EP1039127B1 - Machine axiale à pistons - Google Patents

Machine axiale à pistons Download PDF

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Publication number
EP1039127B1
EP1039127B1 EP00104963A EP00104963A EP1039127B1 EP 1039127 B1 EP1039127 B1 EP 1039127B1 EP 00104963 A EP00104963 A EP 00104963A EP 00104963 A EP00104963 A EP 00104963A EP 1039127 B1 EP1039127 B1 EP 1039127B1
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston engine
swash plate
engine according
spring
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
EP00104963A
Other languages
German (de)
English (en)
Other versions
EP1039127A3 (fr
EP1039127A2 (fr
Inventor
Ralf Dr. Lemmen
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
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1039127A2 publication Critical patent/EP1039127A2/fr
Publication of EP1039127A3 publication Critical patent/EP1039127A3/fr
Application granted granted Critical
Publication of EP1039127B1 publication Critical patent/EP1039127B1/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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block

Definitions

  • the invention relates to an axial piston machine the preamble of claim 1.
  • the invention is based on the object Axial piston machine of the type described above so to turn off that the construction and manufacturing effort, the Reduced control effort and effort are.
  • the axial piston according to the invention is a Provided spring element, which is not only on the slant or swash plate acting second torque generated by that of the resulting piston force the oblique or swash plate exerted first Torque is opposite, but the spring is too a compression spring in the housing on the cylinder block opposite side of the oblique or swash plate arranged and between the oblique or swash plate and one connected to the housing of the axial piston machine Component is effective.
  • the inventive design is particularly suitable for Power limitation of the axial piston machine, wherein the Axial piston machine is designed so that they are in Equilibrium state of torques about their maximum Delivers performance. This will overload the Axial piston machine automatically avoided.
  • FIG. 1 is the axial piston machine according to the invention only partially shown.
  • Axial piston machine 1 is in so-called Swash plate design is formed, and it includes a Cylinder block 2, in which several, on a pitch circle evenly distributed, approximately axial Cylinder bores 3 are provided.
  • piston 4 are arranged longitudinally movable.
  • the cylinder bores 3 are connected by connecting channels 5 with kidney-shaped control openings 6a, 6b in a control disc 7 connected in a partially illustrated Housing 8 is arranged stationary.
  • the cylinder block 2 is on a not shown drive shaft around his Longitudinal center axis rotatably mounted in the housing 8, so that the Cylinder bores 3 cyclically with one at the associated Control port 6a connected, not shown Low pressure line and one at the respectively associated Control port 6b connected, also not represented high-pressure line can be connected.
  • the pistons 4 are facing away from the control disk 7 Ends articulated supported on a swash plate 9; in the present embodiment by means of sliding shoes 11, on a flat sliding surface 12 of the swash plate. 9 abutment and in each case by a ball joint connection 13 with preferably formed as a hollow piston piston 4th are connected.
  • the working spaces of the pistons 4 and their Piston recesses 14 are connected by axial connecting channels 15th in the piston 4 and thus corresponding axial Connecting channels 16 in the shoes 11 for hydrostatic discharge with at the contact surfaces of the Sliding shoes 11 provided pressure pockets 17 connected.
  • a known retraction device denotes that the sliding blocks 11 in permanent contact the sliding surface 12 of the swash plate 9 holds.
  • the retraction device 18 by a sliding blocks 11 in a conventional manner behind-reaching perforated disc 19 formed with a central, spherical segmental dome 21 on one spherical section saddle 22, z.
  • B. a ring on the Shaft not shown, pivotable on all sides is stored. It can be a shoot shaft that the end wall 8a of the housing 8 in a round hole 8b interspersed and z. B. stored by means of a rolling bearing and sealed.
  • the swash plate 9 is a transversely to the Longitudinal axis 23 of the axial piston machine 1 extending Swivel axis 24 in an only hinted illustration Swivel bearing 25, z. B. by means of both sides of Swash plate 9 arranged cylindrical pivot pin, between a pivot position minimum pivot angle W, in the between the sliding surface 12 and the Longitudinal axis 23 included angle z. B. approximately Is zero, and a pivot position maximum swing angle W1 pivotally mounted.
  • the pivot axis 24th with respect to the longitudinal central axis 23 of the cylinder block 2 order the dimension eK transversely offset.
  • the arrangement is made that depends on the number of piston forces in the range a resulting pressure piston resulting piston force Kr offset with respect to the pivot axis 24 in the radial direction is that the resulting piston force Kr the swash plate 9 is acted upon by a torque M1, which is the Swash plate 9 minimal in their pivot position Swivel angle W seeks to pivot.
  • a torque M1 which is the Swash plate 9 minimal in their pivot position Swivel angle W seeks to pivot.
  • one is elastically resilient effective pivoting device 26th provided, the swash plate 9 with a torque M2 applied, which is opposite to the torque M1.
  • Effective element of the return pivot device 26 is a Spring 27, in particular a spiral spring, here a Compression spring which is supported on the housing 8 and with her elastic spring force on the swash plate 9 attacks.
  • e1 radial effective distance of the adjusting device 26 of the Pivot axis 24 is denoted by e1 and in Embodiment larger than the offset dimension eK.
  • each a pivot stop 31, 32nd provided, each by an adjustment preferably is adjustable to a certain amount of Throughput volume in the maximum and minimum To be able to adjust the swivel end position.
  • the adjustable pivot stops 31, 32 formed by adjusting screws 33, which to both Side of the longitudinal center axis 23 in each case in one Threaded hole 34 are screwed into the end wall 8a, by a screw-engaging element 35, z.
  • one Screw head or a screw slot are rotatable and by a securing element, for. B.
  • a lock nut 36 can be secured against unintentional loosening.
  • the adjusting screws 33 in To arrange threaded holes 34, which are approximately axial Arrangement in the swash plate 9 and / or in the end wall 8a, and preferably in each case in the end region of Swash plate 9. This results in an elastic compliant abutment forming return pivot 26th an arrangement point between the pivot stop 32 for the minimum position of the swash plate 9 and the effective distance eK of the resulting piston force Kr.
  • the piston is the fourth facing away back 37 of the swash plate 9 wedge-shaped formed, wherein the two wedge surfaces 37a, 37b a Include obtuse angle in the direction of the Cylinder block 2 is open, with the wedge surfaces 37a, 37b so are arranged that when planting a wedge surface 37 a the Swash plate 9 in its minimum pivoting position and at the plant of the other wedge surface 37b on Swivel stop 31, the swash plate 9 in her maximum pivot position is located.
  • the apex 38 can on the one hand in the pivot axis 24 and the other at the Inside 8c of the end wall 8a are located.
  • the maximum power of the axial piston machine is shown in FIG. 3 as a dot-dashed, hyperbolic curved line N shown.
  • the course of the power curve N is located between the minimum and the maximum working pressure p1, p2 in the vicinity of the oblique in Fig. 3 Section of the enforcement volume characteristic V.
  • Exceeding the maximum power curve N can by a pressure cut through a Pressure relief valve to be prevented at the limit pressure p3.
  • the above-described embodiment allows a passive pressure-dependent throughput volume adjustment and adjustment, which works in pump mode and in motor operation. This is achieved by a pressure-dependent and by the respective balance of torques M1 and M2 predetermined adjustment and adjustment of the swash plate 9 in the range between two Schwenkendwolfen, namely passive against the elastic abutment, here the spring 27, takes place.
  • the adjustment principle for a reduction of the swivel angle of the Swash plate 9 designed with increasing working pressure.
  • the Point of attack of the resulting piston force Kr and the Point of attack of the elastic abutment or the Rear pivoting device 26 mirror image of the pivot axis 24, d. H. to the side where the resulting piston force Kr the swash plate 9 in her Schwenkend sued maximum swing angle W1 applied.
  • Adjusting device 39 With the bias of the spring 27th can be adjusted. It is about a Adjusting screw 41 with a rotary engagement element, z. B. a transverse slot, which has an adjustable limit for the Spring 27 forms and in the present embodiment in the recess 28 in the end wall 8a projects from the outside, in one the bottom of the recess 28 threaded through threaded hole 42 and screwed through a Secured securing element, in particular by a screwed on the outside of the adjusting screw 41 Lock nut 43.
  • a correspondingly effective Damping element 44 may each be on the swash plate 9 or be arranged on the end wall 8a.
  • Fig. 1 is the Damping element 44 integrated in the swash plate 9. It is by a damping cylinder 45 in the form of an approximately axial cylinder bore 46 formed in which a piston 47th is mounted displaceably sealed.
  • the damping cylinder 45 is formed as a blind bore, which on the wedge surface 37a of the swash plate 9 opens.
  • the damping piston 47 is by means of a likewise in the damping cylinder 42nd arranged return spring 48 in its extension direction and against a stationary counterpart, here against the front wall 8a, preferably against the free end of the adjusting screw 33, preloaded.
  • the working chamber of the damping cylinder 45 is via a check valve 49 in an inlet channel 51 with the surrounding the swash plate 9 and the cylinder block 2 Housing interior 52 connected to the z. B. as a leak fluid collecting space serves and low with a fluid accordingly Pressure, especially hydraulic oil, is filled.
  • the Working chamber of the damping cylinder 45 is connected via a Throttle element 53 in addition to the housing interior 52nd connected.
  • the throttle element 53 is shown in the Embodiment as a hole with a relatively small Cross section formed.
  • the inlet channel 51 and the Check valve 49 are thus parallel to the Throttle 53 arranged.
  • the Cylinder bore 46 and the damping piston 47 as long dimensioned that the damping piston 47 relatively far can protrude from the cylinder bore 46 and permanently on associated pivot stop 31, 32 can rest. At this Design results in a damping effect over the entire swivel range. It is then the power of To include return spring 48 in the torques M1, M2, if this restoring force is relatively large. Because it for an extension movement of the damping piston 47, respectively requires only a small spring force, this spring force neglected if it is low.
  • Fig. 2 is an example of a damping element 44 in the End wall 8a integrated arranged to illustrate that the damping elements 44 both on the swash plate 9 as can also be arranged on the end wall 8a.
  • It can an adjusting screw 33 opposite in the Swash plate 9 may be arranged.
  • the adjusting screw 33 and the associated Setting device accessible only from the inside and thus before protected against unauthorized access. This also applies to the adjusting device 39 for adjusting the spring force.
  • the damping element can also be structurally combined with the spring 27 and z. B. in the recess 29th be arranged.

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

Claims (17)

  1. Machine à pistons axiaux (1) dotée d'un bloc à cylindres (2), monté rotatif sur un arbre d'entraínement dans un carter (8), et dans lequel sont prévus des perçages pour cylindres (3), dans lesquels peuvent bouger en étant guidés des pistons (4), qui s'appuient contre un plateau oscillant / incliné (9), pour effectuer un mouvement de va et vient, ledit plateau oscillant / incliné (9) étant monté orientable autour d'un axe d'orientation (24), entre une position d'orientation de débit minimal et une position d'orientation de débit maximal, l'axe d'orientation (24) étant décalé (eK) par rapport à la résultante des forces de piston (Kr) exercées par les pistons (4), dirigée vers le plateau oscillant / incliné (9), de telle sorte que la résultante des forces de piston (Kr) engendre un premier moment de rotation (M1) s'exerçant sur le plateau oscillant /incliné (9),
    un ressort (27) étant prévu, pour engendrer un deuxième moment de rotation (M2), s'exerçant sur le plateau oscillant / incliné (9) en s'opposant au premier moment de rotation (M1),
    le ressort (27) étant disposé, par rapport à l'axe d'orientation (24), du coté de la machine à pistons axiaux (1) où la résultante des forces de pistons (Kr) est décalée et, le deuxième moment de rotation du ressort (27) poussant le plateau oscillant /incliné (9) dans sa position d'orientation de débit maximum,
    caractérisée en ce que,
    le ressort est un ressort de pression, qui est disposé dans le carter (8), sur la face du plateau oscillant / incliné (9) opposée au bloc de cylindres (2) et qui agit entre le plateau oscillant / incliné (9) et un élément de construction lié au carter (8) de la machine à pistons axiaux (1).
  2. Machine à pistons axiaux selon la revendication 1
    caractérisée en ce que,
    l'élément de construction lié au carter (8) de la machine à pistons axiaux (1) est une face avant (8a) de carter.
  3. Machine à pistons axiaux selon l'une des revendications précédentes
    caractérisée en ce que,
    la force du ressort (27) peut être réglée au moyen d'un dispositif de réglage (39).
  4. Machine à pistons axiaux selon l'une des revendications précédentes
    caractérisée en ce que,
    le ressort (27) consiste en un ressort spiral.
  5. Machine à pistons axiaux selon l'une des revendications précédentes
    caractérisée en ce que
    le ressort (27) est disposé par ses extrémités dans un creux (28, 29) dan le plateau oscillant / incliné (9) et/ou dans la face avant de carter (8a).
  6. Machine à pistons axiaux selon l'une des revendications 3 à 5
    caractérisée en ce que
    le dispositif de réglage (39) est accessible depuis l'extérieur d'un carter (8) de la machine à pistons axiaux (1).
  7. Machine à pistons axiaux selon la revendication 6
    caractérisée en ce que
    le dispositif de réglage (39) présente une vis de réglage (41), qui traverse de préférence une face avant (8a) du carter(8).
  8. Machine à pistons axiaux selon l'une des revendications précédentes
    caractérisée en ce que
    une butée (31, 32) est attribuée à chacune des positions d'orientation de débit maximal et/ou de débit minimal.
  9. Machine à pistons axiaux selon la revendication 8
    caractérisée en ce que
    la butée, ou les butées (31, 32), peut, resp. peuvent, être réglées au moyen d'un dispositif de réglage qui est, resp. sont, accessible depuis l'extérieur d'un carter (8) de la machine à pistons axiaux (1).
  10. Machine à pistons axiaux selon la revendication 9
    caractérisée en ce que
    la ou les butées (31, 32) est, resp. sont, formées chacune par une vis de réglage (33).
  11. Machine à pistons axiaux selon la revendication 10
    caractérisée en ce que
    la vis de réglage (33) est disposée dans le plateau oscillant / incliné (9) ou dans une paroi du carter (8), en particulier dans une face avant (8a).
  12. Machine à pistons axiaux selon l'une des revendications 8 à 11
    caractérisée en ce que
    un élément d'amortissement (44) est affecté à la butée ou à chacune des butées (31, 32).
  13. Machine à pistons axiaux selon la revendication 12
    caractérisée en ce que
    l'élément d'amortissement (44) est formé d'un piston d'amortissement (47), qui est monté coulissant dans un cylindre d'amortissement (45), qui y limite une chambre de travail et qui est contraint par un ressort (48) en position d'extension, la chambre de travail étant reliée à un réservoir de fluide au moyen d'une sortie étranglée et d'une admission, qui lors de la poussée du piston d'amortissement (47) se ferme automatiquement.
  14. Machine à pistons axiaux selon la revendication 13
    caractérisée en ce que
    le cylindre d'amortissement (45) est disposé dans le plateau oscillant / incliné (9) ou dans une face avant (8a) d'un carter (8) de la machine à pistons axiaux (1) faisant face au plateau oscillant / incliné.
  15. Machine à pistons axiaux selon la revendication 13 ou 14
    caractérisée en ce que
    la sortie et l'admission sont reliées à l'espace intérieur (52) du carter.
  16. Machine à pistons axiaux selon l'une des revendications 12 à 15
    caractérisée en ce que
    le ressort (27) est un élément constitutif de l'élément d'amortissement (44).
  17. Machine à pistons axiaux selon l'une des revendications précédentes
    caractérisée en ce que,
    la machine à pistons axiaux (1) atteint pratiquement une puissance maximale prédéfinie, en situation d'équilibre des deux moments (M1, M2).
EP00104963A 1999-03-19 2000-03-08 Machine axiale à pistons Expired - Lifetime EP1039127B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19912509A DE19912509C2 (de) 1999-03-19 1999-03-19 Axialkolbenmaschine
DE19912509 1999-03-19

Publications (3)

Publication Number Publication Date
EP1039127A2 EP1039127A2 (fr) 2000-09-27
EP1039127A3 EP1039127A3 (fr) 2001-02-28
EP1039127B1 true EP1039127B1 (fr) 2005-08-17

Family

ID=7901703

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00104963A Expired - Lifetime EP1039127B1 (fr) 1999-03-19 2000-03-08 Machine axiale à pistons

Country Status (2)

Country Link
EP (1) EP1039127B1 (fr)
DE (2) DE19912509C2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012021320A1 (de) * 2012-10-31 2014-04-30 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine mit einer derartigen Verstellvorrichtung
JP6248843B2 (ja) * 2014-07-16 2017-12-20 株式会社豊田自動織機 可変容量型ピストンポンプ
CN108361165B (zh) * 2018-04-09 2019-08-13 李涌权 容量可调型流体泵

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1521884A (en) * 1923-02-14 1925-01-06 Jr Henry B Higgins Pump or motor
US2935951A (en) * 1953-01-29 1960-05-10 Daimler Benz Ag Pump means for hydraulic servo systems
US3282225A (en) * 1965-06-04 1966-11-01 Sunstrand Corp Pump swashplate control
US4945817A (en) * 1989-10-24 1990-08-07 General Motors Corporation Axial piston device
JPH04284180A (ja) * 1991-03-11 1992-10-08 Toyota Autom Loom Works Ltd 可変容量ピストンポンプ
DE19645580C1 (de) * 1996-11-05 1998-04-02 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit Dämpfungselement für die Schräg- oder Taumelscheibe

Also Published As

Publication number Publication date
DE19912509A1 (de) 2000-09-28
EP1039127A3 (fr) 2001-02-28
DE50010945D1 (de) 2005-09-22
DE19912509C2 (de) 2002-11-07
EP1039127A2 (fr) 2000-09-27

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