WO2004015289A1 - Mechanisch-drehzahlabhängig schaltende fliehkraftkupplung - Google Patents
Mechanisch-drehzahlabhängig schaltende fliehkraftkupplung Download PDFInfo
- Publication number
- WO2004015289A1 WO2004015289A1 PCT/EP2003/008219 EP0308219W WO2004015289A1 WO 2004015289 A1 WO2004015289 A1 WO 2004015289A1 EP 0308219 W EP0308219 W EP 0308219W WO 2004015289 A1 WO2004015289 A1 WO 2004015289A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- coupling according
- disc
- force
- counter
- spring
- Prior art date
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
- 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
Definitions
- the invention relates to a speed-dependent centrifugal clutch which interrupts or establishes the flow of power between the input and output when a predetermined speed is exceeded and also independently restores or interrupts the flow of power when the specified speed is undershot.
- Such a clutch for example for driving auxiliary units by the engine of a motor vehicle, may only take up a small amount of space.
- the invention has for its object to provide an inexpensive and as small as possible speed-dependent centrifugal clutch.
- a speed-dependent clutch with a shaft as the first rotating part for torque transmission, which is connected in a rotationally fixed manner to at least one first disk, and with a second rotating part for torque transmission freely rotatably mounted on the shaft, with the at least one counter disk is non-rotatably connected, the first disc and / or the counter disc being mounted so as to be axially displaceable, furthermore with at least one pressure spring element acting on at least one of the axially displaceable disks and with a centrifugal force element which is operatively connected to one of the axially displaceable disks, the centrifugal forces which become effective when the clutch rotates exert an axial force on the associated axially displaceable disk.
- Such a coupling can not only be compact, but also offers the advantage that the axial force caused by the centrifugal forces separates the two disks, depending on the arrangement, only when a predetermined speed is reached, and thus the force flow between the first rotating part and the second rotating part interrupts or brings the two discs against each other and thus creates the power flow between the two turned parts.
- At least one of the disks is expediently provided with a friction lining.
- the spring characteristic of the pressure spring element can be designed so that the two clutch disks quickly separate from one another when the predetermined speed is reached. This is possible, for example, when the spring characteristic of the pressure spring element initially rises steeply to the point at which the counterforce of the pressure spring element still transmits the required torque between the disks and then flattens out, so that the axial force exerted by the centrifugal force element causes the The clutch opens quickly with only a small amount of slip.
- the clutch also closes very quickly, the slip occurring being essentially determined by the acceleration to be applied to the unit to be driven.
- the second rotating part is designed as a housing which comprises the disks, the springs and the centrifugal force element.
- the housing can be open or closed, and a closed design can also be liquid-tight. The outer circumference of the essentially cylindrical housing can then be used to initiate or tap the torque.
- the first disk is mounted on the shaft in a rotationally fixed but axially displaceable manner and is supported on a counter spring which is aligned in its force effect against the force effect of the spring element.
- the counter spring and the spring element which are both preloaded, the two disks are pressed against one another, so that the pressing force, which is necessary for the torque transmission, is effected in accordance with the preload of both springs. If an increasing axial force acting on the counter disc and thus on the spring element is built up during operation by the centrifugal force element, the influence of the spring element on the counter disc is correspondingly reduced.
- This reduction is compensated for by the tracking of the first disc via the counter spring according to its characteristic curve, so that a high frictional force between the discs can be maintained up to the predetermined switching point.
- the wear of the adjoining surfaces of the two disks is also compensated for by the tracking of the disk by the counter spring.
- Fig. 2 shows a modified embodiment of the arrangement.
- Fig. 3 shows another embodiment
- the embodiment of a speed-dependent clutch shown in a longitudinal section in the closed position in FIG. 1 essentially consists of a shaft 1 as the first rotating part for torque transmission, which is non-rotatably connected to at least one disk 2, and a second, freely rotatably mounted on the shaft 1 Turned part 3 for torque transmission.
- the second rotating part 3 is mounted on the shaft 1 via bearings 4 and 5, the bearing 5 simultaneously serving to axially support the rotating part 3, for example in the form of an angular contact ball bearing.
- the second rotating part 3 is designed like a housing and comprises both the disk 2 and a counter disk 6, which is connected to the second rotating part 3 in a rotationally fixed but axially displaceable manner, and the further components assigned to these, which will be described in more detail below ,
- the outer circumference of the second rotating part 3 can be provided for torque transmission with at least one circumferential groove for a V-belt drive or with a toothing for a toothed belt drive or a gear drive.
- the first rotating part, ie shaft 1 is used for torque introduction (drive side) or the torque tap (output side). This special design allows the clutch to be used simultaneously as a gear element for translating the output into slow or fast.
- the disk 2 which is connected to the shaft 1 in a rotationally fixed manner, is arranged to be axially displaceable to a limited extent on the shaft 1, for example via a corresponding longitudinal toothing 7 between the outer periphery of the shaft 1 and the inner periphery of the corresponding bore of the disk 2.
- the counter disc 6, which is non-rotatably connected to the second rotating part 3 is axially displaceably connected to the second rotating part 3, corresponding axially aligned teeth 8 being provided on the inner circumference of the second rotating part 3 on the one hand and on the outer circumference of the counter disc 6 on the other hand.
- the counter disc 6 is supported on a spring element 9, which in turn is supported on a corresponding support area of the second rotating part 3, here for example a cover 10.
- the spring element 9 is preloaded so that the counter disc 6 presses against the disc 2 with such a force that a frictional force is present between the two discs 2 and 6, which is at least sufficient to transmit the predetermined torque.
- At least one of the facing surfaces of the two disks 2 and 6 can be provided with an appropriately designed friction or clutch lining.
- the counter disk 6 is assigned a centrifugal force element 11 which, in the exemplary embodiment shown here, has two end-side rings 11.1 and 11.2, which can be deflected over a plurality of substantially axially aligned and radially Coupling elements 12 are interconnected.
- Each coupling element 12 is provided with a mass body 13 in the area between the two rings 11.1 and 11.2.
- the rings 11.1 and 11.2 solid and to form the coupling elements 12 by rods or the like which are each connected in an articulated manner
- a very easily constructed and easy to manufacture arrangement is achieved in that, on the one hand, the Coupling elements 12 are designed as spiral springs and the centrifugal element including the rings 11.1 and 11.2 is formed overall as a stamped molded part, so that the coupling elements 12 designed as spiral springs and the rings 11.1 and 11.2 are integrally connected with one another in a materially integral manner.
- the design of the centrifugal force element 11 is carried out in such a way that the ring 11.2 is supported on the second rotating part 3, which is designed as a housing, and the other ring 11.1 bears on the counter disc 6.
- Fig. 1 the overall arrangement is shown at a standstill, so that the spring element 9 presses the counter disc 6 against the disc 2, wherein no axial forces are exerted on the counter disc 6 via the centrifugal element 11.
- the coupling elements 12 are designed as articulated elements or the like, a corresponding configuration must be created.
- the disk 2 connected to the shaft 1 is supported on a counter spring 14 in the axial direction with respect to the shaft 1, the spring force of the counter spring 14 being counter to the spring force of the spring element 9.
- the opposing spring forces of the spring element 9 and the counter spring 14 determine the pressing force and thus the frictional force between the discs 2 and 6 and thus the transmissible torque.
- centrifugal forces CF act on the centrifugal force element 11 via the mass bodies 13, which centrifugal forces CF increase proportionally to the square of the rotational speed and accordingly convert into an increasing axial compressive force acting axially on the counter disc 6 via the coupling elements 12 pointing inwards.
- the axially displaceable disk 2 which is supported by the counter spring 14, has the advantage that the wear on the adjoining disk surfaces is caused by the unavoidable, if slight, slippage when opening and closing the clutch is compensated. There is no need to readjust.
- the disc 3 can be corresponding to the preload and the spring characteristics of the counter spring 14 Counter spring 14 are "tracked" by force, so that always a correspondingly large, applied from the counteraction of the counter spring 14
- This effect can be further improved in that the stroke of the disk 2 to be effected by the counter spring 14 or the counter spring 14 itself is limited, so that the tracking force applied by the counter spring 14 ends and the pressing force between the two disks is suddenly set to zero , This can be achieved, for example, by providing a stop for the stroke of the disk 2 in the direction of the counter disk 6.
- the spring element 9 has a linear spring characteristic, so that the costly pressing force applied to the axially fixed disc 2 via the counter disc 6 corresponds to the predetermined spring tension.
- the two disks 6 and 2 remain pressed together until the centrifugal force-proportional, applied by the centrifugal force element 11 ..
- Axial force at the equilibrium point reaches the same size as the pressing force, so that as the axial force increases, the counter disk 6 from the disk 2 lifts off and the clutch is disconnected.
- the spring element 9, on the one hand, and the opposing spring force of the counter spring 14, on the other hand determine certain contact pressure due to the longitudinal displaceability of the washer 2 with a corresponding design of the two springs maintain a corresponding displacement path of the disk 2, so that the minimum difference determining the transferable torque between the pressing force F and the increasing axial force can be maintained over a corresponding displacement path during a displacement practically via the counter spring 14.
- a degressive course or a declining-progressive course can be used for the spring element 9.
- the spring circuit can be designed by appropriate constructive measures or designs of known type such that the transition between the degressive part and the progressive part runs horizontally over a predeterminable stroke distance, the horizontal range of the spring characteristic is to be assigned to the opening range of the clutch. Since the centrifugal force-proportional axial force grows very quickly, the force of the spring element in the degressive area decreases accordingly, the two disks separate very quickly, so that the slip-dependent speed range when opening the clutch can be significantly reduced.
- FIG. 2 shows an embodiment modified from FIG. 1.
- the same components are provided with the same reference numerals, so that reference can be made to the description of FIG. 1.
- Fig. 1 consists in the fact that the axially displaceable on the shaft 1, but non-rotatably mounted disc 2.1 on both sides is assigned a counter disc 6.1 and 6.2.
- the counter disc 6.1 is supported by a counter spring 14 on the cover 10 of the housing-like rotating part.
- the counter disc 6.2 is in turn supported by a spring element 9 on the housing-like rotating part 3.
- the centrifugal force element 11 is connected with its two end rings 11.1 and 11.2 in a form-fitting manner to the counter disc 6.1 on the one hand and the housing 3 on the other hand, so that a tensile force acting in the axial direction acts on the outwardly facing coupling elements 12 when the centrifugal forces CF applied by the mass bodies 13 act is applied to the counter disc 6.2.
- the operation of this version corresponds to the execution according to the rest. Fig. 1.
- the embodiment according to. 1, in which the centrifugal force element 11 is designed such that it transmits compressive forces when the centrifugal forces CF act by radially spreading apart the coupling elements 12 via the rings 11.1 and 11.2, can also be designed as a multi-plate clutch.
- part of the coupling elements 12 assigned to the counter discs 6 is finger-shaped, which are passed through recesses in the counter disc 6.1 assigned to the centrifugal force element and act on the other counter disc 6.2, both counter discs 6 enclosing the disc 2 on both sides.
- the mode of operation can also be reversed with a corresponding design, ie the clutch is open in the lower speed range and the clutch only closes when a predetermined speed is exceeded, so that the unit to be coupled is driven only above the predetermined speed becomes.
- a centrifugal force element 11 of the design shown in FIG. 2 is used, which is designed such that it keeps the clutch open against the force of the spring element 9 at a standstill and the counter disk 6 only when a predetermined speed is exceeded can come to rest on the disc 2.
- the interior can be filled with a fluid, for example an oil, in order to make the coupling more gentle.
- a fluid supply which can be guided via axial bores in the shaft, it is possible to circulate the fluid via a cooler.
- FIG. 3 corresponds in its basic structure to the embodiments according to FIGS. 1 and 2, so that the same components are provided with the same reference numerals. Accordingly, with regard to the mode of operation, reference can also be made to the description of the embodiments according to FIGS. 1 and 2.
- FIG. 3 differs from the previously described embodiments according to FIGS. 1 and 2 essentially in that instead of just one disk 2, a disk package formed from a plurality of disks 2.1 is used, which is connected in a rotationally fixed manner to and on the shaft 1 is axially displaceable to a limited extent, for example via a corresponding longitudinal toothing.
- a plurality of letters 6.1 are used, which are connected to the rotating part 3 in a rotationally fixed but axially displaceable manner, the discs 2.1 alternating with the discs 6.1 in engagement and forming a disc package.
- the coupling elements 12 of the individual centrifugal force elements are each designed as an articulated lever arrangement 12.0, which will be described in more detail below.
- the articulated lever arrangement 12.0 is connected to a ring 11.3, which bears against the disk package formed from the disks 2.1 and 6.1.
- the articulated lever arrangement 12.0 essentially consists of a two-armed angle lever 15, the free end of which is connected to a mass body 13.
- the other end of the angle lever 15 is connected to a transmission lever 16 which extends essentially in the axial direction and which is articulated on the ring 11.3.
- the angle lever 15 is mounted on the hinge 17 on a hinge bracket 18 which is fixed to the rotating part 3. Several such centrifugal elements are mounted on the rotating part 3 distributed over the circumference.
- the drive torque can now be introduced via a belt attachment 3.1 of the rotating part 3 and can be taken directly from the shaft 1 - or as shown here - from a countershaft 19 via a transmission gear.
- the individual disk packs 2.1 of the disk pack are provided with a friction lining 21 on both sides.
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
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10393003T DE10393003D2 (de) | 2002-08-06 | 2003-07-25 | Mechanisch-drehzahlabhängig schaltende Fliehkraftkupplung |
AU2003266952A AU2003266952A1 (en) | 2002-08-06 | 2003-07-25 | Centrifugal clutch which mechanically shifts according to the engine speed |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10236032.4 | 2002-08-06 | ||
DE2002136032 DE10236032A1 (de) | 2002-08-06 | 2002-08-06 | Mechanisch-drehzahlabhängig schaltende Fliehkraftkupplung |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004015289A1 true WO2004015289A1 (de) | 2004-02-19 |
Family
ID=30469495
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/008219 WO2004015289A1 (de) | 2002-08-06 | 2003-07-25 | Mechanisch-drehzahlabhängig schaltende fliehkraftkupplung |
Country Status (3)
Country | Link |
---|---|
AU (1) | AU2003266952A1 (de) |
DE (2) | DE10236032A1 (de) |
WO (1) | WO2004015289A1 (de) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191202125A (en) * | 1912-01-26 | 1912-11-28 | Peto And Radford Ltd | An Improved Clutching Device for Preventing a Driven Shaft Rotating in Excess of a Predetermined Speed. |
US2555929A (en) * | 1945-07-27 | 1951-06-05 | Jensen Kaj Leo | Constant speed clutch governor |
US2631708A (en) * | 1949-08-13 | 1953-03-17 | Knapp Monarch Co | Constant speed centrifugal clutch |
CH567205A5 (en) * | 1973-04-16 | 1975-09-30 | Klaue Hermann | Constant speed coupling for motor vehicles - spring loaded friction clutch as centrifugal governor maintains constant output speed by slipping action |
DE3031647A1 (de) * | 1980-08-22 | 1982-03-04 | Bergwerksverband Gmbh, 4300 Essen | Magnetkupplung |
-
2002
- 2002-08-06 DE DE2002136032 patent/DE10236032A1/de not_active Withdrawn
-
2003
- 2003-07-25 AU AU2003266952A patent/AU2003266952A1/en not_active Abandoned
- 2003-07-25 WO PCT/EP2003/008219 patent/WO2004015289A1/de not_active Application Discontinuation
- 2003-07-25 DE DE10393003T patent/DE10393003D2/de not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB191202125A (en) * | 1912-01-26 | 1912-11-28 | Peto And Radford Ltd | An Improved Clutching Device for Preventing a Driven Shaft Rotating in Excess of a Predetermined Speed. |
US2555929A (en) * | 1945-07-27 | 1951-06-05 | Jensen Kaj Leo | Constant speed clutch governor |
US2631708A (en) * | 1949-08-13 | 1953-03-17 | Knapp Monarch Co | Constant speed centrifugal clutch |
CH567205A5 (en) * | 1973-04-16 | 1975-09-30 | Klaue Hermann | Constant speed coupling for motor vehicles - spring loaded friction clutch as centrifugal governor maintains constant output speed by slipping action |
DE3031647A1 (de) * | 1980-08-22 | 1982-03-04 | Bergwerksverband Gmbh, 4300 Essen | Magnetkupplung |
Also Published As
Publication number | Publication date |
---|---|
AU2003266952A1 (en) | 2004-02-25 |
DE10393003D2 (de) | 2005-09-29 |
DE10236032A1 (de) | 2004-02-19 |
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