CN104121325A - Torque transmission device with cut-off clutch and centrifugal pendulum of hybrid vehicle - Google Patents
Torque transmission device with cut-off clutch and centrifugal pendulum of hybrid vehicle Download PDFInfo
- Publication number
- CN104121325A CN104121325A CN201410177918.3A CN201410177918A CN104121325A CN 104121325 A CN104121325 A CN 104121325A CN 201410177918 A CN201410177918 A CN 201410177918A CN 104121325 A CN104121325 A CN 104121325A
- Authority
- CN
- China
- Prior art keywords
- rotor
- clutch
- torque transmitter
- cut
- centrifugal force
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 32
- 238000002485 combustion reaction Methods 0.000 claims abstract description 38
- 238000013016 damping Methods 0.000 claims abstract description 35
- 241000239290 Araneae Species 0.000 claims description 63
- 230000007246 mechanism Effects 0.000 claims description 45
- 125000006850 spacer group Chemical group 0.000 claims description 45
- 238000003825 pressing Methods 0.000 claims description 7
- 230000000712 assembly Effects 0.000 description 12
- 238000000429 assembly Methods 0.000 description 12
- 230000002349 favourable effect Effects 0.000 description 11
- 238000009826 distribution Methods 0.000 description 2
- 238000002955 isolation Methods 0.000 description 2
- 210000003734 kidney Anatomy 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000010363 phase shift Effects 0.000 description 1
- 239000000523 sample Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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
-
- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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 ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 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
- 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
-
- 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
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings
-
- 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
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
- F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
- F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/42—Clutches or brakes
- B60Y2400/424—Friction clutches
- B60Y2400/4242—Friction clutches of dry type
-
- 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
- F16D2300/22—Vibration damping
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a torque transmission device of a hybrid vehicle, which can use an internal combustion engine and an electric drive device (10) to drive. According to the embodiment, the torque transmission device comprises the electric drive device with a rotor, a cut-off clutch for separating the internal combustion engine from a transmission, and a centrifugal pendulum for vibration damping. In the torque transmission device, the centrifugal pendulum is axially arranged in a rotor so that the vibration damping can be realized with a very low requirement for structural space and a very low inertia moment.
Description
Technical field
The present invention relates to a kind of torque transmitter for the motor vehicle driven by mixed power that can drive by internal-combustion engine and electric driver, its be applicable to be arranged in motor vehicle driven by mixed power in the internal-combustion engine and the drivetrain between speed changer of motor vehicle driven by mixed power.
Background technique
Need under many circumstances torque-transmitting mechanisms, to can guarantee the acting in conjunction of internal-combustion engine and motor in the drivetrain of motor vehicle driven by mixed power.At this, torque-transmitting mechanisms is often on the one hand born from internal-combustion engine and/or motor to the output shaft transmission of torque function of speed changer in other words, bears on the other hand the function of vibration damping.In addition, torque-transmitting mechanisms can be configured to starting apparatus combustion engine.At this, mostly motor is integrated in torque-transmitting mechanisms.For vibration damping, be provided with the flywheel mass of a plurality of for example double mass flywheels or centrifugal force pendulum (Fliehkraftpendel) form.Double mass flywheel is regarded as for reducing the most effectively device at the torsional oscillation of drivetrain.For example with the double mass flywheel of internal damping device, to surpass 1500 speed range that turn be particularly advantageous for per minute.Centrifugal force pendulum is a kind of vibration damper (Tilger), that is to say it is a kind of with one or more device of the associated mass in power stream not, wherein, associated mass encourages with its resonant frequency, and the opposing vibration that will the be subject to damping vibration that relatively will be subject in other words damping has phase shift and moves.Due to the dependence of centrifugal force to rotating speed, such vibration damper is (drehzahladaptiv) of rotating speed adaptation advantageously.In addition, torque-transmitting mechanisms also can have cut-off clutch, especially to different flywheel masses can be engaged with each other.At this, centrifugal force pendulum also can be born the function of energy buffer.Therefore, torque-transmitting mechanisms and separating vibration and fuel saving have been born particularly explicitly for the slow-speed of revolution and the very important task of double-clutch speed changer, even if this is because good isolation also can realize the transmission of torque without slippage of double-clutch speed changer or common automatic transmission in slow-revving situation.
Owing to having a plurality of assemblies, such torque-transmitting mechanisms needs a lot of structure spaces especially in the axial direction.In order to keep the low demand to axial arrangement space, considered cut-off clutch has been arranged in the rotor of motor.In addition, the mechanism with double mass flywheel is known, for especially in the object of the vibration damping of the improvement lower than in the per minute 1500 slow-revving situations that turn, in this double mass flywheel, be integrated with centrifugal force pendulum, especially in the primary side of vibration damping partly of double mass flywheel.In this layout, centrifugal force pendulum is especially effectively and to the requirement in axial arrangement space seldom, but these mechanisms have very high moment of inertia.Also be known to the mechanism building by the double mass flywheel with internal damping device and independent centrifugal force pendulum.
Document DE10 2,012 206 292A1 show a kind of torque transmitter of the drivetrain for Motor Vehicle, and wherein, drivetrain has in the rotor recesses that is arranged in rotor mechanism with the energy converting between mechanical device of rotor mechanism and torque transmitter.Torque transmitter is integrated in rotor recesses in the axial direction substantially.Torque transmitter has torque damping mechanism, and this torque damping mechanism can make torsional vibrations be subject to damping by friction, and this torque damper can be configured to double mass flywheel.Thus, only need axial arrangement space seldom, and transmission of torque can be carried out under very high safety in operation.
Publish document WO2010/028620A1 show a kind of for mixed power application with the internal-combustion engine that can be engaged with each other by cut-off clutch, motor, the torque-transmitting mechanisms of double mass flywheel and another flywheel mass, wherein, one of them flywheel mass of double mass flywheel can with internal-combustion engine in anti-relative rotation (drehfest) be connected, and another flywheel mass can be connected with speed changer and can connect with rotor and the centrifugal force pendulum mechanism of motor, and centrifugal force pendulum mechanism can axially be arranged between rotor and starting clutch or attach troops to a unit in jack shaft or starting clutch.Double mass flywheel is arranged in the driving side of rotor.At this, cut-off clutch can be arranged in double mass flywheel and cause another flywheel mass and double mass flywheel acting in conjunction here.By cut-off clutch and centrifugal force pendulum mechanism, especially the in the situation that of cut-off clutch closure, can make as follows rotational vibrations be subject to damping by flexible mode, that is, the mutual connection of three flywheel masses and vibration damping are also utilized by the centrifugal force pendulum mechanism acting on as vibration damper.
Document DE10 2,011 087 334A1 show a kind of mixed power module with internal-combustion engine and speed changer of the power train for vehicle, wherein, this mixed power module arrangement is between internal-combustion engine and speed changer and have electric driver, cut-off clutch and a freewheel (Freilauf), and wherein, mixed power module structure is used for the transmission of torque function of conventionally being born by oneself by cut-off clutch to be assigned to cut-off clutch and freewheel, thereby vehicle can be driven by internal-combustion engine and/or electric driver selectively.At this, freewheel can be guaranteed from internal-combustion engine towards the transmission of torque of speed changer direction and prevent transmission of torque in the opposite direction.Thus, cut-off clutch can design elongatedly, and in the situation that appropriate structure space demand can be transmitted very high torque.Double mass flywheel can be arranged between internal-combustion engine and electric driver, and the object for vibration damping in this double mass flywheel also can be furnished with centrifugal force pendulum selectively.Document DE10 2,012 206 680A1 show a kind of mixed power module of similar type, and the different space that each single member, especially bearing or double mass flywheel (torque damper) have been shown in this mixed power module is arranged.Double mass flywheel is arranged in the driving side of cut-off clutch selectively in the rotor of electric driver.
Document WO2011/072653A1 shows and a kind ofly for the drivetrain at Motor Vehicle, is arranged in the torque-transmitting mechanisms between the bent axle of internal-combustion engine and the transmission input shaft of vehicular clutch or speed changer, wherein, this torque-transmitting mechanisms has electric driver, double mass flywheel and with the cut-off clutch of two clutch disks, and two clutch disks of cut-off clutch are radially arranged in the rotor of electric driver.Thus, in the situation that can transmit very high torque to the demand of structure space is very little.Vibration can be subject to damping by double mass flywheel and additional friction element.At this, double mass flywheel is arranged between internal-combustion engine and electric driver and has integrated secondary mass, and friction element engages in other words and is integrated in wherein with double mass flywheel.
Document DE10 2,009 032 336A1 show a kind of for being arranged in the torque-transmitting mechanisms of the drivetrain between the bent axle of internal-combustion engine and the transmission input shaft of speed changer of Motor Vehicle, wherein, this torque-transmitting mechanisms has mutual cut-off clutch and the double mass flywheel between bent axle and transmission input shaft that be in series arranged in.Double mass flywheel is arranged between internal-combustion engine and electric driver, and cut-off clutch is arranged in the rotor of electric driver.Thus, can provide a kind of seldom torque-transmitting mechanisms in axial arrangement space that only needs.Document DE10 2,009 032 331A1 show a kind of torque-transmitting mechanisms of similar type.
Document DE100 36 504B4 show a kind of drivetrain for Motor Vehicle, it has the motor of arranging and connecting with auxiliary unit around the drive axis of drivetrain coaxially, wherein, in motor, be furnished with the flywheel mass unit of the rotor field spider of the rotor that is configured for motor, thereby auxiliary unit can be driven by motor and/or flywheel mass unit selectively.At this, can be additionally one or more can with the clutch disk of flywheel mass element connection on be provided with for making rotational vibrations be subject to the damping mechanism of damping.Thus, can be in the situation that the demand in axial arrangement space be seldom realized to the method for operation of saving energy.
In these first disclosed mechanisms, mostly need sizable axial arrangement space, and under many circumstances, the vibration performance in drivetrain only can follow the shortcoming of high moment of inertia to be improved.
Summary of the invention
Task of the present invention is to provide as lower device, by this device for mixed power application in the situation that to radially and/or the demand of axial structure space seldom, can realize the good vibration performance in the drivetrain of Motor Vehicle.
The present invention is set out by the torque transmitter of the motor vehicle driven by mixed power for driving by internal-combustion engine and electric driver, this torque transmitter be applicable to be arranged in motor vehicle driven by mixed power in the internal-combustion engine and the drivetrain between speed changer of motor vehicle driven by mixed power, this torque transmitter with:
-electric driver, it has especially the rotor around the central longitudinal axis rotation of torque transmitter;
-cut-off clutch, it is for throwing off internal-combustion engine and speed changer;
-centrifugal force pendulum, it is for vibration damping.
The regulation according to the present invention, centrifugal force pendulum is axially arranged in internal rotor.Thus, can reduce in primary side, that is to say the inertia of driving side.Can realize very short startup (restarting) time of internal-combustion engine, this is because centrifugal force pendulum originally needn't accelerate when internal combustion engine start.At this, start and also need energy seldom, this and startup to stop robot device or often determined that (only) uses the city operations of electric driver that advantage is provided explicitly.Internal-combustion engine can directly start by electric driver.In special compact structure pattern, also can provide the torque transmitter with good vibration damping characteristic.
At this, be preferably as follows layout and can be understood as the axial layout at internal rotor, in this arrangement, centrifugal force pendulum does not protrude from rotor about central longitudinal axis, but is at least substantially fully arranged in internal rotor.Rotor is overlapping with centrifugal force pendulum in the axial direction.Thus, on the direction of observation of the radial direction along perpendicular to central longitudinal axis, centrifugal force pendulum is covered by rotor completely.
At this, preferably torque transmitter can be understood as central longitudinal axis as lower axis, along each single component tandem arrangement of this axis, and this axis can be arranged essentially parallel to live axle and extends in other words output shaft.For example, rotor and centrifugal force pendulum can be around central longitudinal axis rotations.
At this, each type that is preferably as follows vibration damper can be interpreted as centrifugal force pendulum, and this vibration damper is applicable to use and make vibration be subject to damping at the torque transmitter for hybrid drive, and itself is not in torque flow in other words in power stream.Centrifugal force pendulum can be configured to make the vibration of torque transmitter itself and/or the vibration in drivetrain to be subject to damping.As the example of centrifugal force pendulum, can mention bifilar pendulum (with the pendulum of two suspension points), wherein, shock-absorption quality swings via bolt, and these bolts can move on the kidney shape rolling rail of pendulum mass inside, wherein, all points of pendulum can be depicted identical geometric locus.
At this, the layout of centrifugal force pendulum does not rely on flywheel, especially double mass flywheel.At this, double mass flywheel can, for example in primary side, that is to say at driving side and be arranged between internal-combustion engine and torque transmitter.Preferably, torque transmitter and the damper without integrated centrifugal force pendulum in other words semielliptic spring damper or linear type spring-damper use in combination, especially to can realize less moment of inertia in primary side.Centrifugal force pendulum in rotor also can be used as for the additional cushions of semielliptic spring damper or linear type spring-damper in other words of the damper also can with integrated centrifugal force pendulum.The centrifugal force pendulum of torque transmitter and damper in other words semielliptic spring damper or linear type spring-damper are at least disengageably disposed axially in rotor to a great extent.Thus, can obtain the elongated especially structural type of torque transmitter.
In layout in rotor at centrifugal force pendulum at electric driver, can utilize the structure space under rotor, thereby centrifugal force pendulum is arranged in such a way at internal rotor, that is, centrifugal force pendulum is fully integrated in rotor in the axial direction.At this, cut-off clutch may be embodied to single plate clutch, especially to provide in the axial direction many especially structure spaces for centrifugal force pendulum.
In order to make required axial arrangement space keep very littlely, can corresponding littlely implement in other words by semielliptic spring damper or linear type spring-damper for the additional damper arranging selectively, the isolation difficulty that wherein, may occur can not rely on transmission types and carrys out balance by the centrifugal force pendulum that is arranged in internal rotor.
At this, be preferably as follows device and can be understood as torque transmitter, this device has not only been born vibration damping function and transmission of torque between internal-combustion engine and speed changer, and has born the switching function switching between the drive unit type different.
At this, be preferably as follows car two and can be understood as hybrid electric vehicle two, this vehicle has at least two drive unit, especially internal-combustion engine and the electric drivers that can interdependently not move to a great extent.Can be provided with other drive units selectively.
At this, be preferably as follows mechanism and can be understood as cut-off clutch, this mechanism can be in the drivetrain of motor vehicle driven by mixed power in motor vehicle driven by mixed power by the first drive unit and the second drive unit is thrown off and can be selectively single or move these drive units in the mode of combination with one another.By cut-off clutch, can drive as follows motor vehicle driven by mixed power by different modes, that is, make torque flow control and combine selectively by internal-combustion engine and electric driver.
At this, the parts that preferably rotate in the stator of electric driver can be understood as the rotor of electric driver.
At this, the transmission types of motor vehicle driven by mixed power can freely be selected.Torque transmitter can be for example with double-clutch speed changer or conventionally engage with automatic transmission.
Selectively, double mass flywheel also can be arranged in rotor, especially in the primary side of centrifugal force pendulum.Here, the flange bracket for supporting rotor is preferably arranged in centrifugal force pendulum side and supports by output shaft (transmission input shaft) in primary side in primary side or primary side.
According to favourable mode of execution, centrifugal force pendulum is connected with rotor.Thus, can provide simple Structural Tectonics, wherein, radially inner at centrifugal force pendulum, axial arrangement space can be for other assemblies.
Preferably, centrifugal force pendulum is especially in being fastened in the radial direction the rotor field spider of rotor.In addition preferably, centrifugal force pendulum has flange bracket, and this flange bracket is connected with rotor in anti-relative rotation by fastening piece.Fastening piece is especially radially arranged and can engaged with rotor or rotor field spider and flange bracket in the radial direction.Flange bracket can have circumferential lateral surface, and this circumferential lateral surface defines the interface of rotor field spider.By circumferential lateral surface, can guarantee the centering of centrifugal force pendulum in rotor field spider.Rotor field spider can have corresponding centering face (especially inner circumferential side face).
According to favourable mode of execution, cut-off clutch has at least one clutch disk, and wherein, clutch disk is disposed axially in internal rotor.Thus, can provide structure compact, sealing itself, wherein, clutch disk can with the flange bracket acting in conjunction of torque transmitter.
Preferably, be not only clutch disk, and other assemblies of cut-off clutch or whole cut-off clutch are all arranged in the rotor of electric driver.Thus, can be provided in layout compact especially on axial direction.Power can be directly transferred in rotor field spider or in the flange being connected with rotor field spider.
According to flexible program, cut-off clutch is implemented as the multiple-disk clutch with at least two clutch disks.Two clutch disks can be provided for transmitting higher torque.Preferably, two clutch disks are arranged in rotor, especially at the driving side of spacer flanger and the outlet side of flange bracket.Selectively, also can use three or more clutch disks, significant but the least possible quantity of clutch disk is only, to make trailing moment keep very little.Preferably, cut-off clutch is arranged in the primary side of spacer flanger, and centrifugal force pendulum is arranged in the primary side close to more from speed changer of spacer flanger.In other words, cut-off clutch is arranged in the primary side of centrifugal force pendulum.By centrifugal force pendulum, in the layout of the transmission side (primary side that is to say outlet side) of cut-off clutch, can realize very short startup (restarting) time of internal-combustion engine, this is because centrifugal force pendulum originally makes to accelerate in internal combustion engine start.
Preferably, centrifugal force pendulum is together with cut-off clutch, and especially the clutch disk of all assemblies, the especially cut-off clutch of cut-off clutch is disposed axially in rotor together.The axial arranged advantage that provide of cut-off clutch in rotor is that motor vehicle driven by mixed power can be driven as follows by different modes, that is, make torque flow be controlled and be combined selectively by internal-combustion engine or electric driver.
According to favourable mode of execution, cut-off clutch is configured to freewheel cut-off clutch.Thus, the function of freewheel can combine with the function of cut-off clutch, wherein, can carry out torque distribution.Freewheel can alleviate the load of cut-off clutch.
At this, the cut-off clutch combining with freewheel can be understood as freewheel cut-off clutch, and wherein, cut-off clutch can be arranged together with freewheel or also can arrange dividually with freewheel in position.Freewheel can be for example for example, be formed or is merged into element of construction axially or radially with central bearing by a kind of locking bearing (by interior ring and outer shroud and be arranged in ball wherein or bearing that roller forms).Preferably, freewheel is also disposed axially in rotor and arranges dividually with cut-off clutch in position.So freewheel is advantageously arranged in the primary side of cut-off clutch.In addition preferably, freewheel is arranged in the primary side of centrifugal force pendulum.Particularly preferably, freewheel is arranged in rotor field spider and jack shaft in other words on the spacer flanger between output shaft.
At this, be preferably as follows mechanism and can be understood as freewheel, this mechanism can guarantee optionally orientation-dependent transmission of torque in other words.Freewheel is guaranteed from internal-combustion engine towards the transmission of torque of speed changer direction and is prevented transmission of torque in the opposite direction.Thus, the space requirement that can be used in cut-off clutch minimizes, and can transmit very high torque for axial structure space demand.In addition, freewheel can move as follows together with cut-off clutch, that is, freewheel comes together to transmit a part for the torque of cut-off clutch.Thus, cut-off clutch may be embodied to and has the demand of axial structure space single plate clutch seldom in the wider scope of the torque that will transmit.
Preferably, freewheel is integrated in spacer flanger or is connected with this spacer flanger, and in addition preferably, freewheel is arranged in the primary side of centrifugal force pendulum.According to flexible program, freewheel is arranged in the primary side of spacer flanger.At this selectively, freewheel can be bearing on live axle together with double mass flywheel.
According to favourable mode of execution, torque transmitter have with protruding pressing plate and with the arm spring of bump bonds.At this, centrifugal force pendulum is arranged in the transmission side (primary side) of arm spring.Thus, at the flange bracket of torque transmitter and the power stream between arm spring, can transmit in stable mode and with the good structure stability of torque transmitter.
Preferably, centrifugal force pendulum is in series arranged in arm spring side (especially in primary side) and has flange bracket, and this flange bracket provides in distolateral abutment face, in this abutment face, can recline for the ring-type element of supporting lever spring.Thus, arm spring can with simple mode and at the demand of the structure space to axial situation lower support seldom between spacer flanger and centrifugal force pendulum.
According to favourable mode of execution, arm spring is bearing on rotor at internal rotor.Thus, in the situation that to the demand of axial structure space seldom, arm spring can connect with (uncoupling) bearing in simple mode.The projection of pressing plate can medially be applied on arm spring in radial direction.This combines good leverage is provided with arm spring radially outer supporting in rotor.(uncoupling) bearing can be in the inner side that is arranged in the radial direction centrifugal force pendulum, especially same at internal rotor in identical axial position.
Arm spring can with free end in other words fringe region be bearing between spacer flanger and ring-type element and at this and can operate as follows,, projection medially acts on arm spring, that is to say in the centre portion between the fringe region inside at arm spring and outside of arm spring.At this, projection can be guided through leave a blank portion or a plurality of portion of leaving a blank in spacer flanger.With another free end fringe region in other words, arm spring can abut on (uncoupling) bearing.Therefore, convex to form a kind of lever supporting element, to can adjust equilibrium of forces.In this layout, can keep to the demand in axial arrangement space seldom.
According to favourable mode of execution, torque transmitter has damping mechanism.Thus, can make in the mode of further improving vibration be subject to damping.Preferably, damping mechanism is arranged in the primary side of cut-off clutch.
At this, be preferably as follows the mechanism that is additional to centrifugal force pendulum setting and can be understood as damping mechanism, this mechanism provides additional flywheel mass and/or additional flexible member.As damping mechanism, for example another centrifugal force pendulum be can use, or the damper with the clutch disk of rigidity flywheel and torsion damping, the flywheel of for example casting flywheel or being made by Drawn Steel also can be used.Selectively, also can use and start pusher side (primary side) to be arranged in cut-off clutch semielliptic spring before.
Preferably, damping mechanism is also arranged in rotor.This damping mechanism can engage or not rely on centrifugal force pendulum and arrange with centrifugal force pendulum.It can for example support by output shaft.
According to favourable mode of execution, rotor is connected with the jack shaft being connected on speed changer by spacer flanger.Thus, can in very little axial space structure, in simple and direct mode, realize the support of rotor and supporting.Spacer flanger can be about the centre that size is arranged in rotor that extends axially of rotor, thereby can realize support symmetrical on output shaft.
At this, be preferably as follows axle and can be understood as jack shaft, this axle can bear torque in primary side from the function of torque transmitter output and can be formed into the interface of speed changer.
At this, be preferably as follows for fastening machine element and can be understood as spacer flanger, this machine element is arranged between other assemblies of torque transmitter and is connected with rotor, and can bear the function of transmission of torque.
Preferably, cut-off clutch is arranged in the driving side (primary side) of spacer flanger at least in part.In addition preferably, centrifugal force pendulum is arranged in the transmission side (outlet side) of spacer flanger.Thus, in these quality one can be arranged in a wherein side of spacer flanger, thereby rotor is had for week of rotor then the favourable mass distribution of speech.
According to favourable mode of execution, torque transmitter has the flange bracket being connected with rotor, and wherein, cut-off clutch and centrifugal force pendulum are arranged in the transmission side of flange bracket.Thus, can on the free end of rotor and thus, with very large leverage and in stable mode, realize the support to rotor.
At this, be preferably as follows for fastening machine element and can be understood as flange bracket, this machine element can supporting rotor and can be supported on the housing of torque transmitter.
According to favourable mode of execution, rotor has rotor field spider, is not only furnished with centrifugal force pendulum, but also is furnished with cut-off clutch in this rotor field spider.Thus, can realize integrated at internal rotor of these two assemblies, and can import in rotor field spider for switching the power of cut-off clutch.
At this, rotor field spider can especially well afterwards be pressed into the assembled being arranged in rotor field spider in rotor.(kraftschl ü ssig) that at least power transmission connects connects and can for example by horizontal pressing (Querpressverband), guarantee.Selectively, also can be provided with shape sealed (Fromschluss) and/or material sealed (Stoffschluss), also can arrange by the mode of combination.
Preferably, the fastening piece that centrifugal force pendulum and/or flange bracket and/or spacer flanger utilize radial arrangement to be orientated in other words assembling is in other words connected with rotor field spider.Thus, rotor can be connected with the assembly that is arranged in internal rotor in simple mode in structure.The fastening piece of radial arrangement can be realized simple assembling on the one hand, can realize weightless supporting on the other hand.Fastening piece can be configured to for example sell.Thus, torque transmitter also can depend on by simple mode type (especially axial) size ground design in other words of cut-off clutch.Another advantage is the gapless connection to all features/components that can carry-over moment.Selectively, these assemblies also can weld together, and especially weld together with rotor field spider.
At this, be preferably as follows machine element and can be understood as rotor field spider, this machine element is radially inwardly configured to holding and fixing and also preferred centering flange or vibration damper or clutch or other machines element.At this, rotor field spider is configured to supporting surface is being provided in both sides in the radial direction and itself is being arranged between rotor and built-in machine element at this.
Preferably, rotor has rotor field spider, and this rotor field spider is especially connected with flange bracket in the side of the sensing internal-combustion engine of rotor.For this reason, rotor field spider can axially protruding with the coefficient part of stator around the section for securing bracket flange from rotor.By projection, fastening piece can inserted in rotor field spider and flange bracket in the radial direction.
Preferably, rotor field spider is bearing on live axle and by spacer flanger and is bearing on output shaft by flange bracket.At this, in spacer flanger, can integratedly there is the device of radial compensation function and moment propagation function, this device is preferably arranged between rotor field spider and output shaft.By this device, can compensate in output shaft and torque transmitter radially staggering between the assembly of rotating transmission device in other words.
Accompanying drawing explanation
In accompanying drawing below, also will to the present invention, at length explain by embodiment.Wherein:
Fig. 1 illustrates according to an embodiment of the invention the part with the torque transmitter of single-deck cut-off clutch with sectional view;
Fig. 2 a illustrates according to the part of the torque transmitter of Fig. 1 with perspective, cut-away view;
Fig. 2 b illustrates the assembly that is arranged in this rotor field spider inside according to the part of the rotor field spider of the torque transmitter of Fig. 1 and torque transmitter with perspective, cut-away view;
Fig. 3 a with schematic cross sectional representation go out according to another embodiment of the present invention with the part that is arranged in the torque transmitter of the double mass flywheel in rotor;
Fig. 3 b is with the publish picture flexible program of embodiment shown in 3a of schematic cross sectional representation;
Fig. 4 with schematic cross sectional representation go out according to another embodiment of the present invention with the part that is arranged in the torque transmitter of the freewheel in rotor;
Fig. 5 a with schematic cross sectional representation go out according to another embodiment of the present invention with being arranged in freewheel in rotor and being arranged in the part of the torque transmitter of the double mass flywheel in rotor;
Fig. 5 b is with the publish picture flexible program of embodiment shown in 5a of schematic cross sectional representation;
Fig. 6 a with schematic cross sectional representation go out according to another embodiment of the present invention with the part that is arranged in the torque transmitter of the radial compensating mechanism in rotor;
Fig. 6 b illustrates the flexible program of torque transmitter shown in Fig. 6 a with sectional view.
In accompanying drawing explanation below, for the identical assembly of function, use identical reference character.As long as do not discuss clearly one of them assembly in an accompanying drawing therein, so just can be with reference in conjunction with at least one other the description of the drawings.
Embodiment
Figure 1 illustrates the torque transmitter 1 with housing 4, flange bracket 5, cut-off clutch 6, spacer flanger 7, centrifugal force pendulum 13, motor 10.Torque transmitter 1 is upper along central longitudinal axis M extension at axial direction (x direction).Motor 10 has stator 11 and rotor 12.Rotor 12 has rotor field spider 12a, and this rotor field spider is connected with spacer flanger 7 with flange bracket 5.Be provided with fastening piece 14.2,14.3 for this reason.Similarly, centrifugal force pendulum 13 is connected with rotor field spider 12a by fastening piece 14.1.Fastening piece 14.1,14.2,14.3, arranging in the radial direction assembling in other words, especially inwardly packs in rotor field spider 12a from outer radial.Fastening piece 14.1,14.2,14.3 is preferably configured to pin or bolt.They all can have identical structural type or differently construct according to the load that will transmit.Selectively, fastening piece also can have screw thread, especially outside thread.But aspect simple assembling, pin is fixedly more favourable.Flange 5,7 and centrifugal force pendulum 13 are arranged in rotor field spider 12 inside about axial direction.
Cut-off clutch 6 has clutch disk 6a, and this clutch disk is arranged in the primary side of flange bracket 5 (outlet side looks up in x side further in other words towards the direction of speed changer).Between clutch disk 6a and spacer flanger 7, be furnished with protruding pressing plate 6b, this pressing plate function is on arm spring 8.For this reason, projection is guided through the 7a of the portion of leaving a blank in spacer flanger 7.Arm spring 8 radially outer in the region of side face with its freely outer edge zone be bearing on rotor field spider 12a.It is arranged in spacer flanger 7 and is bearing between the ring-type element 17 on rotor field spider 12a, can swingingly clamp about rotor field spider 12a in other words.Ring-type element 17 itself abuts on the distolateral abutment face 13a.1 of flange bracket 13a of centrifugal force pendulum 13.On inner fringe region, arm spring 8 abuts on (uncoupling) bearing 15, this bearing can by arm spring 8 operate and with piston 9 actings in conjunction.
The centering face 12a.1 that centrifugal force pendulum 13 abuts in rotor field spider 12a with its flange bracket 13a is upper, and fastening piece 14.1 is through passing through the side face (circumferential lateral surface) of flange bracket 13a.Centrifugal force pendulum 13 has roller 13.1, and this roller is connected with pendulum mass 13.2,13.3.
That rotor field spider 12a has is other (second, third, the 4th and the 5th) centering face 12a.2,12a.3,12a.4,12a.5, on these centering faces, assembly can be bearing in the inner and centering of rotor field spider 12a.Centering face 12a.1,12a.2,12a.3,12a.4,12a.5 are separated from each other by boss respectively, and especially also with different radial spacings, arrange relative to each other.Thus, can make assembling become easily, this is because each assembly can be attached troops to a unit in specific centering face.At this, the axial position of each assembly can limit by boss.The second centering face 12a.2 is provided for supporting spacer flanger 7.The 4th centering face 12a.4 is provided for supporting ring-type element 17.The 5th centering face 12a.5 that can arrange selectively is for example provided for supporting rotor position sensor or speed probe (not shown go out).
At this, for set (first) centering face 12a.1 of centrifugal force pendulum 13, be at built-in centering face farthest in the radial direction, thereby centrifugal force pendulum 13 can be packed in rotor field spider 12a from a side or the opposite side of rotor field spider 12a selectively vertically.
By being formed into the live axle 2 of the interface of internal-combustion engine (not shown), can receiving torque and be delivered on the output shaft 3 of the interface that is formed into speed changer (not shown).Flange bracket 5 is bearing in the bearing device 16 on live axle 2.Cut-off clutch 6 engages with live axle 2 by the 6a.1 of tooth portion.
By centrifugal force pendulum 13 the primary side of spacer flanger 7 and axially the layout in rotor 12 inside compact structure pattern can be provided, by this structural type, can adjust good vibration characteristics.At this, rotor field spider 12a surrounds all primary clusterings that surround in other words this layout.This structural type structurally keeps simply, and this is especially because can guarantee simple assembling by fastening piece 14.1,14.2,14.3 and in conjunction with centering face 12a.1 to 12a.4.
Do not illustrate can primary side the double mass flywheel that connects with torque transmitter 1.At this, live axle 2 is preferably formed into the interface of double mass flywheel.
Cut-off clutch 6 can connect with (unshowned) freewheel.So this freewheel is preferably arranged in the region between jack shaft 3 and spacer flanger 7 on spacer flanger 7.Also the structure space axially and radially that can also use between (uncoupling) bearing 15 and spacer flanger 7 can be used by this way, be for example especially also, in order can cut-off clutch 6 to be designed elongatedly as far as possible (being only designed with clutch disk).
In Fig. 2 a, illustrated with housing 4, rotor 12, rotor field spider 12a, centrifugal force pendulum 13, the torque transmitter 1 that is bearing in flange bracket 5, the clutch disk 6a on live axle 2 and is bearing in the spacer flanger 7 on output shaft 3.Centrifugal force pendulum 13 is assemblies that (in primary side) arranges farthest in x direction of torque transmitter 1 and disengageably arranges with other flywheel masses or damper in position.
Rotor field spider 12a has been shown in Fig. 2 b, and flange bracket 5 is fastened in this rotor field spider by fastening piece 14.3, and spacer flanger 7 is fastened in this rotor field spider by fastening piece 14.2.Flange bracket 13a is fastening by fastening piece 14.1.These fastening pieces can upwards distribute at rotor field spider 12a in week, especially the pitch arrangement to remain unchanged.Fastening piece 14.1,14.2,14.3 is configured to pin, and they radially inject rotor field spider 12a and flange 5,7,13a from outside.Flange 5,7,13a the has bearing device corresponding with pin be blind hole in other words, and rotor field spider 12a has the through hole corresponding with pin.The centering making progress in week, can be undertaken by these holes and pin.These pins also can have internal thread selectively, especially for they being disassembled again.Arm spring 8 is inwardly being stretched fartherly than centrifugal force pendulum 13 in the radial direction.Centrifugal force pendulum 13 has a plurality of rollers 13.1, these roller wheel bearing pendulum masses 13.2 and itself can moving on the kidney shape rolling rail of pendulum mass or flange bracket 13a inside.
In Fig. 3 a, illustrated and had with stator 11 and the torque transmitter 1 that is bearing in the electric driver of the rotor 12 in rotor field spider 12a, wherein, in rotor field spider 12a, be furnished with centrifugal force pendulum 13.Rotor field spider 12a supports by flange bracket 5, and this flange bracket is set directly at centrifugal force pendulum 13 sides in primary side.In addition, rotor field spider 12a is connected with spacer flanger 7, and this spacer flanger is connected with output shaft 3.Live axle 2 (being illustrated by arrow) and output shaft 3 extend along central longitudinal axis M at least approx.At output shaft 3 upper supports, have double mass flywheel 18, it is inner that this double mass flywheel is disposed axially in rotor field spider 12a equally.Flange bracket 5 provides in the axial direction the structure space in primary side in the layout of the primary side of spacer flanger 7, thereby can provide position for double mass flywheel 18.
Shown in Fig. 3 b, can arrange flange bracket 5 by which kind of alternative mode: to the support of rotor field spider 12, also can realize by being arranged in the flange bracket 5 of the primary side of centrifugal force pendulum 13.
Torque transmitter 1 shown in Figure 4, in this torque transmitter, rotor field spider 12a supports by flange bracket 5, and this flange bracket is arranged on the primary side of spacer flanger 7.Spacer flanger 7 is connected with output shaft 3 by freewheel 19.Live axle 2 (being illustrated by arrow) and output shaft 3 extend along central longitudinal axis M at least approx.Freewheel 19 is connected with output shaft 3 and is bearing on live axle 2.Double mass flywheel 18 and live axle 2 are connected and are arranged in the primary side of other assemblies of torque transmitter 1.
The torque transmitter 1 with the double mass flywheel 18 being bearing on output shaft 3 has been shown in Fig. 5 a, it is inner that this double mass flywheel is disposed axially in rotor field spider 12a, in addition, be provided with freewheel 19, this freewheel is arranged in the primary side of spacer flanger 7 and engages and be bearing on output shaft 3 together with double mass flywheel 18 with spacer flanger 7.Other assemblies are arranged substantially as described in conjunction with Fig. 3 a.
Torque transmitter 1 with freewheel 19 has been shown in Fig. 5 b, and this freewheel is as arranging shown in Fig. 5 a.Shown in Fig. 5 b, can arrange flange bracket 5 by which kind of alternative mode.Flange bracket 5 and other assemblies are arranged substantially as described in conjunction with Fig. 3 b.
In Fig. 6 a, illustrated and had with stator 11 and the torque transmitter 1 that is bearing in the electric driver of the rotor 12 in rotor field spider 12a, wherein, in rotor field spider 12a, be furnished with centrifugal force pendulum 13.Rotor field spider 12a is bearing on live axle 2 (being illustrated by arrow) by flange bracket 5.In addition, rotor field spider 12a is connected with spacer flanger 7, and this spacer flanger is connected with output shaft 3.Live axle 2 and output shaft 3 extend along central longitudinal axis M at least approx.At live axle 2 upper supports, have double mass flywheel 18, this double mass flywheel is arranged in the primary side of other assemblies of torque transmitter 1.In spacer flanger 7, be integrated with radial compensating mechanism 20, by this radial compensating mechanism, can compensate live axle 2 especially radially staggering with respect to output shaft 3.Radial compensating mechanism 20 is arranged in the section radially extending of spacer flanger 7 and has spring element, when output shaft 3 and rotor field spider 12a (necessary) displacement the and/or when damping of improvement should be provided mutually in the axial direction, this spring element can be compressed or be stretched.
The torque transmitter 1 with the arrangement of components as in the torque transmitter 1 at Fig. 6 a has been shown in Fig. 6 b, wherein, double mass flywheel has not been set.
Reference numerals list
1 torque transmitter
2 interfaces (live axle is especially connected with bent axle) to internal-combustion engine
3 interfaces (jack shaft is output shaft in other words) to speed changer
4 housings
5 flange brackets/tray deck is matching board in other words
6 cut-off clutches
The clutch disk of 6a cut-off clutch
The tooth portion of 6a.1 clutch disk
6b is with protruding pressing plate
7 spacer flangers (output terminal flange)
The leave a blank portion of 7a in spacer flanger
8 arm springs
9 pistons
10 electric drivers
The stator of 11 electric drivers
The rotor of 12 electric drivers
12a rotor field spider
12a.1 (first) centering face
(second) centering face that 12a.2 is other
(the 3rd) centering face that 12a.3 is other
(the 4th) centering face that 12a.4 is other
(the 5th) centering face that 12a.5 is other
13 centrifugal force pendulums/vibration damper
13a flange bracket
13a.1 is in distolateral abutment face
13.1 rollers
13.2 pendulum masses
13.3 pendulum masses
14.1 fastening pieces
14.2 fastening pieces
14.3 fastening pieces
15 (uncoupling) bearing
16 bearing devices on live axle
17 ring-type elements
18 double mass flywheels
19 freewheels
20 radial compensating mechanisms
M central authorities longitudinal axis
Claims (10)
1. the torque transmitter (1) for the motor vehicle driven by mixed power that can drive by internal-combustion engine and electric driver (10), described torque transmitter be applicable to be arranged in described motor vehicle driven by mixed power in the internal-combustion engine and the drivetrain between speed changer of motor vehicle driven by mixed power, described torque transmitter with:
-electric driver (10), described electric driver has especially the rotor (12) around central longitudinal axis (M) rotation of torque transmitter;
-cut-off clutch (6), described cut-off clutch is for throwing off internal-combustion engine and speed changer;
-centrifugal force pendulum (13), described centrifugal force pendulum is for vibration damping;
It is characterized in that, described centrifugal force pendulum is disposed axially in internal rotor.
2. torque transmitter according to claim 1, is characterized in that, centrifugal force pendulum (13) is connected with rotor (12).
3. torque transmitter according to claim 1 and 2, is characterized in that, cut-off clutch (6) has at least one clutch disk (6a), and wherein, clutch disk is disposed axially in rotor (12) inside.
4. according to the torque transmitter described in claim 1,2 or 3, it is characterized in that, cut-off clutch is configured to freewheel cut-off clutch.
5. according to the torque transmitter described in any one in claim 1 to 4, it is characterized in that, torque transmitter have with protruding pressing plate (6b) and with the arm spring (8) of described bump bonds, and centrifugal force pendulum (13) is arranged in the transmission side of arm spring.
6. torque transmitter according to claim 5, is characterized in that, arm spring (8) is bearing on rotor at internal rotor.
7. according to the torque transmitter described in any one in claim 1 to 6, it is characterized in that, torque transmitter has damping mechanism.
8. according to the torque transmitter described in any one in claim 1 to 7, it is characterized in that, rotor is connected with the jack shaft (3) that is connected to speed changer by spacer flanger (7).
9. according to the torque transmitter described in any one in claim 1 to 8, it is characterized in that, torque transmitter has the flange bracket (5) being connected with rotor, and wherein, cut-off clutch (6) and centrifugal force pendulum (13) are arranged in the transmission side of flange bracket.
10. according to the torque transmitter described in any one in claim 1 to 9, it is characterized in that, rotor has rotor field spider (12a), and centrifugal force pendulum (13) and cut-off clutch (6) are arranged in described rotor field spider.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013207757 | 2013-04-29 | ||
| DE102013207757.2 | 2013-04-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104121325A true CN104121325A (en) | 2014-10-29 |
| CN104121325B CN104121325B (en) | 2017-12-22 |
Family
ID=51685240
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410177918.3A Active CN104121325B (en) | 2013-04-29 | 2014-04-29 | Torque transmission device with separating clutch and centrifugal force pendulum for hybrid vehicle |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104121325B (en) |
| DE (1) | DE102014206330A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107636334A (en) * | 2015-07-13 | 2018-01-26 | 舍弗勒技术股份两合公司 | Clutch module for a drive train of a motor vehicle |
| CN108731861A (en) * | 2017-04-17 | 2018-11-02 | 青岛鼎通新能源科技有限公司 | A kind of centrifugal force permanent torque output device |
| CN109416114A (en) * | 2016-06-30 | 2019-03-01 | Zf腓特烈斯哈芬股份公司 | Torque transmission device |
| CN110431031A (en) * | 2017-03-06 | 2019-11-08 | 舍弗勒技术股份两合公司 | Hybrid module for a drive train of a hybrid vehicle and such a drive train |
| CN107054052B (en) * | 2015-12-22 | 2021-12-24 | 舍弗勒技术股份两合公司 | Hybrid powertrain system for use in a hybrid vehicle |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102015209898A1 (en) | 2015-05-29 | 2016-12-01 | Volkswagen Aktiengesellschaft | Hybrid drive module for a motor vehicle |
| DE102015215897A1 (en) | 2015-08-20 | 2017-02-23 | Schaeffler Technologies AG & Co. KG | Coupling device for hybrid drive |
| DE102015225048A1 (en) | 2015-12-14 | 2017-06-14 | Schaeffler Technologies AG & Co. KG | Decoupled centrifugal pendulum for a device for transmitting torque |
| DE102016211954A1 (en) | 2016-06-30 | 2018-01-04 | Zf Friedrichshafen Ag | The torque transfer device |
| DE102017219476A1 (en) | 2017-06-20 | 2018-12-20 | Zf Friedrichshafen Ag | Torque transmitting assembly |
| DE102017127577A1 (en) | 2017-11-22 | 2019-05-23 | Schaeffler Technologies AG & Co. KG | Coupling unit for a drive train with positive coupling and hybrid module with coupling unit as separating clutch |
| DE102019105492A1 (en) | 2018-04-05 | 2019-10-10 | Schaeffler Technologies AG & Co. KG | Torsional vibration damper of a hybrid drive module with internal damper and centrifugal pendulum |
| DE102018115310A1 (en) | 2018-06-26 | 2020-01-02 | Schaeffler Technologies AG & Co. KG | Torque transmission device with a control system for determining the direction of rotation of the rotor |
| DE102019102108A1 (en) | 2019-01-29 | 2020-07-30 | Schaeffler Technologies AG & Co. KG | Hybrid module with an output component |
| DE102020131760A1 (en) * | 2020-12-01 | 2022-06-02 | Schaeffler Technologies AG & Co. KG | hybrid module |
| DE102020131765A1 (en) * | 2020-12-01 | 2022-06-02 | Schaeffler Technologies AG & Co. KG | hybrid module |
| DE102021122703A1 (en) | 2021-09-02 | 2023-03-02 | Schaeffler Technologies AG & Co. KG | Hybrid module with an axis of rotation for a drive train |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6302253B1 (en) * | 1999-03-02 | 2001-10-16 | Mannesmann Sachs Ag | Torque transmission unit |
| CN101143558A (en) * | 2006-09-11 | 2008-03-19 | 通用汽车公司 | Light hybrid vehicle configuration |
| CN101184645A (en) * | 2005-07-05 | 2008-05-21 | 爱信艾达株式会社 | Hybrid vehicle drive device |
| US20090054203A1 (en) * | 2007-06-20 | 2009-02-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydrodynamic coupling device for hybrid vehicles |
| CN102149942A (en) * | 2008-09-11 | 2011-08-10 | 卢克资产管理有限责任公司 | Torque transmission unit |
| CN102414040A (en) * | 2009-05-06 | 2012-04-11 | 舍弗勒技术两合公司 | Dual clutch comprising torsional vibration damper |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10036504B4 (en) | 1999-08-02 | 2011-05-19 | Schaeffler Technologies Gmbh & Co. Kg | powertrain |
| DE102009032336A1 (en) | 2008-07-28 | 2010-02-04 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device for use in drive train of vehicle, has two-mass flywheel arranged at crankshaft-side and separating clutch arranged at transmission input shaft-side, where flywheel and clutch are arranged in series |
| DE102009032331A1 (en) | 2008-07-28 | 2010-02-04 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device for drive train of vehicle between crankshaft of internal combustion engine and gearbox input shaft of gearbox, has separation clutch and dual-mass flywheel |
| DE102010054545A1 (en) | 2009-12-17 | 2011-08-25 | Schaeffler Technologies GmbH & Co. KG, 91074 | Torque transfer device |
| CN103298638B (en) | 2010-12-21 | 2016-08-24 | 舍弗勒技术股份两合公司 | Hybrid module for a vehicle drive train |
| EP2704916A1 (en) | 2011-05-05 | 2014-03-12 | Schaeffler Technologies AG & Co. KG | Torque transmission device |
| DE112012001979A5 (en) | 2011-05-05 | 2014-01-23 | Schaeffler Technologies AG & Co. KG | Hybrid module for a drive train of a vehicle |
-
2014
- 2014-04-02 DE DE102014206330.2A patent/DE102014206330A1/en not_active Ceased
- 2014-04-29 CN CN201410177918.3A patent/CN104121325B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6302253B1 (en) * | 1999-03-02 | 2001-10-16 | Mannesmann Sachs Ag | Torque transmission unit |
| CN101184645A (en) * | 2005-07-05 | 2008-05-21 | 爱信艾达株式会社 | Hybrid vehicle drive device |
| CN101143558A (en) * | 2006-09-11 | 2008-03-19 | 通用汽车公司 | Light hybrid vehicle configuration |
| US20090054203A1 (en) * | 2007-06-20 | 2009-02-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydrodynamic coupling device for hybrid vehicles |
| CN102149942A (en) * | 2008-09-11 | 2011-08-10 | 卢克资产管理有限责任公司 | Torque transmission unit |
| CN102414040A (en) * | 2009-05-06 | 2012-04-11 | 舍弗勒技术两合公司 | Dual clutch comprising torsional vibration damper |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107636334B (en) * | 2015-07-13 | 2020-04-07 | 舍弗勒技术股份两合公司 | Clutch module for a drive train of a motor vehicle |
| CN107709071A (en) * | 2015-07-13 | 2018-02-16 | 舍弗勒技术股份两合公司 | Hybrid module for a drive train of a motor vehicle |
| CN107743452A (en) * | 2015-07-13 | 2018-02-27 | 舍弗勒技术股份两合公司 | Hybrid module for a drive train of a motor vehicle |
| CN107636334A (en) * | 2015-07-13 | 2018-01-26 | 舍弗勒技术股份两合公司 | Clutch module for a drive train of a motor vehicle |
| US11046166B2 (en) | 2015-07-13 | 2021-06-29 | Schaeffler Technologies Ag & Co Kg | Coupling module for a drive train of a motor vehicle |
| CN107709071B (en) * | 2015-07-13 | 2020-08-04 | 舍弗勒技术股份两合公司 | Hybrid module for a drive train of a motor vehicle |
| CN107054052B (en) * | 2015-12-22 | 2021-12-24 | 舍弗勒技术股份两合公司 | Hybrid powertrain system for use in a hybrid vehicle |
| CN109416114A (en) * | 2016-06-30 | 2019-03-01 | Zf腓特烈斯哈芬股份公司 | Torque transmission device |
| CN109416114B (en) * | 2016-06-30 | 2022-04-15 | Zf腓特烈斯哈芬股份公司 | Torque transmission device |
| CN110431031A (en) * | 2017-03-06 | 2019-11-08 | 舍弗勒技术股份两合公司 | Hybrid module for a drive train of a hybrid vehicle and such a drive train |
| CN110431031B (en) * | 2017-03-06 | 2022-10-04 | 舍弗勒技术股份两合公司 | Hybrid module for a drive train of a hybrid vehicle and such a drive train |
| CN108731861A (en) * | 2017-04-17 | 2018-11-02 | 青岛鼎通新能源科技有限公司 | A kind of centrifugal force permanent torque output device |
| CN108731861B (en) * | 2017-04-17 | 2024-02-09 | 青岛鼎通新能源科技有限公司 | Centrifugal force constant torque output device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102014206330A1 (en) | 2014-10-30 |
| CN104121325B (en) | 2017-12-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104121325A (en) | Torque transmission device with cut-off clutch and centrifugal pendulum of hybrid vehicle | |
| US8317006B2 (en) | Double clutch comprising a torsional vibration damper | |
| CN108138900B (en) | Torsional vibration damper and hybrid drive train | |
| US9963140B2 (en) | Hybrid module and drive train having such a module | |
| US11413952B2 (en) | Hybrid module and a drive arrangement for a motor vehicle | |
| US7992661B2 (en) | Hybrid vehicle drive device | |
| JP5661743B2 (en) | Twin clutch with torsional vibration damper | |
| CN105408663B (en) | Turbine torsional vibration damper, converter and torque transmission device | |
| US8651965B2 (en) | Vibration damping device | |
| CN216111941U (en) | Torsional vibration damper with rotating shaft for a drive train | |
| US20140094341A1 (en) | Hybrid module for a drivetrain of a vehicle | |
| CN106415056A (en) | Torque transmission apparatus for hybrid vehicle | |
| CN103596789A (en) | Device for transmitting torque | |
| US20110241500A1 (en) | Drive train for a motor vehicle | |
| US9840139B2 (en) | Structural unit for a hybrid powertrain | |
| US7717792B2 (en) | Torsional detuner | |
| US20080006502A1 (en) | Clutch arrangement for the drive train of a vehicle | |
| US10434865B2 (en) | Hybrid drive module for a motor vehicle | |
| CN103109101A (en) | Double clutch | |
| US11280375B2 (en) | Torsion damping assembly and motor vehicle | |
| CN114083980A (en) | Hybrid module for a drive train having a rotational axis | |
| US20170021713A1 (en) | Transmission assembly for a hybrid vehicle equipped with a pendulum damper | |
| KR20170019452A (en) | Clutch disk and friction clutch system | |
| EP3798465A1 (en) | Torsional vibration damper | |
| KR101163749B1 (en) | Torque converter for hybrid electric vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C53 | Correction of patent of invention or patent application | ||
| CB02 | Change of applicant information |
Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES AG & CO.KG Address before: German Herzogenaurach Applicant before: SCHAEFFLER TECHNOLOGIES GmbH & Co.KG |
|
| COR | Change of bibliographic data |
Free format text: CORRECT: ADDRESS; FROM: Free format text: CORRECT: APPLICANT; FROM: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG TO: SCHAEFFLER TECHNOLOGY GMBH + CO. KG |
|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |