EP1313967A1 - Ensemble de demarrage et procede permettant d'adapter des ensembles de demarrage a des systemes d'entrainement dans des conditions marginales differentes, notamment des machines d'entrainement differentes - Google Patents

Ensemble de demarrage et procede permettant d'adapter des ensembles de demarrage a des systemes d'entrainement dans des conditions marginales differentes, notamment des machines d'entrainement differentes

Info

Publication number
EP1313967A1
EP1313967A1 EP01967177A EP01967177A EP1313967A1 EP 1313967 A1 EP1313967 A1 EP 1313967A1 EP 01967177 A EP01967177 A EP 01967177A EP 01967177 A EP01967177 A EP 01967177A EP 1313967 A1 EP1313967 A1 EP 1313967A1
Authority
EP
European Patent Office
Prior art keywords
clutch
coupling
hydrodynamic
starting unit
turbine wheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP01967177A
Other languages
German (de)
English (en)
Inventor
Heinz Höller
Reinhard Kernchen
Achim Menne
Werner Klement
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Turbo GmbH and Co KG
Original Assignee
Voith Turbo GmbH and 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 DE10110077A external-priority patent/DE10110077A1/de
Priority claimed from EP01106408A external-priority patent/EP1184599B1/fr
Application filed by Voith Turbo GmbH and Co KG filed Critical Voith Turbo GmbH and Co KG
Priority to EP01967177A priority Critical patent/EP1313967A1/fr
Publication of EP1313967A1 publication Critical patent/EP1313967A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • 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
    • 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
    • F16H2045/0215—Details of oil circulation
    • 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
    • F16H2312/00—Driving activities
    • F16H2312/02—Driving off

Definitions

  • the invention relates to a starting unit, in particular with the features from the preamble of claim 1; a method for adapting a starting unit to drive systems with different boundary conditions, in particular different drive machines.
  • 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. Regarding a possible execution of a starting unit for use in
  • Geared with a hydrodynamic clutch is referred to the publication DE 198 04 635 A1.
  • Turbine wheel is spatially arranged 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.
  • this solution is relatively short, it does not meet the requirements of certain predetermined installation situations with regard to the required axial length.
  • this design is characterized by a large number of components and an enormous amount of assembly work.
  • the size of the starting unit is also determined by the required design of this in cooperation with a drive machine and the downstream switching stages when used in drive systems. In particular, a change in the drive machine requires a change in the design of the starting unit.
  • 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 are more universal for a plurality of drive trains with different boundary conditions, for example drive machines of different types Performance that can be used without changes in the design.
  • start-up unit should be characterized by a very small installation space requirement in the axial direction, a small number of components and the combination of functional elements.
  • the design effort is to be kept low.
  • the achievement of the object according to the invention is characterized by the features of claims 1 and 20. Advantageous configurations are described in the subclaims.
  • a starting unit with an input that can be coupled to a drive and an output that can be coupled to the output comprises a starting element in the form of a hydrodynamic clutch and a switchable clutch, comprising at least two clutch elements that can be frictionally connected directly or indirectly via further transmission means - a first clutch element and one second
  • Coupling element which are rotatably coupled to the input and the output.
  • the hydrodynamic clutch and the switchable clutch are arranged in parallel and can be switched together or individually. Parallel arrangement means that these are in two different power branches between the drive and
  • the solution according to the invention makes it possible, if necessary, to split the transferable power into two power branches and to bring them together again at the output.
  • the possible transmission either over only one branch or over both branches offers the advantage that the starting unit with the individual components can be used in different drive systems without changing the design and can be optimally adapted to the boundary conditions of the respective application. Since, according to a particularly advantageous further development, the individual performance components are free, i.e. are independently controllable or adjustable, there is also the option of generating different starting characteristics.
  • Power transmission via the hydrodynamic clutch i.e. is characterized by the first power branch, a second basic functional state, which by the sole
  • the switchable clutch functions as a lock-up clutch.
  • both clutches are in operation.
  • the power consumption of the hydrodynamic clutch is controlled by the filling wheel, while the power consumption of the switchable clutch is adjustable by the contact pressure.
  • Both clutches are separate, i.e. independently controllable.
  • the hydrodynamic clutch In the first basic functional state, the hydrodynamic clutch is switched. In this the power at input E is only transmitted via the hydrodynamic coupling. The switchable clutch is deactivated. In addition, there is the possibility that
  • both power branches are activated, i.e. a first power component is transmitted via the hydrodynamic clutch and a second power component via the switchable clutch.
  • the individual power components can be controlled independently of one another.
  • the third basic state can last from short-term joint activation to activation over a main part of the approach area.
  • Control are specified or can be specified, guaranteed.
  • the power distribution can be via a) an actuating device, which is assigned to each transmission element - hydrodynamic clutch and switchable clutch - and can be controlled separately, for example in the form of a resource or control means supply system with the corresponding influencing means, for example valves, or b) one which is assigned to each transmission element and can be controlled separately Actuator for loading the individual transmission element with the corresponding contact pressure or a certain degree of filling from a shared resource and / or control means or c) a common actuating device that is assigned to a common resource or control means supply system.
  • the switchability and adjustability of the transferable power components takes place via a jointly usable pressure control control system which uses a common supply of operating resources and / or control means.
  • the design requirement for a particularly compact starting unit is the design of the hydrodynamic coupling with a pump wheel shell which is coupled to the pump wheel in a rotationally fixed manner and which encloses the turbine wheel in the axial direction with the direct formation of a first operating means guide channel or space.
  • a second resource guide channel or, if an intermediate wall is present, with the formation of the first resource guide channel or space between the impeller shell and the partition wall, which opens in the region of the inner diameter of the toroidal work space or below it.
  • the first and second resource guide channels or spaces are each optionally available as feed or
  • Drainage channel or space for toroidal work space can be used. 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 centripedal and centrifugal in a simple manner. To supply the equipment with centripetal flow, ie flow the hydrodynamic coupling via the first equipment guide channel - or space to the radially outer area of the toroidal
  • the pump wheel and turbine wheel are preferably designed with an offset in the radial direction.
  • both equipment guiding channels or rooms are sealed against each other.
  • the equipment supply and management system assigned to the hydrodynamic coupling comprises an equipment supply source - or a supply and a first connection for coupling to the first equipment management duct or space, and a second connection for coupling to the second
  • 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 just a constructive one
  • Individual elements of the Equipment supply system may also be part of the hydrodynamic coupling or not. This applies in particular to the means for selectively changing the flow direction of the hydrodynamic coupling by assigning the function of the inflow or outflow to the two operating medium supply channels - or rooms and / or
  • the means comprise a valve device with at least two switching positions.
  • a first switching position is due to the coupling between the inlet, ie. H.
  • Feed line and first resource management channel or room and drain d. H. Return line and second resource guide channel or room and the second switching position characterized by the coupling between the inlet and the second resource guide channel or space and drain and the first resource guide channel or room.
  • Resource management channels - or rooms are preferably coupled to one another via an open circuit.
  • the open circuit contains the resource supply source, which also functions as a resource store, and a coupling of this via the feed and return line to the resource guide channels or spaces in the hydrodynamic coupling.
  • the valve device is only interposed. With this configuration, even during continuous operation of the transmission elements, in particular the hydrodynamic clutch, a cooling circuit can be maintained between the outlet from the work space and the inlet via the operating fluid reservoir.
  • the power consumption "of the hydrodynamic coupling of the filling degree is variable in a further aspect of the invention.
  • control and / or controllability can In the simplest case, this is done by providing a corresponding pressure control valve in the feed or feed line and / or the return line, which can be freely adjusted and optimized with regard to different criteria, such as energy consumption and pollutant emissions
  • the switchable 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, which can be brought into operative connection with one another at least indirectly, ie either directly or indirectly via further clutch plates.
  • Coupling disc is rotatably connected to the output, preferably directly to the turbine wheel.
  • Another possibility, in particular with an odd number of friction surfaces, consists in the provision of a partition, which forms a piston and is fixed in terms of rotation with the turbine wheel, but axially displaceable relative to the latter.
  • the clutch discs are
  • 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 or a non-rotatably connected but axially displaceable one
  • Partition wall used as a piston element used as a piston element.
  • the pressure room for Actuation of the piston element is formed by the part of the toroidal work space enclosed by the turbine wheel.
  • Turbine wheel ensures, while in the second case, only a reversible deformation of the connection between the turbine wheel and the exit of the starting unit enables the pressing.
  • the turbine wheel can be axially displaced in a range of 0.1 to 2 mm. 0
  • Counterforce is generated by equipment supplied to the work area, 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 area and is introduced into the pump wheel from there and the hydrodynamic Flows through the clutch centripedally.
  • both clutch disks of the switchable clutch are close to each other.
  • the remaining gap serves as a throttle point for the equipment flowing through. This throttle establishes a pressure difference between the piston surfaces, from which the contact pressure required for opening and closing for the lock-up clutch results.
  • this is realized 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 which keeps the turbine wheel and thus the clutch disc connected to it at a minimum distance of approximately 1 or more 10ths from the other first clutch disc or other intermediate disc elements fixed in position.
  • this is also possible with the elastic connection of the turbine wheel to the outlet in the axial direction.
  • the spatial arrangement is viewed in the axial direction next to the toroidal working space in front of or behind.
  • the arrangement in the radial direction is characterized by outer and inner dimensions, which are preferably in the area between the outer and the inner
  • Diameter of the toroidal work area Diameter of the toroidal work area.
  • 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. Manufacturing tolerances can be compensated for without problems.
  • the rotationally fixed coupling takes place when the connection is made directly from the turbine wheel to the rear of the part of the turbine wheel forming the to s.
  • 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
  • Inner surface of the impeller shell and in the second case are formed by the separate component or by one 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.
  • TSD torsional vibration damper
  • switchable clutch together.
  • the TSD in the power branch is assigned to the switchable clutch and this is upstream or downstream in this power branch.
  • the TSD is connected upstream and downstream of the two power branches. It is preferably hydrodynamic
  • 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 arrangement for damping vibrations takes place 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.
  • 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 includes 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 by a certain angle, means for spring and / or damping coupling between the primary part and the secondary part.
  • the means for damping coupling include
  • Hydraulic fluid fillable chambers in which vibrations are shifted.
  • the device for damping vibrations only has to 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 predetermined by the hydrodynamic component.
  • the solution according to the invention and its further developments are particularly suitable for use in automatic transmissions. Use in automated manual transmissions is also conceivable.
  • the starting unit can be traded separately as a pre-assembled unit.
  • the connection to the transmission is made by integration in the transmission housing or series connection with switching stages or stepless transmission parts, for example traction mechanism transmissions or toroidal transmissions, in which case the coupling can be implemented, for example, by plugging onto a shaft that can be coupled with shift stages or stepless transmission parts.
  • the starting unit according to the invention is suitable for use in drive trains in stationary systems as well as vehicles.
  • the starting unit designed according to the invention enables a method for adapting it to drive trains with different boundary conditions, without having to change the structural conditions, in particular the design of the individual components. All that is required is an appropriate control the control devices of the individual transmission elements - hydrodynamic clutch or switchable clutch -.
  • the method is characterized in that the power transmission either via the hydrodynamic clutch, the switchable clutch or partially in a first power branch via the hydrodynamic
  • the power that can be transmitted via the first power branch can be controlled and / or regulated.
  • the power which can be transmitted via the switchable clutch can also be controllable and / or adjustable.
  • the controllability and / or regulatability of the power that can be transmitted via the individual power branches can be carried out either independently of one another or in a coupled manner, depending on the use of a common or separate operating equipment or control means supply system and corresponding actuating devices.
  • Couplable power share by controlling the absolute pressure in the toroidal work space and the power share that can be transferred via the switchable clutch by controlling the
  • the manipulated variable for controlling the absolute pressure is either the inlet pressure, d. H. the pressure in the inlet in the toroidal work space or preferably the outlet pressure.
  • Coupling is the differential pressure between the inlet and outlet, i.e. H. Inlet and return.
  • FIGS. 2a to 2c illustrate the individual possible basic states of the power transmission over individual power branches
  • FIGS. 3a and 3b illustrate the basic principle of the construction of a starting unit designed according to the invention on the basis of a particularly advantageous embodiment
  • FIG. 3c illustrates the basic principle of pressure control for realizing the power distribution using a diagram
  • FIG. 7 illustrates an advantageous embodiment of a starting unit according to the invention
  • Figure 8 illustrates an advantageous embodiment of a
  • FIG. 1 illustrates the schematically simplified representation
  • the starter unit 1 comprises an input E which can be coupled with a drive and an output A which can be coupled with downstream transmission stages or an output.
  • the starter unit 1 comprises a starting element 2 in the form of a hydrodynamic clutch 3.
  • Coupling 3 comprises two paddle wheels, a primary wheel functioning as a pump wheel 4 and a secondary wheel functioning as a turbine wheel 5, which together form a working space 6, which is usually toroidal.
  • the starting unit 1 further comprises a switchable in the form of the hydrodynamic clutch 3 parallel to the starting element 2
  • hydrodynamic coupling 3 and switchable clutch 7 either switchable separately or together.
  • the hydrodynamic clutch 3 and the switchable clutch 7 are thus arranged in two different power branches, a first power branch 8 and a second power branch 9.
  • the switchable clutch 7 comprises at least two clutch elements which can be brought into frictional engagement, preferably in the form of clutch disks, i.e. in the direction of force flow between the input E and the output A of the starting unit 1 considered a first clutch disc 10, which also as
  • Clutch input disc can be referred to and a second clutch disc 11, which is referred to as the clutch output disc.
  • An active connection by frictional engagement between the first clutch disc 10 and the second clutch disc 11 can be realized directly or indirectly, in the former case the
  • Friction pairing of the first clutch disc 10 and the second clutch disc 11 is formed, while in the second case further elements bearing friction surfaces are interposed.
  • each transmission element - hydrodynamic clutch 3 and switchable clutch 7 - is assigned its own actuating device 34 and 35, which is only indicated here as a black box and which ensures switchability.
  • the switchability of the switchable clutch 7 is ensured by generating an appropriate contact pressure.
  • Coupling 3 for example, by filling and emptying.
  • the transferable power components are controlled via the first and second power branches 8 and 9 by controlling or varying the contact pressure on the switchable clutch 7 and controlling and / or regulating the degree of filling of the hydrodynamic clutch 3.
  • the three basic states are illustrated in a schematic representation in FIGS. 2a to 2c. These show again the individual power branches 8 and 9, the assignment of the individual elements to them and, by means of the arrow line, the power transmission in the individual basic states - first basic functional state FIG. 2a, second
  • the hydrodynamic clutch 3 In the first basic functional state, the hydrodynamic clutch 3 is switched. In this, the power present at input E is only transmitted via hydrodynamic clutch 3. The switchable clutch 7 is deactivated. In addition, however, there is the possibility of influencing the transmission behavior of the hydrodynamic clutch 3. This is done by changing the degree of filling. An increasing degree of filling at constant speed causes a higher pressure p ⁇ in the working space 6 of the hydrodynamic clutch 3 and vice versa.
  • the switchable clutch 7 is switched. In this the power at input E is only transmitted via this.
  • the hydrodynamic clutch 3 is deactivated. This is done by changing the contact pressure so that the clutch is operated without slippage.
  • both power branches 8 and 9 are activated, i.e. it becomes a first share of performance over the hydrodynamic
  • the individual power components can be controlled independently of one another in a further aspect of the invention.
  • the third basic functional state can range from short-term joint activation to activation via a main part of the
  • Power distribution and free controllability of the power components that can be transmitted via the individual components consists, on the one hand, in an adaptation to various boundary conditions, for example another, to be carried out only in terms of control technology
  • Prime mover i.e. without structural changes to be made. Furthermore, different starting characteristics can be freely set with this control option.
  • both clutches can be assigned a separate pressure control, which are linked to one another by a higher-level control.
  • both systems use a pressure control system in order to minimize the required installation space and the number of components.
  • the pump wheel 4 comprises a pump wheel shell 12 for this purpose. This is either formed by a separate component which is non-rotatably coupled to the pump wheel 4 or is designed as an integral unit with the pump wheel 4.
  • the impeller shell 12 extends in the installed position in the axial direction essentially over the axial extent of the turbine wheel 5 or at least partially encloses it in the radial direction.
  • the turbine wheel 5 is enclosed by the pump wheel shell 12 or, in the case of a multi-part design of its individual parts, in such a way that it is radial
  • the turbine wheel 5 is directly or indirectly, i. H. connected to output A of start-up unit 1 via further transmission elements.
  • the basic structure of the starting unit 1 otherwise corresponds to that described in FIG. 1. The same reference numerals are therefore used for the same elements.
  • the first clutch disc 10 is non-rotatable with the Impeller 4, especially the pump wheel 12 is connected, while the second clutch disc 11 is non-rotatably coupled to the turbine wheel 5 ".
  • a first basic functional state which by the sole power transmission via the hydrodynamic clutch 3, i.e. characterized by the first power branch 8
  • a second basic functional state which is due to the sole power transmission through the switchable clutch 7, i.e. is characterized by the second power branch 9 and -
  • a third basic functional state which is characterized by the common
  • Lock-up clutch In the third basic functional state, both clutches are in operation.
  • the power consumption of the hydrodynamic clutch 3 is controlled by the filling wheel, while the power consumption of the switchable clutch 7 is adjustable by the contact pressure.
  • Both clutches are separate, i.e. independently controllable.
  • the means 13 preferably comprise a piston element 14 to which pressure medium can be applied, the function of the piston element 14 being taken over by the turbine wheel 5.
  • the turbine wheel 5 is either non-rotatably connected to the outlet A, as indicated in FIG. 3a, but is designed to be displaceable in the axial direction, or the connection to the outlet A is made directly non-rotatably, torsionally rigid in the circumferential direction and elastic in the axial direction.
  • an embodiment with axial displaceability is preferred.
  • the controls mentioned can also be operated as regulations.
  • the operating medium is supplied according to FIG. 3b, which represents a functional state with the hydrodynamic coupling 3 actuated, to the working space 6 around the outer circumference 13 of the turbine wheel 5 and thus between the individual elements of the switchable clutch 7, that is to say at least between the first clutch disc 10 and the second clutch disc 11.
  • the counterforce caused by the guidance when the operating medium flow is supplied enables an axial fixation during the sole power transmission in the hydrodynamic clutch 3 of the turbine wheel 5.
  • Start-up unit 1 is a particularly advantageous arrangement of the individual elements - pump wheel 4 and turbine wheel 5 - of the hydrodynamic clutch 3.
  • the pump wheel 4 is spatially in the axial direction behind the one in the power transmission direction between the input E and the output A of the start-up unit 1 Turbine wheel 5 or arranged next to it, while the turbine wheel 5 is arranged spatially between the input E and the pump wheel 4. Due to the integration of the means 13 for generating a contact pressure to realize a frictional connection of the individual elements of the switchable clutch 7 in the hydrodynamic
  • Coupling 3 can reduce the number of components required Minimum are reduced, since no additional separate device for generating or providing the contact pressure for the individual elements, in particular first clutch plate 10 and second clutch plate 11 of the switchable clutch 7, is required. Another advantage is the very short axial length due to the integrated design.
  • Power transmission in the start-up unit is characterized by the equipment management and the pressures in the corresponding connection lines or equipment management channels or rooms.
  • Design requirement on the starting unit 1 is that the impeller shell 12 surrounds the turbine wheel 5 such that between the outer periphery 16 of the
  • Turbine wheel and the inner contour 17 of the pump wheel shell 12 is formed at least one resource guide channel - or space 18 for guiding resources.
  • this should make it possible to draw resources between the turbine wheel 5 and the pump wheel shell 6 in the area of the radially outer dimensions 20 of the hydrodynamic clutch 3, in particular the primary wheel 4 and the turbine wheel 5 in the area of a parting plane 21 between the pump wheel 4 and the turbine wheel 5 in the direction of introduce themselves in the toroidal working space 6 of the working circuit and ensure a centripetal flow.
  • the hydrodynamic clutch 3 in particular the primary wheel 4 and the turbine wheel 5 in the area of a parting plane 21 between the pump wheel 4 and the turbine wheel 5 in the direction of introduce themselves in the toroidal working space 6 of the working circuit and ensure a centripetal flow.
  • the hydrodynamic clutch 3 in particular the primary wheel 4 and the turbine wheel 5 in the area of a parting plane 21 between the pump wheel 4 and the turbine wheel 5 in the direction of introduce themselves in the toroidal working space 6 of the working circuit and ensure
  • Coupling 1 is assigned at least one equipment guide channel or space 19, which enables the equipment to be fed to the toroidal work space 6 in the centrifugal direction.
  • the operating medium channel or space 19 can be a line or channels specially designed and incorporated in the connecting structure.
  • the term channel is here in terms of Function to consider and can also include interiors or combined channels and room sections.
  • the resource guide channel or space designated 18 is present here as an annular resource guide space.
  • each of the operating medium guide channels 18 and 19 is designed in such a way that, in addition to the supply of operating medium to the toroidal working space 6, they can also be used for removal, ie, it is thus connected to at least one entry and / or one exit from the toroidal working chamber 6. It is irrelevant in which area the equipment emerges from the toroidal work space 6. According to the invention, the two
  • Resource guide channels or rooms 18 and 19 can be used either as inlet or outlet, so that the flow direction is also changed.
  • means are provided for optionally changing the flow direction of the hydrodynamic clutch 1. These means can also be referred to as flow direction change means 22.
  • 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 directional valve device 23. This can
  • valve device 23 can also be in a gearbox or on any other
  • the second valve position II of the valve device 23 shown in FIG. 3a causes the hydrodynamic coupling 3 to be flowed through centrifugally.
  • the toroidal shape becomes in the area of the inner circumference Workspace 6 operating materials supplied via the operating medium guide channels or rooms 19.
  • the operating medium is guided via the operating medium guide channel or space 18 on the outer circumference 16 of the turbine wheel 5 and from there into the area of the
  • the equipment supply system 24 is shown in the figures independently of the actual integration of certain parts in the starting unit 1 assigned to them.
  • the individual connecting lines 25 and 26 are connected to one another via corresponding connecting lines 27.1 and 27.2 with a container 36 as a resource and storage device to form an open system 28.
  • the connecting line 27.1 functions as a return line in FIG. 3a, while 27.2 functions as a feed line.
  • Pressure control can take place via a controllable pressure limiting valve 29 in the return line 27.1.
  • a feed pump 38 is arranged in the feed line 27.2. This makes it possible for the power transmission to take place simultaneously via the switchable clutch 7 and the hydrodynamic clutch 3.
  • the power transmission for the switchable clutch 7 is controlled directly via the differential pressure between the two connections 25 and 26 and thus indirectly also the power transmission via the hydrodynamic branch 8, ie the hydrodynamic clutch 3.
  • the power transmission can be carried out via the absolute pressure in the hydrodynamic clutch 3 through which these are changed.
  • the valve device is located in FIG. 3a 23 in the second switching position II. This is characterized in that the flow is centrifugal.
  • the switchable clutch 7 is used alone for power transmission or together - because it is operated with slip - with the hydrodynamic clutch 3.
  • the first switching position I according to FIG. 3b is characterized in that a centripetal flow and sole power transmission over the hydrodynamic Clutch is present.
  • FIG. 3c shows the pump wheel 4, the turbine wheel 5, the pump wheel shell 12, which is non-rotatably coupled to the pump wheel 4, the piston 14, which is rotatably coupled to the turbine wheel 5, and the switchable clutch 7 with a first clutch disk 10 and a second clutch disk 11, which is coupled to the piston element 14.
  • the pressure p. Is the pressure present in the first resource guide channel or space 18, the pressure p 2 is the pressure present in the second resource guide channel or space 19.
  • the pressure in the hydrodynamic clutch 3 is referred to as p k .
  • the pressure control of the hydrodynamic clutch 3 is characterized by changing the pressure p 2 .
  • the transmission behavior of the clutch 3 can be influenced over large ranges at constant speeds by the impeller and turbine wheel number.
  • the pressure p 2 is proportional to the circuit pressure p k . This depends on the degree of filling. An increasing degree of filling means a larger proportion of the operating medium in the equipment circulation, which means that Transferability increases.
  • the degree of filling in the hydrodynamic circuit is influenced by the pressure p 2 or the pressure difference (p 2 -p k ) and this in turn influences the circuit pressure p k .
  • the circuit pressure p k increases with the square of the engine or drive speed. Since in the steady state p k is proportional to p 2 , the circuit pressure p k adapts to the pressure p 2 via the degree of filling, ie the hydrodynamic circuit in the working space 6 changes to partial filling at a constant pressure p 2 and the transfer capability, expressed by the coefficient of performance, falls. With increasing pressure and constant speed, the transmission capacity also increases. This behavior can be changed by adjusting the size of the pressure p 2 with the square of the motor or drive speed n, as illustrated in FIG. 4a.
  • the hydrodynamic clutch 3 transmits moments at a variable output speed in accordance with a characteristic curve of constant pressure, as shown in FIG. 4b.
  • the transmissible torque rises or falls on another characteristic curve of constant pressure, for example from p constant to p constant - 2 .
  • the pressure of the switchable clutch is controlled by pressurizing the axially movable piston 14 on both sides.
  • the resulting axial force results from the pressure difference (p 2 -p.,) And the
  • the manipulated variable for controlling the transferable power via the switchable coupling is therefore the pressure difference between the connections or equipment guide channels or spaces 19 and 18.
  • P 2 acts as a manipulated variable for the pressure control of the hydrodynamic clutch 3 and the pressure difference (p 2 -p.,) As a manipulated variable for controlling the
  • FIG. 5 uses a diagram to illustrate the temporal course of a possible torque distribution during operation of the starting unit 1.
  • the power that can be transmitted via the hydrodynamic clutch, or the torque is almost 100% of the drive torque, here up to about t1.
  • the switchable clutch 7 can then be switched by increasing the pressure difference (p 2 -p.,) Until it is synchronized with the input speed at t3, i.e. the speed at the input of the Starting unit and output of the starting unit transmits the entire moment.
  • the transmitted torque of the hydrodynamic clutch 3 can additionally be adapted to the requirements of the respective driving state.
  • Time t2 characterizes a time with shared power transmission.
  • FIG. 6 illustrates the characteristic curves that characterize this process in the speed-time diagram.
  • FIG. 7 illustrates a particularly advantageous further development of the embodiment according to FIG. 3a.
  • the two resource management channels - or rooms 18 and 19 - are coupled to a resource supply 24 via an open system 28
  • This valve device is, for example, a pressure regulating valve 30 and 31, and both the pressure values to be set in the operating medium channels or rooms 18 and 19
  • Flow direction and the transferable power components of the hydrodynamic clutch and the switchable clutch can be determined.
  • the power components that can be transmitted via each clutch - hydro-dynamic clutch 3 and switchable clutch 7 - can be controlled, without any mutual interference.
  • the power component is transmitted in parallel operation of the hydrodynamic clutch 3 and the switchable clutch 7 via the first power branch 9, in which the hydrodynamic clutch is arranged.
  • a second power component is transmitted via a second power branch, in which the switchable clutch 7 is arranged.
  • the control of the first power component takes place via the control of the absolute pressure p k in the hydrodynamic clutch 1.
  • the pressure present at the first operating medium supply channel or space 19 via the connection 25 acts as a control variable in this regard.
  • the control of the second power component is realized via the differential pressure applied to the connections 25 and 26.
  • the starting unit 1 according to FIG. 3a comprises a device for damping vibrations 33, in particular a torsional vibration damper.
  • a device for damping vibrations 33 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. With regard to the specific configuration of such a device for damping vibrations 33, reference can be made to those known from the prior art
  • the hydrodynamic component, the hydrodynamic clutch 3, the switchable clutch 7 and the device 33 for damping vibrations are connected in series.
  • the device for damping vibrations 33 comprises a
  • the device for damping vibrations 33 is arranged between the hydrodynamic clutch 3, in particular the turbine wheel 5 and the output A, in the case of power transmission via the hydrodynamic clutch 3, and furthermore between the switchable clutch 7 in the case of power transmission via the switchable clutch 7, especially that by the second
  • Coupling disc 11 formed output and the output A of the starting unit 1.
  • the device 33 for damping vibrations is connected in series to the respective power-transmitting element - hydrodynamic clutch 3 or switchable clutch 7.
  • the rest of the basic structure of the starting unit corresponds to that described in FIGS. 3a and 3b.
  • the same reference numerals are used for the same elements. Even if the hydrodynamic clutch 3 and the shiftable clutch 7 are operated simultaneously, i.e. Power transmission over two power branches - transmission of a first power component of the total power via the hydrodynamic
  • FIG. 8 illustrates in a schematically simplified representation a further embodiment of a starting unit 1.8 designed according to the invention with a starting element 2.8 in the form of a hydrodynamic coupling 3.8.
  • the hydrodynamic coupling 3.8 comprises a primary wheel 4.8 and a secondary wheel 5.8, which together form a toroidal working space 6.8.
  • a switchable clutch 7.8 is also provided here, which is switchable parallel to the hydrodynamic clutch.
  • the basic function corresponds to that described in FIGS. 1 to 7.
  • the same reference numerals are used for the same elements.
  • the pump wheel 4.8 viewed spatially in the axial direction, is arranged between the inlet E and the turbine wheel 5.8, ie that
  • turbine wheel 5.8 is not arranged on the engine output side, but on the engine side.
  • the coupling between a drive, in particular the input E of the starting unit 1.8 and the pump wheel 4.8 takes place in the axial direction by enclosing the secondary wheel 5.8.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Arrangement Of Transmissions (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

L'invention concerne un ensemble de démarrage (1) caractérisé en ce qu'il comprend une entrée (E) pouvant être accouplée à des moyens d'entrée et une sortie (A) pouvant être accouplée à des moyens de sortie ; un élément de démarrage (2) sous forme d'un accouplement hydraulique (3) ; un accouplement commutable (7) présentant au moins deux éléments d'accouplement (un premier (10) et un deuxième (11)) pouvant être amenés par friction en liaison coopérante, directement ou indirectement, via d'autres moyens de transmission, et qui sont accouplés, solidaires en rotation, respectivement, à l'entrée (E) et à la sortie (A). L'accouplement hydrodynamique (3) et l'accouplement commutable (7) sont disposés parallèlement dans deux branches de division de puissance et sont commutables individuellement ou l'un et l'autre conjointement.
EP01967177A 2000-08-31 2001-07-14 Ensemble de demarrage et procede permettant d'adapter des ensembles de demarrage a des systemes d'entrainement dans des conditions marginales differentes, notamment des machines d'entrainement differentes Withdrawn EP1313967A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP01967177A EP1313967A1 (fr) 2000-08-31 2001-07-14 Ensemble de demarrage et procede permettant d'adapter des ensembles de demarrage a des systemes d'entrainement dans des conditions marginales differentes, notamment des machines d'entrainement differentes

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE10043146 2000-08-31
DE10043146 2000-08-31
DE10110077A DE10110077A1 (de) 2000-08-31 2001-03-02 Anfahreinheit und Verfahren zur Anpassung von Anfahreinheiten an Antriebssysteme mit unterschiedlichen Randbedingungen, insbesondere unterschiedliche Antriebsmaschinen
DE10110077 2001-03-02
EP01106408A EP1184599B1 (fr) 2000-08-31 2001-03-21 Procédé d'adaption des unités de démarrage aux systèmes d'entraînement avec des conditions de bordure différentes, notamment pour des moteurs d'entraînement différents
EP01106408 2001-03-21
PCT/EP2001/008149 WO2002018817A1 (fr) 2000-08-31 2001-07-14 Ensemble de demarrage et procede permettant d'adapter des ensembles de demarrage a des systemes d'entrainement dans des conditions marginales differentes, notamment des machines d'entrainement differentes
EP01967177A EP1313967A1 (fr) 2000-08-31 2001-07-14 Ensemble de demarrage et procede permettant d'adapter des ensembles de demarrage a des systemes d'entrainement dans des conditions marginales differentes, notamment des machines d'entrainement differentes

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EP1313967A1 true EP1313967A1 (fr) 2003-05-28

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US (1) US6899209B2 (fr)
EP (1) EP1313967A1 (fr)
JP (1) JP2004507690A (fr)
WO (1) WO2002018817A1 (fr)

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US9752667B2 (en) 2014-12-05 2017-09-05 Valeo Embrayages Torque converter and hydrokinetic torque coupling device having turbine-piston lockup clutch, and related methods
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US9739358B2 (en) 2015-04-15 2017-08-22 Valeo Embrayages Hydrokinetic torque coupling device having damper-piston lockup clutch, and related method
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US6899209B2 (en) 2005-05-31
US20030168298A1 (en) 2003-09-11
JP2004507690A (ja) 2004-03-11

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