WO1985005660A1 - Lamellar clutch - Google Patents
Lamellar clutch Download PDFInfo
- Publication number
- WO1985005660A1 WO1985005660A1 PCT/EP1985/000218 EP8500218W WO8505660A1 WO 1985005660 A1 WO1985005660 A1 WO 1985005660A1 EP 8500218 W EP8500218 W EP 8500218W WO 8505660 A1 WO8505660 A1 WO 8505660A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- cylinder
- carrier
- coupling according
- linear motor
- 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
- 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
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- 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
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
- F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
Definitions
- the invention relates to a clutch according to the preamble of the main claim.
- a piston of a linear motor additionally serves directly as an inner disk carrier and is connected in a rotationally fixed and axially movable manner to an output shaft as one of two connecting members for torque transmission via a driving profile, and part of the cylinder of the linear motor serves additionally directly as an outer disk carrier and is firmly connected to the second connecting member in the form of a planet carrier.
- the output shaft completes the cylinder.
- the first sealing ring is arranged between the piston and the output shaft. It only has to endure axial displacements corresponding to the actuation path of the linear motor. Movements in the circumferential direction are completely avoided by the driving profile.
- the second sealing ring is arranged between the two parts of the cylinder, the outer disk carrier and the output shaft. He has to endure both circumferential speeds corresponding to the diameter of the output shaft and the speed difference between the two disk carriers, as well as slight axial displacements in accordance with his own axial compliance with pressure changes.
- the third sealing ring is arranged between the two
- Lamellar carriers on a large sealing diameter near the fins It has to endure both large peripheral speeds and large axial displacements in accordance with the actuation path of the linear motor.
- the invention has for its object to improve a coupling according to the preamble of the main claim so that one of the three sealing rings is omitted and the other two sealing rings only have to endure axial displacements.
- the cylinder as an inner disk carrier and to design the piston as an intermediate member for torque transmission between the inner disk carrier and the drive shaft.
- the two elements of the linear motor Arranged radially between the lamellae and the drive shaft, the two elements of the linear motor additionally take over the transmission of the entire torque, in accordance with their natural radial order.
- An existing installation space is used twice. Further advantages are achieved with the characteristic features of the subclaims which are known per se.
- the drawing shows a section of a longitudinal section through a multi-plate clutch according to the invention in the open state.
- a piston 2 of a linear motor 3 is rotatably fixed via a driving profile 4 and axially fixed between a shaft collar 5 and a locking ring 6.
- a cylinder 7 is arranged in a rotationally fixed manner via a driving profile 8 and is axially movable to a limited extent by an annular end face 9 of the piston 2 and a locking ring 10.
- a plate spring 11 between the locking ring 10 and the piston 2 presses the cylinder 7 axially against the end face 9.
- a radially outer sealing ring 12 is arranged in a circumferential groove 13 in an outer surface 14 of the piston 2 and slides axially in a hollow cylinder surface 15 of the cylinder 7.
- a radially inner diameter ring 16 is arranged in a circumferential groove 17 in an inner surface 18 of the cylinder 7 and slides axially on a cylinder surface 19 of the piston 2.
- the cylinder 7 carries in an outer driving profile 20 non-rotatable and axially movable inner plates 21 and one End plate 22.
- the end plate 22 is axially supported by a collar 23 of the cylinder 7.
- the cylinder 7 is thus also an inner plate carrier 7.
- An outer plate carrier 24 carries in an inner driving profile 25 non-rotatably and axially movable outer plates 26.
- a retaining ring 27 in a circumference ⁇ groove 28 in the driving profile 25 supports an end plate 29 and thus all the slats 21, 22, 2nd 6 axially against the outer disk carrier 24.
- the outer disk carrier 24 is at the same time additionally a planet carrier 24 with planet bolts 30 and, on roller bearings 31, planet gears 32 of a planetary gear 33, which is only partially shown.
- the drive shaft 1 is also a central gear 1 of the planetary gear 33.
- the drive shaft 1 and the planet carrier 24 are the two connecting members 1, 24 for torque transmission.
- Pressure fluid in a chamber 34 between the piston 2 and the cylinder 7, supplied via bores 35, 36 in the drive shaft 1 and in the piston 2, pushes the cylinder 7 and thus also the end plate 22 axially against the other plates 21, 26 and the end plate 29, and thus closes the multi-plate clutch.
- the restoring force of the plate spring 11 must be overcome.
- the actuating force of the multi-plate clutch is supported by an axial needle bearing 37 between the piston 2 and the outer plate carrier 24.
- the plate spring 11 pushes the cylinder 7 back again and thus opens the multi-plate clutch again.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The lamellar clutch is actuated by a fluid-operated linear motor (3). The piston (2) of the linear motor (3) is solidly attached to a drive shaft (1). The cylinder (7) of the linear motor (3) is linked with the piston (2) so that it can move axially but resists torsion, and additionally serves as an internal lamella carrier (7) in the lamellar clutch. The linear motor (3) is arranged radially inside the lamellae (21, 22, 26) and axially inside the outer lamella carrier (24).
Description
Lamellenkupplung Multi-plate clutch
Die Erfindung betrifft eine Kupplung nach dem Oberbegriff des Hauptanspruchs.The invention relates to a clutch according to the preamble of the main claim.
Es ist eine Kupplung dieser Art bekannt (DE-OS 27 32 121) .A clutch of this type is known (DE-OS 27 32 121).
Bei einer Kupplung nach der DE-OS 27 32 121 dient ein Kolben eines Linearmotors zusätzlich unmittelbar als Innenlamellenträger und ist über ein Mitnahmeprofil drehfest und axial beweglich mit einer Abtriebswelle als einem von zwei Anschlußgliedern zur Dreh¬ momentübertragung verbunden, dient ein Teil des Zylinders des Linearmotors zusätzlich unmittelbar als Außenlamellenträger und ist fest mit dem zweiten Anschlußglied in Form eines Planeten¬ trägers verbunden. Der Zylinder wird vervollständigt durch die Abtriebswelle. Zur Abdichtung zwischen dem Kolben und den beiden Teilen des Zylinders sind insgesamt drei Dichtringe erforderlich, die gegen Fliehkraftdruck und zeitweise gegen Betätigungsdruck des Fluids abdichten müssen:In a clutch according to DE-OS 27 32 121, a piston of a linear motor additionally serves directly as an inner disk carrier and is connected in a rotationally fixed and axially movable manner to an output shaft as one of two connecting members for torque transmission via a driving profile, and part of the cylinder of the linear motor serves additionally directly as an outer disk carrier and is firmly connected to the second connecting member in the form of a planet carrier. The output shaft completes the cylinder. To seal between the piston and the two parts of the cylinder, a total of three sealing rings are required, which must seal against centrifugal pressure and at times against the operating pressure of the fluid:
Der erste Dichtring ist angeordnet zwischen dem Kolben und der Abtriebswelle. Er muß nur axiale Verschiebungen ent¬ sprechend dem Betätigungsweg des Linearmotors ertragen. Bewegungen in Umfangsrichtung werden durch das Mitnahme¬ profil vollständig vermieden.The first sealing ring is arranged between the piston and the output shaft. It only has to endure axial displacements corresponding to the actuation path of the linear motor. Movements in the circumferential direction are completely avoided by the driving profile.
Der zweite Dichtring ist angeordnet zwischen den beiden Teilen des Zylinders, dem Außenlamellenträger und der Ab¬ triebswelle. Er muß sowohl Umfangsgeschwindigkeiten ent¬ sprechend dem Durchmesser der Abtriebswelle und der Dreh¬ zahldifferenz zwischen den beiden Lamellenträgern als auch geringe axiale Verschiebungen entsprechend seiner eigenen axialen Nachgiebigkeit bei Druckänderungen ertragen.
- Der dritte Dichtring ist angeordnet zwischen den beidenThe second sealing ring is arranged between the two parts of the cylinder, the outer disk carrier and the output shaft. He has to endure both circumferential speeds corresponding to the diameter of the output shaft and the speed difference between the two disk carriers, as well as slight axial displacements in accordance with his own axial compliance with pressure changes. - The third sealing ring is arranged between the two
Lamellenträgern auf einem großen Dichtdurchmesser nahe den Lamellen. Er muß sowohl große Umfangsgeschwindigkeiten als auch große axiale Verschiebungen entsprechend dem Betäti¬ gungsweg des Linearmotors ertragen.Lamellar carriers on a large sealing diameter near the fins. It has to endure both large peripheral speeds and large axial displacements in accordance with the actuation path of the linear motor.
Während der erste Dichtring keine Probleme erwarten läßt, muß man beim zweiten Dichtring schon mit einer verkürzten Lebens¬ dauer rechnen, weil er als Radialwellendichtring zeitweise, bei Betätigung der Kupplung, durch erhebliche Fluiddrücke zusätzlich belastet wird. Der dritte Dichtring ist den höchsten Belastungen ausgesetzt. Bereits ohne Betätigung der Kupplung läuft er als Radialwellendichtring gegen erhebliche, fliehkraftbedingte Fluid¬ drücke. Durch die gleichen Fliehkräfte bedingt, sammeln sich vor seiner Dichtkante alle abrasiven Partikel, die Dichtkante gräbt sich eine Verschleiß- oder Laufrille in ihre zylindrische Gegen¬ fläche. Bei Betätigung der Kupplung muß der Dichtring aus dieser Laufrille herausgehoben und entsprechend dem Betätigungsweg axial verschoben werden. Dadurch ist für "diesen Dichtring keine be¬ friedigende Lebensdauer zu erwarten.While no problems can be expected from the first sealing ring, a shortened service life must already be expected for the second sealing ring, because it, as a radial shaft sealing ring, is sometimes additionally loaded by considerable fluid pressures when the clutch is actuated. The third sealing ring is exposed to the highest loads. Even without actuating the clutch, it runs as a radial shaft sealing ring against considerable centrifugal fluid pressures. Due to the same centrifugal forces, all abrasive particles collect in front of its sealing edge, the sealing edge digs a wear or running groove in its cylindrical counter surface. When the clutch is actuated, the sealing ring must be lifted out of this groove and moved axially according to the actuation path. As a result, a satisfactory service life is not to be expected for this sealing ring.
Der Erfindung liegt die Aufgabe zugrunde, eine Kupplung nach dem Oberbegriff des Hauptanspruchs so zu verbessern, daß einer der drei Dichtringe entfällt und die beiden anderen Dicht¬ ringe nur axiale Verschiebungen ertragen müssen.The invention has for its object to improve a coupling according to the preamble of the main claim so that one of the three sealing rings is omitted and the other two sealing rings only have to endure axial displacements.
Diese Aufgabe wird mit den kennzeichnenden Merkmalen des Hauptanspruchs erfüllt.This task is accomplished with the characterizing features of the main claim.
Vorteilhaft ist die Ausbildung des Zylinders als Innenla¬ mellenträger und die Ausbildung des Kolbens als Zwischenglied zur Drehmomentübertragung zwischen dem Innenlamellenträger und der Antriebswelle. Radial zwischen den Lamellen und der Antriebs¬ welle angeordnet, übernehmen die beiden Elemente des Linearmotors, entsprechend ihrer natürlichen radialen Reihenfolge, zusätzlich die Übertragung des gesamten Drehmoments. Ein vorhandener Bauraum wird doppelt genutzt.
Weitere Vorteile werden mit den an sich bekannten kenn¬ zeichnenden Merkmalen der Unteransprüche erreicht.It is advantageous to design the cylinder as an inner disk carrier and to design the piston as an intermediate member for torque transmission between the inner disk carrier and the drive shaft. Arranged radially between the lamellae and the drive shaft, the two elements of the linear motor additionally take over the transmission of the entire torque, in accordance with their natural radial order. An existing installation space is used twice. Further advantages are achieved with the characteristic features of the subclaims which are known per se.
Die Zeichnung zeigt einen Ausschnitt aus einem Längsschnitt durch eine Lamellenkupplung nach der Erfindung im geöffneten Zustand.The drawing shows a section of a longitudinal section through a multi-plate clutch according to the invention in the open state.
Auf einer Antriebswelle 1 ist ein Kolben 2 eines Linear¬ motors 3 über ein Mitnahmeprofil 4 drehfest und zwischen einem Wellenbund 5 und einem Sicherungsring 6 axial fest angeordnet. Auf dem Kolben 2 ist ein Zylinder 7 über ein Mitnahmeprofil 8 drehfest und durch eine ringförmige Stirnfläche 9 des Kolbens 2 und einen Sicherungsring 10 begrenzt axial beweglich angeordnet. Eine Tellerfeder 11 zwischen dem Sicherungsring 10 und dem Kol¬ ben 2 drückt den Zylinder 7 axial gegen die Stirnfläche 9. Ein radial äußerer Dichtring 12 ist in einer Umfangsnut 13 in einer Außenfläche 14 des Kolbens 2 angeordnet und gleitet axial in einer Hohlzylinderflache 15 des Zylinders 7. Ein radial innerer Diσhtring 16 ist in einer Umfangsnut 17 in einer Innenfläche 18 des Zylinders 7 angeordnet und gleitet axial auf einer Zylin¬ derfläche 19 des Kolbens 2. Der Zylinder 7 trägt in einem äußeren Mitnahmeprofil 20 drehfest und axial beweglich Innenlamellen 21 und eine Endlamelle 22. Die Endlamelle 22 wird axial abgestützt durch einen Bund 23 des Zylinders 7. Der Zylinder 7 ist damit zusätzlich Innenlamellenträger 7. Ein Außenlamellenträger 24 trägt in einem inneren Mitnahmeprofil 25 drehfest und axial be¬ weglich Außenlamellen 26. Ein Sicherungsring 27 in einer Umfangs¬ nut 28 im Mitnahmeprofil 25 stützt eine Endscheibe 29 und damit alle Lamellen 21, 22, 26 axial gegen den Außenlamellenträger 24 ab. Der Außenlamellenträger 24 ist gleichzeitig zusätzlich ein Planetenträger 24 mit Planetenbolzen 30 und darauf, über Wälz¬ lager 31 gelagerten Planetenrädern 32 eines nur teilweise dar¬ gestellten Planetengetriebes 33. Die Antriebswelle 1 ist gleich¬ zeitig zusätzlich ein Zentralrad 1 des Planetengetriebes 33. Die Antriebswelle 1 und der Planetenträger 24 sind die beiden Anschlußglieder 1, 24 zur Drehmomentübertragung.
Druckfluid in einer Kammer 34 zwischen dem Kolben 2 und dem Zylinder 7, zugeführt über Bohrungen 35, 36 in der Antriebs¬ welle 1 und im Kolben 2, schiebt den Zylinder 7 und damit auch die Endlamelle 22 axial gegen die anderen Lamellen 21, 26 und die Endscheibe 29, und schließt damit die Lamellenkupplung. Da¬ bei muß die Rückstellkraft der Tellerfeder 11 überwunden werden. Die Betätigungskraft der Lamellenkupplung wird durch ein Axial¬ nadellager 37 zwischen dem Kolben 2 und dem Außenlamellenträ¬ ger 24 abgestützt.On a drive shaft 1, a piston 2 of a linear motor 3 is rotatably fixed via a driving profile 4 and axially fixed between a shaft collar 5 and a locking ring 6. On the piston 2, a cylinder 7 is arranged in a rotationally fixed manner via a driving profile 8 and is axially movable to a limited extent by an annular end face 9 of the piston 2 and a locking ring 10. A plate spring 11 between the locking ring 10 and the piston 2 presses the cylinder 7 axially against the end face 9. A radially outer sealing ring 12 is arranged in a circumferential groove 13 in an outer surface 14 of the piston 2 and slides axially in a hollow cylinder surface 15 of the cylinder 7. A radially inner diameter ring 16 is arranged in a circumferential groove 17 in an inner surface 18 of the cylinder 7 and slides axially on a cylinder surface 19 of the piston 2. The cylinder 7 carries in an outer driving profile 20 non-rotatable and axially movable inner plates 21 and one End plate 22. The end plate 22 is axially supported by a collar 23 of the cylinder 7. The cylinder 7 is thus also an inner plate carrier 7. An outer plate carrier 24 carries in an inner driving profile 25 non-rotatably and axially movable outer plates 26. A retaining ring 27 in a circumference ¬ groove 28 in the driving profile 25 supports an end plate 29 and thus all the slats 21, 22, 2nd 6 axially against the outer disk carrier 24. The outer disk carrier 24 is at the same time additionally a planet carrier 24 with planet bolts 30 and, on roller bearings 31, planet gears 32 of a planetary gear 33, which is only partially shown. The drive shaft 1 is also a central gear 1 of the planetary gear 33. The drive shaft 1 and the planet carrier 24 are the two connecting members 1, 24 for torque transmission. Pressure fluid in a chamber 34 between the piston 2 and the cylinder 7, supplied via bores 35, 36 in the drive shaft 1 and in the piston 2, pushes the cylinder 7 and thus also the end plate 22 axially against the other plates 21, 26 and the end plate 29, and thus closes the multi-plate clutch. The restoring force of the plate spring 11 must be overcome. The actuating force of the multi-plate clutch is supported by an axial needle bearing 37 between the piston 2 and the outer plate carrier 24.
Läßt man das Druckfluid aus der Kammer 31 wieder ent¬ weichen, schiebt die Tellerfeder 11 den Zylinder 7 wieder zurück und öffnet damit die Lamellenkupplung wieder.
If the pressure fluid is allowed to escape from the chamber 31 again, the plate spring 11 pushes the cylinder 7 back again and thus opens the multi-plate clutch again.
Bezugszeichenreference numeral
1 Antriebswelle, Zentralrad, 32 Planetenrad1 drive shaft, central gear, 32 planet gear
Anschlußglied 33 ' PlanetengetriebeConnector 33 'planetary gear
2 Kolben, Element, Zwischenglied 34 Kammer2 pistons, element, intermediate member 34 chamber
3 Linearmotor 35 Bohrung3 linear motor 35 bore
4 Mitnahmeprofil 36 Bohrung4 Driving profile 36 hole
5 Wellenbund 37 Axialnadellager5 shaft collar 37 axial needle bearing
6 Sicherungsring6 circlip
7 Innenlamellenträger, Zylinder, Element7 inner disk carrier, cylinder, element
8 Mitnahmeprofi18 Take along professionals1
9 Stirnfläche9 end face
10 Sicherungsring 1 Tellerfeder 2 Dichtring 3 Umfangsnut 4 Außenfläche 5 Hohlzylinderflache, Innenfläche 6 Dichtring 7 Umfangsnut 8 Innenfläche 9 Zylinderfläche, Außenfläche 0 Mitnahmeprofil 1 Innenlamelle 2 Endlamelle 3 Bund 4 Außenlamellenträger, Planetenträger Anschlußglied 5 Mitnahmeprofil 6 Außenlamelle 7 Sicherungsring 8 Umfangsnut 9 Endscheibe 0 Planetenbolzen 1 Wälzlager
10 Circlip 1 Belleville washer 2 Sealing ring 3 Circumferential groove 4 Outer surface 5 Hollow cylinder surface, inner surface 6 Sealing ring 7 Circumferential groove 8 Inner surface 9 Cylinder surface, outer surface 0 Driving profile 1 Inner lamella 2 end lamella 3 collar 4 Outer lamella carrier, planet carrier connecting element 5 Driving profile 6 Outer lamella 7 Circlip 8 Circumferential groove 9 End plate 0 Planetary pin 1 roller bearing
Claims
1. Fluidisch betätigte Lamellenkupplung mit einem Außenla¬ mellenträger mit mindestens einer Außenlamelle und einem ersten Anschlußglied zur Drehmomentübertragung, mit einem Innenlamellen¬ träger mit mindestens einer Innenlamelle und einem zweiten An¬ schlußglied zur Drehmomentübertragung, mit einem fluidisch be¬ tätigten Linearmotor mit zwei zueinander gegen Federkraft axial beweglichen Elementen in Form eines Kolbens und eines Zylinders, mit Dichtringen, die jeweils in einer Umfangsnut eines der beiden Elemente gehalten sind und auf einer zylindrischen Oberfläche des anderen Elements gleitend die beiden Elemente gegeneinander ab¬ dichten, wobei eines der beiden Elemente zusätzlich unmittelbar als Innenlamellenträger dient, dadurch g e k e n n z e i c h ¬ e t , daß1. Fluidically actuated multi-plate clutch with an outer plate carrier with at least one outer plate and a first connecting element for torque transmission, with an inner plate carrier with at least one inner plate and a second connecting element for torque transmission, with a fluidically actuated linear motor with two against each other Spring force of axially movable elements in the form of a piston and a cylinder, with sealing rings, each of which is held in a circumferential groove of one of the two elements and slidably seals the two elements against one another on a cylindrical surface of the other element, one of the two elements additionally directly serves as an inner disk carrier, characterized ¬ et that
- der Zylinder (7) zusätzlich unmittelbar als Innenlamellen¬ träger {7) dient,- The cylinder (7) also serves directly as an inner disk carrier {7),
- der Zylinder (7) über ein Mitnahmeprofil (8) drehfest und axial beweglich mit dem Kolben (2) verbunden ist,- The cylinder (7) is connected to the piston (2) in a rotationally fixed and axially movable manner via a driving profile (8),
- der Kolben (2) drehfest mit einem der beiden Anschlußglie¬ der (1) verbunden ist,- The piston (2) is non-rotatably connected to one of the two connecting members (1),
- der Kolben (2) als Zwischenglied (2) das gesamte Drehmoment zwischen diesem Anschlußglied (1) und dem als Innenlamellen¬ träger (7) dienenden Zylinder (7) überträgt,- The piston (2) as an intermediate member (2) transmits the entire torque between this connecting member (1) and the cylinder (7) serving as an inner plate carrier (7),
- - der Linearmotor (3) radial innerhalb der Lamellen (21,- - The linear motor (3) radially inside the fins (21,
22, 26) angeordnet ist.22, 26) is arranged.
2. Kupplung nach Anspruch 1, dadurch g e k e n ¬ z e i c h n e t , daß der Linearmotor (3) axial innerhalb des Außenlamellenträgers (24) angeordnet ist. 2. Coupling according to claim 1, characterized in that the linear motor (3) is arranged axially within the outer disk carrier (24).
3. Kupplung nach Anspruch 1 oder 2, dadurch g e k e n ¬ z e i c h n e t , daß die Umfangsnuten (17, 28) für die Dicht¬ ringe (12, 16) jeweils entweder in einer Außenfläche (14, 19) des Kolbens (2) oder in einer Innenfläche (18, '15) des Zylinders (7) angeordnet sind.3. Coupling according to claim 1 or 2, characterized in that the circumferential grooves (17, 28) for the sealing rings (12, 16) each either in an outer surface (14, 19) of the piston (2) or in one Inner surface (18, '15) of the cylinder (7) are arranged.
4. Kupplung nach Anspruch 1, 2 oder 3, dadurch g e ¬ k e n n z e i c h n e t , daß die Kupplung entweder durch Fluiddruck geschlossen und durch Federkraft geöffnet oder durch Fluiddruck geöffnet und durch Federkraft geschlossen wird.4. Coupling according to claim 1, 2 or 3, characterized in that the coupling is either closed by fluid pressure and opened by spring force or opened by fluid pressure and closed by spring force.
5. Kupplung nach Anspruch 4, dadurch g e k e n n ¬ z e i c h n e t , daß eine vorgespannte Tellerfeder (11) die Federkraft erzeugt.5. Coupling according to claim 4, characterized in that a preloaded plate spring (11) generates the spring force.
6. Kupplung nach einem der vorangehenden Ansprüche, dadurch g e k e n n z e i c h n e t , daß die Anschlußglieder (1, 24) ein Zentralrad (1) und ein Planetenträger (24) eines Planetenge¬ triebes sind.6. Coupling according to one of the preceding claims, characterized in that the connecting members (1, 24) are a central wheel (1) and a planet carrier (24) of a planetary gear.
7. Kupplung nach einem der vorangehenden Ansprüche, dadurch g e k e n n z e i c h n e t , daß zwischen dem Kolben (2) und dem Planetenträger (24) ein Axiallager (30) angeordnet ist. 7. Coupling according to one of the preceding claims, characterized in that an axial bearing (30) is arranged between the piston (2) and the planet carrier (24).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP8400161 | 1984-05-26 | ||
| LUPCT/EP84/00161 | 1984-05-26 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO1985005660A1 true WO1985005660A1 (en) | 1985-12-19 |
Family
ID=8164943
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP1985/000218 WO1985005660A1 (en) | 1984-05-26 | 1985-05-11 | Lamellar clutch |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP0222742A1 (en) |
| DE (1) | DE3517144A1 (en) |
| WO (1) | WO1985005660A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5261517A (en) * | 1991-06-17 | 1993-11-16 | Deere & Company | Multi-disk clutch |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006031815B4 (en) * | 2006-07-07 | 2009-01-29 | Ortlinghaus-Werke Gmbh | Pressure oil clutch |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB670399A (en) * | 1949-12-08 | 1952-04-16 | Joseph Massardier | Improvements in disc clutches |
| GB916649A (en) * | 1958-05-29 | 1963-01-23 | Peter Grainger Stanton | Improvements relating to clutches particularly for gear boxes |
| DE1256966B (en) * | 1959-12-24 | 1967-12-21 | Ortlinghaus Geb | Pressurized multi-plate clutch |
| DE2732121A1 (en) * | 1976-07-19 | 1978-01-26 | Trw Inc | COUPLING DEVICE |
| FR2432647A1 (en) * | 1978-08-03 | 1980-02-29 | Zahnradfabrik Friedrichshafen | Press hydraulic spring brake and clutch - has springs forming self-sealing components for chamber from outside |
-
1985
- 1985-05-11 EP EP19850902518 patent/EP0222742A1/en not_active Withdrawn
- 1985-05-11 WO PCT/EP1985/000218 patent/WO1985005660A1/en unknown
- 1985-05-11 DE DE19853517144 patent/DE3517144A1/en not_active Withdrawn
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB670399A (en) * | 1949-12-08 | 1952-04-16 | Joseph Massardier | Improvements in disc clutches |
| GB916649A (en) * | 1958-05-29 | 1963-01-23 | Peter Grainger Stanton | Improvements relating to clutches particularly for gear boxes |
| DE1256966B (en) * | 1959-12-24 | 1967-12-21 | Ortlinghaus Geb | Pressurized multi-plate clutch |
| DE2732121A1 (en) * | 1976-07-19 | 1978-01-26 | Trw Inc | COUPLING DEVICE |
| FR2432647A1 (en) * | 1978-08-03 | 1980-02-29 | Zahnradfabrik Friedrichshafen | Press hydraulic spring brake and clutch - has springs forming self-sealing components for chamber from outside |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5261517A (en) * | 1991-06-17 | 1993-11-16 | Deere & Company | Multi-disk clutch |
Also Published As
| Publication number | Publication date |
|---|---|
| DE3517144A1 (en) | 1985-11-28 |
| EP0222742A1 (en) | 1987-05-27 |
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