WO2005010409A1 - Circuit hydraulique - Google Patents

Circuit hydraulique Download PDF

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Publication number
WO2005010409A1
WO2005010409A1 PCT/EP2004/051241 EP2004051241W WO2005010409A1 WO 2005010409 A1 WO2005010409 A1 WO 2005010409A1 EP 2004051241 W EP2004051241 W EP 2004051241W WO 2005010409 A1 WO2005010409 A1 WO 2005010409A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
gear
circuit arrangement
solenoid valve
line
Prior art date
Application number
PCT/EP2004/051241
Other languages
German (de)
English (en)
Inventor
Armin Eiser
Axel Hinz
Josef Lauer
Uwe Greiff
Christoph KÖHLER
Original Assignee
Continental Teves Ag & Co. Ohg
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 DE102004016489A external-priority patent/DE102004016489A1/de
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2005010409A1 publication Critical patent/WO2005010409A1/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
    • 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
    • F16H61/02—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 characterised by the signals used
    • F16H61/0202—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 characterised by the signals used the signals being electric
    • F16H61/0204—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 characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/2807—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor
    • 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
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • F16H2061/305—Accumulators for fluid supply to the servo motors, or control thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • F16H61/68—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 specially adapted for stepped gearings
    • F16H61/684—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 specially adapted for stepped gearings without interruption of drive
    • F16H61/688—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 specially adapted for stepped gearings without interruption of drive with two inputs, e.g. selection of one of two torque-flow paths by clutches

Definitions

  • the invention relates to a hydraulic circuit arrangement for a motor vehicle transmission, according to the preamble of patent claim 1.
  • a hydraulic circuit arrangement of the generic type for actuating an automated manual transmission in a motor vehicle is already known from the special edition of ATZ and MTZ, May 2002, "The new Mercedes-Benz E-ClassN page 134, Figure 1.
  • the circuit arrangement has a pump, which is connected with its suction side to a Vorratsbehalter and with its pressure side to a high-pressure accumulator. From the high-pressure accumulator, individual branches of a high-pressure line lead via a plurality of proportionally controllable electromagnetic valves to a gear regulator as well as to a clutch actuator.
  • the gear actuator which is divided by a piston within a hydraulic cylinder into two chambers, it requires two 3/2 egevenbile to move the piston for the purpose of gear change in one or the other direction.
  • both chambers are connected via the two solenoid valves without pressure to a return line leading to the storage container. If the gear actuator remains depressed, a certain pressure build-up in one of the chambers must first be made to activate the gear actuator, which can have a disadvantageous effect on the system dynamics.
  • One of the two 3/2-way valves is to be controlled accordingly.
  • FIG. 1 shows in a first embodiment of the invention, a hydraulic circuit arrangement for an automated manual transmission with 12 solenoid valves for actuating gear and clutch plates
  • FIG. 2 shows, in a second embodiment according to the invention, an extension of the hydraulic circuit arrangement according to FIG. 1 by two additional pressure regulating valves in the high-pressure supply
  • FIG. 3 shows an embodiment of the circuit arrangement according to FIG. 2, which is provided with two further pressure control valves within the pressure medium return, FIG.
  • Figure 4 based on Figure 2 shows a further expedient circuit arrangement with analog controllable solenoid valves for actuating the gear plate, as well as with digital switching separating valves for the separation of the two hydraulic circuits.
  • FIGS. 1 to 4 are identical with regard to their elementary construction, so that initially a general description of all identical features for the three illustrated circuit arrangements follows. The differences between the three circuits and their peculiarities will be referred to after the description of the basic circuitry.
  • each of the four illustrated circuit arrangements has an electric motor-driven pump 17, which is connected with its suction side to a storage container 8 and with its pressure side to a high-pressure accumulator 13.
  • the state of charge of the high-pressure accumulator 13 is monitored by means of a pressure sensor 10 which is connected to a high-pressure line 1.
  • a pressure sensor 10 which is connected to a high-pressure line 1.
  • a Pressure relief valve 18 is connected between the pump 17 and the high-pressure accumulator 13 a line path at which a Pressure relief valve 18 is connected, which is connected via a check valve 19 and via a filter 20 with the reservoir 8 in conjunction.
  • the high-pressure line 1 Downstream of the high-pressure accumulator 13, the high-pressure line 1 is divided at point A initially two separate high-pressure branches, of which each of the two high-pressure branches in turn has sub-branches, which are connected in the present embodiment via six inlet-side solenoid valves 2 to four gear plate 4 and a few clutch plates 5, the Thus, via the solenoid valves 2 to the high-pressure accumulator 13 are connected.
  • each gear and clutch plate 4, 5 is connected to a branched return line 6.
  • each inserted in the high-pressure line 1 solenoid valve 2 is designed as a 2/2-way valve in poppet design, which separates the connection of the high pressure line 1 with the working chambers 3 of the gear and clutch plates 4, 5 in its normal position.
  • the proposed 2/2-way seat valves are characterized by a particularly leak-proof, cost-effective and small design. This is especially important if within each gear and clutch actuator 4, 5, a defined hydraulic pressure must be maintained.
  • the solenoid valves 2 in the simplest form are designed as binary switching valves, while in FIG. 4 the solenoid valves 2 are used exclusively with normally adjustable seat valves.
  • the circuit arrangement is designed such that the working chamber 3 of each gear selector 4 is defined with a defined the hydraulic pressure is applied.
  • each gear actuator 4 is connected in the connected to the gear actuators branches of the return line 6 each have a further outlet-side solenoid valve 7, as well as arranged in the high-pressure line 1 solenoid valves 2 advantageous as a 2/2-way valve in poppet design is executed.
  • the hydraulically initiated adjusting movement for each gear 4 can vary precisely.
  • the solenoid valves 7 are designed in the simplest form as a binary switching valves, while in Fig. 4, the solenoid valves 7 only come as analog adjustable poppet valves used.
  • Each gear actuator 4 is designed as a double-acting cylinder, in the working chamber 3, a hydraulically actuated piston 9 is used, the adjusting movement is monitored by a displacement sensor 10 and / or by a pressure sensor 11.
  • a first, according to the illustration in the left area of the working chamber 3 provided effective surface of the piston 9 is thus acted upon in each case via one of the solenoid valves 2 used in the high-pressure line 1 from the pressure of the high-pressure line 1 or via a Auslasssei- - ⁇
  • the two clutch plates 5 are designed to be extremely cost-effective as single-acting cylinders, in whose working chambers 3 a piston 9 which is exposed to the hydraulic pressure in the high-pressure line 1 is arranged, which on its left-hand effective surface is illustrated by an inlet-side, proportionally controllable electromagnetic valve 2 with the Pressure of the high-pressure accumulator can be acted upon or via a discharge side, also proprtionally controllable solenoid valve 7 with the reservoir 8 is connectable.
  • the solenoid valves 2, 7 of the Kupplungsstel- lers are advantageously designed as 2/2-way seat valves.
  • the position of the piston 9 in the clutch actuator 5 is monitored as well as the gear plate 4 by means of a displacement and / or pressure sensor 10, 11.
  • This return spring 12 is omitted in the embodiment of FIG. 4, since their function is performed in Fig. 4 by an integrated in each clutch plate 5 leaf spring.
  • the inlet-side solenoid valve 2, which is located in each case between the high pressure accumulator 13 and the clutch plate 5 in the high pressure line 1, and the outlet side solenoid valve 7, which is located between the Vorratsbehalter 8 and the clutch plate 5 in the return line 6, ensure a proportional function sensitive control of the piston actuating movement for the purpose of the gear change required clutch operation.
  • the circuit arrangement according to FIG. 2 additionally includes upstream of the solenoid valve 2 inserted into the high-pressure line 1 an electromagnetically operable pressure-regulating valve 14 in the high-pressure line 1, normally open in the normal position, in order to achieve a sensitive pressure regulation in each selector plate 4.
  • the high pressure line 1 branches downstream of the pressure control valve 14 both in the direction of the inlet side solenoid valve 2 and in the direction of the permanent hydraulic connection to each gear 4, so that in each gear 4, the two active surfaces of the piston 9 via a pressure control valve 14 with the regulated pressure of High-pressure accumulator 13 are acted upon.
  • the circuit arrangement of Figure 3 shows in addition to the circuit of Figure 2 between the pressure control valve 14 and the inlet side solenoid valve 2 for a few gear shifter 4 a connection of another return line 15, in which via another electromagnetically actuated, closed in the basic position pressure control valve 16 is a continuous control the pressure medium return from the range of the working chambers 3, which are each bounded by the second active surface of the piston 9 in the gear selector, to Vorratsbehalter 8.
  • the monitoring of the piston movement within each gear and clutch actuator 4, 5, for example by means of the illustrated pressure sensors 11, the if desired or required, can also be used for the circuit arrangements according to FIGS. 1, 2.
  • Both the two pressure control valves 14 and the two pressure control valves 16 are designed as a simple to produce, leak-free 2/2 way proportional valve in poppet design.
  • the circuit arrangement according to FIG. 4 additionally includes upstream of the solenoid valve 2 inserted into the high-pressure line 1 an electromagnetically operable isolating valve 21 in the high-pressure line 1 in the normal position, in order to separate, if desired or required, both hydraulic circuits for the gear regulators 4 of the gears 1, 3 , 5, 7 and the gears 2, 4, ⁇ , R to achieve.
  • the high-pressure line 1 branches downstream of the separating valve 21 both in the direction of the inlet-side solenoid valve 2 and in the direction of permanent hydraulic connection to each gear 4, so that in each gear 4, the two active surfaces of the piston 9 via the one the two separating valves 21 are acted upon by the regulated pressure of the high-pressure accumulator 13.
  • the circuit arrangements according to FIGS. 1 to 4 are preferably suitable for actuating an automated manual transmission which is designed as a six-speed or seven-speed transmission.
  • the high-pressure as well as the return lines 1, 6 branch for this purpose on the already mentioned four gear shifter 4 and the two clutch plates 5, wherein the branching of the high-pressure lines 1 for even and odd gear ratios of the gear 4 and on the gear actuators 4 assigned after even and odd gear stages split two clutch plates 5 takes place.
  • the first gear wheel 4 has the first and third gears
  • the second gear 4 the fifth (and according to FIG. 4 additionally the seventh) gear
  • the third gear 4 the second and fourth gear
  • the fourth gear 4 the sixth gear (and according to FIG. 4, the reverse gear) is assigned.
  • the first and second gear shifter 4 which has the odd gear ratios
  • the first clutch plate 5 is assigned functionally
  • the third and fourth gear plate 4 which has the even gear stages, cooperating with the second clutch plate 5.
  • the engaged clutch is one of two gears in the power flow of the transmission, depending on which of the two cooperating with the activated clutch plate 5 gear selector 4 is now hydraulically actuated via its associated inlet-side solenoid valve 2.
  • the other provided for the next higher or lower gear ratio gear selector 4 selects the next higher or lower gear already for subsequent load transfer, so that it can be switched without delay interruption by means of the associated clutch actuator 5 at the time of gear change without delay in the power flow.
  • the preselection and the switching of a gear is therefore always in response to the electrohydraulically initiated position of the piston 9 in the gear and clutch plates 4, 5, which are usually engaged with shift forks and Kupplungsaus Wegern in the transmission.
  • This circuit allows automated operation of all gears with extremely low switching times and without a traction interruption, so that the proposed multi-step transmission in conjunction with a dual clutch with significantly reduced design effort as well as a conventional automatic transmission can be operated as a power shift transmission.
  • the fourth, provided for the sixth gear gear 4 can be eliminated with the associated solenoid valves in the case of application of the invention to a five-speed transmission inevitably, resulting in a further simplification of the circuitry for the automated transmission would result.
  • the reverse gear R is provided on the second gear plate 4, which also operates the fifth gear

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Transmission Device (AREA)

Abstract

L'invention concerne un circuit hydraulique, notamment pour actionner la boîte de vitesses d'un véhicule, ce circuit comprenant une pompe (17) et, reliée à un réservoir à haute pression (13), une conduite à haute pression (1) qui est raccordée par une vanne électromagnétique (2) à au moins un actionneur hydraulique (4, 5) de vitesse et/ou d'embrayage, une conduite de retour (6) reliant l'actionneur (4, 5) de vitesse et/ou d'embrayage au réservoir (8). L'invention est caractérisée en ce que la vanne électromagnétique (2) montée dans la conduite à haute pression (1) est une valve à 2/2 voies montée comme une soupape à siège qui, dans la position initiale de la vanne électromagnétique (2), sépare la liaison entre la conduite à haute pression (1) et une chambre de travail (3) de l'actionneur (4, 5) de vitesse et/ou d'embrayage.
PCT/EP2004/051241 2003-07-25 2004-06-25 Circuit hydraulique WO2005010409A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10333984 2003-07-25
DE10333984.1 2003-07-25
DE102004016489.4 2004-04-03
DE102004016489A DE102004016489A1 (de) 2003-07-25 2004-04-03 Hydraulische Schaltungsanordnung

Publications (1)

Publication Number Publication Date
WO2005010409A1 true WO2005010409A1 (fr) 2005-02-03

Family

ID=34105478

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/051241 WO2005010409A1 (fr) 2003-07-25 2004-06-25 Circuit hydraulique

Country Status (1)

Country Link
WO (1) WO2005010409A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010028745A2 (fr) * 2008-09-09 2010-03-18 Volkswagen Aktiengesellschaft Procédé et circuit hydraulique pour la commande hydraulique de la boîte de vitesses notamment automatique ou automatisée d'un véhicule à moteur
DE102008054662A1 (de) * 2008-12-15 2010-06-17 Zf Friedrichshafen Ag Verfahren zur Überwachung einer hydraulischen oder pneumatischen Getriebesteuerung
DE102014117625A1 (de) * 2014-12-01 2016-06-02 Hoerbiger Antriebstechnik Holding Gmbh Schaltgetriebe eines Kraftfahrzeugs

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2163224A (en) * 1984-07-30 1986-02-19 Diesel Kiki Co Shift lever unit for motor vehicle transmission
EP0293800A2 (fr) * 1987-05-30 1988-12-07 Diesel Kiki Co., Ltd. Dispositif de commande pour une transmission automatique
EP0417657A1 (fr) * 1989-09-11 1991-03-20 Zexel Corporation Procédé de contrôle pour un récepteur hydraulique
DE4320353A1 (de) * 1992-06-27 1994-01-05 Teves Gmbh Alfred Hydraulische Getriebeansteuerung
DE19756638A1 (de) * 1997-12-19 1999-06-24 Zahnradfabrik Friedrichshafen Schalteinrichtung
EP1400733A2 (fr) * 2002-09-18 2004-03-24 Volkswagen Aktiengesellschaft Dispositif de commande hydraulique d'une boíte de vitesses à double embrayage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2163224A (en) * 1984-07-30 1986-02-19 Diesel Kiki Co Shift lever unit for motor vehicle transmission
EP0293800A2 (fr) * 1987-05-30 1988-12-07 Diesel Kiki Co., Ltd. Dispositif de commande pour une transmission automatique
EP0417657A1 (fr) * 1989-09-11 1991-03-20 Zexel Corporation Procédé de contrôle pour un récepteur hydraulique
DE4320353A1 (de) * 1992-06-27 1994-01-05 Teves Gmbh Alfred Hydraulische Getriebeansteuerung
DE19756638A1 (de) * 1997-12-19 1999-06-24 Zahnradfabrik Friedrichshafen Schalteinrichtung
EP1400733A2 (fr) * 2002-09-18 2004-03-24 Volkswagen Aktiengesellschaft Dispositif de commande hydraulique d'une boíte de vitesses à double embrayage

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010028745A2 (fr) * 2008-09-09 2010-03-18 Volkswagen Aktiengesellschaft Procédé et circuit hydraulique pour la commande hydraulique de la boîte de vitesses notamment automatique ou automatisée d'un véhicule à moteur
WO2010028745A3 (fr) * 2008-09-09 2010-06-24 Volkswagen Aktiengesellschaft Procédé et circuit hydraulique pour la commande hydraulique de la boîte de vitesses notamment automatique ou automatisée d'un véhicule à moteur
DE102008054662A1 (de) * 2008-12-15 2010-06-17 Zf Friedrichshafen Ag Verfahren zur Überwachung einer hydraulischen oder pneumatischen Getriebesteuerung
US8162799B2 (en) 2008-12-15 2012-04-24 Zf Friedrichshafen Ag Procedure for controlling a hydraulic or pneumatic transmission control unit
DE102014117625A1 (de) * 2014-12-01 2016-06-02 Hoerbiger Antriebstechnik Holding Gmbh Schaltgetriebe eines Kraftfahrzeugs

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