EP3642508A1 - Embrayage centrifuge avec masses centrifuges fabriquées sans enlèvement de copeaux - Google Patents

Embrayage centrifuge avec masses centrifuges fabriquées sans enlèvement de copeaux

Info

Publication number
EP3642508A1
EP3642508A1 EP18730969.5A EP18730969A EP3642508A1 EP 3642508 A1 EP3642508 A1 EP 3642508A1 EP 18730969 A EP18730969 A EP 18730969A EP 3642508 A1 EP3642508 A1 EP 3642508A1
Authority
EP
European Patent Office
Prior art keywords
centrifugal
masses
centrifugal clutch
clutch
mass
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Withdrawn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
EP18730969.5A
Other languages
German (de)
English (en)
Inventor
Roman Heck
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
Publication of EP3642508A1 publication Critical patent/EP3642508A1/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Withdrawn legal-status Critical Current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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/06—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like
    • F16D43/08—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces
    • 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
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • 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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/06—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like
    • F16D43/08—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces
    • F16D43/10—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces the centrifugal masses acting directly on the pressure ring, no other actuating mechanism for the pressure ring being provided
    • 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
    • F16D2250/00—Manufacturing; Assembly
    • F16D2250/0023—Shaping by pressure
    • 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
    • F16D2250/00—Manufacturing; Assembly
    • F16D2250/0084—Assembly or disassembly

Definitions

  • the present invention relates to a centrifugal clutch for a powertrain of a motor vehicle, such as.
  • a motorcycle, a light-horsepower or a scooter with an input member, such as a primary wheel or a gear, which serves for torque introduction, an output member, such as a shaft which serves for torque output, and a switchable friction unit, which is arranged between the input member and the output member and frictionally connects the input member to the output member to transmit torque, wherein for actuating the friction unit, an engine-side centrifugal mass and a transmission-side centrifugal mass are present which are in operative contact with an engine-side or gear-side angle plate such that a radial displacement of at least one of the centrifugal masses forces / causes an axial displacement of the respective / corresponding angle plate.
  • Centrifugal clutches serve in such drive trains to compensate for a drive speed and a transmission speed, in particular during startup of the motor vehicle.
  • the engine-side centrifugal masses facilitate the start-up and the transmission-side centrifugal masses secure the friction fit of the clutch.
  • the dual centrifugal force system makes maximum use of the speed map generated by the engine and reduces fuel consumption.
  • Centrifugal clutches also referred to as semi-automatic motorcycle clutches or semi-automatic clutches, are already well known in the art.
  • the unpublished DE 10 2017 103 108.1 discloses a centrifugal clutch for a drive train of a motor vehicle, comprising an input part, an output part arranged coaxially and rotatably relative to the input part, and a friction unit which can be switched by centrifugal force the friction unit with the input part rotatably connected first friction elements and with the output part rotatably connected second travel belemente, which are arranged alternately layered in an axial direction and for closing the centrifugal clutch by means of at least one centrifugal force switching switching device can be brought into frictional engagement, wherein the at least one centrifugally dependent switching switching device comprises at least one flyweight, which by a at least one centrifugal force depending on a rotation The centrifugal force occurring from the open position to the closed position in a first movement range by at least one brake spring counter to the direction of movement of the at least one flyweight with a first braking force and in a second range of motion is applied by the at least one centrifugal force
  • the unpublished DE 10 2017 103 190.1 discloses a centrifugal clutch having an input part, a coaxial with the input part and rotatably arranged output part and a centrifugal force-dependent switchable between the input part and the output part friction unit, wherein the friction unit with the input part rotatably connected first friction elements and with a leaf spring core of the output member rotatably connected second friction elements which are arranged alternately layered in an axial direction and for closing the centrifugal clutch by means of at least one centrifugally dependent switching switching means frictionally engageable and braced against a platen, wherein the leaf spring core at least a fastener extending through the platen and to which the platen is secured by a snap ring.
  • a friction clutch for a drive train of a motor vehicle comprising a rotatable about an axis arranged, motor-side input part and with this by means of friction partners to form a Frictionally frictionally connectable, gear-side output part, wherein the friction partners by means of at least one centrifugally controlled actuator axially against each other are formed braced.
  • an engine-side actuating device is provided between the input part and the friction partners and a drive-controlled actuating device is provided between the output part and the friction partners.
  • the engine-side centrifugal masses are centered under centrifugal force with the aid of pins in a groove in the primary wheel. Due to the radial displacement under centrifugal force, the centrifugal weights or centrifugal masses move an angle plate over ramps in the axial direction until the plate pack is compressed and the gear is synchronized. When the transmission has been synchronized, the transmission-side centrifugal masses are accelerated. The transmission-side centrifugal masses are guided by the structure as well as the engine-side centrifugal masses. In contrast to the engine-side centrifugal masses, the transmission-side centrifugal masses on a higher weight in order to realize the necessary contact pressure.
  • the clutch is closed when increasing the speed by the centrifugal forces.
  • Another possible guidance of the centrifugal masses is to make the outer disk carrier or the guide plate so that the masses are moved on this guided.
  • both options lead to serious disadvantages: So in the guide over the centering pins a total of twelve cylinder pins needed, which means an increased installation costs and additional costs.
  • the primary wheel must be sped up, since the tolerance position is very narrow in order to be able to generate the guide track for the cylinder pins and, moreover, must subsequently be heat-treated, resulting in additional costs during machining.
  • the second guide option requires additional cutting of the masses, which also results in additional costs.
  • the object of the invention is to avoid or at least mitigate the disadvantages of the prior art, and in particular to provide a way to guide the centrifugal masses in the clutch, that simplifies the assembly and the cost of the items and the processing be reduced.
  • the object of the invention is achieved in a generic centrifugal clutch according to the invention that at least one of the centrifugal masses has such a recess that at least one input device fixed device, such as.
  • the primary wheel or an outer disc carrier having an arm which engages in the recess, that a guidance of the centrifugal force-induced radial displacement of at least one of the centrifugal masses is achieved / ensured / forced.
  • centrifugal force masses for example two, three or four, are distributed over the circumference both on the engine side and on the transmission side.
  • three centrifugal masses are provided both on the engine side and on the transmission side. Uniform distribution over the circumference ensures that that by the radial displacement of the centrifugal masses (by the action of centrifugal force) no imbalance is generated.
  • the recess is formed as a guide groove, which is preferably open at a radially outer end.
  • fixed devices can intervene to guide the centrifugal mass on the one hand, and on the other hand limit their radial displacement.
  • the centrifugal masses is designed as a forging, stamping, embossing or a comparable chipless manufactured component. The non-cutting production of centrifugal masses allows a significant cost savings compared to the machining process.
  • the centrifugal mass has an embossed bevel at preferably a radially inner end of the recess. This slope causes radial displacement of the centrifugal mass, the axial displacement of the angle plate.
  • the input device-fixed device is designed as an outer disk carrier or as a holding plate.
  • the arm is formed by forming. Forming is a cost effective method of manufacture, which can save costs.
  • the embossed bevel forms an angle greater than 0 ° and less than 90 °, preferably approximately 45 °, to a horizontal plane.
  • a steeper bevel ensures that there is no unwanted self-locking and thus disrupting the operation of the centrifugal clutch.
  • the at least one engine-side centrifugal mass is connected to the input component in a manner secure against rotation.
  • the angle plates have at least one bevel, which is geometrically adapted to the embossed slope of the centrifugal mass, that they rest against each other in an operating condition.
  • the invention is that the centrifugal masses are designed so that they can be easily produced by stamping and stamping.
  • the new guide takes place via the holding plate or the outer plate carrier. This results in a guide groove and a stamped bevel for the axial displacement of the angle plate.
  • an additional processing of the centrifugal masses is no longer necessary.
  • the angle plates must be redesigned accordingly.
  • the retaining plate or the outer plate carrier are constructed with shaped arms, so that they serve as a guide and at the same time as a stop of the centrifugal masses.
  • the invention relates to a centrifugal clutch or a semi-automatic multi-disc clutch, in particular for scooters, in which the guidance of the centrifugal masses takes place via the retaining plate or the outer disc carrier.
  • the centrifugal masses each have a guide groove and an embossed bevel.
  • Fig. 1 is a longitudinal sectional view of a centrifugal clutch
  • Fig. 2 is a simplified longitudinal sectional view of that shown in Fig. 1
  • Figure 3 shows a perspective view of a motor-side centrifugal mass and a transmission-side centrifugal mass
  • Figure 4 is a plan view of a primary wheel with mounted motor-side centrifugal mass and motor side angle plate.
  • Fig. 5 is a plan view of the primary gear with mounted gear-side centrifugal mass and gearbox side angle plate.
  • Fig. 1 shows a longitudinal sectional view of a centrifugal clutch 1, as for example.
  • the centrifugal clutch 1 has an input component 2 for torque introduction, which is transmitted from a motor (not shown), and an output component 3 for transmitting torque or torque to a transmission (not shown).
  • a switchable friction unit 4 is formed, via which by frictional engagement the torque introduced via the input component 2 will be transmitted to the output component 3 and thus to the transmission.
  • the centrifugal clutch 1 can also be referred to as a multi-plate clutch.
  • the centrifugal clutch 1 further comprises a motor-side centrifugal mass 5 and a gear-side centrifugal mass 6, which are in operative contact with an angle-side or gear-side angle plate 7, 8.
  • the respective centrifugal mass 5, 6 has a recess 9 (see FIG. 3) into which an apparatus 10 fixed in the input member is secured by means of an arm 11 (see FIG. 2) to guide the centrifugal mass 5, 6 and to limit the radial displacement.
  • the friction unit 4 comprises first friction elements 12, which are designed, for example, as steel disks, and second friction elements 14, which are designed, for example, as friction disks 15, which are arranged alternately in the axial direction.
  • first friction elements 12 are arranged on an outer disk carrier 16
  • second friction elements 14 are arranged on an inner disk carrier 17.
  • the outer disk carrier 16 and the inner disk carrier 17 are arranged coaxially with one another, so that the inner disk carrier 17 is arranged radially inside the outer disk carrier 16.
  • the frictional engagement of the friction unit 4 is effected in such a centrifugal clutch 1 by the fact that the first friction elements 12 and the second friction elements 14 are pressed against each other by centrifugal force such that a frictional engagement between these friction elements 12, 14 and thus a torque of the input component 2 is transmitted to the output component 3.
  • centrifugal masses 5, 6 are displaced radially dependent on centrifugal force, which leads to an axial displacement of the angle plates 7, 8 due to the operative connection between the centrifugal mass 5 and 6 and the angle plate 7 and 8 respectively.
  • This axial displacement of the angle plate or the angle plates 7, 8 causes an axially displaceable disc part 18 is axially displaced in the direction of the friction unit 4, so that a frictional engagement occurs with sufficient centrifugal force.
  • the input component 2 is embodied here as a primary wheel 19 which is connected to a motor (not shown) in torque-transmitting manner.
  • the output member 3 transmits the torque transmitted from the input member 2 via the friction unit 4 to a transmission (not shown) via a shaft (not shown).
  • the shaft is arranged coaxially with the input component 2 or the output component 3 and, in the embodiment shown here, is supported by a rolling bearing 20 in the primary wheel 19 such that the shaft (not shown) and the primary wheel 19 can rotate independently of one another (see FIG . 1 ).
  • centrifugal masses 5 and 6 are shown in a perspective view.
  • three centrifugal masses are provided both on the engine side and on the drive side, which is why the shape of a centrifugal mass 5, 6 in the circumferential direction corresponds to one third of a complete circle. speaks. It can be seen that the engine-side centrifugal mass 5 is smaller than the engine-side centrifugal mass 6. That is, the gear-side centrifugal mass 6 has a higher mass than the engine-side centrifugal mass 5.
  • the centrifugal mass 5 and 6 is stamped and stamped and has a radially extending recess 9, at the radially inner end of a slope 21 is formed in the manner of a ramp, which is also made by embossing.
  • this recess 9 engages in each case an arm 1 1 of the input device fixed device 10, which motor side in the embodiment shown here corresponds to the outer disk carrier 16 (see FIG. 4) and the gear side corresponds to a holding plate 22 (see FIG. 5).
  • the retaining plate 22 is connected to the output member 3.
  • the angle plate 7 and 8 is formed as a disk-shaped or plate-shaped component, which has beveled or inclined finger 24 in the radial direction.
  • the fingers 24 are geometrically matched to the bevel 21 of the respective centrifugal mass 5, 6 so that they rest against one another in an operating state of the centrifugal force coupling 1 (here in the decoupled state) (see FIG. 2).
  • the motor-side angle plate 7 is fixed by means of three circumferentially equally distributed centering pin 25 on the primary wheel 19 radially and against rotation.
  • the centering pin 25 in the axial direction permits a displacement of the angle plate 7.
  • Fig. 5 shows the transmission-side centrifugal mass 6 and the transmission-side angle plate 8 in the mounted state.
  • the transmission-side centrifugal masses 6 are guided over the arms 1 1 of the holding plate 22, which is likewise connected by means of a rivet bolt 26 to the primary wheel 19.
  • the gear-side angle plate 8 also has in the radial direction bevelled fingers 24, which also, as already described in Fig. 4, in an operating condition of the centrifugal clutch 1 on the Slant 21 of the transmission-side centrifugal mass 6 rest.
  • the gear-side angle plate 8 is centered about a centering pin 27, which, as already the centering pin 25 allows a displacement of the angle plate 8 in the axial direction.
  • centrifugal clutch 1 By such a structure of the centrifugal clutch 1, the manufacturing tolerances no longer have to be designed so narrow, which is why the centrifugal masses 5 and 6 are produced by means of cheaper methods such as stamping and embossing or forging or another chipless manufacturing process. Also, the primary wheel 19 as input component 2 can be manufactured with lower accuracy, without resulting in disadvantages in operation.
  • the arms 1 1 of the outer disk carrier 16 and the holding plate 22 can be produced by forming, whereby the cost of producing the outer disk carrier 16 and the holding plate 22 are reduced. All in all, the exemplary embodiment of the centrifugal clutch 1 shown here is a more cost-effective variant compared with the centrifugal force clutches known from the prior art, which also requires less installation effort.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un embrayage centrifuge (1) pour une chaîne cinématique d'un véhicule automobile, comprenant un composant d'entrée (2) qui sert à introduire un couple, un composant de sortie (3) qui sert à fournir en sortie un couple, et une unité de frottement (4) commutable qui est disposée entre le composant d'entrée (2) et le composant de sortie (3) et qui relie par engagement par friction, avec transmission de couple, le composant d'entrée (2) au composant de sortie (3), une masse centrifuge (5) du côté du moteur et une masse centrifuge (6) du côté de la boîte de vitesses étant prévues pour actionner l'unité de frottement (4), lesquelles sont en contact fonctionnel avec une tôle coudée du côté du moteur, respectivement du côté de la boîte de vitesses (7, 8), de telle sorte qu'un déplacement radial d'au moins l'une des masses centrifuges (5 ; 6) entraîne un déplacement axial de la tôle coudée respective (7 ; 8), au moins l'une des masses centrifuges (5 ; 6) présentant un évidement (9) de telle sorte qu'au moins un dispositif (10) fixé au composant d'entrée présente un bras (11) qui vient en prise dans l'évidement (9) de manière à garantir un guidage du déplacement radial d'au moins l'une des masses centrifuges (5 ; 6).
EP18730969.5A 2017-06-19 2018-05-30 Embrayage centrifuge avec masses centrifuges fabriquées sans enlèvement de copeaux Withdrawn EP3642508A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017113349.6A DE102017113349A1 (de) 2017-06-19 2017-06-19 Fliehkraftkupplung mit spanlos gefertigten Fliehkraftmassen
PCT/DE2018/100526 WO2018233758A1 (fr) 2017-06-19 2018-05-30 Embrayage centrifuge avec masses centrifuges fabriquées sans enlèvement de copeaux

Publications (1)

Publication Number Publication Date
EP3642508A1 true EP3642508A1 (fr) 2020-04-29

Family

ID=62599407

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18730969.5A Withdrawn EP3642508A1 (fr) 2017-06-19 2018-05-30 Embrayage centrifuge avec masses centrifuges fabriquées sans enlèvement de copeaux

Country Status (5)

Country Link
US (1) US11346406B2 (fr)
EP (1) EP3642508A1 (fr)
CN (1) CN110709620A (fr)
DE (2) DE102017113349A1 (fr)
WO (1) WO2018233758A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11572924B1 (en) 2022-02-01 2023-02-07 Schaeffler Technologies AG & Co. KG Centrifugal mass assembly for a clutch

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1161423A (en) 1914-12-21 1915-11-23 James Swanda Friction-clutch.
US1552012A (en) 1922-08-14 1925-09-01 B E Sipe Clutch
US4328877A (en) 1980-04-18 1982-05-11 Ballard Billie E Automatic two-speed drive system
US5070984A (en) * 1990-10-22 1991-12-10 Fehring Thomas C Adjustable centrifugal clutch
CA2228088C (fr) * 1998-01-28 2002-08-13 Robert Joss Embrayeur a commande centrifuge
US7137498B2 (en) 2004-03-11 2006-11-21 Eaton Corporation Centrifugal clutch with improved wear life and disengagement characteristics
US7367440B2 (en) * 2005-02-03 2008-05-06 Meritor Transmission Corporation Variable engagement centrifugal clutch assembly
US7530438B2 (en) * 2005-12-01 2009-05-12 Eaton Corporation Single-plane ramp noise reduction for a centrifugal clutch
US8210333B2 (en) * 2007-06-29 2012-07-03 Yamaha Hatsudoki Kabushiki Kaisha Clutch and vehicle having clutch
WO2015135540A1 (fr) * 2014-03-12 2015-09-17 Schaeffler Technologies AG & Co. KG Embrayage à friction à commande centrifuge
JP2016041944A (ja) * 2014-08-14 2016-03-31 株式会社マキタ 遠心クラッチ装置
CN105240423A (zh) * 2015-10-16 2016-01-13 上海稳健压缩机有限公司 联轴器及空气压缩机
DE102016204111A1 (de) 2016-03-14 2017-09-14 Schaeffler Technologies AG & Co. KG Reibungskupplung
DE102016211217B3 (de) 2016-06-23 2017-12-14 Schaeffler Technologies AG & Co. KG Fliehkraftkupplung mit reibungsminimiertem Koppelbolzen und Antriebsstrang
DE102016223606A1 (de) * 2016-11-29 2018-05-30 Schaeffler Technologies AG & Co. KG Fliehkraftkupplung mit zwei in Reihe geschalteten Teilkupplungen
DE102017103190A1 (de) 2017-02-16 2018-08-16 Schaeffler Technologies AG & Co. KG Fliehkraftkupplung für einen Antriebsstrang eines Kraftfahrzeugs mit zumindest einem Befestigungselement für eine Gegendruckplatte
DE102017103108A1 (de) 2017-02-16 2018-08-16 Schaeffler Technologies AG & Co. KG Fliehkraftkupplung für einen Antriebsstrang eines Kraftfahrzeugs mit gebremsten Fliehmassen

Also Published As

Publication number Publication date
CN110709620A (zh) 2020-01-17
DE102017113349A1 (de) 2018-12-20
DE112018003120A5 (de) 2020-03-05
US11346406B2 (en) 2022-05-31
US20200096060A1 (en) 2020-03-26
WO2018233758A1 (fr) 2018-12-27

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