EP0320822B2 - Pompe à pistons axiaux - Google Patents

Pompe à pistons axiaux Download PDF

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Publication number
EP0320822B2
EP0320822B2 EP88120650A EP88120650A EP0320822B2 EP 0320822 B2 EP0320822 B2 EP 0320822B2 EP 88120650 A EP88120650 A EP 88120650A EP 88120650 A EP88120650 A EP 88120650A EP 0320822 B2 EP0320822 B2 EP 0320822B2
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston pump
pistons
pump according
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.)
Expired - Lifetime
Application number
EP88120650A
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German (de)
English (en)
Other versions
EP0320822A1 (fr
EP0320822B1 (fr
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 Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik 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
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Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0320822A1 publication Critical patent/EP0320822A1/fr
Application granted granted Critical
Publication of EP0320822B1 publication Critical patent/EP0320822B1/fr
Publication of EP0320822B2 publication Critical patent/EP0320822B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B1/2042—Valves

Definitions

  • the invention relates to an axial piston pump according to DE-C-3233579, from which the preamble of claim 1 is based.
  • Such an axial piston pump can be adapted to the desired delivery direction.
  • Such an embodiment 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 has for its object to design an axial piston pump of the type mentioned so that it can be adapted to the other direction of delivery with less effort.
  • the axial piston pump can be adjusted by rotating the control part consisting of the control disk and the connecting part through 180 ° to the desired delivery direction. There is therefore no need for an additional connecting part or an additional control disk, as is the case with the known configurations.
  • the connection 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, however, this problem can be solved in a simple manner by using flexible connecting lines or suitable connecting line sections.
  • the invention also makes it possible to adapt such axial piston pumps, the control disks of which are designed asymmetrically with respect to the control openings (control kidneys) or have so-called pressure compensation channels in a manner known per se.
  • 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 and the control disk 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 pump serving 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.
  • 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 swash plate is pivoted out by the engine forces of the axial piston pump, so that no additional pivoting mechanism is required.
  • the swash plate is simple and easy to assemble or disassemble.
  • the features of claim 10 ensure simple and inexpensive manufacture, the bearing bodies being able to be produced from finished balls by reworking such as turning.
  • Claims 11 and 12 relate to mechanical stops, in particular to prevent the swivel plate from overshooting when swiveling in at high positioning speeds.
  • 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 design enables low-friction and low-wear operation with fast operating times.
  • the axial piston pump generally designated 1 in FIG. 1, has a two-part one made of a cup-shaped one Housing part 2 and a connection plate 3 existing housing in which a drive shaft 5 extending along the central axis 4 is mounted in roller bearings 6, 7, one of which is assigned to the cup-shaped housing part 2 and the other of the connection plate 3 is on the drive shaft 5 on a multi-wedge section denoted by 8, a cylinder drum 9 is mounted, which has a plurality of cylinder bores 11, evenly distributed on a pitch circle, in which pistons 12 are received.
  • the pistons 12 have ball heads 13 which engage in sliding shoes 14 which bear against the sliding surface 15 of a swash plate 16.
  • 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 round cross-section pin 25 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.
  • 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 counterclockwise with a torque according to FIG of the cup-shaped housing part 2 arranged and in cylinder bores 34 axially parallel to the drive shaft 5, ie are hydraulically displaceable in the direction of the double arrow 35.
  • the adjusting pistons 33 are arranged opposite the effective resulting piston force 32, i.e.
  • the swash plate 16 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 quantity settings. To limit the maximum pivoting position, stops 37 are arranged on both sides of the axial transverse plane 36 approximately opposite 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 pivot bearings 23 are each connected to the oil-carrying system of the axial piston machine 1 by a lubrication channel 39 which extends from the recess 27 and crosses the bearing shell 29 and the swash plate 16 and is thus oil-lubricated.
  • 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 axially known channels 43, 44 in the sliding shoes 14 and the pistons 12. In this way, when the axial piston pump 1 is in operation, 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 swashplate 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 or pressure channels 51, 52 also adjoin in the connecting plate 3, of which the suction channel 51 is opposite the pressure channel 52 with an enlarged end cross section, namely a large suction opening 53, here a connection for a suction line, not shown.
  • 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. 3, the purpose of which is to improve the sudden effect of the pressure changes in the working spaces 45 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.
  • the control plate 46 has pressure compensation notches 56 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 notches (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 60 (FIG. 5) which preferably extends from the connecting plate 3 and which fits into a blind hole or through-hole 61 in the control plate 46.
  • control plate 46 can optionally be attached with its one or the other end face to the connection plate 3, namely 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.
  • 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 predetermined 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.
  • control kidneys 47, 48 are not symmetrical with respect to the arrangement predetermined by the control channels 57, namely 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 46.
  • control plate 46 is configured in parallel.
  • 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 illustrated in FIG. 1 by arrows 62 and 63.
  • 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 around the circumference, which are axially displaceable in a guide of the cylinder drum 9, between the pressure ring and the carrier piece 19.
  • the compression spring 64 By means of the compression spring 64, the cylinder drum 9 is thus elastically acted 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 e.g. compression springs arranged in the cylinder bores 11 are applied, which act on the pistons 12 in the direction of the swash plate 16.
  • 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 connection plate 3 and the control plate 46 and the general with 68 designated centering with a round in cross-section 69 on the connecting plate 3, which roughly surrounds the cavity 71 of the housing, which is also round in cross-section.
  • the connection plate 3 can thus be rotated and loosened after loosening and removing the fastening screws 67 by 180 °.
  • the axial piston machine 1 can be adapted in a simple manner to a reversal of the conveying direction, and indeed the larger suction opening 53 in cross section can be arranged in the position predetermined by the reversal of the flow direction, namely optionally on one or the other side of the axial piston machine 1, so that trouble-free suction or trouble-free filling of the suction piston cylinders is achieved.
  • 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 removing the Connection plate 3 both individually and on the drive shaft 5 as a pre-assembled unit inserted into the housing part 2 from the open side of the housing and can be removed again in the opposite direction.
  • 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 as a function of the existing working pressure in such a way that the delivery rate decreases with increasing working pressure and the delivery rate increases with decreasing working pressure ( Pressure control) or the delivery rate is only limited depending on the pressure.
  • valve 72 is arranged in a line connecting the pressure channel 52 with the working spaces 73 of the adjusting cylinders, generally designated 74, in order to regulate or control the action on the adjusting pistons 33.
  • This connecting channel which consists of several sections and is designated by 75, is connected to the pressure channel 52 in the region of the connecting plate 3.
  • two connecting channel branches 76, 77 drilled and closed from the outside are in the connecting plate 3 (FIG. 5).
  • 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 connecting plate 3, and it is sealed off from the parting line in a manner not shown.
  • 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.
  • 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.
  • connecting channel branches 91, 92 (FIG. 2) in order to reduce or limit the delivery rate.
  • the connecting duct sections 91, 92 are each connected to the working spaces 73 of the adjusting cylinders 74 via a circumferential groove 93 and a radial and axial connecting duct section 94.95 (FIG. 1) in the adjusting piston 33.
  • venting channel sections 98, 99, 100 which are connected to the housing cavity 71 of the pump housing.
  • 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 can be adjusted 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.
  • valve 72 It is possible within the scope of the invention to design the valve 72 and to arrange it in such a way that it can adjust the swash plate 16 between only two positions, namely between the maximum and minimum settings.
  • the larger suction opening 53, the smaller discharge opening 104, 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.
  • 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.
  • the reversal of the conveying direction is achieved by changing the direction of rotation of the drive shaft 5.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (13)

  1. Pompe à pistons axiaux, à débit constant ou réglable, en particulier du type à plateau oblique, avec un carter en deux parties, à savoir une partie recevant les pistons, directement ou indirectement, et une partie de raccordement à travers laquelle s'étendent le canal de refoulement et le canal d'aspiration, le canal d'aspiration présentant une ouverture d'aspiration de section agrandie par rapport au canal de refoulement, les pistons étant placés dans un barillet rotatif et un plateau de commande avec des ouvertures de commande étant placé entre le barillet et la partie de raccordement, caractérisée en ce que le plateau de commande (46) peut être monté au choix dans deux positions de montage qui sont tournées l'une par rapport à l'autre essentiellement de 180° autour de l'axe médian (4) de la pompe à pistons axiaux (1) et qui sont tournées autour d'un axe transversal (58), s'étendant essentiellement au milieu des ouvertures de commande (47, 48) et en ce que la partie de raccordement (3) peut être montée sur la partie de carter (82), au choix dans deux positions tournées l'une par rapport à l'autre d'essentiellement 180° autour de l'axe médian 4 de la pompe à pistons axiaux (1).
  2. Pompe à pistons axiaux selon la revendication 1, caractérisée en ce que les ouvertures de commande (47, 48) dans le plateau de commande (46) sont légèrement décalées (angle b1) dans le sens périphérique, par rapport à l'axe transversal (58).
  3. Pompe à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que le plateau de commande (46) présente sur ses deux faces, aux extrémités opposées au sens de rotation (54) de la pompe à pistons axiaux (1), des canaux d'égalisation de pression (55, 56).
  4. Pompe à pistons axiaux selon l'une des revendications précédentes, caractérisée en ce que le plateau oblique (16) est réglable au moyen d'un vérin de réglage (74) qui est relié par un canal de liaison (75) s'étendant à travers la partie (2) du carter et la pièce de raccordement (3), avec le canal de refoulement (52) à l'intérieur de la pièce de raccordement (3), le canal de liaison (75) présentant dans la région de la pièce de raccordement (3) deux sections (76, 77) du canal de liaison, dont l'une, la branche (76) du canal de liaison, correspond dans le plan dc jonction (78), et dans une position donnée de montage de la pièce de raccordement (3), à la section du canal de liaison qui s'étend dans la partie (2) du carter, et l'autre branche (77) du canal de liaison correspond, dans le plan de jonction (78) et dans l'autre position de montage de la pièce de raccordement (3), à ladite section du canal de liaison qui s'étend dans la partie (2) du carter.
  5. Pompe à pistons axiaux selon la revendication 4, caractérisée en ce que le vérin de réglage (74) est intégré dans la bride ou dans le fond de la partie (2) du carter.
  6. Pompe à pistons axiaux selon la revendication 4 ou 5, caractérisée en ce que sont prévus deux vérins de réglage (74) dont les pistons de réglage (33) sont disposés côte à côte sur un cercle gradué imaginaire.
  7. Pompe à pistons axiaux selon l'une des revendications 4 à 6, caractérisée en ce qu'au moins un vérin de réglage (74) est commandé ou réglé par une vanne de commande ou de régulation (72) alimentée à la pression de travail.
  8. Pompe à pistons axiaux selon la revendication 7, caractérisée en ce que la vanne de commande ou de régulation (72) est disposée latéralement sur la partie (2) du carter faisant face au vérin de réglage (74), en particulier en une position symétrique par rapport aux deux vérins de réglage (74) existants.
  9. Pompe à pistons axiaux selon l'une des revendications 1 à 8, caractérisée en ce que le plateau oblique (16) est disposé sur deux pièces d'appui (24) présentant une distance entre elles, avec, en direction des pistons, des surfaces d'appui (28) libres, sphériques, sans serrage entre les pièces d'appui (24) et les pistons (12), l'axe d'oscillation (22) s'étendant à travers les pièces d'appui (24) présentant une distance (a) par rapport à la ligne de force (32) correspondante des pistons (12), tandis qu'au moins un piston de réglage (33) appuie, sans serrage, contre la face du plateau oblique (16) opposée à celle dirigée vers les pistons (12).
  10. Pompe à pistons axiaux selon la revendication 9, caractérisée en ce que les pièces d'appui (24) sont formées à la manière d'une tête de champignon et qu'elles sont logées, au moyen de leurs tourillons (25), dans des trous (26) ménagés dans la partie (2) du carter ou dans des pièces annexées à ladite partie du carter.
  11. Pompe à pistons axiaux selon l'une des revendications 4 à 10, caractérisée en ce que la position maximale d'oscillation du plateau oblique (16) est limitée par le fait qu'un piston de réglage (33) est complètement inséré contre une butée.
  12. Pompe à pistons axiaux selon l'une des revendications 4 à 11, caractérisée en ce qu'au plateau oblique (16) est associée, sur la face où est disposé au moins un vérin de réglage (74), au moins une butée (37) pour limiter sa position minimale d'oscillation, cette butée étant de préférence constituée par une vis (38) vissée de l'extérieur dans la partie (2) du carter.
  13. Pompe à pistons axiaux selon l'une des revendications 9 à 12, caractérisée en ce que les têtes des pistons (12) sont montées oscillantes dans des patins (13) reposant sur le plateau d'entraînement (16), et en ce qu'il est prévu chaque fois un canal de graissage s'étendant à partir de l'évidement (27) à travers le plateau oblique (16), et débouchant dans les faces obliques (15), de celui-ci, ce canal correspondant avec des canaux de graissage qui s'étendent longitudinalement à travers les pistons (12) et les patins (13).
EP88120650A 1987-12-18 1988-12-09 Pompe à pistons axiaux Expired - Lifetime EP0320822B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3743125 1987-12-18
DE19873743125 DE3743125A1 (de) 1987-12-18 1987-12-18 Axialkolbenpumpe

Publications (3)

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

Family

ID=6343006

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88120650A Expired - Lifetime EP0320822B2 (fr) 1987-12-18 1988-12-09 Pompe à pistons axiaux

Country Status (4)

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

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Also Published As

Publication number Publication date
EP0320822A1 (fr) 1989-06-21
DE3861956D1 (de) 1991-04-11
DE3743125A1 (de) 1989-07-06
JPH01200068A (ja) 1989-08-11
JP2554927B2 (ja) 1996-11-20
EP0320822B1 (fr) 1991-03-06
US4934253A (en) 1990-06-19

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