EP3055565B1 - Swashplate machine - Google Patents

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 are on a flat support surface sliding shoes, which are attached to a retaining disc. 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 pivoting cradle is by two hydraulic pivoting devices, each of which is formed by an adjusting piston and an adjusting cylinder to a Swivel axis pivots. The pivoting cradle is pivotally supported by a pivot bearing about the pivot axis. For this purpose, two fixed, teilzylindermantelförmige bearing shells are indirectly attached to the housing by the bearing shells are attached to a bearing block and the bearing block is attached directly to the housing. At the two bearing shells are each pivotable, formed on the pivoting cradle part cylinder shell-shaped counter-cups on. The weighing storage is designed as a sliding bearing between the bearing and counter bearing shells. The partially cylindrical bearing shell is attached to two part-cylindrical partial surfaces of the bearing block and for the production of partially cylindrical partial surfaces of the one-piece bracket is a complex and difficult spanabgebende machining due to the overall geometry of the one-piece bracket necessary. In order that sufficient accuracy can be achieved in the machining operation, a large axial length of the one-piece bracket in the direction of the axis of rotation of the drive shaft is required so that a small bending occurs during machining with the machining tool. This large axial length leads disadvantageously to a greater axial length of the entire swash plate machine.

The EP 1 013 928 A2 shows an axial piston pump in a swash plate design with a driven circumferential and a plurality of piston bores arranged therein cylinder barrel, wherein in each separated by webs piston bores linearly between a bottom dead center and a top dead center movable pistons are arranged and a Niederdruckanschlussniere 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 flow 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 on both sides of the cradle for Pivoting the swash plate ever engages a hydraulically actuated swing wing on the engine, both motors are controllable by means of a pivotable about the pivot axis of the cradle arranged plate-shaped control valve spool and are used to adjust the flow rate of the pump.

From the DE 10 2008 013 010 A1 a swivel-bearing of an axial machine is known with a housing, a pivoting cradle and formed by the housing and the pivoting cradle pivotal bearing area. The pivoting cradle and / or the housing and / or a bearing element arranged in the pivotal rolling bearing area are designed to be deformable such that a deflection of the pivoting cradle can be compensated.

Another swashplate machine is off US 2009/0120279 known. This has a one-piece storage for the cradle.

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 and having piston bores, pistons movably mounted in the piston bores, a pivoting cradle mounted pivotably about a pivot axis, a housing, a cradle support for the pivot cradle with at least one fixed cradle Bearing shell on a bearing block and with at least one pivotable counter-bearing shell on the pivoting cradle, wherein the bearing block is formed in several parts. In the manufacture of the bearing block, the partially cylindrical partial surfaces for the attachment of the bearing shells can be machined with high accuracy with a small axial length in the direction of the axis of rotation of the drive shaft. In the machining operations, in particular, a part of the bearing block can be clamped in a tool and then made particularly accurate at a low bending due to a machining tool. As a result, a very small axial length of the multi-part bearing block is possible and still an evasive accurate machining of part-cylindrical surfaces on the multi-part bracket possible.

As a result, the swash plate machine overall advantageously has a small axial length.

In particular, the bearing block is formed in three parts and / or the fixed bearing shell is indirectly attached to the multi-part bearing block to the housing and / or the multi-piece bracket is, in particular directly attached to the housing. The fixed bearing shell is fixed to the multi-part bearing block and the bearing block is fixed to the housing. As a result, the stationary bearing shell is indirectly fixed by means of the bearing block on the housing, in particular a flange of the housing.

In a further embodiment, the weighing bearing has two stationary bearing shells and a first bearing shell is fastened to a first bearing block part and the second bearing shell is fastened to a second bearing block part and / or the multi-part bearing block is designed as an additional component in addition to the housing.

In a supplementary embodiment, the first and second bearing block part, in particular directly, attached to a third bearing block part and / or on the first and / or second bearing block part depending on a fixed bearing shell, in particular directly attached. In the production of the multi-part bearing block, the partly cylindrical partial surfaces on the first position block part and on the second position block part can thus be produced particularly simply with high accuracy, since the first and second bearing block parts are simply fastened in a processing machine and then machined by a machining tool on the partial surfaces can be, with a slight bending of the first and second Lagebockteiles. As a result, the three-part bearing block has a total of a small axial length in the direction of the axis of rotation of the drive shaft. Preferably, the first and second bearing block part each have a partially cylindrical partial surface on which each of the partially cylindrical bearing shell is attached.

The third bearing block part, in particular directly, is preferably fastened to the housing, in particular to a flange of the housing.

In a variant, the third bearing block part as a ring, in particular a disc-shaped ring formed. The third bearing block part is formed a disk-shaped ring and the ring has an opening for the passage of the drive shaft. The inner end sides of the multi-part bearing block have a small distance from the axis of rotation of the drive shaft at or a small distance to the outside of the drive shaft. As a result, the distance of the two bearing shells from each other is small and the bending of the pivoting cradle due to the force applied by the shoes on the support surface of the pivoting cradle pressure forces is low in an advantageous manner. Furthermore, the distance between the two bearing shells is independent of the outer diameter of a bearing for the drive shaft at the opening of the housing. Only by using, for example, geometrically different first and second bearing block parts with an identical third bearing block part, can the two bearing shells be fastened to different bearings for the drive shaft.

Suitably, the first and second bearing block part are fastened to the third bearing block part with a fastening bolt or fastening pin.

In an additional embodiment, the first and / or second bearing block part is positively and / or non-positively and / or materially secured to the third bearing block part, for example by means of a recess form-fitting manner on the third bearing block part and / or with a screw connection and / or with a press connection and / or with a welded connection and / or non-positively due to the pressure force between the first and second bearing block part and the third bearing block part.

In a further embodiment, the third bearing block part is positively and / or non-positively and / or materially attached to the housing, in particular a flange of the housing, for example by means of a screw and / or a rivet and / or positively due to a recess in the housing and / or with a welded joint and / or non-positively due to the compressive force in the direction of the axis of rotation of the drive shaft between the housing and the third bearing block part.

In a further embodiment, the housing and the bearing block parts made of metal, for. As steel or aluminum, and / or the housing and the bearing block parts are made of an identical material.

In a supplementary embodiment, depending on a bearing surface on the bearing shell on each abutment surface of the anvil shell and / or the first and / or second and / or third bearing block part has at a radial inner side a smaller minimum distance, in particular by 10%, 20%, 30% or 40% smaller distance to the axis of rotation of the cylinder drum than the housing, in particular a flange, at an opening with a bearing for the drive shaft. The first and second bearing block part thus have a small distance from each other, so that thereby a slight bending on the pivoting cradle occurs.

In a further variant, the swash plate machine is designed such that the at least one bearing surface and / or the at least one counter-bearing surface in the region of an inner end side facing the drive shaft has a smaller rigidity in a direction parallel to the pivot axis of the pivoting cradle than in the region of an outer end side facing away from the drive shaft , Due to the smaller rigidity of the at least one bearing surface in the region of the inner end side compared to the outer end side and due to the larger bends of the bearing surface in the region of the inner end side in comparison to the region on the outer end side occurs between the bearing surface and the counter surface advantageously a substantially same Surface pressure on. The area preferably comprises less than 10%, 20% or 30% of the total extent of the bearing surface and / or the abutment surface in the direction parallel to the pivot axis.

In a further embodiment, the bearing surface and / or the abutment surface is formed in a section, in particular in all sections, perpendicular to the pivot axis as a circular segment with an identical distance to the pivot axis. The longitudinal axis of a fictitious cylinder on the circle segment preferably corresponds to the pivot axis of the pivoting cradle.

In particular, the swash plate machine comprises two bearing shells and two counter-bearing shells and the two bearing shells and two counter-bearing shells are arranged in a, in particular identical, distance from the axis of rotation of the drive shaft.

In a supplementary embodiment, the at least one bearing shell is formed by a separate bearing shell part, which is attached directly or indirectly to the first and second bearing block part of the swash plate machine. The bearing shell part is a separate component and consists of a different material than the housing and / or the bearing block, for example plastic, PEEK or brass. The counter-bearing shell is formed directly from the pivoting cradle made of steel, so that thereby the bearing surface and the counter-bearing surface are formed of a different material or material to reduce the friction loss at the weighing storage.

In a further variant, the at least one counter bearing shell is formed by the pivoting cradle.

In an additional embodiment, the swashplate machine on the housing and / or the pivoting cradle and / or on at least one bearing block part and / or on a bearing for the drive shaft and / or on the at least one bearing shell and / or on the at least one counter-bearing shell in the area the inner end side of a recess and / or a cavity and / or a relief. In the case of a large total axial force acting on the swivel cradle, a large bending of the swivel cradle occurs on the inner end sides and the recesses and / or the cavity cause a smaller stiffness of the bearing surface and / or the abutment surface in the region of the inner end sides compared to the outer end sides that thus a substantially uniform surface pressure between the bearing surface and the abutment surface occurs.

In a variant, the pivot axis of the pivoting cradle is aligned perpendicular to the axis of rotation of the drive shaft and the cylinder drum.

In a further embodiment, the bearing shell of a different material than the anvil shell.

Suitably, the bearing switching part made of PEEK or brass and the counter bearing shell made of steel.

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.

In a further embodiment, the swashplate machine comprises a drive shaft which is connected at least in a rotationally fixed manner to the cylinder drum and which is mounted rotatably or rotatably about the rotation axis.

In a further embodiment, the swash plate machine comprises at least one pivoting device for pivoting the pivoting cradle.

In an additional 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 a supplementary embodiment, the swash plate machine comprises a high-pressure opening for discharging and / or introducing hydraulic fluid out of and / or into the rotating piston bores.

Brief description of the drawings

Fig. 1

einen Längsschnitt einer Schrägscheibenmaschine durch eine Rotationsachse einer Antriebswelle und senkrecht zu einer Schwenkachse einer Schwenkwiege,

Fig. 2

einen Querschnitt A-A gemäß Fig. 1 einer Ventilscheibe der Schrägscheibenmaschine sowie eine Ansicht einer Schwenkwiege,

Fig. 3

eine Ansicht eines Flansches eines Gehäuses mit dem daran befestigten dritten Lagerbockteil sowie zwei Lagerschalenteile,

Fig. 4

einen Schnitt B-B gemäß Fig. 3 des Flansches und der ersten, zweiten und dritten Lagerbockteile der Schrägscheibenmaschine,

Fig. 5

einen Schnitt C-C gemäß Fig. 3 des Flansches und des dritten Lagerbockteiles der Schrägscheibenmaschine und

Fig. 6

einen Antriebsstrang für ein Kraftfahrzeug.

Hereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings. It shows:

Fig. 1

a longitudinal section of a swash plate machine through an axis of rotation of a drive shaft and perpendicular to a pivot axis of a pivoting cradle,

Fig. 2

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

Fig. 3

a view of a flange of a housing with the attached third bearing block part and two bearing shell parts,

Fig. 4

a section BB according to Fig. 3 the flange and the first, second and third bearing block parts of the swash plate machine,

Fig. 5

a section CC according to Fig. 3 of the flange and the third bearing block part of the swash plate machine and

Fig. 6

a drive train for a motor vehicle.

Embodiments of the invention

An in Fig. 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) in hydraulic energy (volume flow, pressure) or as axial piston 3 for conversion or conversion of hydraulic energy (flow, pressure) into mechanical energy ( Torque, speed). A drive shaft 9 is mounted rotatably or rotatably about a rotation axis 8 by means of a bearing 10 on a flange 21 of a housing or multi-part housing 4 and with a further mounting 10 on the housing 4 of the swash plate machine 1 ( Fig. 1 ). With the drive shaft 9 is a cylinder drum 5 rotatably and connected in the axial direction, wherein the drive shaft 9 and the cylinder drum 5 are formed in one or two parts and the boundary between the drive shaft 9 and the cylinder drum 5 in Fig. 1 is shown in dashed lines. The cylinder drum 5 carries out the rotational movement of the drive shaft 9 with due to a rotationally fixed connection. In the cylinder drum 5, a plurality of piston bores 6 with an arbitrary cross section, for example square or circular, incorporated. The longitudinal axes of the piston bores 6 are aligned substantially parallel to the axis of rotation 8 of the drive shaft 9 or the cylinder drum 5. In the piston bores 6 each have a piston 7 is movably mounted. A pivoting cradle 14 is mounted pivotably about a pivot axis 15 on the housing 4. The pivot axis 15 is perpendicular to the plane of Fig. 1 and parallel to the drawing plane of Fig. 2 aligned. The axis of rotation 8 of the cylinder drum 5 is parallel to and in the plane of Fig. 1 arranged and perpendicular to the drawing plane of Fig. 2 , The housing 4 defines an interior space 44 which is filled with hydraulic fluid.

The pivoting cradle 14 has a flat or planar bearing surface 18 for the indirect support of a retaining disk 37. The retaining plate 37 has bores (not shown), within which a respective sliding shoe 39 is arranged. The sliding blocks 39 are located directly on the support surface 18 of the pivoting cradle 14. Each shoe 39 is connected to a respective piston 7. For this purpose, the sliding block 39 has a bearing ball 40 (FIG. Fig. 1 ), which is fixed in a bearing cup 59 on the piston 7, so that a piston joint 22 between the bearing ball 40 and the bearing cup 59 is formed on the piston 7. The partially spherical trained bearing ball 40 and bearing cup 59 are both complementary or spherical, so characterized in a corresponding possibility of movement between the bearing ball 40 and the bearing cup 59 on the piston 7, a permanent connection between the piston 7 and the shoe 39 is present. Due to the connection of the piston 7 with the rotating cylinder drum 5 and the connection of the bearing cups 59 with the sliding blocks 39, the sliding blocks 39 perform a rotational movement about the axis of rotation 8 with and due to the arrangement of the sliding blocks 39 in the holes of the retaining plate 37 also performs the retaining disc 37 a rotational movement about the rotation axis 8 with out. Thus, the retaining plate 37 is in constant indirect contact with the support surface 18 of the pivoting cradle 14, this is by a compression spring 41 under a Pressing force on the support surface 18 is pressed so that the sliding shoes 39 are pressed by the compression spring 41 on the support surface 18 directly.

The pivoting cradle 14 is - as already mentioned - pivotally mounted about the pivot axis 15 and further comprises an opening 42 (FIG. Fig. 1 ) for the implementation of the drive shaft 9. On the housing 4, a weighing storage 20 is formed. In this case, two counter bearing shells 23 are formed on the pivoting cradle 14. The two pivotable counter bearing shells 23 on the pivoting cradle 14 are each on a bearing shell 17, so that the two bearing shells 17 and two counter-bearing shells 23 form the weighing storage 20. Depending on a bearing surface 33 on the two bearing shells 17 is thus on an abutment surface 34 on the counter-bearing shells 23. The counter-cups 23 are integrally formed by the pivoting cradle 14 made of steel. The pivoting cradle 14 is thus pivotally mounted about the pivot axis 15 by means of a plain bearing 20 as a pivot bearing. In the illustration in Fig. 1 has the support surface 18 according to the sectional formation in Fig. 1 a pivot angle α of approximately + 20 °. The pivoting angle α is present between a fictitious plane perpendicular to the axis of rotation 8 and a plane spanned by the flat bearing surface 18 of the pivoting cradle 14 according to the sectional formation in FIG Fig. 1 , The pivoting cradle 14 can be pivoted between two pivoting angles α between + 20 ° and -20 ° by means of two pivoting devices 24.

The first and second pivoting means 25, 26 as pivoting means 24 has a connection point 32 between the pivoting device 24 and the pivoting cradle 14. The two pivoting devices 24 each have an adjusting piston 29, which is movably mounted in an adjusting cylinder 30. The adjusting piston 29 or an axis of the adjusting cylinder 30 is aligned substantially parallel to the axis of rotation 8 of the cylinder drum 5. At one in Fig. 1 On the left end region of the adjusting piston 29, this has a bearing socket 31, in which a bearing ball 19 is mounted. In this case, the bearing ball 19 on a pivoting arm 16 ( Fig. 1 to 2 ) of the pivoting cradle 14 is present. The first and second pivoting means 25, 26 is thus connected to a respective pivot ball 19 on a respective pivot arm 16 with the pivoting cradle 14. By opening one of the two valves 27, 28 as the first valve 27 on the first pivoting device 25 and the second valve 28 on the second feed device 26 as shown in FIG Fig. 1 can the pivoting cradle 14 are pivoted about the pivot axis 15, as this is applied to the adjusting piston 29 at the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30, a force. In this case, not only the pivoting cradle 14, but also the retaining disc 37 due to the pressurization with the compression spring 41, this pivotal movement of the pivoting cradle 14 from.

In an operation of the swash plate machine 1 as axial piston pump 2 is at a constant speed of the drive shaft 9 of the swash plate machine 1 funded volumetric flow greater, the greater the amount of the swivel angle α and vice versa. This is due to the in Fig. 1 The piston bores 6 of the rotating cylinder drum 5 are thus fluidly connected in an arrangement at the high pressure port 12 to the high pressure port 12 and in an arrangement on the Low-pressure port 13 fluidly connected to the low pressure port 13. In a swivel angle α of 0 ° and in an operation of the swash plate machine 1, for example as axial piston 2 despite a rotational movement of the drive shaft 9 and the cylinder drum 5 no hydraulic fluid from the axial piston pump 2 promoted, since the piston 7 perform no strokes in the piston bores 6. During operation of the swashplate machine 1 both as axial piston pump 2 and as axial piston motor 3, the piston bores 6, which are temporarily in fluid-conducting connection with the high-pressure opening 12, have a greater pressure on hydraulic fluid than the piston bores 6 which are temporarily in fluid-conducting connection with the low-pressure opening 13. An axial end 66 of the cylinder drum 5 rests on the valve disk 11. On a first side 64 of the housing 4 and the flange 21 of the housing 4, an opening 63 is formed with the bearing 10 and a second side 65 has a recess for supporting the drive shaft 9 with a further storage 10. In the opening 63, a mechanical seal 74 is also arranged, so that the hydraulic fluid can not flow out of the inner space 44 to the outside. The bearing surface 33 of the two bearing shells 17 rests on the abutment surface 34 on the pivoting cradle 14, respectively. In this case, the bearing shell 17 is formed by two separate components, namely a first bearing shell 77 and a second bearing shell 78. These two bearing shells 17, 77, 78 are indirectly by means of a three-piece bracket 79 to the housing 4, that is, the flange 21 of the swash plate machine 1, attached. The three-part bearing block 79 comprises a first bearing block part 70, a second bearing block part 71 and a third bearing block part 72, wherein the third bearing block part 72 is formed as a disk-shaped ring 73. The first and second bearing block part 70, 71 each have a partially cylindrical partial surface, on each of which the first bearing shell 77 and the second bearing shell 78 is attached. The first and second bearing block parts 70, 71 and the first and second bearing shells 77, 78 are in a projection direction in the plan view of FIG Fig. 3 rectangular shaped. The annular third bearing block part 72 is positively secured by means of a recess 75 on the flange 21 of the housing 4. Due to the compressive force between the flange 21 and the third bearing block part 72 is thus a positive and non-positive connection between the flange 21 and the third bearing block portion 72. Analogously, the third bearing block portion 72 has two separate recesses 76, each for positive reception of the first Bearing part 70 and the second bearing block part 71. As a result, the first and second bearing part 70, 71 positively and non-positively connected to the third bearing block part 73. Furthermore, the first and second bearing block parts 70, 71 are additionally fastened in a form-fitting manner to the third bearing block part 72 by means of a plurality of fastening bolts 61 or fastening pins 68.

The two bearing shell parts 62 as the first and second bearing shell 77, 78 are made of a different material, for. As PEEK or brass, such as the abutment surface 34 of the pivoting cradle 14 and the flange 21 made of steel and the first, second and third bearing block part 70, 71, 72. The bearing shell part 62 has the bearing surface 33. The bearing surface 33 is formed teilzylindermantelelförmig. At the pivoting cradle 14, an abutment shell 23 is provided, wherein the abutment shell 23 is also formed teilzylindermantelelförmig with an abutment surface 34 of the abutment shell 23. Depending on a bearing shell 17 on the first and second bearing block part 70, 71 is thus formed by a respective bearing shell portion 62 and the anvil shell 23 is direct formed without a separate component of the pivoting cradle 14 made of steel. A fictitious cylinder on the bearing surface 33 and the counter-surface 34 has a longitudinal axis which corresponds to the pivot axis 15 of the pivoting cradle 14. The abutment surface 34 on the pivoting cradle 14 rests on the bearing surface 33 on the bearing shell part 62. The bearing shell 17 and the counter bearing shell 23 thus form the weighing support 20 for the pivoting cradle 14. The bearing block parts 70, 71, 72 are made of steel as the housing 4th

Within the opening 63 of the flange 21, a bearing 10 for the drive shaft 9 and the mechanical seal 74 are arranged. A circular cross-sectional boundary surface of the flange 21 thus limits the opening 63 and the minimum distance 38 between the axis of rotation 8 of the drive shaft 9 and this boundary surface of the flange 21 for the opening 63 is substantially greater than the minimum radial distance 43 between the axis of rotation 8 and a Radial inside 80 of the bearing block 79, in particular of the third bearing block part 72 as well as the first and second bearing block part 70, 71. The two bearing block parts 70, 71 and thus resting thereon the first and second bearing shells 77, 78 and thus the two bearing surfaces 33 point it a small distance to the radial outer side of the drive shaft 9. Because of this small distance of the bearing surfaces 33 and the abutment surfaces 34 can thereby be introduced by the shoes 39 on the support surface 18 of the pivoting cradle 14 compressive forces on the bearing surfaces 33 and mating surfaces 34 at a small distance from each other in the flange 21, thereby advantageously, the pivoting cradle 14 has a slight bend. The large required diameter of the opening 63 for the bearing 10 and the mechanical seal 74 can thus be compensated by the opening 63 projecting over the bearing block 79.

Upon loading of the pivoting cradle 14 due to the pressure forces exerted by the sliding shoes 39 on the pivoting cradle 14 on the supporting surface 18, a greater bending or deformation occurs at the two inner end sides 36 of the bearing surface 33 and also at the first and second bearing block parts 70, 71 As in the outer end sides 35. In the third bearing block part 72 and in the first and second bearing block part 70, 71 are cavities 67 and recesses 69 formed so that thereby the bearing surface 33 in the region of the inner end sides 36 has a lower rigidity than in the region of the outer end sides 35. At a large bend and consequent deformation of the pivoting cradle 14 thus occurs due to the rigidity of the bearing surface 33 between the abutment surface 34 and the Storage surface 33 a substantially constant surface pressure. At the inner end sides 36 it comes so not to very large surface pressures. The substantially uniform surface pressure or pressure causes a uniform mechanical wear on the bearing surface 33 and on the abutment surface 34 due to the sliding bearing between the bearing and abutment surface 33, 34th

In Fig. 6 an inventive drive train 45 is shown. 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. With the planetary gear 48 two shafts 47 are driven, wherein a first shaft 47 is connected to a clutch 49 with a differential gear 56. A second or other shaft, which is driven by the planetary gear 48 drives a first swash plate machine 50 through a clutch 49 and the first swash plate machine 50 is hydraulically connected by means of two hydraulic lines 52 with a second swash plate machine 51. The first and second swash plate machines 50, 51 thereby form a hydraulic gear 60, and from the second swash plate machine 51, the differential gear 56 can also be driven by means of a shaft 47. The differential gear 56 drives the wheels 57 with the wheel shafts 58. Furthermore, the drive train 45 has two pressure accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55. The two accumulators 53 are hydraulically connected by means not shown hydraulic lines with the two swash plate machines 50, 51, so that mechanical energy of the engine 46 in the high-pressure accumulator 54 can be hydraulically stored and also in a recuperation 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 hydraulic energy stored in the high-pressure accumulator 54, the differential gear 56 can additionally be driven with a swash plate machine 50, 51.

Overall, significant advantages are associated with the swash plate machine 1 according to the invention. The bearing block 79 made of steel is designed in several parts, namely in three parts with the first bearing block part 70, the two bearing block part 71 and the third bearing block part 72. The first and second bearing block part 70, 71 each have partially cylindrical part surfaces, on each of which the first and second bearing shell 77th , 78 are attached. In the manufacture of the swashplate machine 1, these partially cylindrical partial surfaces on the separate components of the first and second bearing block part 70, 71 can be produced particularly easily by a machining tool, for example a lathe or a milling cutter. Thus, the first and second bearing block portion 70, 71 a small axial length in the direction of the axis of rotation 8 of the drive shaft 9 and thus also the total bearing block 79, since the third bearing block portion 72 is formed as a disc-shaped ring 73 with a small extension in the direction of As a result, the swash plate machine 1 as a whole has a small axial length and is simple and inexpensive to manufacture in terms of the bearing block 79.

Claims (12)

1. Swashplate machine (1) as axial piston pump (2) and/or axial piston motor (3), comprising

   - a cylinder drum (5) which is mounted so as to be rotatable, or for rotation, about an axis of rotation (8) and which has piston bores (6),

   - pistons (7) which are mounted movably in the piston bores (6),

   - a pivot cradle (14) which is mounted so as to be pivotable about a pivot axis (15),

   - a housing (4)

   - a cradle bearing arrangement (20) for the pivot cradle (14), with at least one fixed bearing shell (17) on a bearing block (79) and with at least one pivotable counterpart bearing shell (23) on the pivot cradle (14),

   characterized in that
   the bearing block (79) is of multi-part form.
2. Swashplate machine according to Claim 1,
   characterized in that
   the bearing block (79) is formed in three parts, and/or
   the fixed bearing shell (17) is fastened indirectly to the housing (4) by means of the multi-part bearing block (79),
   and/or
   the multi-part bearing block (79) is fastened, in particular directly, to the housing (4).
3. Swashplate machine according to Claim 1 or 2,
   characterized in that
   the cradle bearing arrangement (20) has two fixed bearing shells (17), and a first bearing shell (77) is fastened to a first bearing block part (70) and the second bearing shell (78) is fastened to a second bearing block part (71),
   and/or
   the multi-part bearing block (79) is formed as an additional component (79) in addition to the housing (4).
4. Swashplate machine according to Claim 3,
   characterized in that
   the first and second bearing block parts (70, 71) are fastened, in particular directly, to a third bearing block part (72),
   and/or
   in each case one fixed bearing shell (17) is fastened, in particular directly, to the first and/or second bearing block part (70, 71).
5. Swashplate machine according to Claim 4,
   characterized in that
   the third bearing block part (73) is fastened, in particular directly, to the housing (4), in particular to a flange (21) of the housing (4).
6. Swashplate machine according to Claim 4 or 5,
   characterized in that
   the third bearing block part (72) is formed as a ring (73), in particular a disk-shaped ring (73).
7. Swashplate machine according to one or more of Claims 4 to 6,
   characterized in that
   the first and second bearing block parts (70, 71) are fastened to the third bearing block part (72) by means of a fastening bolt (61) or fastening pin (68).
8. Swashplate machine according to one or more of the preceding claims,
   characterized in that
   the housing (4) and the bearing block parts (70, 71, 72) are composed of metal, for example steel or aluminium,
   and/or
   the housing (4) and the bearing block parts (70, 71, 72) are composed of an identical material.
9. Swashplate machine according to one or more of the preceding claims,
   characterized in that
   in each case one bearing surface (33) on the bearing shell (17) lies on in each case one counterpart bearing surface (34) of the counterpart bearing shell (23),
   and/or
   the first and/or second and/or third bearing block part (70, 71, 72) has, at a radial inner side (80), a smaller minimum spacing (43), in particular a spacing which is smaller by 10%, 20%, 30% or 40%, to the axis of rotation (8) of the cylinder drum (5) than the housing (4), in particular a flange (21), at an opening (63) with a bearing arrangement (10) for the drive shaft (9).
10. Swashplate machine according to one or more of the preceding claims,
    characterized in that
    the swashplate machine (1) is designed such that the at least one bearing surface (33) and/or the at least one counterpart bearing surface (34) has a lower stiffness in a direction parallel to the pivot axis (15) of the pivot cradle (14) in the region of an inner end side (36) facing toward the drive shaft (9) than in the region of an outer end side (35) averted from the drive shaft (9).
11. Drivetrain (45) for a motor vehicle, comprising

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

    - at least one pressure accumulator (53),

    characterized in that
    the swashplate machine (1) is designed according to one or more of the preceding claims.
12. Drivetrain according to Claim 11,
    characterized in that
    the drivetrain (45) comprises two swashplate machines (1) which are hydraulically connected to one another and which function as a hydraulic transmission (60),
    and/or
    the drivetrain (45) comprises two pressure accumulators (53) as high-pressure accumulator (54) and low-pressure accumulator (55).

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