CN104755756B

CN104755756B - Inclined disc type machine

Info

Publication number: CN104755756B
Application number: CN201380055766.3A
Authority: CN
Inventors: D·施尼特格; D·瓦勒; T·纳夫齐; F·肖尔茨
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2012-08-28
Filing date: 2013-07-17
Publication date: 2018-02-16
Anticipated expiration: 2033-07-17
Also published as: DE102012215240A1; IN2015DN01593A; EP2890892A1; WO2014032849A1; CN104755756A

Abstract

The present invention relates to one kind as axial poiston pump (2) and/or the inclined disc type machine (1) of axial piston motor (3),It includes the cartridge type rotary drum (5) with piston hole (6) that can rotationally or be rotatably supported around rotation axis (8),The piston (7) that can be supported on to motion in piston hole (6),The drive shaft (9) being connected without relative rotation with cartridge type rotary drum (5),Can be around the revolution wobble-member (14) that axis of oscillation (15) swingingly support,For turning round the wobble-member bearing of wobble-member (14),For at least one pendulous device (24) for swinging revolution wobble-member (14) (pendulous device is connected on each link position (32) with revolution wobble-member (14)),For by hydraulic fluid import rotation piston hole (6) in and/or the low-pressure opening derived from the piston hole of the rotation,For the high pressure opening that hydraulic fluid is exported and/or imported in the piston hole of rotation from the piston hole (6) of rotation,Wherein,In imaginary section,Inclined disc type machine (1) is divided into by the imaginary Part I with the high pressure opening on cartridge type rotary drum (5) and the imaginary Part II with the low-pressure opening on cartridge type rotary drum (5) with the rotation axis of cartridge type rotary drum (5) (8) the and in parallel and imaginary cutting plane vertical with the axis of oscillation (15) of revolution wobble-member (14),And the composite force being applied to by least one pendulous device (24) on revolution wobble-member (14) is based particularly on the construction of at least one link position (32) and/or arrangement and can imported on imaginary Part II in the revolution wobble-member (14),To reduce on the imaginary Part I the caused pressure between the wobble-member bearing and revolution wobble-member (14).

Description

Swash plate machine

Technical Field

The present invention relates to a swash plate machine and a drive train.

Background

Swash plate machines are used as axial piston pumps for converting mechanical energy into hydraulic energy and as axial piston motors for converting hydraulic energy into mechanical energy. A cartridge drum having a piston bore is rotatably or rotationally supported and a piston is disposed in the piston bore. The cartridge drum is connected to the drive shaft without relative rotation, and hydraulic fluid at high pressure temporarily acts on a first portion of the rotating piston bore and hydraulic fluid at low pressure temporarily acts on a second portion of the rotating piston bore. The swing member is supported so as to be capable of swinging about a swing axis, and a restraint plate having a shoe is supported on the swing member. The piston is fixed on the sliding shoe. The constraining disc with the slipper carries out a rotational movement with the drum about the axis of rotation and, here, the planar bearing surface of the swivel wobble is oriented at an acute angle, for example, between 0 ° and +20 ° and between 0 ° and-20 ° with respect to the axis of rotation of the drum. In the case of a rotary wobble whose bearing surface is oriented perpendicularly to the axis of rotation, i.e. with a wobble angle of 0 °, swash plate machines cannot convert mechanical energy into hydraulic energy and vice versa. With two pivoting devices, the pivoting angle of the bearing surface relative to the axis of rotation can be varied, for example, between-20 ° and +20 °, and the pivoting devices exert a pressure on the pivoting rocker. The rotary wobble member is supported on two bearing bushes of the housing of the swash plate machine. In this case, a greater force is exerted on the pivoting wobble plate by the rotating piston at a high pressure of the hydraulic fluid than by the piston at a low pressure of the hydraulic fluid. Thus, the two bearing sleeves are applied with uneven pressure, and the bearing sleeve on an imaginary first part of the swash plate machine is subjected to a greater pressure than the bearing sleeve on an imaginary second part of the swash plate machine having low-pressure openings. The swash plate machine is divided into an imaginary first part and an imaginary second part by an imaginary sectional plane or central plane parallel to the rotational axis of the drum and above it and perpendicular to the axis of oscillation of the rotary wobble member. Due to these different pressures on the two bearing sleeves in the two imaginary parts of the swash plate machine, high mechanical wear occurs on the one bearing sleeve or the respective slide bearing, so that the service life of the swash plate machine is reduced in a disadvantageous manner. Furthermore, due to the high pressures, expensive measures for the plain bearings of the rotary oscillating piece are required in an expensive and costly manner. In this case, the two wobble devices and thus the two connecting points between the wobble device and the pivoting wobble plate are also arranged centrally, i.e. in an imaginary sectional plane or central plane, so that the pressure exerted by the two wobble devices on the pivoting wobble plate is distributed uniformly over the two bearing sleeves. However, because the first part of the swash plate machine is subjected to a greater force by the piston at high pressure than by the piston at low pressure, the said uneven pressure is just generated on both bearing sleeves, and therefore the bearing sleeve on an imaginary first part of the swash plate machine has a much greater pressure than the bearing sleeve on an imaginary second part of the swash plate machine.

EP 1013928 a2 shows an axial piston pump of the swash plate type with a rotatably driven cylinder drum having a plurality of piston bores arranged therein, wherein pistons which are linearly movable between a lower dead center and an upper dead center are arranged in the piston bores which are separated from one another by a partition in each case, and a control disk having a low-pressure connecting kidney and a high-pressure connecting kidney is provided.

CH 405934 shows a swash plate axial piston pump, the non-rotating cylinder of which can be moved longitudinally to vary the delivery volume as a function of the delivery pressure, wherein the slide valve unit is controlled to fix the slide valve piston on the cylinder which is pressed by a spring in the direction of increasing the delivery volume.

DE 2733870C 2 shows a control device for a swash plate axial piston pump in which a hydraulically loaded swivel wing on the motor acts on both sides of a swivel plate in order to swivel the swash plate, wherein the two motors can be controlled by means of a plate-shaped control slide valve which is pivotably arranged about the swivel axis of the swivel plate and serves to adjust the delivery volume of the pump.

Disclosure of Invention

The invention relates to a swash plate machine as an axial piston pump and/or an axial piston motor, comprising a drum which is mounted so as to be rotatable or rotatable about an axis of rotation and has a piston bore, a piston which is mounted so as to be movable in the piston bore, a drive shaft which is connected to the drum in a rotationally fixed manner, a pivoting rocker which is mounted so as to be pivotable about a pivot axis, a rocker bearing for the pivoting rocker, at least one pivoting device for pivoting the pivoting rocker and which is connected to the pivoting rocker at one connecting point, low-pressure openings for introducing hydraulic fluid into the rotating piston bore and/or out of the rotating piston bore, and high-pressure openings for introducing hydraulic fluid out of and/or into the rotating piston bore, wherein, in an imaginary sectional plane, the swash plate is mounted so as to be pivotable or pivotable about the axis of rotation of the drum and parallel thereto and perpendicular to the pivot axis of the pivoting rocker The machine is divided into an imaginary first part with a high-pressure opening on the drum and an imaginary second part with a low-pressure opening on the drum, and the resultant force exerted by the at least one oscillating device on the rotary oscillating piece can be introduced into the rotary oscillating piece on the imaginary second part, in particular on the basis of the configuration and/or arrangement of the at least one connecting location, in order to reduce the pressure generated on the imaginary first part between the oscillating piece bearing and the rotary oscillating piece.

The resultant force, in particular the resultant force, which is exerted on the pivoting and oscillating element by the at least one oscillating device is exerted on the imaginary second part of the pivoting and oscillating element. The force indirectly exerted by the movably mounted piston on the rotary wobble-piece is greater on an imaginary first part of the swash plate machine than on an imaginary second part of the swash plate machine, since the piston on the imaginary first part of the swash plate machine is under high pressure and therefore a greater force is exerted by the piston on the rotary wobble-piece on the first part. Thus, in order to distribute the force acting on the oscillating piece bearing evenly between the imaginary first and second parts, the resultant force exerted by the at least one oscillating device acts on the imaginary second part of the swash plate machine or the rotary oscillating piece, so that the oscillating piece bearing is thus loaded less force on the first part and more force on the imaginary second part than the resultant force exerted on the imaginary sectional plane or central plane. In a corresponding arrangement, a substantially uniform force loading of the wobble plate bearing between the first and second imaginary sections can thus be achieved.

In a further embodiment, the wobble-element bearing is designed such that, when the rotary wobble element is rocked, the pivot axis of the rotary wobble element performs a rocking motion or a rotational and translational motion. The pivoting pendulums thus perform both a pivoting movement and a translational movement during pivoting.

Preferably, the at least one pivoting device is designed as a spindle drive having an electric motor for driving the spindle drive.

In an additional embodiment, the resultant force exerted by the at least one oscillating device on the rotary oscillating member can only be introduced into the rotary oscillating member on the second portion, and/or the swash plate machine comprises a plurality of oscillating devices, and in all the oscillating devices, the resultant force exerted by the oscillating devices on the rotary oscillating member is introduced into the rotary oscillating member only on the second portion. The resultant force is preferably introduced or can be introduced into the rotary oscillating piece by all the oscillating devices, in particular only at the second portion, so that all the resultant force exerted by the oscillating devices on the rotary oscillating piece contributes to a uniform force loading of the oscillating piece bearing.

In a supplementary variant, the resultant force exerted by the at least one pivoting device on the pivoting and swinging part can be introduced into the pivoting and swinging part on the second part at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane, and/or the at least one connection point can be formed on the second part at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane, and/or the swash plate machine comprises a plurality of pivoting devices, and in all pivoting devices the resultant force exerted on the pivoting and swinging part can be introduced into the pivoting and swinging part on the second part at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane, and/or the at least one connection point and/or the at least one pivoting device, In particular, all connection points and/or all pendulums are formed on the second part at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane.

In a supplementary variant, the difference between the distance of the geometric center of gravity of the high-pressure opening from the imaginary sectional plane and the distance of the at least one connecting point from the imaginary sectional plane has a value of less than 1cm, 3cm, 5cm, 7cm, 10cm or 20cm, wherein the distance is oriented perpendicular to the imaginary sectional plane.

Expediently, the swash plate machine has two pendulums, in particular only two pendulums, the two pendulum arms are formed on and/or next to the swivel pendulum and the connecting points are formed on the end regions of the pendulum arms and/or at least one connecting point, in particular all connecting points, is formed, in particular, only outside of an imaginary sectional plane. Thus, at least one interface is not truncated by an imaginary sectional plane.

In an additional embodiment, the at least one wobble device has an adjusting piston for applying a pressure force to the at least one connection point, and the pressure force is preferably oriented in the direction of the axis of rotation toward the rotary wobble element. The wobble device has an adjusting piston which is acted upon, in particular by a hydraulic fluid, and in this case, in particular only by the adjusting piston, applies a pressure in the direction of the axis of rotation from the wobble device in the direction of the swivel swing to the swivel swing at the connection point.

In a supplementary embodiment, the swash machine has a housing and the housing is constructed in one or more parts and/or the wobble bearing is formed by two bearing sleeves, on which one bearing section of the rotary wobble is supported indirectly or directly in each case and which are preferably arranged spaced apart in an imaginary first and second part of the swash machine. The two bearing sleeves can also be connected to one another with the connecting shell of the bearing sleeve being interrupted by an imaginary sectional plane.

In an additional embodiment, the bearing sleeve is formed on the housing, and/or the bearing sleeve and the at least one bearing section are formed as circular segments in a cross section parallel to the imaginary cross-sectional plane. The bearing sleeve and the bearing section are of circular-segment-shaped configuration in a cross section parallel to the imaginary cross-sectional plane, so as to support the swing member swingably about the swing axis.

In a supplementary embodiment, the wobble bearing is designed as a plain bearing, and a sliding intermediate part each made of metal, for example brass, plastic, for example PTFE (polytetrafluoroethylene), or metal with a plastic coating, for example PTFE, for example steel or brass, is arranged between the bearing sleeve and the bearing section. A sliding intermediate part, for example made of PTFE, is used to reduce the friction on the sliding bearing.

In an additional embodiment, the wobble bearing is designed as a rolling bearing, and rolling elements, for example balls or rollers, are arranged between the bearing sleeve and the bearing section.

In an additional embodiment, the swash plate machine comprises a valve disk with high-pressure openings and low-pressure openings, and the valve disk is supported on the drum, and preferably the high-pressure openings and the low-pressure openings are kidney-shaped. The high pressure opening is configured on an imaginary first part of the swash plate machine and the low pressure opening is configured on an imaginary second part of the swash plate machine. The valve disks are fixed and do not perform a rotational movement and are supported indirectly or directly on the rotating drum cylinder. The piston bores formed in the drum are therefore alternately charged with hydraulic fluid under high or low pressure.

In a supplementary embodiment, the swash plate machine has a constraining plate, and on the constraining plate are fixed shoes, on which in each case one piston is fixed, so that the constraining plate carries with it the pistons for the rotary movement of the drum, and the constraining plate is supported indirectly or directly on the rotary wobble member.

The drive train according to the invention for a motor vehicle comprises at least one swash plate machine for converting mechanical energy into hydraulic energy and vice versa, at least one pressure accumulator, wherein the swash plate machine is designed as the swash plate machine described in the present patent application.

Preferably, the drive train comprises two swash plate machines which are hydraulically connected to one another and serve as a hydraulic transmission and/or the drive train comprises two pressure accumulators as a high-pressure accumulator and a low-pressure accumulator.

Drawings

Embodiments of the present invention are described in detail below with reference to the accompanying drawings. In the drawings:

figure 1 shows a longitudinal section of a swash plate machine,

figure 2 shows a cross section a-a according to figure 1 of a valve disc of a swash plate machine and a view of a rotary wobble,

figure 3 shows a perspective view of a rotary wobble member having two pendulums, a cartridge drum and a valve disc,

figure 4 shows a cross section of a rotary oscillating piece and of a bearing bush for a rotary oscillating piece of a swash plate machine according to figure 1,

FIG. 5 shows a beam model of a swing-member, and

fig. 6 shows a drive train for a motor vehicle.

Detailed Description

The swash plate machine 1 shown in longitudinal section in fig. 1 serves as an axial piston pump 2 for converting or converting mechanical energy (torque, rotational speed) into hydraulic energy (volume flow, pressure) or as an axial piston motor 3 for converting or converting hydraulic energy (volume flow, pressure) into mechanical energy (torque, rotational speed). The drive shaft 9 is mounted on the one-piece or multi-piece housing 4 of the swash plate machine 1 (fig. 1) in a rotatable or rotatable manner about the axis of rotation 8 by means of two bearings 10. The drum 5 is connected to the drive shaft 9 in a rotationally fixed manner, so that the drum 5 thus carries along with it the rotary movement of the drive shaft 9. A plurality of piston bores 6 having any cross section, for example a square or circular cross section, are machined in the drum 5. The longitudinal axis of the piston bore 6 is oriented substantially parallel to the rotational axis 8 of the drive shaft 9 or the drum 5. The pistons 7 are each mounted movably in the piston bores 6. A pivoting rocker 14 is mounted on the housing 4 so as to be pivotable about a pivot axis 15. The pivot axis 15 is oriented perpendicular to the plane of view of fig. 1 and 4 and parallel to the plane of view of fig. 2. The axis of rotation 8 of the drum 5 is located parallel to and in the plane of view of fig. 1 and perpendicular to the plane of view of fig. 2.

The rotary wobble-element 14 has a planar or flat bearing surface 18 for indirectly bearing the restraint disk 37, since an intermediate disk 38 is arranged between the restraint disk 37 and the bearing surface 18 of the rotary wobble-element 14. The constrainer disc 37 is provided with a plurality of shoes 39, and here, each shoe 39 is connected to one piston 7. For this purpose, the sliding shoe 39 has a bearing ball 40 (fig. 1) which is fixed in a bearing seat 59 on the piston 7. The bearing ball 40, which is partially designed in the form of a sphere, and the bearing seat 59 are designed to be complementary to one another or to be matched spherically, so that a continuous connection between the piston 7 and the skid shoe 39 is thus possible with a corresponding movement of the bearing ball 40 and the bearing seat 59 on the piston 7 relative to one another. The intermediate disk 38 serves to reduce the friction between the rotating restraint disk 37 and the rotary wobble plate 14, which is mounted in a rotationally fixed manner and not in rotation about the axis of rotation 8. The slipper 39 carries along with it a rotary movement about the axis of rotation 8, on account of the connection of the piston 7 to the rotating drum 5 and of the bearing block 59 to the slipper 39, and the constraining disc 37 also carries along with it a rotary movement about the axis of rotation 8, on account of the fixed connection or arrangement of the slipper 39 on the constraining disc 37. In order to bring the restraint disk 37 into continuous indirect contact with the bearing surface 18 of the rotary wobble member 14, it is pressed under pressure against the bearing surface 18 by a pressure spring 41.

The wobble-swing part 14 is mounted so as to be able to swing about a swing axis 15 as already described, and furthermore has an opening 42 (fig. 1 and 3) for passing through the drive shaft 9, the wobble-swing part bearing 20 is formed on the housing 4, and, due to the cross section formed in fig. 1, the wobble-swing part bearing 20 is shown only in dashed lines, the bearing sleeve 21 is formed on the wobble-swing part bearing 20 (fig. 4), which is formed as a circular segment in a cross section perpendicular to the swing axis 15 according to fig. 1 and 4, here, two bearing segments 17 are formed on the wobble-swing part 14, which are circular segments in the cross section, which are formed as circular segments, the two bearing segments 17 of the wobble-swing part 14 are indirectly mounted on the two bearing sleeves 21 of the wobble-swing part bearing 20, because, between the bearing sleeves 21 and the bearing segments 17 of the wobble-swing part 14 are respectively arranged from plastic, in a sliding intermediate piece 23, the bearing arrangement is shown between the bearing sleeve 21 and the bearing segments 17 of the wobble-swing part 14, the virtual segment is arranged in a virtual section 35, which is located in a vertical plane 33 in a virtual second, which is located in a virtual section perpendicular to the swing plane 34, which is located in the swing plane, in a virtual section perpendicular to the virtual swing plane 33, which is perpendicular to the swing plane 33, which is located in the swing plane 20, 2, and to the virtual swing plane, which is located in the virtual second virtual swing plane, which is located in the virtual swing plane, 2, in the virtual swing plane, which is perpendicular to the virtual swing plane, 2, which is located in the virtual swing axis 15, in the virtual swing plane, and to the virtual swing plane 33, which is located in the virtual swing plane 14, in the virtual swing plane 20, which is located in the virtual swing plane, 2, in fig. 1, 2, and which is located in the virtual swing axis 15, and to the virtual swing plane, which is located in the virtual swing axis 15, and which is located in fig. 1, and the virtual swing axis 15, which is located in the virtual swing axis 9, and which is located in the virtual swing axis 9, which is located in fig. 1, and which is located in the virtual swing axis 9, which is located in the virtual swing axis 9.

The first and second oscillating devices 25, 26 as oscillating devices 24 are arranged on an imaginary second section 35, and the connecting point 32 has a spacing 36 (fig. 2 and 5) with respect to an imaginary sectional plane 33 as a central connecting point 32 between the oscillating devices 24 and the rotary oscillating piece 14. The distance 36 is perpendicular to the imaginary sectional plane 33 or represents the minimum distance from the central connecting point 32 to the imaginary sectional plane 33. The two pivoting devices 24 each have an adjusting piston 29, which is mounted so as to be movable in an adjusting cylinder 30. The axis of the adjusting piston 29 or the adjusting cylinder 30 is oriented here substantially parallel to the axis of rotation 8 of the drum 5. On the end region of the adjusting piston 29 shown on the left in fig. 1, said adjusting piston has a bearing seat 31 in which the bearing ball 19 is supported. Here, a bearing ball 19 is present on the oscillating arm 16 of the swivel pendulum 14 (fig. 1 to 3). The first and second pivoting devices 25, 26 are therefore each connected to the pivoting oscillating element 14 by a bearing ball 19 on the respective oscillating arm 16. By opening one of the two valves 27, 28, illustrated in fig. 1 as the first valve 27 on the first oscillating device 25 and the second valve 28 on the second oscillating device 26, the rotary oscillating member 14 can oscillate about the oscillation axis 15, since a force is thereby exerted on the actuating piston 29 at the opened valve 27, 28. In this case, not only the rotary oscillating part 14 but also the restraint disk 37, due to the force loading by the compression spring 41, also carries out the described oscillating movement of the rotary oscillating part 14.

The greater the value of the pivot angle α at a constant rotational speed of the drive shaft 9 when the swash plate machine 1 is operated as an axial piston pump 2, the greater the volume flow delivered by the swash plate machine 1 and vice versa, for this purpose a valve disk 11 is mounted on the end of the cylinder drum 5 shown on the right in fig. 1, which valve disk has a kidney-shaped high-pressure opening 12 and a kidney-shaped low-pressure opening 13, as a result of which the piston bore 6 of the rotating cylinder drum 5 is in fluid-conducting connection with the high-pressure opening 12 when arranged on the high-pressure opening 12 and is in fluid-conducting connection with the low-pressure opening 13 when arranged on the low-pressure opening 13, the high-pressure opening 12 is formed on an imaginary first part 34 and the low-pressure opening 13 is formed on an imaginary second part 35, the axial piston pump 2 does not deliver hydraulic fluid despite the rotational movement of the drive shaft 9 and the drum 5 when the swash plate machine is operated, for example, as an axial piston pump 2, because the piston 7 does not perform a stroke movement in the piston bore 6.

In the swash plate machine 1 not only as an axial directionWhen the piston pump 2 is operated as an axial piston motor 3, the piston bore 6, which is temporarily connected in a fluid-conducting manner to the high-pressure opening 12 in the imaginary first section 34, has a greater pressure on the hydraulic fluid than the piston bore 6 in the second imaginary section 35, which is temporarily connected in a fluid-conducting manner to the low-pressure opening 13. Therefore, a resultant force as a pressing force applied to the rotary rocking member 14 by all the pistons 7 in the direction of the rotation axis 8 acts as a resultant force F_ZArranged eccentrically, that is to say not on the imaginary sectional plane 33 according to fig. 2, but on the left of the imaginary sectional plane 33 according to the illustration in fig. 2. Thus, the two bearing sleeves 21 are brought to a resultant pressure F_ZIs loaded unevenly, i.e. the bearing bush 21 on the imaginary first part 34 is based on the resultant force F compared to the bearing bush 21 on the second imaginary part 35_ZWith greater force loading. Furthermore, the two pendulums 24 will also act as a pressure force F in the direction of the axis of rotation 8_SIs applied to the swing member 14. The two connecting points 32 have a spacing 36 from the imaginary sectional plane 33, and the resulting pressure F of the pendulum device 24 is therefore_SAlso with a spacing 36 from the imaginary sectional plane 33. The distance 36 between the two connection points 32 is selected as described below, so that the resultant force F on the two bearing sleeves 21 is_LSubstantially equal so that the two bearing sleeves 21 on the first and second imaginary parts 34, 35, respectively, are loaded with substantially equal pressure. Fig. 5 shows a beam model for the swing arm 14. The cross beam 43 is supported on two beam bearings 44, which correspond to the two bearing sleeves 21. Resulting pressure F of all pistons 7_ZAnd the resultant pressure force F of the two oscillating devices 24_SActing on the cross beam 44. Here, the resultant force F, which is the supporting force of the two beam bearings 44_LAre substantially equal.

A drive train 45 according to the invention is shown in fig. 6. The drive train 45 according to the invention has an internal combustion engine 46 which drives a planetary gear 48 by means of a shaft 47. The two shafts 47 are driven by means of a planetary gear 48, wherein the first shaft 47 is connected to a differential gear 56 by means of a clutch 49. A second or further shaft driven by the planetary gear 48 drives a first swash plate machine 50 via a clutch 49, and the first swash plate machine 50 is hydraulically connected to a second swash plate machine 51 by means of two hydraulic lines 52. The first and second swash plate machines 50, 51 thus constitute a hydraulic transmission 60, and the differential gearing 56 can also be driven by the second swash plate machine 51 by means of the shaft 47. Differential gear 56 drives wheels 57 via axles 58. The drive train 45 also has two pressure accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55. In this case, the two pressure accumulators 53 are also hydraulically connected to the two swash plate machines 50, 51 by means of hydraulic lines, not shown, so that mechanical energy of the internal combustion engine 46 can be stored hydraulically in the high-pressure accumulator 54, and furthermore, during waste heat utilization operation of the motor vehicle with the drive train 45, kinetic energy of the motor vehicle can also be stored hydraulically in the high-pressure accumulator 54. By means of the hydraulic energy stored in the high-pressure accumulator 54, the differential gear 56 can additionally be driven by means of the swash plate machines 50, 51.

The main advantages associated with the swash plate machine 1 according to the invention have been studied as a whole. The two pendulums 24 are eccentrically constructed on an imaginary second part 35 of the swash plate machine 1, so that the bearing forces to be absorbed by the two bearing sleeves 21 are therefore substantially equal. Thus, an unnecessarily large wear on the bearing bush 21 on the imaginary first section 34 can be avoided in an advantageous manner. The slide bearing 22 therefore has a greater service life and the costs for producing the swash plate machine 1 can be reduced, since only a small pressure acts on the slide bearing 22.

Claims

1. A swash plate machine (1) as an axial piston pump (2) and/or an axial piston motor (3), comprising

A drum (5) with a piston bore (6) mounted rotatably or rotationally about a rotational axis (8),

a piston (7) movably supported in the piston bore (6),

-a drive shaft (9) connected in a rotationally fixed manner to the drum (5),

a swivel and swing member (14) mounted so as to be able to swing about a swing axis (15),

-a wobble-member bearing (20) for the rotary wobble-member (14),

-at least one oscillating device (24) for oscillating the swing-swing part (14), which oscillating device is connected to the swing-swing part (14) at a respective connection location (32),

-a low-pressure opening (13) for introducing hydraulic liquid into and/or out of the rotating piston bore (6),

-a high pressure opening (12) for conducting hydraulic liquid out of and/or into the rotating piston bore (6),

wherein,

in an imaginary section, dividing the swash plate machine (1) with an imaginary section plane (33) in and parallel to the rotational axis (8) of the cylinder drum (5) and perpendicular to the swing axis (15) of the swing-member (14) into an imaginary first part (34) with a high-pressure opening (12) on the cylinder drum (5) and an imaginary second part (35) with a low-pressure opening (13) on the cylinder drum (5),

it is characterized in that the preparation method is characterized in that,

the connecting points (32) are formed on the imaginary second part (35) at a distance of at least 0.2cm from the imaginary sectional plane (33), and the resulting force exerted by the at least one pivoting device (24) on the pivoting and oscillating part (14) can be introduced into the pivoting and oscillating part (14) on the imaginary second part (35) due to the formation and/or arrangement of the connecting points (32) in order to reduce the pressure occurring on the imaginary first part (34) between the oscillating part bearing (20) and the pivoting and oscillating part (14).

2. The swash plate machine of claim 1,

the resultant force exerted by the at least one oscillating device (24) on the rotary oscillating part (14) can be introduced into the rotary oscillating part (14) only at the second portion (35),

or

The swash plate machine (1) comprises a plurality of oscillating devices (24), and in all the oscillating devices (24), the resultant force exerted by the oscillating devices (24) on the rotary oscillating piece (14) can only be introduced into the rotary oscillating piece (14) on the second portion (35).

3. The swash plate machine according to claim 1 or 2,

the resultant force exerted by the at least one oscillating device (24) on the rotary oscillating piece (14) can be introduced into the rotary oscillating piece (14) on the second portion (35) at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane (33),

or

Each connection location (32) being configured on the imaginary second part (35) at a distance of at least 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane (33),

or

The swash plate machine (1) comprises a plurality of oscillating devices (24) and in all oscillating devices (24) the resultant force exerted on the rotary oscillating piece (14) can be introduced into the rotary oscillating piece (14) on the second portion (35) at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane (33),

or

The connecting points (32) and the at least one pivoting device (24) are formed on the second part (35) at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary sectional plane (33).

4. The swash plate machine according to claim 1 or 2,

the swash plate machine (1) has two pendulums (24),

and/or

Two oscillating arms (16) are formed on the pivoting oscillating element (14), and the connecting point (32) is formed on an end region of the oscillating arm (16),

and/or

The connection points (32) are formed outside the imaginary sectional plane (33).

5. A swash plate machine according to claim 1 or 2, wherein the at least one oscillating device (24) has an adjusting piston (29) for applying pressure to the connection locations (32).

6. The swash plate machine of claim 1,

the swash plate machine (1) has a housing (4), and the housing (4) is constructed in one piece or in several pieces,

and/or

The wobble-element bearing (20) is formed by two bearing sleeves (21), on which one bearing section (17) of the rotary wobble element (14) is supported indirectly or directly, and the bearing sleeves (21) are arranged in the imaginary first and second sections (34, 35) of the swash plate machine (1).

7. A swash plate machine according to claim 6, characterized in that the bearing sleeve (21) is constructed on the housing (4),

and/or

The bearing sleeve (21) and the bearing segments (17) are designed in a circular segment shape in a cross section parallel to the imaginary cross-sectional plane (33).

8. Swash plate machine according to claim 6 or 7, characterized in that the wobble plate bearing (20) is configured as a plain bearing (22) and a sliding intermediate piece (23) of metal, of plastic or of metal with a plastic coating is arranged between the bearing sleeve (21) and the bearing section (17) in each case.

9. A swash plate machine according to claim 1 or 2, characterized in that the swash plate machine (1) comprises a valve disc (11) having the high pressure opening (12) and the low pressure opening (13), and that the valve disc (11) is supported on the drum (5).

10. A swash plate machine according to claim 1 or 2, characterized in that the swash plate machine (1) has a constraining disc (37) and sliding shoes (39) are fixed on the constraining disc (37), on which one piston (7) is fixed respectively, so that the constraining disc (37) together with the sliding shoes (39) also performs the rotary motion of the cylinder drum (5) and the piston (7), and the constraining disc (37) is supported indirectly or directly on the rotary rocking member (14).

11. The swash plate machine of claim 3,

all connection points (32) and all pivoting means (24) are formed on the second part (35) at a distance of at least 0.2cm, 0.5cm, 1cm, 3cm, 5cm, 7cm, 10cm or 20cm from the imaginary section plane (33).

12. The swash plate machine according to claim 1 or 2,

the swash plate machine (1) has only two pendulums (24).

13. The swash plate machine according to claim 1 or 2,

all connection points (32) are formed outside the imaginary sectional plane (33).

14. The swash plate machine according to claim 1 or 2,

all connection points (32) are formed exclusively outside the imaginary sectional plane (33).

15. A swash plate machine according to claim 5, characterized in that the pressure is oriented towards the rotary wobble-member (14) in the direction of the rotation axis (8).

16. The swash plate machine of claim 6,

the bearing sleeves (21) are arranged spaced apart in the imaginary first and second sections (34, 35) of the swash plate machine (1).

17. A swash plate machine according to claim 8, characterized in that the sliding intermediate piece (23) is made of brass.

18. A swash plate machine according to claim 8, characterized in that the sliding intermediate piece (23) is made of PTFE.

19. A swash plate machine according to claim 8, characterized in that the sliding intermediate piece (23) is made of metal with a PTFE coating.

20. A swash plate machine according to claim 8, characterized in that the sliding intermediate piece (23) is made of steel or brass with a plastic coating.

21. A swash plate machine according to claim 8, characterized in that the sliding intermediate piece (23) is made of steel or brass with a PTFE coating.

22. A swash plate machine according to claim 9, characterized in that the high pressure opening (12) and the low pressure opening (13) are configured as kidney-shaped.

23. A drive train (45) for a motor vehicle comprises

-at least one swash plate machine (1) for converting mechanical energy into hydraulic energy and vice versa,

-at least one pressure reservoir (53),

it is characterized in that the preparation method is characterized in that,

the swash plate machine (1) is constructed according to any of the preceding claims.

24. Drive train according to claim 23,

the drive train (45) comprises two swash plate machines (1) which are hydraulically connected to each other and serve as a hydraulic drive (60),

and/or

The drive train (45) comprises two pressure accumulators (53) as a high-pressure accumulator (54) and a low-pressure accumulator (55).