WO2020002412A1 - Module de commande, blocage de différentiel, boîte de transfert et raccordement d'essieu - Google Patents

Module de commande, blocage de différentiel, boîte de transfert et raccordement d'essieu Download PDF

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Publication number
WO2020002412A1
WO2020002412A1 PCT/EP2019/066971 EP2019066971W WO2020002412A1 WO 2020002412 A1 WO2020002412 A1 WO 2020002412A1 EP 2019066971 W EP2019066971 W EP 2019066971W WO 2020002412 A1 WO2020002412 A1 WO 2020002412A1
Authority
WO
WIPO (PCT)
Prior art keywords
switching module
piston
switching
differential lock
dog clutch
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.)
Ceased
Application number
PCT/EP2019/066971
Other languages
German (de)
English (en)
Inventor
Andreas Pfeffer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of WO2020002412A1 publication Critical patent/WO2020002412A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
    • 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
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/088—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members being distinctly separate from the axis of rotation
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • 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
    • 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
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D2011/008—Clutches in which the members have interengaging parts characterised by the form of the teeth forming the inter-engaging parts; Details of shape or structure of these teeth
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/32—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using fluid pressure actuators

Definitions

  • Switching module Differential lock. Transfer case and axis connection
  • the invention relates to a switching module for a differential lock or for a
  • Differential locks enable a distribution of the drive torque to the driven axles or the driven vehicle wheels by blocking a distributor function of the corresponding differential gears, which can facilitate locomotion especially in rough terrain.
  • Axle connections are also known, which make it possible to either drive a vehicle axle or to drag it along.
  • the vehicle axle is driven, the off-road capability and the traction ability of the vehicle increase, whereas when the vehicle axle is carried along, the fuel consumption is reduced.
  • the engagement or disengagement of the differential locks or the engagement or disengagement of the axle engagement takes place via a shift module suitable for this purpose, which usually has a shift fork, a shift sleeve, a
  • Shift rod and a shift piston and a shift cylinder comprises.
  • EP 0 510 457 B1 describes a positive coupling for a transfer case of a motor vehicle and a method for its actuation.
  • the teeth of the coupling parts have sufficiently large tooth gaps to be inserted even under a relative speed
  • An undercut in the toothing prevents the clutch from opening under load.
  • Axial direction are inclined that the clutch can be opened under load.
  • axial forces that have to be absorbed by a locking device, which takes up space and one
  • the known dog clutch arrangements are disadvantageous in that, depending on the design, either the clutch cannot be inserted under load or the clutch cannot be released under load. In addition, they usually consist of a large number of individual parts, which is comparatively complex to manufacture and assemble.
  • the invention relates to a switching module for a differential lock or for a
  • Axis connection comprising a dog clutch with teeth and a switching piston with a maximum force that can be applied, tooth gaps of the teeth being designed to such an extent that the dog clutch can be closed under load.
  • the switching module according to the invention is characterized in that tooth flanks of the toothing have an inclination angle against an axial axis of the
  • the switching module according to the invention thus allows greater flexibility than known switching modules.
  • the dog clutch preferably consists of a first coupling part and a second coupling part, the first coupling part having a first toothing and the second coupling part having a second toothing.
  • first toothing engages in the second toothing, so that a torque can be transmitted.
  • the dog clutch is open, the teeth do not mesh and it can
  • both the first toothing and the second toothing must be designed to be correspondingly solid and stable, so that even if the first and second toothing, in particular the tooth tips of the first and second toothing, collide with one another, this does not lead to damage.
  • the tooth gaps of the toothing must also be at least slightly wider than the circumference of the individual teeth of the claw coupling in order to enable mutual engagement even under load.
  • Tooth flanks are inclined towards the axial axis in such a way that they run at least slightly pointed from the tooth base to the tooth tip, so that the circumference of a tooth tip is less than the circumference of the associated tooth base.
  • the axial axis denotes any straight line which runs parallel to the axial axis of the dog clutch, that is to say extends exclusively in the axial direction, but not in the radial direction.
  • the maximum actuating force that can be applied is greater than the disengaging force, an unintentional opening or at least an unintentional slipping of the claw clutch can be reliably prevented during operation of the switching module according to the invention even under high load.
  • the maximum actuating force that can be applied is in particular greater than the disengaging force that is at the maximum permissible
  • the maximum actuating force that can be applied is therefore greater than the maximum permissible disengagement force.
  • the release force depends on the one hand on the torque acting on the claw clutch, but also on the inclination angle of the tooth flanks. Also a surface condition of the tooth flanks and one influenced by it
  • the coefficient of friction affects the release force.
  • the toothing has no undercut, since an undercut usually prevents the claw clutch from opening under load, since part of the first toothing of the first coupling part engages in the undercut of the second toothing of the second coupling part and vice versa.
  • the torque acting on the dog clutch under load makes opening the dog clutch significantly more difficult or completely prevents it.
  • the first coupling part is designed as a claw sleeve. This gives the advantage of being an additional and separate
  • Shift sleeve for speed synchronization can be dispensed with.
  • the switching module according to the invention therefore advantageously dispenses with additional components, which keeps the manufacturing costs and the module weight low.
  • the switching piston is designed as an annular piston.
  • Shift sleeve itself is arranged.
  • the shift piston is particularly preferably arranged coaxially on the transmission shaft.
  • a shift rod which is usually arranged parallel to the transmission shaft with the shift sleeve and on which the shift piston is usually arranged together with the shift fork, can advantageously be dispensed with. This again saves installation space, manufacturing costs and module weight.
  • the arrangement of the piston on the transmission shaft which is made possible in this way, in particular the coaxial arrangement on the transmission shaft, also has the further advantage that a shift fork can also be dispensed with entirely. This not only means that both the module weight and the
  • Manufacturing costs of the switching module are further reduced, but also the switching times are optimized and the number of parts of the switching module is reduced.
  • a conventional shift piston can preferably also be used, in which case a shift rod and a shift fork are also required to operate the shift module.
  • the switching piston or ring piston When the switching module is actuated, the switching piston or ring piston is axially displaced on the gear shaft.
  • the dog clutch and the switching piston are preferably made of metal, in particular steel. This ensures a comparatively high level of robustness and thus longevity of the components, even under regular and high ones
  • a coupling sleeve of the dog clutch is rotatably mounted axially in the annular piston.
  • the advantage of this arrangement of the coupling sleeve in the ring piston is that that the ring piston can take the coupling sleeve with it and also move it when pressure is applied, which leads to an axial displacement of the switching piston. Since the coupling sleeve is still rotatably mounted in the ring piston, the coupling sleeve can be rotated against the
  • the claw sleeve is mounted coaxially in the ring piston.
  • the claw sleeve or the shift sleeve is rotatably mounted in the annular piston by means of a roller bearing.
  • the roller bearing is more complex than a plain bearing, but it enables comparatively lower friction values to be achieved and thus better efficiency.
  • Another advantage is that the exact position of the ring piston relative to the claw sleeve or shift sleeve is specified via the roller bearing, so that time-consuming work for setting the tooth tip-tooth tip distance and the tooth tip-tooth base distance can be omitted.
  • a prestress necessary for the rolling bearing is preferably generated by an elastic restoring element which urges the ring piston into the idle state in the depressurized state.
  • the roller bearing is preferably designed as an angular contact ball bearing, as a deep groove ball bearing or as an axial bearing. Alternatively, it is preferably provided that a rolling bearing is provided between the shift fork and the claw sleeve or between the shift fork and the shift sleeve when using a shift fork.
  • the switching module further comprises a switching cylinder, which is designed to pressurize the switching piston.
  • Shift cylinders for pressurizing and thus for actuating shift pistons are widespread and technically mature. For example, across from
  • Servomotors are also a cost-effective solution. be designed to actuate the switching piston using oil or air.
  • the switching cylinder can also be single or double acting.
  • the pressure generated in this way causes a corresponding force.
  • the switching module further comprises an elastic reset element which is designed to connect the switching piston with one of the
  • the restoring element is designed as a helical spring or as a plate spring. Coil springs and disc springs can be obtained inexpensively in almost any form of training.
  • the switching piston is pressurized on one side
  • the switching module is actuated in such a way that a differential lock is disengaged or an axle engagement is disengaged. In the depressurized state, however, is
  • Differential lock or the axle engagement preferably engaged.
  • the actuating force which prevents the claw clutch from opening under load due to the then disengaging force, is generated by the restoring element.
  • the differential lock or the axle engagement are disengaged in the depressurized state. The engagement occurs in this case by pressurizing the switching piston with the
  • Pressurization generated It must be large enough not only to counteract the restoring force that occurs under load, but also to counteract the force generated by the restoring element.
  • the shift piston shares a shift cylinder
  • Release space absorbs the release pressure and the engagement space absorbs the engagement pressure. In this case it is a double-acting one
  • the coil spring or plate spring is particularly preferably prestressed under pressure.
  • the restoring element is preferably supported on the claw sleeve. Since the
  • Claw sleeve is arranged radially within the switching piston, can
  • Restoring element in particular if it is designed as a coil spring or
  • Belleville washer saves weight and material with comparatively little
  • the switching module further comprises a rear piston stop.
  • a front piston stop can advantageously be omitted if the
  • Coupling sleeve is mounted by means of roller bearings. If there is no rolling bearing, a front piston stop is preferably additionally provided.
  • the front piston stop or the rolling bearing limits the displaceability of the switching piston in a first axial direction and the rear piston stop limits the displaceability of the switching piston in a second axial direction.
  • the invention also relates to a differential lock for locking a
  • the invention relates to a transfer case with a differential lock.
  • the transfer case according to the invention is characterized in that the
  • Differential lock is a differential lock according to the invention.
  • the invention also relates to an axis connection
  • Axis activation can be activated and deactivated by means of a switching module.
  • the axis connection according to the invention is characterized in that the
  • Switch module is a switch module according to the invention.
  • Fig. 3 exemplarily and schematically a further toothing
  • FIG. 4 exemplary and schematic of a possible form of training
  • Fig. 5 exemplarily and schematically a toothing of an inventive
  • Fig. 6 shows an example of the course of the disengagement force for different
  • the switching module 1 shows, by way of example and schematically, a known switching module 1 which is used, for example, for a differential lock 2.
  • the switching module 1 takes up a comparatively large amount of installation space due to its known design with a shift rod 3 and a shift fork 4. This is essentially due to the parallel arrangement of the shift rod 3 to a gear shaft 8, on which the dog clutch 5 is arranged.
  • it is also necessary to adjust the distance between the tooth heads of a first toothing of a first coupling part 5 ′′ of the claw coupling 5 and the tooth heads of a second toothing of a second coupling part 5 ′′
  • the closed state can be locked via a ball lock 15.
  • Fig. 2 shows an example and schematically a toothing 6 of a dog clutch 5 or a second coupling part 5 ".
  • the tooth flanks 7, 7 ' are inclined at an angle of inclination a against an axial axis 8 of the dog clutch.
  • the angle of inclination a of the tooth flanks 7, 7 'against the axial axis 8 is in
  • FIG. 4 shows an example and schematically a possible embodiment of a switching module 1 according to the invention, for example for a differential lock 2.
  • the switching piston 11 is designed as an annular piston 11. This results in a space-saving design of the whole
  • the dog clutch 5 comprises a first clutch part 5 ′′ and a second clutch part 5 ′′. Both the first and the second coupling part 5 ′′, 5 ′′ have identical toothing 6 (see FIG. 5), tooth gaps 1 1 of the toothing 6 being designed to such an extent that the claw coupling 5 can be closed under load.
  • the tooth flanks 7, 7 ′ of the toothing 6 furthermore have an inclination angle ⁇ against a toothing 8 of the dog clutch 5 in such a way that the dog clutch 5 engages under load
  • the disengagement force arises from the fact that the tooth flanks 7, 7 'run at least slightly pointed from the tooth base to the tooth tip, that is to say that the circumference of a tooth tip is less than the circumference of the associated tooth base.
  • the greater the angle of inclination a the greater the disengagement force, depending on an effective torque.
  • the annular piston 11 is designed such that its maximum actuating force that can be applied is greater than a maximum possible disengagement force, the maximum possible disengagement force resulting from the maximum load capacity of the switching module 1.
  • the first coupling part 5 ′′ simultaneously represents the coupling sleeve 5 ′′ of the claw coupling 5, so that an additional coupling sleeve can be dispensed with.
  • the coupling sleeve 5 ' is, for example, rotatably mounted in the switching piston 11 by means of a roller bearing 12.
  • the straight line 14 shows the increase in the disengagement force 14 with increasing
  • the straight line 14 ' shows the increase in the disengagement force 14' with increasing torque for a toothing with the inclination angle ⁇ and the straight line 14 '' shows the increase in the disengagement force 14 "with increasing torque for a toothing with the tilt angle g.
  • the release force increases linearly with increasing torque.
  • the disengagement force is also dependent on the angle of inclination a, ß or Y, where the following applies, for example: a ⁇ ß ⁇ g.
  • the release force is proportional to the sine of the tilt angle a, ß, g.
  • the switching piston 11 is designed in such a way that its maximum actuating force 11 ′ that can be applied is greater than a maximum possible disengagement force.
  • the maximum actuating force 1 1 'that can be applied is shown in FIG. 5 as a straight line which is independent of the acting torque.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Operated Clutches (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un module de commande (1) pour un blocage de différentiel (2) ou pour un raccordement d'essieu. Le module comprend un embrayage à crabots (5) pourvu d'une denture (6) et un piston (11) de commande présentant une force de réglage (11') pouvant être appliquée au maximum, des entredents de la denture (6) présentant une largeur telle que l'embrayage à crabots (5) peut être fermé sous l'effet d'une charge. Le module de commande (1) selon l'invention se caractérise par le fait que des flancs (7, 7') de la denture (6) présentent un angle d'inclinaison (α, β, γ) par rapport à un axe axial (8) de l'embrayage à crabots (5), de telle sorte que l'embrayage à crabots (5), sous l'effet d'une charge, subit une force de débrayage (14, 14', 14'') et que la force de réglage (11') pouvant être appliquée au maximum est supérieure à la force de débrayage (14, 14', 14''). L'invention concerne en outre un blocage différentiel correspondant, une boîte de transfert correspondante et un raccordement d'essieu correspondant.
PCT/EP2019/066971 2018-06-29 2019-06-26 Module de commande, blocage de différentiel, boîte de transfert et raccordement d'essieu Ceased WO2020002412A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018210691.6A DE102018210691A1 (de) 2018-06-29 2018-06-29 Schaltmodul, Differentialsperre, Verteilergetriebe und Achszuschaltung
DE102018210691.6 2018-06-29

Publications (1)

Publication Number Publication Date
WO2020002412A1 true WO2020002412A1 (fr) 2020-01-02

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PCT/EP2019/066971 Ceased WO2020002412A1 (fr) 2018-06-29 2019-06-26 Module de commande, blocage de différentiel, boîte de transfert et raccordement d'essieu

Country Status (2)

Country Link
DE (1) DE102018210691A1 (fr)
WO (1) WO2020002412A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20210109627A (ko) * 2019-01-10 2021-09-06 이턴 인텔리전트 파워 리미티드 로크 플레이트를 갖는 클러치 팩

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US12391114B2 (en) 2022-04-01 2025-08-19 Dana Automotive Systems Group, Llc Systems for electrified vehicle
US12011995B2 (en) 2022-05-27 2024-06-18 Dana Automotive Systems Group, Llc Electric drive unit with a disconnect assembly and method for operation of said assembly
DE102022211408A1 (de) * 2022-10-27 2024-05-02 Zf Friedrichshafen Ag Differentialsperre zum Sperren von Ausgleichsbewegungen bei einem Differentialgetriebe
DE102022211405A1 (de) * 2022-10-27 2024-05-02 Zf Friedrichshafen Ag Differentialsperre zum Sperren von Ausgleichsbewegungen bei einem Differentialgetriebe
DE102022211409A1 (de) 2022-10-27 2024-05-02 Zf Friedrichshafen Ag Differentialsperre zum Sperren von Ausgleichsbewegungen bei einem Differentialgetriebe
CN119840414A (zh) * 2023-10-17 2025-04-18 阿文美驰技术有限责任公司 具有离合器套环的车桥组件

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US4549449A (en) * 1983-10-11 1985-10-29 Fairfield Manufacturing Company Gear reducer
DE4021653A1 (de) 1989-07-14 1991-01-24 Zahnradfabrik Friedrichshafen Klauenkupplung mit grossem abweiswinkel und kleiner halte- und loesekraft
EP0510457A1 (fr) 1991-04-22 1992-10-28 Steyr-Daimler-Puch Aktiengesellschaft Accouplement à liaison de forme pour la boîte de transfert et le différentiel d'un véhicule à moteur, boîte de transfert et différentiel pourvus dudit accouplement, et sa méthode d'operation
US5377800A (en) * 1993-05-04 1995-01-03 New Venture Gear, Inc. Hydraulically-actuated shift system for a transfer case
US6918851B2 (en) * 2002-11-06 2005-07-19 Dana Corporation Concentric shift system for engaging an interaxle differential lock
US7211017B2 (en) * 2002-11-06 2007-05-01 Dana Corporation Inter-axle differential lock shift mechanism
DE102009023437A1 (de) * 2009-05-29 2010-12-09 Daimler Ag Getriebevorrichtung

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AT511442B1 (de) * 2011-10-10 2012-12-15 Wilhelm Ing Oberaigner Ausgleichsgetriebe
DE102016212807A1 (de) * 2016-07-13 2018-01-18 Zf Friedrichshafen Ag Schaltmodul, Differentialsperre, Gangschaltung und Achszuschaltung

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US4549449A (en) * 1983-10-11 1985-10-29 Fairfield Manufacturing Company Gear reducer
DE4021653A1 (de) 1989-07-14 1991-01-24 Zahnradfabrik Friedrichshafen Klauenkupplung mit grossem abweiswinkel und kleiner halte- und loesekraft
EP0510457A1 (fr) 1991-04-22 1992-10-28 Steyr-Daimler-Puch Aktiengesellschaft Accouplement à liaison de forme pour la boîte de transfert et le différentiel d'un véhicule à moteur, boîte de transfert et différentiel pourvus dudit accouplement, et sa méthode d'operation
US5377800A (en) * 1993-05-04 1995-01-03 New Venture Gear, Inc. Hydraulically-actuated shift system for a transfer case
US6918851B2 (en) * 2002-11-06 2005-07-19 Dana Corporation Concentric shift system for engaging an interaxle differential lock
US7211017B2 (en) * 2002-11-06 2007-05-01 Dana Corporation Inter-axle differential lock shift mechanism
DE102009023437A1 (de) * 2009-05-29 2010-12-09 Daimler Ag Getriebevorrichtung

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20210109627A (ko) * 2019-01-10 2021-09-06 이턴 인텔리전트 파워 리미티드 로크 플레이트를 갖는 클러치 팩
US20220082135A1 (en) * 2019-01-10 2022-03-17 Eaton Intelligent Power Limited Clutch pack with lock plates
US11655887B2 (en) * 2019-01-10 2023-05-23 Eaton Intelligent Power Limited Clutch pack with lock plates
US11940038B2 (en) 2019-01-10 2024-03-26 Eaton Intelligent Power Limited Clutch pack with lock plates
KR20250004183A (ko) * 2019-01-10 2025-01-07 이턴 인텔리전트 파워 리미티드 로크 플레이트를 갖는 클러치 팩
KR102750613B1 (ko) 2019-01-10 2025-01-09 이턴 인텔리전트 파워 리미티드 로크 플레이트를 갖는 클러치 팩
KR102769435B1 (ko) 2019-01-10 2025-02-19 이턴 인텔리전트 파워 리미티드 로크 플레이트를 갖는 클러치 팩

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