DE (1) DE112005002999A5 (fr)
WO (1) WO2006066542A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009029972A1 (de) * 2009-06-23 2010-12-30 Smk Systeme Metall Kunststoff Gmbh & Co. Kg. Pneumatischer Steller
DE102015202677A1 (de) * 2015-02-13 2016-08-18 Schaeffler Technologies AG & Co. KG Kolbenanordnung für ein hydraulisches Kupplungssystem
FR3054272B1 (fr) * 2016-07-25 2018-09-07 Valeo Embrayages Cylindre hydraulique recepteur, notamment pour un systeme de commande hydraulique d'un embrayage

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT249529Y1 (it) * 2000-06-02 2003-05-19 Siv Spa Dispositivo antivibrazioni per il pedale della frizione di unautoveicolo.
DE10028361A1 (de) * 2000-06-08 2001-12-20 Fico Cables Sa Verbindungselement
DE10110931C1 (de) * 2001-03-07 2003-02-13 Lucas Automotive Gmbh Bremsanlage und Kraftübertragungsanordnung hierfür
DE10320004B4 (de) 2003-05-06 2013-10-17 Zf Friedrichshafen Ag Druckmittelantrieb

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006066542A2 *

Also Published As

Publication number Publication date
WO2006066542A2 (fr) 2006-06-29
WO2006066542A3 (fr) 2006-08-24
JP2008524528A (ja) 2008-07-10
BRPI0519196A2 (pt) 2008-12-30
DE112005002999A5 (de) 2007-09-13
KR20070086241A (ko) 2007-08-27
KR101230163B1 (ko) 2013-02-05

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