EP1855002A1 - Hydraulisches Gerät - Google Patents

Hydraulisches Gerät Download PDF

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Publication number
EP1855002A1
EP1855002A1 EP06113728A EP06113728A EP1855002A1 EP 1855002 A1 EP1855002 A1 EP 1855002A1 EP 06113728 A EP06113728 A EP 06113728A EP 06113728 A EP06113728 A EP 06113728A EP 1855002 A1 EP1855002 A1 EP 1855002A1
Authority
EP
European Patent Office
Prior art keywords
piston
drum plate
sleeve
hydraulic device
sleeves
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Withdrawn
Application number
EP06113728A
Other languages
English (en)
French (fr)
Inventor
Peter Augustinus Johannes Achten
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Innas BV
Original Assignee
Innas BV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Innas BV filed Critical Innas BV
Priority to EP06113728A priority Critical patent/EP1855002A1/de
Publication of EP1855002A1 publication Critical patent/EP1855002A1/de
Withdrawn legal-status Critical Current

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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
    • F04B1/2035—Cylinder barrels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure

Definitions

  • the invention relates to a hydraulic device as described in the not pre-published application PCT/NL2005/050062 of the same applicant.
  • This document describes the hydraulic device with piston sleeves that are arranged around pistons and that rotate at a high speed. At high rotation speed of the pistons there is a risk that the sleeves tilt on the drum plate due to the centrifugal force on the sleeve. This is not allowable as this causes leakage and reduction in efficiency.
  • first spring means in order to clamp the sleeve against the drum plate. Although this measure reduces the leakage between the sleeves and the drum plate and improves efficiency it is not sufficient for high rotation speeds such as above 5000 rotations per minute.
  • the hydraulic device is in accordance with claim 1. It has been found that this combination of first spring means and second spring means ensures that the sleeves do not tilt against the drum plate surface so that there is no leakage between the sleeves and the drum plate.
  • the hydraulic device is according to claim 2.
  • the second spring means directly compensate the centrifugal forces on the sleeves.
  • the hydraulic device is according to claim 3. In this way stability of the sleeve is ensured, as otherwise the second spring means would tilt the sleeves at low rotation speeds.
  • the hydraulic device is according to claim 4. In this way a proper sealing between the sleeves and the drum plate is ensured.
  • the hydraulic device is according to claim 5.
  • the sleeves are placed in an oval on the drum plate where the sleeves move during rotation to and from the rotation axis.
  • the circumference around the sleeves does hardly change so a flexible support with an elliptical shape whereby the elliptical shape rotates with the sleeves keeps a more or less constant distance from the sleeves.
  • Spring means attached between such a support and a sleeve will exert a more or less constant force on the sleeve, independent from the rotational position of the oval.
  • a flexible ring surrounding the sleeves as a support for the second spring means ensures that the forces on the ring are independent from the rotational position.
  • the hydraulic device is according to claim 6.
  • An elastic band directly around the contact points of the sleeves is a simple solution for arranging forces directed towards the rotation axis.
  • the hydraulic device is according to claim 7.
  • the grooves on the sleeves position the ring in an easy way.
  • the hydraulic device is according to claim 8. In this way easy to mount second spring means are obtained.
  • the hydraulic device is according to claim 9.
  • the spring means are made from a single part and are easy to assemble.
  • Fig. 1 and 2 show the internal parts of a hydraulic device, such as a pump or hydromotor, which can be fitted into a housing (not shown) in a known manner.
  • a hydraulic device such as a pump or hydromotor
  • a housing not shown
  • the internal parts are provided with a first face plate 4 and a second face plate 17 which are fitted inside the housing.
  • Bearings 2 are fitted inside the housing on both sides of the housing.
  • the housing is provided on the one side with an opening with a shaft seal in a known manner, so that the end of a shaft 1, which is provided with a toothed shaft end 18, protrudes from the housing.
  • a motor can be coupled to the toothed shaft end 18 if the hydraulic device is a pump, and a driven tool can be coupled thereto if the hydraulic device is a motor.
  • the shaft 1 is provided with a flange 14.
  • Pistons 13 are fitted on both sides of the flange 14; in the embodiment shown, twelve pistons 13 on either side.
  • the pistons 13 rotate in a plane of rotation 9 which is at right angles to the shaft 1.
  • a piston sleeve 11, 12 is fitted around each piston, the piston sleeve 11, 12 consists of a sleeve bottom 11 and a sleeve jacket 12.
  • the piston sleeve 11, 12 is fastened in a sealing manner around a spherical seal 28, which forms part of the piston 13.
  • the sleeve bottom 11 rests against a first drum plate 7 and on the other side of the pump or hydromotor, against a second drum plate 16. Together with the piston 13 the drum plate 7 or 16 forms with the interior of the piston sleeve 11, 12 a chamber 10.
  • the first drum plate 7 and the second drum plate 16 are fitted around the shaft 1 by means of a ball hinge 23 and are coupled to the shaft 1 by means of coupling means, such as a key connection, so that the first drum plate 7 and the second drum plate 16 rotate with the shaft 1.
  • the first drum plate 7 rests on a supporting surface 5 of the tapering first face plate 4 by the side remote from the piston sleeve 11, 12, so that the first drum plate 7 pivots about the ball hinge 23 during rotation with the shaft 1.
  • a wedge angle ⁇ is situated between the plane of rotation 9 and the supporting surface 5, so that the rotation axes of the piston sleeves 11, 12 and the piston 13 make a wedge angle ⁇ as well. In the embodiment is the wedge angle ⁇ approximately 9 degrees.
  • a spring plate 24 is connected to the first drum plate 7, another spring plate 24 is connected to the second drum plate 16.
  • the drum plate 24 is provided with spring arms 25 having contact surfaces 15 which press against a top edge 33 of the sleeve jacket 12 on two sides and thus press the piston sleeves 11, 12 against the first drum plate 7 or the second drum plate 16.
  • the contact surfaces 15 are designed as small pads of material having a low sliding resistance which are connected to the spring arms 25 by riveting.
  • the contact surfaces 15 can be formed by local deformation of the spring arm 25.
  • the piston sleeves 11, 12 are pressed against the pivoting first drum plate 7 during rotation of the shaft 1, so that the volume of the chamber 10 changes.
  • the chamber 10 is in communication with line connections for the supply and discharge of fluids, such as oil, in a known manner via a drum plate gate 6 and a face plate gate 3.
  • the piston sleeves 11, 12 may tilt about the spherical seal 28 by the effect of centrifugal forces or by the effect of acceleration forces and deceleration forces. This is prevented by the fact that the piston sleeve 11, 12 is pressed against the first drum plate 7 by the spring arms 25. However, if the forces become too great, there would still be a risk of tilting. In order to compensate for the centrifugal forces the piston sleeves 11, 12 are resiliently pushed towards the rotation axis of the drum plate 4 or 16. In the embodiment shown in figure 1 and 2 the sleeve jackets 12 have a groove 34 at the height of the gravity centre of the piston sleeves 11, 12 and a ring shape spring 35 surrounds the piston sleeves 11, 12.
  • the piston sleeves 11, 12 move in different more or less elliptical paths 36 on the drum plate 7 or 16 as a result of the rotation of the piston 13 and the wedge angle ⁇ between the rotation axes of the pistons and the piston sleeves 11, 12.
  • the projection of the path of the pistons 13 on the plane of the drum plate 7 or 16 is an ellipse and is shown as the interrupted line e.
  • the paths 36 of the pistons and the ellipse e are shown in the situation whereby the wedge angle ⁇ is 40 degrees.
  • the wedge angle ⁇ is 9 degrees so that the paths of the piston sleeves 11, 12 on the drum plate 16 are considerably smaller.
  • the length of the polygon surrounding the piston sleeves 11, 12 is more or less independent of the rotative position of the pistons 13, so the length of the ring shaped spring 35 is more or less constant and the ring shaped spring 35 exerts a more or less constant force in the direction of the rotation axis which compensates the centrifugal force at the piston sleeves 11, 12.
  • the force exerted by the ring shaped spring 35 on the piston sleeve 11, 12 is less than the force exerted by the spring arms 25.
  • this force is more or less 50% of the force exerted by the spring arms 25 on the piston sleeve 10,11.
  • the spring arms 25 can slide over the top edge 33 of the sleeve jacket 12 and the ring shaped spring 35 can slide in the grooves 34 so that the piston sleeve 11, 12 is able to rotate about its axis and wear resulting from friction between the inside of the sleeve jacket 12 and the spherical seal 28 is distributed evenly over the circumference.
  • the piston sleeve 11, 12 seals against the first drum plate 7 having an annular sealing surface 21, which forms part of the side of the sleeve bottom 11 facing the first drum plate 7.
  • the outermost circumference of the sleeve bottom 11 forms a supporting surface 22.
  • a relieving groove 20 is provided between the supporting surface 22 and the sealing surface 21 in order to prevent pressure building up between the supporting surface 22 and the drum plate 7.
  • the dimensions of the sealing surface 21 are chosen such that the resultant of all the forces acting on the piston sleeve 11, 12 and depending on the pressure in the chamber 10 more or less equals zero, so that the piston sleeve 11, 12 is pressed against the first drum plate 7 mainly by the force exerted by the contact surfaces 15 in the direction of the first drum plate 7.
  • Fig. 2 shows the piston sleeve 11, 12 and the second drum plate 16 in more detail.
  • the sleeve bottom 11 is provided with a thin clamping edge 27 which is clamped in the inner diameter of the sleeve jacket 12.
  • Radial grooves 32 are provided between the sleeve bottom 11 and the sleeve jacket 12 which ensure that no build-up of pressure occurs between the underside of the sleeve jacket 12 and the sleeve bottom 11.
  • the thin clamping edge 27 is deformable and increases its clamping force as the pressure in the chamber 10 increases, so that the clamping action between the sleeve bottom 11 and the sleeve jacket 12 is maintained even as the pressure increases. Since the clamping edge 27 is thin and the sleeve jacket 12 is much thicker, the clamping edge 27 thus follows the increase in diameter of the sleeve jacket 12 by the effect of the pressure.
  • the dimensions of the clamping edge 27 and the supporting surface 21 are in addition matched to one another such that the surface of the clamping edge 27, when viewed as a projection on the drum plate 7, is approximately half the size of the surface of the sealing surface 21. Because the pressure between the chamber 10 and the relieving groove 20 decreases more or less linearly along the drum plate 7, the forces directed at the drum plate 7 acting on the clamping edge 27 are approximately equal to the forces directed away from the drum plate acting on the sealing surface 21 and there are approximately no forces which are dependent on the pressure in the chamber 10 exerted on the piston sleeve 11, 12.
  • the piston sleeve 11, 12 is designed in two parts. This has the advantage that both parts can be produced differently and may be made of different materials.
  • the sleeve jacket 12 may be made from tube in a simple manner with the groove 34 and an exactly calibrated inner diameter and a height which is ground to size.
  • the sleeve jacket 12 is made of material of as high a stiffness as possible, such as steel, so that as little deformation as possible occurs in the chamber 10 by the effect of the pressure.
  • the sleeve bottom 11 may be made of flat material, the clamping edge 27 being formed by pressing.
  • the chosen material may be a type of bronze as this has good sliding properties and can slide over the drum plate 7 with little resistance.
  • the drum plate 7 may in that case be made from steel and the face plate 4 may, in turn, be for example made from bronze.
  • An additional advantage of the use of bronze as material is that the material is less stiff, as a result of which the clamping edge 27 is better able to follow the increase in diameter of the sleeve jacket 12 when the pressure increases and the clamping between the sleeve jacket 12 and the sleeve bottom 11 is tighter.
  • Fig. 2 also shows a keyway 29 which is arranged in the drum plate 16 and interacts with a key placed in the shaft 1, and which ensures that the drum plate 16 rotates together with the shaft 1.
  • Figure 4 and 5 show a second embodiment of the springs that push the piston sleeves 11, 12 towards the rotation axis.
  • a flexible ring 38 is positioned around the second drum plate 16 and is coupled thereto at two facing positions with pins 39, whereby the pins 39 are fixed in the second drum plate 16 and the flexible ring 38 is provided with a slot 40 through which the pin 39 extends.
  • the flexible ring 38 has at the location of each piston sleeve 11, 12 a spring arm 37 which pushes the piston sleeve 11, 12 at the height of its gravity centre towards the rotation axis.
  • the piston sleeves 11, 12 each move in an elliptical path 36 relative to the second drum plate 16 whereby the circumference around all sleeve jackets 12 is more or less elliptical.
  • the spring arms 37 press against the sleeve jackets 12 and as a result of the spring forces the flexible ring 38 takes a similar elliptical shape. Due to the play of the pin 39 in the slot 40 the flexible ring 38 can follow the movements of the sleeve jackets 12, whereby the spring arms 37 have a constant height above the second drum plate 16, so they press at the height of the gravity center of the piston sleeves 11, 12. It will be clear that in a similar way a flexible ring 38 is mounted around the first drum plate 7 for containing the piston sleeves 11, 12 that are supported by the first drum plate 7.
  • the spring arms 37 are designed such that the force on the circumference of a sleeve jacket 12 is approximately half of the force exerted on the top edge 33 of the sleeve jacket 12 by the spring arm 25 on the piston sleeve 10,11.
  • Figures 6 and 7 show a third embodiment of springs that push the piston sleeves 11, 12 towards the rotation axis.
  • the flexible ring 38 is connected in the same way as described above around the second drum plate 16.
  • the flexible ring 38 has at the location of the sleeve jacket 12 an opening 41 and at the height of the gravity centre of the piston sleeve 11, 12 the edge of the flexible ring 38 is bent inwards and forms a counter bent strip 42, which presses against the sleeve jacket 12 with a force that is approximately half of the force exerted by the spring arm 25 on the top edge 33 of the sleeve jacket 12. If necessary for making a soft spring the counter bent strip 42 is only fastened to the flexible ring 38 at one end. For the first drum plate 7 the construction is similar.
  • the pump or hydraulic motor has a fixed wedge angle ⁇ which leads to a fixed displacement of the pump or motor.
  • this is achieved by making the wedge angle ⁇ variable.
  • this would mean a wedge angle ⁇ which varies between 0 and 9 degrees.
  • the circumference around the piston sleeves 10,11 is slightly reduced at the maximum wedge angle ⁇ when compared to the situation when the wedge angle ⁇ is zero.
  • the design of the ring shaped spring 35, the spring arms 37 and the counter bent strip 42 should be so that with this variance in the circumference a proper spring force towards the rotation axis is maintained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
EP06113728A 2006-05-09 2006-05-09 Hydraulisches Gerät Withdrawn EP1855002A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06113728A EP1855002A1 (de) 2006-05-09 2006-05-09 Hydraulisches Gerät

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06113728A EP1855002A1 (de) 2006-05-09 2006-05-09 Hydraulisches Gerät

Publications (1)

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EP1855002A1 true EP1855002A1 (de) 2007-11-14

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EP06113728A Withdrawn EP1855002A1 (de) 2006-05-09 2006-05-09 Hydraulisches Gerät

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EP (1) EP1855002A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3246567A1 (de) * 2016-05-19 2017-11-22 Innas B.V. Hydraulikvorrichtung
US10830221B2 (en) 2016-05-19 2020-11-10 Innas Bv Hydraulic device, a method of manufacturing a hydraulic device and a group of hydraulic devices
US11067067B2 (en) 2016-05-19 2021-07-20 Innas Bv Hydraulic device
EP4296504A1 (de) 2022-06-21 2023-12-27 Innas B.V. Hydraulikvorrichtung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003058035A1 (en) * 2002-01-12 2003-07-17 Innas B.V. Hydraulic device
EP1508694A1 (de) * 2003-07-25 2005-02-23 Innas B.V. Hydraulisches Gerät

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003058035A1 (en) * 2002-01-12 2003-07-17 Innas B.V. Hydraulic device
EP1508694A1 (de) * 2003-07-25 2005-02-23 Innas B.V. Hydraulisches Gerät

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3246567A1 (de) * 2016-05-19 2017-11-22 Innas B.V. Hydraulikvorrichtung
WO2017198718A1 (en) * 2016-05-19 2017-11-23 Innas Bv A hydraulic device
US10830221B2 (en) 2016-05-19 2020-11-10 Innas Bv Hydraulic device, a method of manufacturing a hydraulic device and a group of hydraulic devices
US10914172B2 (en) 2016-05-19 2021-02-09 Innas Bv Hydraulic device
US11067067B2 (en) 2016-05-19 2021-07-20 Innas Bv Hydraulic device
EP4296504A1 (de) 2022-06-21 2023-12-27 Innas B.V. Hydraulikvorrichtung
WO2023247524A1 (en) 2022-06-21 2023-12-28 Innas Bv A hydraulic device

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