阅读说明：本技术 液压变速箱致动器以及具有该液压变速箱致动器和变速箱的组件 (Hydraulic gearbox actuator and assembly with hydraulic gearbox actuator and gearbox ) 是由 W.霍布纳 于 2020-03-04 设计创作，主要内容包括：本发明涉及一种液压变速箱致动器(1),具有液压泵(2),所述液压泵具有泵体(5),在所述泵体中布置有转子(6),其中,设置有驱动马达(4),利用所述驱动马达能够沿相反的方向驱动所述转子(6),其中,在所述泵体(5)中形成彼此分开的两个工作室(8,9),所述工作室每个具有两个开口(A,B,C,D),其中至少三个开口(A,B,C)连接到相应的压力供应回路,所述压力供应回路的一侧连接到储液器(3),另一侧连接到所述变速箱致动器(1)的三个压力出口(10,20,30,40)中的一个。(The invention relates to a hydraulic gearbox actuator (1) having a hydraulic pump (2) with a pump body (5) in which a rotor (6) is arranged, wherein a drive motor (4) is provided, with which the rotor (6) can be driven in opposite directions, wherein two working chambers (8, 9) separated from one another are formed in the pump body (5), which working chambers each have two openings (A, B, C, D), wherein at least three openings (A, B, C) are connected to a respective pressure supply circuit, which is connected on one side to a reservoir (3) and on the other side to one of the three pressure outlets (10, 20, 30, 40) of the gearbox actuator (1).)

1. A hydraulic gearbox actuator (1) with a hydraulic pump (2) having a pump body (5) in which a rotor (6) is arranged, wherein a drive motor (4) is provided, with which the rotor (6) can be driven in opposite directions, wherein two working chambers (8, 9) separated from one another are formed in the pump body (5), which working chambers each have two openings (a, B, C, D), wherein at least three openings (a, B, C) are connected to a respective pressure supply circuit, which is connected on one side to a reservoir (3) and on the other side to one of the three pressure outlets (10, 20, 30, 40) of the gearbox actuator (1).

2. The hydrostatic gearbox actuator according to claim 1, characterized in that a fourth opening (C) is directly connected to the reservoir (3).

3. A hydraulic gearbox actuator according to claim 1, characterised in that all openings (a, B, C, D) are connected to a pressure supply circuit which is connected on one side to the reservoir (3) and on the other side to one of the four pressure outlets (10, 20, 30, 40) of the gearbox actuator (1).

4. The hydrostatic gearbox actuator according to any one of the preceding claims, characterized in that in each pressure supply circuit a proportional valve (14, 24, 34, 44) is arranged between the opening (A, B, C, D) and the pressure outlet (10, 20, 30, 40).

5. The hydraulic gearbox actuator according to claim 4, characterised in that the reservoir (3) is divided into a plurality of separate chambers (3A, 3B, 3C, 3D), each proportional valve (14, 24, 34, 44) having a return line (15, 25, 35, 45) leading to a chamber (3A, 3B, 3C, 3D) of the reservoir (3) from which a pressure supply circuit connected to the same working chamber (8, 9) of the hydraulic pump (2) is drawn.

6. The hydraulic gearbox actuator according to any one of the preceding claims, characterised in that a non-return valve (12, 22, 32, 42) is provided in each pressure supply circuit, which non-return valve is arranged between an inlet (11, 21, 31, 41) from the reservoir (3) and a branch to an opening (A, B, C, D) of the hydraulic pump (2).

7. The hydraulic gearbox actuator (1) according to any one of the preceding claims, characterised in that the hydraulic pump (2) is a drum pump or a vane pump.

8. Assembly of a gearbox with a hydraulic gearbox actuator (1) according to any of the preceding claims and with a drive train for a motor vehicle, wherein the gearbox has at least one clutch and brake and the gearbox actuator (1) is capable of actuating at least one clutch and at least one brake.

9. An assembly according to claim 8, characterized in that two of the pressure outlets (10, 20, 30, 40) are connected to respective clutches of the gearbox and two of the pressure outlets are connected to respective brakes of the gearbox.

10. The assembly according to claim 9, characterized in that the brakes are each assigned to a planetary gear set and the clutch is assigned to the internal combustion engine and/or the electric motor.

Technical Field

The present invention relates to a hydraulic gearbox actuator which is particularly suitable for independently shifting a plurality of clutches of a manual gearbox, in particular a planetary gearbox, as used in the drive train of a motor vehicle.

Background

Gearbox actuators with hydraulic pumps are known, which hydraulic pumps can be driven electrically in particular. The hydraulic pump has two delivery outlets which are connected to a first pressure outlet and a second pressure outlet of the gearbox actuator and which can be supplied with hydraulic fluid pressure and a flow of hydraulic fluid. The two pressure pistons can be adjusted arbitrarily variably between the unactuated position and the actuated position by means of the hydraulic pressure and the flow of hydraulic fluid. The pressure piston is used to actuate a friction clutch, which is for example part of a dual clutch transmission.

In order to be able to control or regulate the pressure at the pressure outlets, a proportional valve is arranged between each delivery outlet and the associated pressure outlet.

The hydraulic pump can advantageously be designed as a drum pump or as a vane pump.

However, if it is intended to shift more than two clutches independently of each other, it is no longer possible to use such a gearbox actuator. By further disengaging the clutches towards the combustion engine, more than two clutches must be shifted independently of each other, for example in the case of a hybrid dual clutch gearbox or in the case of a gearbox with a plurality of planetary gearsets, one of its internal gear, sun gear and planet carrier may be non-rotatably supported in a variable speed manner by the clutches, or may be connected to another component, and furthermore the combustion engine and/or the electric motor may be connected or disconnected as required.

In certain applications with a gearbox of the type shown for example in DE 102014204009 a1, it is necessary to shift the first clutch connecting or releasing the internal combustion engine to or from the drive train. The first brake assigned to the first planetary gear set must be shifted. Furthermore, the second brake assigned to the second planetary gear set must be shifted. Finally, the second clutch must be actuated in order to shift the third gear.

Disclosure of Invention

It is an object of the present invention to provide a gearbox actuator which has a simple design and allows more than two clutches to be actuated independently of each other.

In order to achieve this object, according to the invention, a hydraulic gearbox actuator is provided with a hydraulic pump having a pump body in which a rotor is arranged, wherein a drive motor is provided with which the rotor can be driven in opposite directions, wherein two working chambers separated from one another are formed in the pump body, which working chambers each have two openings, of which at least three are connected to a respective pressure supply circuit, which is connected on one side to a reservoir and on the other side to one of the three pressure outlets of the gearbox actuator. The gearbox actuator according to the invention is based on the basic idea that the hydraulic pump operates in one direction or the other according to a pressure supply circuit which must be supplied with pressure for gear shifting. The function of the two openings of each working chamber is changed here. The opening which is the delivery side of the pump in one direction of rotation of the drive motor and thus in one direction of rotation of the rotor becomes the intake side in the opposite operating direction of the rotor. A particular advantage of this gearbox actuator is that the pump body can be provided with four openings which can all serve as delivery sides (although not simultaneously). However, each working chamber of the hydraulic pump may extend over an angle of more than 90 ° in the circumferential direction. Given that the two partitions between the working chambers are very thin, the working chambers can each extend over an angular range of practically 180 °. This results in a robust design and high pumping capacity as a whole.

If the gearbox actuator has three pressure outlets, it is possible to connect the fourth opening directly to the reservoir, since the fourth opening does not require supply pressure. If the hydraulic pump is operated in a direction such that the fourth opening is one of the two delivery sides, the corresponding working chamber delivers hydraulic fluid in a (substantially) pressureless manner in the circuit.

If the gearbox actuator has four pressure outlets, all the openings are connected to a pressure supply circuit which is connected on one side to the reservoir and on the other side to one of the four pressure outlets of the gearbox actuator. In this case, two of the pressure outlets are supplied with hydraulic fluid in a first direction of rotation of the drive motor, while the other two pressure outlets are supplied with hydraulic fluid in a second direction of rotation of the drive motor.

In order to be able to precisely control or regulate the pressure at the corresponding pressure outlet of the gearbox actuator, a proportional valve is preferably arranged in each pressure supply circuit between the opening and the pressure outlet.

According to a preferred embodiment it is provided that the reservoir is divided into separate chambers and that each proportional valve has a return line leading to such a chamber of the reservoir from which the pressure supply circuit is connected to the same working chamber that the pump draws. This ensures that, in the event of a leak or a fault in one of the pressure supply circuits or in the hydraulic circuit supplied by said pressure supply circuit, all hydraulic fluid is not lost through the faulty pressure supply circuit, but the remaining pressure supply circuit and the hydraulic circuit supplied by it remain fully operational for a period of time, so that the vehicle can be driven at least to the nearest parking space and even to the home or garage.

Preferably, a check valve is provided in each pressure supply circuit, which check valve is arranged between the inlet from the reservoir and the branch to the opening of the hydraulic pump. This eliminates the need for a separate valve that is switched when the rotational direction of the hydraulic pump is switched, but due to this design, the required fluid can only be output through the opening serving as the delivery outlet.

Preferably, a roller pump or a vane pump is used as the hydraulic pump, resulting in a compact design and high efficiency.

According to a refinement of the invention, the gearbox actuator according to the invention can be part of an assembly with a gearbox for a drive train of a motor vehicle, wherein the gearbox has at least one clutch and at least one brake, and the gearbox actuator can actuate the at least one clutch and the at least one brake. The transmission actuator, by virtue of having four pressure outlets, can activate different clutches and brakes independently of one another.

It may be provided here that two of the pressure outlets are connected to a respective clutch of the gearbox and two of the pressure outlets are connected to a respective brake of the gearbox. In particular, it can be provided that the brakes are each assigned to a planetary gear set and the clutch is assigned to the internal combustion engine and/or the electric motor.

Drawings

The invention will be described below with reference to three embodiments shown in the drawings, in which:

fig. 1 shows a circuit diagram of a hydraulic gearbox actuator according to a first embodiment of the invention.

Fig. 2 shows a schematic development of a pump body and a rotor of a hydraulic pump for use in the gearbox actuator of fig. 1.

Fig. 3 shows the circuit diagram of fig. 1, wherein the flow of hydraulic fluid in a first operating direction of the hydraulic pump is shown.

Fig. 4 shows the circuit diagram of fig. 1, wherein the flow of hydraulic fluid in a second operating direction of the hydraulic pump is shown.

Fig. 5 shows a circuit diagram of a hydraulic gearbox actuator according to a second embodiment of the invention.

Fig. 6 illustrates the circuit diagram of fig. 5, showing hydraulic fluid flow in a first operating direction of the hydraulic pump.

Fig. 7 shows the circuit diagram of fig. 5, wherein the flow of hydraulic fluid in a second operating direction of the hydraulic pump is shown.

FIG. 8 shows a circuit diagram of a hydraulic transmission actuator according to a third embodiment of the present invention; and

fig. 9 illustrates the circuit diagram of fig. 8, showing hydraulic fluid flow in a second operating direction of the hydraulic pump.

Detailed Description

Fig. 1 schematically shows a hydraulic gearbox actuator 1 having a hydraulic pump 2 and a reservoir 3. The reservoir is attached to the hydraulic pump 2, forming a compact unit.

The gearbox actuator 1 has four pressure outlets 10, 20, 30, 40 to which corresponding hydraulic lines can be connected, which lead to pressure pistons with which the clutches or brakes of the gearbox can be actuated. The clutches may be part of a dual clutch gearbox, may also be part of a planetary gear set, and/or may be used to connect or disconnect an electric motor and/or an internal combustion engine to or from the drive train of a motor vehicle.

In one example of use, the pressure outlets 10 and 40 may be used for a shifting clutch and the pressure outlets 20, 30 may be used for a shifting brake, by which one of the ring gear, the sun gear and the planet gear carrier of the first and second planetary gear sets may be fixed or released.

The hydraulic pump 2 has an electric motor 4 constituting a drive and has a pump body 5. The pump body 5 houses a rotor 6, which rotor 6 can be driven by the electric motor 4 in one or the other direction, depending on the operating direction of the electric motor 4.

The hydraulic pump is designed as a roller pump, so it combines a robust design with a high delivery capacity. The cylinder 7 of the cylinder pump is visible in fig. 2. They are housed in housings of the rotor 6 and extend along the internal profile of the pump body 5.

In the pump body, the two working chambers 8, 9 are delimited from each other. Each working chamber has two openings A, B or C, D. The openings A, B, C, D are arranged here such that they are located at the "beginning" and "end" of the respective working chamber, as viewed in the circumferential direction.

If the rotor 6 is operated in a first direction of rotation (for example, direction RH of fig. 2), the opening a of the working chamber 8 is located on the intake side, while the opening B is located on the delivery side. Thus, in the working chamber 9, the opening C is located on the intake side and the opening D is located on the delivery side. Thus, hydraulic fluid is drawn in through opening A, C and out through opening B, D.

If the hydraulic pump 2 is operated in the opposite direction LH, the function of the opening is reversed: opening B, D is the suction side of the pump and opening A, C is the delivery side.

Each opening a, B, C, D leads to a pressure supply circuit of the gearbox actuator. As shown in fig. 1, the opening D is connected to a pressure supply circuit leading to the pressure outlet 10. The opening a is connected to a pressure supply circuit leading to the pressure outlet 20. The opening B is connected to a pressure supply circuit leading to the pressure outlet 30. The opening C is connected to a pressure supply circuit leading to the pressure outlet 40.

Each pressure supply circuit comprises an inlet line 11, 21, 31, 41, a first check valve 12, 22, 32, 42, a second check valve 13, 23, 33, 43 and a proportional valve 14, 24, 34, 44.

The reservoir 3 is divided into a plurality of chambers 3A, 3B, 3C, 3D assigned to respective openings. When the opening a is the access side of the corresponding working chamber, it is extracted from the chamber 3A, and so on.

The corresponding openings a, B, C, D are connected to the two check valves 12, 13 or 22, 23; 32. 33; 42. 43 "its" pressure supply circuit. The check valves are arranged such that, if this opening is used as the inlet side for the hydraulic pump 2, hydraulic fluid is drawn out of the reservoir via the first check valve 12, 22, 32, 42; the second check valve 13, 23, 33, 43 is blocked. If the corresponding opening is the delivery side of the hydraulic pump 2, hydraulic fluid is delivered to the pressure outlet 10, 20, 30, 40 via the second check valve 13, 23, 33, 43; the first check valve 12, 22, 32, 42 is blocked.

The pressure of the respective pressure outlet 10, 20, 30, 40 can be controlled by means of the proportional valve 14, 24, 34, 44. The fluid pressure of the circuit of the pressure outlets 10, 20, 30, 40 may be regulated in conjunction with the pressure sensors 16, 26, 36, 46.

If the delivery pressure of the hydraulic pump 2 at the openings a, B, C, D serving as fluid outlets is above a predetermined value, the excess hydraulic fluid will be returned directly to the reservoir 3.

For this purpose, a return line 15, 25, 35, 45 is used which leads to a chamber in the reservoir from which withdrawal takes place for the corresponding pressure supply circuit. Thus, return line 15 leads to chamber 3C, return line 25 leads to chamber 3B, return line 35 leads to chamber 3A, and return line 45 leads to chamber 3D.

Fig. 3 shows the operating state of the gearbox actuator in the operating direction RH of the hydraulic pump, where the openings B and D are the delivery sides of the pump. The pressure outlets 10, 30 are supplied with hydraulic fluid, wherein the pressure is controlled or regulated by means of proportional valves 14, 34. The returning hydraulic fluid enters the chambers 3A and 3C of the reservoir 3 via return lines 15, 35. This ensures that in the event of a leak in the other hydraulic circuit, the unaffected hydraulic circuit remains operational for a period of time, so that the vehicle can still be parked safely, and can even be driven into a garage or home.

Fig. 4 shows an operating state of the transmission actuator in the operating direction LH of the hydraulic pump, in which the openings a and C are the delivery sides of the pump. The pressure outlets 20, 40 are thus supplied with hydraulic fluid, the pressure of which is controlled or regulated by means of the proportional valves 24, 44. The returning hydraulic fluid enters the chambers 3B and 3D of the reservoir 3 via return lines 25, 45.

A common feature of all pressure supply circuits of the hydraulic outlets 10, 20, 30, 40 is that the applied pressure can be substantially maintained as long as the corresponding proportional valve 14, 24, 34, 44 is correspondingly activated. This is firstly because the non-return valves 13, 23, 33, 43 do not leak and secondly because the proportional valves 14, 24, 34, 44 do not leak either.

Since each working chamber 8, 9 has only two openings A, B or C, D, a high conveying capacity results, since in practice 180 ° in the circumferential direction can be used to accommodate two openings of each working chamber.

Fig. 5 shows a second embodiment. The same reference numerals are used for components known from the first embodiment, and the above description is to be noted to that extent.

The difference between the first and second embodiment is that in the second embodiment only three pressure outlets 10, 20, 30 are provided.

The opening C is not assigned to any pressure supply circuit here. It is withdrawn directly from the reservoir 3.

In the first operating direction RH of the hydraulic pump 2, the operating mode corresponds to that of the first embodiment as shown in fig. 3.

In the second operating direction LH of the hydraulic pump 2, only the second pressure outlet 20 is supplied with hydraulic fluid; the working chamber 9 runs "unloaded" because it draws hydraulic oil out of the reservoir 3 and pumps it back directly. However, the chamber in which the extraction takes place and the chamber into which the reflux flows are separated here.

Fig. 8 shows a third embodiment. For the components known from the second embodiment, the same reference numerals are used, and to this extent, the above description is noted.

The difference between the second and third embodiments is that in the third embodiment the hydraulic fluid pumped through the working chamber 9 in the second operating direction is again returned (as in the first embodiment) into the chamber of the reservoir 3 from which it was drawn. For this purpose, the circuit connected to the opening C branches into an inlet circuit with a known check valve 42 and a return circuit 50. The latter is provided with a non-return valve 46 which acts in opposition to the first non-return valves 12, 22, 32, 42.