EP0320822A1 - Axial piston pump - Google Patents

Axial piston pump Download PDF

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Publication number
EP0320822A1
EP0320822A1 EP19880120650 EP88120650A EP0320822A1 EP 0320822 A1 EP0320822 A1 EP 0320822A1 EP 19880120650 EP19880120650 EP 19880120650 EP 88120650 A EP88120650 A EP 88120650A EP 0320822 A1 EP0320822 A1 EP 0320822A1
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston pump
channel
housing
control
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.)
Granted
Application number
EP19880120650
Other languages
German (de)
French (fr)
Other versions
EP0320822B1 (en
EP0320822B2 (en
Inventor
Heinz Berthold
Ivan Pecnik
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
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
Family has litigation
Priority to DE3743125 priority Critical
Priority to DE19873743125 priority patent/DE3743125A1/en
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0320822A1 publication Critical patent/EP0320822A1/en
Publication of EP0320822B1 publication Critical patent/EP0320822B1/en
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6343006&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0320822(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Publication of EP0320822B2 publication Critical patent/EP0320822B2/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20Multi-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
    • F04B1/2014Details or component parts
    • F04B1/2042Valves

Abstract

An axial piston pump (1) constant or adjustable flow with a two-part housing, namely a housing part (2) receiving the pistons 812) and a connecting part (3) through which the pressure channel (52) and the suction channel (51) extend, the Suction channel (51) has a suction opening (53) which is enlarged in cross section compared to the pressure channel (52), so that it can be adapted to the other conveying direction with less effort. This is achieved in that the connecting part (3) can optionally be attached to the housing part (2) in two positions rotated by 180 ° about the central axis (4) of the axial piston machine (1).

Description

  • The invention relates to an axial piston pump according to the preamble of claim 1.
  • When an axial piston pump is used in an open circuit, cavitation difficulties arise in the area of the intake opening of the axial piston machine, unless care is taken to ensure that a satisfactory amount of the hydraulic medium to be drawn in is provided. To solve this problem, it is known to design the suction opening in the connection part of the axial piston pump to be larger than the discharge opening on the pressure side. With this configuration, the conveying direction of the axial piston machine is predetermined, and it is therefore not possible to change the conveying direction. In order to be able to use such an axial piston pump for both conveying directions, it has become common practice to provide two connecting parts which are mirror images of one another for the axial piston pump. By exchanging the connecting parts, such an axial piston pump can be adapted to the desired delivery direction. Such a configuration is not only very complex, precisely because two connection parts are to be provided, but also requires storage effort with regard to the connection part not used in each case in order to have it available if required.
  • The invention is based on the object of designing an axial piston pump of the type described at the outset, that it can be adapted to the other direction of conveyance with less effort.
  • This object is achieved by the characterizing features of claim 1.
  • In the embodiment according to the invention, the axial piston pump can be adapted to the desired delivery direction by rotating the control part through 180 °. There is therefore no need for an additional connecting part, as is the case with the known configuration. When the connecting part is rotated, there is a displacement of the suction and discharge openings with respect to the axial piston pump or the machine receiving it, but this problem can be solved in a simple manner by using flexible connecting lines or suitable connecting line sections.
  • The retrofitting of the axial piston pump according to the invention is very simple because it only requires a solution and removal of the existing fastening screws for the connecting part. The connecting part can then be rotated in a simple manner by 180 °, an advantageously existing centering projection with a round cross section between the connecting part and the housing of the axial piston machine being able to serve as a rotary bearing.
  • The configuration according to the invention is suitable for those axial piston pumps in which the delivery direction is changed by changing the direction of rotation of the drive shaft or, in the case of axial piston pumps, adjustable delivery rate by adjusting the adjusting device beyond the zero point.
  • The configurations according to claims 2 to 4 enable the adaptability of such axial piston pumps, the control disks of which are asymmetrical with respect to the control openings (control kidneys) or, in a manner known per se, have so-called pressure compensation channels.
  • According to the embodiment according to claim 5, a simple and practical channel guide for loading the adjusting device of the axial piston pump is proposed, which is functional and advantageous in both mounting positions of the connecting part.
  • The configurations according to claims 6 and 7 relate to an integrated hydraulic adjustment device for an axial piston pump of small or compact and also simple construction also with regard to the individual parts concerned.
  • In an embodiment according to claim 10, the swash plate is pivoted out by the engine forces of the axial piston pump, so that no additional pivoting mechanism is required. In addition, the swash plate is simple and easy to assemble or disassemble. The features of claim 11 ensure simple and inexpensive manufacture, the bearing bodies being able to be produced from finished balls by reworking such as turning.
  • Claims 12 and 13 relate to mechanical stops, in particular to prevent the swivel plate from overshooting when pouring at high positioning speeds.
  • In the embodiment according to claim 14, the bearing that is more heavily loaded is starting from the slideway of the swash plate, intermittent and from the height of the operating pressure is supplied with pressure oil by the pistons and is therefore advantageously lubricated. This configuration enables low-friction and low-wear operation with fast positioning times.
  • The invention is explained in more detail below on the basis of preferred exemplary embodiments illustrated in a drawing. It shows:
    • 1 shows an axial piston pump according to the invention of the swash plate type in axial section;
    • Figure 2 shows the axial piston pump in the bottom view.
    • 3 shows a control disk of the axial piston pump in a top view;
    • Figure 4 shows the section IV-IV in Fig. 3.
    • Fig. 5 shows the connection plate of the axial piston pump in plan view.
  • The axial piston pump generally designated 1 in FIG. 1 has a two-part housing consisting of a cup-shaped housing part 2 and a connecting plate 3, in which a drive shaft 5 extending along the central axis 4 is mounted in roller bearings 6, 7, of which one the cup-shaped housing part 2 and the other of the connection plate 3 is assigned. A cylinder drum 9 is mounted on the drive shaft 5 on a multi-key section designated 8, which cylinder cylinder 9 has a plurality of cylinder bores 11, in which pistons 12 are accommodated, evenly distributed over a pitch circle. The pistons 12 have ball heads 13 which enclose in sliding shoes 14 which rest on the sliding surface 15 of a swash plate 16. The contact with the sliding surface 15 is maintained by a retraction plate 17 which, in the present exemplary embodiment, is mounted on a spherical head-shaped carrier piece 19 with a recess 18 in the form of a spherical segment. The carrier piece 19 is mounted on the drive shaft 5 so as to be longitudinally displaceable.
  • The swash plate 16 is mounted about a swivel axis 22 in a swivel bearing which is formed by two supports, generally designated 23, lying one behind the other along the swivel axis 22, consisting of two mushroom-shaped bearing pieces 24 which, with their pins 25 round in cross section, in bores 26 in Bottom of the cup-shaped housing part 2 are inserted and surround in spherical recesses 27 on the back of the swash plate 16. The spherical convex surfaces of the bearing pieces 24 facing the pistons and the spherical concave surfaces of the recesses 27 thus form housing-side and swashplate-side bearing surfaces 28. In the present exemplary embodiment, pan-shaped bearing shells 29 are used in the recesses 27, each with a radially projecting collar 31 on the peripheral edge of the Recesses 27 abut and are thus secured against tilting movements.
  • The pivot axis 22 of the swash plate 16 is located at a distance a from the line of action of the piston force 32 resulting from the forces of the active pistons 12, this distance a extending beyond the central axis 4. The resulting piston force 32 is generated by the pistons 12 located on the respective pressure side. Due to the distance a, the swash plate 16 is loaded with a torque according to FIG. 1 counterclockwise during operation of the axial piston pump 1. This ensures that the swash plate 16 bears against its adjusting hydraulic adjusting pistons 33, which are arranged parallel to the drive shaft 5 in the base or flange part of the cup-shaped housing part 2 and are hydraulically displaceable in cylinder bores 34 axially parallel to the drive shaft 5, ie in the direction of the double arrow 35 . The adjusting pistons 33 are arranged opposite the effective resulting piston force 32, that is to say they are located on the other side of the axial piston pump 1 with respect to the pivot axis 22, being at an equal distance from the central axis 4, fairly close to one another and symmetrical to one perpendicular to the pivot axis 22 extending transverse axis 36 are arranged, cf. Fig. 2. In the position shown in FIG. 1, the swash plate 16 is in its maximum piston stroke position. By extending the actuating piston 33, the swash plate 16 can be adjusted about the pivot axis 22 in either pivot positions or delivery rate settings. To limit the maximum pivoting position, stops 37 are arranged approximately opposite each other on both sides of the axial transverse plane 36, the actuating pistons 33, which are formed by bolts or screws 38 with stop pins inserted laterally into the housing part 2 from the outside. When bearing against the stops 37, the axial piston machine 1 is set to a minimum piston stroke and a minimum delivery rate.
  • The swivel bearings 23 are each provided with a lubrication channel 39 which extends from the recess 27 and crosses the bearing shell 29 and the swash plate 16 connected to the oil-carrying system of the axial piston machine 1 and thus oil-lubricated. In the present exemplary embodiment, the lubrication channel 39 opens into the sliding surface 15 of the swash plate 16 in the vicinity of the pitch circle on which the pistons 12 are arranged, specifically in an area which the sliding shoes 14 cover with a recess 41 in their sliding surface 42. The recess 41 is connected to the working spaces 45 of the piston cylinders by means of axial channels 43, 44 in the sliding shoes 14 and the pistons 12, which are known per se. In this way, during operation of the axial piston pump 1, the bearing point of the pivot bearing 23, which is subjected to higher loads, is intermittently supplied with lubricating oil under working pressure when the sliding shoes 14 are swept over.
  • The cylinder drum 9 lies with its end facing away from the swash plate 16 against a control plate 46 which is arranged between the cylinder drum 9 and the connection plate 3 and is held on the connection plate 3 in a rotationally fixed manner about the central axis 4. The control plate 46 shown in detail in FIG. 3 has two essentially kidney-shaped control openings 47, 48 penetrating it, to which kidney-shaped suction and pressure channels 51, 52 also adjoin in the connection plate 3, of which the suction channel 51 is opposite the pressure channel 52 end cross enlarged in cross section cut, namely a large suction opening 53, here a connection for a suction line, not shown, has. In the present exemplary embodiment, the control kidney 48 is interrupted on the pressure side by reinforcing webs 50.
  • Known pressure compensation notches 55, 56 are arranged at the ends of the control kidneys 47, 48, which are opposite to the respective direction of rotation, which is exemplified by the arrow 54 in FIG to be reduced if the control channels 57 which are present in the cylinder drum 9 and extend from the working spaces 45 come into contact with the control kidneys 47, 48 containing high or low pressure.
  • In the present exemplary embodiment, the control plate 46 has pressure compensation notches 55 on both sides, namely at one and the same end of at least the high-pressure control kidney 48. That is, on the rear of the control plate 46 according to FIG. 3 there are also pressure compensation notches 55, 56 behind the visible pressure compensation notches 55 , 56 available. The pressure compensation notches 55, 56 extend from the relevant end of the control kidneys 47, 48 and converge in a wedge shape, as shown in the partial section according to FIG. 4. The pressure compensation notch (s) 55 are optionally on both sides of the control plate 46, preferably in the direction of rotation 54 opposite end of the low-pressure control kidney 47 arranged.
  • The control plate 46 is secured against rotation by means of a pin connection with a pin, preferably starting from the connecting plate 3 (FIG. 5), which enters a blind hole or through-hole in the control plate 46 borders. The arrangement is such that the control plate 46 can optionally be attached to one or the other end face of the connection plate 3, namely that it can be folded essentially about a transverse axis 58 parallel to the transverse axis 36 according to FIG. 2, so that the control kidneys 47 , 48 always correspond to the likewise kidney-shaped suction or pressure channels 51, 52 in the connection plate 3. In this case, the arrangement of the pin 60 and a pin hole 61 which receives the pin 60 and passes through here is preferably such that the two optional mounting positions of the control plate 46 differ with respect to the position specified by the connecting plate 3, namely that one mounting position is opposite the one another mounting position offset in the circumferential direction, which is illustrated by the angle b shown in FIG. 4, which represents an offset of the pin hole 61 to the transverse axis 58. That is, the control kidneys 47, 48 are not symmetrical with respect to the arrangement predetermined by the control channels 57, specifically for functional reasons in order to achieve a certain advance, which is known per se. The angle b 1 in Fig. 3 shows the angular offset in the folded mounting position of the control plate 46th
  • In the present exemplary embodiment, the control plate 46 is configured in parallel.
  • In operation, the cylinder drum 9 is rotated by the drive shaft 5. The cylinder bores 11 are mutually connected to the control kidneys 47, 48 via the control channels 57, as a result of which the pumping action results in a known manner due to the movement of the pistons 12. The direction of flow of the hydraulic medium is in Fig. 1 by arrows 62 and 63 clarifies. The seal between the cylinder drum 9 and the control plate 46 is ensured by a compression spring 64 which is clamped between an inner ring 65 of the cylinder drum 9 and a pressure ring. At least one axial pressure element in the present exemplary embodiment extends in the form of three pressure pins 66 distributed over the circumference, which are axially displaceable in a guide of the cylinder drum 9, between the pressure ring and the carrier piece 19. By means of the compression spring 64, the cylinder drum 9 is thus acted upon elastically against the control plate 46 and the carrier piece 19 against the retraction plate 17 and consequently also the swash plate 16 against the support 23. A comparable purpose could also advantageously be achieved by, for example, compression springs arranged in the cylinder bores 11, which act on the pistons 12 in the direction of the swash plate 16.
  • The connection plate 3 is designed such that it can be mounted rotated by 180 ° about the central axis 4. This applies in particular to the four fastening screws 67 evenly distributed on a pitch circle in the present exemplary embodiment and the configurations relating to the control arrangement, such as the kidney-shaped suction or pressure channel sections 51, 52, the pin connection between the connecting plate 3 and the control plate 46 and the general with 68 designated centering with a round cross-section 69 on the connecting plate 3, which roughly encloses in the cross-section also round cavity 71 of the housing. The connection plate 3 can thus be rotated and loosened after loosening and removing the fastening screws 67 by 180 °. By simultaneously flipping the control plate 46 into the other or correct functional position, the axial piston machine 1 can be adapted in a simple manner to a reversal of the conveying direction arrange the suction opening 53, which is larger in cross section, into the position predetermined by the reversal of the direction of flow, namely either on one side or the other of the axial piston machine 1, so that trouble-free suction or a trouble-free filling of the suction piston cylinders is achieved.
  • In the present embodiment, the connection plate 3 is made of drawn profile material, preferably a square cross-section. This enables cost-effective production. The fastening screws 67 are arranged in an opposite position in the corner region of the connection plate 3.
  • The assembly or disassembly of the swash plate 16 is very simple, because after removal of the connection plate 3 both individually and on the drive shaft 5 as a pre-assembled unit inserted from the open side of the housing into the housing part 2 and can be removed in the opposite direction .
  • In the present exemplary embodiment, a valve, generally designated 72, is provided for adjusting the delivery rate of the axial piston pump 1, with which it is possible to regulate the delivery rate setting in dependence on the existing working pressure in such a way that the delivery rate decreases with increasing working pressure and the delivery rate increases with falling working pressure ( Pressure control) or the flow rate is only limited depending on the pressure.
  • For this purpose, the valve 72 is arranged in a line connecting the pressure channel 52 with the working spaces 73 of the adjusting cylinder, generally designated 74, in order to regulate or control the action on the adjusting piston 33. This consists of several sections and Connection channel designated 75 is connected to the pressure channel 52 in the area of the connection plate 3. In order to ensure the hydraulic supply of the adjusting cylinders 74 and the decrease in the working pressure even with the two existing mounting positions of the connecting plate 3 rotated relative to one another, two connecting channel branches 76, 77 drilled and closed from outside are provided in the connecting plate 3 (FIG. 5). provided, of which the one connecting channel branch 76 corresponds in one assembly position and the other connecting channel branch 77 in the other mounting position of the connecting plate 3 rotated by 180 ° at the interface designated 78 (FIG. 1) of the connecting channel 75. This interface 78 is located in the parting line between the housing part 2 and the connection plate 3, and it is sealed off from the parting line in a manner not shown.
  • From this interface 78, the connecting channel 75 initially runs axially in the housing part 2 in the region of the valve 72, which is attached laterally and preferably symmetrically to an attachment surface 79 and is fastened in a manner not shown, the valve housing of which is generally designated 81. In the present exemplary embodiment, the valve 72 has a valve slide 82 with a collar which has control edges on both sides and which forms a variable valve opening with a connecting channel section 87 extending from the bore 86 receiving the slide 82 to the working spaces 73. The slide 82 is urged at its upper end in FIG. 1 by a spring 89 into a position closing the valve opening. If a or a certain working pressure is present, the slide 82 is pressed up against the spring 89, as a result of which the passage on the connecting channel section 87 is opened and the adjusting pistons 33 are hydraulically extended via connecting channel branches 91, 92 (FIG. 2) in order to reduce or limit the delivery rate. The connecting channel sections 91, 92 are each connected via a circumferential groove 93 and a radial and axial connecting channel section 94.95 (FIG. 1) in the adjusting piston 33 to the working spaces 73 of the adjusting cylinders 74.
  • The venting of the adjusting cylinders 74 and of the cavity 97 receiving the spring 89 and a pressure piece 96 is ensured by venting channel sections 98, 99, 100 which are connected to the housing cavity 71 of the pump housing. In the present exemplary embodiment, the ventilation duct section 98 is formed by the bore section 86 lying behind the collar, i.e. this ventilation duct section 98 starts from the valve opening and is closed when the adjusting piston 33 is acted upon by the collar.
  • The biasing force of the spring 89 is adjustable by means of an adjusting screw 101, against which the spring 89 is supported via a spring actuator 102. The adjusting screw 101 can be secured by a nut 103.
  • It is possible within the scope of the invention to design the valve 72 and to make the arrangement such that it can adjust the swash plate 16 between only two positions, namely between the maximum and minimum settings.
  • Within the scope of the invention, it is also possible to use a control disk as control plate 46, the control kidneys 47, 48 of which are arranged symmetrically with respect to the transverse plane 36, which is also designated in FIG. 5. It should be noted in this regard that the suction opening 53 which is larger in cross section, the discharge opening 104 which is smaller in cross section, the suction and pressure channels 51, 52 and the control kidneys 47, 48 in FIG. 1 are shown rotated by 90 ° in order to improve understanding, which is illustrated by a broken line. In reality, the aforementioned design features lie on both sides of the transverse plane 36 (see FIG. 5), which also represents the sectional plane according to FIG. 1, and in which the transverse axis 58 also lies.
  • Depending on the application of the axial piston pump 1, it is also not absolutely necessary to provide pressure compensation notches in the control disk 46. In such a case, the adjustment of the axial piston machine 1 with respect to the implementation of the control disk 46 can also be carried out in that the control disk or control plate 46 is rotated about the central axis 4 by essentially 180 °, in contrast to the folding in the exemplary embodiment described above. Such an embodiment is thus also functional in order to adapt the axial piston pump 1 to the reversal of the conveying direction.
  • In the exemplary embodiment according to FIG. 1, the reversal of the conveying direction is achieved by changing the direction of rotation of the drive shaft 5. However, a reversal of the conveying direction can also be achieved in that the existing adjusting device of the axial piston pump, in contrast to the exemplary embodiment according to FIG. 1, can be adjusted beyond the zero point.

Claims (14)

1. Axial piston pump of constant or adjustable flow rate, in particular of the swash plate type, with a two-part housing, namely a housing part that directly or indirectly accommodates the piston and a connecting part through which the pressure channel and the suction channel extend, the suction channel increasing in cross section compared to the pressure channel Has suction opening,
characterized,
that the connecting part (3) can optionally be attached to the housing part 82) in two positions rotated relative to one another by essentially 180 ° about the central axis (4) of the axial piston machine (1).
2. Axial piston pump according to claim 1, wherein the pistons are arranged in a rotatable cylinder drum, and a control disk with control openings is arranged between the cylinder drum and the connecting part,
characterized,
that the control disk (46) can optionally be mounted in two assembly positions, which are rotated relative to each other essentially by 180 ° about the central axis (4) of the axial piston pump (1) or about a transverse axis (58) running essentially centrally to the control openings (47, 48) ) are twisted.
3. axial piston pump according to claim 2,
characterized,
that the control openings (47, 48) in the control disk (46) are slightly offset in the circumferential direction with respect to the transverse axis (58) (angle b).
4. axial piston machine according to claim 2 or 3,
characterized,
that the control disk (46) has pressure compensation channels (55, 56) on both ends at the ends opposite the direction of rotation (54) of the axial piston pump (1).
5. axial piston pump according to at least one of the preceding claims,
characterized,
that the swash plate (16) is adjustable by an adjusting cylinder (74) which is connected to the pressure channel (52) by a connecting channel (75) extending through the housing part (2) and the connecting part (3) within the connecting part (3) , wherein the connecting channel (75) in the area of the connecting part (3) has two connecting channel sections (76, 77), one of which connecting channel branch (76) in one mounting position and the other connecting channel branch (77) in the other mounting position of the connecting part (3 ) corresponds to the section of the connecting channel in the dividing joint (78) which extends in the housing part (2).
6. Axial piston pump according to claim 5
characterized,
that the adjusting cylinder (74) is integrated in the flange or bottom of the housing part (2).
7. Axial piston pump according to claim 5 or 6, characterized in
that two adjusting cylinders (74) are provided, the adjusting pistons (33) of which are arranged side by side on an imaginary pitch circle.
8. axial piston pump according to at least one of claims 5 to 7,
characterized,
that the at least one adjusting cylinder (74) is controlled or regulated by a control or regulating valve (72) acted upon by the working pressure.
9. axial piston pump according to claim 8,
characterized,
that the control or regulating valve (72) is arranged on the side of the housing part (2) opposite the adjusting cylinder (74), in particular in a position symmetrical to two existing adjusting cylinders (74).
10. axial piston pump according to at least one of claims 1 to 9,
characterized,
that the swash plate (16) on two spaced apart bearing pieces (24) with free towards the pistons, spherical bearing surfaces (28) is loosely arranged between the bearing pieces (24) and the piston (12), which is characterized by the Bearing pieces (24) extending pivot axis (22) has a distance (a) from the corresponding direction of force (32) of the pistons (12) and the at least one adjusting piston (33) loosely against the side of the swash plate (16) facing away from the piston (12) presses.
11. axial piston pump according to claim 10,
characterized,
that the bearing pieces (24) are shaped like mushrooms and are inserted with their pins (25) into holes (26) which are formed in the housing part (2) or add-on parts thereof.
12. Axial piston pump according to at least one of claims 5 to 11,
characterized,
that the maximum swivel position of the swash plate (16) is limited by the adjusting piston (33) fully inserted against a stop.
13. axial piston pump according to at least one of claims 5 to 12,
characterized,
that the swash plate (16) on the side on which the at least one adjusting cylinder (74) is arranged is assigned at least one stop (37) to limit its minimum pivoting position, which is preferably screwed in from the outside into the housing part (2) (38) is formed.
14. axial piston pump according to at least one of claims 10 to 13,
characterized,
that the heads of the pistons (12) are pivotally mounted in sliding shoes (13) which bear against the drive pulley (16), that one each extends from the recess (27) through the swashplate (16), on the inclined surface (15) of which Escaping lubrication channel is provided, which corresponds to lubrication channels, which extend longitudinally through the pistons (12) and the sliding shoes (13).
EP19880120650 1987-12-18 1988-12-09 Axial piston pump Expired - Lifetime EP0320822B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE3743125 1987-12-18
DE19873743125 DE3743125A1 (en) 1987-12-18 1987-12-18 AXIAL PISTON PUMP

Publications (3)

Publication Number Publication Date
EP0320822A1 true EP0320822A1 (en) 1989-06-21
EP0320822B1 EP0320822B1 (en) 1991-03-06
EP0320822B2 EP0320822B2 (en) 1997-01-29

Family

ID=6343006

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880120650 Expired - Lifetime EP0320822B2 (en) 1987-12-18 1988-12-09 Axial piston pump

Country Status (4)

Country Link
US (1) US4934253A (en)
EP (1) EP0320822B2 (en)
JP (1) JP2554927B2 (en)
DE (2) DE3743125A1 (en)

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WO1996001947A1 (en) * 1994-07-08 1996-01-25 Danfoss A/S A piston with a slide shoe and method of manufacturing same
DE19643389C1 (en) * 1996-10-21 1998-01-02 Brueninghaus Hydromatik Gmbh Axial piston machine with adjustable control plate
WO2008071374A1 (en) * 2006-12-11 2008-06-19 Robert Bosch Gmbh Axial piston machine and control plate for an axial piston machine
WO2014187546A1 (en) * 2013-05-22 2014-11-27 Hydac Drive Center Gmbh Axial piston pump

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DE3942189C1 (en) * 1989-12-20 1991-09-05 Hydromatik Gmbh, 7915 Elchingen, De
DE4229007C2 (en) * 1992-08-31 2002-06-13 Linde Ag Axial piston machine in swash plate design
DE4301121C2 (en) * 1993-01-18 1995-03-30 Danfoss As Hydraulic axial piston machine with a swash plate
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JP3179296B2 (en) * 1994-08-11 2001-06-25 株式会社ゼクセルヴァレオクライメートコントロール Hinge ball of variable displacement rocking plate compressor
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US7082762B1 (en) 1999-07-16 2006-08-01 Hydro-Gear Limited Partnership Pump
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Also Published As

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EP0320822B2 (en) 1997-01-29
DE3743125A1 (en) 1989-07-06
EP0320822B1 (en) 1991-03-06
JP2554927B2 (en) 1996-11-20
DE3861956D1 (en) 1991-04-11
JPH01200068A (en) 1989-08-11
US4934253A (en) 1990-06-19

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