Internal-gear pump and hydraulic circuit for a motor vehicle drivetrain

Abstract

An internal-gear pump has a housing which has a first fluid port and a second fluid port. An inner rotor is mounted in the housing so as to be rotatable about an inner rotor axis and has an external toothing. An outer rotor is rotatable in the housing about an outer rotor axis and has an internal toothing which, to generate a pump action, engages with the external toothing of the inner rotor. The internal-gear pump furthermore has a ring element which is mounted movably in the housing so as to be pivotable between a first position and a second position. At least a third fluid port is formed on the housing. The third fluid port is arranged relative to the ring element such that, in the first position of the ring element, the third fluid port is connected to the second fluid port. In the second position, said third fluid port is separated from the second fluid port.

Claims

1. An internal-gear pump, having a housing which has a first fluid port and a second fluid port, an inner rotor which is mounted in the housing so as to be rotatable about an inner rotor axis and which has an external toothing, and an outer rotor which is rotatable in the housing about an outer rotor axis and which has an internal toothing which, to generate a pump action, engages with the external toothing of the inner rotor, and a ring element which is mounted movably in the housing so as to be rotatable about a ring element axis between a first position and a second position and which has a rotor receptacle for rotatably receiving the outer rotor, wherein the rotor receptacle is formed eccentrically with respect to the ring element, wherein at least a third fluid port is formed on the housing, and wherein the third fluid port is arranged relative to the ring element such that, in the first position of the ring element, the third fluid port is connected to the second fluid port, and in the second position, said third fluid port is disconnected from the second fluid port; and wherein the ring element provides eccentricity of the outer rotor with respect to the inner rotor, such that, in the event of a change in a rotational direction of the inner rotor, the ring element is driven along by the outer rotor by a fluid friction, so as to establish either the first position of the ring element or the second position of the ring element depending on the direction of rotation of the inner rotor.

2. The internal-gear pump according to claim 1, wherein at least a fourth fluid port is formed on the housing, wherein the fourth fluid port is arranged relative to the ring element such that, in the second position of the ring element, the fourth fluid port is connected to the second fluid port and, in the first position, said fourth fluid port is separated from the second fluid port.

3. The internal-gear pump according to claim 1, wherein the first position of the ring element is displaced from the second position by 180 degrees.

4. The internal-gear pump according to claim 1, wherein the first fluid port is in the form of a suction port regardless of the rotational direction of the inner rotor, and the second fluid port is in the form of a pressure port regardless of the rotational direction of the inner rotor.

5. A hydraulic circuit comprising an internal-gear pump, the internal-gear pump having a housing which has a first fluid port and a second fluid port, an inner rotor which is mounted in the housing so as to be rotatable about an inner rotor axis and which has an external toothing, and an outer rotor which is rotatable in the housing about an outer rotor axis and which has an internal toothing which, to generate a pump action, engages with the external toothing of the inner rotor, and a ring element which is mounted movably in the housing and which is pivotable between a first position and a second position, wherein the ring element provides eccentricity of the outer rotor with respect to the inner rotor, such that, in the event of a change in a rotational direction of the inner rotor, the ring element is driven along by the outer rotor by a fluid friction, so as to establish either the first position of the ring element or the second position of the ring element depending on the direction of rotation of the inner rotor, wherein at least a third fluid port is formed on the housing, wherein the third fluid port is arranged relative to the ring element such that, in the first position of the ring element, the third fluid port is connected to the second fluid port, and in the second position, said third fluid port is disconnected from the second fluid port, such that the ring element is a valve slide element of the hydraulic circuit.

6. The hydraulic circuit according to claim 5, wherein at least one of the third fluid port and a fourth fluid port is connected to a consumer section of the hydraulic circuit.

7. The hydraulic circuit according to claim 5, having a valve which is connected to the first fluid port or to the second fluid port of the internal-gear pump, wherein the valve is configured to be actuated as a function of the position of the ring element or is configured to be actuated as a function of a rotational direction of the inner rotor.

8. The hydraulic circuit according to claim 7, wherein the valve is configured to be actuated by means of a directly or indirectly acting actuating device, and wherein the directly or indirectly acting actuating device is connected to at least one of the third fluid port and a fourth fluid port.

9. The hydraulic circuit according to claim 7, wherein the valve is configured to be actuated by means of an electrical actuating device, wherein the internal-gear pump is assigned a rotational position sensor arrangement which detects the rotational position of the ring element and outputs a rotational position signal, and wherein the electrical actuating device is activated on the basis of the rotational position signal.

10. The hydraulic circuit according to claim 7, wherein the valve is configured to be actuated by means of an electric actuating device, wherein the hydraulic circuit has an electric motor which drives the inner rotor, wherein the motor is assigned a rotational direction sensor arrangement which detects a direction of rotation of the motor and outputs a rotational direction signal, and wherein the electrical actuating device is activated on the basis of the rotational direction signal.

11. The hydraulic circuit according to claim 10, wherein the rotational direction sensor arrangement is designed to detect the rotational direction of the motor on a basis of a commutation sequence of electrical connection phases of the motor.

12. The hydraulic circuit according to claim 10, wherein the rotational direction sensor arrangement is designed to detect the rotational direction of the motor on a basis of signals from a position encoder system of the motor.

13. A hydraulic circuit which comprises an internal-gear pump, having a housing which has a first fluid port and a second fluid port, an inner rotor which is mounted in the housing so as to be rotatable about an inner rotor axis and which has an external toothing, and an outer rotor which is rotatable in the housing about an outer rotor axis and which has an internal toothing which, to generate a pump action, engages with the external toothing of the inner rotor, a ring element which is mounted movably in the housing and which is pivotable between a first position and a second position, and a valve which is connected to the first fluid port or to the second fluid port of the internal-gear pump, wherein at least a third fluid port is formed on the housing, and wherein the third fluid port is arranged relative to the ring element such that, in the first position of the ring element, the third fluid port is connected to the second fluid port, and in the second position, the third fluid port is disconnected from the second fluid port; and wherein the ring element provides eccentricity of the outer rotor with respect to the inner rotor, such that, in the event of a change in a rotational direction of the inner rotor, the ring element is driven along by the outer rotor by a fluid friction, so as to establish either the first position of the ring element or the second position of the ring element depending on the direction of rotation of the inner rotor.

14. The hydraulic circuit according to claim 13, wherein the valve is configured to be actuated as a function of a rotational direction of the inner rotor.

15. The hydraulic circuit according to claim 13, wherein the valve is configured to be actuated by means of a directly or indirectly acting actuating device, and wherein the actuating device is connected to at least one of a third fluid port and a fourth fluid port.

16. The hydraulic circuit according to claim 13, wherein the valve is configured to be actuated by means of an electrical actuating device, wherein the internal-gear pump is assigned a rotational position sensor arrangement which detects a rotational position of the ring element and outputs a rotational position signal indicative of the rotational position of the ring element, and wherein the electrical actuating device is activated on the basis of the rotational position signal.

17. The hydraulic circuit according to claim 13, wherein the valve is configured to be actuated as a function of a position of the ring element.

18. The hydraulic circuit according to claim 13, wherein the valve is configured to be actuated by means of an electric actuating device, wherein the hydraulic circuit has an electric motor which drives the inner rotor, wherein the motor is assigned a rotational direction sensor arrangement which detects a direction of rotation of the motor and outputs a rotational direction signal indicative of the direction of rotation of the motor, and wherein the electrical actuating device is activated on the basis of the rotational direction signal.

19. The hydraulic circuit according to claim 18, wherein the rotational direction sensor arrangement is designed to detect the rotational direction of the motor on a basis of a commutation sequence of electrical connection phases of the motor.

20. The hydraulic circuit according to claim 18, wherein the rotational direction sensor arrangement is designed to detect the rotational direction of the motor on a basis of signals from a position encoder system of the motor.

Description

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING

(1) Exemplary embodiments of the invention are illustrated in the drawing and will be explained in more detail in the description below, in which:

(2) FIG. 1 is a schematic illustration of an internal-gear pump with a ring element in a first rotational position;

(3) FIG. 2 shows the internal-gear pump from FIG. 1 with the ring element in a second rotational position;

(4) FIG. 3 shows a schematic cross-sectional view of an internal-gear pump according to an embodiment of the invention, specifically with a ring element in a first rotational position;

(5) FIG. 4 shows the internal gear wheel pump of FIG. 3 with the ring element in a second rotational position;

(6) FIG. 5 shows a schematic, perspective view of a further embodiment of an internal-gear pump according to the invention, with a ring element in a first rotational position;

(7) FIG. 6 is a schematic illustration of an internal-gear pump according to an embodiment of the invention, wherein a ring element is mounted so as to be rotatable concentrically with respect to the axis of rotation of an inner rotor and is illustrated in a first rotational position;

(8) FIG. 7 shows the internal-gear pump from FIG. 6 with the ring element in a second rotational position;

(9) FIG. 8 shows a motor vehicle drivetrain having a hydraulic circuit according to the invention in schematic form;

(10) FIG. 9 shows a further embodiment of a hydraulic circuit according to the invention;

(11) FIG. 10 shows a further embodiment of a hydraulic circuit according to the invention; and

(12) FIG. 11 shows a further embodiment of a hydraulic circuit according to the invention.

PREFERRED EMBODIMENTS

(13) FIG. 1 schematically illustrates an internal-gear pump 10. The internal-gear pump 10 comprises a housing 12 with a schematically indicated inner rotor 14 and a schematically indicated outer rotor 16. The internal-gear pump 10 is preferably in the form of a toothed-ring pump or gerotor pump, such that an internal toothing (not illustrated in any more detail) of the outer rotor 16 has one tooth more than the external toothing of the inner rotor 14. A pump action is realized by meshing of the toothings. It is preferably the case that the inner rotor 14 is driven, in particular by means of an electric motor. A ring element 20 is mounted, in the manner of a reversing ring, in the housing 12. The ring element 20 is pivotable concentrically with respect to an axis of the inner rotor 14 between two rotational positions, one of which is illustrated in FIG. 1 at DP1. The ring element 20 furthermore has an outer rotor receptacle (not shown in any more detail) which is formed eccentrically with respect to the inner rotor axis.

(14) On the housing 12 there is formed a first fluid port 22, which is preferably in the form of a suction port and connected to a tank 23. Furthermore, the housing 12 has a second fluid port 24, which is preferably in the form of a pressure port. In FIG. 1, the internal-gear pump 10 is driven in a first direction of rotation DR1. The pressure level at the first fluid port 22 is denoted by P.sub.L. The pressure level at the second fluid port 24 is denoted by P.sub.H, wherein P.sub.H>P.sub.L.

(15) In the illustrated rotational position DP1 of the ring element 20, a third fluid port 26 of the housing 12 is connected to the second fluid port 24, such that a pressure level P.sub.H likewise prevails at said second fluid port. The housing 12 optionally has a fourth fluid port 28 which, in the illustrated rotational position DP1 of the ring element 20, is not connected to the second fluid port 24, such that, at said fourth fluid port, a pressure level P.sub.L prevails which however need not imperatively be equal to the pressure level P.sub.L in the first fluid port 22.

(16) FIG. 2 shows the internal-gear pump 10 of FIG. 1, wherein the ring element 20 is situated in the second rotational position DP2. Furthermore, the inner rotor 14 is being driven in an opposite rotational direction DR2. In this case, as before, a pressure level P.sub.L prevails at the first fluid port 22, and a pressure level P.sub.H prevails at the second fluid port 24. The third fluid port 26 is separated from the second fluid port 24 by the ring element 20, such that a pressure level P.sub.L prevails at said third fluid port. If a fourth fluid port 28 is provided, the latter is preferably connected to the second fluid port 24 in the second rotational position DP2 of the ring element 20, such that a pressure level P.sub.H prevails at said fourth fluid port.

(17) FIGS. 3 and 4 illustrate an internal-gear pump 10 which generally corresponds in terms of design and mode of operation to the internal-gear pump 10 of FIG. 1. Identical elements are denoted by the same reference signs.

(18) It can be seen that an inner rotor 14 is mounted on the housing 12 so as to be rotatable about an inner rotor axis 32. The ring element 20 has a rotor receptacle 34 which is formed eccentrically in relation to the inner rotor axis 32. The outer rotor 16 is received within, and rotatably mounted in, the rotor receptacle 34. The outer rotor axis 36 is, owing to the eccentricity of the rotor receptacle 34, arranged eccentrically in relation to the inner rotor axis 32. In the first rotational position DP1 of the ring element 20 as shown in FIG. 3, said ring element forms, between an outer circumferential section of the ring element 20 and an inner circumferential section of the housing 12 within which the ring element 20 is rotatably mounted, an annular chamber 38 which, in the present case, extends over an angle range of approximately 180.

(19) The illustration in FIG. 3 also shows that the internal-gear pump 10 has, in a manner known per se, a kidney-shaped suction port 40 which is connected to the first fluid port 22. Furthermore, the fluid pump 10 of FIG. 3 has a kidney-shaped pressure port 42 which is connected, in a manner known per se, to the second fluid port 24.

(20) Also illustrated in the housing 12 is a schematically illustrated first connection 44 between the kidney-shaped pressure port 42 and the annular chamber 38 illustrated in FIG. 3, wherein the annular chamber 38 is denoted in FIG. 3 by 38-1 and, in the present case, is connected to the third fluid port 26.

(21) The internal-gear pump 10 furthermore comprises a second connection 46 between the kidney-shaped pressure port 42 and another inner circumferential section of the housing 12, which in the present case is covered by the ring element 20. The ring element 20 consequently acts as a control slide which, in the first rotational position DP1 shown in FIG. 3, connects the second fluid port 24 to the third fluid port 26.

(22) FIG. 4 shows the internal-gear pump 10 of FIG. 3, wherein the ring element 20 is situated in the second rotational position DP2. Here, the ring element 20 now overlaps the first connection 44, whereas the kidney-shaped pressure port 42 is connected via the second connection 46 to the annular chamber now denoted by 38-2, and consequently to the fourth fluid port 28.

(23) The connections 44, 46 shown in the illustrations are merely of a schematic nature and are intended to indicate that, depending on the rotational position of the ring element 20, either the third fluid port 26 or the fourth fluid port 28 is connected to the second fluid port 24, such that the functionality illustrated in FIGS. 1 and 2 is realized.

(24) FIG. 5 shows a further embodiment of an internal-gear pump 10 which generally corresponds in terms of design and mode of operation to the internal gear wheel pump 10 of FIGS. 3 and 4. Identical elements are therefore denoted by the same reference signs. Primarily the differences will be explained below.

(25) Accordingly, the housing 12 of the internal-gear pump 10 has a stop 50 by means of which the ring element 20 can be held in the respective rotational positions DP1, DP2 (DP1 is shown in FIG. 5). In the present case, for simplicity, the stop 50 is formed by a pin 52 which extends through a wall of the housing 12 and which, depending on the rotational position, engages on a first shoulder 54 or on a second shoulder 56 of the ring element 20. The shoulders 54, 56 enclose the annular chamber 38 between them in the circumferential direction.

(26) FIG. 5 also shows that the third fluid port 26 and the fourth fluid port 28 may be formed on a common outer surface of the housing 12, and preferably on an outer surface on which the second fluid port 24 is also formed. The first fluid port 22 is formed on the axially opposite side and is merely schematically indicated in FIG. 5.

(27) FIGS. 6 and 7 show an alternative embodiment of an internal-gear pump 10 which generally corresponds in terms of design and mode of operation to the internal-gear pump 10 of FIGS. 1 and 2. Identical elements are therefore denoted by the same reference signs. Primarily the differences will be explained below.

(28) In the case of the internal-gear pump 10 of FIGS. 6 and 7, the ring element 20 is formed not as a reversing ring but merely as a control slide. Consequently, in one direction of rotation DR1, the first fluid port 22 is in the form of a suction port and the second fluid port 24 is in the form of a pressure port, whereas in the second direction of rotation DR2 (FIG. 7), the second fluid port 24 is in the form of a suction port and the first fluid port 22 is in the form of a pressure port. As a result of the ring element 20 being designed as a control slide, it is the case that, in the first rotational position DP1 of the ring element 20, the third fluid port 26 is connected to the second fluid port 24, whereas, in the second rotational position DP2, the fourth fluid port 28 is connected to the first fluid port 22, which than acts as pressure port. Since, in this embodiment, the ring element 20 acts merely as a control slide and not as a reversing ring, it is however possible to freely select, within broad limits, which fluid port the third and fourth fluid ports 26, 28 are connected to in the respective rotational positions DP1, DP2. Alternatively, in the configuration of FIG. 6, it would also be possible for the third fluid port 26 to be connected to the first fluid port 22, and for the fourth fluid port 28 to be connected to the second fluid port 24, such that a correspondingly reversed fluid port connection is realized in FIG. 7.

(29) In FIG. 8, a drivetrain for a motor vehicle is illustrated in schematic form and denoted generally by 60. The drivetrain 60 comprises a drive motor 62. The drive motor 62 may be an internal combustion engine, but may also be an electric drive motor for providing drive power. The drivetrain 60 also comprises a clutch arrangement 64, which may be a single clutch or a dual-clutch arrangement. Furthermore, the drivetrain 60 comprises a transmission arrangement 66, which may comprise a single-stage or multi-stage transmission, and a transmission without or with gearshift capability. In the case of a transmission with gearshift capability, the transmission arrangement 66 may be a dual-clutch transmission. Filially, the drivetrain 60 comprises a differential 68 by means of which drive power can be distributed between two driven wheels 70L, 70R of the motor vehicle.

(30) The drivetrain 60 also comprises a hydraulic circuit 74. In the hydraulic circuit 74, there is provided an internal-gear pump 10 which, in terms of functionality, is preferably designed in the manner of one of the internal-gear pumps 10, 10, 10 of FIGS. 1 to 5. The internal-gear pump 10 is driven by means of an electric motor 76, wherein the electric motor 76 can be activated in both rotational directions, as schematically indicated in FIG. 8 by a double arrow.

(31) The second fluid port 24 and the third fluid port 26, and if appropriate a fourth fluid port 28, of the internal-gear pump 10 may be connected directly to hydraulic consumer sections, as will be explained below.

(32) In the present case, however, the hydraulic circuit 74 comprises a valve 80, which in the present case is in the form of a 3/2 directional valve. The valve 80 comprises a first hydraulic actuating device 82 for moving the valve 80 into a first switching position. Furthermore, the valve 80 may have a restoring spring 84 which counteracts the first hydraulic actuating device 82. The first hydraulic actuating device 82 may for example be connected to the third fluid port 26.

(33) It is furthermore possible for the valve 80 to have a second hydraulic actuating device 86. In this case, the second hydraulic actuating device 86 is preferably connected to the fourth fluid port 28.

(34) An inlet of the valve 80 is connected to the second fluid port 24. A first outlet of the valve 80 is connected to a first hydraulic consumer section 90, which may for example be assigned to the clutch arrangement 64. A second outlet of the valve 80 is, in the present case, connected to a second hydraulic consumer section 92, which may for example be assigned to the transmission arrangement 66 or to the drive motor 62.

(35) In some embodiments of the hydraulic circuit 74, a central control device 94 (transmission control unit) is provided which actuates the consumer sections 90, 92.

(36) As schematically indicated in FIG. 8, the third fluid port 26 may also be directly connected to a consumer section, as shown in the present case by a third hydraulic consumer section 98.

(37) Furthermore, the second and/or the fourth fluid port 24 may also be directly connected to a hydraulic consumer section of said type.

(38) The consumer sections are generally designed for supplying fluid to certain components of the drivetrain 60. The consumer sections may each comprise actuator devices for actuating certain components of the drivetrain 60, such as, for example, clutches of the clutch arrangement 64 and/or gearshift clutches of the transmission arrangement 66. Furthermore, the consumer sections may in each case alternatively or additionally be purely in the form of lubricating and/or cooling sections.

(39) FIGS. 9 to 11 show further embodiments of hydraulic circuits, which may generally correspond in terms of design and mode of operation to the hydraulic circuit 74 of FIG. 8. Identical elements are therefore denoted by the same reference signs. Primarily the differences will be explained below.

(40) In the case of the hydraulic circuit 74 of FIG. 9, a valve 80 has an electrical actuating device 102, wherein the valve 80 is preloaded by means of a restoring spring 84. Furthermore, in the present case, the hydraulic circuit 74 comprises a rotational position sensor arrangement 104 which comprises a rotational position sensor 106 which can detect the rotational position DP of the ring element 20 of the pump 10, for example by inductive, optical, capacitive, resistive or other means.

(41) In the present case, the rotational position sensor arrangement 104 furthermore comprises a switch 108 which connects a voltage source 110 to the electrical actuating device 102. The switch 108 can be actuated by means of a signal from the rotational position sensor 106.

(42) In one variant, the rotational position sensor 106 may also be connected to an amplifier 112 in order to activate the electrical actuating device 102 even without a switch 108.

(43) In the variant 74 shown in FIG. 10, the same valve 80 is provided, wherein a rotational direction sensor arrangement 116 is provided which detects the rotational direction of the pump 10 or of the electric motor 76. In the present case, the rotational direction DR of the electric motor 76 is detected by means of a sensor 120 which detects the commutation sequence of connection phases 118 of the electric motor 76 and derives the direction of rotation therefrom. A rotational direction signal derived therefrom is amplified by means of an amplifier 112 and is used for activating the electrical actuating device 102.

(44) FIG. 11 shows a modification of the embodiment of FIG. 10, wherein a hydraulic circuit 74 has an electric motor 76 which comprises a position encoder system 122 by means of which the rotational position and/or rotational direction of the electric motor 76 can be detected. In the present case, the position encoder system 122 is connected to a sensor 124, which detects the rotational direction DR and which may comprise an amplifier 112 by means of which the electrical actuating device 102 can be directly activated.