WO2009086876A1 - Embrayage hydrodynamique - Google Patents

Embrayage hydrodynamique Download PDF

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Publication number
WO2009086876A1
WO2009086876A1 PCT/EP2008/010506 EP2008010506W WO2009086876A1 WO 2009086876 A1 WO2009086876 A1 WO 2009086876A1 EP 2008010506 W EP2008010506 W EP 2008010506W WO 2009086876 A1 WO2009086876 A1 WO 2009086876A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve body
valve
hydrodynamic coupling
coupling according
working medium
Prior art date
Application number
PCT/EP2008/010506
Other languages
German (de)
English (en)
Inventor
Markus Kley
Andreas-Nicolas Mayer
Kurt Adleff
Werner Adams
Original Assignee
Voith Patent Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Voith Patent Gmbh filed Critical Voith Patent Gmbh
Publication of WO2009086876A1 publication Critical patent/WO2009086876A1/fr

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
    • 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
    • F16D33/08—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by devices incorporated in the fluid coupling, with or without remote control
    • F16D33/10—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by devices incorporated in the fluid coupling, with or without remote control consisting of controllable supply and discharge openings

Definitions

  • the invention relates to a hydrodynamic coupling, in particular a hydrodynamic coupling without external working medium circuit, in detail with the features of the preamble of claim 1.
  • Hydrodynamic couplings which manage without external working medium circuit, that is, in which the working fluid, with which drive power can be hydrodynamically transmitted from the impeller to the turbine of the hydrodynamic coupling, is always kept within the hydrodynamic coupling, have next to the working space, in which for power transmission the working fluid forms a circulation flow, an adjoining space, also called delay chamber, on, wherein the working medium located in the adjoining space does not participate in a power transmission between impeller and turbine wheel.
  • the adjoining room serves solely to store that portion of working medium within the hydrodynamic coupling which is not currently in the working space, wherein as a rule the adjoining space is dimensioned such that it can also accommodate all the working medium contained in the hydrodynamic coupling in order to completely fill the working space or almost completely empty and thus interrupt the power transmission.
  • a controllable Provide valve either in the inlet channel or in the drainage channel of the hydrodynamic coupling.
  • the inlet channel connects the secondary room in such a flow-conducting manner with the working space that working medium can be conducted from the secondary room into the working space.
  • the drainage channel connects the working space in such a flow-guiding manner with the adjoining space that Working medium can be passed from the work room in the next room.
  • the flow cross-section of the channel can be more or less opened and thus the flowing through the channel working medium volume flow can be regulated, whereby a regulation of the degree of filling of the working space, that is the ratio between the actually in the working space working fluid amount to the maximum possible in this operating state possible in the working space injectable amount of working fluid is possible.
  • a regulation of the degree of filling of the working space that is the ratio between the actually in the working space working fluid amount to the maximum possible in this operating state possible in the working space injectable amount of working fluid is possible.
  • the present invention has for its object to improve the known hydrodynamic couplings such that a faster switching on and off of the power transmission and in particular a more accurate and faster control of the degree of filling of the working space is made possible. At the same time, the construction effort should be minimized and a reliable operating behavior ensured.
  • a valve in particular a single valve, is provided by means of which both the working medium volume flow in the inlet channel and the working medium volume flow in the return channel can be alternately switched on and off and, in particular, continuously and simultaneously adjustable or changeable.
  • both working medium volume flows can be controlled together, in contrast to embodiments in which in each case at least one valve is provided both in the inlet channel and in the return channel.
  • the valve is designed as an electromagnetic valve, so can by changing the voltage applied to the electromagnet or the applied current as the manipulated variable of the
  • Working medium flow both in the inlet channel and in the return channel can be selectively varied by changing the flow cross-section in each channel.
  • the valve has a single valve body, also called throttle element, which engages in such a manner in the inlet channel and the return channel, that by moving, twisting, tilting or the like of the valve body, the flow cross-section in the inlet channel and the return channel can be varied.
  • two or more valve bodies are provided, which are simultaneously actuated as part of a single valve, but are designed separately.
  • the valve is designed as an electromagnetic valve, the two valve bodies can be simultaneously acted upon by the magnetic force of the valve and thereby actuated by the valve bodies being made wholly or partly of a magnetic or magnetizable material.
  • valve body or in a plurality of valve bodies
  • the valve body are designed as axial slide, that is as a piston or generally flow-influencing elements, which are arranged displaceably in the axial direction of the hydrodynamic coupling by actuation of the valve.
  • a rotation or tilting of the valve body or by pressing the valve into consideration may, for example, have openings which can be more or less brought into overlap with flow-conducting openings of an associated component of the hydrodynamic coupling and thus the flow cross-section in the inlet channel or return channel can be reduced or increased.
  • a displacement, in particular in the axial direction, of the at least one valve body it can more or less approximate a component in the hydrodynamic coupling with a flow-conducting opening and thus increase or reduce the working medium quantity flowing into or flowing out of this opening or the working medium volume flow.
  • a shift in a direction other than the axial direction of the hydrodynamic coupling into consideration, for example in the radial direction or diagonally.
  • the at least one valve body as a whole is linearly displaceable.
  • the valve body may include a rocker arm mechanism that tilts or pivots a portion of the valve body upon actuation of the valve.
  • valves In addition to the design of the valve as an electromagnetic valve, other on / off valves or proportional valves come into consideration, for example, electrically, pneumatically, magnetically, hydraulically or mechanically operable valves, in particular proportional, control or servo valves. Also, a simultaneous rotation and displacement of the at least one valve body may be provided by the valve body is carried for example on a thread.
  • additional pressure equalization openings can be provided outside of the region of the valve body which is intended to cover an associated opening more or less, through which the working fluid can flow during displacement of the valve body. This is particularly useful when the valve body is positioned within the side room or in another working medium leading portion of the hydrodynamic coupling.
  • the at least one valve body can either be arranged on a circumferential component of the hydrodynamic coupling, in particular revolving with it, for example on the drive shaft of the hydrodynamic coupling or on an output shaft of the hydrodynamic coupling.
  • an elastic element or a plurality of elastic elements may be provided to bias the valve body or elastic in the opening direction or closing direction.
  • the magnetic force of the valve then acts against the elastic biasing force.
  • Filling degree control / control either a so-called continuous valve for variable adjustment of the flowing through the inlet channel and the return channel working medium or the working medium volume flow to be provided, or the valve is actuated timed, that is activated and deactivated in more or less short intervals, so that a desired, averaged over the time larger or smaller working medium volume flow in the inlet channel and in the return channel adjusts.
  • the valve can then also be designed as a simple on / off valve, the valve body can not be moved in defined intermediate positions in contrast to a continuous valve / can.
  • Figure 1 shows a first embodiment of the invention with a single
  • Valve body which varies both the working medium volume flow in the inlet channel and in the return channel;
  • Figure 2 shows an embodiment according to the figure 1, but with a
  • Valve having two valve bodies - a first valve body in the inlet channel and a second valve body in the return channel - which are operated simultaneously;
  • Figure 3 shows a further embodiment, wherein the valve has two valve body, of which a single is actuated by means of an electromagnet.
  • FIG. 1 shows a hydrodynamic coupling with a bladed impeller 1 and a bladed turbine wheel 2, which together form a toroidal working space 3 that can be filled with working fluid.
  • an auxiliary space 7 is provided, which is connected via a working medium-carrying inlet channel 4 and a working medium-carrying return channel 5 with the working space 3.
  • the inlet channel 4 is formed inside the impeller 1, and the return channel 5 is formed by one or more holes in an intermediate element 12.
  • auxiliary space 7 it is also possible to position the auxiliary space 7 not only radially within the working space 3, but alternatively or additionally also in the axial direction next to the working space 3 and / or radially outside the working space 3.
  • the intermediate element 12 may be stationary, that is, not circumferential, be executed or rotate at a relative speed relative to the impeller 1 and the turbine wheel 2.
  • the intermediate element 12 has at least two operating states, a first operating state in which it is kept stationary, and a second operating state in which it is at a relative rotational speed with respect to the impeller 1 and the turbine wheel 2, in particular slower than the impeller 1 and the turbine wheel 2 rotates.
  • the intermediate element 12 as a skimming device, wherein due to a dynamic pressure of the working medium in front of the inlet opening of the return channel 5 and / or acting on the working fluid in the return channel 5 reduced centrifugal force, the working fluid from the working space 3 and the space within the coupling housing 6, in which the Intermediate member 12 protrudes radially outward to promote in the return channel 5 and in this radially inward.
  • the centrifugal force acting on the working medium in the return channel 5 is less, since the working fluid circulates in this return channel 5 at a lower speed in the circumferential direction of the hydrodynamic coupling, as the working fluid in said space within the housing 6, in which the intermediate element 12 is immersed ,
  • the turbine wheel 2 is formed by the housing 6.
  • the turbine wheel 2 is formed by the housing 6.
  • the turbine wheel 2 it is alternatively also possible to form the turbine wheel 2 as an independent bladed impeller, for example according to the pump impeller 1, and to carry the housing 6 integrally or non-rotatably with the pump impeller 1 or as an independent component, which comprises both the impeller 1 and the turbine wheel 2 encloses.
  • the hydrodynamic coupling has a valve 8 which can be selectively actuated independently of the rotational speed of the hydrodynamic coupling or of a centrifugal force.
  • the valve 8 is designed as an electromagnetic valve, comprising a valve body 10 and an electromagnet 13.
  • the valve body 10 is made magnetically or from a magnetizable material and is thus magnetically attracted or repelled by the magnetic force of the electromagnet 13, depending on the polarity.
  • the valve body 10 is slidably mounted in the axial direction of the hydrodynamic coupling on a drive shaft 9, which is integrally formed with the impeller 1 or this rotatably carries.
  • the valve body 10 is designed in one piece and has a first region which covers the inlet opening for working medium of the inlet channel 4 as a function of the axial position of the valve body 10, and a second region which, depending on the axial position of the valve body 10, the outlet opening for working medium the return channel 5 covers.
  • the first region is positioned at a first end of the valve body 10 and the former second area is provided at the other, opposite to the first end end of the valve body 10.
  • valve body 10 The more the inlet opening of the inlet channel 4 is covered by the valve body 10, that is, the smaller the flow cross section for the working medium flowing from the secondary chamber 7 into the inlet channel 4, the less the outlet opening of the return channel 5 is covered by the valve body 10, that is, the larger is the flow cross-section for working medium, which flows out of the return channel 5 and flows into the auxiliary space 7.
  • valve body 10 In order to reduce the force required to displace the valve body 10 in the axial direction, the valve body 10 has
  • the valve body 2 is switched by means of the electromagnet 13 exclusively between two end positions, wherein in the first end position, the inlet opening for working fluid in the inlet channel 4 as far as possible, in particular completely released and the
  • the valve 8 may be designed either as a continuous valve, in which the valve body 10 can be moved in intermediate positions between the two said end positions, or the valve 8 can be operated in time clocked so as to average over the time working medium volume flow in the inlet channel 4 and return channel 5 to control or regulate.
  • Clocked in this case means that the valve body 10 is moved at predetermined time intervals in each case from the first end position to the second end position and then from the second end position to the first end position or is held for predetermined periods in the respective end position. Accordingly, a corresponding control device can be integrated into or connected to the hydrodynamic coupling, which effects a corresponding time-clocked energization or voltage application to the electromagnet 13.
  • valve body 10 which is designed here as a hollow shaft.
  • the valve body 10 is over than Scope of the hydrodynamic coupling closed ring executed.
  • individual, in the circumferential direction one behind the other and connected to each other ring segments may be provided, for example, in the number corresponding to the number of holes that form the inlet channel 4 and the return channel 5. In the latter case could then possibly be dispensed with pressure equalization holes 11.
  • valve body 10 here two in the axial direction of the hydrodynamic coupling one behind the other and separated parts, or - in other words - a plurality of axially successively connected valve body 10 are provided , which are actuated jointly by the electromagnet 13.
  • the second valve body 10 is used for selectively opening or closing the return channel 5.
  • Both valve bodies can either be moved synchronously to each other or unsynchronized, depending on the embodiment of the valve 8.
  • Crucial is only that the two valve body 10 are moved together and in terms of their opening or closing function mutually to each other, whenever the inlet channel 4 is more or completely closed, the return channel 5 more or completely free.
  • FIG. 2 also shows an alternative possibility of connecting the space in which the return channel 5 opens to the secondary space 7, namely via bores in both valve bodies 10.
  • FIG. 2 also shows an alternative possibility of connecting the space in which the return channel 5 opens to the secondary space 7, namely via bores in both valve bodies 10.
  • other embodiments can also be used here.
  • the magnetic force of the electromagnet 13 via a magnetic force transmitter in particular in the form of a magnetizable Material are transferred to the two valve body 10, wherein this magnetic force transducer 15 is enclosed in particular in the axial direction of the hydrodynamic coupling between the two valve bodies 10.
  • this magnetic force transducer 15 is enclosed in particular in the axial direction of the hydrodynamic coupling between the two valve bodies 10.
  • the one or more valve bodies 10 may be biased against the force of the electromagnet 13, in particular by means of an elastic element, for example by means of a tension spring, compression spring or disc spring.
  • an elastic element is introduced between the valve body 10 and the pump impeller 1 and / or between the valve body 10 and the intermediate element 12 or a bearing provided between intermediate element 12 and drive shaft 9 bearing.
  • FIG. 3 shows a further embodiment of a hydrodynamic coupling according to the invention, with a further development of the embodiment from FIG. 2.
  • Only one of the two or the plurality of valve bodies is actuated by means of the electromagnet 13.
  • this is the second valve body 10 shown on the right in the figure.
  • This is preloaded against the intermediate element 12 by means of an elastic element, in this case a compression spring 16, against a component of the hydrodynamic coupling.
  • the biasing force of the spring 16 counteracts upon excitation of the electromagnet 13 of the magnetic force generated, whereas the biasing force acts in non-energization in the sense of a restoring force for moving the second valve body 10 in its end position.
  • the first valve body 10 (shown here on the left) by means of the flow connection between a Room 18, in which the return channel 5 opens with its outlet opening and the secondary chamber 7 to its displacement with working medium, which flows from the return channel 5 at least partially released flow cross-section into the space 18, acts.
  • the second valve body 10 is first moved, wherein the
  • this flow cross section is moved from a completely closed state into an open state. Consequently, the first valve body 10 is acted upon on one side to its displacement with working fluid, wherein the acting working fluid pressure in the space 18, in particular depending on the position of the second valve body 10 is increasingly changing.
  • the first valve body 10 is free from a magnetic force acting on it of the electromagnet 13 and free from a mechanical connection with a further valve body 10th
  • the second valve body 10 could essentially be formed as a check valve, comprising an elastic element whose restoring force counteracts the flow direction of the working medium in the return channel 5, so that the second valve body 10 would be moved against the biasing force of the elastic element and the flow cross section of the return channel 5 would vary more or less depending on the working medium pressure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

L'invention concerne un embrayage hydrodynamique avec : une roue de pompe (1) et une roue de turbine (2), qui forment une chambre de travail (3) pouvant être remplie de fluide de travail, sachant qu'un conduit d'alimentation (4) est raccordé à la chambre de travail pour alimenter la chambre de travail en fluide de travail, et qu'un conduit de retour (5) est raccordé à la chambre de travail pour évacuer le fluide de travail de la chambre de travail ; et un boîtier (β), qui entoure au moins indirectement la chambre de travail. Une chambre auxiliaire (7) est disposée à l'intérieur du boîtier et/ou sur le boîtier ; elle est reliée en conduction de fluide de travail à la chambre de travail par l'intermédiaire du conduit d'alimentation et du conduit de retour, de sorte que le fluide de travail peut être véhiculé en circuit fermé de la chambre secondaire dans la chambre de travail via le conduit d'alimentation, et de la chambre de travail dans la chambre secondaire via le conduit de retour. Selon l'invention, une soupape (8) est prévue à l'intérieur du boîtier et/ou sur le boîtier ; au moyen de cette soupape (8), un flux volumique de fluide de travail est, simultanément dans le conduit d'alimentation et dans le conduit de retour, alternativement activable et désactivable, ou réglable en continu, ou réglable de manière variable par un actionnement synchronisé dans le temps.
PCT/EP2008/010506 2008-01-03 2008-12-11 Embrayage hydrodynamique WO2009086876A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008003165 2008-01-03
DE102008003165.8 2008-01-03

Publications (1)

Publication Number Publication Date
WO2009086876A1 true WO2009086876A1 (fr) 2009-07-16

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2479448A1 (fr) * 2011-01-18 2012-07-25 Siemens Aktiengesellschaft Embrayage hydrodynamique doté d'une préchambre à plusieurs niveaux

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB478006A (en) * 1935-07-23 1938-01-11 Francois Joseph Georges Henry Improvements in and relating to hydraulic clutch and power transmission devices
US2432191A (en) * 1944-01-19 1947-12-09 Wright Aeronautical Corp Fluid coupling automatic control valve
GB756287A (en) * 1953-09-22 1956-09-05 Atel Const Nord De La France Feed device for a hydraulic coupling
US2875581A (en) * 1948-10-01 1959-03-03 J M Voith G M B H Maschinenfab Hydraulic coupling
DE3939802C1 (de) * 1989-12-01 1991-01-03 Voith Turbo Kg Hydrodynamische Kupplung
WO2000055527A1 (fr) * 1999-03-12 2000-09-21 Voith Turbo Gmbh & Co. Kg Unite de demarrage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB478006A (en) * 1935-07-23 1938-01-11 Francois Joseph Georges Henry Improvements in and relating to hydraulic clutch and power transmission devices
US2432191A (en) * 1944-01-19 1947-12-09 Wright Aeronautical Corp Fluid coupling automatic control valve
US2875581A (en) * 1948-10-01 1959-03-03 J M Voith G M B H Maschinenfab Hydraulic coupling
GB756287A (en) * 1953-09-22 1956-09-05 Atel Const Nord De La France Feed device for a hydraulic coupling
DE3939802C1 (de) * 1989-12-01 1991-01-03 Voith Turbo Kg Hydrodynamische Kupplung
WO2000055527A1 (fr) * 1999-03-12 2000-09-21 Voith Turbo Gmbh & Co. Kg Unite de demarrage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2479448A1 (fr) * 2011-01-18 2012-07-25 Siemens Aktiengesellschaft Embrayage hydrodynamique doté d'une préchambre à plusieurs niveaux

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