PISTON OF A HYDRAULIC MACHINE AND HYDRAULIC PISTON MACHINE

Abstract

A piston (1) of a hydraulic piston machine is described, the piston (1) having a hollow (2) surrounded by a wall (3) and an insert (4) arranged in the hollow (2). Such a piston is used to have a piston machine with high efficiency at low costs. To this end at least two pliable rings (12, 13) are arranged between the insert (4) and the wall (3).

Claims

1. A piston of a hydraulic piston machine, the piston having a hollow surrounded by a wall and an insert arranged in the hollow, wherein at least two pliable rings are arranged between the insert and the wall.

2. The piston according to claim 1, wherein the two rings are located on both sides of a center of mass of the insert.

3. The piston according to claim 1, wherein a first ring secures an axial position of the insert in the piston and a second ring secures a radial position of the insert in the hollow only.

4. The piston according to claim 3, wherein the first ring is located adjacent an open end of the hollow.

5. The piston according to claim 4, wherein the first ring is arranged in an inner groove in the wall and in an outer groove in the insert.

6. The piston according to claim 1, wherein the second ring rests against a bottom of the hollow.

7. The piston according to claim 1, wherein the insert comprises a conical section near an end remote from the open end of the hollow and the second pliable ring is arranged around the conical section.

8. The piston according to claim 1, wherein a gap is formed between the insert and the wall.

9. The piston according to claim 1, wherein at least the first ring comprises at least one thin section having a radial extent smaller than the largest radial extent of the ring.

10. The piston according to claim 9, wherein the ring comprises a number of blocks separated by thin sections.

11. The piston according to claim 10, wherein the blocks are spaced equidistantly.

12. The piston according to claim 10, wherein the thin sections have an axial extension smaller than the axial extension of the blocks.

13. The piston according to claim 1, wherein the first ring and the second ring have the same form.

14. The piston according to claim 1, wherein the insert is of a ceramic material or of fibre reinforced plastics.

15. A hydraulic piston machine comprising a piston according to claim 1.

16. The piston according to claim 2, wherein a first ring secures an axial position of the insert in the piston and a second ring secures a radial position of the insert in the hollow only.

17. The piston according to claim 2, wherein the second ring rests against a bottom of the hollow.

18. The piston according to claim 3, wherein the second ring rests against a bottom of the hollow.

19. The piston according to claim 4, wherein the second ring rests against a bottom of the hollow.

20. The piston according to claim 5, wherein the second ring rests against a bottom of the hollow.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The invention relates to a hydraulic piston machine having a piston as described above.

[0025] The invention will now be described in more detail with reference to the drawing, wherein:

[0026] FIG. 1 shows a longitudinal section of a piston according to line A-A of FIG. 2,

[0027] FIG. 2 shows a top view of the piston,

[0028] FIG. 3 shows a pliable ring in perspective view,

[0029] FIG. 4 shows a top view of the ring, and

[0030] FIG. 5 shows a side view of the ring.

DETAILED DESCRIPTION

[0031] FIG. 1 shows a sectional view of a piston 1 of a hydraulic piston machine. The piston 1 comprises a hollow 2 surrounded by a wall 3. An insert 4 is arranged in the hollow 2.

[0032] The insert 4 is made of a ceramic material or another light weight and stiff material which cannot be compressed. Such a material can be a fibre reinforced plastic material, in particular a fibre reinforced polymer, like PEEK (Polyetheretherketone).

[0033] The hollow 2 comprises an open end 5 through which the insert 4 can be mounted in the hollow 2. Furthermore, the hollow 2 comprises a bottom 6 at the opposite end. The bottom 6 is basically closed except a channel 7 through which liquid can flow to reach a hydrostatic bearing face 8 of a slider shoe 9. The slider shoe 9 is mounted on a ball 10 of the piston, as it is known in the art. During operation the slider shoe 9 rests against an inclined swash plate and is held against the swash plate by means of a retainer plate (not shown).

[0034] A gap 11 is formed between the insert 4 and the wall 3.

[0035] The insert 4 is fixed in the hollow 2 by means of a first pliable ring 12 and a second pliable ring 13. The first pliable ring 12 is arranged in an inner groove 14 in the wall 3 and in an outer groove 15 of the insert 4. The inner groove 14 and the outer groove 15 are located adjacent the open end 5 of the hollow 2.

[0036] The insert 4 comprises a conical section 16 at or near the end remote from the open end of the hollow 2. The second pliable ring 13 is arranged around the conical section 16 and rests against the bottom 6.

[0037] The first pliable ring 12 secures an axial position of the insert 4 in the piston 1 and at the same time secures a radial position of the insert 4 in the hollow 2. The first pliable ring 12 centers the insert 4 with respect to the piston 1 near the open end 5 of the hollow 2.

[0038] The second pliable ring 13 secures only a radial position of the insert 4 in the hollow 2. The two pliable rings 12, 13 are arranged with a certain distance to each other along the longitudinal extension of the insert 4. More precisely, they are arranged on both sides of a center of mass of the insert 4. Thus, they prevent a tilting of the insert 4 with respect to the wall 3.

[0039] FIGS. 3 to 5 show the first pliable ring 12. In a preferred embodiment of the invention, the second pliable ring 13 has the same form.

[0040] The ring 12 is not closed, but open in circumferential direction, i.e. it comprises a clearance 17 in circumferential direction. In an embodiment not shown, the ring 12 can be closed in circumferential direction.

[0041] The ring 12 comprises a number of blocks 18 which are evenly distributed in circumferential direction. In other words, the blocks 18 are spaced equidistantly. This is true for the blocks 18 on both sides of the clearance 17.

[0042] Two adjacent blocks 18 are connected by means of a thin section 19. The thin section 19 comprises (FIG. 4) a radial extent 20 which is smaller than a radial extent 21 of the blocks 18 which is the largest radial extent of the ring 12.

[0043] Furthermore, the thin sections 19 have an axial extension 22 which is smaller than an axial extension 23 of the blocks 18.

[0044] Such a construction has the following effect. Due to the smaller radial extent 20 of the thin sections 19 a passage for a fluid is formed through which the fluid can enter the gap 11 between the insert 4 and the wall 3 and can flow past the ring 13 towards to the hydrostatic bearing 8. Furthermore, the thin sections 19 allow for a deformation of the ring 12 which is necessary to mount the insert 4 together with the rings 12, 13 in the hollow 2.

[0045] When the insert 4 is mounted by pressing it into the hollow 2, the rings 12, 13 are plastically deformed by an amount which varies slightly depending on the production tolerances of the piston and the insert 4. The first ring 12 flows into the inner groove 14 of the wall 3, so that the axial position of the insert 4 inside the hollow 2 is locked and well defined. The primary function of the second ring 13 is to center the insert 4 inside the piston 1.

[0046] The combination of the second pliable ring 13 at the bottom 6 of the hollow 2 and the conical section 16 of the insert 4 ensures good centering of the tip of the insert 4 even if production tolerances for the piston 1 and the insert 4 cause significant variations in the axial clearance between the tip of the insert 4 and the bottom 6 of the hollow 2 in the piston 1.

[0047] Thus, the two ends of the insert 4 are locked against radial movements inside the piston 1. Otherwise the inertial forces acting on the insert 4 during operation at high speed can cause the insert 4 to make small movements inside the piston 1 that can eventually lead to wear, formation of damages, and even to the insert 4 getting dislodged over time.

[0048] The gap 11 allows a fluid flow which helps to cool the piston 1, so that the piston 1 does not overheat. If the piston 1 overheats, it can get stuck in the cylinder due to excessive thermal expansion of the piston. The first ring 12 (and the second ring 13 likewise) allow fluid to pass in the mounted condition.

[0049] The rings 12, 13 furthermore ensure that the insert 4 is accurately centred inside the hollow 2 to ensure uniform size of the gap 11 and uniform fluid flow and cooling in the gap 11. Since the blocks 18 of the rings 12, 13 are placed equidistantly, they ensure even distribution of the fluid flow in the gap 11 and minimize the form defects in the roundness of the piston caused by pressing the insert 4 into the piston.

[0050] The piston 1, more precisely the wall 3 of the piston is made of a material with high strength that can withstand the loads on the piston. It is a material with good tribological properties to ensure low frictional losses and low wear of the piston and the components it interfaces with. Finally, the material of the piston must be compatible with the fluid in the piston machine. This will often lead to the piston being made of metal with a high density. The hollow 2 reduces the mass.

[0051] The insert 4 reduces the compressibility in the volume in which the piston is moved by filling a significant fraction of the dead volume with a material with higher bulk modules than the fluid but with a lower density than the material of the wall 3 and other parts of the piston 1. The material of the insert 4 must be compatible with the fluid but does not need to have the strength and tribological properties of the material of the rest of the piston 1. The use of the two pliable rings 12, 13 helps to reduce the requirements for the strength of the material of the insert 4 because the gap 11 between the insert 4 and the wall 3 enables the insert 4 to remain straight even if the wall 3 itself is deformed by external loads. This enables the use of materials for the insert 4 with very high stiffness but low strengths, such as for extents light weight ceramics or fibre reinforced polymer, like PEEK (Polyetheretherketone), without risking that bending loads are transferred from the piston to the insert 4.

[0052] While the present disclosure has been illustrated and described with respect to a particular embodiment thereof, it should be appreciated by those of ordinary skill in the art that various modifications to this disclosure may be made without departing from the spirit and scope of the present disclosure.