WO2001096163A1 - Embrayages de vehicules - Google Patents

Embrayages de vehicules Download PDF

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Publication number
WO2001096163A1
WO2001096163A1 PCT/GB2001/002573 GB0102573W WO0196163A1 WO 2001096163 A1 WO2001096163 A1 WO 2001096163A1 GB 0102573 W GB0102573 W GB 0102573W WO 0196163 A1 WO0196163 A1 WO 0196163A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
spring
pedal
assistor
diaphragm
Prior art date
Application number
PCT/GB2001/002573
Other languages
English (en)
Inventor
Alastair John Young
Benjamin Chetwood Struve
Original Assignee
Automotive Products Uk Limited
Ap Tmf Limited
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 Automotive Products Uk Limited, Ap Tmf Limited filed Critical Automotive Products Uk Limited
Priority to AU64082/01A priority Critical patent/AU6408201A/en
Priority to GB0202566A priority patent/GB2372546B/en
Priority to EP01938404A priority patent/EP1289815A1/fr
Priority to JP2002510318A priority patent/JP2004503723A/ja
Publication of WO2001096163A1 publication Critical patent/WO2001096163A1/fr

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
    • F16D25/08—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
    • F16D25/087—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 the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers

Definitions

  • This invention relates to vehicle clutches and in particular to vehicle clutch systems comprising a vehicle clutch in which a driven plate is clamped between a pressure plate and a reaction member (e.g. a flywheel) by a diaphragm spring, a clutch operating pedal, and an operating mechanism connecting the pedal with the diaphragm spring to release the clutch on depression of the pedal.
  • a reaction member e.g. a flywheel
  • Such clutch systems are hereinafter referred to as being "of the kind specified”.
  • a vehicle clutch system of the kind specified characterised in that the diaphragm spring has a substantially flat spring clamp load characteristic such that the spring clamp load remains substantially constant throughout the operating life of the clutch; the clutch pedal has an assistor spring means which determines the resistance to depression of the pedal during release of the clutch, and the operating characteristics of the operating mechanism and/or the spring characteristics of the pedal assistor spring means ensure that the resistance to the depression of the pedal increases up to a maximum resistance at or around the disengagement point of the clutch and thereafter reduces.
  • the operating characteristics of the operating mechanism are preferably chosen to counteract the high load/low travel release characteristic of the diaphragm spring.
  • the clutch is of the pull type.
  • the geometry of a pull-type clutch provides a stiffer cover and ensures that the spring remains biased onto fulcrum during the entire clutch release.
  • the driven plate may be cushioned by metal springs (e.g. leaf springs) or advantageously by elastomeric cushioning as described and claimed in, for example EP 0252583 and the other patents referred to later below.
  • the assistor spring means may comprise one or more springs which operate directly on the pedal.
  • spring means may be built into the operating mechanism which operate indirectly on the pedal.
  • the spring means may be built into the master cylinder. This spring means is preferably a diaphragm spring.
  • a master cylinder for the actuation of a vehicle function
  • the master cylinder comprising a body having a bore in which an actuating piston is displaceable by a pedal operated push rod or other actuating means to displace fluid from the bore to actuate the function
  • the master cylinder being characterised in that one or more diaphragm springs act directly or indirectly on the piston, to reduce the load which needs to be applied by the pedal or other actuating means to operate the master cylinder.
  • the invention also provides an assistor spring arrangement for the operation of a vehicle clutch in which a clutch driven plate is clamped between a pressure plate and a reaction member by a diaphragm spring, the assistor spring arrangement being characterised in that two diaphragm spring means are arranged to operate in opposite directions on a clutch actuator member, the diaphragm spring means being capable of operating on both sides of their flat condition to counteract the characteristics of the driven plate clamping diaphragm spring and assist movement of the clutch actuator.
  • FIG. 1 is a diagrammatic representation of a vehicle clutch system in accordance with a first aspect of the present invention.
  • Figure 2 shows- the clamp load/deflection characteristics for a clutch diaphragm spring having so-called flat characteristic
  • Figure 3 shows the clutch pedal 'feel' characteristic
  • Figures 4 and 5 show alternative forms of axial cushioning for use in the clutch driven plate
  • FIGS. 6 and 7 show diagrammatically details of a master cylinder in accordance with a second aspect of the present invention which includes an internal assistor spring means;
  • Figures 8 and 9 show the general form of the load/deflection characteristics of a return spring and an assistor spring employed in the master cylinder of figures 6 and 7;
  • Figures 10 shows the general form of the overall spring assistance provided by the internal springs of the master cylinder of figures 6 and 7, and
  • Figure 11 shows a further alternative form of master cylinder including an internal assistor spring means.
  • this shows a clutch system in which a vehicle clutch 10 is controlled by a pedal 11 via an operating mechanism 12.
  • Clutch 10 has a driven plate 13 which is clamped between a reaction member in the form of a flywheel 14 and a pressure plate 15 by a diaphragm spring 16 which reacts against a clutch cover 17 which is bolted to flywheel 14 at 18.
  • Flywheel 14 is bolted at 19 to an engine crankshaft 20.
  • the driven plate 13 is connected with a gearbox input shaft 21 via a central hub 22.
  • the driven plate may include a sprung or compound centre 23 which employs circumferentially acting springs and friction members to absorb torsional vibrations within the vehicle driveline or may have a solid centre with no such ability to absorb torsional vibrations.
  • the operating mechanism 12 is hydraulic with a master cylinder 24 operated by pedal 11 and a slave cylinder 25 connected with diaphragm spring ! 6 via a release bearing 26 and a clutch operating lever 27 which is pivoted at 28 on a clutch housing (not shown).
  • the pedal 11 is pivoted on a bulkhead of the vehicle at 29.
  • the diaphragm spring 16 has a substantially flat clamp load characteristic as shown in figure 2.
  • the clamp load applied by the diaphragm spring 11 (the vertical axis in figure 2) remains substantially constant over a significant proportion 'P' of the working deflection of the spring (the horizontal axis in figure 2).
  • the clamp load applied by the diaphragm spring remains substantially constant (approximately 7000 Newton in the example shown) over the operating life of the clutch as the thickness of the driven plate decreases.
  • the spacing 'F' between the spring fulcrum 31 and the cover bolts 18 is reduced so that deflection of the cover 17 is reduced and thus efficiency of the operating system is improved. Also by reducing the lever arm 'G' between the pressure plate fulcrum 32 and the line of action of the release bearing 26 deflection of the diaphragm spring is reduced, again helping to reduce losses in the system.
  • the thickness of diaphragm spring 16 may also be increased to reduce losses due to deflection of the diaphragm spring.
  • the pedal 11 is acted on by an over- centre assistor compression spring 30 which applies a rotational spring bias to pedal 11 with a characteristic of the form shown in curve 'B' of figure 3.
  • Spring 30 is mounted on the pedal bulkhead at 30a and is connected with pedal 11 at 30b.
  • the line of action of spring 30 (which joins 30a and 30b) crosses the line Z-Z which connects pedal pivot 29 and spring mount 30a at location 30b2 so that spring 30 goes over-centre.
  • spring 30 applies a counter clockwise movement about pivot 29.
  • the Optimised Clutch System of the present invention provides a clutch system where the clutch clamp load remains substantially constant throughout the operating life of the clutch the variation in and the 'feel' of the clutch operating pedal (as represented by curve ⁇ C of figure 3) is minimised and also remains substantially the same throughout the operating life of the clutch.
  • the operating mechanism which connects pedal 11 with diaphragm spring 16 could alternatively be, for example, a lever and cable system.
  • the driven plate 13 of the clutch may have no axial cushion, as shown in figure 1, or more likely can include axial cushioning provided by a known means.
  • the clutch friction material annuli 13a and 13b of plate 13 maybe mounted on so-called spring segments 13c (shown diagrammatically in figure 4).
  • the driven plate may include an elastomeric axial cushion in which clutch -friction material annuli 13a and 13b are bonded to a backing plate 13c by beads of elastomeric adhesive 13d (figure 5) which are partially compressed when the clutch is engaged and the driven plate 13 is clamped between pressure plate 15 and flywheel 14.
  • elastomeric axial cushioning are shown, for example in EP 0252583, EP 0390797, EP 0323036, EP 0455694, EP 0510014, GB 2247725, EP 0442539, GB 2243419, GB 2272494 and EP 0638149.
  • elastomeric cushioning enables a greater degree of consistency to be achieved with regard to the cushioning force provided by the driven plate throughout the life of the clutch than can be provided by metal cushioning arrangement of the form shown in, for example, figure 3. This further aids the consistency of operation of the entire Optimised Clutch System to be further improved. Also, since elastomeric axial cushioning does not use rivets etc. to secure the friction annuli in position a greater thickness of useable friction material is available.
  • the pedal 11 is acted upon directly by the over-centre assistor spring 30 this over-centre spring action could be provided by one or more springs acting in the operating mechanism 12 between the pedal 11 and the diaphragm spring 16.
  • an assistor spring means could be provided within master cylinder 24 .
  • Such a spring is preferably a diaphragm spring means arranged to counteract the previously described high load/low travel characteristic of spring 16.
  • a master cylinder 40 having a reservoir 41 includes a piston 42 slideable in a bore 43 which pressurises a working chamber 44 which is in turn connected with a slave cylinder (not shown) via piping 45.
  • a spring means in the form of first and second sets of diaphragm springs 46 and 47 acts on opposite sides of piston 42.
  • the first set of diaphragm springs 46 acts as a return spring for the associated pedal 11 whereas the second set of diaphragm springs 47 acts as an assistor spring for pedal 11.
  • the first set of diaphragm springs 46 comprises individual belleville springs 46a (see figure 7) which each have oppositely directed axially projecting peripheral flanges 46b and 46c respectively. This allows each belleville spring to act on both sides of its flat condition.
  • the second set of diaphragm springs 47 comprises individual belleville springs 47a which again have oppositely directed axially projecting peripheral flanges to again allow each individual spring to act on both sides of its flat condition.
  • FIG. 11 shows a further form of master cylinder 50 which includes an assistor spring means in the form of a single return diaphragm spring 56 and a single assistor diaphragm spring 57 which again acts on opposite sides of a piston 52 slideable in a bore 53.
  • the bore is replenished from a reservoir 51 via a non-return valve 58 and piston 52 pressurises a working chamber 54 which is connected with a slave cylinder (not shown) via piping 55.
  • springs 56 and 57 are again generally of the form shown in figures 8 and 9 respectively and these springs thus combine to give an overall master cylinder spring assistance characteristic for pedal 11 generally of the form shown in figure 10.
  • the master cylinder arrangements shown in figure 6 and 11 are not only useable with a main driven plate clamping diaphragm spring having a flat characteristic of the form shown in figure 2 but could be used in any actuation system requiring an assistance characteristic generally of the form shown in figure 10.
  • the master cylinder of figures 6 and 11 could be actuated by a means other than pedal 11.
  • the master cylinder could be electrically actuated when forming part of a pedalless automatically controlled clutch system of the type shown, for example, in GB Patent 2215791.
  • spring arrangements 46/47 and 56/57 described above could be used outside the master cylinder provided they are appropriately connected with the pedal or other actuating means. These spring arrangements could also be used with mechanical operating mechanisms actuated by a pedal or other actuating means (e.g. an electric motor).

Landscapes

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

Abstract

L'invention concerne un système d'embrayage de véhicule dans lequel un disque d'embrayage (13) est serré entre un plateau de pression (15) et un volant (14) par un ressort diaphragme (16). L'embrayage est débrayé par enfoncement de la pédale d'embrayage (11) reliée au ressort diaphragme (16) au moyen d'un mécanisme de commande (24, 25, 26, 27, 30). Le ressort diaphragme (16) possède une caractéristique de charge de serrage d'un ressort sensiblement plat, de sorte que sa charge de serrage reste sensiblement constante pendant toute la durée de fonctionnement de l'embrayage. La pédale d'embrayage (11) possède un ressort de maintien (30) déterminant la résistance à l'enfoncement de la pédale pendant le débrayage, et les caractéristiques de fonctionnement du mécanisme de commande et/ou les caractéristiques d'élasticité du ressort de maintien font que la résistance à l'enfoncement de la pédale (11) augmente jusqu'à une résistance maximale au point de débrayage de l'embrayage ou à proximité de ce point, puis diminue ensuite. L'invention concerne également un maître-cylindre (40, 50) qui comprend des moyens de ressort de maintien et de rappel intérieur (46, 47; 56, 57), lesquels agissent sur un piston (42, 52) du cylindre pour aider au fonctionnement de la pédale d'embrayage associée (11).
PCT/GB2001/002573 2000-06-13 2001-06-12 Embrayages de vehicules WO2001096163A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AU64082/01A AU6408201A (en) 2000-06-13 2001-06-12 Vehicle clutches
GB0202566A GB2372546B (en) 2000-06-13 2001-06-12 Vehicle clutches
EP01938404A EP1289815A1 (fr) 2000-06-13 2001-06-12 Embrayages de vehicules
JP2002510318A JP2004503723A (ja) 2000-06-13 2001-06-12 乗物用クラッチ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0014339.6 2000-06-13
GB0014339A GB0014339D0 (en) 2000-06-13 2000-06-13 Vehicle clutches

Publications (1)

Publication Number Publication Date
WO2001096163A1 true WO2001096163A1 (fr) 2001-12-20

Family

ID=9893488

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2001/002573 WO2001096163A1 (fr) 2000-06-13 2001-06-12 Embrayages de vehicules

Country Status (5)

Country Link
EP (1) EP1289815A1 (fr)
JP (1) JP2004503723A (fr)
AU (1) AU6408201A (fr)
GB (2) GB0014339D0 (fr)
WO (1) WO2001096163A1 (fr)

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3302763A (en) * 1964-11-06 1967-02-07 Gen Motors Corp Clutch pedal with spring assist
US4553470A (en) * 1982-08-04 1985-11-19 Kabushiki Kaisha Daikin Seisakusho Assistor for reducing stepping force
EP0252583A2 (fr) 1986-06-28 1988-01-13 Automotive Products Public Limited Company Ensemble de matériau de garniture de friction et de dispositif support
EP0323036A1 (fr) 1987-12-24 1989-07-05 Automotive Products Plc Ensemble support et matériau de garniture de friction
US4878396A (en) * 1982-03-18 1989-11-07 Valeo Control mechanism for a mechanical coupling device
EP0390797A1 (fr) 1987-12-09 1990-10-10 Automotive Prod Plc Ensembble de materiau de garniture a friction et support.
EP0455694A1 (fr) 1989-01-27 1991-11-13 Automotive Prod Plc Materiau de garniture de friction et ensemble de support.
GB2247725A (en) 1990-09-08 1992-03-11 Automotive Products Plc Friction facing and carrier assembly
EP0510014A1 (fr) 1990-01-10 1992-10-28 Automotive Prod Plc Ensemble forme d'une garniture a friction et d'un support.
GB2272494A (en) 1992-04-11 1994-05-18 Automotive Products Plc A method of manufacture of a friction facing and carrier assembly and apparatus therefor
EP0638149A1 (fr) 1993-02-26 1995-02-15 Automotive Prod Plc Ensemble surface de contact a friction et support.
US5555774A (en) * 1995-03-06 1996-09-17 Ford Motor Company Control pedal effort reduction and return assist
DE19854106A1 (de) * 1998-11-24 2000-05-25 Continental Teves Ag & Co Ohg Hauptzylinder

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3302763A (en) * 1964-11-06 1967-02-07 Gen Motors Corp Clutch pedal with spring assist
US4878396A (en) * 1982-03-18 1989-11-07 Valeo Control mechanism for a mechanical coupling device
US4553470A (en) * 1982-08-04 1985-11-19 Kabushiki Kaisha Daikin Seisakusho Assistor for reducing stepping force
EP0252583A2 (fr) 1986-06-28 1988-01-13 Automotive Products Public Limited Company Ensemble de matériau de garniture de friction et de dispositif support
GB2243419A (en) 1987-12-09 1991-10-30 Automotive Products Plc Friction facing material and carrier assembly
EP0390797A1 (fr) 1987-12-09 1990-10-10 Automotive Prod Plc Ensembble de materiau de garniture a friction et support.
EP0442539A2 (fr) 1987-12-24 1991-08-21 Automotive Products Plc Ensemble support et matériau de garniture de friction
EP0323036A1 (fr) 1987-12-24 1989-07-05 Automotive Products Plc Ensemble support et matériau de garniture de friction
EP0455694A1 (fr) 1989-01-27 1991-11-13 Automotive Prod Plc Materiau de garniture de friction et ensemble de support.
EP0510014A1 (fr) 1990-01-10 1992-10-28 Automotive Prod Plc Ensemble forme d'une garniture a friction et d'un support.
GB2247725A (en) 1990-09-08 1992-03-11 Automotive Products Plc Friction facing and carrier assembly
GB2272494A (en) 1992-04-11 1994-05-18 Automotive Products Plc A method of manufacture of a friction facing and carrier assembly and apparatus therefor
EP0638149A1 (fr) 1993-02-26 1995-02-15 Automotive Prod Plc Ensemble surface de contact a friction et support.
US5555774A (en) * 1995-03-06 1996-09-17 Ford Motor Company Control pedal effort reduction and return assist
DE19854106A1 (de) * 1998-11-24 2000-05-25 Continental Teves Ag & Co Ohg Hauptzylinder

Also Published As

Publication number Publication date
GB0014339D0 (en) 2000-08-02
GB2372546B (en) 2004-12-08
AU6408201A (en) 2001-12-24
GB2372546A (en) 2002-08-28
JP2004503723A (ja) 2004-02-05
GB0202566D0 (en) 2002-03-20
EP1289815A1 (fr) 2003-03-12

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