DE102014216212A1 - 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) rotatable about a rotation axis (8) with piston bores (6), pistons movably mounted in the piston bores (6) ( 7), a housing (4), one with the cylinder drum (5) at least rotatably connected drive shaft (9) which is rotatably mounted about the rotation axis (8) and a part (23) of the drive shaft (9) outside the housing (4) is arranged and on the part (23) of the drive shaft (9) outside the housing (4) a Verzahngeometrie (33) is formed for transmitting a torque, about a pivot axis (15) pivotally mounted pivoting cradle (14) with a support surface (18) for supporting the pistons (7) on the bearing surface (18), wherein the tooth geometry (33) comprises a plurality of teeth extending in the direction of a longitudinal axis (8) of the drive shaft (9) and tangentially between the teeth in the direction of a longitudinal axis (8) of the drive shaft (9) extending grooves are formed and the radial expansions of the grooves in a longitudinal section of the drive shaft (9) are different.

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 7.

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 sliding blocks are mounted with a sliding bearing, which is generally hydrostatically relieved, on the support surface of the pivoting cradle and the sliding blocks are connected to the retaining disc.

In motor vehicles, swash plate machines are used in a drive train. In this case, the drive train includes two swash plate machines and a first swash plate machine is mechanically coupled to a planetary gear as a mechanical transmission and a second swash plate machine is mechanically coupled to a differential gear as a mechanical transmission. For this purpose, a part of the drive shaft is guided outside the housing and has on the part outside a Verzahngeometrie. A gear drive shaft of the mechanical transmission has a Gegenverzahngeometrie and the teeth of the Verzahngeometrie mesh with the mating teeth of the Gegenverzahngeometrie, so that a positive connection between the drive shaft of the swash plate machine and the transmission input shaft for transmitting torque from the drive shaft to the transmission input shaft or vice versa. On the part of the drive shaft of the swash plate machine within the housing acting transverse forces. In addition, there are tolerances in the alignment between the Verzahngeometrie and the Gegenverzahngeometrie, for example due to manufacturing inaccuracies. The transverse forces acting on the drive shaft of the swash plate machine within the housing lead to a bending stress of the drive shaft of the swash plate machine, thereby resulting in a radial movement resulting from the axial end of the drive shaft of the part outside the housing with the gear geometry. The radial movement of the part of the drive shaft outside the housing can not be completely absorbed by the play or the tolerances between the Verzahngeometrie and the Gegenverzahngeometrie, so that it comes to large surface pressures between the Verzahngeometrie and the Gegenverzahngeometrie, especially at an axial end portion of the Verzahngeometrie as edge bearer. This leads to a large mechanical wear between the Verzahngeometrie and the Gegenverzahngeometrie, so that thereby the life of the swash plate machines is disadvantageously reduced. The high mechanical wear also leads to energy losses in the transmission of torque from the drive shaft to the transmission input shaft and vice versa.

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 linearly between a bottom dead center and a top dead center movable piston 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 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 housing, a drive shaft at least rotatably connected to the cylinder drum, which rotatable about the rotation axis is mounted, and a part of the drive shaft is disposed outside of the housing and on the part of the drive shaft outside the housing a Verzahngeometrie is formed for transmitting torque, a pivot about a pivot axis pivotally mounted pivoting cradle with a support surface for supporting the piston on the support surface, said the tooth geometry comprises a plurality of teeth extending in the direction of a longitudinal axis of the drive shaft and grooves are formed tangentially between the teeth extending in the direction of a longitudinal axis of the drive shaft and the radial dimensions of the grooves are different in a longitudinal section of the drive shaft. Due to the different radial expansions of the grooves of the Verzahngeometrie in the longitudinal section occur even with a radial movement of the part of the drive shaft outside the housing due to a bending of the drive shaft no large surface pressures between the Verzahngeometrie and a Gegenverzahngeometrie on a transmission input shaft, because the radial dimensions of the grooves adapted to these radial movements of the part of the drive shaft. Furthermore, there is a sufficient permanent positive engagement between the teeth of the Verzahngeometrie and the mating teeth of the Gegenverzahngeometrie, so that thereby the torque can be reliably transmitted from the drive shaft to the transmission input shaft and vice versa. Thus occurs at the Verzahngeometrie significantly reduced wear and also can thereby the efficiency of the swash plate machine and a drive train can be increased, since the energy losses are reduced in the transmission of torque from the drive shaft to the transmission input shaft or vice versa.

In an additional embodiment, with an external toothing, the radial expansions of the grooves are greater at axial end regions, in particular 1.5, 2, 3 or 4 times greater than at an axial middle region of the external toothing or at an internal toothing radial expansions of the grooves at an outer axial end portion larger, in particular by 1.5, 2, 3 or 4 times greater than at an inner axial end portion, respectively in the longitudinal section of the drive shaft.

In an additional embodiment, the radial end of the teeth, preferably in a section perpendicular to the axis of rotation, with a maximum distance to the axis of rotation of the drive shaft with an external toothing in the longitudinal section of the drive shaft at a substantially constant radial distance to the axis of rotation of the drive shaft or the radial end of the teeth, preferably in a section perpendicular to the axis of rotation, with a minimum distance to the axis of rotation of the drive shaft at an internal toothing in the longitudinal section of the drive shaft has a substantially constant radial distance from the axis of rotation of the drive shaft. Preferably, a substantially constant radial distance means that the radial distance differs by less than 20%, 10%, 5%, 2% or 1%. The radial end region of the teeth can also be convexly curved in a cross section, for example, partially circular or partially ellipsoidal, and the radial end of the teeth in the cross section with the maximum distance from the axis of rotation in the outer toothing is the relevant end through which the longitudinal section is essentially carried out is and at which the substantially constant distance in the longitudinal section occurs. This applies analogously to an internal toothing and / or a Gegenverzahngeometrie.

In a further embodiment, the grooves are formed at positions, preferably in a section perpendicular to the axis of rotation, with a minimum distance to the axis of rotation of the drive shaft convexly curved with external teeth in the longitudinal section of the drive shaft or the grooves are in positions, preferably in a section perpendicular to the axis of rotation, with a maximum distance from the axis of rotation of the drive shaft concavely curved at an internal toothing in the longitudinal section of the drive shaft. In the case of an internal toothing, the positions with a maximum distance to the axis of rotation of the drive shaft are therefore first to be determined, preferably in sections perpendicular to the axis of rotation, and subsequently these positions or substantially these positions are to be cut in the longitudinal section and at these positions are the grooves formed concavely curved in the longitudinal section. Conversely, this is an external toothing on the grooves. The grooves or boundaries of the grooves on the drive shaft may, for example, be concavely curved in cross-section in the region of the positions or be formed by two straight lines which are aligned at an acute angle to one another.

In a supplementary variant, the difference between the radial expansions of the grooves in a longitudinal section of the drive shaft is at least 2%, 5%, 10% or 20% of the total axial extent of the gearing geometry and / or on each groove in the longitudinal direction is the maximum difference between the positions with a minimum radial distance to the axis of rotation of the drive shaft with an external toothing or the positions with a maximum radial distance to the axis of rotation of the drive shaft with an internal toothing at least 2%, 5%, 10% or 20% of the total axial extent of the gear geometry.

Suitably, the drive shaft is formed on the Verzahngeometrie as a hollow shaft.

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 with a drive shaft which is rotatably mounted about the rotation axis, and a part of the drive shaft is arranged outside of a housing and on the part of Drive shaft outside the housing a Verzahngeometrie formed with teeth for transmitting torque, at least one accumulator, at least one gear with a gear input shaft with a Gegenverzahngeometrie with mating teeth and the mating teeth with the teeth of the Verzahngeometrie the drive shaft mesh for transmitting a torque, wherein the at least one Swashplate machine is designed as a swashplate machine described in this patent application and / or the Gegenverzahngeometrie a plurality in the direction of a longitudinal axis of the Getriebeantriebswel includes extending counter teeth and tangentially formed between the opposing teeth extending in the direction of a longitudinal axis of the transmission input shaft grooves and the radial dimensions of the grooves are different in a longitudinal section of the transmission input shaft.

In an additional embodiment, the tooth geometry is designed as external toothing and the counter tooth geometry is formed as internal toothing or the tooth geometry is formed as internal toothing and the counter tooth geometry is formed as external toothing.

In a further embodiment, the radial expansions of the grooves at axial end portions are larger, in particular by 1.5, 2, 3 or 4 times greater than in an axial central region of the external teeth or in an internal toothing in an external toothing radial expansions of the grooves at an outer axial end portion larger, in particular by 1.5, 2, 3 or 4 times greater than at an inner axial end portion, respectively in the longitudinal section of the transmission input shaft.

In a supplementary variant, the radial end of the mating teeth, preferably in a section perpendicular to the axis of rotation, with a maximum distance to the axis of rotation of the transmission input shaft with an external toothing in the longitudinal section of the drive shaft at a substantially constant radial distance to the axis of rotation of the transmission input shaft or the radial end of the mating teeth, preferably in a section perpendicular to the axis of rotation, with a minimum distance to the axis of rotation of the gear drive shaft at an internal toothing in the longitudinal section of the gear drive shaft has a substantially constant radial distance to the axis of rotation of the gear drive shaft.

In an additional embodiment, the grooves are formed at positions, preferably in a section perpendicular to the axis of rotation, with a minimum distance to the axis of rotation of the gear drive shaft convexly curved at an external toothing in the longitudinal section of the gear drive shaft or the grooves at positions, preferably in a section perpendicular to the rotation axis, with a maximum distance to the rotation axis of the transmission input shaft concavely curved at an internal toothing in the longitudinal section of the transmission input shaft are formed. In the case of an internal toothing, the positions with a maximum distance to the axis of rotation of the drive shaft are therefore first to be determined, preferably in sections perpendicular to the axis of rotation, and subsequently these positions or substantially these positions are to be cut in the longitudinal section and at these positions are the grooves formed concavely curved in the longitudinal section. Conversely, this is an external toothing on the grooves.

Preferably, the difference of the radial expansions of the grooves in a longitudinal section of the gear drive shaft is at least 2%, 5%, 10% or 20% of the total axial extent of the counter-tooth geometry and / or on a respective longitudinal groove the maximum difference between the positions is a minimum Distance to the axis of rotation of the transmission input shaft at an outer toothing or the positions with a maximum distance to the axis of rotation of the gear drive shaft with an internal toothing at least 2%, 5%, 10% or 20% of the axial total extent of the Gegenverzahngeometrie. The cross section is a section perpendicular to the axis of rotation.

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, as a transmission input shaft, a shaft is considered with a Gegenverzahngeometrie, in which the Gegenverzahngeometrie in mechanical form-locking operative connection with a Verzahngeometrie the drive shaft of the swash plate machine is for transmitting torque, in particular, the transmission input shaft directly or indirectly, z. Example, by means of a clutch, with a transmission, in particular mechanical transmission, mechanically coupled.

In a supplementary embodiment, concave or convexly curved also contemplates a geometry in which the concave or convex curvature is approximated by a plurality of straight lines in a longitudinal section.

In a further embodiment, the swash plate machine comprises a weighing storage for the pivoting cradle.

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

Hereinafter, embodiments 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 perspective view of a portion of a drive shaft outside of a housing of the swash plate machine according to 1 .

4 a side view of the drive shaft according to 3 .

5 a longitudinal section of the drive shaft according to 3 through grooves,

6 a longitudinal section of a transmission input shaft through grooves,

7 a partial section perpendicular to a rotational axis of the drive shaft according to 3 at a gearing geometry,

8th a partial section perpendicular to the axis of rotation of the transmission input shaft according to 6 at a Gegenverzahngeometrie and

9 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 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 educated. Here are at the pivoting cradle 14 formed two bearing sections. The two bearing sections of the pivoting cradle 14 lie on 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 1 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 one Recess for supporting 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 36 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.

In 9 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 as a mechanical transmission 43 become two waves 47 driven, being a first shaft 47 with a clutch 49 with a differential gear 56 connected is. A second or different wave 47 as a gear drive shaft 72 that 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 as a gear drive shaft 72 also the differential gear 56 are driven. The differential gear 56 as a mechanical transmission 43 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.

The swashplate machine 1 has the drive shaft 9 on. A part 17 the drive shaft 9 is inside the case 4 arranged and another part 23 the drive shaft 9 is outside the case 4 arranged. At the part 23 the drive shaft 9 outside the case 4 is a gear geometry 33 ( 1 . 3 . 4 . 5 and 7 ) educated. The tooth geometry 33 as an external toothing 34 includes a variety of teeth 61 extending in the direction of a longitudinal axis 8th as the axis of rotation 8th the drive shaft 9 extend, ie in an axial direction 74 , In a tangential direction 76 or circumferential direction 76 between the teeth 61 are grooves 62 available. A radial end 67 the teeth 61 is at the external toothing 34 the end 67 as an end 81 with a maximum radial distance to the axis of rotation 8th with respect to a cross section. The grooves 62 point in the section as a cross section perpendicular to the axis of rotation 8th ( 7 ) Positions 84 with a minimum radial distance to the axis of rotation 8th on. In 5 is a longitudinal section of the Verzahngeometrie 33 of the part 23 the drive shaft 9 on teeth 61 shown. In the cut in 5 are accordingly only the ends 81 the teeth 61 with the maximum radial distance of the tooth 61 to the axis of rotation 8th cut with respect to a cross-section according to 7 , The grooves 62 are shown by dashed lines. In the in 5 illustrated longitudinal section of the teeth 61 have the radial ends 67 the teeth 61 as the ends 81 a substantially constant radial distance 78 to the axis of rotation 8th on. The axial end portions of the teeth 61 each have a phase 77 ( 5 ) on. The phases 77 do not have a radial end 67 or end 81 on and also no positions 84 so on the stages 77 also no radial expansions 85 the grooves 62 occur. The drive shaft 9 is at the part 23 with the tooth geometry 33 designed as a hollow shaft. The axial distance between the axial ends of the teeth 61 in the axial direction 74 is the total axial extent 71 the gearing geometry 33 , The radial extent 85 a groove 62 in a section perpendicular to the axis of rotation 8th is the difference between the maximum radial distance of one end 81 of the tooth 67 which the groove 62 limited, and the minimum radial distance of the position 84 the groove 62 each to the axis of rotation 8th , In 7 is a fictitious circle 86 drawn in and the circle 86 with the center of the rotation axis 8th is approximately on the ends 81 the teeth 61 on, so that the radial extent 85 graphically better drawn. Notwithstanding this (not shown) may be on the ends 81 two adjacent teeth 61 in the 7 cross section shown a notional straight line and the line lies in the plane of 7 so that the straight line is the circle 85 replaced. The radial extent 85 the groove 62 is the radial difference between the position 84 and the fictitious circle 85 or the fictitious line as another way to determine the radial extent 85 the groove 62 , The grooves 62 are at the positions 84 in the 5 shown Longitudinal section formed convexly curved. The radial extent 85 the grooves 62 is at an axial center area 88 the external toothing 34 thus smaller than at the two axial end portions 87 due to the convex curvature in the longitudinal section. The axial center area 88 For example, it covers 30% of the total axial extent 71 and the two axial end portions 87 each 35% of the total axial extent.

The transmission input shaft 72 ( 1 . 6 and 8th ) as a stub shaft 73 has a conically tapered male portion 80 on. At the transmission input shaft 72 is a Gegenverzahngeometrie 36 as an internal toothing 35 educated. The counter tooth geometry 36 on the gear drive shaft 72 is geometrically complementary to the Verzahngeometrie 33 on the drive shaft 9 educated. In an analogous manner, the Gegenverzahngeometrie 36 a variety of opposing teeth 68 on and the opposing teeth 68 extend in the direction of a longitudinal axis 8th as the axis of rotation 8th the transmission input shaft 72 , In tangential direction 76 are thus between the opposing teeth 68 groove 62 educated. The radial end 67 the opposing teeth 68 is set in a section perpendicular to the axis of rotation 8th the transmission input shaft 72 as the end 82 the opposing teeth 68 with the minimum radial distance of the opposing teeth 68 to the axis of rotation 8th , The radial distance is in a radial direction 75 perpendicular to the axis of rotation 8th determined. In the in 8th illustrated section of the transmission input shaft 72 have the grooves 62 positions 83 with a maximum radial distance to the axis of rotation 8th on. In 6 is a longitudinal section through the transmission input shaft 72 at the Gegenverzahngeometrie 36 at two grooves 62 shown, so that the opposing teeth 68 are shown only dashed. The grooves 62 are formed concavely curved in the longitudinal section. In the longitudinal section in 6 at the positions 83 the grooves 62 with the maximum radial distance 70 to the axis of rotation 8th occurs the maximum radial distance 70 in the longitudinal section in 6 at the axial end of the Gegenverzahngeometrie 36 on which of the swashplate machine 1 is facing. At the grooves 62 in the 6 shown longitudinal section occurs the minimum radial distance 69 to the axis of rotation 8th the transmission input shaft 72 at the axial end of the Gegenverzahngeometrie 36 turned away from the swash plate machine 1 on. At the conical plug-in section 80 are also teeth 61 and grooves 62 trained, however, these are not used for torque transmission, so that the teeth 61 and grooves 62 at the conical insertion section 80 not considered in the consideration of the invention and no radial end 67 or end 82 exhibit and no position 85 , so that on the insertion section 80 no radial expansions 85 the grooves 62 occur. At the opposing teeth 68 the Gegenverzahngeometrie 36 is the radial end 67 the opposing teeth 68 in the 8th illustrated section perpendicular to the axis of rotation 8th the transmission input shaft 72 set as an end 82 with a minimum radial distance of the opposing teeth 68 to the axis of rotation 8th the transmission input shaft 72 , Between the axial ends of the counter tooth geometry 36 occurs the total axial extent 71 the Gegenverzahngeometrie 36 on. The radial extent 85 a groove 62 in a section perpendicular to the axis of rotation 8th according to 8th is the difference between the minimum radial distance of one end 82 of the tooth 67 which the groove 62 limited, and the maximum radial distance of the position 83 the groove 62 each to the axis of rotation 8th , In 8th is a fictitious circle 86 drawn in and the circle 86 with the center of the rotation axis 8th is approximately on the ends 82 the teeth 61 on, so that the radial extent 85 graphically better drawn. Notwithstanding this (not shown) may be on the ends 82 in the 8th cross section shown a notional straight line and the line lies in the plane of 8th so that the straight line is the circle 85 replaced. The radial extent 85 the groove 62 is the radial difference between the position 83 and the fictitious circle 85 or the fictitious line as another way to determine the radial extent 85 the groove 62 , The grooves 62 are at the positions 83 in the 6 formed longitudinal section concave curved. The radial extent 85 the grooves 62 at an inner axial end region 89 the internal toothing 35 is thus smaller than at an outer axial end portions 90 due to the concave curvature in the longitudinal section. The two axial end areas 89 . 90 For example, each comprise 25% of the total axial extent 71 ,

The axial end of the part 23 the drive shaft 9 outside the case 4 with the Verzahngeometrie 33 due to lateral forces acting on the drive shaft 9 as the part 17 inside the case 4 act, movements in a radial direction 75 out. Due to the convex curved tooth geometry 33 in the longitudinal section and the concave curved Gegenverzahngeometrie 36 in the longitudinal section exists between the Verzahngeometrie 33 and the Gegenverzahngeometrie 36 even with such movements of the axial end of the part 23 in the radial direction 75 a sufficient clearance or tolerance between the gearing geometry 33 and the Gegenverzahngeometrie 36 , so that even at large on the drive shaft 9 at the part 17 acting shear forces no large surface pressures between the Verzahngeometrie 33 and the Gegenverzahngeometrie 36 occur, in particular at an axial inner end region 89 the Gegenverzahngeometrie 36 turned away to the pivoting cradle 14 , Due to the convex and concave curvature is also in operation between the teeth 61 the gearing geometry 33 and the opposing teeth 68 the Gegenverzahngeometrie 36 a constant sufficient form fit for transmitting torque from the drive shaft 9 on the transmission input shaft 72 or the other way around.

Overall, considered with the swash plate machine according to the invention 1 and the drive train according to the invention 45 significant benefits. Due to the convex design of the Verzahngeometrie 33 in the longitudinal section and the concave design of the Gegenverzahngeometrie 36 is the geometry of the gear geometry 33 and the Gegenverzahngeometrie 36 to a movement of the axial end of the part 23 in the radial direction 75 adapted due to a bending stress of the drive shaft 9 , This allows large surface pressures between the Verzahngeometrie 33 and the Gegenverzahngeometrie 36 be avoided and still a sufficient sufficient form fit between the Verzahngeometrie 33 and the Gegenverzahngeometrie 36 to provide. The swashplate machine 1 and the powertrain 45 This advantageously has a long service life and 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 ), - a housing ( 4 ), - one with the cylinder drum ( 5 ) at least rotatably connected drive shaft ( 9 ), which around the axis of rotation ( 8th ) is rotatably or rotatably mounted, and a part ( 23 ) of the drive shaft ( 9 ) outside the housing ( 4 ) and on the part ( 23 ) of the drive shaft ( 9 ) outside the housing ( 4 ) a tooth geometry ( 33 ) is designed to transmit a torque, - 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 ), characterized in that the tooth geometry ( 33 ) a plurality in the direction of a longitudinal axis ( 8th ) of the drive shaft ( 9 ) extending teeth ( 61 ) and tangentially between the teeth ( 61 ) in the direction of a longitudinal axis ( 8th ) of the drive shaft ( 9 ) extending grooves ( 62 ) are formed and the radial dimensions ( 85 ) of the grooves ( 62 ) in a longitudinal section of the drive shaft ( 9 ) are different. Swash plate machine according to claim 1, characterized in that in the case of external toothing ( 34 ) the radial expansions ( 85 ) of the grooves ( 62 ) at axial end regions ( 87 ) are larger, in particular by 1.5, 2, 3 or 4 times larger than at an axial middle region ( 88 ) of external teeth ( 34 ) or with an internal toothing ( 35 ) the radial expansions ( 85 ) of the grooves ( 62 ) at an outer axial end region ( 90 ) are larger, in particular by 1.5, 2, 3 or 4 times larger than at an inner axial end region ( 89 ). Swash plate machine according to claim 1 or 2, characterized in that the radial end ( 67 . 81 ) the teeth ( 61 ) with a maximum distance to the axis of rotation ( 8th ) of the drive shaft ( 9 ) in an outer toothing ( 34 ) in the longitudinal section of the drive shaft ( 9 ) has a substantially constant radial distance ( 78 ) to the axis of rotation ( 8th ) of the drive shaft ( 9 ) or the radial end ( 67 . 82 ) the teeth ( 61 ) with a minimum distance to the axis of rotation ( 8th ) of the drive shaft ( 9 ) in an internal toothing ( 35 ) in the longitudinal section of the drive shaft ( 9 ) has a substantially constant radial distance ( 78 ) to the axis of rotation ( 8th ) of the drive shaft ( 9 ) having Swash plate machine according to one or more of the preceding claims, characterized in that the grooves ( 62 ) at positions ( 84 ) with a minimum distance to the axis of rotation ( 8th ) of the drive shaft ( 9 ) convexly curved with an outer toothing ( 34 ) in the longitudinal section of the drive shaft ( 9 ) are formed or the grooves ( 62 ) at positions ( 83 ) with a maximum distance to the axis of rotation ( 8th ) of the drive shaft ( 9 ) concavely curved with an internal toothing ( 35 ) in the longitudinal section of the drive shaft ( 9 ) are formed. Swash plate machine according to one or more of the preceding claims, characterized in that the difference of the radial expansions ( 85 ) of the grooves ( 62 ) in a longitudinal section of the drive shaft ( 9 ) at least 2%, 5%, 10% or 20% of the total axial extent ( 71 ) of the tooth geometry ( 33 ) is Swash plate machine according to one or more of the preceding claims, characterized in that the drive shaft ( 9 ) at the gearing geometry ( 33 ) as a hollow shaft ( 9 ) is trained. 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 with a drive shaft ( 9 ), which around the axis of rotation ( 8th ) is rotatably or rotatably mounted, and a part ( 23 ) of the drive shaft ( 8th ) outside of a housing ( 4 ) and on the part ( 23 ) of the drive shaft ( 9 ) outside the housing ( 4 ) a tooth geometry ( 33 ) with teeth ( 61 ) is designed for transmitting a torque, - at least one pressure accumulator ( 53 ), - at least one transmission ( 43 ) with a transmission input shaft ( 72 ) with a counter-tooth geometry ( 36 ) with opposing teeth ( 68 ) and the opposing teeth ( 68 ) with the teeth ( 61 ) of the tooth geometry ( 33 ) of the drive shaft ( 9 ) mesh for transmitting a torque, characterized in that the at least one swash plate machine ( 1 ) is formed according to one or more of the preceding claims and / or the Gegenverzahngeometrie ( 36 ) a plurality in the direction of a longitudinal axis ( 89 the transmission input shaft ( 72 ) extending opposing teeth ( 68 ) includes and tangentially between the opposing teeth ( 68 ) in the direction of a longitudinal axis ( 8th ) of the transmission input shaft ( 72 ) extending grooves ( 62 ) are formed and the radial dimensions ( 85 ) of the grooves ( 62 ) in a longitudinal section of the transmission input shaft ( 72 ) are different. Drive train according to claim 7, characterized in that the tooth geometry ( 33 ) as external teeth ( 34 ) is formed and the Gegenverzahngeometrie ( 36 ) as internal toothing ( 35 ) is formed or the Verzahngeometrie ( 33 ) as internal toothing ( 35 ) is formed and the Gegenverzahngeometrie ( 36 ) as external teeth ( 34 ) is trained. Drive train according to claim 7 or 8, characterized in that (at an external toothing 34 ) the radial expansions ( 85 ) of the grooves ( 62 ) at axial end regions ( 87 ) are larger, in particular by 1.5, 2, 3 or 4 times larger than at an axial middle region ( 88 ) of external teeth ( 34 ) or with an internal toothing ( 35 ) the radial expansions ( 85 ) of the grooves ( 62 ) at an outer axial end region ( 90 ) are larger, in particular by 1.5, 2, 3 or 4 times larger than at an inner axial end region ( 89 ). Drive train according to one or more of claims 7 to 9, characterized in that the radial end ( 67 ) of the opposing teeth ( 68 ) with a maximum distance to the axis of rotation ( 8th ) of the transmission input shaft ( 72 ) in an outer toothing ( 34 ) in the longitudinal section of the drive shaft ( 9 ) has a substantially constant radial distance ( 78 ) to the axis of rotation ( 8th ) of the transmission input shaft ( 72 ) or the radial end ( 67 ) of the opposing teeth ( 68 ) with a minimum distance to the axis of rotation ( 8th ) of the transmission input shaft ( 72 ) in an internal toothing ( 35 ) in the longitudinal section of the transmission input shaft ( 72 ) has a substantially constant radial distance ( 78 ) to the axis of rotation ( 8th ) of the transmission input shaft ( 72 ) having. Drive train according to one or more of claims 7 to 10, characterized in that the grooves ( 62 ) at positions ( 84 ) with a minimum distance to the axis of rotation ( 8th ) of the transmission input shaft ( 72 ) convexly curved with an outer toothing ( 34 ) in the longitudinal section of the transmission drive shaft ( 72 ) are formed or the grooves ( 62 ) at positions ( 83 ) with a maximum distance to the axis of rotation ( 8th ) of the transmission input shaft ( 72 ) concavely curved with an internal toothing ( 35 ) in the longitudinal section of the transmission input shaft ( 72 ) are formed. Drive train according to one or more of claims 7 to 11, characterized in that the difference of the radial expansions ( 85 ) of the grooves ( 62 ) in a longitudinal section of the transmission input shaft ( 72 ) at least 2%, 5%, 10% or 20% of the total axial extent ( 71 ) of the counter-tooth geometry ( 36 ) is.

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