DE102015208925A1 - 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 mounted rotatably or rotatably about the rotation axis (8), a low-pressure opening for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores (6) and the low-pressure port at one of the cylinder drum (5) facing the end of a low-pressure channel is formed and the low-pressure channel in sections with sectional planes through and parallel to the axis of rotation (8) ND-channel centers, a high-pressure opening for and / / or introducing hydraulic fluid from and / or into the rotating piston bores (6) and facing the high-pressure port on one of the cylinder drums (5) The end of a high-pressure channel is formed and the high-pressure channel in cuts with sectional planes through and parallel to the axis of rotation (8) HD channel centers, the smaller the axial distances in the direction of the axis of rotation (8) of the cylinder drum (5) of the ND-channel centers to the cylinder drum (5), the smaller are the radial distances of the ND channel centers to the axis of rotation (8) of the cylinder drum (5) and / or the smaller the axial distances in the direction of the axis of rotation (8) of the cylinder drum (5) HD channel centers to the cylinder drum (5), the smaller the radial distances of the HD channel centers to the axis of rotation (8) of the cylinder drum (5).

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 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.

The cylinder drum is located on an axial end facing away from the cylinder drum on a distributor plate. In the distributor plate, a high-pressure channel and a low-pressure channel are formed, which each form a high-pressure opening and a low-pressure opening on a first side of the distributor plate. In an operation of the swash plate machine as an axial piston pump hydraulic fluid is sucked by the low-pressure channel under a small pressure as a low pressure suction side and through the high-pressure channel, the hydraulic fluid is discharged at a higher pressure than high pressure again. The distributor plate and thus the high and low pressure channel in the distributor plate is fixed and the cylinder drum performs a rotational movement about the axis of rotation. The hydraulic fluid flowing into the piston bores through the low-pressure passage is thus accelerated during the inflow from the low-pressure passage into the piston bores or flow extensions of the piston bores to the rotational movement of the cylinder drum. The larger the rotational speed to which the hydraulic fluid is to be accelerated, the larger the hydraulic losses due to hydraulic friction and the lower the suction capacity of the swash plate machine as the axial piston pump on the low-pressure passage.

The low-pressure channel is limited by limitations of the distributor plate and also has the low-pressure channel ND-channel centers (low-pressure channel centers) on. The boundaries of the low-pressure channel in this case have a constant radial distance to the axis of rotation of the cylinder drum or the axis of rotation of the drive shaft. The ND channel centers also have a constant distance to the axis of rotation. As a result, the low-pressure opening has a large radial distance to the rotation axis and thus occurs at the mouth of the low-pressure opening in the piston bores or flow extensions of the piston bores on a large rotational speed. Because of this large radial distance and the resulting high rotational speed thus the hydraulic fluid must be strongly accelerated when introducing the low pressure channel into the piston bores or flow extensions of the piston bores, so that disadvantageously large hydraulic losses due to friction occur and thus the swash plate machine as axial piston pump only has a low absorbency in a disadvantageous manner.

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 acted swing wing on the engine, both motors by means of a pivot about the pivot of the cradle arranged plate-shaped control valve spool are controllable and serve to adjust the flow rate of the pump.

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 low-pressure port for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores and the low-pressure port is formed at an end of a low pressure passage facing the cylinder barrel, and the low pressure port is cut into sections having sectional planes through and parallel to the rotational axis of ND duct centers (Low-pressure channel centers), a high-pressure opening for discharging and / or introducing hydraulic fluid from and / or into the rotating piston bores and the high-pressure opening at one end of a cylinder drum facing the end Druckkanales is formed and the high-pressure channel in cuts with sectional planes through and parallel to the axis of rotation HD channel (high-pressure channel centers), wherein the smaller the axial distances in the direction of the axis of rotation of the cylinder drum of the ND-channel centers to the cylinder drum, the smaller the radial distances of the ND channel centers to the axis of rotation of the cylindrical drum and / or the smaller the axial distances in the direction of the axis of rotation of the cylinder drum of the HD channel centers to the cylinder drum, the smaller the radial distances of the HD channel centers to the axis of rotation of the cylinder drum.

The ND channel centers thus have at the low-pressure opening, that is at the mouth of the low-pressure channel in the piston bores or in the extensions of the piston bores, a small radial distance to the axis of rotation of the drive shaft. When operating the swash plate machine as an axial piston pump thus the hydraulic fluid when flowing out of the low pressure opening and when flowing into the piston bores or the flow extensions of the piston bores only a slight acceleration of the hydraulic fluid to the low rotational speed of the cylinder drum on the piston bores and the flow extensions of the piston bores required , The piston bores or flow extensions of the piston bores on the cylinder drum are aligned with the low-pressure opening. As a result, small hydraulic losses occur when flowing out of the low-pressure opening and when flowing into the piston bores or flow extensions of the piston bores during operation of the swash plate machine as axial piston pump on the suction side, that is, on the low-pressure channel. As a result, the swash plate machine advantageously has a high absorbency.

Due to the small radial distance of the high-pressure opening to the axis of rotation of the drive shaft, low hydraulic losses also occur at the high-pressure channel, since during operation of the swash plate machine as axial piston pump when the hydraulic fluid is discharged from the piston bores or the flow extensions of the piston bores, the hydraulic fluid returns from the rotational movement to the rotary shaft is braked fixed high-pressure channel in the distributor plate.

In a supplementary variant, the radial distances of the ND channel centers to the axis of rotation of the cylinder drum are substantially, preferably with a deviation of less than 20% or 10%, directly proportional to the axial distances in the direction of the axis of rotation of the cylindrical drum of the ND channel centers the cylindrical drum and / or the radial distances of the HD channel centers to the axis of rotation of the cylinder drum are substantially, preferably with a deviation of less than 20% or 10%, directly proportional to the axial distances in the direction of the axis of rotation of the cylinder drum of the HD channel centers to the cylinder drum.

In an additional embodiment, the radial distances of the ND channel centers to the axis of rotation of the cylinder barrel towards the cylinder barrel, preferably steadily, decrease and / or the radial distances of the HD channel centers to the axis of rotation of the cylinder barrel increase towards the cylinder barrel, preferably steady, down.

The low-pressure channel and the high-pressure channel are expediently formed on a distributor plate, and the distributor plate has a first axial side and a second axial side opposite the first side, and the first side of the distributor plate rests against the cylindrical drum on an axial end of the cylindrical drum facing away from the pivoting cradle and / or the low-pressure opening and the high-pressure opening are fixed.

In a supplemental embodiment, the radial distance of the ND channel center to the axis of rotation of the cylinder drum at the first side of the distributor plate is smaller than at the second side, in particular at the first side smaller than 90 % or 80% or 70% of the radial distance of the ND channel center on the second side and / or the radial distance of the HD channel center to the axis of rotation of the cylindrical drum is smaller at the first side of the distributor plate than at the second side, in particular at the first side less than 90% or 80% or 70% of the radial distance of the HD channel center on the second side.

In an additional embodiment, at least one boundary, in particular both boundaries, of the low-pressure channel is formed as a partial cone jacket tapering in the direction of the cylinder drum and / or at least one boundary, in particular both boundaries, of the high-pressure channel is or are in the direction of trained to the cylinder drum tapered part cone sheath.

In an additional variant, at the first side of the distributor plate, the minimum radial distance of the low-pressure channel and / or the low-pressure opening to the axis of rotation is less than the maximum radial distance to the axis of rotation of a second bearing for the drive shaft in a section on the second side of the distributor plate a sectional plane perpendicular to the axis of rotation and the second bearing for the drive shaft has a greater axial distance to the pivoting cradle than the axial end of the cylinder drum on which the distributor plate rests and / or on the first side of the distributor plate is the minimum radial distance of the high pressure channel and or the high-pressure opening to the rotation axis smaller than the maximum radial distance to the rotation axis of a second support for the drive shaft in a section on the second side of the distributor plate with a sectional plane perpendicular to the axis of rotation and the second storage f r, the drive shaft has a larger axial distance from the pivot cradle to as the axial end of the cylinder drum on which the distribution plate rests. The maximum radial distance of the second bearing on the second side of the distributor plate is structurally predetermined and thereby causes a large radial distance of the low-pressure channel on the second side of the distributor plate. Due to the formation of the low-pressure channel with a decreasing radial distance from the second side to the first side of the distributor plate so that the low-pressure channel has the advantageous small radial distance to the axis of rotation on the first side.

In an additional embodiment, the axial distances in the direction of the axis of rotation of the cylindrical drum of the ND-channel centers to the cylinder drum, the axial distances to a notional distance plane and the fictitious distance plane is aligned perpendicular to the axis of rotation of the cylinder drum and the fictitious distance plane intersects the cylinder drum and / or the axial distances in the direction of the axis of rotation of the cylinder drum of the HD channel centers to the cylinder drum are the axial distances to a fictitious distance plane and the fictitious distance plane is aligned perpendicular to the axis of rotation of the cylinder drum and the fictitious distance plane intersects the cylinder drum.

In a supplementary variant, the high-pressure opening is divided into high-pressure partial openings and the high-pressure channel is subdivided into high-pressure partial channels.

Suitably, each high-pressure part of channel HD channels on.

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 supplementary embodiment, the swashplate machine comprises a pivoting cradle mounted pivotably about a pivot axis with a support surface for direct or indirect support of the pistons on the support surface.

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.

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 distributor plate of the swash plate machine and a view of a pivoting cradle,

3 a section with a sectional plane through and parallel to the axis of rotation of a cylinder drum of the swash plate machine according to 1 in the area of a distributor plate and

4 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 as a first storage 17 on a flange 21 one- or multi-part housing 4 and with another storage 10 as second storage 23 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 rotatably connected, wherein the drive shaft 9 and the cylinder drum 5 are formed in two parts 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. The cylinder drum 5 is in the axial direction, ie in the direction of the axis of rotation 8th , From a spring, not shown, on a distributor plate 11 pressed and the cylinder drum 5 is axial with respect to the drive shaft 9 movable. 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 and 3 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 drive shaft 9 is through an opening 38 the annular retaining disc 37 guided. 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 66 the cylinder drum 5 a distributor plate 11 on with a kidney-shaped high-pressure opening 12 and a kidney-shaped low-pressure opening 13 , In the distributor plate 11 are a high pressure channel 34 and a low pressure channel 35 incorporated. The distributor plate 11 is located on a first page 75 on the axial end 66 the cylinder drum 5 on, so the first page 75 a sliding bearing for the cylinder drum 5 forms. A second page 76 the distributor plate 11 which are opposite to the first page 75 is, lies on the case 4 ie a second page 65 of the housing 4 on. The high-pressure opening 12 is from an axial end of the high pressure passage 34 on the first page 75 formed and the low-pressure opening 13 is from an axial end of the low pressure passage 35 on the first page 75 educated. The high pressure channel 34 is in high pressure subchannels 36 divided and thus is also the high-pressure opening 12 in high pressure part openings 33 divided. This subdivision has only static reasons due to the large on the high pressure channel 35 occurring pressures of the hydraulic fluid. The piston bores 6 or flow extensions of 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. The axial end 66 the cylinder drum 5 lies on the distributor plate 11 on. On a first page 64 of the housing 4 or the flange 21 of the housing 4 is an opening 63 with the first storage 17 trained and a second page 65 has a recess for mounting the drive shaft 9 with the second storage 23 on.

The retaining disc 37 is formed annularly as a flat disc and thus has an opening for the passage of the drive shaft 9 on. At the retaining disc 37 are sliding shoes 39 with bearing balls 40 attached. 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.

In 3 is a section through the swashplate machine 1 in the area of the distributor plate 11 represented with a sectional plane through and parallel to the axis of rotation 8th the cylinder drum 5 and the drive shaft 9 , In the 3 Section shown thus includes all points of the axis of rotation 8th , The low pressure channel 35 points in the in 3 section shown ND sewer centers (low pressure channel centers) 62 as points on and the ND channel centers 62 form in 3 a straight. The low pressure channel 35 has a first boundary 73 with a small radial distance to the axis of rotation 8th on and a second limit 74 with a large radial distance to the axis of rotation 8th on. In the sectional formation in 3 is the first and second limit 73 . 74 formed as a straight line, so that thereby the line, which points the ND-channel centers 62 forms, exactly in the middle between the two boundaries 73 . 74 is arranged. The ND Canal Center 62 is thus due to the representation in 3 to the effect that in a section perpendicular to 3 the radial distance of the first and second boundary 73 . 74 to the axis of rotation 8th is determined and that Low pressure center channel 62 the mean radial distance of the first and second boundaries 73 . 74 to the axis of rotation 8th is. The cylinder drum 5 is through a fictitious distance plane 43 cut and the fictitious distance plane 43 is perpendicular to the axis of rotation 8th aligned. The axial distance 68 of the ND Canal Center 62 is thus the axial distance of the ND channel center 62 to the fictitious distance level 43 , The radial distance 70 of the ND Canal Center 62 is the radial distance 70 perpendicular to the axis of rotation 8th , The smaller the axial distances 68 the ND sewer centers 62 to the distance level 43 are, the smaller the radial distances 70 the ND sewer centers 62 and vice versa, that is the radial distances 70 the ND sewer centers 62 take in the direction of the cylinder drum 5 from. In an analogous way, the axial distances 67 the HD channel centers 61 the smaller, the smaller the radial distances 69 the HD channel centers 61 to the axis of rotation 8th are. The high pressure channel 34 points in the section in 3 analogous to a first limit 71 and a second boundary 72 on.

At the first page 75 the distributor plate 11 occurs a minimum radial distance 77 of the low pressure channel 35 , that is the low-pressure opening 13 , to the rotation axis 8th on. In a section with a cutting plane on the second side 76 the distributor plate 11 has the second storage 23 a maximum radial distance 79 to the axis of rotation 8th on. The minimum radial distance 77 of the low pressure channel 35 on the first page 75 is much smaller than the maximum radial distance 79 the second storage 23 , This is possible due to the structural design of the low-pressure channel 35 with a decreasing radial distance towards the cylinder drum 5 , The maximum radial distance 79 is structurally specified and the small radial distance 70 of the ND Canal Center 62 on the first page 75 the distributor plate 11 can only by the inventive design of the low-pressure channel 35 be achieved. In an analogous manner, the minimum radial distance is also 78 of the high pressure channel 35 on the first page 75 the distributor plate 11 less than the maximum radial distance 79 the second storage 23 ,

In 4 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 and the drive train according to the invention 45 significant benefits. The low pressure opening 13 as the axial end of the low pressure channel 35 on the distributor plate 11 points at the low pressure opening 13 an ND channel center 61 with a very small radial distance 70 to the axis of rotation 8th on. When introducing hydraulic fluid, which through the low-pressure channel 35 into the piston bores 6 or flow extensions of the piston bores 6 from the low pressure channel 35 into the piston bores 6 flows in, the hydraulic fluid during the influx in a rotational movement to accelerate at a rotational speed, which is the rotational speed of the piston bores 6 or flow extensions of the piston bores 6 at the low pressure opening 13 equivalent. The low pressure opening 13 Aligns with the piston bores 6 or the flow extensions of the piston bores 6 as the ends of the piston bores 6 at the axial end 66 the cylinder drum 5 , The smaller the radial distance 70 of the ND Canal Center 62 to the axis of rotation 8th is, the lower the rotational speed of the cylinder drum 5 at the ND Canal Center 62 and at a smaller rotational speed, the inflowing hydraulic fluid is to be accelerated. Due to the small radial distance 70 of the ND Canal Center 62 at the low pressure opening 13 Thus, only a small acceleration of the hydraulic fluid to a low rotational speed is required, thereby advantageously low hydraulic losses occur in this increase in the rotational speed of the hydraulic fluid and thus the Swash plate machine 1 during operation of the swash plate machine 1 as axial piston pump 2 has a high absorbency. In addition, also be at the high-pressure opening 12 during the outflow of the hydraulic fluid under a larger pressure during operation of the swash plate machine 1 as axial piston pump 2 due to the required lower reduction of the rotational speed of the hydraulic fluid reduces the hydraulic losses. Also when operating the swashplate machine 1 as axial piston motor 3 can reduce the hydraulic losses when entering and leaving the high and low pressure ports 12 . 13 in and out of the piston bores 6 thereby advantageously reduced and thus the efficiency of the swash plate machine 1 increase.

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 [0005]
• CH 405934 [0006]
• DE 2733870 C2 [0007]

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, - a low-pressure opening ( 13 ) for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores ( 6 ) and the low-pressure opening ( 13 ) on one of the cylinder drums ( 5 ) facing the end of a low pressure channel ( 35 ) is formed and the low-pressure channel ( 35 ) in sections with sectional planes through and parallel to the axis of rotation ( 8th ) ND channel centers ( 62 ), - a high-pressure opening ( 12 ) for discharging and / or introducing hydraulic fluid from and / or into the rotating piston bores ( 6 ) and the high-pressure opening ( 12 ) on one of the cylinder drums ( 5 ) facing the end of a high-pressure channel ( 34 ) is formed and the high-pressure channel ( 34 ) in sections with sectional planes through and parallel to the axis of rotation ( 8th ) HD channel centers ( 61 ), characterized in that the smaller the axial distances ( 68 ) in the direction of the axis of rotation ( 8th ) of the cylinder drum ( 5 ) of the ND-channel centers ( 62 ) to the cylinder drum ( 5 ), the smaller are the radial distances ( 70 ) of the ND-channel centers ( 62 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) and / or the smaller the axial distances ( 67 ) in the direction of the axis of rotation ( 8th ) of the cylinder drum ( 5 ) of the HD channel centers ( 61 ) to the cylinder drum ( 5 ), the smaller are the radial distances ( 69 ) of the HD channel centers ( 61 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ). Swash plate machine according to claim 1, characterized in that the radial distances ( 70 ) of the ND-channel centers ( 62 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) substantially, preferably with a deviation of less than 20% or 10%, directly proportional to the axial distances ( 68 ) in the direction of the axis of rotation ( 8th ) of the cylinder drum ( 5 ) of the ND-channel centers ( 62 ) to the cylinder drum ( 5 ) and / or the radial distances ( 69 ) of the HD channel centers ( 61 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) substantially, preferably with a deviation of less than 20% or 10%, directly proportional to the axial distances ( 67 ) in the direction of the axis of rotation ( 8th ) of the cylinder drum ( 5 ) of the HD channel centers ( 61 ) to the cylinder drum ( 5 ) are. Swash plate machine according to claim 1 or 2, characterized in that the radial distances ( 70 ) of the ND-channel centers ( 62 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) in the direction of the cylinder drum ( 5 ), preferably steadily, decrease and / or the radial distances ( 69 ) of the HD channel centers ( 61 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) in the direction of the cylinder drum ( 5 ), preferably steadily, decrease. Swash plate machine according to one or more of the preceding claims, characterized in that the low-pressure channel ( 35 ) and the high pressure channel ( 34 ) on a distributor plate ( 11 ) are formed and the distributor plate ( 11 ) a first axial side ( 75 ) and a second, the first page ( 75 ) opposite axial side ( 76 ) and the first page ( 75 ) of the distributor plate ( 11 ) on a pivoting cradle ( 14 ) facing away from the axial end ( 66 ) of the cylinder drum ( 5 ) on the cylinder drum ( 5 ) and / or the low-pressure opening ( 13 ) and the high-pressure opening ( 12 ) are formed fixed. Swash plate machine according to claim 4, characterized in that the radial distance ( 70 ) of the ND sewer center ( 62 ) to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) on the first page ( 75 ) of the distributor plate ( 11 ) is smaller than on the second page ( 76 ), especially on the first page ( 75 ) is less than 90% or 80% or 70% of the radial distance ( 70 ) of the ND sewer center ( 62 ) on the second page ( 76 ) and / or the radial distance ( 69 ) of the HD channel center ( 61 ) to the axis of rotation ( 8th ) of the cylinder drum ( 8th ) on the first page ( 75 ) of the distributor plate ( 11 ) is smaller than on the second page ( 76 ), especially on the first page ( 75 ) is less than 90% or 80% or 70% of the radial distance ( 69 ) of the HD channel center ( 61 ) on the second page ( 76 ). Swash plate machine according to one or more of the preceding claims, characterized in that at least one boundary ( 73 . 74 ), in particular both limitations ( 73 . 74 ), the low pressure channel ( 35 ) than towards the cylinder drum ( 5 ) is formed tapered partial cone sheath or are and / or at least one boundary ( 71 . 72 ), in particular both limitations ( 71 . 72 ), the high pressure channel ( 34 ) than towards the cylinder drum ( 5 ) tapered partial cone sheath is or are formed. Swash plate machine according to one or more of the preceding claims, characterized in that on the first side ( 75 ) of the distributor plate ( 11 ) the minimum radial distance ( 77 ) of the low pressure channel ( 35 ) and / or the low-pressure opening ( 13 ) to the axis of rotation ( 8th ) is less than the maximum radial distance ( 79 ) to the axis of rotation ( 8th ) a second storage ( 23 ) for the drive shaft ( 9 ) in a section on the second side ( 76 ) of the distributor plate ( 11 ) with a sectional plane perpendicular to the axis of rotation ( 8th ) and the second storage ( 23 ) for the drive shaft ( 9 ) a greater axial distance to the pivoting cradle ( 14 ) than the axial end ( 66 ) of the cylinder drum ( 5 ) on which the distributor plate ( 11 ) and / or on the first page ( 75 ) of the distributor plate ( 11 ) the minimum radial distance ( 78 ) of the high pressure channel ( 34 ) and / or the high-pressure opening ( 12 ) to the axis of rotation ( 8th ) is less than the maximum radial distance ( 79 ) to the axis of rotation ( 8th ) a second storage ( 23 ) for the drive shaft ( 9 ) in a section on the second side ( 76 ) of the distributor plate ( 11 ) with a sectional plane perpendicular to the axis of rotation ( 8th ) and the second storage ( 23 ) for the drive shaft ( 9 ) a greater axial distance to the pivoting cradle ( 14 ) than the axial end ( 66 ) of the cylinder drum ( 5 ) on which the distributor plate ( 11 ) rests. Swash plate machine according to one or more of the preceding claims, characterized in that the axial distances ( 68 ) in the direction of the axis of rotation ( 8th ) of the cylinder drum ( 5 ) of the ND-channel centers ( 62 ) to the cylinder drum ( 5 ) the axial distances ( 68 ) to a fictitious distance level ( 43 ) and the fictitious distance level ( 43 ) perpendicular to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) and the fictitious distance plane ( 43 ) the cylinder drum ( 5 ) cuts and / or the axial distances ( 67 ) in the direction of the axis of rotation ( 8th ) of the cylinder drum ( 5 ) of the HD channel centers ( 61 ) to the cylinder drum ( 5 ) the axial distances ( 67 ) to a fictitious distance level ( 43 ) and the fictitious distance level ( 43 ) perpendicular to the axis of rotation ( 8th ) of the cylinder drum ( 5 ) and the fictitious distance plane ( 43 ) the cylinder drum ( 5 ) cuts. Swash plate machine according to one or more of the preceding claims, characterized in that the high-pressure opening ( 12 ) in high-pressure part openings ( 33 ) and the high-pressure channel ( 34 ) in high pressure sub-channels ( 36 ) is divided. Swash plate machine according to claim 9, characterized in that each high-pressure part channel ( 36 ) HD channel centers ( 61 ) having. 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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