WO2012076097A1 - Machine à pistons - Google Patents

Machine à pistons Download PDF

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Publication number
WO2012076097A1
WO2012076097A1 PCT/EP2011/005669 EP2011005669W WO2012076097A1 WO 2012076097 A1 WO2012076097 A1 WO 2012076097A1 EP 2011005669 W EP2011005669 W EP 2011005669W WO 2012076097 A1 WO2012076097 A1 WO 2012076097A1
Authority
WO
WIPO (PCT)
Prior art keywords
pivoting
piston
piston engine
cylinder
drive shaft
Prior art date
Application number
PCT/EP2011/005669
Other languages
German (de)
English (en)
Inventor
Michael Gaumnitz
Heino Foersterling
Karsten Mischker
David Breuer
Alexander Mark
Joerg Dantlgraber
Udo Buedel
Marcus Herrmann
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 WO2012076097A1 publication Critical patent/WO2012076097A1/fr

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Classifications

    • 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
    • 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
    • F04B1/22—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 having two or more sets of cylinders or pistons
    • F04B1/24—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 having two or more sets of cylinders or pistons inclined to the main shaft axis
    • 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
    • F04B1/328—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 axis of the cylinder barrel relative to the swash plate

Definitions

  • the invention relates to a piston engine according to the preamble of
  • Axial piston engines with several cylinder-piston units are known from the prior art, in which an oblique position of a component coupled to the cylinders relative to a component of the axial piston engine coupled to the pistons is required to produce a stroke of the pistons in the respective cylinders. Furthermore, the cylinder-piston units must rotate (relative to a housing).
  • axial piston machines are known according to the oblique axle principle, in which the pistons are coupled to a disk of a shaft, while the cylinders are formed in a cylinder drum inclined with respect to the shaft. Since the cylinder drum rotates synchronously with the shaft during operation of the axial piston machine, the pistons rotate accordingly.
  • axial piston machines are known according to the swash plate principle, in which the pistons are coupled to a swash plate, which is inclined with respect to a shaft.
  • the cylinders are formed in a cylindrical drum which is concentric with the shaft.
  • the cylinder drum and the pistons rotate synchronously with the shaft during operation of the axial piston machine. Because of the necessary relative movement of the pistons relative to the swash plate, feet of the pistons are received in piston shoes that slide over the swash plate.
  • EP 1 705 372 A1 shows a further piston engine in a floating-cup technology (FCT), which has two groups of cylinder-piston units.
  • FCT floating-cup technology
  • Cylinders in the form of sleeves are supported via a drum disc on a respective pivoting cradle, while the pistons are fixed to a common drum or disc.
  • the disc is concentric with the shaft and rotatably mounted on the shaft. Since the disc with the piston rotates synchronously with the shaft during operation of the piston engine, the cylinder sleeves accordingly revolve.
  • Schwenkwiegen are kidney-shaped control slots. To seal these control slots to the interior of the machine housing down the drum discs are necessary, which have individual matched to the cylinder sleeves and stroking the control slots breakthroughs and rotate with the cylinder-piston units.
  • the pivoting balances are designed to be adjustable in their angle, so that the stroke of the cylinder-piston units and thus the flow rate of the machine can be changed.
  • a disadvantage of such piston engines of the latter type with two groups of cylinder-piston units is that the control of a volume flow, as required for example for the realization of hydraulic control circuits, requires an increased effort.
  • the invention is based on the object to provide a piston engine in a floating Cup or Tilting Cup Technology (FCT or TCT) with two groups of cylinder-piston units, with which hydraulic control circuits are realized with less effort can.
  • FCT or TCT floating Cup Technology
  • the hydrostatic piston engine according to the invention has a first and a second group of cylinder sleeve-piston units.
  • the pistons are - preferably via a common disc - coupled to a drive shaft and run with this.
  • the cylinders are formed by cylinder sleeves.
  • the stroke between the cylinder sleeves and the piston of the first group depends on the position of a first adjustable pivoting cradle and the stroke between the cylinder sleeves and the piston of the second group from the position of a second adjustable pivoting cradle.
  • the both pivoting swivels or their swivel angle are - preferably mechanically, hydraulically, pneumatically or electrically - coupled to each other and in their
  • Adjustment synchronized, so aligned in path and time This creates a piston machine of the FCT or TCT type with two groups of cylinder-piston units with which hydraulic control circuits can be realized.
  • the two groups of cylinder-piston units, the two pivoting pivots are arranged substantially mirror-inverted to a plane perpendicular to the drive shaft central plane of the piston engine.
  • a pin or bolt is attached to the two pivoting pivots directly or via a respective connecting element, for example via a lever arm.
  • the two pins or bolts are guided in a running approximately parallel to the drive shaft common backdrop, and a distance of the gate to the drive shaft is adjustable in particular via a control cylinder. Then, the synchronous adjustment can be done mechanically by a linear adjustment.
  • a spindle nut is coupled to the two pivoting pivots each directly or via a connecting element, for example a lever arm, wherein the two spindle nuts are coupled via a spindle extending approximately parallel to the drive shaft.
  • a connecting element for example a lever arm
  • the synchronous adjustment can be done mechanically by a rotational adjustment.
  • a gear segment is attached to the two pivoting pivots each directly or via a connecting element, for example via a lever arm, wherein the two gear segments mesh with each other.
  • a first linear actuator is coupled to the first pivoting cradle directly or via a connecting element, for example a lever arm
  • a second linear actuator is coupled to the second pivoting cradle directly or via a connecting element, for example a lever arm.
  • the two linear actuators can be electric linear motors, piezo actuators, pneumatic actuators or hydraulic actuators.
  • the first linear actuator may be a first actuating cylinder, while the second linear actuator is a second actuating cylinder. This creates a hydraulic adjustment device.
  • the hydraulic flow divider is formed by two constant-displacement pumps, of which the two adjusting cylinders can be supplied, and when the two constant-displacement pumps are coupled to one another via a connecting shaft. Then, the synchronous adjustment can be done hydraulically by a rotational adjustment movement of the connecting shaft.
  • the connecting shaft can serve as a common drive shaft.
  • Stepped cylinder is formed with stepped piston, of which the two adjusting cylinders are supplied.
  • An annular space and a cylindrical space of the stepped cylinder are each connected to one of the two actuating cylinders.
  • An annular space bounding the annular space of the stepped piston and a cylindrical space defining end face of the stepped piston are the same size. Then, the synchronous adjustment can be done hydraulically by a linear adjustment movement of the stepped piston.
  • a control valve whose respective actuator is connected by a common electronic control unit as a function of a respective one, can be connected upstream of the two positioning cylinders Displacement sensor is adjustable.
  • the two displacement sensors are coupled to a respective actuating piston of the actuating cylinder. This also allows an asynchronous adjustment of the piston engine or the stroke of its two cylinder-piston units.
  • first pivoting cradle - preferably via an additional first lever arm - a first additional actuating cylinder is articulated to a first actuating cylinder opposite side of the drive shaft, while corresponding to the second pivoting cradle - preferably via an additional second lever arm - a second additional actuating cylinder is articulated on a second actuating cylinder opposite side of the drive shaft.
  • the effective directions of the respective actuating cylinder and the respective additional actuating cylinder are directed in a same pivoting direction of the corresponding pivoting cradle.
  • the first actuating cylinder and the first additional actuating cylinder can be supplied via a first line pair from a common first pump, wherein the second actuating cylinder and the second additional actuating cylinder can be supplied via a second line pair from a common second pump.
  • the two pumps are coupled to one another via a connecting shaft.
  • each pivoting cradle is pivoted via an introduction of a pair of forces, which leads in particular to the high-pressure side pivot bearing for a reduction in the losses due to leakage.
  • the connecting shaft can serve as a common drive shaft.
  • a first flow divider can be arranged in the first line pair, while a second flow divider is arranged in the second line pair.
  • the first pivoting cradle via a first rotary actuator and the second pivoting cradle is pivotable via a second rotary actuator.
  • the two rotary actuators are coupled to each other.
  • the actuators can be designed electrically, piezoelectrically, pneumatically or hydraulically.
  • the first rotary actuator is a first hydraulic swing-wing motor and the second rotary actuator is a second hydraulic swing-wing motor.
  • the two swing-wing motors each have a working line acting in the direction of increasing the pivoting angle and a working line acting in the direction of reducing the pivoting angle
  • the coupling of the swivel-weighing adjustment according to the invention can take place via two flow dividers.
  • the one flow divider is connected to the two acting in the direction of enlargement of the pivot angle working lines and the other flow divider with the two acting in the direction of a reduction of the pivot angle working lines.
  • the two flow dividers are each two pumps coupled to each other via a connecting shaft.
  • the inventive coupling of the two SchenkWiegen can also be done via a drive shaft obliquely employed coupling rod, which is hinged to the first pivoting cradle via a first joint and on the second pivoting cradle via a second joint.
  • the two joints are each articulated on different sides of the drive shaft to the respective pivoting cradle. It can be additionally provided a second coupling rod for generating a symmetry and as a gain.
  • the inventive coupling of the two Schenkwiegen can also be done via two obliquely stretched and crossed on the drive shaft and crossed pliable traction means, which are each attached to the first pivoting cradle at a first attachment point and the second pivoting cradle at a second attachment point.
  • the two attachment points of the two traction means are attached to different sides of the drive shaft to the respective pivoting cradle.
  • the two pivoting pivots can also be arranged approximately parallel to one another and coupled to one another via a coupling rod arranged essentially parallel to the drive shaft.
  • Figure 1 shows a first embodiment of the piston engine according to the invention in a schematic side view
  • Figure 2 shows a second embodiment of the piston engine according to the invention in a schematic side view
  • Figure 3 shows a third embodiment of the piston engine according to the invention in a schematic side view
  • Figure 4 shows a fourth embodiment of the piston engine according to the invention in a schematic side view
  • Figure 5 shows a fifth embodiment of the piston engine according to the invention in a schematic side view
  • Figure 6 shows a sixth embodiment of the piston engine according to the invention in a schematic side view
  • Figure 7 shows a seventh embodiment of the piston engine according to the invention in a schematic side view
  • FIG. 8 shows an eighth embodiment of the piston pump according to the invention in a schematic side view
  • 9 shows a ninth embodiment of the piston engine according to the invention in a schematic side view
  • Figure 10 shows a tenth embodiment of the piston engine according to the invention in a schematic side view
  • Figure 11 shows an eleventh embodiment of the piston engine according to the invention in a schematic side view.
  • Figure 1 shows a first embodiment of the piston engine according to the invention in a schematic side view.
  • the piston machine has a continuous drive shaft, of which only two end sections 1a, 1b are shown in FIG. 1, which are each mounted via a roller bearing 2a, 2b.
  • the pivoting pivots 4a, 4b with the swash plates 6a, 6b and the cylinder sleeves 8a coupled thereto are arranged in mirror image with respect to a central plane 10 and obliquely with respect to the drive shaft of the piston engine.
  • the middle plane 10 is perpendicular to the drive shaft and is shown in Figure 1 in a "cut" representation as a dashed line.
  • a disc (not shown in FIG. 1) is arranged non-rotatably connected to the drive shaft (compare disc 742 from FIG.
  • a plurality of pistons are fastened, of which only one piston 12a is shown by way of example in FIG.
  • the piston machine according to the invention is used as a pump, it is driven on one of the end sections 1a, 1b of the drive shaft.
  • the pistons 12 a are taken in an orbit around the drive shaft and in turn take the cylinder sleeves 8 a with. Due to the inclination of the two swash plates 6a, 6b, the cylinder sleeves 8a perform a lifting movement relative to the respective piston 12a.
  • each pivot cradle 4a, 4b two approximately kidney-shaped slots are provided, one of which with a high-pressure channel HDa, HDb and the other with a low-pressure channel NDa, NDb are connected.
  • the two high-pressure channels HDa, HDb lead to a common (not shown) high-pressure port of the piston engine, while the two low-pressure channels NDa, NDb are connected to a common (not shown) low-pressure port of the piston engine.
  • the two high-pressure channels HDa and HDb can also remain separate and serve the pressure medium supply of each other hydraulic consumers. The same applies to the low-pressure channels.
  • a mechanical coupling is provided, which is driven by a Differenziaizylinder 14.
  • a pin 18a, 18b is attached.
  • the two pins 18a, 18b also extend mirror-symmetrically to the central plane 10 and perpendicular to the plane of the drawing.
  • a straight gate 20 which extends approximately parallel to the drive shaft on both sides of the central plane 10 and mirror-symmetrical to this.
  • the gate 20 is according to the arrow on the Differenziaizylinder 14 in the direction perpendicular to the drive shaft movable.
  • the two pins 18a, 18b either move towards or away from each other and thus move over the respective lever arm 16a, 16b and via the respective pivoting cradle 4a, 4b, the two swash plates 6a, 6b synchronously.
  • Figure 2 shows a second embodiment of a piston engine according to the invention in a schematic side view.
  • the drive shaft with the two end sections 1a, 1b and the two roller bearings 2a, 2b and the two pivoting jaws 4a, 4b with the two swash plates 6a, 6b and with the two drum discs 7a, 7b and the four channels HDa, HDb, NDa
  • the second embodiment also has two groups of cylinder-piston units, of which only one cylinder-piston unit 8a, 12a is shown by way of example in FIG.
  • the adjusting device of the second exemplary embodiment has two lever arms 116a, 116b fastened to the respective pivoting cradle 4a, 4b which extend upward from a respective axis of rotation 119a, 119b (in FIG. 2) and are arranged mirror-symmetrically with respect to the central plane 10. From the respective
  • Swivel cradle 4a, 4b remote end portions of the two lever arms 116a, 116b are rotatably connected to a respective spindle nut 118a, 118b.
  • the two spindle nuts 118a, 118b are arranged on a common spindle 120, which is fixed axially by means of suitable mounting.
  • the spindle 120 extends approximately parallel to the drive shaft and can be rotated by an electric motor 114 in both directions in rotation. By opposing threaded portions on the spindle 120 in the areas of the respective spindle nut 118a, 118b, these are moved by a rotation of the spindle 120 either towards or away from each other.
  • the coupling according to the invention is the setting of the two
  • Figure 3 shows a third embodiment of the piston engine according to the invention in a schematic side view. The correspond
  • the third embodiment also has two groups of cylinder-piston units, of which only one cylinder-piston unit 8a, 12a is shown by way of example in FIG.
  • a gear segment 218a, 218b is arranged in each case.
  • the two gear segments 218a, 218b are arranged mirror-symmetrically with respect to the middle plane 10 and mesh with each other. This results in a mechanical coupling of the two swash plates 6a, 6b, wherein the swivel angle of the two swash plates 6a, 6b can be adjusted by an adjustment device (not shown).
  • Figure 4 shows a fourth embodiment of the piston engine according to the invention in a schematic side view.
  • the drive shaft with the two end sections 1a, 1b and the two roller bearings 2a, 2b, the two pivoting jaws 4a, 4b with the two swash plates 6a, 6b and the two drum discs 7a, 7b, the four channels HDa, HDb, NDa, NDb those of the first embodiment of Figure 1.
  • the fourth embodiment also has two groups of cylinder-piston units, of which in Figure 1, only a cylinder-piston unit 8a, 12a is shown by way of example.
  • a coupling rod 320 is provided according to the fourth embodiment, which is coupled via a first joint 318a to the first pivot cradle 4a and a second hinge 318b to the second pivot cradle 4b.
  • the coupling rod 320 extends obliquely to the drive shaft and obliquely to the central plane 10.
  • the first joint 318a is disposed in a region of the first pivoting cradle 4a, which has comparatively large distance to a relative to the central plane 10 mirror image region of the second pivoting cradle 4b, while the second joint 318b is disposed at a portion of the second pivot cradle 4b, which has a comparatively small distance to a relative to the central plane 10 mirror image region of the first pivot cradle 4a.
  • the two joints 318a, 318b are arranged on different sides of the two pivoting jaws 4a, 4b with respect to the drive shaft.
  • the coupling rod 320 or one of the two pivoting jaws 4a, 4b is moved by means of an adjustment device (not shown), wherein the two swash plates of FIGS. 6a, 6b are mechanically synchronized.
  • Figure 5 shows a fifth embodiment of the piston engine according to the invention in a schematic side view. The correspond
  • the two lever arms 116a, 116b are correspondingly attached to the pivoting jaws 4a, 4b, which extend upward (in FIG. 5) from the respective rotation axis 119a, 119b and thereby mirror-symmetrically to the middle level 10 are arranged.
  • the end portions of the lever arms 116a, 116b facing away from the respective pivoting cradle 4a, 4b are connected via a respective rotary sliding joint to a piston rod of a respective adjusting cylinder 422a, 422b.
  • the directions of action of the two actuating cylinders 422a, 422b are directed parallel to the drive shaft to the outside, whereby by such a movement, the pivot angle of the two swash plates 6a, 6b are increased.
  • return springs are provided to reset the actuating cylinder 422a, 422b and thus to reduce the pivot angle of the two swash plates 6a, 6b.
  • each control cylinder 422a, 422b is assigned a constant-displacement pump 424a, 424b via which the respective actuating cylinder 422a, 422b can be supplied with pressure medium.
  • the two constant-displacement pumps 424a, 424b have a connecting shaft 426, via which their two delivery volumes and thus the adjustment paths of the two adjusting cylinders 422a, 422b are hydraulically synchronized.
  • FIG. 6 shows a sixth embodiment of the piston engine according to the invention in a schematic side view.
  • the sixth embodiment largely corresponds to the fifth embodiment according to FIG. 5. Therefore In the following, only the difference of the sixth embodiment compared to the fifth embodiment is explained:
  • an annular space 532 and a cylindrical space 534 are formed, an annular space 532 bounding annular surface of the stepped piston 530 and a cylindrical space 534 defining end face of the stepped piston 530 are equal.
  • the annulus 532 of the step cylinder 528 is connected to the first actuator cylinder 422a, while the cylindrical space 534 of the step cylinder 528 is connected to the second actuator cylinder 422b.
  • Figure 7 shows a seventh embodiment of the erfindunin piston engine in a schematic side view.
  • the seventh exemplary embodiment largely corresponds to the fifth exemplary embodiment according to FIG. 5 and the sixth exemplary embodiment according to FIG. 6, so that only the differences from the fifth and the sixth exemplary embodiment are explained below:
  • the two actuating cylinders 422a, 422b are connected via a respective 3/2-way valve , which serves as a control valve 636a, 636b, either connected to high pressure P or relieved to low pressure T.
  • the two adjusting cylinders 422a, 422b With a connection of the two control valves 636a, 636b with high pressure, the two adjusting cylinders 422a, 422b are moved outwards, whereby the pivoting angle of the two swash plates 6a, 6b are increased.
  • the positions of the two piston rods of the adjusting cylinders 422a, 422b are detected by a respective displacement sensor 638a, 638b and transmitted to a control unit 640. From the control unit 640, the control valves 636a, 636b are set via respective actuators.
  • the inventive coupling of the adjustment of the two swash plates 6a, 6b takes place in the seventh embodiment in the form of an electro-hydraulic control of the adjustment.
  • Figure 8 shows an eighth embodiment of the piston pump according to the invention in a schematic representation.
  • a concentric disc 742 is arranged perpendicular to the drive shaft 1.
  • pistons 742 are distributed on both opposite sides of the disk, of which only one piston 12a, 12b is shown by way of example in FIG. 8. These immerse each in a cylinder sleeve 8a, 8b.
  • the cylinder sleeves 8a of the first group of cylinder-piston units 8a, 12a are coupled via the first drum disk 7a to the first swash plate 6a, while correspondingly the cylinder sleeves 8b of the second group of cylinder-piston units 8b, 12b via the second drum disk 7b are coupled to the second swash plate 6b.
  • the two swash plates 6a, 6b are in normal operation obliquely to the drive shaft 1 and the disc 742.
  • the disc 742 and thus indirectly also the drive shaft 1 via two radial bearings 744a, 744b supported on a (not shown) housing of the piston engine.
  • the two swash plates 6a, 6b are aligned approximately parallel to one another via their respective pivoting cradles 704a, 704b.
  • This parallel position is maintained even with a pivoting of the two swash plates 6a, 6b, wherein the synchronization according to the invention of the pivoting takes place mechanically in this embodiment.
  • a coupling rod 720 is provided which extends approximately parallel to the drive shaft 1.
  • the coupling rod 720 is pivotally connected via approximately perpendicular to the drive shaft 1 extending connecting portions 721a, 721 b with the two pivoting rockers 704a, 704b.
  • FIG. 9 shows a ninth embodiment of the piston engine according to the invention in a schematic side view.
  • the drive shaft 1 with the two end sections 1a, 1b and with the two rolling bearings 2a, 2b, the two pivoting pivots 4a, 4b with the swash plates 6a, 6b and with the (not shown in Figure 9) pulleys 7a, 7b and the four Channels HDa, HDb, NDa, NDb those of the first embodiment shown in FIG 1.
  • the respective pivot angle of the two swash plates 6a, 6b is at each
  • Pivoting cradle 4a, 4b arranged a swing-wing motor 846a, 846b.
  • the two swing-wing motors 846a, 846b can each be driven in two directions, whereby a reduction or enlargement of the respective
  • Swivel angle and thus the intake or delivery volume of the piston engine according to the invention is adjustable.
  • Two displacement machines (constant displacement pumps / motors or also flow divider) 424a, 424b, whose delivery volume flows via a connecting shaft 426th
  • Connecting shaft 826 are equalized, supply the two swing-wing motors 846a, 846b with pressure medium, which supply leads to a pivoting back of the swash plates 6a, 6b.
  • FIG. 10 shows a tenth embodiment of the invention
  • Piston engine in a lateral schematic representation.
  • This embodiment has all the components of the fifth embodiment according to Figure 5, so that only the components beyond it are explained below:
  • an additional lever arm 917a, 917b attached to which a corresponding additional actuating cylinder 923a, 923b is articulated.
  • the two additional lever arms 917a, 917b, the two additional actuating cylinders 923a, 923b and their return springs are identical to those of the fifth embodiment according to FIG 5.
  • the additional actuating cylinder 923a, 923b and their return springs are aligned parallel to the drive shaft 1.
  • the two additional lever arms 917a, 917b and the two additional actuating cylinders 923a, 923b are arranged with respect to the drive shaft 1 with respect to the two lever arms 116a, 116b or with respect to the two actuating cylinders 422a, 422b.
  • the two additional actuating cylinders 923a, 923b are in the same way with pressure medium from the respective associated displacement machines
  • Constant pumps / motors or power divider supplies, as the two actuating cylinders 422 a, 422 b and also act in the direction of increasing the pivot angle of the piston engine.
  • Figure 11 shows an eleventh embodiment of the piston engine according to the invention in a lateral schematic representation. Since the eleventh embodiment largely corresponds to the tenth embodiment, only the differences from the tenth embodiment shown in FIG. 10 will be explained below.
  • a first flow divider 1050a, 1052a is arranged to make the torque introduction uniform.
  • a flow divider 1050b, 1052b is also arranged between the second constant-displacement pump 424b and the two second actuating cylinders 422b, 923b supplied by it.
  • the two displacement machines 424a and 424b work here primarily as fixed displacement pumps, which is why they are also referred to above.
  • the two current dividers each consist of two constant-speed motors 1050a, 1050b, which are mechanically coupled to one another via a respective connecting shaft 1052a, 1052b.
  • the connecting shafts 426, 826 of the exemplary embodiments according to FIGS. 9, 10 and 11 can also be used to drive the two fixed-displacement pumps 424a, 424b or 824a, 824b coupled thereto.
  • a hydrostatic piston engine having a first and a second group of cylinder-piston units.
  • the pistons are - preferably via a common disc - coupled to a drive shaft and run with this.
  • the Cylinders of the first group are coupled to a first swash plate while the cylinders of the second group are coupled to a second swash plate.
  • the first oblique disk is pivotable via a first pivoting cradle and the second inclined disk correspondingly via a second pivoting cradle.
  • the two pivoting pivots or their pivoting angles are - preferably mechanically, hydraulically, pneumatically or electrically - coupled to each other and synchronized.

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

Abstract

L'invention concerne une machine à pistons hydrostatique comprenant un premier et un second groupe d'ensembles cylindre-piston. Les pistons sont reliés à un arbre d'entraînement, de préférence par l'intermédiaire d'un plateau commun, et sont entraînés en rotation par ledit arbre. La course entre les cylindres et les pistons du premier groupe dépend de la position d'un support basculant réglable et la course entre les cylindres et les pistons du second groupe de la position d'un second support de pivotement réglable. Les deux supports de pivotement, à savoir leur angle de pivotement, sont de préférence couplés par une liaison mécanique, hydraulique, pneumatique ou électrique, leur réglage commun étant synchronisé.
PCT/EP2011/005669 2010-12-08 2011-11-11 Machine à pistons WO2012076097A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010053804 DE102010053804A1 (de) 2010-12-08 2010-12-08 Kolbenmaschine
DE102010053804.3 2010-12-08

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WO2012076097A1 true WO2012076097A1 (fr) 2012-06-14

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CN113107812B (zh) * 2021-04-30 2022-08-30 重庆市南川区金鑫纸业有限公司 造纸用真空系统脱水装置

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