US20070251377A1 - Variable capacity hydrostatic axial piston machine - Google Patents
Variable capacity hydrostatic axial piston machine Download PDFInfo
- Publication number
- US20070251377A1 US20070251377A1 US11/736,996 US73699607A US2007251377A1 US 20070251377 A1 US20070251377 A1 US 20070251377A1 US 73699607 A US73699607 A US 73699607A US 2007251377 A1 US2007251377 A1 US 2007251377A1
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- United States
- Prior art keywords
- spherical
- piston
- axial piston
- machine according
- piston machine
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- 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.)
- Abandoned
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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
- F04B1/2014—Details or component parts
-
- 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
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
Definitions
- the invention relates to a variable capacity hydrostatic axial piston machine according to the features of claim 1 .
- Variable capacity hydrostatic machines which, for example, are used as hydraulic motors, have a cylinder drum which is mounted such that it can rotate about its central longitudinal axis and has cylinder bores distributed on its circumference, in which pistons can be displaced.
- the cylinder drum is mounted in the housing of the axial piston machine such that it can pivot about a pivot axis running transversely with respect to its axis of rotation, so that the central longitudinal axis of the cylinder drum forms an adjustable angle with the axis of the drive shaft.
- the pistons are supported in an articulated manner on the drive flange of the drive shaft at the adjustable angle.
- the spherical piston heads are in this case pivotably mounted in spherical shells, which are formed in the drive flange or in piston shoes fitted there.
- a retaining device which engages behind the spherical heads, for example by a perforated plate screwed on.
- An axial piston machine of this type is known, for example from EP 1 251 271 A2.
- spherical joint connections having a spherical shell which encloses an angle which is greater than 180°.
- the latter has lateral flats or recesses, so that it can be inserted at an angle deviating from the working position and is held in the working position by the spherical shell.
- Spherical joints of this type are described, for example, in DE-OS 2 307 641.
- this object is achieved 10 with a variable capacity hydrostatic axial piston machine which has a drive shaft with a drive flange having an end face oriented towards displacement pistons, in which end face spherical shells for holding substantially spherical piston heads are formed.
- the calotte of the spherical shells in this case go beyond the semisphere and have a circular opening with a smaller diameter than the spherical shell diameter.
- the spherical calotte of the piston heads have a recess having a smaller diameter than that of the circular opening of the spherical shells so that at the vertex of the piston a spherical section making up less than the semisphere and, spaced apart from the latter by the recess a retaining collar having a larger diameter than the circular opening of the spherical shell are formed.
- a transverse groove is formed in the circular opening of the spherical shell in such a way that the piston head with the retaining collar can be threaded into the spherical shell through the transverse groove and is retained there in the working position of the piston.
- a piston shoe can be dispensed with and overall space for a larger domed sphere can be obtained, at the same time a smaller total overall length being achieved.
- the larger domed sphere in this case permits a high level of balance of the hydrostatic load from the piston force, so that only a small part of the piston force has to be transmitted mechanically via the frictional contact.
- the retaining collar preferably forms a spherical layer, which begins approximately in the middle of the spherical dome of the piston heads and extends approximately from the middle of the spherical dome beyond the latter by about 1 ⁇ 8 to 1 ⁇ 4, preferably about 1 ⁇ 6, of the sphere diameter, which means that the height of this spherical layer is between 1 ⁇ 8 and 1 ⁇ 4 of the sphere diameter, preferably 1 ⁇ 6 of the sphere diameter. Therefore, the part of the solid sphere on the piston side is eliminated.
- the piston rod can adjoin the retaining collar directly.
- the recess is preferably rotationally symmetrical in relation he piston longitudinal axis. Therefore, economical manufacturing by turning is possible. The same advantage results during the production of the transverse grooves if they are formed rotationally symmetrically in relation to the axis of the drive shaft and form a circular ring around the latter.
- the particular advantage of the invention resides in the fact that in order to thread them into the spherical shells the pistons can be set at an angle to the end face of the drive flange which is smaller than the smallest such angle occurring during the operation of the axial piston pump.
- the threading of the pistons can be carried out in blique position which does not occur during the operation of the machine so that the piston heads are retained securely in the spherical shells.
- the difference between the mounting and operating positions of the piston may be enlarged further by mounting grooves being provided in the end face of the drive flange which make threading possible at a minimum angle between the end face of the drive flange and the piston longitudinal axis.
- the pistons preferably have a bore in the longitudinal direction through which hydraulic pressure is led from the cylinder chamber to the spherical dome of the piston head for the purpose of balancing the hydrostatic load on the mounting.
- This load relief is optimized by the fact that, firstly, in order to limit the hydrostatic balancing force, a circumferential groove is formed in the spherical section of the piston head and is surrounded on the outside by an annular spherical layer as a sealing surface, and secondly, a spiral groove is formed in the spherical section of the piston head from the bore as far as the circumferential groove.
- FIG. 1 shows an exemplary embodiment of the invention with the mounting position of the piston
- FIG. 2 shows the exemplary embodiment from FIG. 1 with the piston mounted
- FIG. 3 shows an exemplary embodiment of the piston
- FIG. 4 shows the piston from FIG. 3 in a perspective view
- FIG. 5 shows the mounting of the piston in a sectional illustration.
- FIG. 1 an exemplary embodiment of the invention is shown in the state in which the piston is being mounted and threaded into the associated spherical shell of the drive flange.
- the drive shaft 1 of the variable capacity axial piston machine has a drive flange 2 , on whose end face 3 the pistons 4 are pivotably mounted.
- spherical shells 5 are formed in the end face 3 of the drive flange 2 and accommodate the spherical heads 6 of the displacement pistons 4 .
- the spherical shells 5 go beyond the semisphere. They comprise an angle which is greater than 180° and open towards the pistons with a circular opening 7 which is smaller than the spherical shell diameter.
- the mounting of the piston is made possible by the fact that a transverse groove 11 passing through the circular opening 7 is formed and in the example illustrated, as a circumferential groove forms a circular ring around the longitudinal axis of the drive shaft.
- the specially designed head 6 having the retaining collar 10 is pushed into the spherical shell obliquely in the axial direction through this transverse groove 11 .
- the retaining collar 10 and the groove dimensions are configured in such a way that the mounting of the pistons is possible only with the illustrated highly oblique position of the piston axis in relation to the shaft axis.
- the angle between the end face 3 of the drive flange 2 and the piston axis can be kept particularly small by the fact that mounting grooves 12 running radially from the shaft axis to the spherical shells 5 are provided in the end face 3 of the drive flange 2 , so that an extreme oblique position can be achieved which deviates considerably from the working position of the pistons, in which only smaller oblique positions occur, equivalent to a considerably larger angle between the piston axis and the end face 3 .
- FIG. 2 corresponds to the illustration of FIG. 1 and shows the piston 4 in the mounted position with the spherical head 6 pushed into the spherical shell 5 and an orientation of the pistons corresponding to their working position.
- the circumferential transverse groove 11 and the mounting grooves 12 are formed as in FIG. 1 .
- the construction can also be designed such that the mounting grooves 12 run outwards, for example, the pistons 4 assuming a position during the mounting which is not oriented obliquely towards the shaft axis but outwards, obliquely away from the shaft axis.
- the piston 4 with its head 6 is illustrated detail.
- the piston 4 extends along the piston longitudinal axis 19 .
- the head 6 is basically spherical with a diameter 18 in order to form a spherical joint with the spherical shells in the drive flange.
- the center of the sphere of the piston head 6 and its vertex 13 lie on the piston longitudinal axis 19 .
- the sphere of the head 6 is in this case not formed as a solid body. To a certain extent, it is reduced to a spherical section 9 at the vertex 13 of the piston 4 and to the retaining collar 10 .
- the spherical section at the vertex 13 has, in the direction of the piston longitudinal axis, a height of about 1 ⁇ 5 to 1 ⁇ 4 of the sphere diameter.
- a recess 8 is provided between spherical section 9 and retaining collar 10 .
- This recess 8 has a diameter which is smaller than the diameter of the circular opening 7 of the spherical shell and reaches approximately as far as the central plane of the sphere.
- the retaining collar 10 forms a spherical layer and extends from approximately the central plane of the sphere in the direction of the adjacent piston rod 21 with a spherical layer height of about 1 ⁇ 6 of the sphere diameter.
- the recess 8 is rotationally symmetrical in relation to the piston longitudinal axis 19 . In this way, a circularly cylindrical part with a smaller diameter than the sphere diameter is formed between the spherical section 9 and the retaining collar.
- the piston 4 has a longitudinal bore 20 ( FIG. 5 ) with 35 an opening at the vertex 13 of the piston head 6 , through which the hydraulic pressure from the cylinder chamber is led to the hydrostatic pressure relief face of the surface of the spherical section 9 .
- a spiral groove 16 is introduced there which originates from the opening of the longitudinal bore in the vertex 13 of the spherical section 9 and ends in a circumferential groove 14 which limits the pressure area.
- a sealing surface 15 Following the circumferential groove 14 in the form of a circular ring there is formed a sealing surface 15 , likewise in the form of a circular ring.
- FIG. 5 the piston 4 and the relationships as the piston 6 is pushed into the spherical shell 5 of the drive flange are illustrated once more in section.
- the installation is carried out in the mounting direction 17 at the smallest possible angle ⁇ between the end face 3 of the drive flange 2 and the piston longitudinal axis 19 so that a sufficiently large difference from the maximum oblique position occurring during the operation of the axial piston machine is provided.
- the spherical section 9 can be introduced readily into the spherical shell 5 because of the recess 8 while the retaining collar 10 is threaded through the transverse groove described previously.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention relates to a variable capacity hydrostatic axial piston machine having a drive shaft which has a drive flange having an end face oriented towards displacement pistons in which end face spherical shells for holding substantially spherical piston heads are formed. The calotte of the spherical shells in this case go beyond the semisphere and each have a circular opening with a smaller diameter than the spherical shell diameter. The spherical calotte of the piston heads have a recess having a smaller diameter than that of the circular opening of the spherical shells so that at the vertex of the piston a spherical section making up less than the semisphere and, spaced apart from the latter by the recess a retaining collar having a larger diameter than the circular opening of the spherical shells are formed. A transverse groove is formed in the circular openings of the spherical shells in such a way that the piston head with the retaining collar can be threaded into the spherical shell through the transverse groove and is retained there in the working position of the piston.
Description
- The invention relates to a variable capacity hydrostatic axial piston machine according to the features of
claim 1. - Variable capacity hydrostatic machines which, for example, are used as hydraulic motors, have a cylinder drum which is mounted such that it can rotate about its central longitudinal axis and has cylinder bores distributed on its circumference, in which pistons can be displaced. The cylinder drum is mounted in the housing of the axial piston machine such that it can pivot about a pivot axis running transversely with respect to its axis of rotation, so that the central longitudinal axis of the cylinder drum forms an adjustable angle with the axis of the drive shaft. The pistons are supported in an articulated manner on the drive flange of the drive shaft at the adjustable angle. The spherical piston heads are in this case pivotably mounted in spherical shells, which are formed in the drive flange or in piston shoes fitted there. In order to be able to insert the spherical heads of the pistons into the spherical shells and to hold them axially there during the operation of the machine, they are generally retained by a retaining device which engages behind the spherical heads, for example by a perforated plate screwed on. An axial piston machine of this type is known, for example from
EP 1 251 271 A2. - Also known are spherical joint connections having a spherical shell which encloses an angle which is greater than 180°. In order to be able to insert the spherical head, the latter has lateral flats or recesses, so that it can be inserted at an angle deviating from the working position and is held in the working position by the spherical shell. Spherical joints of this type are described, for example, in DE-OS 2 307 641.
- It is an object of the invention to specify an axial piston machine of the type described at the beginning having improved spherical guidance of the pistons in the drive flange.
- According to the invention, this object is achieved 10 with a variable capacity hydrostatic axial piston machine which has a drive shaft with a drive flange having an end face oriented towards displacement pistons, in which end face spherical shells for holding substantially spherical piston heads are formed. The calotte of the spherical shells in this case go beyond the semisphere and have a circular opening with a smaller diameter than the spherical shell diameter. The spherical calotte of the piston heads have a recess having a smaller diameter than that of the circular opening of the spherical shells so that at the vertex of the piston a spherical section making up less than the semisphere and, spaced apart from the latter by the recess a retaining collar having a larger diameter than the circular opening of the spherical shell are formed. A transverse groove is formed in the circular opening of the spherical shell in such a way that the piston head with the retaining collar can be threaded into the spherical shell through the transverse groove and is retained there in the working position of the piston.
- With the invention, for example a piston shoe can be dispensed with and overall space for a larger domed sphere can be obtained, at the same time a smaller total overall length being achieved. The larger domed sphere in this case permits a high level of balance of the hydrostatic load from the piston force, so that only a small part of the piston force has to be transmitted mechanically via the frictional contact.
- The retaining collar preferably forms a spherical layer, which begins approximately in the middle of the spherical dome of the piston heads and extends approximately from the middle of the spherical dome beyond the latter by about ⅛ to ¼, preferably about ⅙, of the sphere diameter, which means that the height of this spherical layer is between ⅛ and ¼ of the sphere diameter, preferably ⅙ of the sphere diameter. Therefore, the part of the solid sphere on the piston side is eliminated. The piston rod can adjoin the retaining collar directly.
- The recess is preferably rotationally symmetrical in relation he piston longitudinal axis. Therefore, economical manufacturing by turning is possible. The same advantage results during the production of the transverse grooves if they are formed rotationally symmetrically in relation to the axis of the drive shaft and form a circular ring around the latter.
- The particular advantage of the invention resides in the fact that in order to thread them into the spherical shells the pistons can be set at an angle to the end face of the drive flange which is smaller than the smallest such angle occurring during the operation of the axial piston pump.
- Therefore, the threading of the pistons can be carried out in blique position which does not occur during the operation of the machine so that the piston heads are retained securely in the spherical shells. The difference between the mounting and operating positions of the piston may be enlarged further by mounting grooves being provided in the end face of the drive flange which make threading possible at a minimum angle between the end face of the drive flange and the piston longitudinal axis.
- The pistons preferably have a bore in the longitudinal direction through which hydraulic pressure is led from the cylinder chamber to the spherical dome of the piston head for the purpose of balancing the hydrostatic load on the mounting. This load relief is optimized by the fact that, firstly, in order to limit the hydrostatic balancing force, a circumferential groove is formed in the spherical section of the piston head and is surrounded on the outside by an annular spherical layer as a sealing surface, and secondly, a spiral groove is formed in the spherical section of the piston head from the bore as far as the circumferential groove.
- Further features and advantages of the invention emerge from the following figure description.
- In the drawing:
-
FIG. 1 shows an exemplary embodiment of the invention with the mounting position of the piston; -
FIG. 2 shows the exemplary embodiment fromFIG. 1 with the piston mounted; -
FIG. 3 shows an exemplary embodiment of the piston; -
FIG. 4 shows the piston fromFIG. 3 in a perspective view; and -
FIG. 5 shows the mounting of the piston in a sectional illustration. - In
FIG. 1 , an exemplary embodiment of the invention is shown in the state in which the piston is being mounted and threaded into the associated spherical shell of the drive flange. Thedrive shaft 1 of the variable capacity axial piston machine has adrive flange 2, on whoseend face 3 thepistons 4 are pivotably mounted. For this purposespherical shells 5 are formed in theend face 3 of thedrive flange 2 and accommodate thespherical heads 6 of thedisplacement pistons 4. Thespherical shells 5 go beyond the semisphere. They comprise an angle which is greater than 180° and open towards the pistons with acircular opening 7 which is smaller than the spherical shell diameter. - The mounting of the piston is made possible by the fact that a
transverse groove 11 passing through thecircular opening 7 is formed and in the example illustrated, as a circumferential groove forms a circular ring around the longitudinal axis of the drive shaft. The specially designedhead 6 having theretaining collar 10 is pushed into the spherical shell obliquely in the axial direction through thistransverse groove 11. Theretaining collar 10 and the groove dimensions are configured in such a way that the mounting of the pistons is possible only with the illustrated highly oblique position of the piston axis in relation to the shaft axis. The angle between theend face 3 of thedrive flange 2 and the piston axis can be kept particularly small by the fact that mountinggrooves 12 running radially from the shaft axis to thespherical shells 5 are provided in theend face 3 of thedrive flange 2, so that an extreme oblique position can be achieved which deviates considerably from the working position of the pistons, in which only smaller oblique positions occur, equivalent to a considerably larger angle between the piston axis and theend face 3. -
FIG. 2 corresponds to the illustration ofFIG. 1 and shows thepiston 4 in the mounted position with thespherical head 6 pushed into thespherical shell 5 and an orientation of the pistons corresponding to their working position. The circumferentialtransverse groove 11 and themounting grooves 12 are formed as inFIG. 1 . Alternatively, the construction can also be designed such that themounting grooves 12 run outwards, for example, thepistons 4 assuming a position during the mounting which is not oriented obliquely towards the shaft axis but outwards, obliquely away from the shaft axis. - In
FIGS. 3 and 4 , thepiston 4 with itshead 6 is illustrated detail. Thepiston 4 extends along the pistonlongitudinal axis 19. Thehead 6 is basically spherical with adiameter 18 in order to form a spherical joint with the spherical shells in the drive flange. The center of the sphere of thepiston head 6 and itsvertex 13 lie on the pistonlongitudinal axis 19. The sphere of thehead 6 is in this case not formed as a solid body. To a certain extent, it is reduced to aspherical section 9 at thevertex 13 of thepiston 4 and to theretaining collar 10. In the example illustrated the spherical section at thevertex 13 has, in the direction of the piston longitudinal axis, a height of about ⅕ to ¼ of the sphere diameter. Arecess 8 is provided betweenspherical section 9 and retainingcollar 10. Thisrecess 8 has a diameter which is smaller than the diameter of thecircular opening 7 of the spherical shell and reaches approximately as far as the central plane of the sphere. Theretaining collar 10 forms a spherical layer and extends from approximately the central plane of the sphere in the direction of theadjacent piston rod 21 with a spherical layer height of about ⅙ of the sphere diameter. Therecess 8 is rotationally symmetrical in relation to the pistonlongitudinal axis 19. In this way, a circularly cylindrical part with a smaller diameter than the sphere diameter is formed between thespherical section 9 and the retaining collar. - The
piston 4 has a longitudinal bore 20 (FIG. 5 ) with 35 an opening at thevertex 13 of thepiston head 6, through which the hydraulic pressure from the cylinder chamber is led to the hydrostatic pressure relief face of the surface of thespherical section 9. In order that the pressure can propagate on the pressure relief face aspiral groove 16 is introduced there which originates from the opening of the longitudinal bore in thevertex 13 of thespherical section 9 and ends in acircumferential groove 14 which limits the pressure area. Following thecircumferential groove 14 in the form of a circular ring there is formed a sealingsurface 15, likewise in the form of a circular ring. - In
FIG. 5 , thepiston 4 and the relationships as thepiston 6 is pushed into thespherical shell 5 of the drive flange are illustrated once more in section. The installation is carried out in the mountingdirection 17 at the smallest possible angle α between theend face 3 of thedrive flange 2 and the pistonlongitudinal axis 19 so that a sufficiently large difference from the maximum oblique position occurring during the operation of the axial piston machine is provided. Thespherical section 9 can be introduced readily into thespherical shell 5 because of therecess 8 while the retainingcollar 10 is threaded through the transverse groove described previously. The result is then an operating angle complementary to the angle α of 90° minus a minus a safety margin of at least 10° so that in the working position during the operation of the axial piston machine the piston is retained securely by the spherical shell going beyond the semisphere.
Claims (10)
1. Variable capacity hydrostatic axial piston machine having a drive shaft (1) which has a drive flange (2) having an end face (3) oriented towards displacement pistons (4) in which end face spherical shells (5) for holding substantially spherical piston heads (6) are formed:
the calotte of the spherical shells (5) going beyond the semi sphere and each having a circular opening (7) with a smaller diameter than the spherical shell diameter;
the spherical calotte of the piston heads (6) having a recess (8) having a smaller diameter than that of the circular opening (7), so that at the vertex (13) of the piston, a spherical section (9) making up less than the semisphere and spaced apart from the latter by the recess (8), a retaining collar (10) having a larger diameter than the circular opening (7) of the spherical shells (5) are formed; and
a transverse groove (11) being formed in the circular openings (7) of the spherical shells (5) in such a way that the piston head (6) with the retaining collar (10) can be threaded into the spherical shell (5) through the transverse groove (11) and is retained there in the working position of the piston (4).
2. Axial piston machine according to claim 1 , in which the retaining collar (10) forms a spherical layer which begins approximately in the central plane of the spherical dome of the piston heads (6).
3. Axial piston machine according to claim 1 , in which the retaining collar (10) forms a spherical layer which extends approximately from the central plane of the spherical dome beyond the latter by about ⅛ to ¼, preferably about ⅙ of the sphere diameter.
4. Axial piston machine according to claim 1 , in which the recess (8) is rotationally symmetrical in relation to the piston longitudinal axis (19).
5. Axial piston machine according to claim 1 , in which the transverse grooves (11) of the spherical shells form a circular ring around the axis of the drive shaft (1).
6. Axial piston machine according to claim 1 , in which, in order to thread them into the spherical shells (5) the pistons (6) can be set at an angle (α) to the end face (3) of the drive flange (2) which is smaller than the smallest such angle occurring during the operation of the axial piston pump.
7. Axial piston machine according to claim 6 , in which mounting grooves (12) are provided in the end face (3) of the drive flange (2) which make threading possible at a minimum angle (α) between the piston longitudinal axis (19) and the end face (3) of the drive flange (2).
8. Axial piston machine according to claim 1 , in which the pistons (6) have a bore (20) in the longitudinal direction through which hydraulic pressure is led from the cylinder chamber to the spherical section (9) of the piston head (6) for the purpose of balancing the hydrostatic load on the mounting.
9. Axial piston machine according to claim 8 in which in order to limit the hydrostatic balancing force a circumferential groove (14) is formed in the spherical section (9) of the piston head (6) and is surrounded on the outside by an annular spherical layer as a sealing surface (15).
10. Axial piston machine according to claim 9 in which a spiral groove (16) is formed in the spherical section (9) of the piston head (6) from the bore (20) as far as the circumferential groove (14).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006019884A DE102006019884B4 (en) | 2006-04-28 | 2006-04-28 | Hydrostatic axial piston machine in bent axis design |
DEDE102006019884.0 | 2006-04-28 |
Publications (1)
Publication Number | Publication Date |
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US20070251377A1 true US20070251377A1 (en) | 2007-11-01 |
Family
ID=38542353
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/736,996 Abandoned US20070251377A1 (en) | 2006-04-28 | 2007-04-18 | Variable capacity hydrostatic axial piston machine |
Country Status (2)
Country | Link |
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US (1) | US20070251377A1 (en) |
DE (1) | DE102006019884B4 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104153986A (en) * | 2014-07-21 | 2014-11-19 | 浙江沃尔液压科技有限公司 | Axial plunger hydraulic pump for hydraulic return stroke |
IT201900001613A1 (en) * | 2019-02-05 | 2020-08-05 | Dana Motion Sys Italia Srl | Piston for axial piston hydraulic machines. |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021202936A1 (en) | 2021-03-25 | 2022-09-29 | Robert Bosch Gesellschaft mit beschränkter Haftung | Axial piston machine with ball joint made from rotationally symmetrical individual parts |
DE102021212098A1 (en) | 2021-10-27 | 2023-04-27 | Robert Bosch Gesellschaft mit beschränkter Haftung | Sliding shoe for an axial piston machine and axial piston machine therewith |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3196801A (en) * | 1962-10-11 | 1965-07-27 | Lucas Industries Ltd | Fluid pumps or motors |
US4920860A (en) * | 1987-09-18 | 1990-05-01 | Volvo Hydraulik Ab | Device for biasing a cylinder drum of a variable-displacement axial piston machine against an associated slide valve member |
US6343888B1 (en) * | 1997-03-26 | 2002-02-05 | Brueninghaus Hydromatik Gmbh | Method for the production of a ball jointed connection |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH445299A (en) * | 1964-12-04 | 1967-10-15 | Thoma Hans Prof Ing Dr | Axial piston machine with slide shoe and swash plate |
DE2307641A1 (en) * | 1973-02-16 | 1974-08-22 | Bosch Gmbh Robert | BALL JOINT |
DE4214765A1 (en) * | 1992-05-04 | 1993-11-11 | Sachsenhydraulik Gmbh | Piston-slipper connection for axial piston swashplate pump - uses ball with flattened surfaces attached to neck of slipper |
DE4429053C1 (en) * | 1994-08-16 | 1995-11-02 | Brueninghaus Hydromatik Gmbh | Ball head to support piston of hydrostatic piston machine on lifting body |
DE10119236C1 (en) * | 2001-04-19 | 2002-12-12 | Brueninghaus Hydromatik Gmbh | Axial piston machine with an inclined axis design, with a swivel angle sensor |
-
2006
- 2006-04-28 DE DE102006019884A patent/DE102006019884B4/en not_active Expired - Fee Related
-
2007
- 2007-04-18 US US11/736,996 patent/US20070251377A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3196801A (en) * | 1962-10-11 | 1965-07-27 | Lucas Industries Ltd | Fluid pumps or motors |
US4920860A (en) * | 1987-09-18 | 1990-05-01 | Volvo Hydraulik Ab | Device for biasing a cylinder drum of a variable-displacement axial piston machine against an associated slide valve member |
US6343888B1 (en) * | 1997-03-26 | 2002-02-05 | Brueninghaus Hydromatik Gmbh | Method for the production of a ball jointed connection |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104153986A (en) * | 2014-07-21 | 2014-11-19 | 浙江沃尔液压科技有限公司 | Axial plunger hydraulic pump for hydraulic return stroke |
IT201900001613A1 (en) * | 2019-02-05 | 2020-08-05 | Dana Motion Sys Italia Srl | Piston for axial piston hydraulic machines. |
US11092174B2 (en) | 2019-02-05 | 2021-08-17 | Dana Motion Systems Italia S.R.L. | Pistone for hydraulic machines with axial pistons |
Also Published As
Publication number | Publication date |
---|---|
DE102006019884B4 (en) | 2008-04-17 |
DE102006019884A1 (en) | 2007-10-31 |
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