EP3574236A1 - Actionneur de passage de vitesse, blocage de différentiel, boîte de transfert, boîte de vitesses manuelle et raccordement d'essieu - Google Patents

Actionneur de passage de vitesse, blocage de différentiel, boîte de transfert, boîte de vitesses manuelle et raccordement d'essieu

Info

Publication number
EP3574236A1
EP3574236A1 EP18700521.0A EP18700521A EP3574236A1 EP 3574236 A1 EP3574236 A1 EP 3574236A1 EP 18700521 A EP18700521 A EP 18700521A EP 3574236 A1 EP3574236 A1 EP 3574236A1
Authority
EP
European Patent Office
Prior art keywords
switching module
piston
switching
shift
differential lock
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.)
Withdrawn
Application number
EP18700521.0A
Other languages
German (de)
English (en)
Inventor
Andreas Pfeffer
Franz Reitinger
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 EP3574236A1 publication Critical patent/EP3574236A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only 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
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with 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
    • 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

Definitions

  • the invention relates to a Wegaktuatorik for a differential lock, for a
  • Claim 1 and a corresponding differential lock, a corresponding transfer case, a corresponding manual transmission and a corresponding Achsscnies.
  • differential locks enable uniform distribution of the differential
  • Vehicle wheels which can facilitate locomotion especially in rough terrain.
  • axle connections are also known, which make it possible to selectively drive or to tow a vehicle axle.
  • the driven state of the vehicle axle the off-road capability and the traction capability of the vehicle increase, whereas in the entrained state of the vehicle axle, the fuel consumption is reduced.
  • the most varied forms of training of manual transmissions are known, wherein such transmissions usually have a plurality of different gear ratios. Each of these grades defines a specific one
  • Coupling for a transfer case of a motor vehicle and a method for its operation Trained as a dog clutch clutch assembly consists on the one hand of a driving coupling part, which is in communication with the drive train and a Radantriebsstrang, and on the other hand from a
  • the driven coupling part which is connected to a wheel drive train to be activated and is designed as a sliding sleeve to be moved via an engaging member by means of a shift fork.
  • the engagement member comprises a piston with a piston rod and a fluid cylinder. At the front end of the piston rod, the shift fork is attached. The piston is acted upon by fluid on one side while a compression spring is supported on another side. In the rest position, the shift fork is pressed by the compression spring in a first direction and brings the clutch in a disengaged state. The engaged state of the clutch is achieved by the piston rod is moved in a second direction by a corresponding pressurization until the coupling parts
  • the invention relates to a Wegaktuatorik for a differential lock, for a
  • the Heidelbergaktuatorik invention is characterized in that the switching piston is designed as an annular piston.
  • control piston As an annular piston this can advantageously be arranged directly on a gear shaft on which the shift sleeve itself is arranged. Particularly preferably, the control piston is arranged coaxially on the transmission shaft.
  • Shift sleeve are arranged together on the shaft can be advantageously dispensed with a shift rod, which is usually arranged parallel to the transmission shaft with the shift sleeve and on which usually the shift piston is arranged together with the shift fork. This saves installation space, weight and costs.
  • the switching module according to the invention is equally suitable for switching a differential lock as well as for switching a gearbox of a motor vehicle or for actuating an axle connection of a vehicle transmission.
  • the differential lock or the gear stage to be shifted of the gearbox or the Achszuscnies are disengaged in the unpressurized state.
  • the engagement takes place in this case by a
  • the switching piston divides a switching cylinder of
  • Release space receives the release pressure and the engagement chamber receives the engagement pressure. In this case, it is a double-acting
  • the switching piston Upon actuation of the switching module, the switching piston is axially displaced on the transmission shaft.
  • the shift sleeve and the control piston are preferably made of metal, in particular steel. This ensures a comparatively high robustness and thus longevity of the components even under regular and high
  • the shift sleeve is rotatably mounted axially in the control piston. From this arrangement of the shift sleeve in the control piston there is the advantage that the control piston at a pressurization, which leads to an axial displacement of the control piston on the shift rod, take the shift sleeve and can also move. By the shift sleeve is still rotatably mounted in the control piston, so a rotatability of the shift sleeve is ensured against the control piston.
  • the shift sleeve is mounted coaxially in the control piston.
  • the shift sleeve is mounted by means of a sliding bearing in the control piston. This represents a cost-effective and technically reliable way to ensure the rotatability of the shift sleeve against the control piston.
  • the shift sleeve is mounted by means of a roller bearing in the control piston.
  • the roller bearing is more complex compared to the plain bearing, but allows the achievement of comparatively lower friction and thus a better efficiency.
  • Another advantage is that the exact position of the control piston is specified for the shift sleeve on the roller bearing, so that time-consuming work to adjust the tooth head-tooth space distance and the tooth top tooth space distance can be omitted.
  • a necessary for the rolling bearing preload is preferably generated by an elastic return element, which urges the control piston in the non-pressurized state in the idle state.
  • the rolling bearing is designed as angular contact ball bearings, deep groove ball bearings or axial bearings.
  • the switching module further comprises a switching cylinder, which is designed to pressurize the switching piston with a pressure.
  • Cylinder for pressurizing and thus for the operation of control pistons are widely used and technically mature. They represent e.g. across from
  • Servo motors also a cost-effective solution. be designed for actuating the control piston by means of oil or by air.
  • the shift cylinder may also be simple or double acting.
  • the switching module further comprises an elastic return element, which is designed to act on the switching piston with a pressure-counteracting force.
  • the switching piston is at
  • the restoring element is designed as a helical spring or as a plate spring.
  • Coil springs and disc springs are inexpensive in almost any form of training available.
  • the coil spring or diaphragm spring is biased to pressure.
  • the return element is supported on the shift sleeve. Because the
  • Shift sleeve is disposed radially within the control piston
  • the switching module further comprises a front piston stop and a rear piston stop.
  • the front piston stop thereby limits the displaceability of the control piston in a first axial direction and the rear piston stop limits the displaceability of the control piston in a second axial direction.
  • Adjustment of the tooth-head-tooth-space-distance as well as the tooth-head-tooth-space distance can be omitted.
  • Control piston defined to the shift sleeve.
  • the switching piston two different, stepped radial
  • the actuating piston can be introduced into an opening provided for receiving it until it strikes against another component with the larger of its two outer radial peripheries, which indicates that it has reached its setpoint position.
  • a sealing element in particular an O-ring is arranged. Since the switching piston is preferably fluid-actuated, can thus be accomplished in a simple manner sealing against the fluid.
  • the invention also relates to a transfer case with a differential lock for blocking a distributor function of the transfer case, wherein the differential lock is engageable and disengageable by means of a switching module.
  • the transfer case according to the invention is characterized in that the at least one switching module is a switching module according to the invention.
  • the invention further relates to a manual transmission with shiftable gear ratios, wherein the gear ratios are switchable by means of at least one switching module.
  • the transmission according to the invention is characterized in that the at least one switching module is an inventive switching module.
  • the invention also relates to an axle connection, wherein the axle connection can be engaged and disengaged by means of a switching module.
  • the axle connection according to the invention is characterized in that the
  • At least one switching module is an inventive switching module.
  • FIG. 3 shows an example and schematically a possible embodiment of a
  • FIG. 5 shows an example and schematically another possible embodiment of a switching module according to the invention.
  • Fig. 6 by way of example and schematically another possible embodiment of a switching module according to the invention in a differential lock.
  • Fig. 1 shows an example and schematically a known switching module 1, consisting of a shift sleeve 2, a shift fork 3, a control piston 4, a
  • the switching piston 4 is arranged in a shift cylinder, not shown, the means of pneumatic pressure actuation of the control piston 4, that is, an axial displacement of the control piston. 4 on the shift rod 5, allows.
  • the pressurization takes place against a restoring force of the return element 6, which according to the example as
  • Coil spring 6 is formed. Since the shift piston 4 and the shift fork 3 are mechanically firmly connected, the shift fork 3 follows the axial displacement of the shift piston 4. Because also the shift fork 3 axially fixed, but rotatable, is connected to the shift sleeve 2, the shift fork 3 transmits the axial displacement of the control piston 4 the shift sleeve 2. Thus, the shift sleeve 2 can be switched on and disengaged via an actuation of the control piston 4. However, the structure of the known switching module 3 is disadvantageous in that
  • FIG. 2 shows by way of example and schematically a known, as shown in Fig. 1 switching module 1 in a differential lock 7.
  • Fig. 1 switching module 1 in a differential lock 7.
  • claims the switching module 1 due to its known training comparatively much space in the transfer case 7.
  • This is essentially on the Parallel arrangement of the shift fork 5 to a transmission shaft 8, on which the shift sleeve 2 is arranged.
  • it is in the case of the known transfer case 7 shown in FIG. 2
  • Fig. 3 shows an example and schematically a possible embodiment of a switching module 1 according to the invention, which is equally suitable for use in a differential lock, a manual transmission or a Achsveraltung.
  • the switching module 1 comprises a shift sleeve 2, a return element 6 and a control piston 4, wherein the control piston 4 is formed as an annular piston 4.
  • the control piston 4 is formed as an annular piston 4.
  • Transmission shaft 10 are arranged.
  • the use of a shift rod 6 and a shift fork 3 is thus advantageously not necessary, which can save material, manufacturing costs and weight.
  • the shift sleeve 2 is
  • control piston 4 by means of a sliding bearing rotatably mounted in the control piston 4.
  • a slide bearing is relatively inexpensive to produce.
  • the return element 6 is designed as a helical spring 6 and acts on the switching piston 4 permanently with a force which counteracts a force applied to actuate the switching piston 4 pressure.
  • the control piston 4 has two different, stepped radial outer peripheries 4 ', 4 ", which enable a simple arrangement or assembly of the control piston 4 in a differential lock, a gearshift or an axle connection each outer circumference 4 ', 4 "one each as an O-ring 11th
  • FIG. 4 shows, by way of example and schematically, the switching module 1 described in FIG. 3 in a differential lock 7.
  • the switching module 1 is arranged in a space-saving manner on the transmission shaft 10.
  • a front piston stop 12 and a rear piston stop 13 are provided, which shift the operating piston 4 or Mechanically limit the sliding sleeve 2.
  • Fig. 5 shows by way of example and schematically another possible embodiment of a switching module 1 according to the invention, which differs from the switching module 1 of Fig. 3 only in that instead of a sliding bearing has a roller bearing 14, which is designed as a deep groove ball bearing 14, for example.
  • the return element 6 biases the deep groove ball bearing 14 in both the engaged and in the disengaged state of the switching module 1.
  • FIG. 6 shows by way of example and schematically the switching module 1 described in FIG. 5 in a differential lock 7. Since the switching module 1 in this case has a roller bearing 14 instead of having a sliding bearing, the front piston stop 12 provided in FIG. 4 and the rear piston stop 13 can advantageously be dispensed with. Instead, the necessary calibration by the rolling bearing 14 results.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un module (1) de passage de vitesse pour un blocage de différentiel (7), pour une boîte de vitesses manuelle ou pour un raccordement d'essieu. Le module comprend un manchon (2) de passage de vitesse et un piston (4) de passage de vitesse. Le module (20) de passage de vitesse selon l'invention se caractérise en ce que le piston (4) de passage de vitesse est réalisé sous la forme d'un piston annulaire (4). L'invention concerne en outre un blocage différentiel correspondant, une boîte de transfert correspondante, une boîte de vitesses manuelle correspondante et un raccordement d'essieu correspondant.
EP18700521.0A 2017-01-30 2018-01-02 Actionneur de passage de vitesse, blocage de différentiel, boîte de transfert, boîte de vitesses manuelle et raccordement d'essieu Withdrawn EP3574236A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017201411.3A DE102017201411B4 (de) 2017-01-30 2017-01-30 Schaltmodul für eine Differentialsperre, für ein Schaltgetriebe oder für eine Achszuschaltung
PCT/EP2018/050022 WO2018137896A1 (fr) 2017-01-30 2018-01-02 Actionneur de passage de vitesse, blocage de différentiel, boîte de transfert, boîte de vitesses manuelle et raccordement d'essieu

Publications (1)

Publication Number Publication Date
EP3574236A1 true EP3574236A1 (fr) 2019-12-04

Family

ID=60997449

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18700521.0A Withdrawn EP3574236A1 (fr) 2017-01-30 2018-01-02 Actionneur de passage de vitesse, blocage de différentiel, boîte de transfert, boîte de vitesses manuelle et raccordement d'essieu

Country Status (5)

Country Link
US (1) US11408497B2 (fr)
EP (1) EP3574236A1 (fr)
CN (1) CN110234911A (fr)
DE (1) DE102017201411B4 (fr)
WO (1) WO2018137896A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019208345B4 (de) * 2019-06-07 2022-07-07 Zf Friedrichshafen Ag Differentialsperre
DE102022108834A1 (de) * 2022-04-12 2023-10-12 Schaeffler Technologies AG & Co. KG Aktuierungselement für eine Kupplung, mit zumindest einem Federelement und Kupplung

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2803149A (en) * 1954-06-11 1957-08-20 Rockwell Spring & Axle Co Shift mechanism for locking differential
DE1480172A1 (de) * 1965-09-29 1969-07-31 Schmid Leopold F Differentialbremse fuer Ausgleichsgetriebe von Kraftfahrzeugen
JPS59164419A (ja) * 1983-03-05 1984-09-17 Toyota Motor Corp 変速機トランスフア装置
US4549449A (en) * 1983-10-11 1985-10-29 Fairfield Manufacturing Company Gear reducer
DE4113128C2 (de) 1991-04-22 1995-05-24 Steyr Daimler Puch Ag Klauenkupplung
US5377800A (en) * 1993-05-04 1995-01-03 New Venture Gear, Inc. Hydraulically-actuated shift system for a transfer case
US5582557A (en) * 1995-06-07 1996-12-10 Titan Wheel International, Inc. Hydraulically-operable locking differential with in-line piston means
US6073502A (en) * 1998-03-20 2000-06-13 Muncie Power Products, Inc. Power takeoff device
US20030224896A1 (en) * 2002-05-15 2003-12-04 I-Chao Chung Hydraulic differential lock
US7211017B2 (en) * 2002-11-06 2007-05-01 Dana Corporation Inter-axle differential lock shift mechanism
DE102005037559B4 (de) * 2005-08-10 2021-03-25 Zf Friedrichshafen Ag Sperrbares Differenzial
US7524260B2 (en) * 2006-06-14 2009-04-28 Arvinmeritor Technology, Llc Drive axle with internal air shift mechanism
CN102083648A (zh) * 2008-07-07 2011-06-01 迪尔公司 电动液压差速器锁
DE102009029038A1 (de) 2009-08-31 2011-03-03 Zf Friedrichshafen Ag Verfahren zur Synchronisierung, Stellmotor und Schalteinrichtung mit Stellmotor
DE102015207930A1 (de) * 2015-04-29 2016-11-03 Zf Friedrichshafen Ag Vorrichtung zum Betätigen mehrerer Schaltelemente einer Getriebeeinrichtung

Also Published As

Publication number Publication date
US11408497B2 (en) 2022-08-09
WO2018137896A1 (fr) 2018-08-02
US20190390754A1 (en) 2019-12-26
CN110234911A (zh) 2019-09-13
DE102017201411B4 (de) 2019-08-08
DE102017201411A1 (de) 2018-08-02

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