• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Hydraulic axial piston machine. A hydraulic axial piston machine (1) is described, the machine comprises a housing, a cylinder block (2) rotatably mounted in the housing around an axis of rotation (7) and having at least one cylinder (3), and a valve arrangement (4) between the cylinder block (2) and the housing, the valve arrangement has a first part (4) rotatable with the cylinder block (2) and a second part mounted stationary with respect to the housing . This type of machine must have high efficiency. To this end the first part (4) comprises an elastically deformable spring section (9). (Machine-translation by Google Translate, not legally binding)
    公开号:ES2835102A1
    申请号:ES202030922
    申请日:2020-09-11
    公开日:2021-06-21
    发明作者:Andersen Stig Kildegaard；Iversen Frank Holm
    申请人:Danfoss AS；
    IPC主号:
    专利说明:

    [0002] Hydraulic axial piston machine
    [0004] The present invention relates to a hydraulic axial piston machine comprising a housing, a cylinder block rotatably mounted in the housing about an axis of rotation and having at least one cylinder, and a valve arrangement between the cylinder block. and the housing, the valve arrangement has a first part rotatable with the cylinder block and a second part mounted stationary with respect to the housing.
    [0006] This type of axial piston machine is known, for example, from US 100 94 364 B2.
    [0008] In an axial piston machine the cylinder block comprises one or more cylinders wherein a piston is arranged in each cylinder. Each piston is connected to a piston shoe that rests against a swash plate and is held against the swash plate by means of retainer means. In some classes of such axial piston machines, the other end of these springs pushes on the cylinder block which in turn pushes on the first or rotary part of the valve arrangement.
    [0010] In either case, some force is needed to push the rotating part of the valve arrangement against the stationary part. When this is achieved by transferring a force from the cylinder block onto the rotating part, it is preferable that this force transfer occurs at the same location in the valve arrangement on different machines to avoid variations in performance between individual machines. Furthermore, it is preferable that the force is well distributed and has a centroid near the axis of rotation to avoid a localized spike in contact pressure and wear that can occur if the force is transferred into localized contact.
    [0012] The underlying object of the invention is to have an axial piston machine that has good efficiency.
    [0014] This object is solved with a hydraulic axial piston machine as described in the beginning in that the first part comprises an elastically deformable spring section.
    [0016] The spring section is formed in one piece with the first part so that only the first part needs to be handled during assembly of the machine. No additional spring parts are necessary here. When the spring section is formed into the first or rotary part, tolerances can be kept small and the first parts of several different machines of the same class can be made largely identical.
    [0018] In one embodiment of the invention the spring section is arranged around the axis of rotation. This means that the force produced by the spring means can be distributed around the axis of rotation.
    [0020] In one embodiment of the invention the spring section is deformable in the axial direction only. Thus, there is no deformation in the radial direction and the position of a contact between the spring section and the cylinder block is maintained. The risk of wear can be kept small.
    [0022] In an embodiment of the invention the transfer of force from the cylinder block to the first part by means of the spring section is symmetrical with respect to the axis of rotation. The spring section will receive the force from the cylinder block. The spring section will deform slightly in the axial direction due to the force. The first part is designed to compensate for axial misalignment and will therefore align with the second part of the valve arrangement and not with the end face of the cylinder block. Therefore, the axial deformation of the spring section will be slightly asymmetric with respect to the axis of rotation. If the axial deformation of the spring due to force from the cylinder block is greater than the asymmetry of the axial deformation due to misalignment, the centroid of the contact force will be close to the axis of rotation and the force transfer from the section of spring to the remainder of the first part of the valve arrangement will be nearly symmetrical around the axis of rotation.
    [0024] In one embodiment of the invention the spring section is machined from the first part. Machining can be done, for example, by turning. This is a simple way to make the spring section in one part with the rest of the first part.
    [0026] In one embodiment of the invention the spring section comprises an edge that surrounds the axis of rotation and contacts the cylinder block. The edge can be moved slightly in the axial direction relative to the rest of the first part.
    [0028] In one embodiment of the invention the edge has a thickened section at the end that contacts the cylinder block. The thickened section provides a larger contact phase between the cylinder block and the spring section, thus lowering the contact pressure and thereby the risk of wear between the cylinder block and the thickened section.
    [0029] In one embodiment of the invention the edge is connected to a radially outer part of the first part by means of a hinge section, wherein the hinge section has a thickness that is less than a thickness of the first part. The spring section is basically deformed in the hinge section.
    [0031] In one embodiment of the invention the edge has the greatest thickness that is greater than the thickness of the hinge section. This is a simple way to concentrate the formation of the spring section in the hinge section.
    [0033] In one embodiment of the invention the hinge section comprises a wave-like shape. The wave-like shape allows a deformation of the hinge section in which the edge moves basically parallel to the axial direction.
    [0035] In an embodiment of the invention in a sectional view the hinge section comprises two areas as a concave arc that are connected by a region as a convex arc. The concave arc areas have a center of curvature on the cylinder block side and the convex arc area has a center of curvature on the second part side. The spring section is designed so that axial deformation of the spring section will not cause significant relative movement between the cylinder block and the edge. This will minimize wear at the interface between the cylinder block and the lip.
    [0037] In one embodiment of the invention the convex arc region is curved more strongly than at least one of the concave arc region. This contributes to the desired deformation of the spring section.
    [0039] In one embodiment of the invention the spring section rests against a protrusion of the cylinder block. Thus, it is not necessary for the spring section to protrude from the first part. Consequently, during machining of the first part, less material has to be removed.
    [0041] The invention will now be described in more detail with reference to the drawings, in which:
    [0042] Figure 1 shows a schematic illustration of parts of an axial piston machine,
    [0044] Figure 2 shows a detail of Figure 1 in a larger view and
    [0045] Figure 3 shows a second embodiment of the detail of Figure 2
    [0046] Figure 1 schematically shows parts of an axial piston machine 1, ie a cylinder block 2 having a cylinder 3 and a first part 4 of a valve arrangement. The first part 4 comprises a support plate 5 and a wear plate 6. The wear plate 6 can be made of a ceramic material, while the support plate 5 is made of metal. The housing and the second part are omitted to simplify the illustration.
    [0048] In this type of hydraulic axial piston machine a piston is arranged in cylinder 3 (not shown). During operation the piston moves up and down in cylinder 3 and the free volume of cylinder 3 varies. The piston is connected to a piston shoe which is held against a swash plate by means of retainer means.
    [0050] When the axial piston machine 1 operates as a pump, a rod 8 which is connected to the cylinder block 2 is rotated. A piston that moves away from the valve arrangement draws liquid into cylinder 3 and a piston that moves toward the valve arrangement displaces the liquid under high pressure to the outside.
    [0052] When the hydraulic axial piston machine operates as a motor, liquid is pushed into the cylinder which presses the piston away from the valve arrangement. This movement of the piston together with the effect of the swash plate creates a torque to rotate the cylinder block 2 as is known in the art.
    [0054] In order to control the flow of the liquid, the valve arrangement is provided.
    [0056] The first part 4 of the valve arrangement must be loaded against the second part of the valve arrangement with some force in order to prevent leakage.
    [0058] In the present case such a force is produced by the springs of a retainer system that holds the piston shoes against a swash plate. These springs are usually compressed several mm. This high compression makes the force insensitive to production tolerances.
    [0060] The first part 4, more precisely the support plate 5, comprises a spring section 9. The spring section 9 comprises an edge 10 that surrounds the stem 8 and the axis of rotation 7. The edge 10 contacts in the block of cylinders 2. For this purpose the cylinder block 2 is provided with a protrusion 11. The height of the protrusion 11 can be quite small. The height must be dimensioned so that the spring section 9 deforms sufficiently before the cylinder block 2 contacts in the first part 4 radially outside the spring section 9.
    [0061] The cavities 12 or push plates connect each cylinder 3 to the first part 5. Each cavity 12 is sealed in the cylinder 3 by means of an O-ring 13.
    [0063] Figure 2 shows the spring section 9 in more detail. The same elements are denoted by the same reference numerals as in Figure 1.
    [0065] The edge 10 has a thickened section 15 at the end that contacts the cylinder block 2. The edge connects to a radially outer part 16 of the support plate 5 by means of a hinge section 17. The hinge section 17 it has a thickness that is less than a thickness of the support plate 5. The support plate 5 basically has a constant thickness of the spring section 9.
    [0067] The edge 10 has the largest thickness which is greater than the thickness of the hinge section 17. This means that the spring section 9 is deformed mainly in the hinge section 17 with the consequence that during a deformation of the spring section 9 edge 10 is moved only in axial direction and does not move in radial direction with respect to axis of rotation 7.
    [0069] The hinge section 17 comprises two zones like concave arc 18, 19 which are connected by one zone like convex arc 20. The center of curvature of the zones like concave arc 18, 19 is on the side of cylinder block 2 while the center of curvature of the area as convex arc 20 is on the side of the second part. The convex arc region 20 bends more strongly than at least one of the concave arc regions 18, 19, that is, it has a smaller radius of curvature.
    [0071] Figure 3 shows a slightly different shape of the spring section 9. The same and like parts as in Figure 1 and 2 are denoted by the same reference numerals.
    [0073] In this embodiment the spring section 9 similarly comprises an edge 10. However, the hinge section 17 is slightly different. It comprises only a concave arc-like area that is connected to the radial outer part of the support plate 5 by means of a straight section 21.
    [0075] With the spring section 9 shown in Figure 2 or 3 a slightly compliant / flexible contact is achieved between the cylinder block 2 and the first or rotary part 4 of the valve arrangement that distributes the contact force between the cylinder block 2 and the first part 4 of the valve arrangement almost symmetrically around the axis of rotation 7 of the axial piston machine.
    [0076] The spring section 9 is formed by machining, for example turning, the support plate 5 of the first or rotary part 4 of the valve arrangement. The spring section 9 is symmetrical with respect to the axis of rotation 7.
    [0078] One side of the spring section 9 will receive the force from the cylinder block 2. This is the edge 10. The spring section 9 will deform slightly in the axial direction due to the force. The rotating or first part 4 of the valve arrangement is designed to compensate for axial misalignment and will therefore align with the second or stationary part of the valve arrangement and not with the end face of the cylinder block 2. Therefore, the axial deformation of the spring section 9 will be slightly asymmetric with respect to the axis of rotation 7. If the axial deformation of the spring section 9 due to the force from the cylinder block 2 is greater than the asymmetry of the axial deformation due to misalignment, the centroid of the contact force will be close to the axis of rotation 7 and the transfer of force from the spring section to the remainder of the first or rotary part 4 of the valve arrangement will be nearly symmetrical about an axis of rotation 7.
    [0080] In addition to contributing to high efficiency, less wear, and fewer performance deviations between individual machines, the embodiment shown has the following advantages: the spring section 9 can be designed so that axial deformation of the spring section 9 will not cause significant relative movement between cylinder block 2 and edge 10. This is particularly true for the embodiment shown in Figure 2. This will minimize wear at the interface between cylinder block 2 and spring section 9 compared to, for example, placing a disc spring between cylinder block 2 and rotating part 4 of the valve arrangement because a disc spring will also deform radially when deformed axially.
    [0082] What's more, there is no need to add extra components to a machine. Therefore there is no need to produce extra components or keep them in stock, there is no extra component that can be forgotten or incorrectly assembled during assembly or service.
    [0084] As the spring section 9 is machined from material already available, the added cost is minimized.
    权利要求:
    Claims (13)
    [1]
    1. Hydraulic axial piston machine (1) comprising a housing, a cylinder block (2) rotatably mounted in the housing about an axis of rotation (7) and having at least one cylinder (3), and an arrangement of valves between the cylinder block (2) and the housing, the valve arrangement has a first part (4) rotatable with the cylinder block (2) and a second part mounted stationary with respect to the housing, characterized in that The first part (4) comprises an elastically deformable spring section (9).
    [2]
    Machine according to claim 1, characterized in that the spring section (9) is arranged around the axis of rotation (7).
    [3]
    Machine according to claim 1 or 2, characterized in that the spring section (9) is deformable in the axial direction only.
    [4]
    Machine according to any one of claims 1 to 3, characterized in that the transfer of force from the cylinder block (2) to the first part (4) by means of the spring section (9) is symmetrical with respect to the axis rotation (7).
    [5]
    Machine according to any one of claims 1 to 4, characterized in that the spring section is machined from the first part (4).
    [6]
    Machine according to any one of claims 1 to 5, characterized in that the spring section (9) comprises an edge (10) that surrounds the axis of rotation (7) and contacts the cylinder block (2).
    [7]
    Machine according to claim 6, characterized in that the edge (10) has a thickened section (15) at the end that contacts the cylinder block (2).
    [8]
    Machine according to claim 6 or 7, characterized in that the edge (10) is connected to a radially outer part of the first part (4) by means of a hinge section (17), wherein the hinge section (17) has a thickness that is less than a thickness of the first part (4).
    [9]
    9. Machine according to claim 8, characterized in that the edge (10) has the largest thickness which is greater than the largest thickness of the hinge section (17).
    [10]
    10. Machine according to any one of claims 7 to 9, characterized in that the hinge section (17) comprises a wave-like shape.
    [11]
    Machine according to claim 10, characterized in that in a sectional view the hinge section (17) comprises two zones as a concave arc (18, 19) which are connected by a zone like a convex arc (20).
    [12]
    Machine according to claim 11, characterized in that the area as a convex arc (20) is curved more strongly than at least one of the areas as a concave arc (18, 19).
    [13]
    Machine according to any one of claims 1 to 12, characterized in that the spring section (9) rests against a protrusion (11) of the cylinder block (2).
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    同族专利:
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3295460A|1964-12-21|1967-01-03|Tom H Thompson|Valve plate mounting for a cylinder and multi-piston type pump|
    EP1705372A1|2005-03-11|2006-09-27|Innas B.V.|Variable pump or hydraulic motor|
    DE102008060067A1|2008-12-02|2010-06-10|Robert Bosch Gmbh|Control plate for use between control cover and cylinder drum of axial piston pump, has outer sealing bar, where sub region i.e. recess, of outer sealing bar includes high elasticity relative to another sub region|
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    US10094364B2|2015-03-24|2018-10-09|Ocean Pacific Technologies|Banded ceramic valve and/or port plate|
    法律状态:
    2021-06-21| BA2A| Patent application published|Ref document number: 2835102 Country of ref document: ES Kind code of ref document: A1 Effective date: 20210621 |
    优先权:
    申请号 | 申请日 | 专利标题
    DE102019135083.2A|DE102019135083A1|2019-12-19|2019-12-19|Hydraulic axial piston machine|
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