DE102014204898A1 - Swash plate machine - Google Patents

Abstract

Swashplate machine (1) as axial piston pump (2) and / or axial piston motor (3), comprising a cylinder drum (5) rotatably or rotationally mounted about an axis of rotation (8) with piston bores (6), pistons movably mounted in the piston bores (6) ( 7), one with the cylinder drum (5) at least rotatably connected drive shaft (9) which is rotatably or rotatably mounted about the rotation axis (8), a about a pivot axis (15) pivotally mounted pivoting cradle (14) with a support surface (18 ) for supporting the pistons (7) on the support surface (18) and with at least one abutment portion (23) for supporting the pivoting cradle (14), a cradle support (20) for the pivoting cradle (14) with at least one bearing portion (17) and with at least one bearing portion (17) of the at least one abutment portion (23) of the pivoting cradle (14) is mounted, wherein on the at least one bearing portion (17) and / or on the at least one abutment portion (23) Vertie are formed (33).

Description

The present invention relates to a swashplate machine according to the preamble of claim 1 and a drive train according to the preamble of claim 11.

State of the art

Swash plate machines serve as axial piston pumps for converting mechanical energy into hydraulic energy and as axial piston motor for converting hydraulic energy into mechanical energy. A cylinder drum with piston bores is rotatably or rotatably mounted and pistons are arranged in the piston bores. The cylinder drum is fixedly connected to a drive shaft and a hydraulic fluid acts temporarily on a first part of the rotating piston bores under high pressure and a hydraulic fluid acts temporarily on a second part of the rotating piston bores at low pressure. A pivoting cradle is pivotally mounted about a pivot axis and on the pivoting cradle is on a retaining disc with sliding shoes. The pistons are attached to the sliding shoes. The retaining disc with the sliding shoes together with the cylinder drum performs a rotational movement about an axis of rotation and a flat bearing surface of the pivoting cradle is at an acute angle, for example between 0 ° and + 20 ° and between 0 ° and -20 ° as a swivel angle aligned with the axis of rotation of the cylinder drum. The shoes are mounted with a sliding bearing on the support surface of the pivoting cradle and the shoes are connected to the retaining disc. The pivoting cradle is pivoted by two hydraulic pivoting devices, each of which is formed by an adjusting piston and an adjusting cylinder, about a pivot axis.

The pivoting pivoting cradle is mounted on two separate part-cylindrical shell-shaped abutment sections by means of a sliding bearing on two separate fixed part-cylindrical shell-shaped bearing sections. The bearing sections are each formed by a bearing shell. The sliding bearing between the two pivotable abutment sections on the pivoting cradle and the two bearing sections is hydrostatically relieved, so that thereby hydraulic energy is required for the hydrostatic discharge. Disadvantageously, thus, the swash plate machine has a low efficiency due to the loss of hydraulic energy for the hydrostatic discharge.

The EP 1 013 928 A2 shows an axial piston pump in a swash plate design with a driven rotating and a plurality of piston bores arranged therein cylinder barrel, wherein in each separated by webs piston bores are arranged between a bottom dead center and a top dead center movable pistons and a low-pressure connection kidney and a Hochdruck Hochdruck kidney having control disc provided is.

The CH 405 934 shows a Schrägscheibenaxialkolbenpumpe whose non-rotating cylinder block for varying the delivery rate in dependence on the delivery pressure is longitudinally displaceable, wherein on the pressed by a spring in the direction of increasing the delivery cylinder block, a control slide unit is fixed with a spool.

The DE 27 33 870 C2 shows a control device for a Schrägenscheibenaxialkolbenpumpe, in which acts on both sides of the cradle for pivoting the swash plate depending on a hydraulically actuated swing wing on the engine, both motors are controllable by means of a pivot about the pivot axis of the cradle pivotally mounted plate-shaped control valve slide and adjusting the flow rate of the pump serve.

Disclosure of the invention

Advantages of the invention

Swash plate machine according to the invention as axial piston pump and / or axial piston motor, comprising a cylinder drum rotatable about a rotation axis with piston bores, pistons movably mounted in the piston bores, a drive shaft at least rotatably connected to the cylinder drum, which is rotatable about the rotation axis, a pivoting about a pivot axis mounted pivoting cradle with a support surface for supporting the piston on the support surface and at least one abutment portion for supporting the pivoting cradle, a weighing storage for the pivoting cradle with at least one bearing portion and at least one bearing portion of the at least one abutment portion of the pivoting cradle is mounted , wherein depressions are formed on the at least one bearing section and / or on the at least one counter-bearing section. The recesses improve the lubrication and reduce the abrasion of the weighing storage. In an embodiment of a pivotable bearing shell, z. B. PEEK, on the other pivoting cradle made of steel, the wells can also be formed on the pivotable bearing shell of the pivoting cradle and the fixed bearing section has a contact surface made of steel without depressions.

In a further embodiment, there is no contact between the at least one bearing section and the at least one counter bearing section and / or outside the depressions, the at least one bearing section, each with a contact surface in contact with a respective mating contact surface of the at least one counter bearing section.

In a further embodiment, the contact surface of the at least one bearing portion and the mating contact surface of the at least one abutment portion are formed teilzylindermantelelförmig and a fictitious cylinder shell of a fictitious cylinder on the at least one contact surface and rests on the at least one mating contact surface and the fictitious cylinder has a central longitudinal axis and the centric Longitudinal axis of the fictitious cylinder is identical to the pivot axis of the pivoting cradle.

In a supplementary variant, the recesses are aligned substantially perpendicular to the pivot axis of the pivoting cradle and / or the recesses are formed in cross-section substantially circular or elliptical and / or the swash plate machine has at least 20, 30 or 50 wells.

In a further embodiment, the at least one bearing section or the at least one counter bearing section is formed by a respective bearing shell made of plastic, PEEK, polyamide, PPS or brass. A different material on the bearing portion and abutment portion is required for the sliding bearing.

In an additional embodiment, the depressions are arranged substantially in several rows one behind the other on the at least one bearing part which is part of a cylinder jacket and / or on the at least one part-cylinder jacket-shaped counter bearing section.

In a further variant, no depressions are formed on the at least one part-cylinder jacket-shaped bearing section and / or on the at least one partially cylindrical jacket-shaped counter bearing section between the depressions in a direction parallel to the direction of the recesses arranged in rows.

In a further embodiment, the depressions have an extent perpendicular to the pivot axis of the pivoting cradle between 0.2 mm and 8 mm, preferably between 0.4 mm and 5 mm, in particular between 0.7 mm and 2 mm.

In an additional embodiment, the extent perpendicular to the pivot axis of the recesses between 0.1% and 10%, preferably between 0.5% and 5%, in particular between 1 and 3%, of the radial distance of the contact surface of the at least one bearing portion and the Counter contact surface of the at least one abutment portion to the pivot axis of the pivoting cradle and / or a sliding bearing between the at least one bearing portion and the at least one abutment portion has no hydrostatic discharge.

In a supplementary variant, the extent of the depressions perpendicular to the pivot axis of the depressions is between 100% and 10%, preferably between 80% and 20%, in particular between 60% and 30%, of the radial thickness of the bearing shell.

Drive train according to the invention for a motor vehicle, comprising 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 a swash plate machine described in this patent application.

Preferably, the drive train includes two swash plate machines, which are hydraulically connected to each other and act as a hydraulic transmission and / or the drive train comprises two pressure accumulator as high-pressure accumulator and low pressure accumulator.

Suitably, the swash plate machine comprises at least one pivoting device for pivoting the pivoting cradle.

In a further variant, the swash plate machine comprises a low-pressure opening for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores.

In an additional embodiment, the swash plate machine includes a high pressure port for discharging and / or introducing hydraulic fluid from and / or into the rotating piston bores.

Brief description of the drawings

In the following, an embodiment of the invention will be described in more detail with reference to the accompanying drawings. It shows:

1 a longitudinal section of a swash plate machine,

2 a cross section AA according to 1 a valve disc of the swash plate machine and a view of a pivoting cradle,

3 a longitudinal section of a bearing portion and abutment portion of a weighing storage for a pivoting cradle of the swash plate machine,

4 a view of a warehouse section of weighing storage and

5 a drive train for a motor vehicle.

Embodiments of the invention

An in 1 in a longitudinal section shown swash plate machine 1 serves as axial piston pump 2 For conversion or conversion of mechanical energy (torque, speed) into hydraulic energy (volume flow, pressure) or as axial piston motor 3 for conversion or conversion of hydraulic energy (volume flow, pressure) into mechanical energy (torque, speed). A drive shaft 9 is by means of a storage 10 on a flange 21 one- or multi-part housing 4 and with another storage 10 on the housing 4 the swash plate machine 1 around a rotation axis 8th rotatably or rotatably mounted ( 1 ). With the drive shaft 9 is a cylinder drum 5 rotationally fixed and connected in the axial direction, wherein the drive shaft 9 and the cylinder drum 5 one or two parts are formed and the boundary between the drive shaft 9 and the cylinder drum 5 in 1 is shown in dashed lines. The cylinder drum 5 guides the rotational movement of the drive shaft 9 with out due to a non-rotatable connection. In the cylinder drum 5 are a variety of piston bores 6 with any cross-section, for example square or circular, incorporated. The longitudinal axes of the piston bores 6 are essentially parallel to the axis of rotation 8th the drive shaft 9 or the cylinder drum 5 aligned. In the piston bores 6 is each a piston 7 movably mounted. A pivoting cradle 14 is about a pivot axis 15 pivotable on the housing 4 stored. The pivot axis 15 is perpendicular to the drawing plane of 1 and 3 as well as parallel to the drawing plane of 2 aligned. The rotation axis 8th the cylinder drum 5 is parallel to and in the drawing plane of 1 arranged and perpendicular to the drawing plane of 2 , The housing 4 limited liquid-tight an interior 44 which is filled with hydraulic fluid.

The pivoting cradle 14 has a flat or planar support surface 18 for the indirect support of a retaining disc 37 and for the direct application of sliding shoes 39 on. The retaining disc 37 is with a variety of sliding shoes 39 provided and every shoe 39 is there with one piston each 7 connected. For this purpose, the sliding shoe 39 a camp ball 40 ( 1 ), which in a Lagerpfanne 59 on the piston 7 is attached, so that a piston joint 22 between the bearing ball 40 and the pan 59 on the piston 7 is trained. The partially spherical bearing ball 40 and pan 59 Both are complementary or spherical, so thereby at a corresponding movement possibility to each other between the bearing ball 40 and the pan 59 to the piston 7 a permanent connection between the piston 7 and the sliding shoe 39 is available. Due to the connection of the pistons 7 with the rotating cylinder drum 5 and the connection of the bearing pans 59 with the sliding shoes 39 lead the sliding shoes 39 a rotational movement about the axis of rotation 8th with out and due to the firm connection or arrangement of the sliding shoes 39 on the retaining disc 37 also carries the retaining disc 37 a rotational movement about the axis of rotation 8th with out. So that the sliding shoes 39 in constant contact with the support surface 18 the pivoting cradle 14 stand, the retaining disc 37 from a compression spring 41 under a compressive force on the support surface 18 pressed.

The pivoting cradle 14 is - as already mentioned - around the pivot axis 15 pivoted and also has an opening 42 ( 1 ) for carrying out the drive shaft 9 on. At the housing 4 is a weighing storage 20 with two part-cylinder shell-shaped bearing sections 17 educated. Here are at the pivoting cradle 14 two partial cylinder shell-shaped counter bearing sections 23 educated. The two abutment sections 23 the pivoting cradle 14 lie on the bearing sections 17 the weighing storage 20 on. The pivoting cradle 14 is thus by means of a sliding bearing on the weighing storage 20 or the housing 4 around the pivot axis 15 pivoted. In the illustration in 1 has the bearing surface 18 according to the sectioning in 1 a pivot angle α of approximately + 20 °. The swivel angle α is between a notional plane perpendicular to the axis of rotation 8th and one of the flat bearing surface 18 the pivoting cradle 14 spanned level exists according to the sectional formation in 1 , The pivoting cradle 14 can between two pivotal limit angle α between + 20 ° and -20 ° by means of two pivoting devices 24 be pivoted.

The first and second pivoting device 25 . 26 as pivoting devices 24 has a junction 32 between the pivoting device 24 and the swivel cradle 14 on. The two pivoting devices 24 each have an adjusting piston 29 on, which in an adjusting cylinder 30 is movably mounted. The adjusting piston 29 or an axis of the adjusting cylinder 30 is essentially parallel to the axis of rotation 8th the cylinder drum 5 aligned. At one in 1 left end portion of the adjusting piston shown 29 this has a bearing cup 31 in which a bearing ball 19 is stored. Here is the bearing ball 19 on a swivel arm 16 ( 1 to 2 ) of the pivoting cradle 14 available. The first and second pivoting device 25 . 26 is thus each with a ball bearing 19 on each one swivel arm 16 with the swivel cradle 14 connected. By opening one of the two valves 27 . 28 as the first valve 27 at the first pivoting device 25 and the second valve 28 at the second gift device 26 as shown in 1 can the swivel cradle 14 around the pivot axis 15 be pivoted, as a result of the adjusting piston 29 on the open valve 27 . 28 with a hydraulic fluid under pressure in the adjusting cylinder 30 a force is applied. Not only does the swing cradle lead here 14 but also the retaining disc 37 due to the pressurization with the compression spring 41 this pivoting movement of the pivoting cradle 14 with out.

During operation of the swashplate machine 1 as axial piston pump 2 is at constant speed of the drive shaft 9 that of the swashplate machine 1 the larger the amount of the swivel angle α and the other way around, the greater the volumetric flow delivered. This is due to the in 1 right end of the cylinder drum 5 a valve disc 11 on, with a kidney-shaped high-pressure opening 12 and a kidney-shaped low-pressure opening 13 , The piston bores 6 the rotating cylinder drum 5 thus become fluid conducting in an arrangement at the high pressure port 12 with the high-pressure opening 12 connected and in an arrangement at the low pressure opening 13 with the low-pressure opening 13 fluidly connected. At a swivel angle α of 0 ° and during operation of the swash plate machine, for example as axial piston pump 2 is despite a rotational movement of the drive shaft 9 and the cylinder drum 5 no hydraulic fluid from the axial piston pump 2 promoted as the pistons 7 no strokes in the piston bores 6 To run. During operation of the swashplate machine 1 both as axial piston pump 2 as well as axial piston motor 3 have the temporarily in fluid communication with the high pressure port 12 standing piston bores 6 a greater pressure on hydraulic fluid than the piston bores 6 temporarily in fluid communication with the low pressure port 13 stand. An axial end 66 the cylinder drum 5 lies on the valve disc 11 on. On a first page 64 of the housing 4 or the flange 21 of the housing 4 is an opening 63 with storage 10 trained and a second page 65 has a recess for mounting the drive shaft 9 with another storage 10 on.

The retaining disc 37 is annular as a flat disc and thus has an opening 38 for the implementation of the drive shaft 9 on. The retaining disc 37 has eight holes inside which the shoes 39 are arranged so that the sliding shoes 39 in the radial direction, ie perpendicular to a longitudinal axis of the bores, with respect to the retaining disc 37 are mobile. The retaining disc 37 and the sliding shoes 39 are formed in several parts. The number of holes corresponds to the number of sliding shoes 39 and pistons 7 and in each hole is a sliding shoe 39 attached. The retaining disc 37 does not lie directly on the support surface 18 on.

The pivoting cradle 14 is as already described with two pivotable abutment sections 23 on two fixed bearing sections 17 stored with a plain bearing. The two part cylinder jacket bearing sections 17 are each from a bearing shell 36 educated ( 3 ). The bearing shell 36 consists of PEEK and lies on each an abutment section 23 made of steel, because the pivoting cradle 14 also made of steel and the two counter bearing sections 23 machined on the one-piece swivel cradle 14 with the abutment sections 23 are made. The different materials for the bearing sections 17 and the counter bearing sections 23 are required for sliding bearing. The two bearing shells 36 are at a bearing block 61 fastened from steel and the bearing block 61 is on the flange 21 fixed. In the longitudinal section in 1 are the two bearing shells 36 as well as the counter bearing sections 23 not cut because these are above and below the drawing plane of 1 on the swash plate machine 1 are formed. This is necessary because in the drawing plane of 1 the drive shaft 9 and the opening 42 the pivoting cradle 14 is available. A partially cylindrical jacket-shaped contact surface 34 the two bearing sections 17 or the bearing shell 36 is thus on a partially cylindrical jacket-shaped mating contact surface 35 the counter bearing sections 23 on. A fictitious cylinder (not shown), with its cylinder surface on the contact surfaces 34 and the mating contact surfaces, has a central longitudinal axis, which is the pivot axis 15 the pivoting cradle 14 equivalent. The contact surface 34 and the mating contact surface 35 has a radial distance 69 to the pivot axis 15 on and the radial distance 69 corresponds to the radius of the fictitious cylinder. The bearing shell 36 has a radial thickness 62 of 2 mm on and in the bearing shells 36 are a plurality of circular cross-section depressions 33 formed with an extension perpendicular to the pivot axis 15 of 1 mm. At the wells 33 There is thus no contact between the bearing shell 36 and the anvil section 23 because the pits 33 in the radial direction outwards starting with the contact surface 34 are formed. The wells 33 are geometrically on the outer surface of the bearing shell 36 arranged to be in a plurality of substantially parallel rows 68 are arranged. In a direction parallel to the rows 68 are between the rows in several inter-row areas 43 no depressions on the contact surface 33 available, ie only the contact surface 34 available. The wells 33 serve as receiving pockets for dirt and micro particles, allowing the highly loaded contact between the contact surface 34 and the mating contact surface 35 less abrasion due to dirt and micro particles is exposed, because between the contact surface 34 and the mating contact surface 35 less dirt and micro particles are present. The wells 33 also serve as a receiving space and reservoir for the hydraulic fluid within the interior 44 , which acts as a lubricant for the sliding bearing, so that between the contact surface 34 and the mating contact surface 35 more hydraulic fluid is arranged as a lubricant, thus reducing the friction and the life of the plain bearing of the weighing storage 20 is increased. The bearing shell 36 points in partial areas in the direction of the rows 68 a smaller compliance or hardness than in partial areas between the rows 68 or in the inter-row areas 43 because through the depressions 33 the bearing shell 36 in partial areas in the direction of the rows 68 less contact surface 34 has or is weakened. The distribution of the surface pressure between the contact surface 34 and the mating contact surface 35 is thus better distributed so that manufacturing tolerances can be better compensated.

The contact surface 34 the bearing shell 36 in the subregions in the direction of the rows 68 is at the wells 33 interrupted and a direction of movement 67 of the counter bearing section 23 on the storage section 17 is at an acute angle to the direction of the rows 68 aligned. In the sections towards the rows 68 is thus a better promotion of hydraulic fluid due to the pivoting movement of the pivoting cradle 14 possible because of the depressions 33 the hydraulic fluid can flow with a lower flow resistance than between the contact surface 34 and the mating contact surface 35 , As a result, the lubrication of the sliding bearing is additionally improved.

In 5 is an inventive drive train 45 shown. The drive train according to the invention 45 has an internal combustion engine 46 on which by means of a wave 47 a planetary gear 48 drives. With the planetary gear 48 become two waves 47 driven, being a first shaft 47 with a clutch 49 with a differential gear 56 connected is. A second or other shaft, which of the planetary gear 48 powered by a clutch 49 a first swash plate machine 50 on and the first swash plate machine 50 is by means of two hydraulic lines 52 with a second swashplate machine 51 hydraulically connected. The first and second swashplate machine 50 . 51 thereby form a hydraulic transmission 60 and from the second swash plate machine 51 can by means of a wave 47 also the differential gear 56 are driven. The differential gear 56 drives with the wheel shafts 58 the wheels 57 at. Furthermore, the drive train 45 two accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55 on. The two accumulators 53 are here by means not shown hydraulic lines with the two swash plate machines 50 . 51 hydraulically connected, so that mechanical energy of the internal combustion engine 46 in the high-pressure accumulator 54 hydraulically stored and further in a recuperation operation of a motor vehicle with the drive train 45 also kinetic energy of the motor vehicle in the high-pressure accumulator 54 can be stored hydraulically. By means of the high-pressure accumulator 54 stored hydraulic energy can be used with a swash plate machine 50 . 51 in addition the differential gear 56 are driven.

Overall, considered with the swash plate machine according to the invention 1 significant benefits. The wells 33 reduce abrasion and increase lubrication with hydraulic fluid weighing 2 , so that thereby on a hydrostatic relief of the form of sliding bearing weighing storage 20 can be omitted with a long life of weighing storage 20 , The swashplate machine 1 thus has a high efficiency.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1013928 A2 [0004]
• CH 405934 [0005]
• DE 2733870 C2 [0006]

Claims (12)

Swashplate machine ( 1 ) as axial piston pump ( 2 ) and / or axial piston motor ( 3 ), comprising - one about an axis of rotation ( 8th ) rotatably or rotationally mounted cylindrical drum ( 5 ) with piston bores ( 6 ), - in the piston bores ( 6 ) movably mounted pistons ( 7 ), - one with the cylinder drum ( 5 ) at least rotatably connected drive shaft ( 9 ), which around the axis of rotation ( 8th ) is rotatably or rotationally mounted, - one about a pivot axis ( 15 ) pivotally mounted pivoting cradle ( 14 ) with a bearing surface ( 18 ) for the storage of the pistons ( 7 ) on the support surface ( 18 ) and with at least one abutment section ( 23 ) for the storage of the pivoting cradle ( 14 ), - a weighing storage ( 20 ) for the pivoting cradle ( 14 ) with at least one storage section ( 17 ) and on which at least one bearing section ( 17 ) the at least one abutment portion ( 23 ) of the pivoting cradle ( 14 ), characterized in that on the at least one bearing section ( 17 ) and / or on the at least one abutment section ( 23 ) Wells ( 33 ) are formed. Swash plate machine according to claim 1, characterized in that at the recesses ( 33 ) no contact between the at least one bearing section ( 17 ) and the at least one abutment portion ( 23 ) and / or outside the wells ( 33 ) the at least one storage section ( 17 ) each with a contact surface ( 34 ) in contact with a respective mating contact surface ( 35 ) of the at least one abutment portion ( 23 ) stands. Swash plate machine according to claim 2, characterized in that the contact surface ( 34 ) of the at least one storage section ( 17 ) and the mating contact surface ( 35 ) of the at least one abutment portion ( 23 ) are formed part-cylindrical jacket-shaped and a fictitious cylinder jacket of a fictitious cylinder on the at least one contact surface ( 34 ) and at least one mating contact surface ( 35 ) rests and the fictitious cylinder has a central longitudinal axis and the central longitudinal axis of the notional cylinder is identical to the pivot axis ( 15 ) of the pivoting cradle ( 14 ). Swash plate machine according to one or more of the preceding claims, characterized in that the depressions ( 33 ) substantially perpendicular to the pivot axis ( 15 ) of the pivoting cradle ( 14 ) and / or the depressions ( 33 ) are formed in cross-section substantially circular or elliptical and / or the swash plate machine ( 1 ) at least 20, 30 or 50 wells ( 33 ) having. Swash plate machine according to one or more of the preceding claims, characterized in that the at least one bearing section ( 17 ) or the at least one abutment section ( 23 ) of one bearing shell each ( 36 ) is made of plastic, PEEK, polyamide, PPS or brass. Swash plate machine according to one or more of the preceding claims, characterized in that on the at least one part-cylinder jacket-shaped bearing portion ( 17 ) and / or on the at least one part-cylinder jacket-shaped abutment section ( 23 ) the depressions ( 33 ) essentially in several rows ( 68 ) are arranged one behind the other. Swash plate machine according to one or more of the preceding claims, characterized in that on the at least one part-cylinder jacket-shaped bearing portion ( 17 ) and / or on the at least one part-cylinder jacket-shaped abutment section ( 23 ) between the depressions ( 33 ) in a direction parallel to the direction of the rows ( 68 ) arranged recesses ( 33 ) no depressions ( 33 ) are formed. Swash plate machine according to one or more of the preceding claims, characterized in that the depressions ( 33 ) an extension perpendicular to the pivot axis ( 15 ) of the pivoting cradle ( 14 ) between 0.2 mm and 8 mm, preferably between 0.4 mm and 5 mm, in particular between 0.7 mm and 2 mm. Swash plate machine according to one or more of the preceding claims, characterized in that the extension perpendicular to the pivot axis ( 15 ) of the depressions ( 33 ) between 0.1% and 10%, preferably between 0.5% and 5%, in particular between 1 and 3%, of the radial distance ( 69 ) of the contact surface ( 34 ) of the at least one storage section ( 17 ) and the mating contact surface ( 35 ) of the at least one abutment portion ( 23 ) to the pivot axis ( 15 ) of the pivoting cradle ( 14 ) and / or a sliding bearing between the at least one bearing section ( 17 ) and the at least one abutment portion ( 23 ) has no hydrostatic discharge. Swash plate machine according to one or more of the preceding claims, characterized in that the extension perpendicular to the pivot axis ( 15 ) of the recesses between 100% and 10%, preferably between 80% and 20%, in particular between 60% and 30%, of the radial thickness ( 62 ) of the bearing shell ( 36 ) is. Powertrain ( 45 ) for a motor vehicle, comprising - at least one swashplate machine ( 1 ) for the conversion of mechanical energy into hydraulic energy and vice versa, - at least one pressure accumulator ( 53 ), characterized in that the swash plate machine ( 1 ) is formed according to one or more of the preceding claims. Drive train according to claim 11, characterized in that the drive train ( 45 ) two swashplate machines ( 1 ), which are hydraulically connected to each other and as a hydraulic transmission ( 60 ) and / or the powertrain ( 45 ) two accumulators ( 53 ) as a high-pressure accumulator ( 54 ) and low-pressure accumulator ( 55 ).

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