EP0634568B1 - Reibschaltkupplung insbesondere für ein Lüfterrad eines Kfz-Motor-Ventilators - Google Patents
Reibschaltkupplung insbesondere für ein Lüfterrad eines Kfz-Motor-Ventilators Download PDFInfo
- Publication number
- EP0634568B1 EP0634568B1 EP94110850A EP94110850A EP0634568B1 EP 0634568 B1 EP0634568 B1 EP 0634568B1 EP 94110850 A EP94110850 A EP 94110850A EP 94110850 A EP94110850 A EP 94110850A EP 0634568 B1 EP0634568 B1 EP 0634568B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- clutch
- friction disc
- housing
- fan wheel
- piston
- 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 - Lifetime
Links
- 238000002485 combustion reaction Methods 0.000 claims description 10
- 230000005540 biological transmission Effects 0.000 claims description 3
- 230000004308 accommodation Effects 0.000 claims 1
- 230000009365 direct transmission Effects 0.000 claims 1
- 230000008878 coupling Effects 0.000 description 13
- 238000010168 coupling process Methods 0.000 description 13
- 238000005859 coupling reaction Methods 0.000 description 13
- 238000001816 cooling Methods 0.000 description 6
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 239000010949 copper Substances 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000003292 diminished effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/02—Controlling of coolant flow the coolant being cooling-air
- F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/02—Controlling of coolant flow the coolant being cooling-air
- F01P7/08—Controlling of coolant flow the coolant being cooling-air by cutting in or out of pumps
- F01P7/081—Controlling of coolant flow the coolant being cooling-air by cutting in or out of pumps using clutches, e.g. electro-magnetic or induction clutches
Definitions
- the invention relates in particular to a friction clutch for a fan wheel of a motor vehicle internal combustion engine or the like according to the preamble of claim 1.
- DE 32 03 143 C2 is a friction disc clutch for the Fan wheel of a fan in particular Motor vehicle internal combustion engines became known at which the fan wheel with the friction disc clutch switched off by an eddy current coupling Coupling device is towed.
- Task and aim of the known It is the friction disc clutch, the fan wheel the motor vehicle engine even when switched off Friction disc clutch via an eddy current clutch with a certain minimum towing speed to move for example the cooling of those located in the engine compartment to ensure electronic components.
- the fan wheel can cover increased cooling requirements of the fan in the known device via a Electromagnetically actuated friction disc clutch on the immediate speed of the drive shaft, d. H. on the Engine speed are driven. Such a state is however only when the engine is subjected to the highest loads required. Otherwise, when switched off electromagnetic friction disc clutch a diminished Fan speed can be set, which is characterized by the maximum drag speed of the eddy current clutch determined. For example, this towing speed is the known one Arrangement in the order of approx. 1100 rpm. she will by the number of permanent magnets and by the Distance between rotor and permanent magnet regulated. The known device can therefore two fan speeds generate by the towing speed of the Eddy current clutch and the engine speed itself determined are.
- a corresponding device with two electromagnetic actuatable clutch units is from DE 34 43 523 A1 known.
- Friction disc clutches for the fan drive are therefore in various configurations have become known. Work with it such friction disc clutches purely frictional, so that in Contrary to form-fitting couplings the power to Indent must act as long as the clutch is transmitting power should. As an engagement force and thus as a clutch force consequently mainly used magnetic traction. This can be disadvantageous in special applications, because additional current management measures with appropriate Storage of the stator for the electromagnetic clutch required are.
- the friction disc clutch according to the invention for the drive A fan wheel unfolds its full advantages with large ones Bus engines or truck engines that are turbocharged Motors are trained.
- the charge air of a turbocharger must are usually cooled on the radiator of the motor vehicle, to bring them to an optimal working temperature.
- Such vehicles work with a so-called Retarder brake that brakes the vehicle via a Oil circuit, a so-called Vöttinger clutch accomplish. This is the one that occurs when braking Energy is used to move an oil stream, which is Oil in turn can heat up considerably.
- This oil also has to go through that Fan system can be cooled in an oil cooler.
- the water cooler of the internal combustion engine must also be cooled be what about the fan drive of the fan he follows.
- the friction clutch according to the invention should therefore in such a system of aggregates will be integrated, whereby the already existing compressed air circuit for Air brakes of the motor vehicle or an oil circuit to the extent that a corresponding one is hereby used
- the friction clutch can be connected.
- a air-operated piston / cylinder device one Friction disc clutch actuated or overrides that an immediate application of the fan wheel with the Engine speed should make.
- open Friction disc clutch should be an additional existing Eddy current coupling in a manner known per se Required lower drag speed of the fan wheel cause. It is generally sufficient that the Eddy current coupling directly with the drive shaft of the Friction clutch is connected so that the fan wheel driven at least with the associated towing speed becomes. Of course there can be another one too Intermediate clutch to be turned on, the Eddy current clutch only used when needed.
- the actuation of the friction disc clutch via a pneumatic or hydraulically acting piston / cylinder arrangement alternatively take place in such a way that either with appropriate Pressurization opened the friction disc clutch or closed is.
- the former causes one Safety device, since no pressure is applied the friction disc clutch is closed and thus that Fan wheel at motor speed, d. H. at maximum speed is driven. Accordingly, the pneumatics or hydraulics fall off, the fan wheel works at maximum speed.
- the pneumatic or hydraulic Piston / cylinder drive for the friction disc clutch such are switched that this only with one Pressurization of the piston / cylinder device activated is, so that only in this case a full speed drive of the fan wheel.
- the friction clutch 1 shown in FIG. 1 is used for Drive of a fan wheel 2 and thus as a cooling unit especially for a motor vehicle internal combustion engine.
- the shown friction clutch is a so-called Two-stage clutch trained, as in the DE 32 03 143 C2 of the applicant is described. On the The content of this publication is hereby expressly referred to taken.
- one first friction disc clutch 5 is provided, the pneumatic or is hydraulically actuated. Is this first Friction disc clutch switched on, so there is a non-positive connection between the drive shaft 4 and the fan wheel 2 to be driven in a ratio of 1: 1.
- this first friction disc clutch 5 is switched off, the fan wheel 2 is nevertheless driven via the eddy current clutch 6, which is still present, at a reduced towing speed, the towing speed depending on the distance s 1 between the impeller 7 and the permanent magnets 8.
- this distance is selected between 0.5 and 4 mm, with towing speeds being set, for example, in the order of magnitude up to approximately 1100 rpm.
- the number of permanent magnets also determines the size of the towing speed.
- the drive shaft 4 the friction clutch 1 via a cup-shaped housing 9 driven, a key 10 a positive Connection to the drive shaft 4 and a connecting flange 11 Connection to the crankshaft of a not shown Automotive internal combustion engine forms.
- a cross section Z-shaped housing 13 screwed, which for receiving the Rotor 7 of the eddy current clutch 6 is used.
- the friction disc clutch 5 is annular from the Eddy current clutch 6 enclosed.
- the eddy current clutch 6 consists of a face wheel with its rotor Copper disc 14 and a downstream steel disc 15, which by means of a screw connection 16 on the annular Rotor 7 are attached.
- a magnetic disk wheel 17 Opposed to the rotor wheel 7 of the eddy current clutch 6 with a gap s 1 is a magnetic disk wheel 17, in which the permanent magnets 8 are embedded on the circumference of the annular disk.
- the number of magnets is determined by the respective application and determines the size of the towing speed.
- the magnetic disk wheel 17 has a cross section again Z-shaped or cup-shaped clutch housing 18 connected, which is to accommodate the first Friction disc clutch 5 is used.
- the pot-shaped Coupling housing 18 is radial Mounting flange 19 via a screw 20 with the Magnetic disk wheel 17 connected.
- Another Screw connection 21 connects this radial Mounting flange 19 of the cup-shaped clutch housing 18th with a mounting housing 22 flanged on the end face for the fan wheel 2 via a screw connection 23.
- This Fan wheel mounting housing 22 is approximately in cross section L-shaped with a radial wall section 24 and an axial, pot-shaped wall section 25 which extends towards the front.
- the Fan wheel mounting housing 22 also has one 1 axially extending in the direction Internal combustion engine housing section 26, the performs several functions.
- the mounting housing 22 is via the axial housing section 26 on the drive shaft 4 via a double ball bearing 27 rotatably mounted.
- the radial wall section 24 with the axial Housing section 26 has an annular recess 28 with a cylinder chamber 29 for receiving a pneumatic piston 30 connected is.
- the annular pneumatic piston 30 of the The friction disc clutch 5 is in the cup-shaped housing 18 its cylindrical outer surface 31 mounted.
- the inner one Bearing surface 32 of the annular piston 30 is supported the axial housing surface of the housing section 26.
- the radially outer leg 33 approximately has twice the length as the radially inner Leg 34.
- the piston 30 is at its radial End face 35 is pressurized with compressed air Fastening housing 22 via a compressed air supply bore 36 is fed.
- a compressed air supply bore 36 is fed.
- the axial and cup-shaped Wall section 25 of the mounting housing 22 with a Rotary coupling 37 for the air supply to the interior 38 of the Wall section 25 provided.
- the friction disc clutch 5 can be actuated pneumatically Coupling trained.
- an axially displaceable armature plate 39 which by means of an annular spring washer 40 without torsional play Housing 18 is attached.
- the ring spring washer 40 instructs on its surface several mounting holes that alternately for fastening the adjacent components to serve.
- the screw connection 57 serves this purpose
- Spring assembly 41 presses the radially outer area of the Armature disk 39 against the radial end face 42 of the axially extending outer leg 33 of the pressure piston 30.
- armature disk 39 Opposing the armature disk 39 is a counter disk 43 arranged, which is connected via a screw 44 to the Fastening housing 22 is connected.
- The serves axially extending housing section 26 of the Fastening housing 22 as a spacer and as a housing section for receiving the pressure piston 30.
- the friction clutch according to FIG. 1 works as follows:
- the eddy current clutch 6 is effective the engine speed of the motor vehicle engine via the connecting flange 11 on the pot-shaped housing 9 and from there on the Z-shaped Housing 13 transmits.
- the flanged to the housing 13 Eddy current clutch 6 causes a reduced Speed transmission to the radial mounting flange 19 of the clutch housing 18 and from there to Fastening housing 22 to which the fan wheel 2 is fastened is.
- the fan blade is accordingly of the fan 3 with a reduced towing speed driven.
- the pressure piston 30 is on relieves its end face 35 with pressure medium, so that this exerts no pressure on the armature plate 39.
- the spring assembly 41 presses the armature disk 39 against the friction disc lining 45 and this against the Counter washer 43, so that a positive connection between the drive shaft 4 rotating at engine speed and the clutch pack, consisting of armature plate 39 with Ring spring washer 40, friction washer lining 45 and counter washer 43 consists.
- This torque is via the fixed connection of the Armature plate 39 to the clutch housing 18 and Fastening housing 22 on the one hand or by the Counter washer 43 via the screw connection 44 for Fastening housing 22 on the other hand on the fan wheel 2 and thus transferred to the fan 3.
- the selected arrangement according to Fig. 1 has the advantage that at failing compressed air supply in the system the higher Fan speed by forcing the Friction disc clutch 5 is formed. In case of doubt, therefore the higher cooling effect of the fan in this Circuit arrangement effective.
- the motor vehicle engine is driven via a pulley 48 on the drive shaft 4 of the friction clutch 1.
- the drive shaft 4 is positively connected to a receiving housing 13 for the eddy current clutch 6.
- This receiving housing has an axial wall section 49, a funnel-shaped wall section 50 and a radially extending wall section 51.
- the radial wall section 51 carries on its left end face the magnetic disk wheel 17 for receiving the permanent magnets 8 of the eddy current clutch 6.
- the rotor 7 of the eddy current clutch formed from the copper disk 14 and the steel disk 15, is opposite with a gap s 1 .
- the rotor 7 of the eddy current clutch 6 is in the Fan wheel mounting housing 22 embedded on the front and firmly connected to it. Via a screw connection 23 the impeller 2 attached to the mounting housing 22.
- the Impeller mounting housing 22 is on the drive shaft 4 via the ball bearing 27 freely rotatable, the Ball bearing 27 on the axial wall portion 49 of the Housing 13 is arranged.
- the clutch housing 18 for receiving the piston 30 of the Friction disc clutch 5 has an annular circumferential Cylinder chamber 52 in which the annular piston 30 is axially displaceable.
- the one behind the piston 30 lying cylinder space 29 serves to pressurize the end face piston surface 35 with a pneumatic or hydraulic pressure medium, which has a radial extending supply bore 36 supplied to the cylinder chamber 29 becomes.
- a rotary coupling 37 in turn serves to feed the Pressure medium to the cylinder chamber 29.
- the clutch housing 18 is with its radially outer axial wall section 53 via the screw connection 21 with the fan wheel mounting housing 22 rotatably connected.
- the friction disk clutch 5 is formed by the armature disk 39, which in turn is fastened to the clutch housing 18 in an axially displaceable manner via a spring disk 54 and a screw connection 55, 57.
- the armature disk 39 and the piston 30 form an axially displaceable structural unit which is held by the ring spring washer 54.
- the armature disk 39 interacts with the rear surface 56 of the radial wall section 51 of the housing 13, which lies opposite the armature disk 39 with a gap s 2 .
- the rear end face 56 and the armature disk 39 are designed as friction disk linings.
- the pressure chamber 29 of the cylinder chamber 52 is not included Pressure medium loaded, so the friction disc clutch 5 is not active.
- the pulley 48 opens the drive shaft 4 transmitted engine speed via the Key 10 on the housing 13 and thus on the Transfer eddy current clutch 6.
- the eddy current clutch 6 transfers a reduced speed to the Fan wheel mounting housing 22 and thus on that Fan wheel 2.
- the size of the towing speed is determined by the Structure of the eddy current clutch 6 determined.
- the embodiment according to FIG. 2 accordingly includes one Compressed air circuit, the one when the compressed air acts direct coupling of the motor speed to the fan wheel causes.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Operated Clutches (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Description
- Fig. 1
- ein erstes Ausführungsbeispiel für eine Reibschaltkupplung mit Schaltung der Reibscheibenkupplung bei Druckentlastung der Kolben/Zylindereinheit und
- Fig. 2
- eine alternative Ausführungsform mit der Schaltung der Reibscheibenkupplung bei druckbelasteter Kolben/Zylindereinheit.
Claims (10)
- Reibschaltkupplung für ein Lüfterrad eines Kraftfahrzeug-Verbrennungsmotors oder dergleichen, wobei das Lüfterrad (2) zur unmittelbaren Übertragung der Motordrehzahl über eine erste Reibscheibenkupplung (5) direkt mit einer Antriebswelle (4) oder dergleichen verbunden ist und das Lüfterrad (2) bei abgeschalteter Reibscheibenkupplung (5) durch eine zweite, als Wirbelstromkupplung ausgebildete Kupplungsvorrichtung (6) mitgeschleppt wird, dadurch gekennzeichnet, daß die Reibscheibenkupplung (5) zum direkten Antrieb des Lüfterrades (2) als pneumatisch oder hydraulisch betätigbare Kupplung (5) mit einer Kolben/Zylindereinheit ausgebildet ist, die über eine Drehkupplung (37) mit Druckmedium beaufschlagbar ist und daß der Antriebskolben (30) eine mittels einer flexiblen Ringfederscheibe (40, 54) axial verschiebbare Ankerscheibe (39) betätigt, die mit einem Reibscheibenbelag (45) der Reibscheibenkupplung (5) zusammenwirkt.
- Kupplung nach Anspruch 1, dadurch gekennzeichnet, daß die Antriebswelle (4) der Reibschaltkupplung (1) über ein Antriebsgehäuse (13) direkt mit der Wirbelstromkupplung (6) verbunden ist, wobei die Wirbelstromkupplung (6) abtriebseitig mit einem Lüfterrad-Befestigungsgehäuse (22) zur Befestigung des Lüfterrades (2) verbunden und das Lüfterrad-Befestigungsgehäuse (22) über ein Kugellager (27) von der Antriebswelle (4) drehzahlmäßig entkoppelt ist.
- Kupplung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß ein Lüfterrad-Befestigungsgehäuse (22) mit einem Reibscheibenkupplungs-Aufnahmegehäuse (18) direkt verbunden ist, welches einen Zylinderraum (29, 52) zur Aufnahme eines Antriebskolbens (30) der Kolben/Zylindereinheit aufweist und daß der axial verschiebbare Antriebskolben (30) die Reibscheibenkupplung (5) im Sinne einer Druckbeaufschlagung oder Druckentlastung der Reibscheibenkupplung (5) und damit zu einer direkten Verbindung oder Entkopplung der Antriebswelle (4) mit dem Lüfterrad (2) betätigt.
- Kupplung nach einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Antriebswelle (4) mit einer axial verschiebbaren flexiblen Kupplungsscheibe (46) verbunden ist, die beidseitig einen Reibscheibenbelag (45) trägt und daß die Kupplungsscheibe (46) bei nicht druckbeauschlagtem Antriebskolben (30) zwischen der mit einem Kupplungsgehäuse (18) verbundenen Ankerscheibe (39) und einer mit dem Lüfterrad-Befestigungsgehäuse (22) festverbundenen Gegenscheibe (43) kraftschlüssig eingeklemmt ist.
- Kupplung nach einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Ankerscheibe (39) von einer Tellerfeder (41) axial gegen den Reibscheibenbelag (45) der Reibscheibenkupplung (5) andrückbar ist.
- Kupplung nach einem oder mehreren der vorhergehenden Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Antriebskolben (30) bei einer Druckbeaufschlagung die Reibscheibenkupplung (5) im Sinne einer Kupplungsbetätigung und damit einer unmittelbaren Drehzahlübertragung schließt.
- Kupplung nach einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das mit der Antriebswelle (4) verbundene Gehäuse (13) zur antriebsseitigen Befestigung der Wirbelstromkuppplung (6) mit seinem radialen Wandungsabschnitt (51) gleichzeitig als Gegenscheibe (43) der Reibscheibenkupplung (5) dient, die mit der Ankerscheibe (39) bei einer Kraftbeaufschlagung des Antriebskolbens (30) zusammenwirkt.
- Kupplung nach Anspruch 7, dadurch gekennzeichnet, daß die Ankerscheibe (39) über eine flexible Ringfederscheibe (40, 54) axial verschiebbar im Kupplungsgehäuse (18) gelagert ist.
- Kupplung nach einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Ankerscheibe (39) und der Kolben (30) eine bauliche, axial verschiebbare Einheit bilden, die zwischen sich die flexible Ringfederscheibe (54) einschließen.
- Kupplung nach einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Druckbeaufschlagung des Antriebskolbens (30) über eine Drehkupplung (37) auf das drehbare Anschlußgehäuse (25, 18) zum Druckraum (29) der Kolben/Zylindereinheit erfolgt.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4323651 | 1993-07-15 | ||
DE4323651A DE4323651A1 (de) | 1993-07-15 | 1993-07-15 | Reibschaltkupplung, insbesondere für ein Lüfterrad eines Kfz-Motor-Ventilators |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0634568A1 EP0634568A1 (de) | 1995-01-18 |
EP0634568B1 true EP0634568B1 (de) | 1998-05-13 |
Family
ID=6492835
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94110850A Expired - Lifetime EP0634568B1 (de) | 1993-07-15 | 1994-07-13 | Reibschaltkupplung insbesondere für ein Lüfterrad eines Kfz-Motor-Ventilators |
Country Status (3)
Country | Link |
---|---|
US (1) | US5586636A (de) |
EP (1) | EP0634568B1 (de) |
DE (2) | DE4323651A1 (de) |
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US6092638A (en) * | 1998-03-05 | 2000-07-25 | Horton, Inc. | Splineless rotational control apparatus |
DE19821098A1 (de) * | 1998-05-12 | 1999-11-18 | Behr Gmbh & Co | Antriebseinrichtung für den Kühllüfter eines Kraftfahrzeugmotors |
IT1303836B1 (it) | 1998-11-19 | 2001-03-01 | Baruffaldi Spa | Dispositivo di trasmissione del moto per ventole di autoveicoli agiunto ad induzione a concatenamento frontale |
US6209700B1 (en) | 1999-09-27 | 2001-04-03 | Tractech Inc. | Electric clutch including resilient disk biasing means |
US6375442B1 (en) * | 2000-02-10 | 2002-04-23 | Eaton Corporation | Supercharger clutch system |
IT1316682B1 (it) * | 2000-02-29 | 2003-04-24 | Baruffaldi Spa | Dispositivo di trasmissione del moto per ventole di autoveicoli acomando coassiale dell'innesto |
WO2001083960A1 (en) | 2000-05-03 | 2001-11-08 | Horton, Inc. | Eddy current fan drive |
US6634476B2 (en) * | 2000-10-20 | 2003-10-21 | Usui Kokusai Sangyo Kaisha, Limited | Magnet type fan clutch apparatus |
DE10158732B4 (de) * | 2001-11-30 | 2008-11-27 | Linnig Trucktec Gmbh | Antriebsorgan für eine Wasserpumpe des Kühlwasserkreislaufes eines Verbrennungsmotors sowie Reibschaltkupplung |
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DE10303183B4 (de) * | 2002-12-23 | 2007-06-14 | Linnig Trucktec Gmbh | Wirbelstromkupplung sowie Lüfterkupplung mit einer Wirbelstromkupplung |
WO2004093306A2 (en) * | 2003-04-10 | 2004-10-28 | Prasanna Srinivasa G N | Motion control using electromagnetic forces |
US6838796B1 (en) * | 2003-08-05 | 2005-01-04 | Horton, Inc. | Two-speed rotational control apparatus with eddy current drive |
DE102005001330A1 (de) * | 2005-01-11 | 2006-08-10 | Linnig Trucktec Gmbh | Reibschaltkupplung für ein anzutreibendes Element, insbesondere Lüfterrad |
DE102005014347B4 (de) * | 2005-03-24 | 2009-06-18 | Linnig Trucktec Gmbh | Reibschaltkupplung |
DE102007056492B3 (de) * | 2007-11-22 | 2009-06-04 | Voith Patent Gmbh | Lüfterrad |
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DE202008005470U1 (de) * | 2008-04-18 | 2008-08-07 | Linnig Antriebstechnik Gmbh | Reibschaltkupplung sowie Antriebssystem für die Kühlung eines Verbrennungsmotors eines Fahrzeugs mit einer Reibschaltkupplung |
WO2010056830A2 (en) | 2008-11-12 | 2010-05-20 | Horton, Inc. | Two-speed clutch and retro-fit kit |
US9046137B2 (en) | 2010-01-22 | 2015-06-02 | Kit Masters Inc. | Fan clutch apparatus and methods |
US8863929B2 (en) * | 2010-12-22 | 2014-10-21 | Kit Masters | Viscous two-speed clutch |
DE202011051969U1 (de) | 2011-06-15 | 2012-09-17 | Kendrion Linnig Gmbh Commercial Vehicle Systems | Wirbelstromkupplung |
CN105221600B (zh) * | 2013-03-27 | 2017-10-13 | 龙口中宇热管理系统科技有限公司 | 低碳经济性电磁风扇离合器 |
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CN103925064B (zh) * | 2014-03-18 | 2016-04-20 | 龙口中宇热管理系统科技有限公司 | 电磁离合传动装置 |
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DE3015545A1 (de) * | 1980-04-23 | 1981-10-29 | Pintsch Bamag Antriebs- Und Verkehrstechnik Gmbh, 4220 Dinslaken | Kupplung |
DE8109726U1 (de) * | 1981-04-01 | 1981-07-30 | Linnig Antriebstechnik GmbH, 7778 Markdorf | "Magnetkupplung" |
US4418807A (en) * | 1981-05-11 | 1983-12-06 | Horton Industries, Inc. | Friction interface unit for a clutch and a brake |
DE3137270C2 (de) * | 1981-09-18 | 1986-12-18 | Horton Industries, Inc., Minneapolis, Minn. | Druckmittelbetätigbare Reibscheibenkupplung |
DE3143434A1 (de) * | 1981-11-02 | 1983-05-11 | Karl-Heinz 7990 Friedrichshafen Linnig | "schaltbare reibungskupplung" |
DE3203143A1 (de) * | 1982-01-30 | 1983-08-04 | Karl-Heinz 7990 Friedrichshafen Linnig | Luefterantrieb |
DE3443523C2 (de) * | 1984-11-29 | 1996-02-29 | Stromag Maschf | Zweistufenkupplung für den Antrieb eines Kühllüfters |
DE3607701A1 (de) * | 1986-03-08 | 1987-09-10 | Fichtel & Sachs Ag | Reibungskupplung mit zusatzschwungmasse auf der getriebeeingangswelle |
US4899861A (en) * | 1987-03-16 | 1990-02-13 | Rockford Powertrain, Inc. | Variable speed drive for engine cooling fans |
DE3739537A1 (de) * | 1987-11-21 | 1989-06-01 | Linnig Karl Heinz | Elektromagnetisch betaetigbare reibscheibenkupplung |
DE3828110A1 (de) * | 1988-08-18 | 1990-02-22 | Fluid Misch Und Dispergiertech | Wirbelstromkupplung |
US5059161A (en) * | 1990-02-02 | 1991-10-22 | Horton Industries, Inc. | Rotational control apparatus |
DE4041568A1 (de) * | 1990-12-22 | 1992-06-25 | Behr Gmbh & Co | Luefterantrieb mit fluessigkeitsreibungskupplung |
DE4207709A1 (de) * | 1992-03-11 | 1993-09-16 | Linnig Karl Heinz | Elektromagnetisch betaetigbare reibscheibenkupplung |
DE4207710C2 (de) * | 1992-03-11 | 2001-05-31 | Linnig Karl Heinz | Elektromagnetisch betätigbare Reibscheibenkupplung |
-
1993
- 1993-07-15 DE DE4323651A patent/DE4323651A1/de not_active Withdrawn
-
1994
- 1994-07-13 EP EP94110850A patent/EP0634568B1/de not_active Expired - Lifetime
- 1994-07-13 DE DE59405940T patent/DE59405940D1/de not_active Expired - Fee Related
- 1994-07-14 US US08/274,688 patent/US5586636A/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP0634568A1 (de) | 1995-01-18 |
DE59405940D1 (de) | 1998-06-18 |
DE4323651A1 (de) | 1995-01-19 |
US5586636A (en) | 1996-12-24 |
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