EP3987183A1 - Radialkolbenmaschine mit einem kugelkolben - Google Patents
Radialkolbenmaschine mit einem kugelkolbenInfo
- Publication number
- EP3987183A1 EP3987183A1 EP20735095.0A EP20735095A EP3987183A1 EP 3987183 A1 EP3987183 A1 EP 3987183A1 EP 20735095 A EP20735095 A EP 20735095A EP 3987183 A1 EP3987183 A1 EP 3987183A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- spherical
- radial
- radial piston
- piston machine
- 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.)
- Withdrawn
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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0408—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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0413—Cams
-
- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
-
- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
- F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
- F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks
Definitions
- the invention relates to a radial piston machine with pistons which perform a stroke movement in a cylinder.
- radial piston machines can either be used as
- Work machines serve, for example, as a pump, or as a motor.
- cylinders are arranged in a rotor and a piston element is arranged in each cylinder, which is connected to a guide element, the guide element running on a sliding surface and thereby forcing the piston element to move.
- Hydraulic displacement machines which include radial piston machines, work according to the displacement principle. They can therefore be operated both as pumps and as motors if the pressure medium flow is controlled accordingly. Pumps and motors usually have the same structural design.
- radial piston machines In the case of radial piston machines, a distinction can then still be made between radial piston machines that are acted upon from the inside and those that are acted upon from the outside.
- radial piston machines with internally applied pressure the working spaces of the cylinders are filled with a pressure medium and emptied from the inside, for example via a radial hollow shaft.
- the cylinders rotate around the radial hollow shaft.
- pistons arranged in the cylinders are supported on an outer ring, which is why they are acted upon on the inside
- Radial piston machines are also referred to as externally supported radial piston machines.
- the outer ring on which the working pistons are supported is in an eccentric position to the hollow shaft.
- Radial piston machines are therefore also referred to as internally supported radial piston machines.
- a drive shaft has a
- a cylinder star in which a plurality of radially aligned cylinders are arranged in a star shape.
- the cylinder star is rotatably mounted on a control pin.
- Pistons arranged radially in the cylinders of the cylinder star are supported by hydrostatically relieved sliding shoes on a cam ring mounted eccentrically to the cylinder star.
- the piston and sliding shoe are connected to each other by a ball joint and tied with a snap ring. Alternatively, the ball joint can also be flanged.
- An oil flow is in fluid connection with the cylinders of the cylinder star via inlet and outlet channels in the housing.
- EP 0 011 145 B1 discloses in particular a slide shoe for hydrostatic
- Ring piston machines in which a shaft with a ball head is mounted in a spherical surface of a piston.
- the spherical surface is formed in a stepped bore penetrating the piston in the longitudinal direction.
- the piston itself is arranged in a cylinder bore located in a cylinder body.
- a snap ring holds the piston and shoe together.
- cylindrical pistons in particular are used.
- the pistons In order to reduce the friction of the pistons on the inner walls of the cylinder, the pistons must be designed to be long in relation to their diameter. This increases the volume of such a radial piston machine, since the cylinder star must be designed with a correspondingly sufficient diameter in order to provide the appropriate installation space for the cylinders.
- the object of the invention is therefore to design a radial piston machine in such a way that the friction is reduced. Another object of the invention is to increase the permissible tensile force on the piston or to extend the service life of a piston before a defect occurs.
- the piston element is spherical at least in the region of the piston element which seals the inner walls of the cylinder during the stroke movements.
- the spherical design of the piston element results in a sealing area which is ring-shaped, that is to say forms a closed circular line.
- a closed circular line causes far lower frictional forces than a flat seal with a cylindrical piston.
- the manufacturing quality of a spherical piston element can be selected to be lower than that of a longitudinal piston according to the prior art in order to achieve the same purpose.
- the rotor diameter can be selected to be smaller with the same output, so that this results in a more compact design of the
- Radial piston machine results. At the same time, a higher working pressure can also be selected because the weak point of the radial piston machine is no longer determined by an articulated connection.
- the round bottom flask therefore eliminates the limitation of the internal pressure in the housing caused by the tensile, compressive and lateral forces acting on a joint.
- piston machines with longitudinal pistons there were limitations with regard to internal housing pressures or dynamic pressures in an external leakage oil line, which were caused, for example, by the elevated position of the hydraulic tank, filters or coolers in the leakage oil line. With the elimination of such a restriction, that expands
- the surface of the segmented spherical piston that comes into contact with the inner walls of the cylinder is a symmetrical spherical zone.
- a spherical zone is the curved outside of a spherical disk or a spherical ring, for example.
- a spherical disk, also known as a spherical layer, is obtained as the middle part of a solid sphere when the solid sphere is cut into three parts by two parallel planes. If the parallel planes are on different sides of the
- a symmetrical spherical zone can also be obtained by a radial drilling through a sphere.
- a tilt angle ⁇ of the spherical zone on both sides of approximately 9 ° resulted on the basis of the selected geometric conditions.
- a tilt angle would be advantageous a of about 10 °, better 12 ° should be selected.
- the ratio of the thickness of the spherical disk or the height H of the spherical disk to the diameter di ⁇ that of the spherical disk corresponds to twice the tangent function of the tilt angle a. At 12 ° on both sides, this results in a ratio of the thickness H of the spherical disk to the diameter di ⁇ of the spherical disk of approximately 0.4.
- tilt angle a may also be required in individual cases, or a small tilt angle a may also be sufficient. Tilt angles a of up to 20 ° seem to be technically sensible or achievable.
- the at least partially spherical piston element can advantageously be connected to the guide element via a connecting element, the
- Connecting element is rigidly connected to the piston and / or rigidly to the sliding element. Due to the spherical section of the piston element, the spherical
- Piston element as long as its movement is not restricted by a forced guidance, or the connecting element does not come into contact with the cylinder walls, all degrees of freedom to rotate in the cylinder, for example, to perform a pitch, yaw or roll movement.
- the forced movement of the piston element is restricted to a nodding movement and a lifting movement.
- Piston element can be run. The losses of the piston machine and the wear within the piston guide in the cylinder are reduced.
- the sliding shoe has a rounded contour that is matched to the pivot angle and the inside diameter of the cylinder.
- the contour of the sliding shoe only needs to be able to map the kinematic pivoting movement of the sliding shoe due to the design.
- the piston according to the invention with at least partially spherical piston element can be produced, for example, by means of turning, milling or grinding. Alternatively, production, also of individual parts, is the same
- the piston element can of course also be connected to the connecting element by a joint and / or the connecting element can be connected to the guide element by a joint.
- Act radial piston machine or an externally loaded radial piston machine In the case of an internally acted upon radial piston machine, the guide elements run on a cam ring which is arranged eccentrically to the radial axis of the cylinder carrier. In the case of the externally loaded radial piston machine, the guide elements run on an eccentric shaft rotating in the interior of the cylinder carrier eccentrically to the center of the cylinder carrier.
- FIG. 1 shows a radial piston machine with the round piston according to the invention
- 3A, 3B and 3C show a section from a radial piston machine
- the invention relates to a novel piston for a radial piston machine, wherein the radial piston machine, apart from the novel piston, can be a radial piston machine according to the prior art.
- Due to the shape of the piston it is referred to below as a round bottom flask, although the part of the round bottom flask which comes into contact with an inner wall of a hollow cylinder, strictly speaking, only a segment of a sphere must correspond. In this sense, when a spherical shape is spoken of in the following for linguistic simplification, it is intended to mean only a section
- FIG. 1 shows a simplified view of a radial piston machine 1 loaded on the inside and supported on the outside, partially in section.
- this radial piston machine can be operated both as a pump and as a motor. The following is representative of both
- Radial piston pump 1 has a housing 10 which is approximately cup-shaped and is closed by a housing cover, not shown.
- a cam ring 12 which can be displaced in an adjustment direction 3 and which is mounted with its side faces between the shoulders of the housing bottom and the housing cover with appropriate play. Due to the sectional view, only the side surface 13 of the cam ring 12 facing the viewer is visible in FIG. 1, which when the housing 10 is closed comes to rest on the inside of the housing cover. The shoulders of the housing bottom are covered by the cam ring 12 in this illustration, or are omitted for the sake of clarity.
- the inner circumference of the cam ring 12 forms a sliding surface 14 for sliding shoes 22, on which ball pistons 21 are supported and which are movably guided in radially extending bores 5 of a cylinder carrier. Since the cylinder carrier is set in rotary motion in this design, the cylinder carrier is referred to below as rotor 16. Due to the
- piston bore 5 When these bores interact with the spherical pistons 21, these bores are referred to below as piston bore 5.
- the piston bores 5 are distributed rotationally symmetrically around the radial axis 17 of the rotor 16.
- the number of piston bores partly depends on the size of the rotor 16 or on the displacement or absorption volume of the radial piston pump 1. In the example shown here of a radial piston pump with a displacement or Displacement volume of 19 cm 3 / rev at a maximum operating pressure of 350 bar, seven piston bores 5 are provided in the rotor 16.
- the rotor 16 is fixed in a control pin bore of the housing 10
- control pin 18 is set in rotation by a drive shaft.
- that generated by the spherical piston 21 is
- the spherical piston 21 seals a working space of the
- Radial piston machine 1 from the interior 11 of the radial piston machine 1, the working space within the piston bore 5 extending from the spherical piston 21 as an extension of the piston bore in the direction of the control pin 18 to the control pin 18.
- the control pin bore and the drive shaft are covered in FIG. 1 by the control pin 18, or on the cut-off side of the diagram, and are therefore not visible.
- Ball piston 21 and slide shoe 22 are connected to one another by means of a piston rod 23.
- the piston rod 23 can also be designed as a connecting rod, that is to say the connecting rod can be movably connected to the spherical piston 21 via a joint arranged on the spherical piston 21.
- the piston rod 23 or the connecting rod can be movably connected to the sliding shoe 22 by a joint arranged on the sliding shoe 22.
- the spherical shape of the spherical piston 21 is used not only as a seal between the working space and the interior 11 of the radial piston machine 1, but also as the sole joint.
- This has the particular advantage that a weakening of the combination of ball piston 21, piston rod 23 and slide shoe 22 by joints is avoided.
- the piston rod 23 can be designed as a taper of the round bottom flask 21 such that the piston rod achieves a high level of strength.
- the spherical shape, or the spherical segment shape, allows the spherical piston 21 to move within the piston bore 5, positively guided by the slide shoe 22 in particular to execute a limited tilting movement in or against the direction of rotation of the rotor 16 in its plane of rotation.
- the tilting movement of the round piston 21 is limited by the piston rod 23, which can come to a stop on the piston bore walls, in particular the piston bore openings that point towards the stroke ring 12.
- the ball piston 21 is not subjected to any lateral movements.
- the cam ring 12 can be displaced in the interior space 11 transversely to the control pin 18 for the purpose of changing the delivery rate by means of two actuating pistons 31, 32 in the adjustment direction 3.
- the two actuating pistons 31, 32 act at two diametrically opposite points on the
- an eccentric, parallel to the central axis of the control pin 18 longitudinally extending first low-pressure channel 41 and a second low-pressure channel 42, each of which opens into a first circumferential groove, hereinafter referred to as low-pressure slot 45, on the control pin 21 are formed for the supply of a pressure medium. Furthermore, an eccentric, parallel to the central axis of the control pin 21, a first high-pressure channel 43 and a second one are in each case for the discharge of the pressure medium
- High-pressure channel 44 is formed, each of which opens into a second circumferential groove, hereinafter referred to as high-pressure slot 46, on the control pin 21.
- the low-pressure slot 45 and the high-pressure slot 46 are located in the mouth area of the piston bore 5 of the rotor 16 that accommodates the round pistons 21 a high pressure connection of the radial piston pump 1. low pressure connection and
- the high pressure connection of the radial piston pump 1 are not visible in this drawing because they are located on the back of the housing base from the viewer.
- two low-pressure channels 41, 42 and two high-pressure channels 43, 44 were selected because this, in conjunction with a known special geometric configuration of the control pin 18, offers advantages in terms of flow technology. To that To fulfill the basic principle of the radial piston machine 1, however, a single low-pressure channel 41 and a single high-pressure channel 43 would be sufficient.
- the ball pistons 21 are entrained in the piston bores 5 in the direction of the rotational movement. Due to the rotary movement of the rotor 16, a centrifugal force acts on the spherical pistons 21 guided in the piston bores 5, whereby the respective spherical piston 21 is pressed radially outward in the piston bores 5 until the sliding shoes 22 of the spherical piston 21 with their ends facing away from the control pin 18 come to rest on the stroke ring 12.
- the term "outward” denotes a direction starting from the axis of rotation 17 of the rotor 16 from the
- the axis of rotation 17 of the rotor 16 points away, while the expression “inward” denotes a direction which points in the direction of the axis of rotation 17 of the rotor 16.
- the term “outside” denotes a relative position of an object with a greater radial distance from the axis of rotation 17 of the rotor 16 than an object which has a radially smaller distance from the axis of rotation 17 of the rotor 16.
- the distance D between the outside of the rotor 16 and the inside of the cam ring 12 is in each position of the Rotor 16 the same.
- the radial distance between the spherical pistons 21 with respect to the axis of rotation 17 does not change during a rotary movement of the rotor 16, so that the spherical pistons 21 do not perform a stroke within the respective piston bore 5.
- the distance D between the rotor 16 and the cam ring 12 is changed cyclically when the rotor 16 rotates within the cam ring 12 .
- This change in distance has the effect that when the distance D between the cam ring 12 and the rotor 16 decreases, the sliding surface 14 of the cam ring 12 exerts a counterforce on the sliding shoes 22, which presses the spherical pistons 21 inward against the centrifugal force.
- Compression phase is called.
- the low-pressure slot 45 is arranged on the control pin 18 such that the low-pressure slot 45 and thus also the first and second low-pressure channels 41, 42 are in fluid connection with the respective spherical piston 21 in the expansion phase.
- the lifting movement of the spherical piston 21 radially outward therefore generates a suction effect which sucks in the pressure medium applied to the low-pressure connection and fills the working space of the piston bore 5 with pressure medium.
- the high-pressure slot 46 is arranged on the control pin 21 in such a way that during the compression phase the
- High pressure slot 46 and thus also the first and second high pressure channels 43, 44 are in fluid connection with the respective spherical piston 21. The lifting movement of the
- Ball piston 21 radially inward therefore produces a pressure effect which the im
- Working chamber of the relevant piston bore 5 pushes accumulated pressure medium through the high-pressure slot 46 into the high-pressure channels 43, 44.
- the cyclical stroke movement of the ball piston 21 thus forces a pressure medium flow from the low-pressure to the high-pressure channel.
- the operating mode as a motor there is a pressure medium flow from the high pressure to the low pressure channel.
- the radial piston machine is given a pressure energy in pumping mode by a drive torque, or pressure energy is withdrawn and converted into a motor mode
- FIG. 2 shows a piston element 2 which comprises the spherical piston 21 and the sliding shoe 22, which are rigidly connected to one another by means of the piston rod 23.
- a bore 29 runs through a longitudinal axis of the spherical piston 21, the piston axis 20, through which during operation of the piston machine 1 pressure medium, which is located in the piston bore 5, is pressed onto a shoe sole 26.
- the sliding shoe sole 26 is thereby forced into a hydrostatic equilibrium, in which a friction-reducing film of pressure medium is formed between the sliding sole and sliding surface 14.
- the sliding shoe sole 26 is adapted to the geometry of the sliding surface 14, that is to say it is curved outward. Furthermore, as shown in FIG. 3, the sliding shoe 22 has a front sliding shoe end 27 relative to its piston axis 20, viewed in the direction of rotation, and a rear sliding shoe end 28 opposite to this.
- the spherical piston 21 could assume a completely spherical shape.
- An ideally perfect spherical shape is required, however, only at the points of the spherical piston 21 which come into contact with the piston bore wall 51 in order to seal the piston bore space, or, to be more precise, almost come into contact.
- the great circle of the spherical piston 21, which is perpendicular to the piston axis 20, is referred to below as the center circle 24.
- the extension of the plane spanned by the central circle 24 cuts the piston bore beyond the central circle 24 in a cutting circle, which is referred to below as the sealing circle because it defines the working space of the piston bore 5 with respect to the interior space 11 of the piston engine 1 actually closes.
- the sum of all sealing circles that can form during one full revolution defines a spherical zone 250, that is, the outer circumference of a spherical disk in which the at least partially spherical piston element 71 must correspond to an ideal spherical shape.
- the diameter di ⁇ of the center circle 24 is selected to be slightly smaller than the diameter of the piston bore 5.
- a center circle 24 that is 10 ⁇ m smaller, for example results in a central position of the center circle 24 and piston bore wall 51 all around a clearance of 5pm between working circle and center circle. This results from the viscosity of the pressure medium A sufficient seal between the working space and the interior 11 of the piston machine 1.
- the person skilled in the art will of course select the clearance between the spherical piston 21 and the piston bore wall 51 so that it is ideally suited for the given dimensions and the particular application.
- 3A shows the spherical piston 21 at its outer dead point, that is to say during the transition from the expansion phase to the compression phase. At the outer dead center is through the
- the spherical piston 21 is generally aligned at its outer dead center in such a way that the piston axis 20 with the
- Piston bore axis 50 more or less coincides.
- the geometry of the individual elements of the annular piston machine 1 are selected so that the center circle 24 of the spherical piston 21 is close to the outer piston bore opening 52, but still sufficiently deep in the piston bore wall 51 to ensure that the piston 2 is safely guided within the piston bore 5 and a To ensure sealing between piston bore wall 51 and center circle 24.
- the piston 2 is then rotated further by the forces acting from the piston bore wall 51 on the center circle 24 of the spherical piston 21
- the compression phase is tilted about its center point Z opposite to the direction of rotation 15 of the rotor 16.
- the center circle 24 rotates on the piston bore wall 51 facing away from the direction of rotation in the direction of the outer one
- the center circle 24 of the spherical piston 21 thus loses contact with the piston bore wall 51.
- the spherical shape of the spherical piston 21 now creates a new great circle of the
- the center point of each sealing circle is identical to the center point Z of the spherical piston 21.
- Compression phase i.e. at the transition from outer dead center AT to inner
- Dead center IT reverses these relationships and the tilt angle a hurries
- Tilting movement has its greatest extent on the one hand, as shown in FIG. 3B, in approximately half of the movement between inner dead center IT and outer dead center AT of piston 2, or in approximately half of the movement of piston 2 between the outer ones
- FIG. 3C shows the spherical piston 2 at its inner dead center when the distance between the cam ring 12 and the rotor 16 has reached a minimum distance D min .
- a piston head 210 which adjoins the partially spherical piston 21 on the side facing away from the piston rod 23, is essentially frusto-spherical, so that the piston head 210 at the inner dead center IT largely adjoins a funnel-shaped transition from the piston bore 5 can adapt to the control pin 18. This advantageously minimizes the dead volume in the inner dead center IT.
- this angle a is also equal to the angle a between the plane of the sealing circle and the plane of the center circle.
- the spherical piston 21 is designed symmetrically so that the spherical section or the spherical zone 250, as shown in FIG. 2, comprises at least an angle between -a and + a. Furthermore, depending on the selected geometry of the round piston machine 1 and the piston 2, the tapering at the position of the piston rod 23 is to be selected so that the piston rod does not come into contact with the piston bore walls 51 or the rotor 16 during operation to prevent damage to the piston bore rod 23 , or rotor 16 and piston bore walls 51 to avoid.
- Fig. 4 shows the basic structure of an internally supported radial piston machine 6, in which
- Low-pressure channels and high-pressure channels are arranged on the outside 66 of a piston carrier 61, which in this case is stationary.
- the formation of the low pressure channels and high pressure channels in an internally supported radial piston machine 6 are the
- the piston carrier 61 forms a receptacle for a plurality of piston bores 5, which are arranged radially around a center point 60 of the piston carrier 61 at the same distance from one another, so that the extensions of the longitudinal axes 50 of the piston bores 5 intersect at the center point 60 of the piston carrier 61.
- piston carrier 61 is designed as a cavity in which an eccentric shaft 63 rotates about the piston carrier center point 60.
- the eccentric center point E is located at a distance D from the piston carrier center point 60, as a result of which the eccentric center point E rotates on a circular path 64 around the piston carrier center point 60.
- a round piston according to the invention is arranged, which is essentially formed from a spherical piston element 71, a piston rod 73 and a sliding shoe 72.
- Each round bottom flask is served by one each
- the restoring element which in this exemplary embodiment are designed as helical springs 74, is pressed in the direction of the eccentric shaft 63 or the eccentric center point E, that is to say into the interior of the radial piston machine.
- Radial piston machine 6 seals the at least partially spherical
- Piston element 71 from the working space of the radial piston machine 6 inwards.
- the working space in which the pressure medium is supplied or discharged is thus the part of the piston bore 5 that extends between the outer periphery 66 of the
- Piston carrier 61 and the at least partially spherical piston element 71 extends.
- the outer circumference of the eccentric shaft 63 forms a sliding surface 65 on which the sliding shoes 72 of the round pistons 7 are supported with sliding soles 76. Since the sliding surface 65 of the eccentric shaft is convex in this embodiment, the
- Shoe soles 76 correspondingly concave. During one full revolution of the eccentric shaft 63, two periodic stroke movements are forced on the ball piston 7 by the sliding shoes 72 sliding on the eccentric shaft 63, a first one
- the round pistons 7 lead in the expansion and Compression phases from a tilting movement. Due to the piston element 71, which is at least partially spherical, a circular sealing circle between an inner wall 51 of the piston bore 5 and a spherical zone 75 of the round piston 7 is maintained at all times. In this exemplary embodiment, too, a play between the ball piston 7 and the piston bore wall 51 prevents the ball piston 7 from jamming.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102019116680.2A DE102019116680A1 (de) | 2019-06-19 | 2019-06-19 | Radialkolbenmaschine mit einem Kugelkolben |
PCT/EP2020/066976 WO2020254501A1 (de) | 2019-06-19 | 2020-06-18 | Radialkolbenmaschine mit einem kugelkolben |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3987183A1 true EP3987183A1 (de) | 2022-04-27 |
Family
ID=71266619
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20735095.0A Withdrawn EP3987183A1 (de) | 2019-06-19 | 2020-06-18 | Radialkolbenmaschine mit einem kugelkolben |
Country Status (5)
Country | Link |
---|---|
US (1) | US20220349394A1 (de) |
EP (1) | EP3987183A1 (de) |
CN (1) | CN113994091A (de) |
DE (1) | DE102019116680A1 (de) |
WO (1) | WO2020254501A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022128195A1 (de) | 2022-10-25 | 2024-04-25 | Voith Patent Gmbh | Hydraulische Radialkolbenmaschine |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH445199A (de) * | 1966-07-29 | 1967-10-15 | Paschke Hanns Dieter | Umlaufkolbenmotor |
SE312072B (de) * | 1968-07-23 | 1969-06-30 | Asea Ab | |
DE2233053A1 (de) * | 1972-07-06 | 1974-03-28 | Mathias Prof Dipl Ing Ott | Radialkolbenmaschine |
US4926744A (en) * | 1974-11-29 | 1990-05-22 | Karl Eickmann | Radial piston hydraulic machine with piston having twelve circumferential fluid bearing pockets |
DE2849042A1 (de) | 1978-11-11 | 1980-05-22 | Bosch Gmbh Robert | Gleitschuh fuer hydrostatische kolbenmaschinen |
DE3219378A1 (de) * | 1981-05-29 | 1982-12-16 | Alfred Teves Gmbh, 6000 Frankfurt | Radialkolbenmaschine, insbesondere pumpe |
DE3147240A1 (de) * | 1981-11-28 | 1983-06-09 | Mannesmann Rexroth GmbH, 8770 Lohr | Radialkolbenmaschine |
DE58906590D1 (de) * | 1989-06-08 | 1994-02-10 | Luk Fahrzeug Hydraulik | Radialkolbenmaschine. |
FR2693511B1 (fr) * | 1992-07-10 | 1995-01-20 | Barmag Luk Automobiltech | Pompe à pistons radiaux. |
DE19818396C2 (de) * | 1998-04-24 | 2001-08-16 | Bosch Gmbh Robert | Radialkolbenpumpe mit asymmetrischen Gleitsteinen |
US6834575B2 (en) * | 2000-04-21 | 2004-12-28 | Jurij Manfreda | Piston assembly for a radial piston hydraulic motor |
DE102007030132A1 (de) * | 2007-06-29 | 2009-01-02 | Robert Bosch Gmbh | Radialkolbenmaschine |
US20120111185A1 (en) * | 2009-05-26 | 2012-05-10 | Husco International, Inc | Compact Eccentric Radial Piston Hydraulic Machine |
DE102012210430A1 (de) * | 2012-06-20 | 2013-12-24 | Zf Friedrichshafen Ag | Radialkolbenmaschine |
-
2019
- 2019-06-19 DE DE102019116680.2A patent/DE102019116680A1/de not_active Withdrawn
-
2020
- 2020-06-18 CN CN202080043421.6A patent/CN113994091A/zh not_active Withdrawn
- 2020-06-18 EP EP20735095.0A patent/EP3987183A1/de not_active Withdrawn
- 2020-06-18 WO PCT/EP2020/066976 patent/WO2020254501A1/de active Search and Examination
- 2020-06-18 US US17/618,267 patent/US20220349394A1/en not_active Abandoned
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US20220349394A1 (en) | 2022-11-03 |
DE102019116680A1 (de) | 2020-12-24 |
CN113994091A (zh) | 2022-01-28 |
WO2020254501A1 (de) | 2020-12-24 |
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