Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
  • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
  • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
  • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
  • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
• • 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
  • F16D13/00—Friction clutches
  • F16D13/58—Details
  • F16D13/583—Diaphragm-springs, e.g. Belleville
  • F16D13/585—Arrangements or details relating to the mounting or support of the diaphragm on the clutch on the clutch cover or the pressure plate
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
  • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
  • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
  • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
  • B60K6/48—Parallel type
  • B60K2006/4825—Electric machine connected or connectable to gearbox input shaft
• • 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
  • F16D13/00—Friction clutches
  • F16D13/22—Friction clutches with axially-movable clutching members
  • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
• • 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
  • F16D2300/00—Special features for couplings or clutches
  • F16D2300/26—Cover or bell housings; Details or arrangements thereof
• • 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
  • F16D25/087—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 the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/60—Other road transportation technologies with climate change mitigation effect
  • Y02T10/62—Hybrid vehicles

Definitions

• Embodiments of the present invention generally relate to clutches, in particular separating clutches, as can be used, for example, in hybrid drives.
• a hybrid drive is understood to mean a vehicle drive which has more than one drive unit or one drive source.
• a first drive unit is an internal combustion engine, such as.
• a second drive unit is usually designed as an electric machine or electric motor.
• Hybrid drives can be differentiated into so-called micro, mild or medium and full hybrid drives based on various factors.
• a full hybrid drive allows driving with only the electric motor as the drive source.
• a separating clutch (KO clutch) is typically arranged between the internal combustion engine and the electric machine.
• K0 coupling Various variants of such a K0 coupling are described for example in DE 10 2005 053 887 A1.
• a coupling housing is fixedly connected to a rotor of the electric drive or part of a rotor carrier and forms a disc-shaped connection to the rotor bearing or an output hub.
• the diameter of the rotor bearing or the output hub is usually smaller than the diameter of a Kupplungsbetuschigers or releaser.
• a counter-holder can be riveted by means of spacer bolts and a diaphragm spring can be clamped to the support diameters.
• Such a design principle causes a pressure plate or pressure plate or the actuator disadvantageously must pass through the disc-shaped coupling housing.
• a further problem with known disconnect couplings is that the counterholder and the spacer bolts must support an entire contact pressure via a contact point, which can lead to spacer pin fractures.
• the mentioned passage through the clutch housing also requires axial space, which runs counter to a goal for smaller and smaller hybrid modules.
• a clutch assembly in particular for a motor vehicle, is provided.
• the clutch assembly is used for torque transmission between a first and a second shaft, such as a drive train of the motor vehicle.
• exemplary embodiments of the clutch arrangement have a coupling housing which can be frictionally coupled to the first shaft via a clutch.
• a portion of the clutch housing is non-rotatably coupled to a counterpart to the portion axially (ie in the direction of a shaft or axis of rotation) and connected to the second shaft counter support, so that when the clutch is closed, a torque transmission between the first shaft and the clutch housing and, by means of the counter-holder, can continue between the clutch housing and the second shaft.
• the torque flow can therefore take place from the first shaft via the clutch, which may be a dry clutch for example, to the clutch housing and from there further via torque transmitting spacers to the counter housing axially spaced from the clutch housing portion and finally to the second shaft, or in the reverse direction.
• the clutch which may be a dry clutch for example, to the clutch housing and from there further via torque transmitting spacers to the counter housing axially spaced from the clutch housing portion and finally to the second shaft, or in the reverse direction.
• both shafts can serve both as a drive shaft and as an output shaft.
• first shaft and second shaft are interchangeable.
• the portion of the coupling housing or the coupling housing portion may extend from a radially outer portion of the coupling housing radially inwardly toward the second shaft, so that one can also speak of a radial coupling housing portion.
• the counter-holder may in embodiments extend radially from the second shaft outwardly toward the radially outward portion of the clutch housing so that there is a radial overlap area between the radial clutch housing portion and the axially spaced radial counter-mount in which the radial clutch housing portion and the counter-holder, for example by means of axial spacer bolts, rotatably (ie torque-transmitting) are interconnected.
• the axial spacer elements for example, pass through corresponding through openings of a placed between the radial coupling housing portion and the counter-holder elastic return element, such as a membrane or disc spring. That is, for actuation of a pressure plate of the clutch assembly can, axially between the radial clutch housing portion and the radial counter support, an elastic return element radially from a radially closer to the second shaft positioned release device to the opposite radially outwardly positioned pressure plate extend.
• the counter-holder elastic return element such as a membrane or disc spring
• the radial coupling housing portion may extend only to radially above a releaser of the release device, so that the radial coupling housing portion is annular and thus provides an encircling within the radial coupling housing portion ring opening for engaging the releaser.
• the circumferential annular opening is between the surface of the second shaft and the inner radial end of the radial coupling housing portion, which allows a comparatively uncomplicated operation of the return element at the radially inner region through the annular opening.
• the clutch assembly may be used, for example, as a disconnect clutch assembly (KO clutch).
• the disconnect clutch assembly is configured to couple an internal combustion engine and an electric machine to a rotating component (rotor).
• the coupling housing can be designed as a carrier for the rotating component, ie as a rotor carrier.
• Embodiments of a disconnect clutch arrangement therefore have a rotor carrier which can be coupled in a friction-locked manner to a motor shaft via a clutch.
• a portion of the rotor carrier is rotatably coupled to a to the rotor support portion axially spaced and with a transmission shaft (rotationally fixed) connected counter-holder, so that when the clutch is a torque transmission between the motor shaft and the rotor carrier and, by means of the mating support, further between the rotor carrier and the transmission shaft can take place.
• the torque flow can thus take place from the motor shaft via the coupling to the rotor carrier and from there further via distance elements to the counter support and finally to the transmission shaft, or in the opposite direction.
• the clutch assembly may be used as a dry clutch, such as a dry clutch.
• a disc or multi-plate clutch may be formed. Both "normally-closed” and “normally-open” couplings are possible.
• a conventional disc-shaped connection between the clutch housing or rotor carrier and rotor bearing or output hub can be separated and divided into at least two disc-shaped components, namely the radial coupling housing portion and the counter-holder.
• the two components are rotatably and non-positively and torque transmitting means axialverschsatzlitisder components such as spacer bolts connected to each other.
• An elastic return element such as a diaphragm or disc spring, is located in an axial gap between the disc-shaped coupling housing portion and the anvil.
• the counter-holder has the additional task of transmitting bearing forces or moments between the clutch housing or rotor carrier and the transmission shaft.
• Fig. 1 is a sectional view of a clutch assembly according to an embodiment of the present invention
• Fig. 2 is an enlarged view of one half of the coupling arrangement according to
• FIG 3 shows a disconnect clutch arrangement between an internal combustion engine and a transmission according to an embodiment of the present invention.
• FIG. 1 shows a clutch assembly 10 according to an embodiment of the present invention.
• the clutch assembly 10 may be used for example in a motor vehicle to frictionally couple a first shaft 12 and a direction indicated by the reference numeral 14 second shaft with each other.
• the first shaft 12 may for example be an output shaft, such as a transmission shaft
• the second shaft 14 may act as a drive shaft, such as an engine shaft (crankshaft).
• the functions of input and output shaft can also be reversed.
• the shaft 14 can also act as an output shaft and the shaft 12 as a drive shaft, depending on the direction in which torque is to be transmitted.
• the coupling assembly 10 has a coupling housing 18 attached to a flange-like and radially extending support 16.
• the clutch housing 18 has a radially outwardly extending region or section 18b, which extends substantially parallel to a rotation axis A, which may correspond to the first and / or the second shaft 12, 14.
• the various individual parts of the coupling arrangement 10 are arranged radially inside the coupling housing 18 or inside the radially outer area 18b.
• the clutch housing 18 may also act as a support for a rotor of an electric machine. This is particularly advantageous for applications in which the clutch assembly 10 is used as a disconnect between an internal combustion engine and an electric motor, such as in hybrid vehicles.
• a dry clutch in particular a friction clutch
• FIG. 1 a clutch arrangement 10.
• embodiments are not limited to such coupling concepts.
• the present invention can be applied to embodiments with wet clutches. It can be used clutches with one or more clutch discs, in particular also multi-plate clutches.
• the exemplary friction clutch assembly 10 has a clutch plate 20 with clutch linings or friction rings 22, which can cooperate with friction linings on the part of the radial support 1 6 and the side of a clutch pressure plate 26.
• the clutch disc 20 together with its friction linings 22 can be non-rotatably coupled via a hub 24 and a toothing 15 to the shaft 14 (eg crankshaft) not explicitly illustrated in FIG. 1, so that the clutch disc 20 rotates together with the shaft 14.
• a pressure plate 26 is provided, which may be connected, for example, with the clutch housing or cover 18.
• the pressure plate 26 can be actuated by means of an elastic actuating or restoring element 28.
• the elastic actuating element 28 shown in FIG. 1 may be, for example, a plate or diaphragm spring.
• a so-called normally-closed clutch is shown in which the elastic return element 28 presses the pressure plate 26 and thus the friction linings 22 of the clutch disc 20 against a cooperating friction surface of the carrier 16 in the unactuated or unrestrained state To obtain connection between the clutch disc 20 and the carrier 1 6 and the clutch housing 18 (engaged state).
• the clutch housing 18 further includes, according to embodiments, a portion 18c extending radially inwardly from the radially outward axial portion 18b of the clutch housing in the direction of the axis of rotation A.
• This radial section 18c of the clutch housing 18, which may also be an axial boundary of the clutch assembly 10 or the components installed therein, is non-rotatable and torque-transmitting via spacer bolts 30, for example, with a counterpart holder 32 axially spaced therefrom and non-rotatably connected to the output shaft 12 coupled to receive torque transmission between the shafts 14 and 12 via the clutch housing 18 and the mating bracket 32 with the clutch assembly 10 engaged.
• the radially extending portion 18 c of the clutch housing which are also considered as inwardly directed radial flange of the clutch housing 18 can extends from the radially outer axial portion 18 b of the clutch housing radially inwardly in the direction of the shaft 12, but without extending all the way to the shaft 12.
• the counter support 32 axially spaced from the portion 18c toward the clutch housing portion 18c extends radially from the shaft 12 outwardly toward the radially outward axial portion 18b of the clutch housing 18, but not all the way to the axial portion 18b extend.
• the radial coupling housing portion 18c does not extend to the shaft 12, so that an annular access opening 36 results annularly around the shaft 12, via which the elastic return element 28, which is arranged axially between the radial coupling housing portion 18c and the radial counter support 32 , by means of a release device (not shown) can be operated.
• the elastic return element or the diaphragm spring 28 has a cantilever 38 on which the release device not shown in FIG. 1 can engage. This is indicated by the arrow 40.
• the radial mating bracket 32 does not extend to the axial portion 18b of the clutch housing 18 to keep a radial area between the end of the mating bracket 28 and the radially outer axial housing portion 18b for the pressure plate 26. That is, the radial clutch housing portion 18c and the radial counter support 32 overlap with their respective radial end portions in the radial direction. It is however, the radial overlap region is smaller than the respective radial total extension of the coupling housing portion 18c and the counter support 32nd
• the counter-holder 32 and the radial coupling housing portion 18c in their radial overlap region for torque transmission rotatably coupled to each other.
• the radial coupling housing portion 18c and the counter-holder 32 by means of force and / or torque-transmitting spacer elements, such. B. spacer bolts 30, which cause the torque transmission between the clutch housing 18 and the shaft 12, rotatably connected to each other.
• spacer elements 30 arranged in the circumferential direction, corresponding passage openings 43 are provided in the elastic return element 28 (see FIG. 2).
• the clutch housing 18, 18b, 18c, counter support 32, return element 28 and pressure plate 26 always rotate simultaneously with the shaft 12 or not rotate, depending on the operating condition. In contrast, the clutch disc 20 always rotates together with the shaft 14.
• a disengagement device for actuating the elastic return element 28 disposed axially between the radial clutch housing section 18c and the counter support 31 can be mounted on one of the counter support 32 axially opposite side of the discoidal return element 28.
• the release device can be arranged so as to actuate the return element 28 or its collar 38 by means of a releaser radially within the circumferential recess 36 of the radial coupling housing portion 18c.
• the radial portion 18c of the clutch housing 18 thus extends in embodiments only to radially above a releaser of a release device for actuating the return element 28th
• FIG 3 shows an axial section of a section of a motor vehicle drive train 50 with a torsional vibration damper arrangement 52 coupled to an internal combustion engine and a manual transmission 54, which may be designed, for example, as an automatic transmission. It can be seen that, for example, within a transmission bell 56, a clutch assembly 60 has been integrated into the drivetrain 50 in order to drive the vehicle purely by electric motor, purely internal combustion engine or in a mixed mode of operation, as is common in hybrid vehicles.
• a stator 62 of a permanent-magnet electric machine designed as an internal rotor is arranged rotatably supported by means of a stator support 64, for example by means of a screw connection inside the transmission bell 56.
• the design of the electric machine is irrelevant for the further embodiments, i. This may, for example, be provided as an asynchronous machine, reluctance machine or the like.
• an external rotor can be used by modifications, an external rotor.
• a rotatably mounted inside the stator 62 rotor 66 has a rotor carrier 18 with a radial support portion 1 6 and an axial portion screwed therewith 18b and a rotor yoke, on whose outer peripheral surface a plurality of permanent magnets may be arranged, whose magnetic field with one of a winding system of Stators 62 generated additional magnetic field interact and thus can drive the rotor 66 and can serve to drive the vehicle or the starting of the not explicitly shown in FIG. 3 internal combustion engine.
• the clutch housing 18 additionally assumes the role of a rotor carrier.
• the radial support portion 1 6, or an axial flange 1 6a thereof, is connected to the stator 64 via a merely exemplary double row bearing arrangement 65 rotatably mounted, whereby a radial relative position between the stator 62 and rotor 66 is set.
• the rotor 66 is shown in FIG. 3 via a friction clutch, which substantially corresponds to the clutch assembly 10 described above with reference to FIGS. 1 and 2, with a crankshaft or secondary shaft 14 of the torsional vibration damper assembly 52 of the internal combustion engine and with an input shaft 12 of the Gear 54 in operative connection.
• the arrangement of the rotor 66 with the coupling is extremely compact, in that the coupling is arranged in the rotor 66 within a receiving space delimited by the axial rotor carrier section 18b and the radial rotor carrier section 18c, and thus no further axial and radial installation space is claimed therefrom.
• the internal combustion engine rotates the drive shaft 14 or via its toothing 15 and the hub 24 and the clutch disc 20, as already explained with reference to FIGS. 1 and 2.
• the internal combustion engine and clutch disc 20 are therefore rotatably coupled with each other via the shaft 14, the teeth 15 and the hub 24.
• the arrangement of shaft 14 and hub 24 is mounted with the axial flange 1 6a of the radial support portion 1 6 (and the stator 64) via a needle bearing 67.
• the transmission shaft 12 via the radial counter-holder 32, the axial spacer elements 30 and the radial rotor support portion 18c rotatably connected to the clutch housing 18, which acts as a rotor carrier. This means that the components mentioned always rotate together.
• Fig. 3 shows a cooperating with the clutch assembly 60 disengaging device 70, which includes a releaser 72, a release bearing 74 and a hydraulic cylinder 76.
• the disengaging device 70 in particular its disengager 72, is arranged in a radial region between the surface of the gear shaft 12 and the radial end of the radial rotor carrier section 18c. This area corresponds to the annular arranged around the shaft 12 opening 36, which serves for engaging the releaser 72 to the collar 38 of the elastic return element 28, and thus for engagement and disengagement.
• the releaser 72 is disposed on a side of the disc-shaped elastic return element 28, which is opposite to the radial counter-holder 32. That is, the disengager 72 is located axially on the same side of the return member 28 as the overlying radial rotor support portion 18c. The latter, however, does not extend in the radial direction as far as the disengager 72, so that it can unhinderedly actuate the elastic return element 28 in the resulting peripheral opening region 36.
• the operation of the releaser 72 can be done by exerting a force directed axially in the direction of the return element 28, which, starting from the hydraulic cylinder 76 via the axial forces receiving bearing 74, is transmitted to the releaser 72.
• the release bearing 74 may be an angular contact ball bearing, so that the axial force can be transmitted from an outer ring of the bearing 74 to a bearing inner ring of the release bearing 74 acting as a disengager 72.
• the disconnect device 60 advantageously enables engagement of the disengagement device 70 with the discoid return element 28.
• the actuator 72 need not be cumbersome (e.g. by means of cams) pass through a disc-shaped coupling housing, since this is advantageous according to embodiments in two radially extending and axially separated components 18c and 32 split.
• the counter-holder 32 extends closer to the clutch disc 20 than the radial clutch housing portion 18c.
• the restoring element 28 is arranged, the radially inwardly located collar 38 is freely accessible from the outside axially and whose radially outer end cooperates with the pressure plate 26.
• the return element 28 is supported on contact areas 42, around which it can tilt when actuated.
• spacer bolts 30 described merely by way of example can also be replaced by other axial shaping of at least one or the two components 18c, 32 which can engage through the spacer bolt holes 43 of the diaphragm spring 28.
• aspects have been described in the context of a device, it will be understood that these aspects also constitute a description of the corresponding method, so that a block or a component of a device is also to be understood as a corresponding method step or as a feature of a method step. Similarly, aspects described in connection with or as a method step also represent a description of a corresponding block or detail or feature of a corresponding device.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Mechanical Operated Clutches (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=48790452

Family Applications (1)

Country Status (2)

Citations (7)

Family Cites Families (3)

• 2012
  • 2012-08-17 DE DE102012214651.2A patent/DE102012214651A1/de not_active Withdrawn
• 2013
  • 2013-07-12 WO PCT/EP2013/064758 patent/WO2014026813A1/fr not_active Ceased

Patent Citations (7)

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