CA1140060A - Clutch-brake unit - Google Patents
Clutch-brake unitInfo
- Publication number
- CA1140060A CA1140060A CA000336312A CA336312A CA1140060A CA 1140060 A CA1140060 A CA 1140060A CA 000336312 A CA000336312 A CA 000336312A CA 336312 A CA336312 A CA 336312A CA 1140060 A CA1140060 A CA 1140060A
- Authority
- CA
- Canada
- Prior art keywords
- clutch
- oil
- input shaft
- plates
- brake unit
- 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.)
- Expired
Links
- 238000005086 pumping Methods 0.000 claims abstract description 27
- 230000004044 response Effects 0.000 claims description 4
- 239000012530 fluid Substances 0.000 claims description 3
- 230000009471 action Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 47
- 238000012423 maintenance Methods 0.000 description 3
- 238000001914 filtration Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
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
- F16D65/00—Parts or details
- F16D65/78—Features relating to cooling
- F16D65/84—Features relating to cooling for disc brakes
- F16D65/853—Features relating to cooling for disc brakes with closed cooling system
-
- 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
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
-
- 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
- F16D67/00—Combinations of couplings and brakes; Combinations of clutches and brakes
- F16D67/02—Clutch-brake combinations
- F16D67/04—Clutch-brake combinations fluid actuated
Abstract
CLUTCH-BRAKE UNIT
ABSTRACT OF THE DISCLOSURE
There is disclosed herein a clutch-brake unit having a clutch disc pack and a separate brake disc pack which are designed for selective actuation by a single piston arrangement to transmit rotational driving forces from an input shaft to an output shaft via the clutch disc pack and to brake rotation of the output shaft via the brake disc pack as desired. An integral oil pump is provided on the input shaft and cooperates with portions of the housing to provide a high volume centrifugal pumping action to continuously circulate oil through passages provided in the housing, input shaft, output shaft and across the clutch and brake disc packs so as to cool them. Provisions are also incorporated whereby the oil flow may be directed to external auxiliary apparatus such as an oil cooler if desired.
ABSTRACT OF THE DISCLOSURE
There is disclosed herein a clutch-brake unit having a clutch disc pack and a separate brake disc pack which are designed for selective actuation by a single piston arrangement to transmit rotational driving forces from an input shaft to an output shaft via the clutch disc pack and to brake rotation of the output shaft via the brake disc pack as desired. An integral oil pump is provided on the input shaft and cooperates with portions of the housing to provide a high volume centrifugal pumping action to continuously circulate oil through passages provided in the housing, input shaft, output shaft and across the clutch and brake disc packs so as to cool them. Provisions are also incorporated whereby the oil flow may be directed to external auxiliary apparatus such as an oil cooler if desired.
Description
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Summary of the Invention The present invention relates generally to a combir.ation 15 clutch-braXe unit and more particularly to a new and improved oil submerged clutch-brake unit having integral oil pumping means operative to continuously circulate oil whenevcr the unit is operating.
Clut h-brake units of various types have long been employed to transmit rotational energy between a power source and equipment to be
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Summary of the Invention The present invention relates generally to a combir.ation 15 clutch-braXe unit and more particularly to a new and improved oil submerged clutch-brake unit having integral oil pumping means operative to continuously circulate oil whenevcr the unit is operating.
Clut h-brake units of various types have long been employed to transmit rotational energy between a power source and equipment to be
2~ driven thereby. Such units are generally employed so as to provide means ~or alternately stopping and starting such driven equipment without requiring the shutting down of the power source thereby conserving power as well as enabling other equipment which may be drivcn by a common power source to be operatcd. Thc inclusion of the braking fcaturcs enables more rapid-25 dcceleration of thc output shaft than that providcd by friction alone.
I)urin~ operation and particularly durin~ initial pcriods 'I , . . .
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of clutch actuation and braking such clutch-brake units generate high amounts of heat and wear between -the respective torque transmitting surfaces. Accordingly, it is desirable to provide means to both lubricate and cool these surfaces. ~lowever, for reasons of economy both in maintenance and operation as well as in required investment, it is desirable to avoid the addition of auxiliary pumping equipment to supply this lubrlcant.
Accordingly, the present invention provldes an improved clutch-brake unit having an integral high volume centrifugal oil pumping means provided on the input shaft which is in operation whenever the input shaft is rotating. Oil passage means are also provided for continuously circulating the oil through the unit and dispersing the oil over substantially all of the torque transmitting surfaces thereby preventing any excessive localized wear. Additionally, provisions are also made whereby the oil pumping means may be effective to circulate all or a portion of the oil through external auxiliary apparatus such as an oil coller or filtration equipment for example. Thus, the presen-t invention provides a durable clutch-brake unit requiring substantially less maintenance as well as eliminating the need for auxiliary external pumping apparatus to circulate lubricant.
Further, the reduced maintenance affords indirect cost savings to users of the present invention by insuring the driven equipment will be available for operation a greater percentage of the time.
Generally, the clutch-brake unit of the present invention includes a housing which defines a central cavity between opposed longitudinally spaced end walls. An input shaft extends into the cavity through one of the end walls ws/~
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and an output shaft extends in-to the cavity through -the other of the end walls. A series of radially disposed clutch plates are mounted in the cavity for rotation with the input shaft and first and second series of radially disposed axially spaced friction plates are mounted within the cavity for rotation with the output shaft. A series of radially disposed brake plates are non-rotatably mounted within the cavity and adapted to be actuated to cooperate with the second series of friction plates to brake rotation of the output shaft. The clutch pla-tes and the first series of friction plates are adapted to be actuated so as to cooperate to transmit rotational energy between the input and output shafts. Oil pumping means are mounted on the input shaft and operative to circulate oil over the clutch pla-tes, the first and second series of friction plates and the brake plates to cool same in response to rotation of the input shaft.
Additional advantages and features of the present invention will become apparent from the subsequent description and the appended claims taken in conjunction with the accompanying drawings.
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.. '' . ' , Bricf l~cscription Or 1hc Drn~vin~s Fi~ure 1 is a lon~itudinnl side elevational view of a clutch-brake unit in accordancc with the prescnt invcntion partially . broken away;
.; 5 Figure 2 is a transverse cross-sectional view of the clutch-brake unit of Figure 1 the scction being taken along line 2-2 . thereof;
. Figure 3 is a fragmentary perspective view of an impeller vane provided on the input shaft;
Figure 4 is a fragmentary radial cross-sectiol~al view OI the input shaft the section being taken along line 4-4 of Figure l; and Figure 5 is a developed view of a portion of the output . shaft illustrating the arrangement of the radial oil outlet passages provided therein;
lS Description of the Preferred Embodiment Referring now to the drawings a clutch brake unit in accordance with the present invention is indicated generally at 10 and comprises a generally cylindrically shapcd housing 12 having opposcd longitudinally spaced end walls 1~ and 16 which partially define an interior cavity 18 therebetween. End wall 16 has a large opening 15 provided therein whicll is closed by a removable end wall 17. Housing 12 also has a longitudinally extending opening 20 at the top thereof which is closed by menns oî a cover platc 22 secured to housing 12 in any suitab?e ma~ cr suc?l as by n plurnlity of bolts or the like. Housing 12 may also bc providcd witl) outwardly projccting c~ctcrnal hent rndinting fins 2~ if dcsircd to nssist in dissipating hcnl ~enerated during opcration of thc clulch-brnke unit.
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An input shaft 2G extends into cavity 1~ through an opening 28 provided in end wall 14 and is rotatably journalcd thcrein by means of bearings 27 and 2~. Input shaf~ 26 is providcd with an enlarged diarneter annu]ar supporting scction 30 at its inner end from which a p]urality of drive lugs 32 project axially outward. As illustrated, clutch-brake unit 10 is provided with four drive lugs 32 substantially ~ equally spaced around supporting section 30 although it should be noted .: that a greater or lesser numb~r of such drive lugs may be provided for larger or smaller capacity clutch-brake units. A plurality of 10 friction clutch plate members 34 are mounted on drive lugs 32 and extend radially inward therefrom. Also, a plurality of oil pump impeller vanes 36 are provided on drive lugs 32 extending generally radially outwardly therefrom and substantially coextensive therewith.
An output shaft 38 extends into cavity 18 through an 15 opening 40 provided in removable end wall 17 and is rotatably supported therein by a suitable bearing assembly 42. Output shaft 38 is coaxial with input shaft 26 and has an inner end portion 44 rotatably supported by a bearing ~6 engaging an annular radially inwardly facing shoulder 48 provided on input shaft 26, end portion 44 projecting partially into 20 an axially extending bore 50 provided in input shaft 26. Output shaft 38 has an enlarged diameter portion 52 having a plurality of axially extending circumfercntially spaced slots 54 provided therein and a plurality of relatively shallow, axially extending notches 56 intermediate slots 54.
l~n annular not&h 58 is also provided approximately midway along portion 25 52 in which is fittcd a split snap ring 60 which divides portion 52-into clutch disc portion 62 ant3 bra~c disc portion 64. lS plurality of clutch {)Q6~
discs 66 and br~ke discs 68 arc cach providcd with complemcntary notches which interfit within notchcs 58 and are mounted upon respective portions 62 and 64 so as to be rotatablc with output shaft 38.
A pluralit~ of friction brake platcs 70 are supported upon a plurality of axially projecting brake lugs 72 extending outward from a support member 74 non-rotatably secured to and supported from removable end wall 17. As illustrated in Figure 1, clutch plates 34 are interposed between friction clutch discs 66 and brake plates 70 are interposed between friction brake discs 68.
An annular clutch actuating member 76 is disposed adjacent the outer end of clutch disc portion 62 and operatiyely connected to a brake actuating mernber 78 disposed adjacent the outer end of brake disc portion 64 of output shaft 38. Brake actuating member 78 and clutch actuating member 76 are interconnected by a plurality of screws 79 and rods 81 arranged in alternating relationship and extending through slots 54 in such a manner as to fixedly retain actuating members 76 and 78 in a predetermined spaced relationship. A piston actuating rneans, indicated generally at 83,is operatively connected to and adapted to impart axial rnovement to actuating members 76 and 78 so as to thereby actuate either the clutch or brake portion of clutch brake unit 10. The operation of clutch-brake unit lO and additional structural details thereof are substantially identical to that described in U. S. Patent 3, 969, ~98 entitled Clutch-Brake Unit and assigned to the present assi.~nee.
As best.seen with re:~erence to Figure 2, cavity 18 has ~, .
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a generally cylindrical portion 80 ccntrally disposcd bctwcen end walls 14 and 16 ancl surrounding clutch discs and plates 66 and 34 ancl brakc discs and plates 68 and 70. As shown the diameter of portion 80 is such as to place interior wall portion ~2 in close proximity to impeller vanes 36 and to cooperate therewith to provide a high-volume centrifugal oil pumping action.
As best seen with reference to Fig-lre 3 an impeller vane 36 is preferably intcgrally formed with each drive lug 32 and eomprises a radially outwardly extending protrusion defined in part 10 by circumferentially spaced radially outwardly diverging side walls 8~ and 86 extending axially outward from annular flange portion 88 provided on support section 30. The outer end of impeller vane 36 includes a beveled or radially inwardly inclined surface 90 which serves to facilitate oil flow into the vanes such as from brake plates 15 and discs as well as from reservoir 92 provided in the lower portion ~
of housing 12 thereby assisting the pumping action thereof. The radially outer surface 93 of impeller vane 36 is convex in shape having a radius of curvature equal to the radius of the arc scribed by each vane during rotation of the input shaft.
Vanes 36 in cooperation with cylindrical shaped portion - 80 act to pump oil from reservoir 92 to a pumping chamber 94 provided at the top of housing 12 and being defined in part by a depending projection 96 integrally formec3 on cover plate ~2. Projection 96 has a first concave surface ~8 overlying and radial]y spaced from the path of impeller vanes 25 36 a second concnve surface lûO overlying brake plate membcrs 70 and ;m inclincd surîaco 102 also concave in transverse cross-scctional .:
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shape interconnccting surraccs 9~ and 100 which operate to assist in dirccting vi] flowing radially outward from brakc plate membcrs 70 into pumping chamber 94.
An oil outlet passagc 104 is provided in housing 12 extending from the left cnd (as secn in Figure 1) of pumping charrlber 94 radially inwardly and axially to the left to an annular space 106 adjacent bearing 29 and surrounding input shaft 26. Input shaft 26 is provided with a plurality of radially inwardly extending oil passages 108 in fluid communication with space 106 and cylindrical bore 50 pro~
lO . vided in input shaft 26 into which end portion 44 of output shaft 38 isinterfitted. Preferably input shaft 26 will have three equally spaced radial passages 108. Output shaft 38 is provided with an axially extending passage 110 opening outward from end portion 44 into bore 50 which passage is preferably coaxial with the axis of rotation of output shaft 38.
A plurality of radially outwardly extending oil outlet passages 112 are also provided along output shaft 38, a first series 114 thereof being positioned in radial alignment with clutch plates 3~ and clutch friction discs 66 and a second axial spaced series 116 being positioned in radial alignment with brake plates 70 and brake friction discs 68. Each of these passages 112 open into selected axially extending slots 54 provided on enlarged diameter portion 52 of output shaft 38.
As bcst seen with reference to Figure 5, the first series 114 of radial oil outlet passages 112 comprises three substantially equally circumfcrcntially spaccd groups 118, 120 and 122 each group .25 comprising threc such axially spaccd passagcs 112. .E:ach group 118, 120 and 12" is staggcrcd or shiftc(3 slightly in an axial direction such .4Q~6~ !
that no two passage.s }12 have openings which are eireumferenti~lly aligned. Simi]arly, the second series 116 of radial oil outlet passages 112 also comprises three substantially equally circumferentially spaeed groups 124, 126, and 128 each comprising three passages 112. Again, eaeh group is shifted in an axial direction slightly so that no two passages 112 have openings which are eireumferentially aligned. This staggering of oil outlet passages 112 insures th:-t an adequate supply of oil is directed between and over each of the elutch and brake plates 34 and 7Q and eluteh and brake friction discs 66 and 6~.
~n additional radial outwardly extending oil outlet passage 13Q is also provided at the terminal end 132 oE axial passage 110 which operates to provide lubricating oil to bearing assembly 42 as well as to the area of interface between that piston assembly 83 and output shaft 33.
Referring once again to Figure 1, for large capacity, clutch-brake units additional external cooling may be required or it may be desirable in some units to cireulate the oil through other auxiliary external apparatus such as filtration equipment or the like. ~ccordingly, eover plate 22 is provided with a pair of spaced openings 134 and 136 to which suitable eonduits may be eoqmected via appropriate fittings to eonduct oil to such auxiliary apparatus as an oil cooler 133. As shown, opening 134 opens direetly into pumping ehamber 94 and operates to allow oil flow to oil cooler 13û. Opening 136 communieates with a downward~y or radially inward]y extending passage 139 provided in housing 12 whieh operates to direet the oil to spaee 106. ~'hile passages 104, 139 and openings 134 and 136 may be si~ed so as to direct only a portion of the oil through oil cooler 13~, passagc 104 mny also be provided with Sm en]argcd diameter portion 140 adjncent pumping cllamber 9~ whieh is adapted to receive a plug thereby totally elosing off passage 104 and insuring substantially all oil flow will be directecl through oil cooler 13g.
R~ferring now to the overall operation of the eluteh-brake unit 10 ernbodying the principles of the present invention, it will be seen that the torque transmitting portion of the clutch is characterized by an alternate arrangement of a plurality of eluteh plate members 34 and a plurality of eluteh friction discs 66, with one of the discs 66 being disposed adjacent the face of the eluteh aetuating member 76 and another of the dises 66 being disposed udjaeent the side of the eenter ring 60.
These torque transmitting elements within housing 12 are intended to be rotatable in a bath of oil contained within the housing 12, with the result that a substantially high percent of the kinetic energy produced in starting and stopping heavy loads is transmitted by "shearing" the `
oil between the various frietion plates, thus substantially inereasing not - only the life of these friction plates over those in clùtch and brake units which operate dry, but also increasing the maximvm operating speed of the unit 10 of the present invention. The high volurne eentrifugal oil pump described above operates to insure an adequate supply of oil aeross the elutch plates 34, brake plates 70, elutch frietion discs 66, and bral;e frietion discs 680 When input shaft 26 rotates, pump vanes 36 will operate to begin circulatirlg oil from reservoir 92 to pumping ehamber 94 then througll eitl-er openings 134 and 136 or passage 10~ to space 106 and throll~ll radial passages 10~ in input sh:ift 26. Oil will then flow througl .
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~ ~4Q~6 :' -axia] passage 110 in output shaft 38 to racli~l outlct passagcs 112 and - outwardly over the clutch and brake platcs 34 and 70 and clutch and brakc friction discs 66 and 68 rcspectively. It should be noted that while vanes 36 will generatc sufficient prcssure to insure adequate oil flow, the oil flow across the plates and discs will be assisted by the centrifugal force generated by rotation of the output shaft 38. As input shaft 26 will be continuously rotating whenever the clutch-brake unit is in operation, the provision of impeller vanes thereon insure that an adequate supply of oil is provided to the clutch plates and discs at all times including 10 when output shaft just begins to rotate, the high heat generating period.
Once input shaft 26 has begun to rotate and the impeller vanes provided thereon have begun circulating the oil as described above, piston assembly 83 may be actuated thereby causing simultaneous axial movement of brake actuating member 78 and clutch actuating member 15 76 to the right as seen in Figure 1. This movement will release brake plates 70 and brake friction discs 68 which have heretofore prevented rotation of output shaft 38. Further movement will then cause clutch -plates 34 and clutch friction discs 66 to move together between the sides - of clutch actuating member 76 and ring 60 into torc~ue transmitting 20 relationship. Output shaft 38 will then begin to rotate as the slippage between clutch plates 34 and discs 66 decreases. As input shaft 26 is continuously rotating at full or nearly full speed, a continuous supply of oil is distributed via passages 112 between each of the clutch plates and discs thcrcby scrving to both lubricate and cool them. In order to-25 shut down clutch-brakc unit, thc abovc proccàurc is mercly rcverscd wlth dcactivation of piston as.scmb1y ~3 aIlowing axial movcmcnt of -~0-1 ~L 40 Q6~ !
actuating membcrs 76 and 7û to thc lcft as scen in Ii`igurc 1 thcrcby rclcasing clutch plates and discs 34 and 66 and drawing bralcc platcs 70 and discs 6û togcther to provide a braking torque to output shaft.
Again, as input shaft ~6 continucs to rotatc at full speed, an adcquate supply of oil will be directed across bralce plates 70 and discs 68 to cool and lubricate them during the entire braking operation.
While it will be apparent that the preferred embodiment of the invention disclosed is well calculated to provide the advantages and features above stated, it will be appreciated that the invention is susceptible to modification, variation and change without departing from the proper scope or fair meaning of the subjoined claims.
I)urin~ operation and particularly durin~ initial pcriods 'I , . . .
1, ' . .
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11~0~6~ !
of clutch actuation and braking such clutch-brake units generate high amounts of heat and wear between -the respective torque transmitting surfaces. Accordingly, it is desirable to provide means to both lubricate and cool these surfaces. ~lowever, for reasons of economy both in maintenance and operation as well as in required investment, it is desirable to avoid the addition of auxiliary pumping equipment to supply this lubrlcant.
Accordingly, the present invention provldes an improved clutch-brake unit having an integral high volume centrifugal oil pumping means provided on the input shaft which is in operation whenever the input shaft is rotating. Oil passage means are also provided for continuously circulating the oil through the unit and dispersing the oil over substantially all of the torque transmitting surfaces thereby preventing any excessive localized wear. Additionally, provisions are also made whereby the oil pumping means may be effective to circulate all or a portion of the oil through external auxiliary apparatus such as an oil coller or filtration equipment for example. Thus, the presen-t invention provides a durable clutch-brake unit requiring substantially less maintenance as well as eliminating the need for auxiliary external pumping apparatus to circulate lubricant.
Further, the reduced maintenance affords indirect cost savings to users of the present invention by insuring the driven equipment will be available for operation a greater percentage of the time.
Generally, the clutch-brake unit of the present invention includes a housing which defines a central cavity between opposed longitudinally spaced end walls. An input shaft extends into the cavity through one of the end walls ws/~
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and an output shaft extends in-to the cavity through -the other of the end walls. A series of radially disposed clutch plates are mounted in the cavity for rotation with the input shaft and first and second series of radially disposed axially spaced friction plates are mounted within the cavity for rotation with the output shaft. A series of radially disposed brake plates are non-rotatably mounted within the cavity and adapted to be actuated to cooperate with the second series of friction plates to brake rotation of the output shaft. The clutch pla-tes and the first series of friction plates are adapted to be actuated so as to cooperate to transmit rotational energy between the input and output shafts. Oil pumping means are mounted on the input shaft and operative to circulate oil over the clutch pla-tes, the first and second series of friction plates and the brake plates to cool same in response to rotation of the input shaft.
Additional advantages and features of the present invention will become apparent from the subsequent description and the appended claims taken in conjunction with the accompanying drawings.
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.. '' . ' , Bricf l~cscription Or 1hc Drn~vin~s Fi~ure 1 is a lon~itudinnl side elevational view of a clutch-brake unit in accordancc with the prescnt invcntion partially . broken away;
.; 5 Figure 2 is a transverse cross-sectional view of the clutch-brake unit of Figure 1 the scction being taken along line 2-2 . thereof;
. Figure 3 is a fragmentary perspective view of an impeller vane provided on the input shaft;
Figure 4 is a fragmentary radial cross-sectiol~al view OI the input shaft the section being taken along line 4-4 of Figure l; and Figure 5 is a developed view of a portion of the output . shaft illustrating the arrangement of the radial oil outlet passages provided therein;
lS Description of the Preferred Embodiment Referring now to the drawings a clutch brake unit in accordance with the present invention is indicated generally at 10 and comprises a generally cylindrically shapcd housing 12 having opposcd longitudinally spaced end walls 1~ and 16 which partially define an interior cavity 18 therebetween. End wall 16 has a large opening 15 provided therein whicll is closed by a removable end wall 17. Housing 12 also has a longitudinally extending opening 20 at the top thereof which is closed by menns oî a cover platc 22 secured to housing 12 in any suitab?e ma~ cr suc?l as by n plurnlity of bolts or the like. Housing 12 may also bc providcd witl) outwardly projccting c~ctcrnal hent rndinting fins 2~ if dcsircd to nssist in dissipating hcnl ~enerated during opcration of thc clulch-brnke unit.
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An input shaft 2G extends into cavity 1~ through an opening 28 provided in end wall 14 and is rotatably journalcd thcrein by means of bearings 27 and 2~. Input shaf~ 26 is providcd with an enlarged diarneter annu]ar supporting scction 30 at its inner end from which a p]urality of drive lugs 32 project axially outward. As illustrated, clutch-brake unit 10 is provided with four drive lugs 32 substantially ~ equally spaced around supporting section 30 although it should be noted .: that a greater or lesser numb~r of such drive lugs may be provided for larger or smaller capacity clutch-brake units. A plurality of 10 friction clutch plate members 34 are mounted on drive lugs 32 and extend radially inward therefrom. Also, a plurality of oil pump impeller vanes 36 are provided on drive lugs 32 extending generally radially outwardly therefrom and substantially coextensive therewith.
An output shaft 38 extends into cavity 18 through an 15 opening 40 provided in removable end wall 17 and is rotatably supported therein by a suitable bearing assembly 42. Output shaft 38 is coaxial with input shaft 26 and has an inner end portion 44 rotatably supported by a bearing ~6 engaging an annular radially inwardly facing shoulder 48 provided on input shaft 26, end portion 44 projecting partially into 20 an axially extending bore 50 provided in input shaft 26. Output shaft 38 has an enlarged diameter portion 52 having a plurality of axially extending circumfercntially spaced slots 54 provided therein and a plurality of relatively shallow, axially extending notches 56 intermediate slots 54.
l~n annular not&h 58 is also provided approximately midway along portion 25 52 in which is fittcd a split snap ring 60 which divides portion 52-into clutch disc portion 62 ant3 bra~c disc portion 64. lS plurality of clutch {)Q6~
discs 66 and br~ke discs 68 arc cach providcd with complemcntary notches which interfit within notchcs 58 and are mounted upon respective portions 62 and 64 so as to be rotatablc with output shaft 38.
A pluralit~ of friction brake platcs 70 are supported upon a plurality of axially projecting brake lugs 72 extending outward from a support member 74 non-rotatably secured to and supported from removable end wall 17. As illustrated in Figure 1, clutch plates 34 are interposed between friction clutch discs 66 and brake plates 70 are interposed between friction brake discs 68.
An annular clutch actuating member 76 is disposed adjacent the outer end of clutch disc portion 62 and operatiyely connected to a brake actuating mernber 78 disposed adjacent the outer end of brake disc portion 64 of output shaft 38. Brake actuating member 78 and clutch actuating member 76 are interconnected by a plurality of screws 79 and rods 81 arranged in alternating relationship and extending through slots 54 in such a manner as to fixedly retain actuating members 76 and 78 in a predetermined spaced relationship. A piston actuating rneans, indicated generally at 83,is operatively connected to and adapted to impart axial rnovement to actuating members 76 and 78 so as to thereby actuate either the clutch or brake portion of clutch brake unit 10. The operation of clutch-brake unit lO and additional structural details thereof are substantially identical to that described in U. S. Patent 3, 969, ~98 entitled Clutch-Brake Unit and assigned to the present assi.~nee.
As best.seen with re:~erence to Figure 2, cavity 18 has ~, .
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a generally cylindrical portion 80 ccntrally disposcd bctwcen end walls 14 and 16 ancl surrounding clutch discs and plates 66 and 34 ancl brakc discs and plates 68 and 70. As shown the diameter of portion 80 is such as to place interior wall portion ~2 in close proximity to impeller vanes 36 and to cooperate therewith to provide a high-volume centrifugal oil pumping action.
As best seen with reference to Fig-lre 3 an impeller vane 36 is preferably intcgrally formed with each drive lug 32 and eomprises a radially outwardly extending protrusion defined in part 10 by circumferentially spaced radially outwardly diverging side walls 8~ and 86 extending axially outward from annular flange portion 88 provided on support section 30. The outer end of impeller vane 36 includes a beveled or radially inwardly inclined surface 90 which serves to facilitate oil flow into the vanes such as from brake plates 15 and discs as well as from reservoir 92 provided in the lower portion ~
of housing 12 thereby assisting the pumping action thereof. The radially outer surface 93 of impeller vane 36 is convex in shape having a radius of curvature equal to the radius of the arc scribed by each vane during rotation of the input shaft.
Vanes 36 in cooperation with cylindrical shaped portion - 80 act to pump oil from reservoir 92 to a pumping chamber 94 provided at the top of housing 12 and being defined in part by a depending projection 96 integrally formec3 on cover plate ~2. Projection 96 has a first concave surface ~8 overlying and radial]y spaced from the path of impeller vanes 25 36 a second concnve surface lûO overlying brake plate membcrs 70 and ;m inclincd surîaco 102 also concave in transverse cross-scctional .:
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shape interconnccting surraccs 9~ and 100 which operate to assist in dirccting vi] flowing radially outward from brakc plate membcrs 70 into pumping chamber 94.
An oil outlet passagc 104 is provided in housing 12 extending from the left cnd (as secn in Figure 1) of pumping charrlber 94 radially inwardly and axially to the left to an annular space 106 adjacent bearing 29 and surrounding input shaft 26. Input shaft 26 is provided with a plurality of radially inwardly extending oil passages 108 in fluid communication with space 106 and cylindrical bore 50 pro~
lO . vided in input shaft 26 into which end portion 44 of output shaft 38 isinterfitted. Preferably input shaft 26 will have three equally spaced radial passages 108. Output shaft 38 is provided with an axially extending passage 110 opening outward from end portion 44 into bore 50 which passage is preferably coaxial with the axis of rotation of output shaft 38.
A plurality of radially outwardly extending oil outlet passages 112 are also provided along output shaft 38, a first series 114 thereof being positioned in radial alignment with clutch plates 3~ and clutch friction discs 66 and a second axial spaced series 116 being positioned in radial alignment with brake plates 70 and brake friction discs 68. Each of these passages 112 open into selected axially extending slots 54 provided on enlarged diameter portion 52 of output shaft 38.
As bcst seen with reference to Figure 5, the first series 114 of radial oil outlet passages 112 comprises three substantially equally circumfcrcntially spaccd groups 118, 120 and 122 each group .25 comprising threc such axially spaccd passagcs 112. .E:ach group 118, 120 and 12" is staggcrcd or shiftc(3 slightly in an axial direction such .4Q~6~ !
that no two passage.s }12 have openings which are eireumferenti~lly aligned. Simi]arly, the second series 116 of radial oil outlet passages 112 also comprises three substantially equally circumferentially spaeed groups 124, 126, and 128 each comprising three passages 112. Again, eaeh group is shifted in an axial direction slightly so that no two passages 112 have openings which are eireumferentially aligned. This staggering of oil outlet passages 112 insures th:-t an adequate supply of oil is directed between and over each of the elutch and brake plates 34 and 7Q and eluteh and brake friction discs 66 and 6~.
~n additional radial outwardly extending oil outlet passage 13Q is also provided at the terminal end 132 oE axial passage 110 which operates to provide lubricating oil to bearing assembly 42 as well as to the area of interface between that piston assembly 83 and output shaft 33.
Referring once again to Figure 1, for large capacity, clutch-brake units additional external cooling may be required or it may be desirable in some units to cireulate the oil through other auxiliary external apparatus such as filtration equipment or the like. ~ccordingly, eover plate 22 is provided with a pair of spaced openings 134 and 136 to which suitable eonduits may be eoqmected via appropriate fittings to eonduct oil to such auxiliary apparatus as an oil cooler 133. As shown, opening 134 opens direetly into pumping ehamber 94 and operates to allow oil flow to oil cooler 13û. Opening 136 communieates with a downward~y or radially inward]y extending passage 139 provided in housing 12 whieh operates to direet the oil to spaee 106. ~'hile passages 104, 139 and openings 134 and 136 may be si~ed so as to direct only a portion of the oil through oil cooler 13~, passagc 104 mny also be provided with Sm en]argcd diameter portion 140 adjncent pumping cllamber 9~ whieh is adapted to receive a plug thereby totally elosing off passage 104 and insuring substantially all oil flow will be directecl through oil cooler 13g.
R~ferring now to the overall operation of the eluteh-brake unit 10 ernbodying the principles of the present invention, it will be seen that the torque transmitting portion of the clutch is characterized by an alternate arrangement of a plurality of eluteh plate members 34 and a plurality of eluteh friction discs 66, with one of the discs 66 being disposed adjacent the face of the eluteh aetuating member 76 and another of the dises 66 being disposed udjaeent the side of the eenter ring 60.
These torque transmitting elements within housing 12 are intended to be rotatable in a bath of oil contained within the housing 12, with the result that a substantially high percent of the kinetic energy produced in starting and stopping heavy loads is transmitted by "shearing" the `
oil between the various frietion plates, thus substantially inereasing not - only the life of these friction plates over those in clùtch and brake units which operate dry, but also increasing the maximvm operating speed of the unit 10 of the present invention. The high volurne eentrifugal oil pump described above operates to insure an adequate supply of oil aeross the elutch plates 34, brake plates 70, elutch frietion discs 66, and bral;e frietion discs 680 When input shaft 26 rotates, pump vanes 36 will operate to begin circulatirlg oil from reservoir 92 to pumping ehamber 94 then througll eitl-er openings 134 and 136 or passage 10~ to space 106 and throll~ll radial passages 10~ in input sh:ift 26. Oil will then flow througl .
, ' ' .
~ ~4Q~6 :' -axia] passage 110 in output shaft 38 to racli~l outlct passagcs 112 and - outwardly over the clutch and brake platcs 34 and 70 and clutch and brakc friction discs 66 and 68 rcspectively. It should be noted that while vanes 36 will generatc sufficient prcssure to insure adequate oil flow, the oil flow across the plates and discs will be assisted by the centrifugal force generated by rotation of the output shaft 38. As input shaft 26 will be continuously rotating whenever the clutch-brake unit is in operation, the provision of impeller vanes thereon insure that an adequate supply of oil is provided to the clutch plates and discs at all times including 10 when output shaft just begins to rotate, the high heat generating period.
Once input shaft 26 has begun to rotate and the impeller vanes provided thereon have begun circulating the oil as described above, piston assembly 83 may be actuated thereby causing simultaneous axial movement of brake actuating member 78 and clutch actuating member 15 76 to the right as seen in Figure 1. This movement will release brake plates 70 and brake friction discs 68 which have heretofore prevented rotation of output shaft 38. Further movement will then cause clutch -plates 34 and clutch friction discs 66 to move together between the sides - of clutch actuating member 76 and ring 60 into torc~ue transmitting 20 relationship. Output shaft 38 will then begin to rotate as the slippage between clutch plates 34 and discs 66 decreases. As input shaft 26 is continuously rotating at full or nearly full speed, a continuous supply of oil is distributed via passages 112 between each of the clutch plates and discs thcrcby scrving to both lubricate and cool them. In order to-25 shut down clutch-brakc unit, thc abovc proccàurc is mercly rcverscd wlth dcactivation of piston as.scmb1y ~3 aIlowing axial movcmcnt of -~0-1 ~L 40 Q6~ !
actuating membcrs 76 and 7û to thc lcft as scen in Ii`igurc 1 thcrcby rclcasing clutch plates and discs 34 and 66 and drawing bralcc platcs 70 and discs 6û togcther to provide a braking torque to output shaft.
Again, as input shaft ~6 continucs to rotatc at full speed, an adcquate supply of oil will be directed across bralce plates 70 and discs 68 to cool and lubricate them during the entire braking operation.
While it will be apparent that the preferred embodiment of the invention disclosed is well calculated to provide the advantages and features above stated, it will be appreciated that the invention is susceptible to modification, variation and change without departing from the proper scope or fair meaning of the subjoined claims.
Claims (30)
1. A clutch-brake unit comprising:
a housing defining a central cavity between opposed longitudinally spaced end walls;
an input shaft extending into said cavity through one of said end walls;
an output shaft extending into said cavity through the other of said end walls;
a series of radially disposed clutch plates mounted in said cavity for rotation with said input shaft;
first and second series of radially disposed axially spaced friction plates mounted within said cavity for rotation with said output shaft:
a series of radially disposed brake plates non-rotatably mounted within said cavity and adapted to be actuated to cooperate with said second series of friction plates to brake rotation of said output shaft;
said clutch plates and said first series of friction plates being adapted to be actuated so as to cooperate to transmit rotational energy between said input and said output shafts; and oil pumping means mounted on said input shaft, said oil pumping means being operative to circulate oil over said clutch plates, said first and second series of friction plates and said brake plates to cool same in response to rotation of said input shaft.
a housing defining a central cavity between opposed longitudinally spaced end walls;
an input shaft extending into said cavity through one of said end walls;
an output shaft extending into said cavity through the other of said end walls;
a series of radially disposed clutch plates mounted in said cavity for rotation with said input shaft;
first and second series of radially disposed axially spaced friction plates mounted within said cavity for rotation with said output shaft:
a series of radially disposed brake plates non-rotatably mounted within said cavity and adapted to be actuated to cooperate with said second series of friction plates to brake rotation of said output shaft;
said clutch plates and said first series of friction plates being adapted to be actuated so as to cooperate to transmit rotational energy between said input and said output shafts; and oil pumping means mounted on said input shaft, said oil pumping means being operative to circulate oil over said clutch plates, said first and second series of friction plates and said brake plates to cool same in response to rotation of said input shaft.
2. A clutch-brake unit as set forth in Claim 1 wherein said housing is provided with oil passage means for conducting oil from said pumping means and said input shaft is provided with oil passages in fluid communication with said housing oil passage for directing oil to said clutch plates, said first and second series of friction plates and said brake plates.
3. A clutch-brake unit as set forth in Claim 2 wherein said output shaft has an axially extending passage in fluid communication with said input shaft oil passages and a plurality of radially extending passages communicating between said axial passage and said friction plates.
4. A clutch-brake unit as set forth in Claim 3 wherein said output shaft radial oil passages are arranged in circumferentially spaced groups each group being axially staggered so as to avoid circum-ferential alignment of any two such passages.
5. A clutch-brake unit as set forth in Claim 4 wherein said plurality of radially extending passages are spaced axially and circumferentially.
6. A clutch-brake unit as set forth in Claim 1 wherein said oil pump means comprises a plurality of circumferentially spaced vanes provided on said input shaft adapted to rotate in close proximity to the sidewalls of said housing and to cooperate therewith to centrifugally pump said oil.
7. A clutch-brake unit as set forth in Claim 6 wherein each of said vanes is defined in part by radially outwardly diverging sidewalls.
8. A clutch-brake unit as set forth in Claim 7 wherein said input shaft has a plurality of axially projecting drive lugs provided thereon and said vanes are axially elongated and project radially outwardly from said drive lugs.
9. A clutch-brake unit as set forth in Claim 8 wherein said drive lugs and said vanes project axially outward from an annular flange portion of said input shaft.
10. A clutch-brake unit as set forth in Claim 9 wherein said drive lugs and said vanes are integrally formed with said input shaft.
11. A clutch-brake unit comprising:
a housing defining a central cavity between opposite longitudinally spaced end walls and an oil reservoir in a lower portion thereof;
an input shaft extending into said cavity and rotatably journaled in one of said end walls;
a series of clutch plates mounted on said input shaft within said cavity and rotatable therewith;
a series of brake plates non-rotatably mounted within said cavity and spaced from said clutch plates;
an output shaft coaxial with said input shaft extending into said cavity and rotatably journaled in the other of said end walls;
first and second series of friction plates mounted in axial spaced relationship on said output shaft, said first series of plates adapted to cooperate with said clutch plates when actuated to transmit rotational energy from said input shaft to said output shaft and said second series of plates adapted to cooperate with said brake plates when actuated to brake rotational movement of said output shaft;
actuating means for selectively actuating one of said first and second series of friction plates;
a pumping chamber in said housing;
oil pump means provided on said input shaft and operable to pump oil from said reservoir to said pumping chamber; and oil passage means for conducting oil from said pumping chamber across said first and second series of friction plates, said clutch plates and said brake plates.
a housing defining a central cavity between opposite longitudinally spaced end walls and an oil reservoir in a lower portion thereof;
an input shaft extending into said cavity and rotatably journaled in one of said end walls;
a series of clutch plates mounted on said input shaft within said cavity and rotatable therewith;
a series of brake plates non-rotatably mounted within said cavity and spaced from said clutch plates;
an output shaft coaxial with said input shaft extending into said cavity and rotatably journaled in the other of said end walls;
first and second series of friction plates mounted in axial spaced relationship on said output shaft, said first series of plates adapted to cooperate with said clutch plates when actuated to transmit rotational energy from said input shaft to said output shaft and said second series of plates adapted to cooperate with said brake plates when actuated to brake rotational movement of said output shaft;
actuating means for selectively actuating one of said first and second series of friction plates;
a pumping chamber in said housing;
oil pump means provided on said input shaft and operable to pump oil from said reservoir to said pumping chamber; and oil passage means for conducting oil from said pumping chamber across said first and second series of friction plates, said clutch plates and said brake plates.
12. A clutch-brake unit as set forth in Claim 11 wherein said oil pump means comprises at least one vane provided on said input shaft and rotatable therewith to transfer oil from said reservoir to said pumping chamber.
13. A clutch-brake unit as set forth in Claim 12 wherein said output shaft has a drive lug provided thereon and said vane projects radially from said drive lug.
14. A clutch-brake unit as set forth in Claim 13 wherein said vane projects radially outward from said lug and is defined in part by circumferentially spaced diverging sidewalls.
15. A clutch-brake unit as set forth in Claim 11 wherein said oil pump means comprises a plurality of circumferentially spaced vanes provided on said input shaft adapted to rotate in close proximity to the sidewalls of said housing and to cooperate therewith to centrifugally pump said oil.
16. A clutch-brake unit as set forth in Claim 15 wherein said pumping chamber has an inlet opening through said sidewall.
17. A clutch-brake unit as set forth in Claim 11 wherein said oil passage means comprises an axially extending passage in said output shaft and a plurality of radially extending passages communicating between said axial passage and said friction plates.
18. A clutch-brake unit as set forth in Claim 17 wherein said plurality of radially extending passages are spaced axially and circumferentially.
19. A clutch-brake unit as set forth in Claim 17 wherein said input shaft is provided with oil passages for directing said oil from said housing to said axially extending passage.
20. A clutch-brake unit as set forth in Claim 19 wherein said housing contains a first oil passage for directing said oil from said pumping chamber to said input shaft through said housing and a second passage for directing oil from an external source to said input shaft.
21. A clutch-brake unit as set forth in Claim 20 wherein a selected one of said passages is blocked off.
22. A clutch-brake unit as set forth in Claim 20 wherein said pumping chamber has an opening for supplying oil to said external source.
23. A clutch-brake unit as set forth in Claim 22 wherein said external source is an oil cooler.
24. A clutch-brake unit as set forth in Claim 19 wherein said input shaft oil passages comprises a plurality of circumferentially spaced radially extending passages.
25. A clutch-brake unit as set forth in Claim 18 wherein said output shaft radial oil passages are arranged in circumferentially spaced groups each group being axially staggered so as to avoid circum-ferential alignment of any two such passages.
26. A clutch-brake unit as set forth in Claim 25 wherein said groups are axially aligned with said first and second series of friction plates so as to direct a continuous supply of oil thereacross in response to rotation of said input shaft.
27. A clutch-brake unit as set forth in Claim 11 wherein said oil pump means is a high volume centrifugal pump,
28. A clutch-brake unit as set forth in Claim 27 wherein said central cavity has a generally cylindrically shaped portion of a predetermined diameter, said input shaft having a plurality of circum-ferentially spaced drive lugs provided thereon, and at least one impeller vane projecting radially outward from each of said drive lugs, said impeller vanes scribing a circle within said cylindrical portion during rotation of said input shaft having a diameter only slightly less than said predetermined diameter.
29. A clutch-brake unit as set forth in Claim 28 wherein said input shaft comprises four of said lugs and said clutch plates are mounted on said lugs and project radially inward therefrom.
30. A clutch-brake unit comprising:
a housing defining a central cylindrical cavity between opposite longitudinally spaced end walls and an oil reservoir;
an input shaft extending into said cavity and rotatably journaled in one of said end walls and having an enlarged diameter annular flange portion provided thereon;
a plurality of circumferentially spaced drive lugs projecting axially from said annular flange portion:
a plurality of oil pump impeller vanes projecting axially from said flange portion and radially outward from said drive lugs each of said vanes being defined in part by radially outwardly diverging sidewalls;
a series of clutch plates mounted on said drive lugs and rotatable with said input shaft;
an output shaft coaxial with said input shaft extending into said cavity and rotatably journaled in the other of said end walls, said output shaft having an end portion interfitted within a portion of said input shaft and an axially extending oil passage opening out of said end portion;
a series of brake plates non-rotatably mounted within said cavity;
first and second series of friction plates mounted in axial spaced relationship on said output shaft, said first series of plates adapted to cooperate with said clutch plates when actuated to transmit rotational energy from said input shaft to said output shaft and said second series of plates adapted to cooperate with said brake plates when actuated to brake rotational movement of said output shaft;
actuating means for selectively actuating one of said first and second series of friction plates;
a pumping chamber in said housing opening into said cylindrical cavity;
oil passage means in said housing;
said impeller vanes rotating in close proximity to said cylindrical cavity portion of said housing and being operative to pump oil from said reservoir through said pumping chamber, said oil passage means, said axial passage, said radial passages and across said clutch plates, said brake plates and said first and second series of friction plates in response to rotation of said input shaft.
a housing defining a central cylindrical cavity between opposite longitudinally spaced end walls and an oil reservoir;
an input shaft extending into said cavity and rotatably journaled in one of said end walls and having an enlarged diameter annular flange portion provided thereon;
a plurality of circumferentially spaced drive lugs projecting axially from said annular flange portion:
a plurality of oil pump impeller vanes projecting axially from said flange portion and radially outward from said drive lugs each of said vanes being defined in part by radially outwardly diverging sidewalls;
a series of clutch plates mounted on said drive lugs and rotatable with said input shaft;
an output shaft coaxial with said input shaft extending into said cavity and rotatably journaled in the other of said end walls, said output shaft having an end portion interfitted within a portion of said input shaft and an axially extending oil passage opening out of said end portion;
a series of brake plates non-rotatably mounted within said cavity;
first and second series of friction plates mounted in axial spaced relationship on said output shaft, said first series of plates adapted to cooperate with said clutch plates when actuated to transmit rotational energy from said input shaft to said output shaft and said second series of plates adapted to cooperate with said brake plates when actuated to brake rotational movement of said output shaft;
actuating means for selectively actuating one of said first and second series of friction plates;
a pumping chamber in said housing opening into said cylindrical cavity;
oil passage means in said housing;
said impeller vanes rotating in close proximity to said cylindrical cavity portion of said housing and being operative to pump oil from said reservoir through said pumping chamber, said oil passage means, said axial passage, said radial passages and across said clutch plates, said brake plates and said first and second series of friction plates in response to rotation of said input shaft.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US960679A | 1979-02-05 | 1979-02-05 | |
| US9,606 | 1979-02-05 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1140060A true CA1140060A (en) | 1983-01-25 |
Family
ID=21738680
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000336312A Expired CA1140060A (en) | 1979-02-05 | 1979-09-25 | Clutch-brake unit |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS55107137A (en) |
| CA (1) | CA1140060A (en) |
| DE (1) | DE2944008C2 (en) |
| FR (1) | FR2448072B1 (en) |
| GB (1) | GB2041480B (en) |
| IT (1) | IT1193833B (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4693350A (en) * | 1979-02-05 | 1987-09-15 | Sommer Co. | Clutch-brake unit |
| US4415067A (en) * | 1981-05-29 | 1983-11-15 | Force Control Industries, Inc. | Liquid cooled brake unit |
| US4633986A (en) * | 1984-09-07 | 1987-01-06 | Industrial Clutch Corporation | Clutch/brake apparatus |
| JPH038816Y2 (en) * | 1985-01-11 | 1991-03-05 | ||
| JPH0218839Y2 (en) * | 1985-06-27 | 1990-05-25 | ||
| KR0121944B1 (en) * | 1989-04-08 | 1997-11-25 | 라이문트 라우에 및 에델버트 발터어 | Liquid-colled multi-disc brake |
| GB9122112D0 (en) * | 1991-10-18 | 1991-11-27 | Lucas Ind Plc | Self-energising disc brake |
| JPH05193384A (en) * | 1992-01-22 | 1993-08-03 | Tochigi Fuji Ind Co Ltd | Power transmission device |
| DE4447455A1 (en) * | 1994-12-13 | 1996-06-20 | Joachim Kreisl | Device for the oil return of wet-running clutches and brakes |
| DE4444282A1 (en) * | 1994-12-13 | 1996-06-27 | Joachim Kreisl | Fluid operated clutch and brake |
| JPH10103074A (en) * | 1996-10-02 | 1998-04-21 | Tochigi Fuji Ind Co Ltd | Auxiliary machine driving gear |
| US6422364B1 (en) * | 2000-11-10 | 2002-07-23 | Midwest Brake Bond Company | Press drive with oil shear clutch/brake units |
| DE102005017173B4 (en) * | 2005-04-13 | 2011-05-12 | Ortlinghaus-Werke Gmbh | Clutch-brake combination |
| CA2969351C (en) * | 2014-12-27 | 2023-03-14 | Kinetics Drive Solutions Inc. | Improved cooling system for multi-disc brake assembly |
| DE102016124643A1 (en) * | 2016-12-16 | 2018-06-21 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Friction clutch assembly and method for cooling a friction clutch |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2195778A (en) * | 1938-06-21 | 1940-04-02 | Eugene C Hill | Hydraulic clutch or transmission |
| US2788877A (en) * | 1951-04-09 | 1957-04-16 | British Insulated Callenders | Friction clutches |
| FR1518672A (en) * | 1966-10-27 | 1968-03-29 | Borg Warner | Self-contained wet friction clutch device |
| GB1262640A (en) * | 1968-04-18 | 1972-02-02 | Leonard Taylor | Improvements in combined clutches and brakes |
| GB1445105A (en) * | 1972-10-12 | 1976-08-04 | Girling Ltd | Multi-plate disc brakers for vehicles |
| US3924715A (en) * | 1974-04-17 | 1975-12-09 | Force Control Ind | Clutch-brake unit |
| US4135611A (en) * | 1977-01-14 | 1979-01-23 | Gulf & Western Manufacturing Company | Press drive clutch with brake |
-
1979
- 1979-09-25 CA CA000336312A patent/CA1140060A/en not_active Expired
- 1979-10-18 GB GB7936236A patent/GB2041480B/en not_active Expired
- 1979-10-24 IT IT26773/79A patent/IT1193833B/en active
- 1979-10-26 FR FR7926696A patent/FR2448072B1/en not_active Expired
- 1979-10-31 DE DE2944008A patent/DE2944008C2/en not_active Expired
- 1979-11-28 JP JP15415179A patent/JPS55107137A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| IT7926773A0 (en) | 1979-10-24 |
| DE2944008C2 (en) | 1984-09-27 |
| FR2448072B1 (en) | 1985-07-12 |
| JPS55107137A (en) | 1980-08-16 |
| FR2448072A1 (en) | 1980-08-29 |
| GB2041480A (en) | 1980-09-10 |
| IT1193833B (en) | 1988-08-24 |
| DE2944008A1 (en) | 1980-08-07 |
| GB2041480B (en) | 1983-05-11 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |