WO2002018819A1 - Accouplement hydrodynamique, systeme d'alimentation en moyens de production pour accouplement hydrodynamique et ensemble de demarrage dote d'un tel accouplement - Google Patents

Accouplement hydrodynamique, systeme d'alimentation en moyens de production pour accouplement hydrodynamique et ensemble de demarrage dote d'un tel accouplement Download PDF

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Publication number
WO2002018819A1
WO2002018819A1 PCT/EP2001/008185 EP0108185W WO0218819A1 WO 2002018819 A1 WO2002018819 A1 WO 2002018819A1 EP 0108185 W EP0108185 W EP 0108185W WO 0218819 A1 WO0218819 A1 WO 0218819A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
turbine wheel
space
starting unit
hydrodynamic
Prior art date
Application number
PCT/EP2001/008185
Other languages
German (de)
English (en)
Inventor
Heinz Höller
Reinhard Kernchen
Achim Menne
Werner Klement
Original Assignee
Voith Turbo Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE10110078A external-priority patent/DE10110078A1/de
Priority claimed from EP01106979A external-priority patent/EP1184600A1/fr
Application filed by Voith Turbo Gmbh & Co. Kg filed Critical Voith Turbo Gmbh & Co. Kg
Priority to BR0113576-7A priority Critical patent/BR0113576A/pt
Priority to JP2002523507A priority patent/JP2004507692A/ja
Priority to EP01955352A priority patent/EP1313966A1/fr
Priority to US10/363,115 priority patent/US20040011032A1/en
Publication of WO2002018819A1 publication Critical patent/WO2002018819A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic 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
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit
    • 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
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit
    • F16D33/16—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by means arranged externally of the coupling or clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/18—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/14—Control of torque converter lock-up clutches

Definitions

  • the invention relates to a hydrodynamic coupling, in particular with the features from the preamble of claim 1; furthermore, a resource supply system for a hydrodynamic clutch and a starting unit with a hydrodynamic clutch.
  • Starting units for use in manual transmissions, automated manual transmissions or automatic transmissions are known in a large number of designs. These usually include a hydrodynamic component in the form of a hydrodynamic speed / torque converter or a hydrodynamic clutch.
  • a hydrodynamic component in the form of a hydrodynamic speed / torque converter or a hydrodynamic clutch.
  • a possible design of a starting unit for use in transmissions with a hydrodynamic coupling reference is made to the publication DE 198 04 635 A1. This discloses an embodiment of a starting unit with a small axial length, comprising a pump wheel and a turbine wheel, which together form a toroidal working space, the pump wheel being arranged on the motor output side, ie the turbine wheel being arranged spatially between an input of the starting unit and the pump wheel.
  • the pump wheel is rotatably connected to the input or to a drive coupled to it via an element which simultaneously forms the pump wheel shell.
  • a lock-up clutch is provided, which is connected in parallel to the hydrodynamic clutch. This enables power transmission from the entrance of the start-up unit to the exit bypassing the hydrodynamic component.
  • the lockup clutch is arranged as a separate component next to the pump wheel and turbine wheel unit.
  • the starting unit comprises a device for damping vibrations, which is arranged in a diameter range which is arranged above the radially outer dimension of the toroidal working space of the hydrodynamic coupling and is part of the lock-up clutch or forms a coupling element.
  • the device for damping vibrations is arranged essentially in the area of a plane or slightly offset from one another with the hydrodynamic coupling.
  • the invention is therefore based on the object of developing a starting unit of the type mentioned at the outset, comprising a hydrodynamic clutch and a lock-up clutch which can be connected in parallel, and their individual elements in such a way that they require very little installation space in the axial direction, and a small number of components and the Summary of functional elements is characterized.
  • the design effort should be kept as low as possible.
  • a hydrodynamic coupling with two paddle wheels - a pump wheel and a turbine wheel - which together form a toroidal working space comprises a pump wheel shell which is coupled non-rotatably to the pump wheel and which connects the turbine wheel in the axial direction with the formation of a first resource guide channel or space encloses. Furthermore, a second operating medium guide channel or space is provided, which opens in the area of the inner diameter of the toroidal work space or below it. According to the invention, the first and second equipment guide duct or space can be used either as feed or drain duct or space to the toroidal work space. Through this optional change in the function of the individual resource management channels or. In spaces, the flow direction of the hydrodynamic coupling can be changed between centripetal and centrifugal in a simple manner.
  • the solution according to the invention forms the basic design requirement for the construction of a hydrodynamic coupling for the creation of a starting unit with a minimal axial length when used in starting units with a lock-up clutch and pressure build-up for the lock-up clutch via the operating resources of the hydrodynamic coupling.
  • the resource system assigned to the hydrodynamic clutch comprises a resource supply source and a first connection to the Coupling with the first resource routing channel or room and a second connection for coupling with the second resource routing channel or room.
  • means are provided for optionally changing the flow direction of the hydrodynamic coupling by assigning the function of the inlet or the outlet to the two operating medium supply channels or rooms.
  • connection is not only to be understood as a constructive element but also with regard to its function as a functional element. This refers to the transition between the equipment guide channels or spaces of the hydrodynamic coupling and the connecting lines to the equipment source. Individual elements of the equipment supply system may or may not be part of the hydrodynamic coupling.
  • the means comprise a valve device with at least two switch positions.
  • a first switch position is characterized by the coupling between the inlet and the first resource management channel or space and drain and the second resource guide channel or space
  • the second switch position is characterized by the coupling between the inlet and second resource guide channel or space and drain and the first resource guide channel or space.
  • Both resource management channels - or rooms are preferably coupled to one another via an open circuit.
  • the design of the hydrodynamic coupling is a fluid coupling, that is, a component which, when transmitting power between an input and an output, only permits a speed change, ie is free of a change in the torque compared to a converter and is therefore necessarily coupled to the speed.
  • These can be regulated or unregulated.
  • Controlled hydrodynamic clutches are clutches in which the degree of filling can be changed during operation between full filling and emptying, whereby the power consumption and thus the transmission capacity of the coupling can be adjusted and, when used in vehicles, a stepless load-dependent speed control of the drive machine and / or output side is made possible
  • the hydrodynamic clutch can be designed as a clutch with a toroidal working space, which is formed by a primary blade wheel functioning as a pump wheel and a secondary blade wheel functioning as a turbine wheel, or as a so-called double clutch, ie with two toroidal working spaces formed by the primary blade wheel and secondary blade wheel.
  • the controllability takes place primarily via the change in the mass flow, ie the influencing of the degree of filling in the work space or the equipment circulation in the Working circuit.
  • the degree of filling of the hydrodynamic coupling is preferably controlled and / or regulated via a pressure control. Coupled with the change in the degree of filling is the change in the absolute pressure of the toroidal work space. For this reason, partial filling states can be adjusted by changing the absolute pressure. ⁇
  • This free adjustability makes it possible to control optimized operating points in the map of the drive machine with regard to different criteria, for example energy consumption and pollutant emissions.
  • the starting unit designed according to the invention a hydrodynamic coupling with the features of claim 1 comprises an input that can be coupled to a drive and an output that can be coupled to an output.
  • the hydrodynamic coupling is arranged between the entrance and the exit.
  • a so-called impeller shell is assigned to the impeller, which is connected to it in a rotationally fixed manner and encloses the turbine impeller in the axial direction to form a first operating means guide channel or space.
  • the pump wheel shell can be made in one piece with the pump wheel, but preferably multi-part designs are used, the rotationally fixed connection being effected via corresponding connecting elements or other coupling options.
  • the hydrodynamic coupling a second resource guide channel or space, which opens in the area of the inner diameter of the toroidal work space or below it.
  • the first and second equipment guide duct or space can be used either as feed or drain duct or space to the toroidal work space.
  • the starting unit further comprises a switchable clutch, in particular a lock-up clutch, which can be connected in parallel to the hydrodynamic clutch. This means that, as a rule, especially for use in automated gearboxes, during a large part of the operation of the starting unit, the power transmission takes place via only one of the two elements - hydrodynamic clutch or lock-up clutch.
  • the power transmission takes place via a hydrodynamic power branch taking advantage of the hydrodynamic power transmission, while in the second case the power transmission takes place essentially mechanically through the mechanical coupling.
  • both elements are in engagement at least in the transition area, ie when switching between hydrodynamic and mechanical power branch.
  • this joint intervention is of limited duration and should not exceed certain predefined times.
  • the lock-up clutch is designed as a mechanical clutch, preferably in a disk design.
  • the lock-up clutch comprises at least a first clutch element in the form of a first clutch plate and a second clutch element in the form of a second clutch plate at least indirectly, that is to say can be brought into operative connection with one another in a frictionally locking manner either directly or indirectly via further transmission means.
  • Integration of components of the lock-up clutch in the hydrodynamic component is provided.
  • a clutch element usually a first clutch disc
  • the clutch disks are assigned means for generating a contact pressure and thus for generating an at least indirect frictional connection between the first clutch disk and the second clutch disk.
  • the solution according to the invention enables a starting unit to be designed with very little space requirement in the axial direction, since here already existing components are simultaneously entrusted with the takeover of the function of the other element.
  • the means for generating a contact pressure comprise at least one piston element which can be pressurized with pressure medium. This can be assigned separately to the clutch discs. In a particularly compact and thus advantageous embodiment, however, the turbine wheel is used as a piston element.
  • the pressure chamber for acting on the piston element is formed by the part of the toroidal working chamber enclosed by the turbine wheel.
  • a counterforce is required when the turbine wheel is axially displaceable, which fixes the turbine wheel in its position in relation to the pump blade wheel.
  • this counterforce is generated by equipment supplied to the work space, which is guided along the outer circumference of the turbine wheel between the individual clutch disks of the lock-up clutch in the area of the parting plane between the pump wheel and turbine wheel in the area of the outer diameter of the toroidal work space and is introduced into the pump wheel from there and flows through the hydrodynamic clutch centripetal.
  • both lie Clutch disks of the switchable clutch close to each other.
  • the remaining gap in the 10th-mm range serves as a throttling point for the equipment flowing through.
  • This throttling point establishes a pressure difference between the piston surfaces, from which the contact pressure required for opening and closing for the bypass results.
  • this can be implemented in designs with a rotationally fixed connection and axial displacement by pretensioning the turbine wheel, for example by means of at least one spring device. Analogously, this is also possible with the elastic connection of the turbine wheel to the outlet in the axial direction.
  • the counterforce which is caused between the clutch discs by guiding the operating fluid in the case of a centripetal flow and is effective on the turbine wheel, is eliminated.
  • the operating medium is now fed to the toroidal working chamber in the area of the inner circumference and the pressure force generated by the operating medium on the turbine wheel causes the turbine wheel to be displaced or tilted in the direction away from the pump wheel, the clutch disc, which is connected to the turbine wheel in a rotationally fixed manner, frictionally connected to the clutch disc coupled to the pump wheel shell is brought into operative connection.
  • the spatial arrangement is viewed in the axial direction next to the toroidal work space or behind it.
  • the arrangement in the radial direction is characterized by external and internal dimensions, which are preferably in the range between the outer and the inner diameter of the toroidal working space.
  • the friction surfaces, which are formed by the clutch disks, are preferably aligned parallel to the parting plane between the pump wheel and the turbine wheel, so that the required contact pressure can be kept as low as possible; Manufacturing tolerances can be compensated for without problems.
  • the rotationally fixed coupling to the turbine wheel is preferably carried out directly on the rear of the part of the turbine wheel which forms the toe.
  • the rotationally fixed connection of the individual clutch disks to the turbine wheel and the pump wheel or the pump wheel shell can also be realized in different ways. Are conceivable
  • the friction surface can be directly from the clutch disc, i. H. in the former case are formed by the outside of the turbine wheel and an inner surface of the pump wheel shell and in the second case by the separate component or by a friction lining assigned to the outer circumference of the turbine wheel or the individual clutch disks.
  • the starting unit comprises a device for damping vibrations, in particular a torsional vibration damper.
  • a device for damping vibrations is for hydrodynamic component in the form of the hydrodynamic coupling and the bypass coupling preferably arranged in series.
  • the device for damping vibrations is arranged between the turbine wheel and the outlet.
  • the turbine wheel is coupled to the input of the device for damping vibrations or the input of the device for damping vibrations is connected in a rotationally fixed manner to the pump wheel via the pump wheel shell via the frictional connection when the hydrodynamic power branch is bridged.
  • the device for damping vibrations is viewed in the axial direction essentially in the area or in one plane with the hydrodynamic component.
  • the device for damping vibrations is arranged in the radial direction within the diameter describing the inner circumference of the part of the hydrodynamic coupling forming the toroidal working space. With this design, in addition to a particularly short axial length, the space available in the radial direction is optimally utilized. There are no restrictions with regard to the design of the device for damping vibrations, ie any type of vibration damper is conceivable. Devices for damping vibrations, which are based only on friction damping, or hydraulic damping devices are used, for example.
  • the design as a hydraulic damping device comprises, in addition to a primary part and a secondary part, which can be rotatably coupled to one another for the purpose of torque transmission and can be rotated relative to one another in the circumferential direction, means for spring and / or damping coupling between the primary part and the secondary part.
  • the means for damping coupling comprise chambers which can be filled with hydraulic fluid and into which vibrations are displaced.
  • the device for damping vibrations must be can only be designed for the output torque on the turbine wheel, which is why the device for damping vibrations in the radial and axial directions is very small and generally does not increase the dimensions of the starting unit specified by the hydrodynamic component.
  • the solution according to the invention is suitable for use in manual transmissions, in particular automatic transmissions, but also transmissions with a continuously variable transmission part (CVT), for example in the form of traction mechanism transmissions and toroidal transmissions.
  • CVT continuously variable transmission part
  • the starting unit can be used as Unit can be traded separately pre-assembled.
  • the connection to the transmission is made by integration in the transmission housing or series connection with switching stages, in both cases the coupling can be realized, for example, by plugging onto a shaft that can be coupled with subsequent stages or a continuously variable transmission part.
  • the starting unit according to the invention is suitable for use in drive trains in stationary systems as well as vehicles.
  • Figures 1a and 1b illustrate the basic principle of the optional change of the flow direction of a hydrodynamic clutch according to the invention
  • Figure 2a illustrates an advantageous embodiment of a starting unit according to the invention
  • Figure 2b illustrates a detail according to Figure 2a
  • FIG. 3 illustrates an advantageous embodiment according to
  • Figure 4 illustrates an advantageous embodiment of a
  • FIGS. 6 and 7 show a schematically highly simplified representation
  • FIGS. 1a and 1b illustrate the basic principle of the functional changes by changing the flow through a hydrodynamic clutch 1 in a schematic, simplified representation.
  • This comprises a primary wheel, which is generally referred to as an impeller 2, and a turbine wheel 3, which is referred to as a secondary wheel. in which a closed working circuit 5 is formed by circulating the operating medium during the operation of the hydrodynamic coupling.
  • the primary wheel 2 is coupled in a rotationally fixed manner to a pump wheel shell 6, which surrounds the turbine wheel 3 in the axial direction.
  • the pump wheel shell 6 encloses the turbine wheel 3 in such a way that at least one operating medium guide channel or space 9 for guiding operating medium is formed between the outer periphery 7 of the turbine wheel and the inner contour 8 of the pump wheel shell.
  • the hydrodynamic coupling 1 is assigned at least one operating medium guide channel or chamber 12, which enables the operating medium to be fed to the toroidal working chamber 5 in the centrifugal direction.
  • the equipment guide duct - or room 12 can be a Act line or specially trained and incorporated channels in the adjacent construction.
  • each of the equipment guide channels is designed in such a way that, in addition to supplying equipment to the toroidal work space 4, they can also be used for removal, ie, it is connected to at least one entry and / or exit from the toroidal work space. It is irrelevant in which area the equipment emerges from the toroidal work space 4.
  • the two equipment guide channels or rooms 9 and 12 can be used either as an inlet or outlet, so that the direction of flow is also changed.
  • means are provided for optionally changing the flow direction 13 of the hydrodynamic clutch 1.
  • Flow direction change means are referred to.
  • these include a valve device which interchanges the function of the described operating medium channels or operating medium guide rooms with regard to their function inlet or outlet.
  • the valve device is designed as a 4/2-way valve device 14.
  • the second valve position of the valve device 14 shown in FIG. 1a is characterized in that the hydrodynamic clutch 1 is flowed through centrifugally.
  • the toroidal working space 4 is supplied with operating means via the operating means guide channels or rooms 12.
  • the operating medium is guided via the operating medium guide channel or space 9 on the outer circumference 7 of the turbine wheel 3 and from there into the area of the separating plane 11 in the area of the radially outer dimension 10 the hydrodynamic coupling 1 into the toroidal working space 4.
  • the hydrodynamic clutch will . flows through centripedally when building a circuit.
  • both equipment guide channels - or rooms are sealed against each other, ie pressure-tight and liquid-tight.
  • FIG. 2a illustrates the basic structure of a design according to the invention in a highly simplified diagram
  • Start-up unit 16 with a hydrodynamic clutch 1 designed according to the invention comprises an input E that can be coupled to a drive and an output A that can be coupled with downstream transmission stages or an output.
  • the start-up unit 16 comprises a starting element in the form of the hydrodynamic clutch 1.
  • the starting unit 16 also includes a clutch 17 which can be switched in parallel with the starting element.
  • a lock-up clutch is understood to be a switchable clutch device which enables power transmission in a drive system with several power branches bypassing one power branch.
  • the switchable clutch 17 comprises at least two frictionally operable clutch elements, preferably in the form of clutch discs - viewed in the direction of force flow between the input E and the output A of the starter unit 1 - a first clutch disc 19, which can also be referred to as a clutch input disc, and a second Clutch disc 20, which is also referred to as a clutch output disc.
  • An active connection by frictional engagement between the first clutch disc 19 and the second clutch disc 20 can be realized directly or indirectly.
  • the pump wheel 2 of the hydrodynamic clutch 1 comprises a pump wheel shell 6. This is either formed by a separate component which is coupled to the pump wheel 2 in a rotationally fixed manner, or is designed as an integral unit with the pump wheel 2.
  • the impeller shell 6 extends in the axial direction essentially over the axial extent of the turbine wheel 3 or at least partially encloses it in the radial direction.
  • the turbine wheel 3 is preferably enclosed by the pump wheel shell 6 or, in the case of a multi-part design, of its individual parts in such a way that they extend in the radial direction up to the area of the outlet A.
  • the turbine wheel 3 is connected directly or indirectly, ie via further transmission elements, to the output A of the starting unit 16.
  • the first clutch disc 19 is rotatably connected to the input E and the second clutch disc 20 is rotatably connected to the output A of the starting unit 16.
  • the first clutch disc 19 is non-rotatably coupled to the pump wheel 3, in particular the pump wheel shell 6, while the second clutch disc 20 is non-rotatably connected to the turbine wheel 3.
  • the switchable clutch 17 is preferably arranged in the radial direction in the region of the radial extension of the toroidal working space 4.
  • the means 21 preferably comprise a piston element 22 which can be pressurized with pressure medium, the function of the piston element 22 being taken over by the turbine wheel 3 in the case shown.
  • the turbine wheel 3 is either, as indicated in the figure, non-rotatably connected to the output A, but designed to be displaceable in the axial direction, or the connection to the output A is made directly non-rotatably, torsionally rigid in the circumferential direction and elastic in the axial direction.
  • the operating medium supply channels or spaces 12 and 9 are arranged directly on the hydrodynamic coupling 1, arranged in the hydrodynamic coupling 1 or associated with the means 13 for optionally changing the flow direction.
  • a 4/2-way valve device 14 is used for this, as already described in FIG. 1.
  • the 4/2-way valve device is connected to the operating medium guide channels or rooms 9 and 12 and controls the operating medium flow direction through the hydrodynamic coupling 1 in accordance with its position.
  • the working circuit is supplied centripedally to the working space 4, ie around the outer circumference 7 of the turbine wheel 3 and thus between the individual elements of the switchable clutch 17, in particular the first clutch disc 19 and the second clutch disc 20.
  • the counterforce caused by the guidance when the operating medium flow is supplied enables the turbine wheel 3 to be axially fixed during power transmission in the hydrodynamic coupling 1 of the pressure building up in the working space 4, an axial force which is no longer from the turbine wheel 3 is supported, but leads to a displacement of the turbine wheel 3 in the axial direction.
  • This displacement brings about a frictional connection between the two clutch disks of the switchable clutch device 17, so that the turbine wheel 3 is mechanically coupled to the pump wheel 2, the piston element 22, which is acted upon by a compressive force, being integrated in the hydrodynamic clutch 1, specifically by the turbine wheel 3 is formed.
  • the part of the turbine wheel 3 which carries the second clutch disc 20 takes over the function of the piston element 22 and the operating medium located in the toroidal working space takes over the function of pressurizing, in the case of a piston element 22 the function of a pressure chamber. In this functional state, the flow through the hydrodynamic clutch is centrifugal.
  • the embodiment of the starting unit 16 shown in FIG. 2a is a particularly advantageous arrangement of the individual elements - pump wheel 2 and turbine wheel 3 - of the hydrodynamic clutch 1.
  • the turbine wheel 3 In the transmission direction between the input E and the output A of the starting unit 1 the turbine wheel 3 is arranged spatially in the axial direction behind the pump wheel or next to it, while the pump wheel 2 is arranged spatially between the input E and the turbine wheel 3.
  • the means 21 for generating a contact pressure to realize a frictional connection of the individual elements of the switchable clutch 17, which acts as a lock-up clutch in the illustrated case, in the hydrodynamic clutch 1 Due to the integration of the means 21 for generating a contact pressure to realize a frictional connection of the individual elements of the switchable clutch 17, which acts as a lock-up clutch in the illustrated case, in the hydrodynamic clutch 1, the number of components required can be reduced to a minimum, since no additional separate devices for generating or providing the contact pressure for the individual elements, in particular the first clutch plate 19 and the second clutch plate 20, of the switchable clutch 17 are required. Another significant advantage is due to the integrated version in the very short axial length. In the case of optimized bucket wheels, this can be shortened even further with the solution according to the invention compared to the designs in the prior art.
  • the pump wheel 2 is connected to the drive E by means of fastening elements 23 according to an advantageous further development of a solution according to FIG. 2b, the drive here being coupled to a crankshaft 25 via a coupling of so-called flexplate 24 individual drive machine, not shown, takes place, ie in the axial direction with flexible and torsionally rigid membranes in the circumferential direction.
  • the fastening elements 23 extend partially into the blade base 26 of the pump wheel 2. This is illustrated on the basis of a detail from a structural design of a starting unit 16 according to FIG. 2a in FIG. 2b.
  • the second clutch disc 20 is preferably arranged on the rear side, ie the outer circumference 7 of the turbine wheel 3.
  • the arrangement is preferably carried out parallel to the parting plane 11 between the pump wheel 2 and the turbine wheel 3, preferably in the region between the dimensions of the inner diameter 27 and the outer diameter 28 of the toroidal working space 4.
  • the second clutch disc 20 is preferably formed directly by the turbine wheel, wherein the friction surface can be generated by a lining applied to the outer surface of the secondary wheel 3.
  • the starting unit 16 according to FIG. 3 comprises a device for damping vibrations 29, in particular a torsional vibration damper.
  • a device for damping vibrations 29 in particular a torsional vibration damper.
  • This can take many forms. In the simplest case, this is designed as a simple friction damping device. However, versions with hydraulic damping are also conceivable.
  • the specific configuration of such a device for damping vibrations 29 reference can be made to the designs known from the prior art. The specific selection is at the discretion of the responsible specialist.
  • the hydrodynamic component, the hydrodynamic clutch 1, the switchable clutch 17 and the device 29 for damping vibrations are connected in series.
  • the device for damping vibrations 29 comprises a primary part 30, which is non-rotatably connected to the turbine wheel 3 and thus the second clutch disc 20, and a secondary part 31, which is non-rotatably coupled to the output A. Means for damping and / or spring coupling are provided between primary part 30 and secondary part 31.
  • the device for damping vibrations 29 is arranged, depending on the power transmission branch, for power transmission via the hydrodynamic clutch 1 between the hydrodynamic clutch 1, in particular the turbine wheel 3 and the output A, furthermore for power transmission via the switchable clutch 17 between the switchable clutch 17, in particular the output formed by the second clutch disc 20 and the output A of Starting unit 16.
  • the device 29 for damping vibrations is connected in series to the respective power-transmitting element - hydrodynamic clutch 1 or switchable clutch 17.
  • the hydrodynamic clutch 1 and the switchable clutch 17 are operated simultaneously, that is to say power transmission via two power branches - transmission of a first power component of the total power via the hydrodynamic clutch and transmission of the second power component via the switchable clutch 17 - the torsional vibration damper is connected in series after the two power branches.
  • the rest of the basic structure of the starting unit corresponds to that described in FIG. 2a.
  • the same reference numerals are used for the same elements.
  • FIG. 4 illustrates in a schematically simplified representation a further embodiment of a starting unit 16.4 designed according to the invention with a starting element 17.4 in the form of a hydrodynamic coupling 1.4.
  • the hydrodynamic coupling 1.4 also comprises a primary wheel 2.4 and a secondary wheel 3.4, which together form a toroidal working space 4.4.
  • a switchable clutch 17.4 is also provided here, which is switchable parallel to the hydrodynamic clutch.
  • the basic function corresponds to that described in FIGS. 2 and 3.
  • the same reference numerals are used for the same elements.
  • FIGS. 2 and 3 The same reference numerals are used for the same elements.
  • the turbine wheel 3.4 viewed spatially in the axial direction, is arranged between the input E and the pump wheel 2.4, that is to say, contrary to the explanations of the preceding figures, the pump wheel 2.4 is not arranged on the motor side but on the motor output side ,
  • the coupling between a drive, in particular the input E of the starting unit 16.4 and the pump wheel 2.4 takes place in the axial direction, enclosing the secondary wheel 3.4, the connection of the turbine wheel 3.4 to the output via the output A takes place in the radial direction within the space between the coupling between the input E and the pump wheel 2.4 and, viewed spatially, between the input E and the output A of the starting unit before the coupling between the input E and the pump wheel 2.4.
  • FIGS. 5a and 5b illustrate the mode of operation of the starting unit 16 designed according to the invention using an embodiment according to FIG. 3.
  • the same reference numerals are used for the same elements.
  • Figure 5a illustrates the supply of operating fluid to the work area 4 during hydrodynamic operation, i.e. Power transmission via the hydrodynamic coupling 1 around the outer circumference 7 of the turbine wheel 3 to the parting plane 11 between the pump and turbine wheel in the area of the outer diameter 28 of the toroidal working chamber 4 and from there into the working chamber 4. In this state, the hydrodynamic coupling 1 is flowed through centripedally.
  • FIG. 5b illustrates the changed operating medium guidance when switching over to the switchable clutch 17 to the turbine wheel 3 in the area of the inner circumference of the working space 4 for the purpose of building up pressure on the blade base of the turbine wheel 3 to the inner diameter of the toroidal working space 4.
  • the hydrodynamic coupling 1 with centrifugal flow In this functional state, the hydrodynamic coupling 1 with centrifugal flow.
  • FIG. 6 illustrates the possibility of controlling the power consumption of the hydrodynamic clutch 1 both directly and indirectly by means of pressure control.
  • the corresponding connections B and C are assigned to the operating medium guide channels or spaces 9 and 12 which are sealed off from one another by means of a seal (not shown in detail).
  • the equipment is guided outside the toroidal working space 4 for the purpose of cooling via an open circuit 32.
  • the change in the flow through the hydrodynamic coupling 1, as shown in FIGS. 1 and 5, is also carried out, for example, via a valve device 14 which determines the assignment of the individual operating fluid flow channels or lines to the inlet and outlet according to the switching position.
  • the inlet and outlet are designated 33 and 34, respectively, and they can be connected to the equipment guide channels and rooms as desired.
  • the connection shown at 34 acts as an inlet and the connection shown at 33 as a return.
  • the connection shown at 34 is coupled to channels (not shown in detail) for guiding the operating medium around the outer circumference 7 of the turbine wheel 3.
  • the coupled flow of operating medium when guided between the individual clutch disks 19 and 20 to be frictionally connected to one another, serves to deactivate the switchable clutch 17 designed as a lock-up clutch.
  • the hydrodynamic clutch 1 is flowed through centripedally. This means a direction of flow towards the center, into the center of the working circuit 35 which arises in the toroidal working space 4.
  • the connection C serves to drain with resources from the toroidal working space 4.
  • the connection designated B acts as an outlet and the connection designated C as an inlet.
  • the operating medium is introduced centrifugally from the direction of the axis of rotation into the toroidal working space 4 and effects the function shown in FIG.
  • the turbine wheel 3 of the hydrodynamic clutch 1 functions as a piston element for the clutch disks 19 that can be frictionally connected to one another and 20 of the switchable clutch 17.
  • the open circuit 32 contains a container 36. Coupled with this " are a feed line 37 and a return line 38, which can optionally be coupled to the individual operating means guide channels or spaces 9 and 12 via the valve device 14.
  • the feed line 37 is assigned to the connection C
  • the return line 38 forms the connection B.
  • a controllable pressure relief valve 39 is provided in the return line 38, which can limit the pressure in the return line 38 to a certain value
  • a further conveying device 40 is provided, which makes it possible to have the power transmission carried out simultaneously via the switchable clutch 17 and the hydrodynamic clutch 1.
  • the power transmission for the switchable clutch 17 is directly controlled via the differential pressure between the two connections B and C. t and therefore indirectly also via the hydrodynamic branch, ie the hydrodynamic clutch 1.
  • the power transmission via the hydrodynamic clutch can be changed via the absolute pressure.
  • FIG. 7 Another possibility according to FIG. 7 is to directly assign means for controlling the pressure to the inlet to the toroidal working space 4 and the outlet from the toroidal working space 4.
  • the inlet and outlet B or C from the toroidal work space 4 are coupled to one another via a connecting line 41, which is coupled to an operating material container 43 via a further connecting line 42.
  • the control of the degree of filling in the toroidal working chamber 4 of the hydrodynamic coupling 1 can be effected by changing the absolute pressure p * ut abso carried out in the toroidal working space.
  • the individual connections B and C each have controllable valve devices 44 and 45 for controlling the pressures in the inflow and outflow - depending on the assignment of the individual connections B and C as supply or drain lines - assigned. In the simplest case, as shown in this figure, these are designed as independently controllable pressure control valve devices.
  • the connecting lines 41 and 42 as well as the connections B and C and the operating medium container 43 form an operating medium supply system 46.
  • a pressure relief valve 47 is preferably provided in the connecting line 41.
  • both the direction of flow and the transferable power in the hydrodynamic coupling are determined by the pressure values to be set in the equipment channels or rooms 9 and 12.
  • the power components that can be transmitted via each clutch — hydro-hydraulic clutch 1 and switchable clutch 17 — can be controlled individually or jointly.
  • a first power component is transmitted via a first power branch in which the hydrodynamic clutch 1 is arranged.
  • a second power component is transmitted via a second power branch, in which the switchable clutch 17 is arranged.
  • the control of the first power component takes place via the control of the absolute pressure in the hydrodynamic clutch 1.
  • the pressure present at the operating medium supply channel or space 12 via connection C acts as a control variable in this regard.
  • the control of the second power component is realized via the differential pressure applied at ports B and C.

Abstract

L'invention concerne un accouplement hydrodynamique (1), caractérisé en ce qu'il comprend deux roues à aubes, à savoir, une roue de pompe (2) et une roue de turbine (3) générant entre elles un espace de travail (4) de forme générale torique ; une coque de roue à pompe (6) accouplée à la roue à pompe (2) entourant la roue de turbine (3) en direction axiale, avec formation d'un premier conduit ou espace (9) de guidage des moyens de production ; un deuxième conduit ou espace (12) de guidage des moyens de production débouchant dans la zone du diamètre intérieur de l'espace de travail torique (6) ou au-dessous de cet espace, le premier et le deuxième conduit ou espace (12) de guidage des moyens de production étant utilisés au choix, respectivement, comme conduit ou espace d'entrée ou de sortie, en direction dudit espace de travail torique (4) ou à partir de celui-ci.
PCT/EP2001/008185 2000-08-31 2001-07-16 Accouplement hydrodynamique, systeme d'alimentation en moyens de production pour accouplement hydrodynamique et ensemble de demarrage dote d'un tel accouplement WO2002018819A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
BR0113576-7A BR0113576A (pt) 2000-08-31 2001-07-16 Embreagem hidrodinâmica, sistema de abastecimento de meio de serviço para uma embreagem hidrodinâmica e unidade de arranque com uma embreagem hidrodinâmica
JP2002523507A JP2004507692A (ja) 2000-08-31 2001-07-16 流体クラッチ、流体クラッチ用の作動油供給システム、及び流体クラッチを有する始動ユニット
EP01955352A EP1313966A1 (fr) 2000-08-31 2001-07-16 Accouplement hydrodynamique, systeme d'alimentation en moyens de production pour accouplement hydrodynamique et ensemble de demarrage dote d'un tel accouplement
US10/363,115 US20040011032A1 (en) 2000-08-31 2001-07-16 Hydrodynamic coupling, operating resources supply system for hydrodynamic coupling and starter unit with a hydrodynamic coupling

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE10043146 2000-08-31
DE10043146.1 2000-08-31
DE10110078A DE10110078A1 (de) 2000-08-31 2001-03-02 Hydrodynamische Kupplung, Betriebsmittelversorgungssystem für eine hydrodynamische Kupplung und Anfahreinheit mit einer hydrodynamischen Kupplung
DE10110078.7 2001-03-02
EP01106979.6 2001-03-21
EP01106979A EP1184600A1 (fr) 2000-08-31 2001-03-21 Distribution de fluide d'un accoupplement hydrodynamique et unité de démarrage avec accouplement hydrodynamique

Publications (1)

Publication Number Publication Date
WO2002018819A1 true WO2002018819A1 (fr) 2002-03-07

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PCT/EP2001/008185 WO2002018819A1 (fr) 2000-08-31 2001-07-16 Accouplement hydrodynamique, systeme d'alimentation en moyens de production pour accouplement hydrodynamique et ensemble de demarrage dote d'un tel accouplement

Country Status (4)

Country Link
EP (1) EP1313966A1 (fr)
JP (1) JP2004507692A (fr)
BR (1) BR0113576A (fr)
WO (1) WO2002018819A1 (fr)

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US20150027111A1 (en) * 2013-07-25 2015-01-29 Schaeffler Technologies Gmbh & Co. Kg Turbine shell defining a spring receiving pocket

Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
DE102004015706B4 (de) * 2004-03-29 2012-12-06 Voith Turbo Gmbh & Co. Kg Hydrodynamische Baueinheit und Verfahren zur Beschleunigung des Befüllvorganges einer hydrodynamischen Baueinheit

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US3476219A (en) * 1968-03-22 1969-11-04 Eaton Yale & Towne Overmatching rotor to stator retarder arrangement to combat cavitation
JPH01208238A (ja) * 1988-02-12 1989-08-22 Toyota Motor Corp 車両用フルードカップリング
EP0450405A1 (fr) * 1990-04-02 1991-10-09 Eaton Corporation Isolateur pour une transmission avec amortisseur hydraulique et ressort spiralé
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US3252352A (en) * 1963-02-18 1966-05-24 Ford Motor Co Hydrokinetic power transmitting mechanism
US3476219A (en) * 1968-03-22 1969-11-04 Eaton Yale & Towne Overmatching rotor to stator retarder arrangement to combat cavitation
JPH01208238A (ja) * 1988-02-12 1989-08-22 Toyota Motor Corp 車両用フルードカップリング
EP0450405A1 (fr) * 1990-04-02 1991-10-09 Eaton Corporation Isolateur pour une transmission avec amortisseur hydraulique et ressort spiralé
US5697866A (en) * 1994-05-25 1997-12-16 Nissan Motor Co., Ltd. Engine-CVT drivetrain control system
US5813505A (en) * 1995-07-19 1998-09-29 Luk Getriebe-Systeme Gmbh Hydrokinetic torque converter
US5853350A (en) * 1995-07-20 1998-12-29 Honda Giken Kogyo Kabushiki Kaisha Control device for lockup clutch
DE19804635A1 (de) 1998-02-06 1999-08-26 Mannesmann Sachs Ag Hydrodynamische Kupplungseinrichtung mit einer Überbrückungskupplung
US6085879A (en) * 1998-03-12 2000-07-11 Luk Getriebe-Systeme Gmbh Hydrokinetic torque converter
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Publication number Priority date Publication date Assignee Title
US20150027111A1 (en) * 2013-07-25 2015-01-29 Schaeffler Technologies Gmbh & Co. Kg Turbine shell defining a spring receiving pocket
CN105579737A (zh) * 2013-07-25 2016-05-11 舍弗勒技术股份两合公司 限定出容纳弹簧式容腔的涡轮壳

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JP2004507692A (ja) 2004-03-11
BR0113576A (pt) 2003-07-15

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