EP1671032A1 - Machine a piston hydrostatique munie de deux circuits hydrauliques - Google Patents

Machine a piston hydrostatique munie de deux circuits hydrauliques

Info

Publication number
EP1671032A1
EP1671032A1 EP04790263A EP04790263A EP1671032A1 EP 1671032 A1 EP1671032 A1 EP 1671032A1 EP 04790263 A EP04790263 A EP 04790263A EP 04790263 A EP04790263 A EP 04790263A EP 1671032 A1 EP1671032 A1 EP 1671032A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
group
cylinder drum
piston machine
cylinder bores
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP04790263A
Other languages
German (de)
English (en)
Other versions
EP1671032B1 (fr
Inventor
Günter Wanschura
Jürgen GINTNER
Jerzy Kreja
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1671032A1 publication Critical patent/EP1671032A1/fr
Application granted granted Critical
Publication of EP1671032B1 publication Critical patent/EP1671032B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • F04B1/2042—Valves

Definitions

  • the invention relates to a hydrostatic piston machine for simultaneous operation in a first and a second hydraulic circuit.
  • the hydrostatic piston machine comprises a cylinder drum, into which a first group of cylinder bores is made, which can be connected to a first hydraulic circuit. Furthermore, a second group of cylinder bores is made in the cylinder drum, which can be connected to a second hydraulic circuit.
  • the cylinder bores of the first and the second group are made in the cylinder drum on a common pitch circle. The outer diameter of the cylinder drum is not increased by a radial offset between the cylinder bores of the first group and the second group.
  • the minimum diameter on which the cylinder bores are arranged is determined exclusively by the required delivery volume and the maximum feasible setting angle of a swivel plate.
  • all the pistons which are arranged in the cylinder bores of the first group and the second group coexist support only a uniform distance from the cylinder drum axis on the swivel plate, which results in a more uniform load and improved vibration behavior.
  • the subclaims relate to advantageous developments of the hydrostatic piston machine according to the invention.
  • the cylinder bores of the first group are connected to the first hydraulic circuit by first connecting channels, the first connecting channels being separated from second connecting channels by the opening on the
  • the assignment of the individual cylinder bores of the first group is thus carried out by a first connecting channel, which is at a first distance from the cylinder drum axis on the
  • a control plate is provided in which at least one first control kidney and a second one
  • Control kidneys are arranged, the first and second control kidneys each extending along an arc of a circle.
  • the radius of the respective circular arc corresponds to the distance from the cylinder drum axis in which the first connecting channels or the second
  • a further control kidney is preferably assigned to each of the first and second hydraulic circuits. So the first hydraulic circuit and the second hydraulic circuit completely separate from each other and each have a separate pressure or suction connection.
  • the third control kidney required for this in turn extends along an arc of a circle whose radius corresponds to the radius of the arc of a circle along which the first control kidney extends. Accordingly, the fourth control kidney extends along an arc corresponding to the second control kidney.
  • the control plate In order to center the cylinder drum and to form a hydrodynamic plain bearing on the end face of the cylinder drum, the control plate is spherically shaped on the side facing the cylinder drum.
  • the spherical shape corresponds to a spherical recess made in the end face of the cylinder drum. With the spherical recess, the cylinder drum lies against the spherical shape of the control plate, as a result of which the cylinder drum is centered.
  • a defined leakage flow is generated from the mouths of the connecting channels, as a result of which a hydrodynamic plain bearing is formed between the contact surfaces of the control plate and the cylinder drum.
  • both the first connecting channels and the second connecting channels extend parallel to the cylinder drum axis. So that the connecting channels z. B. be introduced by milling in a particularly simple manner in the cylinder drum without having to reclamp the workpiece or having to change the infeed angle of the tool.
  • connection channels are introduced into the cylinder drum with a radial directional component, it is particularly advantageous if those connection channels which open out at the shorter distance from the longitudinal axis of the cylinder drum on the end face of the cylinder drum point towards the mouth Cylinder drum axis are oriented. Together with the spherical depression on the end face of the cylinder drum, this results in an exit angle of approximately a right angle. This not only simplifies production, but also leads to increased durability of the piston machine.
  • Another advantage with regard to the pulsation of the hydrostatic piston machine results if the number of cylinder bores of the first and the second group is identical. It is particularly advantageous if both the number of cylinder bores in the first group and the number of cylinder bores in the second group is an odd number.
  • the cylinder bores of the first group and the second group are arranged alternately along the common pitch circle.
  • a particularly versatile hydrostatic piston machine is obtained when the pistons, which are arranged in the cylinder bores of the first and the second group, are supported on a common swivel plate, so that at a right angle of the swivel plate with respect to the cylinder drum axis, the stroke of all pistons is zero and the swivel plate can pivot from this position in both directions.
  • FIG. 1 is a hydraulic circuit diagram of a hydrostatic piston machine according to the invention
  • FIG. 3 shows an enlarged illustration of a section of the longitudinal section of the hydrostatic piston machine according to the invention
  • FIG. 5 is a sectional view of a cylinder drum of the hydrostatic piston machine according to the invention.
  • 7 is a first view of the end face of the cylinder drum
  • 8 shows a first view of a control plate of the hydrostatic piston machine according to the invention
  • Fig. 9 is a sectional view of the control plate of the hydrostatic piston machine according to the invention.
  • FIG. 10 shows a second view of the control plate of the hydrostatic piston machine according to the invention.
  • the hydrostatic piston machine 1 comprises a pump 2 for the parallel delivery of pressure medium into two separate, closed hydraulic circuits.
  • the delivery rate of the pump 2 can be changed jointly by an adjusting device 3 for both hydraulic circuits.
  • the adjusting device 3 consists of a cylinder and an actuating piston 4 arranged therein, which is acted upon in a known manner on an oppositely oriented piston surface in each case in an actuating pressure chamber with an actuating pressure.
  • the two signal pressure chambers are each connected via a signal pressure line 6a, 6b to a steep pressure control valve 5.
  • a differential pressure acts on the control piston 4, by means of which the control piston 4 is deflected from its central position, in which it is held by two centering springs.
  • the pump 2 is set to a changed delivery volume. The adjustment affects both the first and the second hydraulic circuit.
  • the first hydraulic circuit is formed from a first working line 7 and a second working line 8.
  • the pump 2 feeds either into the first working line 7 or the second working line 8.
  • pressure medium is simultaneously conveyed into a first working line 7 'of the second hydraulic circuit or, when conveying into the second working line 8 of the first hydraulic circuit into a second working line 8 'of the second hydraulic circuit.
  • the first hydraulic circuit consisting of its first working line 7 and its second working line 8 is hydraulically independent of the second hydraulic circuit, consisting of its first working line 7 'and its second working line 8'.
  • a filter 12 is arranged, which removes impurities from the suctioned pressure medium.
  • a first high-pressure limiting valve 13 and a second high-pressure limiting valve 14 are provided for feeding into the first hydraulic circuit, the first high-pressure limiting valve 13 with the first working line 7 of the first hydraulic circuit and the second high-pressure limiting valve 14 with the second Working line 8 of the first hydraulic circuit is connected.
  • a third high-pressure limiting valve 13 ' is connected to the first working line 7' of the second hydraulic circuit and a fourth high-pressure limiting valve 14 'is connected to the second working line 8' of the second hydraulic circuit.
  • the first to fourth high-pressure relief valves 13, 13 ', 14 and 14' are connected together to a feed line 15, into which the auxiliary pump 9 conveys the pressure medium drawn in.
  • a check valve 17 is arranged in each of the high-pressure relief valves 13 to 14', which has a flow path from the feed line 15 in the direction of feeding pressure medium of the connected working line 7, 8, 7 'or 8' opens as long as the pressure in the feed line 15 is greater than the respective working pressure.
  • a pressure relief valve 18 is arranged in the high pressure relief valves 13, 13 ', 14 and 14', which opens in the direction of the feed line 15 when a critical pressure in the respective working line 7, 8, 7 'or 8' is exceeded ,
  • the control pressure control valve 5 is designed as a 4/3 way valve, which is continuously adjustable. To set a certain position, starting from its neutral position, in which it is held by compression springs, the control pressure control valve 5 is acted upon by a force acting in the axial direction.
  • This force is generated as a force difference between two proportional magnets 20a and 20b, each of which acts in the same direction on a valve piston of the control pressure control valve 5, each with a compression spring.
  • the respectively regulated position of the actuating piston 4 is taken into account when regulating the actuating pressure by connecting a valve sleeve of the actuating pressure control valve 5 to the actuating piston 4 via a coupling rod 21.
  • the signal pressure control valve 5 is connected to the feed line 15 via a signal pressure supply line 16.
  • the adjusting device 3 can thus be actuated when the pump 2 starts up from the point in time at which the auxiliary pump 9 has built up a pressure in the feed pressure line 15.
  • the adjusting device 3 can thus be actuated independently of the quantity of pressure medium delivered by the pump 2 into the first hydraulic circuit or second hydraulic circuit.
  • the auxiliary pump 9 and the pump 2 are driven in the illustrated embodiment by a common drive shaft 22.
  • the longitudinal section of the hydrostatic piston machine according to the invention shown in FIG. 2 shows how the common drive shaft 22 is supported by a roller bearing 23 at one end of a pump housing 24.
  • the common drive shaft 22 is mounted in a slide bearing 26 which is arranged in a connection plate 25 which closes the pump housing 24 at the opposite end.
  • a recess 33 is formed which penetrates the connection plate completely in the axial direction, in which the slide bearing 26 is arranged on the one hand and on the other hand is penetrated by the common drive shaft 22.
  • the auxiliary pump 9 is inserted into a radial extension of the recess 33.
  • the common drive shaft 22 has a first toothing 27.1 and a second toothing 27.2 which are in engagement with corresponding toothing of an auxiliary pump shaft 28.
  • the auxiliary pump shaft 28 is supported in the recess 33 by a first auxiliary pump sliding bearing 34 and by a second auxiliary pump sliding bearing 35 in the auxiliary pump connecting plate 31.
  • a gear wheel 29 is arranged on the auxiliary pump shaft 28 and engages with a ring gear 30. Via the gear wheel 29, the ring gear 30, which is rotatably arranged in the auxiliary pump connection plate 31, is also driven by the auxiliary pump shaft 28 and thus ultimately by the common drive shaft 22.
  • the suction and the pressure-side connection for the auxiliary pump 9 are formed in the auxiliary pump connection plate 31.
  • the auxiliary pump 9 is fixed by a cover 32, which is mounted on the connection plate 25, in the radial extension of the recess 33 of the connection plate 25.
  • the inner ring of the roller bearing 23 is fixed in the axial direction on the common drive shaft 22.
  • the inner ring rests on the one hand on a collar 36 of the common drive shaft 22 and is held in this axial position on the other side by a retaining ring 37 which is inserted in a groove of the common drive shaft 22.
  • the axial position of the roller bearing 23 with respect to the pump housing 24 is determined by a disk 38 which bears against a shoulder of a shaft opening 39 in the pump housing 24.
  • a sealing ring 40 and finally a further locking ring 41 are also arranged in the shaft opening 39, the locking ring 41 being inserted into a circumferential groove in the shaft opening 39.
  • the cylinder drum 43 arranged, which has a central through opening 44, which is penetrated by the common drive shaft 22.
  • the cylinder drum 43 is secured against rotation via a further drive toothing 45, but is connected to the common drive shaft 22 so as to be displaceable in the axial direction, so that a rotary movement of the common drive shaft 22 is transmitted to the cylinder drum 43.
  • a further securing ring 46 is inserted, against which a first support disk 47 bears.
  • the first support disk 47 forms a first spring bearing for a compression spring 48.
  • a second spring bearing for the compression spring 48 is formed by a second support disk 49, which is supported on the end face of the further drive toothing 45.
  • the compression spring 48 thus exerts a force in the opposite axial direction on the one hand on the common drive shaft 42 and on the other hand on the cylinder drum 43.
  • the common drive shaft 22 is loaded so that the outer ring of the roller bearing 23 is supported on the disc 38.
  • the compression spring 48 acts on the cylinder drum 43, which has a spherical one formed on the end face of the cylinder drum 43
  • Well 51 is held in contact with a control plate 52.
  • the control plate 52 in turn lies sealingly on the connection plate 25 with the side facing away from the cylinder drum 43.
  • the cylindrical drum 43 is centered by the spherical depression 51, which corresponds to a corresponding spherical shape of the control plate 52.
  • the position of the control plate 52 in the radial direction is determined by the outer circumference of the slide bearing 26.
  • the slide bearing 26 is only partially inserted into the recess 33 in the connecting plate 25.
  • cylinder drum 43 distributed cylinder bores 53 are introduced over a common pitch circle, in which pistons 54 are arranged, which are longitudinally displaceable in the cylinder bores 53. At the end facing away from the spherical recess 51, the pistons 54 partially protrude from the cylinder drum 43. At this end, a slide shoe 55 is attached to each of the pistons 54, by means of which the pistons 54 are supported on a running surface 56 of a swivel plate 57.
  • the angle that the running surface 56 of the swivel plate 57 forms with the central axis can be changed.
  • the tilting disk 57 can be adjusted by the adjusting device 3.
  • the swivel plate 57 is mounted on rollers in the pump housing 24.
  • a first high-pressure connection 58 and a second high-pressure connection 58 ′ are shown schematically in the connection plate 25, which can be connected to the cylinder bores 53 in a manner not shown via the control plate 52 .
  • An enlarged view of the components interacting inside the pump housing 24 is shown in FIG. 3.
  • the swivel disk 57 On its side facing away from the tread 56, the swivel disk 57 is supported on a cylindrical roller bearing 58, the cylindrical rollers of which are held by a bearing cage 59.
  • the bearing cage 59 In order to ensure a safe return of the cylindrical rollers to their starting position after each pivoting movement, the bearing cage 59 is fastened to a securing mechanism 60, by means of which the bearing cage 59 executes a controlled movement both when pivoting out and when pivoting back.
  • the pivoting disk 57 is coupled to a sliding block 61 which, in a manner not shown, rotates the pivoting disk 57 about an axis lying in the plane of the drawing.
  • the cylinder bores generally designated 53 in FIG. 2 are subdivided into a first group of cylinder bores 53.1 and a second group of cylinder bores 53.2.
  • a slide shoe 55 is arranged on the end of the pistons 54 facing away from the control plate 52.
  • the slide shoe 55 is fastened with a recess on a spherical head of the piston 54, so that the slide shoe 55 is movably fixed to the piston 54 and tensile and compressive forces can be transmitted.
  • a sliding surface 62 is formed on the sliding shoe 55, with which the sliding shoe 55 and thus the piston 54 are supported on the running surface 56 of the swivel disk 57.
  • Lubricating oil grooves are formed in the sliding surface 62, which pass through a lubricating oil channel 63 formed in the sliding block 55 and which is in the piston 54 as a lubricating oil bore 63 '. is continued, are connected to the cylinder bores 53 formed in the cylinder drum 43.
  • the pistons 54 By supporting the sliding shoes 55 on the running surface 56, the pistons 54 perform a lifting movement when the common drive shaft 22 rotates, by means of which the pressure medium located in the cylinder spaces in the cylinder drum 43 is pressurized. A part of this pressure medium exits on the sliding surface 62 and thus forms a hydrodynamic bearing for the sliding shoe 55 on the running surface 56.
  • first connection channels 64.1 and second connection channels 64.2 are connected to the cylinder bores of the first group 53.1 and the cylinder bores of the second group 53.2.
  • the first and second connecting channels 64.1 and 64.2 run from the cylinder bores of the first group 53.1 and the cylinder bores of the second group 53.2 to the spherical recess 51, which is formed on an end face 65 of the cylinder drum 43.
  • a hardened area 66 is formed on the cylinder drum 43 to reduce wear, for example.
  • a third control kidney 69 and a fourth control kidney 70 are preferably formed in the control plate 52. While the first and third control kidneys 67 and 69 via the connection plate 25 with working lines 7 and 8 of the first hydraulic Circuit are connected, the second control kidney 68 and the fourth control kidney 70 are connected to the working lines 7 'and 8' of the second hydraulic circuit in a corresponding manner.
  • the geometric configuration of the control kidneys 67 to 70 in the control plate 52 is explained below with reference to FIGS. 8 to 10.
  • the first and third control kidneys 67 and 69 have an identical first distance R ⁇ 'from the longitudinal axis 71 of the cylinder drum 43, which is smaller than the second distance R 2 ' from the longitudinal axis, which in turn is identical for the second control kidney 68 and the fourth control kidney 70 71.
  • the first connecting channels 64.1 are alternately connected to the first control kidney 67 and the third control kidney 69, so that, due to the stroke movement of the pistons 54 arranged in the cylinder bores 53.1 of the first group, the pressure medium z. B. is sucked in via the third control kidney 69 and pumped through the first control kidney 67 into the pressure-side working line 7 or 8 of the first hydraulic circuit.
  • the first connecting channels 64.1 open out on the end face 65 of the cylinder drum 43 at a first distance R x from the longitudinal axis 71 of the cylinder drum 43, which corresponds to the first distance R x 'of the first and third control kidneys 67 and 69 from the longitudinal axis 71 corresponds to the cylinder drum 43.
  • the first connecting channels 64.1 are arranged in the cylinder drum 43 in such a way that they have a radial directional component by means of which the first distance R x of the mouth at the end face 65 is smaller than the distance on the opposite side of the first connecting channels 64.1.
  • the second connecting channels 64.2 accordingly open out on the end face 65 of the cylinder drum 43 with a second distance D 2 , which corresponds to the second and fourth control kidneys 68 and 70 from the longitudinal axis 71 with a second distance D 2 '.
  • the cylinder bores of the second group 53.2 are alternately connected to the second and fourth control kidneys 68 and 70 via the second connecting channels 6 .2.
  • a hold-down plate 72 which engages around the sliding shoes 55 on a shoulder provided for this purpose.
  • the hold-down plate 72 has a spherical, central recess 73 with which it is supported on a support head 74 which is arranged on the end of the cylinder drum 43 facing away from the end face 65.
  • FIG. 4 shows a further section through a piston machine according to the invention.
  • the section plane does not coincide with the swivel axis of the swivel disk 57.
  • the swivel plate 57 is shown in a swiveled-out state. It follows directly that the volume conveyed is dependent on the angle of the swivel plate 57 and the distance of the sliding shoes 55 from the longitudinal axis 71 of the cylinder drum 43.
  • FIG. 5 shows an enlarged illustration of the cylinder drum 43.
  • the cylinder drum 43 is rotationally symmetrical with respect to its longitudinal axis 71.
  • the hardened region 66 can be seen in the region of the spherical depression 51 which is formed on the end face 65.
  • the first connecting channels 64.1 like the second connecting channels 64.2, open out in this hardened region 66 on the end face 65.
  • the first connecting channels 64.1 open out on the front side at a first distance R x from the longitudinal axis 71.
  • the second connecting channels 64.2 open out on the end face 65 at a second distance R 2 from the longitudinal axis 71, which is greater than the first distance R.
  • the first connection channels 64.1 open into the cylinder bores of the first group 53.1 at a third distance R 3 , the third distance R 3 in the exemplary embodiment shown being identical to a fourth distance R 4 at which the second connection channels 64.2 enter the cylinder bores of the second group 53.2 discharge.
  • first connecting channels 64.1 have a radial directional component.
  • the radial directional component is chosen such that the first distance R x is smaller than the third distance R 3 .
  • the second distance R 2 can also be larger can be selected as the fourth distance R 4 , so that the second connecting channels 64.2 also have a radial directional component.
  • a further measure in order to achieve a greater scope with regard to the distance of the openings of the first and second connecting channels 64.1 and 64.2 from the longitudinal axis 71 is the first connecting channels 64.1 and the second connecting channels
  • the first distance R is identical to the third distance R 3 , the first and third distances R x and R 3 being smaller than the second and fourth distances R 2 and R 4 , which in turn are identical.
  • Such an arrangement is advantageous if there are large diameters of the cylinder bores 53, so that a sufficiently large offset can be achieved between the first connecting channels 64.1 and the second connecting channels 64.2.
  • bushings 74 are inserted into the cylinder bores of the first group 53.1 as well as into the cylinder bores of the second group 53.2.
  • the liners 74 are made of a material that can withstand a higher load than the material of the cylinder drum 43.
  • the cylinder drum 43 itself can be produced from an easy-to-process material that is not suitable for the direct insertion of the pistons 54.
  • the hardened area 66 which withstands the high pressure loads and the friction occurring there, is formed on the end face 65 in the area of the system with the control plate 52.
  • FIG. 6 shows a top view of the cylinder drum 43 from the side of the swivel plate 57.
  • the cylinder bores of the first group 53.1 and the cylinder bores of the second group 53.2 are evenly distributed and arranged alternately over a common pitch circle 76.
  • the cylinder bores of the first group 53.1 and the cylinder bores of the second group 53.2 have an identical diameter.
  • a total of ten cylinder bores 53 are made in the cylinder drum 43 in the exemplary embodiment shown. Of the total of ten cylinder bores 53, five cylinder bores are assigned to the first group 53.1 and five cylinder bores to the second group 53.2. The symmetrical arrangement and an identical The number of cylinder bores in the first group 53.1 and cylinder bores in the second group 53.2 improve the pulsation behavior of the axial piston machine. It is particularly advantageous if the first group and the second group contain an identical, odd number of cylinder bores 53.
  • the end face 65 of the cylinder drum 43 is shown as a top view in FIG. 7.
  • the mouths of the first connecting channels 64.1 are kidney-shaped and open out in the area of the spherical depression 51 on a circle with the first radius R x .
  • the kidney-shaped openings of the first connecting channels 64.1 each have an identical geometry. They extend over a first length L-_ along a circular arc with the first radius R x , the kidney-shaped openings being arranged symmetrically with respect to the circular arc.
  • the outlets of the second connecting channels 64.2 are also kidney-shaped and each extend with a second length L 2 along an arc of a circle with the second radius R 2 .
  • the kidney-shaped openings of the second connecting channels 64.2 are also arranged symmetrically with respect to the circular arc with the second radius R 2 , the width of the openings in the radial direction being smaller than the width of the openings of the first connecting channels 64.1.
  • the second length L 2 of the mouths second connection channels 64.2 is greater than the first length L x of the openings of the first connection channels 64.1, so that the opening cross section of the openings of the first connection channels 64.1 is identical to the opening cross section of the openings of the second connection channels 64.2.
  • FIG 8 shows a top view of a control plate 52 of a hydrostatic piston machine 1 according to the invention.
  • two recesses 78.1 and 78.2 are provided on the outer circumference of the control plate 52.
  • the first control kidney 67 consists of a first section 67 'and a second section 67''.
  • Each of the two sections 67 'and 67'' is kidney-shaped.
  • the two kidney-shaped sections 67 'and 67''each have an identical third length L 3 and extend along an arc with a first control kidney radius R', which is in particular identical to the first radius R. of the mouths of the first connecting channels 64.1.
  • a first separating web 79 is formed between the first section 67 ′ and the second section 67 ′′ of the first control kidney 67.
  • the first section 67 'and the second section 67''of the first control kidney 67 are arranged symmetrically with respect to the circular arc with the first control kidney radius R x '.
  • the openings of the first connecting channels 64.1 are therefore in register with the first section 67 'or the second section 67''of the first control kidney 67.
  • the second control kidney 68 is also formed by a first section 68 ′ and a second section 68 ′′.
  • the two sections 68 'and 68''of second control kidneys 68 are again each kidney-shaped and are also separated from one another by the first separating web 79.
  • the two sections 67 'and 67''of the first control kidney 67 and the two sections 68' and 68 '' of the second control kidney 68 are each arranged symmetrically with respect to the separating web 79.
  • the sections 68 'and 68''of the second control kidney 68 extend along an arc with the second control kidney radius R 2 ', their width being smaller than the width of the sections 67 'and 67''of the first control kidney 67.
  • the kidney-shaped sections 68 'and 68'' are also arranged symmetrically with respect to the circular arc with the second control kidney radius R 2 '.
  • the second kidney control port radius R 2 ' is preferably identical to the second radius R.sub.2.
  • the width of the sections 68 ′ and 68 ′′ of the second control kidney 68 in accordance with the width of the openings of the second connection channels 64.2.
  • the second connecting channels 64.2 depending on the angle of rotation of the common drive shaft 22 and the cylinder drum 43, come into complete overlap with the sections 68 ′ and 68 ′′ of the second control kidney 68.
  • the first section 68 ′ and the second section 68 ′′ of the second control kidneys 68 extend with a fourth length L 4 along the circular arc with the second control kidney radius R 2 '.
  • the control times of the axial piston machine are set by the selected lengths and the position of the kidney-shaped sections on the respective circular arcs.
  • a first section 69 ′ and a second section 69 ′′ of the third control kidney 69 as well as a first section 70 ′ and a second section 70 ′′ of the fourth control kidney 70 are introduced diametrically opposite in the control plate 52.
  • the geometry and the arrangement of the third control kidney 69 corresponds to that of the first control kidney 67 and the geometry and the arrangement of the fourth Control kidney 70 corresponds to that of second control kidney 68.
  • first separating web 79 there is a second separating web between first sections 69 ', 70' and second sections 69 '', 70 '' of third and fourth control kidneys 69 and 70, respectively 81 trained
  • Control kidney 69 and 70 is a circumferential groove 80 in the
  • Control plate 52 introduced.
  • return bores 82.1, 82.2, 82.3 and 82.4 are provided, which are used for the return transport of pressure medium from the hydrodynamic plain bearing into the circumferential one
  • Groove 80 arrives.
  • the circumferential groove 80 relieves the spherical shape of the control plate 52 in the region of the first and third control kidneys 67 and 69 and the second and fourth control kidneys 68 and 70, independently of one another.
  • a separate hydrodynamic plain bearing is thus formed between the cylinder drum 43 and the control plate 52 for each hydraulic circuit.
  • the pressure medium is likewise returned to the inside of the pump housing 24 via the return bores 82.1 to 82.4 on the side facing away from the cylinder drum 43.
  • FIG. 9 shows a section through a control plate 52 along the line IX-IX of FIG. 8. It can be seen there that the first sections 69 'and 70' of the third and fourth control kidneys 69 and 70 shown in FIG. 9 are arranged in a region with a spherical shape 83. The circumferential groove 80 is arranged in between. In the area of the first recess 78.1 on the outer circumference of the control plate 52 there is a radially inward offset and a centering hole from the side of the connection plate 26 84 introduced into the control plate 52, which serves to receive a centering pin, not shown.
  • an inner centering bore 87 is made in the control plate 52, which is designed in several stages. As was already briefly stated in the explanation of FIG. 2, the part of the slide bearing 26 protruding from the connecting plate 25 projects into this inner centering bore 87. Due to the multi-stage design of the inner centering bore 87, an outer circumferential collar can be formed on the slide bearing 26, which collar serves as a stop when inserted into the recess 33 of the connecting plate 25.
  • a flat region 85 is formed on the control plate 52, through which the control plate 52 lies sealingly against a corresponding, flat surface of the connection plate 25 .
  • the flat area 85 does not extend over the entire diameter of the control plate 52, but leaves a recessed area 86 free in the radially outer area of the control plate 52.
  • this area 86 set back from the flat area 85, there is a gap between the control plate 52 and the connecting plate 25, through which the pressure medium discharged through the return bores 82.1 to 82.4 flows into the interior of the pump housing 24.
  • a further circumferential groove 88 is arranged in the flat region 85, the radius of which is identical to the radius of the circumferential groove 80.
  • the circumferential groove 80 and the further circumferential groove 88 are thus connected to one another via the return bores 82.1 to 82.4.
  • the exit of the return bores 82.1 to 82.4 into the further circumferential groove 88 is shown in the view of the control plate 52 from the side of the connection plate 25.
  • a first runs from the first recess 78.1 and the second recess 78.2, which are arranged on the outer circumference of the control plate 52 Drain groove 89.1 and a second drain groove 89.2 in the radial direction to the inner center hole 87.
  • the pressure medium flowing through the circumferential groove 80 and the return bores 82.1 to 82.4 into the further circumferential groove 88 is thus via the enlarged area 90.1 or the enlarged area 90.2 and the adjoining drainage grooves 89.1 or 89.2 into the outer area of the control plate 52 and thus the inside of the pump housing 24 is discharged.
  • a piston machine is used for a first and a second, separate, closed hydraulic circuit, the cylinder bores 53 being arranged on a single, common pitch circle 76 in the cylinder drum 43.
  • the cylinder bores 53 are assigned to the first or second hydraulic circuit via first connecting channels 64.1 or second connecting channels 64.2, which are also arranged in the cylinder drum 43.
  • the outlets of the first connecting channels 6 .1 and the second connecting channels 64.2 are at a different distance from the longitudinal axis 71 of FIG Cylinder drum 43, this different distance corresponding to the arrangement of the first and third control kidneys 67 and 69 or second and fourth control kidneys 68 and 70 of a control plate 52 belonging to the respective first or second hydraulic circuit.
  • the same odd number of cylinder bores 53 are preferably assigned to each hydraulic circuit.
  • the connecting channels can either be arranged radially offset from one another, but parallel to the longitudinal axis 72 in the cylinder drum 43, or they can have a radial directional component.
  • those connecting channels 64.1 and 64.2 have a smaller distance from the

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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 comportant un tambour cylindrique (43) dans lequel sont aménagés un premier groupe d'alésages (53,1) et un second groupe d'alésages (53,2). Les alésages du premier groupe (53,1) peuvent être reliés avec un premier circuit hydraulique et les alésages du second groupe (53, 2), avec un second circuit hydraulique. Les alésages du premier groupe (53,1) et les alésages du second groupe (53,2) sont aménagés sur un cercle partiel (76) commun dans le tambour cylindrique (43).
EP04790263A 2003-10-10 2004-10-11 Machine a piston hydrostatique munie de deux circuits hydrauliques Active EP1671032B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10347085A DE10347085B3 (de) 2003-10-10 2003-10-10 Hydrostatische Kolbenmaschine mit zwei hydraulischen Kreisläufen
PCT/EP2004/011356 WO2005035980A1 (fr) 2003-10-10 2004-10-11 Machine a piston hydrostatique munie de deux circuits hydrauliques

Publications (2)

Publication Number Publication Date
EP1671032A1 true EP1671032A1 (fr) 2006-06-21
EP1671032B1 EP1671032B1 (fr) 2007-02-21

Family

ID=34428281

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04790263A Active EP1671032B1 (fr) 2003-10-10 2004-10-11 Machine a piston hydrostatique munie de deux circuits hydrauliques

Country Status (4)

Country Link
US (1) US7513189B2 (fr)
EP (1) EP1671032B1 (fr)
DE (2) DE10347085B3 (fr)
WO (1) WO2005035980A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005036773A1 (de) * 2005-08-04 2007-02-08 Linde Ag Verdrängereinheit mit einem Steuerspiegelkörper
CN102192119A (zh) * 2010-03-12 2011-09-21 北京华德液压工业集团有限责任公司 双排缸孔缸体的轴向柱塞泵
CH703754A2 (de) * 2010-09-06 2012-03-15 Marko Palic Verfahren für den Betrieb einer Axialkolbenmaschine sowie Axialkolbenmaschine.
CN103835908A (zh) * 2012-11-27 2014-06-04 北京华德液压工业集团有限责任公司 一种斜轴式轴向柱塞泵
CN106368921B (zh) * 2016-10-17 2019-05-10 北京华德液压工业集团有限责任公司 一种超高压轴向柱塞泵

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GB563850A (en) * 1940-05-02 1944-09-01 Automotive Prod Co Ltd Improvements in or relating to liquid pressure actuated pumps
US3188963A (en) * 1962-06-04 1965-06-15 Bendix Corp Fluid intensifier
DE3127610A1 (de) 1980-07-15 1983-01-20 Linde Ag, 6200 Wiesbaden Axialkolbenpumpe fuer zwei foerderstroeme
DE3727853A1 (de) * 1986-08-20 1988-05-19 Rexroth Mannesmann Gmbh Axialkolbenpumpe
JPH02283870A (ja) * 1989-04-05 1990-11-21 Zahnradfab Friedrichshafen Ag 軸方向ピストンポンプ
US5988987A (en) * 1996-08-28 1999-11-23 Fia Solutions, Inc. Method for merging and/or ratio blending aliquant
DE10030147C1 (de) * 2000-06-20 2002-06-06 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine
US6912849B2 (en) * 2002-04-09 2005-07-05 Komatsu Ltd. Cylinder driving system and energy regenerating method thereof

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Also Published As

Publication number Publication date
US7513189B2 (en) 2009-04-07
EP1671032B1 (fr) 2007-02-21
DE10347085B3 (de) 2005-06-16
US20070101857A1 (en) 2007-05-10
DE502004002990D1 (de) 2007-04-05
WO2005035980A1 (fr) 2005-04-21

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