WO2012168083A2 - Machine à piston axial dans un mode de construction à disque incliné - Google Patents

Machine à piston axial dans un mode de construction à disque incliné Download PDF

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Publication number
WO2012168083A2
WO2012168083A2 PCT/EP2012/059682 EP2012059682W WO2012168083A2 WO 2012168083 A2 WO2012168083 A2 WO 2012168083A2 EP 2012059682 W EP2012059682 W EP 2012059682W WO 2012168083 A2 WO2012168083 A2 WO 2012168083A2
Authority
WO
WIPO (PCT)
Prior art keywords
piston
dead center
cylinder
cylinders
displacement
Prior art date
Application number
PCT/EP2012/059682
Other languages
German (de)
English (en)
Other versions
WO2012168083A3 (fr
Inventor
Rolf Lernbecher
Udo Diehl
Ralph Engelberg
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 WO2012168083A2 publication Critical patent/WO2012168083A2/fr
Publication of WO2012168083A3 publication Critical patent/WO2012168083A3/fr

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-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
    • F04B1/22Multi-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 having two or more sets of cylinders or pistons
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-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
    • F04B1/2014Details or component parts
    • F04B1/2035Cylinder barrels

Definitions

  • Axial piston machine is a collective term for a device used in hydraulics such as axial piston pump or axial piston motor.
  • An axial piston pump converts mechanical energy such as torque and speed into hydraulic energy such as volume flow and pressure.
  • An axial piston motor is very similar to the structure of an axial piston pump, but sets in contrast to
  • Axial piston pump converts hydraulic energy such as flow and pressure into mechanical energy such as torque and speed.
  • axial piston machine in swash plate construction is suitable
  • a big advantage of axial piston machines over other types is the high stability and the good inner seal, which makes high pressures possible.
  • pressures of 500 to 600 bar are achieved by means of such axial piston pumps.
  • Axial piston machines range from about 1 to about 1000 kW with speeds up to 12,000 min "1 .
  • Axial piston machine provided in swash plate construction with a piston drum, wherein the piston drum is rotatably connected to a drive shaft rotatable about a rotation axis.
  • the piston drum has a plurality of first cylinders arranged substantially parallel to the axis of rotation.
  • the first cylinders are arranged on a first circle with a first diameter.
  • a first piston displaceable between a first bottom dead center and a first top dead center along a first translational direction is arranged.
  • Each first piston can be coupled in a pressure-transfer-capable manner along the first translational direction to a swivel disk which is arranged in an articulated manner and adjustable in its inclination relative to the axis of rotation.
  • the piston drum has a plurality of second cylinders arranged substantially parallel to the axis of rotation, wherein the second cylinders are arranged on a second circle with a second diameter.
  • a second piston displaceable between a second bottom dead center and a second top dead center along a second translational direction is arranged, wherein each second piston can be coupled to the swashplate in a pressure-transmitting manner along the translational direction.
  • the first diameter is different from the second diameter.
  • the center of the first circle is equal to the center of the second circle.
  • other cylinders can be arranged in, for example, a third and / or fourth circle, these circles may be concentric to the first and second circle.
  • the cylinder which are arranged on the circle with the larger diameter, promote a larger volume with a larger working stroke. Since the efficiency increases with increasing stroke, the efficiency of the axial piston machine is due to the
  • the first translational direction may be parallel to the second translational direction.
  • the individual pistons abut with so-called sliding shoes on the swash plate fixed relative to the pistons so that only compressive forces can be transmitted from the pistons to the swash plate and vice versa.
  • the skids slide against the abutment surface on the swashplate.
  • the first cylinders of the axial piston machine are present in a first number and the second cylinders are present in a second number.
  • the first number is different from the second number.
  • the first cylinders of the axial piston machine are present in a first number and the second cylinders are present in a second number.
  • the first number is equal to the second number.
  • the first number of first cylinders of the axial piston machine and / or the second number of second cylinders are odd.
  • the choice of an odd number of cylinders can at least largely prevent pulsations or vibrations of the fluid in the system.
  • the first number of cylinders may for example be even and only the second number may be odd.
  • the first cylinder of the axial piston machine has a first cylinder wall and a first displacement.
  • the first piston has a first piston bottom.
  • the first displacement is limited by the first piston bottom displaced into the first bottom dead center, by the first piston bottom displaced into the first top dead center and by the first cylinder wall.
  • the second cylinder has a second cylinder wall and a second displacement.
  • the second piston has a second piston bottom which is different from the first piston crown.
  • the second displacement is from the second piston bottom displaced into the second bottom dead center, from the second piston bottom displaced into the second top dead center, and from the second piston bottom
  • the first piston has a first piston stroke limited by the first bottom dead center and the first top dead center
  • the second piston has a second piston stroke limited by the second bottom dead center and the second top dead center. If one considers the displacement at the same first piston stroke and second piston stroke, the first displacement and the second displacement are different.
  • the cylinders are formed as a straight circular cylinder, this means that the first piston head of the first piston in the first cylinder has a first piston head diameter, which of a second
  • Cylinder is different.
  • Piston diameter may be a first generated by the first cylinders
  • volume flow vary.
  • first displacement and the second displacement in connection with the first number of the first cylinder and the second number of the second cylinder may be designed such that the first Volumetric flow of the second flow differs.
  • the second volume flow will be greater than the first volume flow.
  • the first cylinder has a first cylinder wall and a first displacement.
  • the first piston has a first piston bottom.
  • the first displacement is limited by the first piston bottom displaced into the first bottom dead center, by the first piston bottom displaced into the first top dead center and by the first cylinder wall.
  • the second cylinder has a second one
  • the second piston has a second piston crown.
  • the second displacement is from the second piston bottom displaced into the second bottom dead center, from the second piston bottom displaced into the second top dead center, and from the second piston bottom
  • the first piston has a first piston stroke limited by the first bottom dead center and the first top dead center.
  • the second piston has a second piston stroke limited by the second bottom dead center and the second top dead center.
  • the first and the second displacement are the same when the first piston stroke and the second piston stroke are the same.
  • This embodiment differs from the previous embodiment in that, when the first cylinder and the second cylinder are formed as a straight circular cylinder, a first
  • Piston bottom diameter of the first piston crown of the first piston and a second piston crown diameter of the second piston crown of the second piston are equal.
  • the advantages described in the preceding embodiment are also valid for this embodiment. In this case as well, care is taken in an advantageous manner that the first volume flow of the first cylinder in conjunction with the first number and the second volume flow of the second cylinder in conjunction with the second number are different. Again, the second volume flow will usually be greater than the first volume flow.
  • the first cylinder extends along a first centerline.
  • the second cylinder extends along a second centerline.
  • a first half-way begins from the rotation axis and cuts the first center line.
  • a second half-straight starts from the axis of rotation and intersects the second center line.
  • Half-way and the second half-way span a plane that is perpendicular to the axis of rotation.
  • An included angle between the first half-line and the second half-line is not equal to 0 °.
  • a first cylinder and a second cylinder can be arranged opposite one another, so that the included angle is thereby 180 °.
  • the first cylinder and the second cylinder may be directly adjacent because the angle enclosed between the two straight lines would thus be 0 °.
  • This advantageous arrangement can be in full load operation, so if the swash plate is deflected maximum to the axis of rotation, effectively suppress pulsations.
  • the angle may be such that when a first cylinder of a
  • Axial piston machine also has a control, wherein the control element is connected fluid-tight with a side facing away from the swash plate of the piston drum.
  • the piston drum is rotatable with respect to the control.
  • the control element provides the first cylinders with a first input area and a first output area.
  • the control element provides a second input region and a second output region for the second cylinders.
  • all areas are separated from each other fluid-tight.
  • a fluid supplied to the first input portion has no connection to a fluid supplied to the second input portion.
  • the fluid which is supplied to the first input area, separated by the control of the fluid, which is discharged by means of the first or the second output area.
  • the first cylinders with a first fluid
  • the second cylinders with a second fluid
  • the first fluid may be different from the second fluid.
  • the control element may for example be designed such that the Ports are designed as kidney-shaped or annular recesses.
  • the first input area and the first input area are designed as kidney-shaped or annular recesses.
  • Output region may be arranged on a common third circle with a third diameter, wherein the annular or kidney-shaped formation of the first input terminal of the kidney-shaped or annular shape of the first output terminal are interrupted only by webs.
  • the webs will be arranged in such a manner depending on the pivoting direction of the swash plate, that a separation of the input region from the output region takes place in a region in which the first piston reverses its translational motion, so if the first piston its lower and top dead center has reached.
  • the second input area and the second output area may be configured as well, the second input area and the second input area
  • Diameter may be arranged, wherein the fourth diameter may be different from the third diameter.
  • a first high pressure is associated with the first input region and a second high pressure is associated with the second input region.
  • the first input region is separable from the first high pressure by means of a first valve and the second high pressure region is separable from the second high pressure by means of a second valve.
  • first high pressure and the second high pressure will be the same. Both the first high pressure and the second high pressure can usually from a common hydrostatic or hydraulic accumulator
  • the first valve and the second valve may be arranged such that when the axial piston engine is not in operation, the first high pressure and the second high pressure are separated from the hydrostatic drive. This makes it possible, for example, to avoid emptying of a hydraulic accumulator in a hydraulic hybrid vehicle.
  • the first output region and the first input region can be connected to one another in a fluid-conducting manner by a first valve.
  • the second output area and the second Entrance area are fluidly connected by a second valve with each other.
  • the first cylinder and / or second cylinder can be shorted.
  • a short circuit that can be done in the respective
  • Circulating fluid circulate, without that by the piston movement, by the rotating axial piston machine with a swung out
  • predetermined speed and / or at a predetermined torque in the partial load range are swung more strongly with respect to the axis of rotation than is the case with an axial piston machine with only first cylinders. This allows the entire axial piston in a cheaper
  • Efficiency map are operated. It is also possible, by a suitable choice of activation or deactivation of the first and / or second cylinder, to operate the axial piston machine in wide operating ranges with large swash angles of the swashplate. This increases the
  • the first valve and the second valve are each a 2/3-way valve.
  • the valves are usually designed as solenoid valves.
  • the axial piston machine forms a compact unit which has only a high-pressure and a low-pressure connection to the outside. It is noted that thoughts on the invention herein are described in the context of a swash plate type axial piston machine. It will be clear to a person skilled in the art that the individual features described can be combined with one another in various ways so as to arrive at other embodiments of the invention.
  • Figure 1 shows an axial piston machine in swash plate design in
  • FIG. 2 shows the axial piston machine from FIG. 1 under pump operation
  • FIG. 3 shows the axial piston machine from FIG. 1 under engine operation
  • Figure 4 shows an axial piston machine in swash plate design with first and second cylinders in longitudinal section with a rotation axis perpendicular to a standing disc;
  • FIG. 5 shows the axial piston machine from FIG. 4 under pump operation
  • FIG. 6 shows a piston drum of the axial piston machine from FIG. 4 in FIG.
  • FIG. 7 shows a control element of the axial piston machine from FIG. 4 in FIG.
  • Figure 8 shows a circuit diagram of a control of the axial piston machine of Figure 4 with two 2/3-way valves; and FIG. 9 shows the axial piston machine from FIG. 4 with 2/3-way valves integrated in the control element.
  • Axial piston machine 2 exemplified.
  • a swash plate 4 is rotatably mounted about a pivot point 6, wherein the pivot point 6 can intersect a rotation axis 10.
  • an adjusting unit 8 is shown, which is fixedly connected to a housing, not shown here.
  • the swash plate 4 which is perpendicular to the axis of rotation 10 in FIG. 1 and correspondingly assumes an angle of inclination ⁇ of 90 °, is deflected relative to the axis of rotation 10, as can be seen in FIGS. 2 and 3.
  • the adjusting unit 8 with the
  • a drive shaft 12 is rotatably arranged, which is connected in translational and rotational direction fixed to a piston drum 14.
  • first cylinders 16 are arranged parallel to the axis of rotation 10, in which first piston 18 with first piston plates 19 are located.
  • the first piston 18 are with their first sliding shoes 20 on a surface 22 of the swash plate 4.
  • compressive forces can be transmitted.
  • the first pistons 18 slide along a first cylinder wall 30.
  • the first cylinders 16 are arranged circularly and concentrically about the axis of rotation 10. The cylinders are connected to both a high pressure H and a low pressure N.
  • the section through the piston drum 14 is selected in such a way that one of the first cylinders 16 connected to the high-pressure H is shown above the axis of rotation 10. Furthermore, the section through the piston drum 14 is selected such that one of the first cylinders 16 connected to the low pressure N is shown below the axis of rotation 10.
  • One of the surface 22 of the swash plate 4 opposite side 15 of the piston drum 14 is rotatable fluid-tight with a fixedly connected to a housing, not shown here
  • connection plate 34 connected. In the mode of operation of the axial piston machine shown in FIG. 1, the first pistons 18 are not moved relative to one another by a rotation of the drive shaft 12, so that a fluid located in the first cylinders 16 is neither compressed nor relaxed.
  • FIG. 2 shows the axial piston machine 2 from FIG. 1 in pump operation under full load in longitudinal section. It is clearly visible that the swash plate 4 has been deflected by means of the adjusting unit 8 in its maximum position and thus the trapped between the swash plate 4 and the axis of rotation 10
  • Inclination angle ⁇ is considerably greater than 90 °.
  • the oblique axis machine 2 in the present embodiment is operated as an axial piston pump, also called Hydrostat, in a swash plate design. It is clearly visible that the first piston head 19 of the first piston 18 moves between a first bottom dead center 24 and a first top dead center 26.
  • the first displacement 28 is bounded by the first cylinder wall 30, by the first piston head 19, when it is displaced into its first bottom dead center 24, and the first piston head 19, when it is displaced into its first top dead center 26.
  • the drive shaft 12 is driven by a drive unit, not shown.
  • the drive unit can rotate the drive shaft 12.
  • the drive shaft can be rotated speed or torque-controlled fluid is displaced by the in the direction of the swash plate 4 from the first lower 24 to the first top dead center 26 displacing first piston 18 on the
  • FIG. 3 shows the axial piston machine 2 from FIG. 1 under engine operation
  • FIG. 4 shows an axial piston machine 2 of swashplate construction from FIG. 1, in which a piston drum 36 additionally has second cylinders 38, in which second pistons 40 are arranged with a second piston bottom 42.
  • the second cylinders 38 are arranged substantially parallel to the first cylinders 16.
  • the first cylinder 16 are arranged on a first circle 58 having a first diameter 59, wherein a center of the first circle 58 is located on the axis of rotation 10.
  • Concentric with the first circle 58 is a second circle 60 having a second diameter 61 on which the second cylinders 38 are arranged.
  • the second piston 40 are on the surface 22 of the swash plate 4 by means of second sliding shoes 44 such that between the second piston 40 and the swash plate 4 compressive forces can be transmitted.
  • Piston drum 36 is fluid-tight rotatably connected to a fixedly connected to a housing not shown control 56.
  • the first cylinders 16 are connected to both a first high pressure Hl and a first low pressure Nl.
  • the second cylinders 38 are connected both to a second high pressure H2 and to a second low pressure N2.
  • the section through the piston drum 36 is selected such that one of the first cylinders 16 connected to the high-pressure H 1 and the second cylinders 38 connected to the second high-pressure H 2 is shown one above the axis of rotation 10. Furthermore, the section through the
  • Piston drum 14 is selected such that of the first cylinder 16 connected to the low pressure Nl and the second low pressure N2 connected second cylinders 38 each one below the axis of rotation 10 is shown.
  • Opposite side 17 of the piston drum 36 is a piston drum front 17, through which the first 18 and second pistons 40 pass to their respective cylinders 16, 38.
  • FIG. 5 shows the axial piston machine known from FIG.
  • the first cylinder 16 and the second cylinder 38 are each formed as a straight circular cylinder, wherein the first cylinder 16 and the second cylinder 38 the same
  • the second piston 40 has a second piston stroke 54.
  • the piston stroke 54 is determined by a distance by which the second piston head 42 from a second bottom dead center 46 to a second upper one
  • Dead center 48 is shifted.
  • a second displacement 50 is analogous to the first displacement 28 limited by the displaced in the second bottom dead center 46 second piston head 42, displaced by the second top dead center 48 second piston head 42 and a second cylinder 52. It is clearly visible that the first bottom dead center 24 and the second bottom dead center 46 are on a common line. This is, however, coincidental in the swiveling out of the swashplate 4 shown here. Furthermore, it can be seen that the second piston stroke 54 is greater than the first piston stroke 32, since the second cylinders 38 are farther away from their axis of rotation 10 than the first cylinders 16. Thus, the second displacement 50 is greater than the first displacement 28.
  • this arrangement in this arrangement in this arrangement in
  • FIG. 6 shows one of the swash plate 4 opposite
  • the first 16 and second cylinder 38 are each shown hatched.
  • the first circle 58 with the first diameter 59 the first cylinder 16 are arranged uniformly distributed.
  • the number of first cylinders arranged here 16 is seven.
  • the second circle 60 with the second diameter 61 nine second cylinders 38 are uniformly distributed over the second circle 60.
  • the second number of second cylinders 38 is greater than the first number of first cylinders 16. Of course, the number may be the same.
  • the second diameter 61 is larger than the first diameter 59.
  • the axis of rotation 10 occurs at the intersection S through the piston drum front
  • the first cylinders 16 extend around a first central axis 62, which intersects the piston drum front 17 in the first center Ml.
  • the second cylinders 38 extend around a second center axis 64 which intersects the piston drum front 17 in the second center M2.
  • a first half-line 70 is shown.
  • a second half-line 72 is shown.
  • the two half-lines 70, 72 span a plane which is perpendicular to the axis of rotation 10.
  • Half-line 72 is an angle ß included.
  • the angle ⁇ is here not equal to 0 °.
  • FIG. 7 shows the control element 56 of the axial piston machine 2 from FIG. 4 in a plan view.
  • the control element 56 is divided into upper and lower halves, a first high-pressure Hl and a second high-pressure H2 being provided in the upper half, and a first low-pressure Nl and a second low-pressure N2 being provided in the lower half.
  • a first compressed fluid is supplied by the first high-pressure side Hl by means of a first input region 74 to the first cylinders 16 in engine operation or taken in pump operation.
  • the first input region 74 is formed as a circular or kidney-shaped recess in the control 56. This also applies to a first exit region 76.
  • a first relaxed fluid is passed through the first low-pressure pressure side Nl by means of the first exit region
  • the first input region 74 and the first output region 76 are arranged on a third circle 73 with a third diameter 75, wherein the high pressure side Hl from the low pressure side Nl and the first
  • Entrance area 74 from the first exit area 76 through a web 81st is separated and the third diameter 75 corresponds approximately to the first diameter 59.
  • a second compressed fluid is supplied through the second high-pressure side H2 by means of a second input region 78 to the second cylinders 38 during engine operation or removed during pump operation.
  • the second input portion 78 is referred to as an annular or kidney-shaped recess in the
  • Control 56 is formed. This also applies to a second
  • a second relaxed fluid is the second through the second low-pressure side N2 by means of the second output region 80
  • Cylinders 38 removed during engine operation or supplied in pump mode.
  • the second input region 78 and the second output region 80 are arranged on a fourth circle 77 with a fourth diameter 79, wherein the second high-pressure side H2 is separated from the second low-pressure side N2 and the second input region 78 is separated from the second output region 80 by a web 81 and the fourth diameter 79 corresponds approximately to the second diameter 61.
  • the third diameter 75 is smaller than the fourth diameter 79.
  • the third diameter 75 correspond to the first diameter 59 and the fourth diameter 79 to the second
  • Diameter 61 In the present embodiment, the
  • Areas 74, 76, 78, 80 each have a width B, which are the same in the embodiment shown here.
  • the widths B of the respective regions 74, 76, 78, 80 may be changed relative to each other.
  • the widths B of the two input regions 74, 78 and / or the widths B of the two output regions 76, 80 may be different from one another. Also, in the
  • Entrance areas 74, 78 and the output areas 76, 80 additionally webs, for example, be arranged for stiffening.
  • FIG. 8 shows a circuit diagram of a control of the axial piston machine 2 from FIG. 4 with two 3/2-way solenoid valves 82, 88.
  • This circuit diagram is equally valid for an axial piston motor and a swash plate type axial piston pump.
  • the axial piston machine 2 is operated in the partial load range.
  • the first solenoid valves 82 are energized and the second solenoid valve 88 shown energized.
  • both are both of the axial piston machine 2 is not operated, both are
  • Solenoid valves 82, 88 de-energized and take a switching position like that Solenoid valve 82.
  • the first solenoid valve 82 consists of a first
  • the second solenoid valve 88 consists of a second valve chamber 92 and a fourth valve chamber 96.
  • a connected to the solenoid valve 82, 88 coil 86 is against a spring force of a spring 84, the solenoid valve 82, 88 of a first switching position, as shown in solenoid valve 82, in which a third valve chamber 94 is pressurized, displaced to a second switching position, as shown in solenoid valve 88, in which a second valve chamber 92 is pressurized.
  • Solenoid valve 88 or both be energized. Now, as shown here, the second solenoid valve 88 is energized and the first solenoid valve 82 is energized, the second high pressure H2 from the second input portion 78 of the high pressure side H is supplied by means of the second solenoid valve 88.
  • the second output region 80 of the second low-pressure side N2 is provided with a
  • the first cylinders 16 are operated in a short-circuit operation in that the first solenoid valve 82 connects the high-pressure side H 1, that is, the first input region 74, to the low-pressure N.
  • Axial piston machine to operate in a part load range with a better efficiency Axial piston machine to operate in a part load range with a better efficiency.
  • FIG. 9 shows an arrangement in which the first 3/2-way solenoid valve 82 and the second 3/2-way solenoid valve 88 are integrated in the control element 56. This requires only one high pressure H port and one low pressure N port.
  • FIG. 9 shows that already known from FIG. 9
  • Axial piston machine 2 in swash plate design Axial piston machine 2 in swash plate design.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à piston axial dans un mode de construction à disque incliné présentant un tambour (14, 36) de piston, le tambour (14, 36) de piston étant relié sans pouvoir tourner à un arbre d'entraînement (12) rotatif autour d'un axe de rotation (10). Le tambour (14, 36) de piston présente une pluralité de premiers cylindres (16) disposés de manière sensiblement parallèle à l'axe de rotation (10). Les premiers cylindres (16) sont disposés sur un premier cercle (58) présentant un premier diamètre (59). Dans chaque premier cylindre (16) est disposé un premier piston (18), déplaçable entre un premier point mort (24) inférieur et un deuxième point mort (26) supérieur, le long d'une première direction de translation. Chaque premier piston (18) peut être couplé, de manière apte à un transfert de pression le long de la première direction de translation, à un disque incliné (4) disposé de manière articulée et à inclinaison réglable par rapport à l'axe de rotation (4). Selon l'invention, le tambour (36) de piston présente une pluralité de deuxièmes cylindres (38) disposés de manière sensiblement parallèle à l'axe de rotation (10). Les deuxièmes cylindres (38) sont disposés sur un deuxième cercle (60) présentant un deuxième diamètre (61). Chaque deuxième cylindre (38) est muni d'un deuxième piston (40) déplaçable entre un deuxième point mort (46) inférieur et un deuxième point mort (48) supérieur le long d'une deuxième direction de translation. Chaque deuxième piston (40) peut être couplé de manière apte à un transfert de pression le long de la deuxième direction de translation au disque incliné (4). Le premier diamètre (59) est différent du deuxième diamètre (61).
PCT/EP2012/059682 2011-06-09 2012-05-24 Machine à piston axial dans un mode de construction à disque incliné WO2012168083A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110077253 DE102011077253A1 (de) 2011-06-09 2011-06-09 Axialkolbenmaschine in Schrägscheibenbauweise
DE102011077253.7 2011-06-09

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WO2012168083A2 true WO2012168083A2 (fr) 2012-12-13
WO2012168083A3 WO2012168083A3 (fr) 2013-08-15

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CN106837728A (zh) * 2017-02-21 2017-06-13 哈尔滨工业大学 一种多排式斜轴轴向柱塞泵

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1343916A (fr) * 1962-11-23 1963-11-22 Maschfab Eisengiesserei Beien Perfectionnements apportés aux pompes hydrauliques à pistons
DE3026765A1 (de) * 1980-07-15 1982-02-11 Linde Ag, 6200 Wiesbaden Axialkolbenpumpe fuer zwei foerderstroeme
JP3724929B2 (ja) * 1997-09-11 2005-12-07 本田技研工業株式会社 斜板式油圧装置
JP2003214101A (ja) * 2002-01-21 2003-07-30 Honda Motor Co Ltd 回転式流体機械
US7029241B2 (en) * 2002-04-26 2006-04-18 Patrick Wade Rousset Circumferential piston compressor/pump/engine (CPC/CPP/CPE); circumferential piston machines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113358277A (zh) * 2021-05-31 2021-09-07 常州工学院 一种高频气压波传感器检测装置
CN113358277B (zh) * 2021-05-31 2022-12-09 常州工学院 一种高频气压波传感器检测装置

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