WO2015036176A1 - Machine à plateau inclinable en tant que pompe à pistons axiaux et/ou moteur à piston axiaux - Google Patents

Machine à plateau inclinable en tant que pompe à pistons axiaux et/ou moteur à piston axiaux Download PDF

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Publication number
WO2015036176A1
WO2015036176A1 PCT/EP2014/066774 EP2014066774W WO2015036176A1 WO 2015036176 A1 WO2015036176 A1 WO 2015036176A1 EP 2014066774 W EP2014066774 W EP 2014066774W WO 2015036176 A1 WO2015036176 A1 WO 2015036176A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder drum
swash plate
bearing
plate machine
drum
Prior art date
Application number
PCT/EP2014/066774
Other languages
German (de)
English (en)
Inventor
Matthias Greiner
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2015036176A1 publication Critical patent/WO2015036176A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0652—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • 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 12.
  • 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.
  • Cylinder drum with piston bores is rotatably or rotatably mounted and pistons are arranged in the piston bores.
  • the cylinder drum is rotatably connected to a drive shaft and on a first part of the rotating piston bores temporarily acts a hydraulic fluid under high pressure and a second part of the rotating piston bores temporarily acts a hydraulic fluid under low pressure.
  • a pivoting cradle is around one
  • Swivel axis mounted pivotally and on the pivoting cradle lie on sliding shoes.
  • the pistons are attached to the sliding shoes.
  • Retaining disc with the sliding shoes performs together with the cylinder drum a rotational movement about a rotation axis and a flat
  • Support surface of the pivoting cradle is aligned at an acute angle, for example between 0 ° and + 20 ° and between 0 ° and -20 ° as a pivot angle, to the axis of rotation of the cylinder drum.
  • the shoes are with a plain bearing, which is generally hydrostatically relieved, on the
  • the pistons in the piston bores have different axial positions in a pivoted pivoting cradle, so that different centripetal forces act on the pistons due to the rotational movement of the cylinder drum. This leads to a tilting movement of the cylinder drum, which leads to leaks between the
  • EP 1 013 928 A2 shows an axial piston pump in a swashplate design with a driven circumferential and a plurality of piston bores having cylinder bores, wherein in each of webs separated piston bores are arranged linearly between a bottom dead center and a top dead center movable pistons and a Niederbuchan gleichniere and a Hochdruckin kidney having control disk is provided.
  • the CH 405 934 shows a Schrägusionnaxialkolbenpumpe whose non-rotating cylinder block for varying the flow rate in dependence on the delivery pressure is longitudinally displaceable, wherein at the pressed by a spring in the direction of increasing the delivery cylinder block a
  • Control slide unit is attached with a spool.
  • DE 27 33 870 C2 shows a control device for a
  • Oblique disk axial piston pump on each side of the cradle for pivoting the swash plate, each a hydraulically acted upon
  • Swinging wing engages the engine, wherein both motors are controllable by means of a pivotable about the pivot axis of the cradle arranged plate-shaped control valve spool and for adjusting the delivery of the
  • Swash plate machine as axial piston pump and / or axial piston motor, comprising one rotatable about an axis of rotation or
  • Piston holes in the direction of a longitudinal axis of the piston bores movably mounted pistons, one with the cylinder drum at least rotatably connected
  • Swashplate machine comprises a device for limiting a tilting movement of the cylinder drum.
  • Tilting movement of the cylinder drum limits a tilt angle of the
  • the cylinder drum of the swash plate machine advantageously has no large tilt angle, thereby avoiding tumbling of the cylinder drum due to a large tilt angle and thus also damage to the swash plate machine resulting can be avoided in an advantageous manner.
  • a tilting movement of the cylinder drum also leads to hydraulic losses between the piston bores on the cylinder drum and a high and low pressure opening on a valve disc of the swash plate machine.
  • the device for limiting the tilting movement of the cylinder drum limits a tilting movement of the cylinder drum about a tilt axis perpendicular to the axis of rotation of the cylinder drum.
  • the tilting axis is substantially perpendicular to the axis of rotation of the
  • Cylinder drum and / or substantially perpendicular to the longitudinal axis of Gear shaft aligned that is aligned with a deviation of less than 10 °, 5 ° or 3 ° perpendicular to the axis of rotation of the cylinder drum and / or perpendicular to the longitudinal axis of the drive shaft.
  • the device limits the limitation of
  • Cylinder drum mechanical contact between the device and the cylinder drum is required. If the cylinder drum does not have a tilt angle or only a tilt angle below the tilt limit angle, no contact occurs between the device and the cylinder drum and thus also no friction between the device and the cylinder drum.
  • the device for limiting the tilting movement of the cylinder drum acts only from a Kippgrenzwinkel, which to larger
  • Tilting movement of the cylinder drum designed as a, in particular exclusive, mechanical device.
  • the device for limiting the tilting movement thus has, for example, no electric, pneumatic or hydraulic actuators for moving the device and / or the mechanical device is stationary and / or immovable.
  • the cylinder drum bearing as the device is preferably an optional cylinder drum bearing, as the
  • Cylinder drum bearing preferably acts only from a Kippgrenzwinkel for storage of the cylinder drum.
  • the cylinder drum bearing is in contact with a radial outer side of the cylinder drum or is brought into contact for limiting the tilting movement of the cylinder drum.
  • the radial outer side of the cylinder drum is a particularly effective outside of the cylinder drum for limiting the tilt angle of the cylinder drum, as in a Tilting movement of the cylinder drum, the distance of the radial outer side to the longitudinal axis of the drive shaft changed.
  • the cylindrical drum bearing is in contact or in contact with an axial distance to an axial end of the cylinder barrel and the axial end of the cylinder barrel is an axial end facing away from the pivoting cradle and the axial distance is at least 10%, 20%, 30% or 40% of the total axial extent of the cylinder drum.
  • a sufficient axial distance of the cylinder drum bearing to the axial end of the cylinder drum is required so that of the
  • Cylinder drum can be applied to limit the tilting movement of the
  • Cylinder drum because the tilting axis is positioned in the region of a fictitious plane and the notional plane rests on the axial end of the cylindrical drum, said axial end is an axial end of the cylinder drum facing away from the pivoting cradle.
  • the cylinder drum bearing is tangentially completely circumferentially in contact or is brought into contact with the radial outer side of the
  • Cylinder drum or the cylinder drum bearing is tangentially rotating only in at least two or three areas in contact or can be brought into contact with the radial outer side of the cylinder drum.
  • Cylinder drum in three areas in contact or is in three areas with the cylinder drum on the radially outside in contact, which is
  • Cylinder drum bearing for example, designed as a three-point bearing for the cylinder drum with respect to a tilting movement of the cylinder drum.
  • the cylinder drum bearing at a tilt angle of 0 ° at a distance to the radial outside of the
  • the cylinder drum bearing has at a tilt angle of 0 ° at a distance from the radial outer side of the cylinder drum and only with a tilting movement of the cylinder drum to a Kippgrenzwinkel occurs contact between the cylinder drum bearing and the radial
  • Tilt angle of the cylinder drum thus occur no frictional forces between the Cylinder drum bearing and the radial outside of the cylinder drum on.
  • the cylinder drum bearing advantageously acts only when it is necessary for the operation of the swash plate machine to prevent a large tilt angle of the cylinder drum.
  • the swash plate machine comprises a housing and the device, in particular the cylinder drum bearing, is fixedly connected to the housing, in particular the Zylindertrommelgleitlagerung is formed by the housing.
  • the Zylindertrommelgleitlagerung a tribological coating, for. As carbon, brass, PTFE or PEEK, on.
  • the tribological coating reduces the friction between the cylinder drum bearing and the radial outside of the cylinder drum. As a result, the efficiency of the
  • Sliding disc machine can be additionally improved.
  • Inventive drive train 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 as one in this patent application
  • the drive train comprises 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
  • the swash plate machine comprises a weighing storage for the pivoting cradle.
  • the swash plate machine comprises at least one
  • 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.
  • the swash plate machine includes a high pressure port for discharging and / or introducing hydraulic fluid from and / or into the rotating piston bores.
  • 1 is a longitudinal section of a swash plate machine
  • Fig. 2 shows a cross section A-A of FIG. 1 a valve disc of
  • Fig. 3 shows a longitudinal axis of the drive shaft and the cylinder drum in a tilted cylinder drum
  • FIG. 4 shows a drive train for a motor vehicle.
  • a swashplate machine 1 shown in a longitudinal section in FIG. 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,
  • a drive shaft 9 is by means of a bearing 10 at a
  • piston bores 6 with an arbitrary cross-section, for example square or circular, incorporated.
  • Piston bores 6 are aligned substantially parallel to the axis of rotation 8 of the drive shaft 9 or the cylinder drum 5.
  • Piston holes 6 are each a piston 7 movably mounted.
  • Swivel cradle 14 is mounted pivotably about a pivot axis 15 on the housing 4.
  • the pivot axis 15 is aligned perpendicular to the plane of Fig. 1 and parallel to the plane of Fig. 2.
  • the axis of rotation 8 of the cylinder drum 5 is arranged parallel to and in the plane of the drawing of FIG. 1 and perpendicular to the plane of the drawing of FIG.
  • Hydraulic fluid is filled.
  • the pivoting cradle 14 has a flat or planar support surface 18 for the indirect support of a retaining disk 37 and for the direct support of sliding shoes 39.
  • the retaining disc 37 is connected to a plurality of sliding shoes 39 by the sliding shoes in holes of the
  • Retaining disc 37 are arranged and each shoe 39 is connected to a respective piston 7.
  • the retaining disc 37 has an opening 38 for the passage of the drive shaft 9.
  • Bearing ball 40 (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 that in a corresponding movement possibility to each other 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 shoes 39 lead a
  • Rotational movement about the axis of rotation 8 with out and due to the fixed Connection or arrangement of the sliding blocks 39 on the retaining disc 37 also guides the retaining disc 37 a rotational movement about the
  • the pivoting cradle 14 is - as already mentioned - pivotally mounted about the pivot axis 15 and further comprises an opening 42 (Fig. 1) for
  • a weighing storage 20 is formed on the housing 4.
  • 14 two bearing sections are formed on the pivoting cradle.
  • the two bearing sections of the pivoting cradle 14 rest on the weighing support 20.
  • the pivoting cradle 14 is thus by means of a
  • Swivel axis 15 pivotally mounted.
  • the support surface 18 according to the sectional formation in Fig. 1 has a pivot angle ⁇ of approximately + 20 °.
  • the pivot angle ⁇ 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
  • the pivoting cradle 14 can between two pivotal limit angle ⁇ between + 20 ° and -20 ° by means of two
  • Swivel devices 24 are pivoted.
  • 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.
  • Adjusting piston 29 has this a bearing cup 31, in which a
  • Bearing ball 19 is mounted.
  • the bearing ball 19 on a pivot arm 16 (Fig. 1 to 2) of the pivoting cradle 14 is present.
  • Pivoting device 25, 26 is thus connected to a respective pivot ball 19 on a respective pivot arm 16 with the pivoting cradle 14.
  • the pivoting cradle 14 can be pivoted about the pivot axis 15, since a force is applied to the adjusting piston 29 at the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30.
  • the pivoting cradle 14 does not only does 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 with.
  • a valve disk 1 1 is located on the end of the cylinder drum 5 shown on the right in FIG. 1, with a kidney-shaped high-pressure opening 12 and a kidney-shaped
  • the cylinder drum 5 is axially movable and tiltable about a tilting axis 33 with respect to the drive shaft 9 and with a central spring
  • the cylinder drum 5 is pressed in the axial direction of the valve disc 1 1.
  • the tilting axis 33 is perpendicular to the axis of rotation 8 of
  • the central spring 73 rests on a support ring 34 which on the
  • Cylinder drum 5 is fixed and on a further support ring 35 which is fixed to the drive shaft 9.
  • the piston bores 6 of the rotating cylinder drum 5 are thus fluidly connected in an arrangement on the high pressure port 12 to the high pressure port 12 and fluidly connected in an arrangement on the low pressure port 13 with the low pressure port 13.
  • a swivel angle ⁇ 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.
  • Axial piston motor 3 have 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 disc 1 1.
  • On a first side 64 of the housing 4 and the flange 21 of the housing 4 is a Opening 63 formed with the bearing 10 and a second side 65 has a recess for supporting the drive shaft 9 with a further storage 10.
  • the cylinder drum 5 is connected by means of the rotationally fixed connection 43 only rotationally fixed to the drive shaft 9, so that the cylinder drum 5 with respect to the drive shaft 9 in the direction of a longitudinal axis 61 of the drive shaft 9 is axially movable and in addition with respect to the drive shaft 9 is tilted with respect to the tilting axis 33rd
  • the central spring 73 is required so that upon start-up of the swash plate machine 1, the cylinder drum 5 is pressed at the axial end 66 with a sufficient pressure force on the valve disc 1 1 to a substantially fluid-tight connection between the high and low pressure openings 12, 13 at the Valve disk 1 1 and the piston bores 6 on the cylinder drum 5 to achieve.
  • Swivel angle ⁇ of the cylinder drum 5 not equal to 0 °, have the piston 7 in the
  • Cylinder drum 5 about the tilting axis 33.
  • Fig. 1 is the
  • Tilting movement of the cylinder drum 5 about the tilting axis 33 has the
  • Cylinder drum 5 on a tilt angle ß a respective positive and negative tilt angle ß is shown simplified, that is, there is an angle ß between the longitudinal axis 62 of the cylinder barrel 5 and the longitudinal axis 61 of the drive shaft 9.
  • the tilt angle ⁇ of the cylinder drum 5 is limited by a device 23 for limiting the tilting movement of the cylinder drum 5 to a Kippgrenzwinkel ß of, for example, 1 °, 2 ° or 3 °.
  • the representation in FIG. 3 for the size of the tilt angle ⁇ thus does not correspond to reality in this respect.
  • Device 23 is designed as a cylinder drum bearing 67, for example, as a cylinder drum slide bearing 68 or as a
  • Cylinder drum roller bearing 69 with rolling elements not shown.
  • the cylinder drum bearing 67 has at a tilt angle ß of the cylinder drum 5 of 0 ° or at a tilt angle ß of less than the Kippgrenzwinkel ß, to which the cylinder drum 5 can be tilted maximum, no contact with a radial outer side 70 of the cylinder drum 5.
  • a tilt angle ß of 0 ° that is, in an identity between the longitudinal axis 61 of
  • Cylinder drum bearing 67 thus acts only if the tilt angle ß exceeds a maximum tilt angle ß or up to the Kippgrenzwinkel ß, up to which a tilting of the cylinder drum 5 about the tilting axis 33 is possible.
  • the cylinder barrel 5 has an overall axial extent 71 in the direction of
  • the cylinder drum bearing 67 has an axial distance 72 to the axial end 66 of the cylinder drum 5 on the valve disc 11 and this corresponds to about 30% of the axial
  • FIG. 4 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.
  • 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 by means of two hydraulic lines 52 with a second swash plate machine 51 hydraulically connected.
  • 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.
  • Differential gear 56 drives the wheels 57 with the wheel shafts 58.
  • 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 thereby mechanical energy of the engine 46 in the high-pressure accumulator 54 can be stored hydraulically 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.
  • the differential gear 56 can additionally be driven with a swash plate machine 50, 51.
  • the swash plate machine 1 is connected to the cylinder drum bearing 67 as the mechanical device 23 for
  • Tilting movement of the cylinder drum 5 about the tilting axis 33 is thereby limited to a Kippgrenzwinkel ß, so characterized on the one hand, the hydraulic losses between the cylinder drum 5 at the axial end 66 and the valve disc 1 1 are limited and also substantially tumbling the
  • Cylinder drum 5 due to large tilt angles ß can be avoided and thereby also resulting damage to the
  • the device 23 increases the speed capability of the swash plate machine 1, that is, the maximum possible speed of the cylinder drum 5 with proper operation to about 6000 U / min.
  • the central spring 73 can also be designed with a lower thickness, since the device 23 is present to limit the tilting movement at higher rotational speeds of the swashplate machine 1. As a result, due to the lower compressive forces applied by the central spring 73 to the cylinder drum 5, low frictional forces also occur between the cylinder drum 5 and the valve disk 11, so that in the Operation of the swash plate machine 1, an additional higher efficiency can be achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Machine à piston axiaux (1) en tant que pompe à pistons axiaux (2) et/ou moteur à pistons axiaux (3), qui comporte un barillet (5) monté rotatif autour d'un axe de rotation (8) et pourvu d'alésages pour pistons (6), des pistons (7) montés coulissants dans la direction d'un axe longitudinal des alésages pour pistons (6) dans lesdits alésages pour pistons (6), un arbre d'entraînement (9) relié au moins solidaire en rotation avec le barillet (5) et monté rotatif autour de l'axe de rotation (8), et un plateau inclinable (14) monté pivotant autour d'un axe de pivotement (15) et pourvu d'une surface d'appui (18) pour l'appui des pistons (7) sur ladite surface d'appui (18). Selon l'invention, ladite machine à pistons axiaux (1) comporte un dispositif (23) servant à limiter un mouvement de basculement du barillet (5).
PCT/EP2014/066774 2013-09-11 2014-08-05 Machine à plateau inclinable en tant que pompe à pistons axiaux et/ou moteur à piston axiaux WO2015036176A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310218124 DE102013218124A1 (de) 2013-09-11 2013-09-11 Schrägscheibenmaschine
DE102013218124.8 2013-09-11

Publications (1)

Publication Number Publication Date
WO2015036176A1 true WO2015036176A1 (fr) 2015-03-19

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PCT/EP2014/066774 WO2015036176A1 (fr) 2013-09-11 2014-08-05 Machine à plateau inclinable en tant que pompe à pistons axiaux et/ou moteur à piston axiaux

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WO (1) WO2015036176A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015212601A1 (de) 2015-07-06 2017-01-12 Robert Bosch Gmbh Verfahren zur Steuerung und Regelung eines Antriebsstranges

Citations (6)

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Publication number Priority date Publication date Assignee Title
DE941343C (de) * 1953-03-25 1956-04-05 Ingrid Moser Steuerung fuer Fluessigkeitspumpen und -getriebe
DE1924010A1 (de) * 1969-05-10 1970-11-19 Bosch Gmbh Robert Hydrostatische Kraftuebertragungseinrichtung
GB1374816A (en) * 1972-03-01 1974-11-20 Dowty Technical Dev Ltd Hydraulic swash plate pump
DE4340061A1 (de) * 1993-11-24 1995-06-01 Linde Ag Axialkolbenmaschine in Schrägscheibenbauart
DE19855899A1 (de) * 1998-12-03 2000-06-08 Linde Ag Axialkolbenmaschine
DE102009058715A1 (de) * 2009-12-17 2011-07-07 Robert Bosch GmbH, 70469 Axialkolbenmaschine in Schrägscheibenbauweise

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Publication number Priority date Publication date Assignee Title
CH405934A (de) 1962-07-26 1966-01-15 Weatherhead Co Schrägscheiben-Axialkolbenpumpe
US4076459A (en) 1976-09-14 1978-02-28 Abex Corporation Horsepower limiter control for a variable displacement pump
EP1013928A3 (fr) 1998-12-22 2000-11-08 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE941343C (de) * 1953-03-25 1956-04-05 Ingrid Moser Steuerung fuer Fluessigkeitspumpen und -getriebe
DE1924010A1 (de) * 1969-05-10 1970-11-19 Bosch Gmbh Robert Hydrostatische Kraftuebertragungseinrichtung
GB1374816A (en) * 1972-03-01 1974-11-20 Dowty Technical Dev Ltd Hydraulic swash plate pump
DE4340061A1 (de) * 1993-11-24 1995-06-01 Linde Ag Axialkolbenmaschine in Schrägscheibenbauart
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DE102009058715A1 (de) * 2009-12-17 2011-07-07 Robert Bosch GmbH, 70469 Axialkolbenmaschine in Schrägscheibenbauweise

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