WO2017020909A1 - Actionneur d'embrayage hydrostatique servant à l'actionnement d'un embrayage à friction - Google Patents

Actionneur d'embrayage hydrostatique servant à l'actionnement d'un embrayage à friction Download PDF

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Publication number
WO2017020909A1
WO2017020909A1 PCT/DE2016/200360 DE2016200360W WO2017020909A1 WO 2017020909 A1 WO2017020909 A1 WO 2017020909A1 DE 2016200360 W DE2016200360 W DE 2016200360W WO 2017020909 A1 WO2017020909 A1 WO 2017020909A1
Authority
WO
WIPO (PCT)
Prior art keywords
spindle
piston
clutch actuator
drive
pressure
Prior art date
Application number
PCT/DE2016/200360
Other languages
German (de)
English (en)
Inventor
Eduard Müller
Matthias Ehrlich
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112016003582.9T priority Critical patent/DE112016003582A5/de
Publication of WO2017020909A1 publication Critical patent/WO2017020909A1/fr

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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
    • F16D29/00—Clutches and systems of clutches involving both fluid and magnetic actuation
    • F16D29/005—Clutches and systems of clutches involving both fluid and magnetic actuation with a fluid pressure piston driven by an electric motor
    • 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
    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/108—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches
    • 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
    • F16D2025/081—Hydraulic devices that initiate movement of pistons in slave cylinders for actuating clutches, i.e. master cylinders
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/10—System to be controlled
    • F16D2500/102—Actuator
    • F16D2500/1021—Electrical type
    • F16D2500/1023—Electric motor
    • F16D2500/1025—Electric motor with threaded transmission

Definitions

  • Hydrostatic clutch actuator for operating a friction clutch
  • the invention relates to a hydrostatic clutch actuator for actuating a friction clutch, a friction clutch and a drive train, in particular for a motor vehicle.
  • hydrostatic clutch actuators for hydraulically actuating a friction clutch are known from the prior art and comprise the master cylinder of the hydraulic actuating system for this purpose.
  • hydrostatic clutch actuators for hydraulically actuating a friction clutch are known from the prior art and comprise the master cylinder of the hydraulic actuating system for this purpose.
  • Clutch actuator is usually a pressure cylinder (master cylinder) provided for receiving a hydraulic fluid, wherein the receiving volume by means of a pressure piston (master piston) is variable.
  • the pressure piston is in the
  • Pressure cylinder moves translationally, so that the recording volume of the
  • Pressure cylinder is changed.
  • a rotary electric drive is preferably used and the rotational movement is translated by means of a spindle drive into a translational movement of the pressure piston.
  • WO 201 1/050 766 A1 discloses a hydrostatic clutch actuator in which a pressure piston is arranged in a pressure cylinder, which is fixed translationally with a drive spindle, wherein the rotary drive by means of a planetary-roller transmission (PWG) this rotation in a translatory
  • PWG planetary-roller transmission
  • a disadvantage of this embodiment is the cantilevered embodiment of the translationally moving drive spindle.
  • This disadvantage is achieved, for example, by a hydrostatic clutch actuator according to WO 201 1/050 767 A1, in that the drive spindle is fixed in translation and is driven in rotation by an electric drive (directly).
  • the pressure piston also by means of a planetary gear transmission, of the drive spindle and relative to the drive spindle moves translationally.
  • the pressure piston is designed as an annular piston, which is supported radially on the inside and thus relieves the planetary-rolling gear of possible lateral forces.
  • a disadvantage of this embodiment is that the overall radial structure is very large. Planetary gear transmissions are known for example from EP 0 320 621 A1.
  • the invention relates to a hydrostatic clutch actuator for actuating a friction clutch, wherein the hydrostatic clutch actuator has at least the following components:
  • a pressure piston which is translatable to vary the receiving volume in the printing cylinder
  • the hydrostatic clutch actuator is characterized above all in that the pressure piston is formed as a solid piston of the spindle sleeve itself
  • the hydrostatic clutch actuator is particularly adapted for precise and rapid hydraulic actuation of a friction clutch.
  • an electric motor is provided with which the drive spindle is rotatable.
  • Drive spindle rotatably connected to the rotor of the electric motor.
  • the drive spindle is also translational, ie axially in the direction of
  • the spindle sleeve is in contrast to the drive spindle translationally movable and secured against rotation, preferably rotationally relative to the stator of the electric motor
  • the spindle sleeve comprises a spindle nut with a thread corresponding to the drive thread of the drive spindle, so that the rotational movement of the drive spindle is translated into a translational movement of the spindle sleeve. That is, in a (single) full revolution of the drive spindle, the spindle sleeve (preferably exactly) by the amount of
  • the spindle nut of the spindle sleeve is a translating or reducing gear, so that the transmission itself is translationally moved by the amount of thread pitch of the drive spindle at a full revolution of the drive spindle, but the spindle sleeve is moved more or less translationally different depending on the gear ratio ,
  • the pressure cylinder forms a cylinder volume and has on one side a piston opening into which the pressure piston can be inserted.
  • the pressure piston is translationally movable in the pressure cylinder and the
  • Piston opening is sealed by the plunger at least in printing operation against an adjacent environment. Furthermore, the pressure cylinder has a conduit opening through which a hydraulic fluid can flow out and in and thus in a hydraulic actuation system, the slave piston in the slave cylinder can be actuated.
  • the spindle sleeve here forms, preferably in one piece, at the same time the pressure piston, so that by the translational movement of the spindle nut, the receiving volume in the printing cylinder according to the translational movement of the spindle sleeve is variable.
  • the pressure piston is a solid piston, not as an annular piston, executed so that the pressure piston is immersed with a full circular area in a full-circle pressure cylinder.
  • the full circle surface may have an axial extent, for example, a gradation on.
  • Spindle sleeve is thus closed at the end, ie on the side facing away from the electric motor, executed closed, and preferably forms a pot shape, wherein the pot bottom forms the pressure surface of the pressure piston.
  • the pressure cylinder is in this case arranged in the axial extension of the electric motor from behind the drive spindle.
  • Pressure cylinder correspond to the radial dimensions of at least one
  • the dimensions of the printing cylinder and the spindle sleeve are formed correspondingly such that a radial support of the spindle sleeve in the printing cylinder is possible, preferably in operation with a lubricant film arranged therebetween.
  • the pressure cylinder is arranged such that the receiving volume of the printing cylinder is smallest when the spindle sleeve is located at a position furthest away from the electric motor, and the receiving volume of the printing cylinder is greatest when the spindle sleeve at a position closest to the electric motor located.
  • the annular piston provides a structure in which a closed power flow circuit is formed, which does not have the screwing of the pressure cylinder on
  • Screwed are leitbar, without loosening the screw or a deterioration of the sealing effect are to be feared. Furthermore, it has hitherto been avoided because of the greater sealing reliability, to arrange (molded) seals moved.
  • the spindle sleeve has a planetary-rolling gear for the gradient-true transmission of the rotational movement of the drive spindle in the translational movement of the pressure piston.
  • a planetary geared transmission PWG
  • S-PWG planetary geared transmission
  • the planetary gear transmission and a corresponding axial bearing are in this case arranged in the interior of the spindle sleeve, wherein preferably the spindle sleeve forms a first stop shoulder for a first thrust bearing and opposite one
  • a guide cage is further provided, by means of which the spindle sleeve
  • the guide cage is adapted to secure the spindle sleeve against rotation, so as to allow a translation of the rotational movement of the drive spindle in a translational movement of the pressure piston.
  • the guidance of the guide cage in interaction with corresponding guide means of the spindle sleeve is set up so precisely that the rotational play is negligible in the case of a pitch-true drive of the spindle sleeve or is sufficiently low for precise operation of a hydraulic actuation system for a friction clutch.
  • a (virtually incompressible) lubricating film is particularly preferably provided between the guide cage and the corresponding guide means of the spindle sleeve.
  • the drive spindle is formed from threaded rod material and has in the
  • Electric motor and a radial and axial guide bearing on a guide sleeve Electric motor and a radial and axial guide bearing on a guide sleeve.
  • Such a threaded rod material is particularly cost-effective and may be malleable to a more cost-effective price of a more stable material than is possible with a conventional drive spindle as a turned part with thread-free paragraph.
  • a guide sleeve is listed on the threaded rod material, and this guide sleeve is, for example, on the threaded rod material
  • Threaded rod material (guide sleeve has no thread or thread with a smaller depth of cut on) axially secured, and / or axially secured by means of an axial securing, for example by means of a Seegerings.
  • This guide sleeve or a further guide sleeve preferably further forms an axial stop in order to fix the drive spindle translationally therewith. This is particularly preferred
  • the pressure piston has an axially dynamic seal in the form of a
  • Piston seal with radially inside static sealing seat and with radial
  • the pressure piston has a (preferably single) axially dynamic seal, which is moved in translation with the pressure piston.
  • the static sealing seat of this seal is arranged radially on the inside and is, preferably suitably supported directly, on the pressure piston or the spindle sleeve.
  • the axially dynamic seal is axially fixed by a corresponding axial stop and an axial securing, for example a clamping ring, on the pressure piston or on the spindle sleeve.
  • Radial on the outside of the dynamic sealing seat is formed by a sealing lip, which is oriented such that the sealing lip in the operation of, compared to the adjacent environment larger pressure in the pressure cylinder against the
  • Cylinder wall of the printing cylinder is pressed.
  • a reservoir of hydraulic fluid forms the adjacent environment and, if that
  • hydraulic fluid preferably flows from the adjacent reservoir into the pressure cylinder.
  • no further secondary seal is preferably provided, and no fluid-tight barrier but merely a pressure barrier is formed by the axially dynamic seal.
  • a reservoir for the hydraulic fluid is provided, wherein (preferably) the reservoir is arranged in an annular space around the drive spindle and at least partially axially overlapping with the drive spindle.
  • a reservoir for a hydraulic fluid is provided in an annular space, via which hydraulic fluid can be added when the volume and / or pressure in the hydraulic Actuation system decreases.
  • the radial extent of the one proposed here increases
  • hydrostatic clutch actuator as a result of the use of the solid piston proposed here significantly.
  • This additionally gained space is preferably used as an annular space for the reservoir, wherein the reservoir in the annulus is preferably sufficiently large for operation and no additional reservoir is needed.
  • the reservoir is at least partially axially overlapping and at least partially axially between the electric motor and the back of the
  • the reservoir extends radially inwardly to the drive spindle and acts here additionally as a lubricant in possibly existing plain bearings and WälzSystemlagern.
  • a guide cage for the spindle sleeve forms a structural separation between the
  • a reservoir for the hydraulic fluid is provided, wherein the reservoir has at least one communication opening to the printing cylinder, wherein the at least one communication opening is opened in a communicating manner with a minimum stroke and is closed in the printing operation.
  • a reservoir is connected via at least one communication opening with the pressure cylinder such that via this at least one communication port hydraulic fluid can flow freely compensating in the pressure cylinder or can flow out of the pressure cylinder when the pressure piston is at a position which a corresponds to minimum stroke. With the minimum stroke, the capacity of the impression cylinder is maximum. That is, the pressure piston is, in an interpretive
  • the gasket is circumferentially but axially behind the at least one communication opening so that the flow path to the receiving space is free.
  • the at least one communication opening is designed as an axial slot, and preferably open to the side facing away from the receiving space, and at least one axial portion of the respective slot is then open to the receiving space. The seal then lies over the peripheral region between the at least one
  • the dynamic sealing lip of the pressure piston then projects into the communication opening and / or the cylinder migration of the printing cylinder forms a return at the corresponding position, so that the dynamic seal of the printing cylinder in this position no longer has a sealing effect.
  • Rotary axis proposed for releasably connecting an output shaft to a consumer, wherein the friction clutch comprises at least the following components:
  • a hydrostatic clutch actuator according to an embodiment according to the above description, wherein the pressure cylinder forms a master cylinder which is communicatively connected to the slave cylinder for hydraulically actuating the pressure plate.
  • the friction clutch is adapted to detachably transfer a torque from an output shaft to a load and vice versa. This is usually achieved via the (at least one) friction pack, which is an axial
  • an actuating spring for example a plate spring
  • the actuating piston is hydraulic, ie by means of a change of
  • Actuation volume in the slave cylinder translationally movable. If, for example, the actuating volume is increased, the actuating piston is moved in the pressing direction and thus a contact pressure on the pressure plate and thus on the
  • Friction package exercised If the actuating volume is reduced in this example, the actuating piston is moved back, thus interrupting the (complete) transmission of torque by means of the friction clutch.
  • the actuating volume of the slave cylinder is via the master piston or the
  • hydrostatic clutch actuator is that this has a very low overall volume.
  • the proposed here hydrostatic clutch actuator (approximately) on the dimensions of a conventional hydrostatic clutch actuator with an annular piston with a same stroke and a same receiving volume, in which case in addition a reservoir for hydraulic fluid with a
  • hydrostatic clutch actuator identical with the conventional hydrostatic clutch actuator with an annular piston, in particular the electric motor, the control electronics together
  • Measuring technology the electrical and / or hydraulic connections or access, the motor housing, the rolling element bearings, the planetary-Wälz gear. For some applications, it is useful to continue to use the available space for a reservoir for hydraulic fluid for a corresponding reservoir, this being provided alternatively or additionally.
  • a drive train which comprises a drive unit with an output shaft and a friction clutch according to the above description, wherein the output shaft for
  • Torque transmission by means of the friction clutch is detachably connectable with at least one consumer.
  • the drive train is set up to transmit a torque which is provided by a drive unit, for example an energy conversion machine, preferably an internal combustion engine or an electric drive machine, and output via its output shaft, for at least one consumer, ie switchable and switchable.
  • a drive unit for example an energy conversion machine, preferably an internal combustion engine or an electric drive machine, and output via its output shaft, for at least one consumer, ie switchable and switchable.
  • An exemplary consumer is at least one drive wheel of a motor vehicle and / or an electric generator for
  • Provision of electrical energy Conversely, a recording of an inertial energy introduced, for example, by a drive wheel can also be implemented.
  • the at least one drive wheel then forms the drive unit, wherein the
  • Inertia energy by means of the friction clutch to an electric generator for recuperation, so for the electrical storage of the braking energy, with a suitably equipped drive train is transferable.
  • a plurality of drive units are provided, which are connected by means of the friction clutch in series or in parallel or decoupled from each other operable, or whose torque is releasably available for use available. Examples are hybrid drives of electric drive machine and internal combustion engine, but also
  • Multi-cylinder engines in which individual cylinders (groups) can be engaged.
  • the use of the friction clutch described above is particularly advantageous.
  • Actuating system in particular the encoder unit, has a particularly low overall volume and / or a large reservoir for hydraulic fluid with a total of maximum conventional construction volume.
  • a motor vehicle which has at least one drive wheel which can be driven by means of a drive train according to the above description.
  • the drive unit for example an internal combustion engine or an electric drive machine, in front of the driver's cab and across the vehicle
  • Drive train has a friction clutch or a transmitter unit of particularly small size. At the same time, the volume of the reservoir for hydraulic fluid is sufficiently large. Thus, a total of a system of small size is possible.
  • Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and power, and this definition is subject to constant change according to the needs of the market.
  • vehicle class In the US market will be vehicles of the class Small cars and micro cars are classified according to European Classification of the Class of Subcompact Car and in the British market they correspond to the class Supermini or the class City Car.
  • micro car class Examples of the micro car class are a Volkswagen up! or a Renault Twingo.
  • Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.
  • Fig. 1 a conventional hydrostatic clutch actuator in section
  • Fig. 2 a hydrostatic clutch actuator in section
  • FIG. 4 shows a friction clutch with a hydrostatic clutch actuator
  • FIG. 5 shows a drive train in a motor vehicle with a friction clutch.
  • a conventional hydrostatic Kupplungsaktor 30 is shown in section, wherein a conventional annular piston 54 is shown above a translational axis 42 in a position with minimum lift and below the translational axis 42 in a position with maximum stroke. The space required for this axial space is through the conventional return stroke length 35 and the
  • the conventional peripheral overall length 32 is provided and the far right in the illustration is the
  • the conventional hydrostatic clutch actuator 30 shown here has a conventional annular piston 54, which is movable along the translatory axis 42 between the positions shown.
  • a conventional spindle sleeve 55 is provided, which is drivable here by means of a pitch-true planetary-roller gear 8 of a conventional drive spindle 43.
  • the conventional drive spindle 43 in this case has a conventional spindle paragraph 51, as well as a conventional
  • the electric motor 6 is here in one
  • Motor housing 44 at least partially axially in the field of conventional
  • Pressure cylinder 49 extends. Opposite the adjacent environment, which is here formed by the (dry) conventional piston housing 50, is the
  • the static seal toward the conventional pressure cylinder 49 is formed in each case and the dynamic sealing lip is formed toward the conventional annular piston 54 and they are translationally fixed.
  • the conventional annular piston 54 is connected to the conventional spindle sleeve 55.
  • the conventional reservoir 37 is in this case provided externally and forms between the conventional primary seal 39 and the conventional secondary seal 40 a conventional communication opening 38, which forms a return in the conventional primary seal 39, so that the conventional communication opening 38 in the position shown above the translational axis 42 minimal hubs with the conventional
  • Pressure cylinder 49 is communicatively connected.
  • a hydrostatic clutch actuator 1 is shown in which a
  • the pressure piston 4 which is embodied here in one piece with the spindle sleeve 7 and also as a solid piston, is movable in the pressure cylinder 3 along the translational axis 42 between a position of the minimum stroke and a position of the maximum stroke. As a result, the receiving volume in the printing cylinder 3 is changed.
  • a hydraulic fluid is displaced by a hydraulic connection opening 45 from the pressure cylinder 3 or sucked into the pressure cylinder 3, so as to actuate a hydraulically communicating slave piston.
  • the pressure piston 4 in this case has the axially dynamic seal formed by a piston seal 12, which is moved with the pressure piston 4 and its static sealing seat 13 radially inward and its dynamic sealing seat 14, here a pressure cylinder 3 facing the dynamic sealing lip, radially outward on the cylinder conversion of the printing cylinder 3 has.
  • the dynamic sealing seat 14 is located in the position of the minimum stroke (shown below the translational axis 42) axially behind the communication openings 16 (here as slots), so that the reservoir 15, which is arranged here in an annular space axially overlapping with the drive spindle 5, by means of
  • a (here common) guide sleeve 1 1 is provided for the radial and axial guide bearing 10 and the electric motor 6, which is screwed for example on the drive spindle 5 with a cutting thread and also forms a spindle stop 53 at the radial and axial guide bearing 10.
  • a conventional electric motor 6 is preferred, and particularly preferably one Conventional radial and axial guide bearing 10, here a four-point bearing, used, wherein the radial extent of the guide sleeve 1 1 by a
  • a conventional motor housing 44 is preferably used here.
  • the pressure cylinder 3 is in this case formed by means of a much simpler housing and connected directly to the conventional motor housing 44.
  • a bearing receptacles 47 is provided, which is formed here advantageously as (for example, deep-drawn) sheet metal component.
  • a guide cage 9 is provided, by means of which the spindle sleeve 7 is secured against rotation and in this advantageous embodiment is also held by the bearing seat 47.
  • the guide cage 9 is here between the
  • FIG. 3 shows a hydrostatic clutch actuator 1 above the translational axis 42 and a conventional hydrostatic clutch actuator 30 below the translational axis 42 for direct comparison. It can be seen here that the same electric motor 6 and the same radial and axial guide bearing 10 can be used in the conventional hydrostatic clutch actuator 30 and the hydrostatic clutch actuator 1.
  • the spindle sleeve 7 and the conventional spindle sleeve 55 and the planetary roller gear 8 are in this case (approximately) shown in the same position, whereby thereby the pressure piston 4 in the position of the maximum stroke, so the smallest receiving volume in the pressure piston 3, is located and the conventional annular piston in the position of the minimum stroke, ie the largest receiving volume in the conventional pressure cylinder 49.
  • the spindle sleeve 7 and the conventional spindle sleeve 55 and the planetary roller gear 8 are in this case (approximately) shown in the same position, whereby thereby the pressure piston 4 in the position of the maximum stroke, so the
  • Ring piston 54 the view of the conventional hydraulic port opening 46 free, through which the hydraulic fluid in the conventional pressure cylinder 49 is pushed or sucked. In this direct comparison is also good to see that the piston seal 12 of the plunger 4 in the
  • Solid piston design is significantly less expensive than this
  • an approximately cost-same but more stable component than bearing receptacle 47 is formed, which can be manufactured from (deep-drawn) sheet metal material.
  • the electric motor housing 44 together with the control electronics and measuring electronics is in this case for both
  • Embodiments (almost) identical.
  • FIG. 4 shows, by way of example, a friction clutch 2 as a (dry) double clutch with a first friction pack 21 and a second friction pack 60 which can be actuated by means of a first slave cylinder 24 with a first actuating piston 23 or by means of a second slave cylinder 63 with a second actuating piston 62 ,
  • a friction clutch 2 as a (dry) double clutch with a first friction pack 21 and a second friction pack 60 which can be actuated by means of a first slave cylinder 24 with a first actuating piston 23 or by means of a second slave cylinder 63 with a second actuating piston 62 ,
  • About the output shaft 18 is a torque around the
  • Rotary axis 17 can be entered, which by means of the first Reibver 21 on a first transmission shaft 68 and by means of the second Reibvers 60 to a second
  • Transmission shaft 69 is releasably transferable.
  • the first friction pack 21 consists here of several friction plates, namely a first pressure plate 22, a first
  • Friction discs namely a right first friction disc 58 and a left first friction disc 59, for which friction plates are used, together.
  • the second friction pack 60 is also made here of a plurality of friction plates, namely a second pressure plate 61, a second intermediate plate 64 and a second
  • Counter plate 65 and here from several friction plates, namely a right second friction plate 66 and a left second friction plate 67, for which also Friction blades are usable together.
  • the designation right and left here refers solely to the illustration in FIG. 4.
  • the friction packs 21 and 60 are of a hydrostatic clutch actuator 1 (transmitter unit), which is pure here
  • a hydraulic line 70 preferably automated, operable.
  • the friction packs 21 and 60 are compressed and a torque from the output shaft 18 is frictionally transferable to the respective transmission shaft 68 and 69, respectively.
  • Fig. 5 is a drive train 25, comprising a drive unit 26, here as
  • the drive train 25 is arranged here in a motor vehicle 71, wherein the drive unit 26 is arranged with its motor axis 29 transversely to the longitudinal axis 28 in front of the driver's cab 27.

Abstract

L'invention concerne un actionneur d'embrayage hydrostatique servant à l'actionnement d'un embrayage à friction, l'actionneur d'embrayage hydrostatique comprenant au moins les composants suivants : - un cylindre de pression comportant un volume variable de réception d'un liquide hydraulique, le cylindre de pression étant mobile en translation ; - une broche d'entraînement rotative et fixe en translation servant au déplacement en translation du piston de pression ; - un moteur électrique servant à la rotation de la broche d'entraînement ; - une douille de broche mobile en translation et bloquée en torsion qui peut être entraînée par la broche d'entraînement et qui est fixe axialement par rapport au piston de pression. L'actionneur d'embrayage hydrostatique est avant tout caractérisé en ce que le piston de pression est formé par la douille de broche même, sous la forme d'un piston plein. L'actionneur d'embrayage hydrostatique selon l'invention permet de réduire considérablement l'espace nécessaire au montage, tout en réduisant les coûts de fabrication.
PCT/DE2016/200360 2015-08-06 2016-08-04 Actionneur d'embrayage hydrostatique servant à l'actionnement d'un embrayage à friction WO2017020909A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112016003582.9T DE112016003582A5 (de) 2015-08-06 2016-08-04 Hydrostatischer kupplungsaktor zum betätigen von einer reibkupplung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015214976.5 2015-08-06
DE102015214976.5A DE102015214976A1 (de) 2015-08-06 2015-08-06 Hydrostatischer Kupplungsaktor zum Betätigen von einer Reibkupplung

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WO2017020909A1 true WO2017020909A1 (fr) 2017-02-09

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PCT/DE2016/200360 WO2017020909A1 (fr) 2015-08-06 2016-08-04 Actionneur d'embrayage hydrostatique servant à l'actionnement d'un embrayage à friction

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WO (1) WO2017020909A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0320621A1 (fr) 1987-11-17 1989-06-21 Deutsches Zentrum für Luft- und Raumfahrt e.V. Dispositif pour convertir un mouvement rotatif en un mouvement axial
EP1437519A1 (fr) * 2003-01-09 2004-07-14 LuK Lamellen und Kupplungsbau Beteiligungs KG Maítre-cylindre pour système de debrayage
EP1612446A1 (fr) * 2004-06-30 2006-01-04 LuK Lamellen und Kupplungsbau Beteiligungs KG Procédé pour calibrer un dispositif de mesure de déplacement incrémental utilisé en actionneur d'embrayage fermé par pression et un tel actionneur.
DE102007003902A1 (de) * 2007-01-19 2008-07-24 Robert Bosch Gmbh Kupplungssystem und Verfahren zur Steuerung eines Kupplungssystems
WO2011050766A1 (fr) 2009-10-29 2011-05-05 Schaeffler Technologies Gmbh & Co. Kg Actionneur d'embrayage hydrostatique
WO2011050767A1 (fr) 2009-10-29 2011-05-05 Schaeffler Technologies Gmbh & Co. Kg Actionneur hydrostatique

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* Cited by examiner, † Cited by third party
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EP0320621A1 (fr) 1987-11-17 1989-06-21 Deutsches Zentrum für Luft- und Raumfahrt e.V. Dispositif pour convertir un mouvement rotatif en un mouvement axial
EP1437519A1 (fr) * 2003-01-09 2004-07-14 LuK Lamellen und Kupplungsbau Beteiligungs KG Maítre-cylindre pour système de debrayage
EP1612446A1 (fr) * 2004-06-30 2006-01-04 LuK Lamellen und Kupplungsbau Beteiligungs KG Procédé pour calibrer un dispositif de mesure de déplacement incrémental utilisé en actionneur d'embrayage fermé par pression et un tel actionneur.
DE102007003902A1 (de) * 2007-01-19 2008-07-24 Robert Bosch Gmbh Kupplungssystem und Verfahren zur Steuerung eines Kupplungssystems
WO2011050766A1 (fr) 2009-10-29 2011-05-05 Schaeffler Technologies Gmbh & Co. Kg Actionneur d'embrayage hydrostatique
WO2011050767A1 (fr) 2009-10-29 2011-05-05 Schaeffler Technologies Gmbh & Co. Kg Actionneur hydrostatique

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