GB2347719A - Overload clutch unit - Google Patents

Overload clutch unit Download PDF

Info

Publication number
GB2347719A
GB2347719A GB0003656A GB0003656A GB2347719A GB 2347719 A GB2347719 A GB 2347719A GB 0003656 A GB0003656 A GB 0003656A GB 0003656 A GB0003656 A GB 0003656A GB 2347719 A GB2347719 A GB 2347719A
Authority
GB
United Kingdom
Prior art keywords
clutch
annular piston
annular
halves
plates
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.)
Granted
Application number
GB0003656A
Other versions
GB2347719B (en
GB0003656D0 (en
Inventor
Friedhelm Kempers
Dietrich Braun
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.)
Halbach and Braun Industrieanlagen GmbH
Original Assignee
Halbach and Braun Industrieanlagen 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 Halbach and Braun Industrieanlagen GmbH filed Critical Halbach and Braun Industrieanlagen GmbH
Publication of GB0003656D0 publication Critical patent/GB0003656D0/en
Publication of GB2347719A publication Critical patent/GB2347719A/en
Application granted granted Critical
Publication of GB2347719B publication Critical patent/GB2347719B/en
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs
    • F16D7/027—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs with multiple lamellae
    • 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
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members
    • F16D43/211—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members with radially applied torque-limiting friction surfaces

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Position, Course, Altitude, Or Attitude Of Moving Bodies (AREA)
  • Cigarettes, Filters, And Manufacturing Of Filters (AREA)

Abstract

A clutch unit 1 for the drives of mining and conveying devices, comprises a first clutch half 2 on the driving side, and a second clutch half 3 on the driven side, and a multi-plate clutch 4 which rotatably connects the two clutch halves. The clutch plates 4 are pressed against each other with frictional engagement, for the transmission of torque, by means of an annular piston 5 which can be acted upon by a pressure medium. One or more clutch springs 6 for storing the clutch force set by means of the annular piston are associated with the clutch plates 4 on the side thereof facing the annular piston. There is no disengagement of the clutch halves. Instead, overload protection is made possible by the elastic storage or transmission of the clutch force by means of the clutch springs, to allow the clutch halves to rotate relative to each other.

Description

"CLUTCH UNIT" This invention relates to a clutch unit, particularly for the drives of mining and conveying devices, having a clutch half on the driving side, a clutch half on the driven side, and having clutch plates which connect the two clutch halves, particularly in the form of construction of a multi-plate clutch, wherein the clutch plates of the two clutch halves can be pressed against each other with frictional engagement, for the transmission of torque, by means of an annular piston which can be acted upon by a pressure medium with the generation of a predetermined clutch force, and the annular piston rotates with one of the two clutch halves.
A clutch of this type is known as an overload clutch (see DE 31 30 050). Said overload clutch is equipped with a rotational speed monitoring device which operates and disengages the clutch at a predetermined difference in rotational speed between the two clutch halves. The action of pressure medium on the operating cylinder-and-piston arrangement which is necessary for this purpose is effected via a rotary leadthrough.
A basic object of the present invention is to create a clutch unit of the form of construction described at the outset which can be used in individual applications and which at the same time is distinguished by its reliability of operation and its simple construction.
According to the present invention, there is provided a clutch unit, particularly for the drives of mining and conveying devices, having a clutch half on the driving side, a clutch half on the driven side, and having clutch plates which connect the two clutch halves fixed in rotation, particularly in the form of construction of a multi-plate clutch, wherein the clutch plates of the two clutch halves can be pressed against each other with frictional engagement, for the transmission of torque, by means of an annular piston which can be acted upon by a pressure medium with the generation of a predetermined clutch force, and the annular piston rotates with one of the two clutch halves, wherein one or more clutch springs for storing the clutch force set by means of the annular piston are associated with the clutch plates on the side thereof facing or facing away from the annular piston. The annular piston, the clutch plates and the clutch springs consequently form a functional unit. Furthermore, provision is made for one or more singular pressure medium supply connections for the annular piston to be provided in one or the other clutch half. Due to the clutch springs, an elastic clutch is created which is capable of functioning without costly rotational speed monitoring or the like. In operation, the clutch instead functions automatically, as it were, if the set torque is exceeded.
The clutch force and with it the torque which is transmitted can be continuously adjusted via the pressure medium supply connection. In this manner, the clutch can be adapted to the respective operating requirements and to different drive configurations. The clutch adjustment is simply inspected and adapted when the clutch is at a standstill, e. g. by reading a manometer and varying the pressure by means of a hydraulic hand pump. A rotary leadthrough for hydraulics or electrics is no longer necessary, because the clutch force which is fixedly set by the annular piston is stored elastically by the clutch springs. As a result, the clutch unit according to the invention is distinguished by its particularly simple and operationally reliable construction.
Other features which are essential to the invention are listed below. Thus provision is made for the clutch springs to be constructed as annular springs. According to one preferred embodiment, the annular springs are constructed as a saucer springs. When a plurality of clutch springs is used, the individual saucer springs form a saucer spring stack. The saucer springs result in a particularly efficient and uniform transmission of the clutch force on to the clutch plates. Moreover, this design is distinguished by its particularly simple construction. In principe, however, it is also possible to employ a multiplicity of coil springs which are uniformly distributed over the periphery of the clutch plates.
In one advantageous embodiment of the clutch unit according to the invention, the clutch spring acts on the clutch plates with a pressure distribution ring disposed therebetween. The transmission of the spring force on to the clutch plates is thus optimised and non-uniform wear is prevented.
The invention is explained in more detail below with reference to the drawings, which merely illustrate examples of embodiments, and where: Figure 1 is a cross-section through a clutch unit according to the invention ; and Figure 2 is a cross-section through another embodiment of a clutch unit according to the invention.
The Figures show a clutch unit 1 for the drives of mining and conveying devices, having a clutch half 2 on the driving side, a clutch half 3 on the driven side, and having clutch plates 4 which connect the two clutch halves fixed in rotation, in the form of construction of a multiplate clutch. The clutch plates 4 of the two clutch halves 2,3 can be pressed against each other with frictional engagement, for the transmission of torque, by means of an annular piston 5 which can be acted upon by a pressure medium with the generation of a predetermined clutch force. The annular piston 5 rotates with the clutch half 3 on the driven side. The Figures also show that one or more clutch springs 6 for storing the clutch force set by means of the annular piston 5 are associated with the clutch plates 4 on the side thereof facing the annular piston 5.
In the embodiment shown in Figure 1, the clutch unit 1 acts as an overload protection device on the chain wheel 7 of a cutter drive. The clutch half 2 on the driving side is attached fixed in rotation to the drive shaft 8 of the cutter drive. The chain wheel 7, which is rotatably mounted, directly adjoins the clutch half 3 on the driven side. The annular piston 5 can be acted upon by pressure medium by means of an annular cylinder 9. For this purpose, a singular pressure medium supply connection 10 for the annular piston 5 or the annular cylinder 9 thereof is provided in the clutch half 3 on the driven side. The clutch springs 6 are constructed as annular springs 6. It can be seen from Figure 1 that the annular springs there are two saucer springs 6 which are combined in a saucer spring stack. These store the clutch force which is set by means of the annular piston 5. The annular piston 5, the saucer springs 6 and the clutch plates 4 consequently form a functional unit. It can also be seen from Figure 1 that the clutch springs 6 act on the clutch plates 4 with a pressure distribution ring 11 interposed therebetween. In operation, all the components of the clutch unit 1 are first of all in rotation. If the chain wheel 7 is overloaded and if the torque which can be transmitted is thus exceeded, the clutch half 2 on the driving side can continue to rotate at the predetermined speed of rotation, whilst the clutch half 3 on the driven side, together with the chain wheel 7, rotates at a reduced speed of rotation or is stopped completely. There is no disengagement of the clutch halves 2,3. Instead, the overload protection is made possible by the elastic storage or transmission of the clutch force by means of clutch springs.
Figure 2 shows the clutch unit according to the invention as an overload protection device for conveyor drives. Here, the clutch half 2 on the driving side is attached fixed in rotation to the driven shaft 12 of an electric motor, whilst a transmission shaft 13 adjoins the clutch half 3 on the driven side. A flexible rotary coupling 14 (Tschan), which is not explained in detail below, is provided for this purpose. The clutch unit 1 is disposed in a clutch housing 15.
Moreover, a brake linkage 16 is provided in the region of the clutch half 3 on the driven side.
The annular cylinder 9, the annular piston 5 and the clutch spring 6 are again disposed in the region of the clutch half 3 on the driven side. In this embodiment, only a single saucer spring 6 is provided, which again acts on the clutch plates 4 via a pressure distribution ring 11.
Whereas in the embodiment shown in Figure 1 the annular cylinder 9 is mounted on the drive-side shaft via a plain bearing arrangement 17, the annular cylinder 9 in the embodiment shown in Figure 2 is mounted on the drive-side shaft via a rolling bearing arrangement 18. Moreover, corresponding sealing means can be seen in Figures 1 and 2 between the annular cylinder and the annular piston.

Claims (6)

  1. CLAIMS 1. A clutch unit particularly for the drives of mining and conveying devices, having a clutch half on the driving side, a clutch half on the driven side, and having clutch plates which connect the two clutch halves fixed in rotation, particularly in the form of construction of a multi-plate clutch, wherein the clutch plates of the two clutch halves can be pressed against each other with frictional engagement, for the transmission of torque, by means of an annular piston which can be acted upon by a pressure medium with the generation of a predetermined clutch force, and the annular piston rotates with one of the two clutch halves wherein one or more clutch springs for storing the clutch force set by means of the annular piston are associated with the clutch plates on the side thereof facing or facing away from the annular piston.
  2. 2. A clutch unit according to claim 1, wherein one or more singular pressure medium supply connections for the annular piston (or the annular cylinder thereof) are provided in one or the other clutch half.
  3. 3. A clutch unit according to claims 1 or 2, wherein the clutch spring is constructed as an annular spring.
  4. 4. A clutch unit according to claim 3, wherein the annular spring is constructed as a saucer spring.
  5. 5. A clutch unit according to any one of claims 1 to 4, wherein the clutch spring acts on the clutch plates with a pressure distribution ring disposed therebetween.
  6. 6. A clutch unit substantially as herein before described with reference to the accompanying drawing (s).
GB0003656A 1999-03-06 2000-02-18 Overload clutch unit Expired - Fee Related GB2347719B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE29904108U DE29904108U1 (en) 1999-03-06 1999-03-06 Coupling unit, in particular for drives of extraction and conveying facilities

Publications (3)

Publication Number Publication Date
GB0003656D0 GB0003656D0 (en) 2000-04-05
GB2347719A true GB2347719A (en) 2000-09-13
GB2347719B GB2347719B (en) 2002-11-06

Family

ID=8070451

Family Applications (1)

Application Number Title Priority Date Filing Date
GB0003656A Expired - Fee Related GB2347719B (en) 1999-03-06 2000-02-18 Overload clutch unit

Country Status (2)

Country Link
DE (1) DE29904108U1 (en)
GB (1) GB2347719B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2862113A1 (en) * 2003-11-06 2005-05-13 Walterscheid Gmbh Gkn COUPLING OF THE CLUTCH TYPE, IN PARTICULAR FOR THE TRAINING OF AGRICULTURAL TOOLS
CN103291774A (en) * 2013-04-10 2013-09-11 中煤张家口煤矿机械有限责任公司 Torque-adjustable overload protection device

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITPD20090125A1 (en) * 2009-05-08 2010-11-09 Alit S R L MOTION TRANSMISSION DEVICE FOR CONVEYOR BELTS
CN108194534A (en) * 2018-03-06 2018-06-22 上海布拓传动系统设备有限公司 800kw limits torque guard
DE102019131090B3 (en) * 2019-11-18 2020-10-22 Halbach & Braun Maschinenfabrik Gmbh + Co. Clutch unit and drive system with such a clutch unit
DE102021119719A1 (en) 2021-06-16 2022-12-22 Schaeffler Technologies AG & Co. KG Torque limiter with an axis of rotation for a drive train

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5090539A (en) * 1987-03-11 1992-02-25 Zahnradfabrik Friedrichshafen Ag Pressure-medium actuated friction disk clutch or brake
GB2302922A (en) * 1995-06-29 1997-02-05 Gkn Driveline Limited Transmission torque-limiting device
GB2323140A (en) * 1996-05-17 1998-09-16 Gkn Viscodrive Gmbh A viscous fluid operated friction coupling with means to change shear channel cross-section
US5884739A (en) * 1996-08-23 1999-03-23 Gkn Viscodrive Gmbh Coupling assembly with reservoir for highly viscous fluid

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3690429A (en) 1971-07-15 1972-09-12 Honda Motor Co Ltd Clutch with dual pistons and springs
DE2705196C3 (en) 1977-02-08 1980-08-14 Centralnyj Nautschno-Issledovatelskij Avtomobilnyj I Avtomotornyj Institut (Nami), Moskau Friction clutch for a gearbox of a gas turbine engine
DE3444103C2 (en) 1984-12-04 1994-08-11 Steyr Daimler Puch Ag Hydraulic clutch
JPH0542653Y2 (en) 1987-11-05 1993-10-27
DE4041159C2 (en) 1990-12-21 1994-01-27 Daimler Benz Ag Fluid-operated friction clutch with only axially movable friction discs
DE4119874A1 (en) 1991-06-17 1993-01-07 Deere & Co MULTI-DISC CLUTCH
DE4237075C1 (en) 1992-11-03 1994-06-23 Deere & Co Fluid-operated friction disc clutch
DE19754491A1 (en) 1997-12-09 1999-06-17 Stromag Ag Vehicle multiple disk brake with piston unit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5090539A (en) * 1987-03-11 1992-02-25 Zahnradfabrik Friedrichshafen Ag Pressure-medium actuated friction disk clutch or brake
GB2302922A (en) * 1995-06-29 1997-02-05 Gkn Driveline Limited Transmission torque-limiting device
GB2323140A (en) * 1996-05-17 1998-09-16 Gkn Viscodrive Gmbh A viscous fluid operated friction coupling with means to change shear channel cross-section
US5884739A (en) * 1996-08-23 1999-03-23 Gkn Viscodrive Gmbh Coupling assembly with reservoir for highly viscous fluid

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2862113A1 (en) * 2003-11-06 2005-05-13 Walterscheid Gmbh Gkn COUPLING OF THE CLUTCH TYPE, IN PARTICULAR FOR THE TRAINING OF AGRICULTURAL TOOLS
US7168545B2 (en) 2003-11-06 2007-01-30 Gkn Walterscheid Gmbh Coupling
CN103291774A (en) * 2013-04-10 2013-09-11 中煤张家口煤矿机械有限责任公司 Torque-adjustable overload protection device
CN103291774B (en) * 2013-04-10 2016-01-06 中煤张家口煤矿机械有限责任公司 A kind of Torque-adjustable overload protection device

Also Published As

Publication number Publication date
GB2347719B (en) 2002-11-06
DE29904108U1 (en) 1999-07-08
GB0003656D0 (en) 2000-04-05

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Legal Events

Date Code Title Description
732E Amendments to the register in respect of changes of name or changes affecting rights (sect. 32/1977)
PCNP Patent ceased through non-payment of renewal fee

Effective date: 20170218