EP1700034A1 - Axialkolbenmaschine zum unabhä ngigen fördern in mehrere hydraulische kreisläufe - Google Patents
Axialkolbenmaschine zum unabhä ngigen fördern in mehrere hydraulische kreisläufeInfo
- Publication number
- EP1700034A1 EP1700034A1 EP04803814A EP04803814A EP1700034A1 EP 1700034 A1 EP1700034 A1 EP 1700034A1 EP 04803814 A EP04803814 A EP 04803814A EP 04803814 A EP04803814 A EP 04803814A EP 1700034 A1 EP1700034 A1 EP 1700034A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pistons
- group
- piston machine
- pivot axis
- axial piston
- 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
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
- F04B1/14—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 stationary cylinders
- F04B1/16—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 stationary cylinders 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
- F04B1/2078—Swash plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
Definitions
- the invention relates to an axial piston machine with a first group of pistons for delivery in a first hydraulic circuit and with a second group of pistons for delivery in a second hydraulic circuit.
- the pistons of the first group and the pistons of the second group are each arranged on a separate pitch circle, with the pistons that are assigned to the pitch circle with the smaller diameter being supported on a first swash plate that are hemispherical on the side facing away from the pistons and is mounted in the second swash plate.
- the first and the second swash plate can be pivoted separately about a common axis for independently adjusting the delivery rates of the first hydraulic circuit and the second hydraulic circuit, with a recess being provided in the second swash plate for adjusting the first swash plate, through which the adjusting device can be adjusted accesses first swashplate.
- the first swash plate can also be slightly inclined to change the dead center position about a second axis which is perpendicular to the actual pivot axis.
- a disadvantage of this arrangement is that although the second swash plate can be mounted in a known manner with a spherical outer contour, the second swash plate must at the same time be designed as a bearing for the first swash plate. Furthermore, it is disadvantageous that a recess is provided in the second swash plate for adjusting the swivel angle of the inner swash plate. Since the swash plate must absorb considerable pressure forces the necessary recess can neither designed arbitrarily positioned 'nor arbitrary. However, this leads to a restriction with regard to the possibility of adjusting the first swash plate, as a result of which the delivery volume of the corresponding hydraulic circuit can only be changed to a limited extent.
- the axial length of the axial piston machine is extended by the two swash plates being stored one inside the other. Part of the advantage of using a single axial piston machine for conveying into two hydraulic circuits is lost again.
- the axial piston machine has a first group of pistons for conveying a pressure medium in a first hydraulic circuit.
- the swash plate on which the pistons of the first group are supported can be pivoted about a first pivot axis.
- The are also supported on the same swash plate Pistons from the second group for conveying a pressure medium into a second hydraulic circuit.
- the swash plate can be pivoted about a second pivot axis, by means of which an effective stroke volume of the pistons of the second group is set.
- the effective stroke volume for the first hydraulic circuit and for the second hydraulic circuit can be set individually.
- the possible adjustable swivel angles are not limited by the angle set with respect to the other swivel axis.
- the two pivot axes are each arranged to be longitudinally displaceable in corresponding first and second cylinder bores.
- the first and second cylinder bores can each be connected to the first and second hydraulic circuits via a pair of control kidneys.
- a pair of control kidneys is arranged symmetrically to the vertical projection of the corresponding pivot axis into the plane of the control kidneys.
- a further advantage is to arrange the pistons of the first or second group provided for delivery in the first hydraulic circuit or the second hydraulic circuit on a common pitch circle.
- this results in an identical delivery volume in the two hydraulic circuits.
- the arrangement of all pistons on only one pitch circle results in improved synchronism of the axial piston machine, with correspondingly lower vibrations and less noise.
- z. B. specifically limit the maximum delivery rate in a certain ratio to the other hydraulic circuit for a second delivery circuit.
- the maximum delivery rate is not achieved by using only a limited swivel angle range. This results in one Correspondingly fine gradation option when setting the delivery volume, since the full adjustment range for the inclination angle of the swash plate is retained.
- Figure 1 is a sectional view of an axial piston machine for conveying into two hydraulic circuits.
- FIG. 2 shows an enlarged illustration of the engine of the axial piston machine according to FIG. 1;
- FIG. 3 shows a schematic illustration with a swash plate inclined about a pivot axis
- FIG. 4 shows a schematic illustration with a swash plate inclined around another swivel axis
- Fig. 5 is a plan view of a control plate of the axial piston machine according to the invention.
- the longitudinal section of a hydrostatic piston machine 1 according to the invention shown in FIG. 1 shows how a common drive shaft 2 is supported by a roller bearing 3 at one end of a pump housing 4.
- the common drive shaft 2 is mounted in a slide bearing 6, which is arranged in a connecting plate 5, which closes the pump housing 4 at the opposite end.
- connection plate 5 there is a recess 7 which penetrates the connection plate 5 completely in the axial direction and in which the slide bearing 6 is arranged and which is penetrated by the common drive shaft 2.
- the auxiliary pump 8 is inserted into a radial extension of the recess 7.
- the common drive shaft 2 has a toothing 9 which is in engagement with a corresponding toothing of an auxiliary pump shaft 10.
- the auxiliary pump shaft 10 is in the recess 7 by a first auxiliary pump sliding bearing 11 and by a second auxiliary pump sliding bearing 12 in one
- Auxiliary pump connection plate 13 mounted.
- a gear 14 is arranged, which is in engagement with a ring gear 15.
- the ring gear 15 which is rotatably arranged in the auxiliary pump connection plate 13, is also driven by the auxiliary pump shaft 10 and thus ultimately by the common drive shaft 2.
- the suction and the pressure-side connection for the auxiliary pump 8 are formed in the auxiliary pump connection plate 13.
- the auxiliary pump 8 is fixed by a cover 16, which is mounted on the connection plate 5, in the radial extension of the recess 7 of the connection plate 5.
- the inner ring of the roller bearing 3 is fixed on the common drive shaft 2 in the axial direction.
- the inner ring rests on the one hand on a collar 17 of the common drive shaft 2 and is held in this axial position on the other side by a retaining ring 18 which is inserted in a groove of the common drive shaft 2.
- the axial position of the roller bearing 3 with respect to the pump housing 4 is determined by a locking ring 19 which is inserted in a circumferential groove in the shaft opening 20.
- the roller bearing 3 rests on a housing shoulder, not shown, of the pump housing 4.
- a sealing ring 21 and finally a further locking ring 22 are also arranged in the shaft opening 20, the locking ring 22 being inserted into a circumferential groove in the shaft opening 20.
- a drive toothing 23 is formed, via which the hydrostatic piston machine is driven by a drive machine, not shown.
- a cylinder drum 24 is arranged in the interior of the pump housing 4 and has a central through opening 25, which is penetrated by the common drive shaft 2.
- the cylinder drum 24 is secured against rotation via driving teeth 26, but is connected to the common drive shaft 2 such that it can be displaced in the axial direction, so that a rotary movement of the common drive shaft 2 is transmitted to the cylinder drum 24.
- a further securing ring 27 is inserted, against which a first support disk 28 bears.
- the first support disk 28 forms a first spring bearing for a compression spring 29.
- a second spring bearing for the compression spring 29 is by a second support disc 30 is formed, which is supported on the end face of the driving toothing 26.
- the compression spring 29 thus exerts a force in the opposite axial direction on the one hand on the common drive shaft 2 and on the other hand on the cylinder drum 24.
- the common drive shaft 2 is loaded so that the outer ring of the roller bearing 3 is supported on the retaining ring 19.
- the compression spring 29 acts on the cylinder drum 24, which is held in contact with a control plate 32 by means of a spherical depression 31 formed on the end face of the cylinder drum 24.
- the control plate 32 in turn lies sealingly on the connection plate 5 with the side facing away from the cylinder drum 24.
- the cylindrical drum 24 is centered by the spherical recess 31, which corresponds to a corresponding spherical shape of the control plate 32.
- the control plate 32 can also be designed as a flat disk if, for example, centering realized in a different way together with a spherical control plate 32 would lead to overdetermination.
- the position of the control plate 32 in the radial direction is determined by the outer circumference of the slide bearing 6.
- the slide bearing 6 is only partially inserted into the recess in the connecting plate 5.
- cylinder bores 33 In the cylinder drum 24 distributed over a common pitch circle cylinder bores 33 are made, in which pistons 34 are arranged, which are longitudinally displaceable in the cylinder bores 33. At the end facing away from the spherical recess 31, the pistons 34 partially protrude from the cylinder drum 24. At this end, a slide shoe 35 is attached to each of the pistons 34, by means of which the pistons 34 are supported on a running surface 36 of a swash plate 37. To generate a stroke movement of the pistons 34, the angle that the running surface 36 of the swash plate 37 forms with a central axis 40 can be changed. For this purpose, the swash plate 37 can be adjusted in its inclination by an adjusting device 38. The swash plate 37 is mounted in the pump housing 4 to absorb the forces which are transmitted to the swash plate 37 by the sliding shoes 35.
- connection plate 5 To connect the hydrostatic piston machine 1 to a first hydraulic circuit and to a second hydraulic circuit, a first connection 39 and a second connection 39 ′ are shown schematically in the connection plate 5, which can be connected to the cylinder bores 33 in a manner not shown via the control plate 32 ,
- FIG. 2 An enlarged view of the components interacting inside the pump housing 4 is shown in FIG. 2.
- the swash plate 37 is coupled to a sliding block 44, which rotates the swash plate 37 in a manner not shown about an axis lying in the plane of the drawing.
- the cylinder bores generally designated 33 in FIG. 1 are divided into a first group of cylinder bores 33.1 and a second group of cylinder bores 33.2.
- a slide shoe 35 is arranged on the end of the piston 34 facing away from the control plate 32.
- the sliding block 35 is fastened with a recess on a spherical head of the piston 34, so that the sliding block 35 is movably fixed to the piston 34 and tensile and compressive forces can be transmitted.
- a sliding surface 45 is formed on the sliding shoe 35, with which the sliding shoe 35 and thus the piston 34 are supported on the running surface 36 of the swash plate 37.
- Lubricating oil grooves are formed in the sliding surface 45 and are connected to the cylinder bores 33 formed in the cylinder drum 24 via a lubricating oil channel 46 formed in the sliding block 35, which is continued in the piston 34 as a lubricating oil bore 46 '.
- the pistons 34 By supporting the sliding shoes 35 on the running surface 36, the pistons 34 perform a lifting movement when the common drive shaft 2 rotates, by means of which the pressure medium located in the cylinder chambers in the cylinder drum 24 is pressurized.
- the sliding shoes 35 are hydrostatically relieved on the running surface 36 of the swash plate 37.
- first connection channels 47.1 and second connection channels 47.2 are connected to the cylinder bores of the first group 33.1 and the cylinder bores of the second group 33.2, respectively.
- the first and second connecting channels 47.1 and 47.2 run from the cylinder bores of the first group 33.1 and the cylinder bores of the second group 33.2 to the spherical recess 31, which is formed on an end face 48 of the cylinder drum 24.
- a third control kidney and a fourth control kidney are preferably formed in the control plate 32, which are not recognizable in FIG. 2 because of the position of the cutting plane. While the first and the second bullet kidneys 50 and 51 via the connection plate 5 with the working lines of the first hydraulic Circuit are connected, the third control kidney and the fourth control kidney are connected in a corresponding manner to the working lines of the second hydraulic circuit.
- the geometric configuration of the control kidneys in the control plate 32 is explained below with reference to FIG. 5.
- the first and second control kidneys 50 and 51 have an identical first distance R x from the central axis 40 of the cylinder drum 24, which is greater than the distance R 2, which in turn is identical for the third and fourth control kidneys.
- the first connecting channels 47.1 are alternately connected to the first control kidney 50 and the second control kidney 51, so that, due to the stroke movement of the pistons 34 arranged in the cylinder bores 33.1 of the first group, the pressure medium z. B. is sucked in via the second control kidney 51 and pumped through the first control kidney 50 into the pressure-side working line of the first hydraulic circuit.
- the first connecting channels 47.1 are arranged in the cylinder drum 24 in such a way that the first distance R of the mouth on the end face 48 is greater than the second distance R 2 in which the second connecting channels 47.2 open on the front side 48.
- the second connecting channels 47.2 have a radial directional component and accordingly open out on the end face 48 of the cylinder drum 24 with the second distance R 2 , which corresponds to the distance of the third and fourth control kidneys from the central axis 40.
- the cylinder bores of the second group 33.2 are alternately connected to the third and fourth control kidneys via the second connecting channels 47.2.
- a retraction plate 52 which engages around the sliding shoes 35 on a shoulder provided for this purpose.
- the retraction plate 52 has e.g. B. a spherical, central recess 53 with which it is supported on a retraction ball 54 which is arranged on the end of the cylinder drum 24 facing away from the end face 48.
- FIG. 3 it is shown how, starting from an axial piston machine of FIGS. 1 and 2, an independent adjustment of the delivery rates for the two hydraulic circuits can be achieved with a swash plate 37 '.
- the swash plate 37 ' can be tilted about a first pivot axis 55 and about a second pivot axis 56.
- the first and second swivel axes 55 and 56 lie in the plane of the running surface 36 of the swash plate 37 and, when the axial piston machine is set to zero delivery volume in both hydraulic circuits, form an angle of 90 ° with the central axis 40.
- FIG. 3 shows that the swash plate 37 'is inclined about the second pivot axis 56. This creates an effective stroke for pumping pressure medium into the second hydraulic circuit.
- An effective stroke is a movement of the pistons 34, which leads to an actual delivery of pressure medium.
- the third control kidney 57 and the fourth control kidney 58 are each arranged symmetrically with respect to a vertical projection 56 ′ of the second pivot axis 56 into the plane of the control kidneys ,
- the second connecting channels 47.2 move during half a revolution of the cylinder drum 24 from the bottom dead center to the top dead center in essentially along the third control kidney 57, so that the pressure medium is pressed via the third control kidney 57 into the pressure-side working line of the second hydraulic circuit. Accordingly, during the second half of a revolution of the cylinder drum 24, the second connecting channels 47.2 move substantially along the fourth control kidney 58 on the way from the top dead center to the bottom dead center and carry out a suction stroke.
- the first control kidney 50 and the second control kidney 51 are in turn formed symmetrically to a vertical projection 55 ′ of the first pivot axis 55 into the plane of the control kidneys.
- the first pivot axis 55 and the second pivot axis 56 are arranged at a right angle to one another. Accordingly, the first and second control kidneys 50 and 51 and the third and fourth control kidneys 57 and 58 in the control plate 32 are likewise arranged rotated by 90 ° with respect to one another.
- a conveyance into the first hydraulic circuit does not take place with the deflection of the swash plate 37 'shown.
- the position of the first and second control kidneys 50 and 51 is symmetrical with respect to the position of the top and bottom dead center, so that despite the use of the common swash plate 37 'in the first hydraulic circuit, only a small pulsation is generated as long as the swash plate 37' is not is additionally inclined about the first pivot axis 55.
- the arrangement of the first to fourth control kidneys 50, 51, 57 and 58 in the control plate 32 is explained again in the description of FIG. 5.
- first pivot axis 55 and the second pivot axis 56 are arranged at right angles to one another, with both pivot axes 55 and 56 in the plane of the tread 36 lie.
- the intersection of the first pivot axis 55 with the second pivot axis 56 coincides with the intersection of the two pivot axes 55 and 56 with the central axis 40.
- the swash plate 37 On its side facing away from the tread 36, the swash plate 37 'is hemispherical at least in an area 59 adjacent to the tread 36.
- a ball bearing or a plain bearing can be provided as a bearing in order to support the swash plate and to enable its rotation.
- the hemispherical region 59 is delimited by a flattened area 63, which is preferably parallel to the running surface 36.
- the inclination of the swash plate 37 ' can either be set via a separate adjusting device for each pivot axis 55 and 56, only the adjusting device for the pivot axis 55 being shown in FIG. 1 and the adjusting device for the pivot axis 56 not being recognizable in the sectional view , or via a common adjusting device via which a resulting inclination angle of the swash plate 37 'is set.
- those pistons which can be connected to the third control kidney 57 or the fourth control kidney 58 via the second connecting channels 47.2 lead in the Area in which a connection to the respective hydraulic circuit is established, only a slight movement around the bottom dead center or around the top dead center, which in turn only generates a small pulsation in the working lines of the second hydraulic circuit.
- the control plate 32 is shown in a plan view.
- the first pivot axis 55 and the second pivot axis 56 are perpendicular to one another.
- the vertical projections 55 'and 56' shown in FIG. 5 each form an axis of symmetry for the first and second control kidneys 50 and 51 and for the third and fourth control kidneys 57 and 58.
- the control plate 32 has a centering opening 62 in the center, with which the position of the control plate in the axial piston machine 1 is defined.
- the centering opening 62 centers the control plate on the slide bearing 6.
- a groove 63.1 and 63.2 extends in the radial direction from the centering opening 62.
- a further groove 64.1 and 64.2 extends analogously along the projection 56 'of the further pivot axis 56.
- the four grooves 63.1, 63.2, 64.1 and 64.2 are connected to one another via an annular groove 60.
- the annular groove 60 itself is arranged concentrically with the centering opening 62 and the control kidneys.
- the control kidneys 50 and 51 extend along a circular line with a radius that is larger than the radius of the circular line along which the third and fourth control kidneys 57 and 58 extend.
- four bores 61.1 to 61.4 are arranged evenly distributed.
- the bores 61.1 to 61.4 connect the annular groove 60 to the side of the control plate 32 facing the cylinder drum 24 Leakage pressure medium are discharged into the interior of the axial piston machine 1.
- an axial piston machine for two open circuits or one closed and one open circuit can also be provided with the displacement volume adjustment according to the invention. More than two cycles are also easily conceivable.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10358728A DE10358728B4 (de) | 2003-12-15 | 2003-12-15 | Axialkolbenmaschine zum unabhängigen Fördern in mehrere hydraulische Kreisläufe |
PCT/EP2004/014184 WO2005057009A1 (de) | 2003-12-15 | 2004-12-13 | Axialkolbenmaschine zum unabhängigen fördern in mehrere hydraulische kreislaüfe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1700034A1 true EP1700034A1 (de) | 2006-09-13 |
EP1700034B1 EP1700034B1 (de) | 2007-03-21 |
Family
ID=34672760
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04803814A Expired - Fee Related EP1700034B1 (de) | 2003-12-15 | 2004-12-13 | Axialkolbenmaschine zum unabhä ngigen fördern in mehrere hydraulische kreisläufe |
Country Status (4)
Country | Link |
---|---|
US (1) | US7458312B2 (de) |
EP (1) | EP1700034B1 (de) |
DE (2) | DE10358728B4 (de) |
WO (1) | WO2005057009A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006021570A1 (de) * | 2006-04-10 | 2007-10-18 | Robert Bosch Gmbh | Hydrostatische Kolbenmaschine mit drehbarer Steuerscheibe |
EP1970566A2 (de) * | 2007-03-12 | 2008-09-17 | Kabushiki Kaisha Toyota Jidoshokki | Verdichter mit variabler Verdrängung |
WO2010053521A1 (en) * | 2008-10-29 | 2010-05-14 | Ecothermics Corporation | Axial piston multi circuit machine |
DE102012004302A1 (de) | 2012-03-01 | 2013-09-05 | Robert Bosch Gmbh | Elektrohydraulisches System |
CN102705191B (zh) * | 2012-06-01 | 2015-09-23 | 沈如华 | 调色机的色浆定量供应装置 |
DE102013108408A1 (de) * | 2013-08-05 | 2015-02-05 | Linde Hydraulics Gmbh & Co. Kg | Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise mit einem Gleichlaufgelenk zur Mitnahme der Zylindertrommel |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB204374A (en) | 1922-06-21 | 1923-09-21 | Fritz Egersdoerfer | Pumps and compressors |
US1714148A (en) * | 1927-12-21 | 1929-05-21 | Weldy Arthur Sheldon | Pump |
US2520632A (en) * | 1945-03-22 | 1950-08-29 | Torq Electric Mfg Company | Hydraulic pump or motor |
US2445281A (en) * | 1945-10-04 | 1948-07-13 | Charles H Rystrom | Hydraulic pump |
DE1136285B (de) | 1954-03-09 | 1962-09-06 | Passavant Werke | Verfahren zur kontinuierlichen Reinigung von alkalischen, schwefelwasserstoffhaltigen Abwaessern aus Lederfabriken durch Eisenung |
FR1340850A (fr) * | 1962-07-19 | 1963-10-25 | Perfectionnements aux pompes à piston et analogues | |
DE1653634A1 (de) * | 1967-04-22 | 1971-07-15 | Teves Gmbh Alfred | Hydrostatische Maschine fuer zwei Druckmittelkreise |
IT1082968B (it) * | 1977-04-05 | 1985-05-21 | Gherner Lidio | Motore idraulico a pistoni assiali |
DD136285A1 (de) * | 1978-12-28 | 1979-06-27 | Wolfgang Tautenhahn | Hydrostatische axialkolbenmaschine |
DE3026765A1 (de) * | 1980-07-15 | 1982-02-11 | Linde Ag, 6200 Wiesbaden | Axialkolbenpumpe fuer zwei foerderstroeme |
DE3413867C2 (de) * | 1983-04-13 | 1995-04-06 | Linde Ag | Axialkolbenpumpe für zwei Förderströme |
JPH10184532A (ja) * | 1996-12-26 | 1998-07-14 | Daikin Ind Ltd | 可変容量形ピストンポンプ |
US7406911B2 (en) | 2001-03-06 | 2008-08-05 | Honda Giken Kogyo Kabushiki Kaisha | Expander |
-
2003
- 2003-12-15 DE DE10358728A patent/DE10358728B4/de not_active Expired - Fee Related
-
2004
- 2004-12-13 WO PCT/EP2004/014184 patent/WO2005057009A1/de active IP Right Grant
- 2004-12-13 US US10/582,828 patent/US7458312B2/en not_active Expired - Fee Related
- 2004-12-13 DE DE502004003321T patent/DE502004003321D1/de active Active
- 2004-12-13 EP EP04803814A patent/EP1700034B1/de not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2005057009A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE10358728B4 (de) | 2006-01-05 |
US7458312B2 (en) | 2008-12-02 |
DE502004003321D1 (de) | 2007-05-03 |
EP1700034B1 (de) | 2007-03-21 |
WO2005057009A1 (de) | 2005-06-23 |
DE10358728A1 (de) | 2005-07-14 |
US20070101858A1 (en) | 2007-05-10 |
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