Patent Application
20140150641
This application claims priority under 35 U.S.C. §119 to patent application no. DE 10 2012 222 172.7 filed on Dec. 4, 2012 in Germany, the disclosure of which is incorporated herein by reference in its entirety.
The disclosure relates to an axial piston machine.
DE 23 58 870 B2 has disclosed an axial piston machine of oblique axis construction which can be operated either as a pump or as a motor. The axial piston machine comprises a housing, a drive shaft and a cylinder drum. The drive shaft is mounted in the housing in such a way as to be rotatable with respect to a first axis of rotation by means of a hydrostatic sliding bearing. The cylinder drum is mounted so as to be rotatable with respect to a second axis of rotation, which intersects the first axis of rotation. The angle of inclination between the first and second axes of rotation can be adjusted by means of an adjusting device, wherein the disclosure under consideration can also be used in the case of axial piston machines in which said angle of inclination is fixed. The cylinder drum has a plurality of circular-cylindrical cylinder bores, which are aligned parallel to the second axis of rotation. A piston is accommodated in each cylinder bore in a manner which allows linear motion, said piston being connected at a first end to the drive shaft by means of a ball joint. Here, the ball joint is arranged away from the first axis of rotation on a flange of the drive shaft. When the drive shaft rotates, the pistons rest against the cylinder bore, giving a rotary drive connection between the drive shaft and the cylinder drum. The pistons have a section in the form of a circular cone which tapers toward the ball joint. This enables the pistons to be tilted relative to the associated cylinder bores, ensuring that they do not jam during the rotation of the drive shaft. At the second end, that situated opposite the first end, the pistons have a spherical section, by means of which they rest in a substantially sealed manner on the cylinder bore, more specifically in each of the tilted positions thereof. This spherical section is also referred to as a piston land. The section in the form of a circular cone merges without offsets and kinks into the spherical section.
It is the object of the disclosure to minimize abrasion on the cylinder bore caused by the reciprocating motion of the pistons. At the same time, the installation space occupied by the axial piston machine should not be increased.
According to the disclosure, this object is achieved by virtue of the fact that the piston has, at the second end, a flat end face, which forms a corner with the spherical section. This means that the distance between the bearing force in the ball joint and the bearing force on the spherical section of the piston for a given piston length is particularly large. At the same time, the length of the piston which projects into the cylinder bore is particularly great. The ratio between the two said lengths determines the magnitude of the supporting forces acting between the piston and the cylinder bore. The increase in said lengths means that said supporting forces are particularly small, thereby reducing wear on the cylinder bore. The end face of the piston is preferably aligned perpendicularly to a center line defined by the conical section.
Advantageous developments and improvements of the disclosure are given in the dependent claims.
The corner between the end face and the spherical section of the piston can have a radius or a chamfer. This enables the piston to be inserted easily into the cylinder bore during the assembly of the axial piston machine. At the same time, the radius or chamfer do not hinder the tilting movement of the associated piston.
The cylinder drum can be composed of cast iron. In the case of a cylinder drum made of cast iron, the wear caused by the piston on the cylinder bore is particularly great, and therefore the minimization according to the disclosure of said wear is particularly advantageous. The use of the following types of materials is preferred: EN-GJS-400-15, EN-GJS-400-18, EN-GJS-500-7 and EN-GJS-600-3
The cylinder drum can be produced by casting. As a result, the cylinder drum can be produced at a particularly low cost. The cylinder drum is preferably finish-machined in the region of the cylinder bore to ensure that the surface is particularly smooth and the bore diameter is particularly accurate there.
The cylinder bore can have a surface layer which has a greater hardness than the remainder of the cylinder drum. By means of the high hardness of said surface layer, wear can be further minimized Surface layers of this kind typically have a low thickness of, for example, less than 20 μm. The wear-related abrasion of said surface layer must never be greater than the thickness thereof during the entire operating life of the axial piston machine because the axial piston machine would otherwise suffer excessive wear after a very short time. The minimization according to the disclosure of wear in connection with the surface layer proposed is therefore particularly advantageous.
The section of the piston which is in the form of a circular cone can be interrupted adjacent to the spherical section by an encircling first groove, in which a separate first sealing ring is accommodated. It is not possible to completely exclude a small gap between the spherical section of the piston and the cylinder bore. It is for this reason that the seal at that point is supposed to be improved by the first sealing ring. This sealing ring can be designed in accordance with DE 10 2009 018 297 A1, for example. For optimum sealing, it is important that the first sealing ring should be arranged very close to the spherical section of the piston. At the same time, the first groove must not project into the spherical section since, otherwise, the contact between the spherical section and the cylinder bore would be disrupted. This would result in increased wear on the cylinder bore. By means of the proposed arrangement of the first sealing ring, the ring is protected by the spherical section from damage due to contaminants in the pressurized fluid.
The section of the piston which is in the form of a circular cone can be interrupted by an encircling second groove, in which a separate second sealing ring is accommodated, wherein the second sealing ring is arranged on the side of the first sealing ring remote from the spherical section. By means of the second sealing ring, sealing between the cylinder bore and the piston is further improved.
The width of the spherical section can be between 2 and 8 mm. This width has proven advantageous in tests carried out by the applicant.
A spherical head of the ball joint can be arranged on the first end of the piston, wherein the distance between the center of the spherical head and the spherical section of the piston is between 80 mm and 140 mm. This distance has proven advantageous in tests carried out by the applicant. In particular, the overlap between the sealing rings and the cylinder bore for the maintenance of the sealing function in any position of the axial piston machine is assured.
The disclosure is explained in greater detail below with reference to the attached drawings, in which:
At the opposite end from the drive journal 44, the drive shaft 40 has a flange 46. There, the drive shaft 40 is connected to a plurality of pistons 80, in each case by means of an associated ball joint 84. In this case, the ball joints 84 are arranged away from the first axis 41 of rotation.
A cylinder drum 60, which has a circular-cylindrical cylinder bore 62 for each piston 80, is furthermore provided. The end face 63 of the cylinder drum remote from the drive shaft 40 has a concave spherical curvature and rests on a matching first end face 31 on a control disk 30. This engagement between the cylinder drum 60 and the control disk 30 forms a hydrostatic sliding bearing, by means of which the cylinder drum 60 is mounted so as to be rotatable with respect to a second axis 61 of rotation. The second axis 61 of rotation is defined by a separate bearing part 64, which engages in the flange 46 of the drive shaft 40 by means of a ball joint 65. In this case, the ball joint 65 is arranged at the point of intersection of the first and second axes 41; 61 of rotation. The bearing part 64 engages by means of a circular-cylindrical section in a matching circular-cylindrical bore in the cylinder drum 60, which are arranged concentrically with respect to the second axis 61 of rotation. A spring 66, in particular a helical spring, is installed under preload between the bearing part 64 and the cylinder drum 60, with the result that the cylinder drum 60 is pressed against the control disk 30.
The second end face 32 of the control disk 30 is of circular-cylindrical design with respect to the point of intersection of the first and second axes 41; 61 of rotation and rests against a matching circular-cylindrical surface on the end plate 25 of the housing 20. The second axis 61 of rotation of the cylinder drum 60 can therefore be pivoted relative to the first axis 41 of rotation. For this purpose, an adjusting device 21 is provided on the housing 20, being hydraulically actuable for example. The adjusting device 21 has a movable driver 24, which engages in the control disk 30, thus enabling it to move the latter with respect to the housing 20. Here, the path of motion of the control disk 30 is limited by a first and a second end stop 22; 23, which are in the form of screw bolts which are screwed into the housing 20. The greater the angle between the first and second axes 41; 61 of rotation, the larger is the displacement volume, i.e. the sum of the swept volumes of all the pistons 80, of the axial piston machine 10.
The spherical section 87 of the piston is arranged on the second end 83 of the piston 80, the end opposite the first end 82. The sphere diameter of the spherical section 87 corresponds to the bore diameter of the cylinder bore, wherein the center of the sphere is arranged on the center line 81. The section 86 in the form of a circular cone merges without offsets and kinks into the spherical section 87. The width 92 of the spherical section 87 is 3 mm, for example. The distance 93 between the spherical section 87 and the center of the spherical head 85 is 99.5 mm, for example. A flat end face 88, which is aligned perpendicularly to the center line 81, is furthermore provided on the second end 83 of the piston 80. With the spherical section 87, the end face 88 forms a corner, on which a small radius 89 is provided.
The section 86 in the form of a circular cone on the piston 80 is interrupted by a first and a second groove, which are formed in a rotationally symmetrical manner with respect to the center line 81. A first sealing ring 90 is accommodated in the first groove, wherein a second sealing ring 91 is accommodated in the second groove. The first and/or second sealing ring 90; 91 can be designed in accordance with DE 10 2009 018 297 A1, for example, the entire contents of which are incorporated by reference into the present application. The first sealing ring 90 is arranged as close as possible to the spherical section 87. In the extreme case, that edge of the first groove which is on the right in
10 axial piston machine
20 housing
21 adjusting device
22 first end stop
23 second end stop
24 driver
25 end plate
30 control disk
31 first end face of the control disk
32 second end face of the control disk
40 drive shaft
41 first axis of rotation
42 first rotation bearing
43 second rotation bearing
44 drive journal
45 radial shaft sealing ring
46 flange
60 cylinder drum
61 second axis of rotation
62 cylinder bore
63 end face of the cylinder drum
64 bearing part
65 ball joint of the bearing part
66 spring
80 piston
81 center line
82 first end of the piston
83 second end of the piston
84 ball joint of the piston
85 spherical head
86 section in the form of a circular cone
87 spherical section
88 end face
89 radius
90 first sealing ring
91 second sealing ring
92 width
93 distance
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2012 222 172.7 | Dec 2012 | DE | national |
