DE102006016397B4 - Transmission and a method for controlling a transmission for a motor vehicle - Google Patents

Abstract

Gearbox (3) for a motor vehicle (1) which, as a gearbox (7) provided with shift sleeves (8), cooperates with a clutch device which has a double clutch (9), i.e. a plurality of clutches (10, 11), which double clutch (9) is a comprises first clutch (10) and a second clutch (11) which can be connected to a first gear shaft and a second gear shaft, the first clutch (10) having a first hydraulic cylinder (14, 21) and the second clutch (11) a second hydraulic cylinder (15, 22) is operated, the first hydraulic cylinder (14, 21) having a first clutch pressure regulator (16, 19, 25, 34, 39, 43) and the second hydraulic cylinder (15, 22) a second clutch pressure regulator (17 , 20, 26, 35, 40, 44) is connected upstream, the first clutch pressure regulator (16, 19, 25, 34, 39, 43) and the second clutch pressure regulator (17, 20, 26, 35, 40, 44) each following Are designed as a slide valve having an electromagnet, because characterized in that between the clutch pressure regulators (16, 17, 19, 20, 25, 26, 34, 35, 39, 40, 43, 44) and the hydraulic cylinders (14, 15, 21, 22) of the first and the second clutch (10 and 11) a first switching device (23) and a second switching device (24) are provided and that each switching device (23, 24) is designed in the manner of a switching valve with which a defined rapid separation of the respective clutch (10, 11) can be accomplished, a control device (27, 36, 41, 45) and the control device being provided in front of the clutch pressure regulators (16, 17, 19, 20, 25, 26, 34, 35, 39, 40, 43, 44) (27, 36, 41, 45) is formed by a pressure maintenance valve.

Description

The invention relates to a transmission for a motor vehicle according to the preambles of claims 1, 2, 4 and a method for operating such a transmission for a motor vehicle according to the preamble of claim 3. The invention thus relates to a transmission for a motor vehicle as provided with a shift sleeves Manual transmission cooperates with a plurality of clutches, preferably a double clutch having clutch device.

It is known a transmission of a motor vehicle DE 103 49 220 A1 , which is designed as a manual transmission and is switched by means of a double clutch. The manual transmission has a first partial transmission and a second partial transmission, whose input shafts cooperate with a first and a second clutch of the dual clutch, which dual clutch is connected to an internal combustion engine of the motor vehicle. Intermediate shafts of the gearbox act on an output shaft, which drive wheels of the motor vehicle with the interposition of a differential.

The DE 10 2004 001 278 A1 deals with a dual-clutch transmission for a motor vehicle having two input shafts, two clutches and a first and a second drive shaft. The first input shaft is connectable to the first clutch and the second input shaft is connectable to the second clutch. The input shafts and drive shafts comprise intermeshing gears and at least two gears form a speed step. In this case, at least one gear of a gear stage is designed as a one-and / or disengageable idler gear and the other gear, for example. As a fixed gear.

From the DE 100 20 187 A1 shows a hydraulic circuit for an automated dual clutch transmission of a motor vehicle, wherein the dual clutch transmission comprises a countershaft transmission with two parallel power transmission branches and two clutches. In the dual clutch transmission operates a high pressure circuit with an actuator for the countershaft transmission and / or the clutches and a low pressure circuit for lubrication and / or cooling of components of the dual clutch transmission. In addition, a Verstellpumpe for variably providing the high pressure for the high pressure circuit is provided.

From the EP 1 449 708 A1 is a synchronized double clutch transmission for a vehicle and a hydraulic arrangement for actuating a first clutch of the dual clutch with a first hydraulic cylinder and a second clutch of the dual clutch with a second hydraulic cylinder known. The pressure in the clutch line is determined by using a hydraulic feedback with an external measuring cell by the current of the electromagnet of a clutch pressure regulator.

From the DE 103 47 203 A1 Arrangements for the hydraulic control of the transmission are known, wherein the focus of attention is the supply of the clutch and Getriebeaktuatorik with pressurized oil through a clutch device and the transmission commonly associated pump assembly, based on the pressure medium for the actuation of the clutch assembly and for the actuation of the Gear is available or can be supplied.

From the EP 1 710 477 A1 is a switching system of a gearbox with at least two actuators for engaging and disengaging gears known. The switching system includes a group selector valve that selects one of the two groups of actuators.

The object of the invention is to provide a transmission for a motor vehicle, which cooperates as a provided with shift sleeves gearbox with a plurality of clutches, preferably a dual clutch having clutch device, which is characterized by using easy-to-implement components by an excellent function.

According to the invention, this object is achieved by a transmission with the features of claims 1, 2 and / or 4 and by a method according to claim 3. Further, the invention ausgestaltende features are included in the following claims.

The advantages achieved by the invention are to be seen in the fact that the first clutch pressure regulator and the second clutch pressure regulator, which are each designed in the manner of a solenoid valve having a solenoid, ensure safe operation for changing gear of the gearbox. These clutch pressure regulators in conjunction with the method of their control allow a good function of the dual clutch of the transmission. The hydraulic cylinders immediately downstream connected in the manner of switching valves constructed switching devices have a relatively large cross-section to the tank line, whereby a relatively rapid emptying of the supply line to the tank can be achieved; said emptying causes a rapid separation of the associated coupling. The two clutch pressure regulators, which influence the first clutch and the second clutch of the dual clutch with the interposition of the switching means, a pressure-holding valve is connected upstream, which ensures that the respective operating pressure is set in the supply lines to the clutch cylinders within a working operating pressure.

Advantageous in terms of feasibility and effectiveness in the transmission with multiple shift sleeves, which cooperates with the first partial transmission and a second partial transmission of said gearbox influencing dual clutch is that each partial transmission has control elements, which are formed by switching actuators. In order to functionally operate the transmission or the manual transmission with the sliding sleeves in connection with these control elements, the method developed for this purpose is suitable.

In addition, the transmission, which is designed as a shift sleeves having shift gear and cooperating with a plurality of couplings preferably acting as a double clutch coupling device cooperates, both in terms of use of components and also performance standards. Inter alia, the control elements for moving the sliding sleeves and the clutch pressure regulators contribute to this.

In the drawings, embodiments of the invention are shown, which are explained in more detail below.

Show it:

1 : a motor vehicle from above with a gearbox that is equipped as a manual transmission with shift sleeves and cooperates with a double clutch;

2 : a first hydraulic circuit diagram for actuating hydraulic cylinders for clutches of the double clutch;

3 : a view accordingly 2 with a second hydraulic circuit diagram;

4 : a view accordingly 2 with a third hydraulic circuit diagram;

5 a fourth hydraulic circuit diagram for controls for moving sliding sleeves;

6 : a detail X the 5 as a construction representation and on a larger scale;

7 a fifth hydraulic circuit diagram for actuating hydraulic cylinders for clutches of the dual clutch and control elements for moving shift sleeves;

8th : a view accordingly 7 with a sixth hydraulic circuit diagram;

9 : a view accordingly 7 with a seventh hydraulic circuit diagram;

10 : a view accordingly 7 with an eighth hydraulic circuit diagram.

A motor vehicle 1 includes an internal combustion engine 2 that under mediation of a transmission 3 and a differential 4 bikes 5 and 6 drives. Between internal combustion engine 2 and gear 3 as a manual transmission 7 with shift sleeves 8th is formed, is a double clutch 9 intended. The double clutch 9 has a first clutch 10 and a second clutch 11 on, with the first clutch 10 with a first partial transmission 12 and the second clutch 11 with a second partial transmission 13 interacts. The first partial transmission 12 are associated with a first gear G1, a third gear G3, a fifth gear G5 and a seventh gear G7; the second partial transmission 13 a second gear G2, a fourth gear G4 and a sixth gear G6 and a reverse gear GR - 1 -. To operate the first clutch 10 and the second clutch 11 - Clutch actuation KB - serve a first hydraulic cylinder 14 and a second hydraulic cylinder 15 ,

• (1) im unbestromten Zustand des Elektromagneten des Schieberventils ist ein Durchgang des Drucköls zur Kupplung gesperrt und die Zuleitung zur Kupplung gegen den Tank geöffnet, dergestalt, dass Drucköl aus der Kupplung abfließt;
• (2) beim Bestromen des Elektromagneten wird die Öffnung zum Tank geschlossen und das Drucköl zur Kupplungszuleitung freigegeben;
• (3) die Referenzdruckfläche gegen die Kraft des Elektromagneten wirkt;
• (4) eine Referenzkraft ein Produkt aus Druck mal Wirkfläche ist;
• (5) ein Referenzdruck wird in der Zuleitung zum jeweiligen Kupplungszylinder abgenommen und der entsprechenden Wirkfläche zugeführt;
• (6) die Zuleitung zum Kupplungszylinder wird dann geschlossen, wenn die Referenzkraft im Gleichgewicht zur Magnetkraft steht;
• (7) beim Absenken des Drucks in der Zuleitung zum Kupplungszylinder sich das Schiebeventil solange öffnet bis das Gleichgewicht zwischen der Kraft des Elektromagneten und der Referenzkraft wieder hergestellt ist;
• (8) zum Absenken des Drucks in der Zuleitung zum Kupplungszylinder wird die Kraft des Elektromagneten reduziert, dergestalt, dass die Referenzkraft den Ventilkolben gegen die verminderte Kraft des Elektromagneten bewegt und die Zuleitung zum Kupplungszylinder in Richtung Tank öffnet;
• (9) der Druck in der Zuleitung solange absinkt bis sich die Kraft des Elektromagneten und die Referenzkraft im Gleichgewicht befinden.

The first hydraulic cylinder 14 is a first clutch pressure regulator 16 upstream; the second hydraulic cylinder 15 a second clutch pressure regulator 17 - 2 ; first hydraulic circuit diagram -. The first clutch pressure regulator 16 and the second clutch pressure regulator 17 are each one of a kind Electromagnet-containing slide valve formed, each slide valve having a reference pressure surface. Regarding the mode of action of the clutch pressure regulator 16 and 17 reference is made to the method of clutch actuation KB according to the control of the clutch pressure regulator:

• (1) in the energized state of the solenoid of the spool valve, a passage of the pressurized oil is blocked to the clutch and open the supply line for coupling against the tank, such that pressure oil flows out of the clutch;
• (2) when energizing the electromagnet, the opening is closed to the tank and released the pressure oil to the clutch supply line;
• (3) the reference pressure surface acts against the force of the electromagnet;
• (4) a reference force is a product of pressure times effective area;
• (5) a reference pressure is taken in the supply line to the respective clutch cylinder and fed to the corresponding effective area;
• (6) the supply line to the clutch cylinder is then closed when the reference force is in equilibrium with the magnetic force;
• (7) when lowering the pressure in the supply line to the clutch cylinder, the slide valve opens until the equilibrium between the force of the electromagnet and the reference force is restored;
• (8) to reduce the pressure in the supply line to the clutch cylinder, the force of the electromagnet is reduced, such that the reference force moves the valve piston against the reduced force of the electromagnet and opens the supply line to the clutch cylinder in the direction of the tank;
• (9) the pressure in the supply line decreases until the force of the electromagnet and the reference force are in equilibrium.

In 3 - Second hydraulic circuit diagram - is shown that between the first and second clutch pressure regulators 19 and 20 and first and second hydraulic pressure cylinders 21 and 22 the first clutch 10 and the second clutch 11 a first switching device 23 and a second switching device 24 are provided. Each switching device, z. B. 23 , is designed in the manner of a switching valve, with a defined rapid separation of the respective clutch 10 or 11 that by the hydraulic cylinders 21 and 22 be influenced, bewerkstelligbar.

For pressure oil influencing is before the first and second clutch pressure regulators 25 and 26 a control device 27 arranged - 4 , third hydraulic circuit diagram -. The control device 27 is designed as a pressure maintenance valve. The latter ensures that the working pressure in the supply line to the first hydraulic cylinder does not drop below a safe operating pressure.

• (1) der Weg des Ventilkobens proportional zur Stromstärke des Elektromagneten ist;
• (2) bei unbestromter Stellung des Ventilkobens oder bei maximal bestromter Stellung des Ventilkobens Ölübergangsstellen die größten Querschnitte aufweisen;
• (3) in einer Mittelstellung des Ventilkobens die Ölübergangsstellen gesperrt sind;
• (4) auf dem Weg des Ventilkolbens von einer Endstellung zur Mittelstellung sich der Strömungsquerschnitt linear zur Stromstärke des Elektromagneten bzw. auch annähernd proportional die Durchflussmenge des überströmenden Öls verringert.

Out 5 - fourth hydraulic circuit diagram - shows how the shift sleeves 8th of the gearbox 7 or of each partial transmission 12 or 13 by a first control element 28 and a second control element 29 be actuated - switching operation SchB -, which are designed as Schaltaktuatoren and structurally form Gleichgangzylinder, means hot the effective piston surfaces are the same size for both directions of movement. With the controls 28 and 29 or switching actuators connected is a socket selector valve 30 , which is designed as a solenoid valve with two switching positions. The socket selector valve 30 or solenoid switching valve upstream of a gearshift valve 31 that the basic functions of an axial piston 32 having a three-position valve - 6 - owns. The gearshift valve 31 is operated via the oil supply P and the outlets A and B, which can also be referred to as control channels. In addition, the axial piston works 32 with a proportional solenoid 33 together. The function of the manual transmission 7 in conjunction with the controls 28 . 29 , the socket selector valve 30 and the gearshift valve 31 is clarified by the method for controlling the transmission, according to which

• (1) the travel of the valve lifter is proportional to the current of the solenoid;
• (2) in the de-energized position of the valve head or at the maximum energized position of the valve head, oil-transfer points have the largest cross-sections;
• (3) in a central position of the Ventilkobens the oil transfer points are locked;
• (4) on the way of the valve piston from an end position to the middle position, the flow cross-section decreases linearly to the current of the electromagnet or approximately proportionally reduces the flow rate of the overflowing oil.

The 7 - fifth hydraulic circuit diagram - gives the operation of hydraulic cylinders for the clutches 10 and 11 - KB and control elements for moving the shift sleeves 8th - SchB - again. This is the clutch pressure regulators 34 and 35 an pressure maintenance valve 36 upstream, which contributes to the fact that at the beginning of a clutch overlap, the pressure in the actuated clutch does not fall below a set value.

According to 8th - Sixth hydraulic circuit diagram - is the manual transmission 7 , which in principle is approximately built like the manual transmission 7 , with a main pressure regulator 37 and a pressure balance 38 Mistake. The main pressure regulator 37 ensures a dominant pressure maintenance for the basic function clutch operation. The pressure balance 38 is powered and switched by pressures in the hydraulic cylinders of the clutches 10 and 11 and gives the respective higher clutch pressure as action pressure to the main pressure regulator 37 further. The main pressure regulator 37 is between pressure regulators (clutch pressure regulators) 39 and 40 the partial transmission 12 and 13 or a pressure maintenance valve 41 and the pressure balance 38 arranged with hydraulic cylinders of the clutches 10 and 11 are connected.

The 9 - seventh hydraulic circuit diagram - shows a first volumetric flow limiter 42 for the couplings 10 and 11 that operates between pressure regulators (Clutch pressure regulators) 43 and 44 or a pressure maintenance valve 45 the partial transmission 12 and 13 or the couplings 10 and 11 and a main pressure regulator 50 is provided. A second volume flow limiter 47 for the shift sleeves 8th is via lines on the one hand with pressure regulators 48 and 49 and on the other hand with a main pressure regulator 50 connected.

Based on 10 is clarified that a pressure balance 51 in conjunction with a switching pressure regulator 52 ensures a demand-based switching pressure. In addition, by a residual pressure regulator 53 and a cooling valve 54 a functionally compliant cooling oil pressure is reached, before the residual oil is fed to a pump suction side. LIST OF REFERENCE NUMBERS 1 motor vehicle 34 . 35 1st and 2nd clutch pressure regulator 2 Internal combustion engine 36 Pressure maintenance valve 3 transmission 37 Main pressure regulator 4 differential 38 pressure compensator 5 . 6 bikes 39 . 40 1st and 2nd clutch pressure regulator 7 manual transmission 41 Pressure maintenance valve 8th shift sleeves 42 1. Flow limiter 9 Double coupling 43 . 44 1st and 2nd clutch pressure regulator 10 first clutch 45 Pressure maintenance valve 11 second clutch 12 first partial transmission 47 2. Flow limiter 13 second partial transmission 48 . 49 pressure regulator 14 first hydraulic cylinder 50 Main pressure regulator 15 second hydraulic cylinder 51 pressure compensator 16 first clutch pressure regulator 52 Switching regulator 17 second clutch pressure regulator 53 Residual pressure regulator 19 first clutch pressure regulator 54 cooling valve 20 second clutch pressure regulator 21 first hydraulic cylinder G1 first course 22 second hydraulic cylinder G2 second gear 23 first switching device G3 third gear 24 second switching device G4 fourth gear 25 first clutch pressure regulator G5 fifth gear 26 second clutch pressure regulator G6 sixth gear 27 Control device (pressure maintenance valve) G7 seventh gear GR reverse gear 28 and 29 1st and 2nd control element (1st and 2nd shift actuator) KB Clutch actuation (1st and 2nd hydraulic cylinder) 30 Sleeve selector valve SchB shift operation 31 Gear shift valve P Control channel (oil supply) 32 Axial piston (valve piston) A, B Control channels (outgoing) 33 Proportional solenoid

Claims (12)

Transmission ( 3 ) for a motor vehicle ( 1 ), which as one with shift sleeves ( 8th ) provided manual transmission ( 7 ) with a double clutch ( 9 ), ie several couplings ( 10 . 11 ) cooperating coupling device, which double clutch ( 9 ) a first clutch ( 10 ) and a second clutch ( 11 ), which are connectable to a first gear shaft and a second gear shaft, wherein the first clutch ( 10 ) with a first hydraulic cylinder ( 14 . 21 ) and the second clutch ( 11 ) with a second hydraulic cylinder ( 15 . 22 ), wherein the first hydraulic cylinder ( 14 . 21 ) a first clutch pressure regulator ( 16 . 19 . 25 . 34 . 39 . 43 ) and the second hydraulic cylinder ( 15 . 22 ) a second clutch pressure regulator ( 17 . 20 . 26 . 35 . 40 . 44 ), wherein the first clutch pressure regulator ( 16 . 19 . 25 . 34 . 39 . 43 ) and the second clutch pressure regulator ( 17 . 20 . 26 . 35 . 40 . 44 ) are each designed in the manner of an electromagnet having a slide valve, characterized in that between the clutch pressure regulators ( 16 . 17 . 19 . 20 . 25 . 26 . 34 . 35 . 39 . 40 . 43 . 44 ) and the hydraulic cylinders ( 14 . 15 . 21 . 22 ) of the first and the second clutch ( 10 and 11 ) a first switching device ( 23 ) and a second switching device ( 24 ) are provided and that each switching device ( 23 . 24 ) is designed in the manner of a switching valve with which a defined rapid separation of the respective coupling ( 10 . 11 ) can be accomplished, wherein before the clutch pressure regulators ( 16 . 17 . 19 . 20 . 25 . 26 . 34 . 35 . 39 . 40 . 43 . 44 ) a control device ( 27 . 36 . 41 . 45 ) is provided for pressure oil influencing and the control device ( 27 . 36 . 41 . 45 ) is formed by a pressure maintenance valve. Transmission ( 3 ) for a motor vehicle ( 1 ), which can be used as a plurality of shift sleeves ( 8th ) having manual transmission ( 7 ) is formed and with a double clutch ( 9 ) comprehensive coupling device cooperates with which dual clutch ( 9 ) a first partial transmission ( 12 ) and a second partial transmission ( 13 ) of the gearbox ( 7 ) is influenced, wherein each partial transmission ( 12 . 13 ) Control elements ( 28 . 29 ) for moving the sliding sleeves ( 8th ), which are formed by shift actuators, characterized in that the shift actuators ( 28 . 29 ) designed as a synchronous cylinder and to a socket selector valve ( 30 ), which sleeve selection valve ( 30 ) is shown as a solenoid valve with two switching positions to which a gearshift valve ( 31 ), which performs the basic function of an axial piston ( 32 comprising the three-position valve and that, in addition, the gearshift valve ( 31 ) an axial piston ( 32 ) with a proportional electromagnet ( 33 ) having. Method for controlling a transmission ( 3 ) for a motor vehicle ( 1 ), which can be used as a plurality of shift sleeves ( 8th ) having manual transmission ( 7 ) is formed and with a double clutch ( 9 ) comprehensive coupling device cooperates with which dual clutch ( 9 ) a first partial transmission ( 12 ) and a second partial transmission ( 13 ) of the gearbox ( 7 ) are influenced, wherein each partial transmission ( 12 . 13 ) Control elements ( 28 . 29 ) for moving the sliding sleeves ( 8th ), which by switching actuators ( 28 . 29 ), characterized in that the sliding sleeves ( 8th ) by the two-sided controlled synchronous cylinder with equal effective piston surfaces for both directions of movement running shift actuators ( 28 . 29 ), each two shift actuators ( 28 . 29 ) in common to each one solenoid valve in the form of a socket selector valve ( 30 ) are connected with two switch positions on two sides, wherein a first switching actuator ( 28 ) or a second shift actuator ( 29 ) via the respective socket selection valve ( 30 ) are connectable to a pressure oil supply line and a supply line to the tank, which socket selection valve ( 30 ) for influencing the pressure oil on two control channels (outlets A, B) of an electromagnetically controlled valve with axial piston ( 32 ), Control channels (A, B, P) and a connection to the tank is connected, which valve as a gearshift valve ( 31 ) is operated, (1) the path of the axial piston ( 32 ) proportional to the current of the electromagnet ( 33 ), (2) in a de-energized position of the axial piston ( 32 ) or at a maximum energized position of the axial piston ( 32 ) Oil passage points of the control channels (A, P or B, P) have largest cross-sections, (3) in a middle position of the axial piston ( 32 ) the oil transfer points of the control channels (A and B) are locked, (4) on the way of the axial piston ( 32 ) from an end position to the middle position, the flow cross-section linear to the current strength of the electromagnet ( 33 ) decreases or approximately proportionally reduces the flow rate of the overflowing oil. Transmission ( 3 ) for a motor vehicle ( 1 ), which are used as sliding sleeves ( 8th ) having manual transmission ( 7 ) and with a plurality of couplings ( 10 . 11 ), as a double clutch ( 9 ), which are connectable to a first transmission shaft and a second transmission shaft, which first clutch ( 10 ) with a first hydraulic cylinder ( 14 . 21 ) and which second coupling ( 11 ) with a second hydraulic cylinder ( 15 . 22 ) is actuated, wherein the manual transmission ( 7 ) a first partial transmission ( 12 ) and a second partial transmission ( 13 ) and each partial transmission ( 12 . 13 ) Control elements ( 28 . 29 ) for moving the sliding sleeves ( 8th ) and wherein each coupling ( 10 . 11 ) with a hydraulic cylinder ( 14 . 15 . 21 . 22 ) is actuated, the ever a clutch pressure regulator ( 16 . 17 . 19 . 20 . 25 . 26 . 34 . 35 . 39 . 40 . 43 . 44 ), characterized in that the clutch pressure regulator ( 16 . 17 . 19 . 20 . 25 . 26 . 34 . 35 . 39 . 40 . 43 . 44 ) is designed in the manner of an electromagnet having a slide valve and that the clutch pressure regulators ( 16 . 17 . 19 . 20 . 25 . 26 . 34 . 35 . 39 . 40 . 43 . 44 ) one pressure maintenance valve each ( 27 . 36 . 41 . 45 ) and the pressure maintenance valves ( 27 . 36 . 41 . 45 ) a main pressure regulator ( 37 . 50 ) is connected upstream in a supply line with a functional pressure. Transmission ( 3 ) according to claim 4, characterized in that between the clutch pressure regulators ( 19 and 20 ; 25 and 26 ; 34 and 35 ; 39 and 40 ; 43 and 44 ) and the hydraulic cylinders ( 21 and 22 ) of the first and the second clutch ( 10 and 11 ) a first switching device ( 23 ) and a second switching device ( 24 ) are provided. Transmission ( 3 ) according to claim 5, characterized in that each switching device ( 23 . 24 ) is designed in the manner of a switching valve with which a defined rapid separation of the respective coupling ( 10 or 11 ) can be accomplished. Transmission ( 3 ) according to one of the preceding claims 4 or 5 or 6, characterized in that before the clutch pressure regulators ( 25 and 26 ; 34 and 35 ; 39 and 40 ; 43 and 44 ) a control device ( 27 ) is provided for pressure oil. Transmission ( 3 ) according to one of the preceding claims 4 or 5 or 6 or 7, characterized in that the main pressure regulator ( 37 ) with a pressure balance ( 38 ) works together. Transmission ( 3 ) according to one of the preceding claims 4 or 5 or 6 or 7 or 8, characterized in that between the clutch pressure regulators ( 43 and 44 ) of the partial transmission ( 12 and 13 ) and a main pressure regulator ( 50 ) a first volume flow limiter ( 42 ) for the couplings ( 10 and 11 ) is arranged. Transmission ( 3 ) according to claim 9, characterized in that a second volume flow limiter ( 47 ) for the shift sleeves ( 8th ) is provided. Transmission ( 3 ) according to claim 10, characterized in that the second volume flow limiter ( 42 ) a switching pressure regulator ( 52 ) is connected upstream. Transmission ( 3 ) according to claim 11, characterized in that the switching pressure regulator ( 52 ) with a residual pressure regulator ( 53 ) and a cooling valve ( 54 ) works together.

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