EP1287232B1 - Moteur a piston axial - Google Patents

Moteur a piston axial Download PDF

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Publication number
EP1287232B1
EP1287232B1 EP01915304A EP01915304A EP1287232B1 EP 1287232 B1 EP1287232 B1 EP 1287232B1 EP 01915304 A EP01915304 A EP 01915304A EP 01915304 A EP01915304 A EP 01915304A EP 1287232 B1 EP1287232 B1 EP 1287232B1
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston engine
engine according
tooth
disposed
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
EP01915304A
Other languages
German (de)
English (en)
Other versions
EP1287232A1 (fr
Inventor
Rainer Stölzer
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 EP1287232A1 publication Critical patent/EP1287232A1/fr
Application granted granted Critical
Publication of EP1287232B1 publication Critical patent/EP1287232B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • 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
    • F01B3/0082—Details
    • 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
    • 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
    • F04B1/2092—Means for connecting rotating cylinder barrels and rotating inclined swash plates

Definitions

  • the housing interior As an intermediate collecting container for leakage fluid.
  • a certain amount of leakage oil accumulates in the interior of the housing, which is under a low pressure and flows through a discharge gap or a discharge channel to a tank.
  • the leakage fluid in the housing interior can serve for the lubrication of moving parts of the axial piston machine. It is also advantageous if the leakage fluid is present as a film between the contact surfaces of non-relatively moving parts, whereby contact corrosion and abrasion resulting from vibrations are avoided or at least reduced. It is also advantageous if the hydraulic fluid can reach the desired lubrication points as unhindered as possible.
  • a barrier in the housing interior, which prevents a desired supply of the fluid to the lubrication point.
  • a barrier forms a multi-tooth coupling between two parts of the axial piston machine in the housing interior.
  • the purpose of a multi-tooth clutch is to connect two parts rigidly, for. B. against a relative rotation to each other.
  • Such a multi-tooth clutch can be provided in the axial piston machine of the type specified between a drive shaft and a cylinder drum mounted thereon. Since a multi-tooth clutch should transmit considerable coupling forces, one is strives to form the adjacent surfaces of the multi-tooth clutch not only in the region of the flanks of the teeth and the tooth gaps so that they are largely close together. As a result, the multi-tooth coupling forms a liquid barrier, which prevents or at least reduces the access of the hydraulic fluid to both sides of the multi-tooth clutch.
  • the multi-tooth coupling forms a barrier which prevents the fluid from flowing from one side to the other side of the multi-tooth coupling. This is particularly problematic in the known embodiment because the fluid is prevented from flowing into a ring clearance between the drive shaft and the cylinder drum.
  • An arranged in the region of a control disc bearings for pivotal mounting of the drive shaft to the respective housing wall is thereby separated from an intensive flow, lubrication and cooling of the hydraulic fluid.
  • the toothing is weakened when the holes for the pressure pins extend through the middle of the teeth or in the area of a pressure pin a tooth is omitted.
  • the invention leads Design thus neither to a significant weakening of the cross section of the teeth nor to a reduction in the surface pressure.
  • the stability and life of the multi-tooth clutch thus remains despite the presence of one or more distributed on the circumference arranged through channels.
  • the cross-sectional shape of the at least one feedthrough channel can be different and adapted to structural conditions.
  • a rounded or semicircular or U-shaped cross-sectional shape is advantageous in order to avoid a notch effect.
  • the cross-sectional shape can also be square or hollow wedge-shaped, which is advantageous for manufacturing reasons and reasons mentioned below.
  • the inventive at least one feedthrough channel can also serve to receive a pin as part of the axial piston machine, for. B. a pre-described pressure pin which extends between two arranged on both sides of the multi-tooth clutch and axially movable components, for. B. between a compression spring and a support ring for a retraction device.
  • the pressure pin extends through the feedthrough channel and can, for. B. be performed in a sliding motion with little movement.
  • the feedthrough channel does not serve to provide flow communication between both sides of the spline coupling, but serves to provide a mechanical passage extending through the passageway To allow connection, and without significantly affecting the stability of the teeth.
  • the pin can be slidably guided in the passage channel with little play, so that a fluid passage is not present. If the at least one passage channel is formed with a sufficiently larger cross-section than the pin, then the embodiment according to the invention can form a passage for both the mechanical connection and for the fluid.
  • the feedthrough channel is open towards the tooth head surface or tooth space base.
  • the advantage of this embodiment is that the at least one feedthrough channel can be produced as a simple and inexpensive groove, z. As by a machining with a collision tool, a broaching tool, a rolling hammer tool or a milling tool, especially when incorporating the profile in the cutter geometry.
  • the axial piston machine 1 shown by way of example has a closed housing 2 with a cup-shaped housing part 3, the housing interior 4 is detachably closed by a so-called connector part 5, which is screwed in the sense of a cover at the free edge of the housing part 3 by suggestively illustrated screws 6.
  • a drive shaft 7 is rotatably mounted, which passes through the bottom wall 3a of the cup-shaped housing 3 in a bearing hole 8 and by rolling bearings 9, 11 directly or indirectly rotatably mounted on the bottom wall 3a of the cup-shaped housing 3 and the connecting part 5.
  • the drive shaft 7 and the cylinder drum 17 rotate together about the axis of rotation 7a, the piston due to the inclined plane on the swash plate 26, here on the inclined surface 26a, in the piston bores 21 are moved back and forth.
  • the axial piston machine 1 can operate in pump operation or in engine operation.
  • the shoes 29 is associated with a retraction device 33 which holds the shoes 29 in abutment with the inclined surface 26a and is formed in the present embodiment by a retracting disc 33, with the edge edges 35 flanges 29a the sliding blocks 29 engages behind in a conventional manner.
  • the return pulley 33 is axially supported with a spherical-zone-shaped concave bearing surface 37 on a corresponding ball-zone-shaped convex bearing surface 38 on a support ring 39, which is mounted with a bearing hole 41 axially displaceable on the drive shaft 7 and is supported in the direction of the cylinder drum 17 with a force, which is greater than the lift-off forces.
  • the support ring 39 is preferably non-rotatably connected by a second multi-tooth clutch 19a with the drive shaft 7, wherein the teeth 43a provided in common for both multi-tooth clutches and can be correspondingly long.
  • the multi-tooth clutch 19 consists of a plurality of teeth 43a, 44a and tooth gaps 43b, 44b arranged on the lateral surface of the drive shaft 7 or on the inner lateral surface of the cylinder drum 13 and each in the circumferential direction whose main shape and size are each designed so that the teeth Fill out tooth spaces substantially.
  • the teeth are each loaded in the circumferential direction, wherein effective compressive forces are transmitted in the circumferential direction, which produce a certain surface pressure on the teeth 43a, 44a delimiting tooth flanks 43c, 44c.
  • the surfaces extending between the flanks 43c, 44c are designated with head surfaces 43d, 44d and tooth space base surfaces 43e, 44e.
  • the toothing preferably has a passage channel 45 centrally in at least one tooth head surface 43d, 44d and / or in at least one tooth space base 43e, 44e of the drive shaft 7 and / or the cylinder drum 17 on, thus connecting the two interior sections 4a, 4b with each other, so that a flow can take place.
  • the lubrication respectively associated surfaces are improved and prevents wear, abrasion and contact corrosion, or at least reduced.
  • the duct also serves to connect the other indoor section 4b to the leakage drain.
  • the cross-sectional shape of the at least one feedthrough channel 45 may be rounded (FIGS. 2 and 5) or circular arc sectionally curved (FIG. 7) or angular (FIGS. 3 and 6), e.g. B. be square or triangular.
  • the feedthrough channels 45 in the tooth head surfaces 43d, 44d and / or in the tooth space base surfaces 43e, 44e of the drive shaft 7 and / or the cylinder drum 17 can follow each other directly in the circumferential direction or omit one or more Zannkopf vom 43d, 44d and / or tooth space base surfaces 43e, 44e be arranged.
  • the above-mentioned and yet to be described embodiments may optionally be used in combination or in each case by itself.
  • the spring 42 is disposed on the control disk 13 facing side of the multi-tooth clutch 19 in an arranged between the cylinder drum 17 and the drive shaft 7 annulus and preferably formed by a spiral spring which presses with its the control disk 13 facing the end against an inner shoulder surface 47 on the cylinder drum 17 and biases it against the control disk 13.
  • the control disk 13 facing away from the end of the spring 42 spans with a plurality of oppositely arranged axial pressure pins 48 which extend through a respective feedthrough channel 45 to the support ring 39, the retraction device 33 before. Between the pressure pins 48 and the spring 42, a pressure ring 49 may be arranged.
  • the length of the pressure pins 48 is dimensioned larger than the axial length of the multi-tooth clutch 19, so that they protrude into the annular space 46.
  • the passageways 45 form axial guides for the pressure pins 48.
  • the feedthrough channels 45 are adapted to the cross-sectional shape and size of the pressure pins 48 with a slight play of play, the feedthrough channels 45 only fulfill a guiding function for the pressure pins 48 In such a case, it can be ensured by another flow passage that the fluid passes from one housing interior section 4a to the other 4b, here into the annular space 46 and to the rolling bearing 11, in order to lubricate this area and, if necessary, also to cool it and / or to rinse.
  • An adapted cross-sectional shape results z. B. then, if two z. B. semicircular feedthrough channels 45 are arranged opposite to each other, in which a common round or square pressure pin 48 engages with little play, as shown in FIG. 7 shows right.
  • the feedthrough channels 45 it is advantageous to design the feedthrough channels 45 so that they both form a guiding function for the pressure pins 48 and also form at least one passage for the fluid.
  • This can be achieved in that the number of feedthrough channels 45 is greater than the number of pressure pins 48 and thus at least one feedthrough channel 45 can serve as a free passage.
  • this can also be achieved in that the cross-sectional shape of the feedthrough channels 45 and 48 of the pressure pins is different.
  • an angular shape for the feedthrough channels 45 and a round shape for the pressure pins 48 offers.
  • opposing, z. B. in cross-section angular feedthrough channels 45 a common pressure pin 48 different z. B. round cross-sectional shape, record, as shown in Fig. 7 left.
  • the feedthrough channels 45 a leadership function on the Pressure pins 48 exert by the latter are guided in a line and free passage channel cross-sections 45a remain, through which a fluid flow can take place.
  • All embodiments of the invention have in common that a weakening of the tooth flanks 43c and 44c is avoided. Since no teeth 43a, 44a omitted, despite the feedthrough channels 45 an effective connection between the drive shaft 7 and cylinder drum 17 is provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (12)

  1. Moteur à pistons axiaux (1) comprenant un boîtier (2) avec un tambour cylindrique (17) et un plateau oblique (26) disposé axialement à côté du tambour, agencés à l'intérieur du compartiment intérieur (4) au boîtier,
    dans lequel, dans le tambour cylindrique (17), sont agencés plusieurs perçages à pistons (21) qui s'étendent approximativement parallèlement à l'axe médian de celui-ci, dans lesquels sont guidés des pistons (23) en translation, dont les extrémités de pistons tournées vers le plateau oblique (26) sont appuyées contre le plateau oblique (26),
    dans lequel, dans le boîtier (2), un arbre d'entraînement (7) est monté en rotation, relié solidairement en rotation à une partie du moteur par un accouplement à dents multiples (19) comprenant des dents (43a, 44a) et des intervalles interdentaires (43b, 44b) agencés en alternance et régulièrement en direction périphérique et en engrènement mutuel, et
    dans lequel, dans la région de l'accouplement à dents multiples (19) est agencé au moins un canal traversant (45) qui s'étend essentiellement parallèlement à l'axe de rotation de l'arbre d'entraînement (7) et d'un côté à l'autre de l'accouplement à dents multiples (19),
    caractérisé en ce que :
    le canal traversant (45) est agencé dans une surface (43b, 44e) au sommet d'une dent et/ou dans une surface qui lui est opposée (44e, 43b) au fond d'un intervalle interdentaire, et en ce que
    le canal traversant comprend une gorge et débouche vers la surface associée au sommet d'une dent (43b, 44e) et/ou au fond d'un intervalle interdentaire (44e, 43b).
  2. Moteur à pistons axiaux selon la revendication 1, caractérisé en ce que la forme de section transversale du canal traversant (45) est arrondie ou en forme de U.
  3. Moteur à pistons axiaux selon la revendication 1, caractérisé en ce que la forme de section transversale du canal traversant (45) est polygonale, par exemple de forme triangulaire ou carrée.
  4. Moteur à pistons axiaux selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal traversant (45) s'étend dans les deux surfaces mutuellement opposées au sommet d'une dent (43d) et au fond d'un intervalle interdentaire (44d).
  5. Moteur à pistons axiaux selon l'une quelconque des revendications précédentes, caractérisé en ce que plusieurs canaux traversant (45) sont agencés de façon répartie à la périphérie dans une surface (43d, 44d) au sommet d'une dent et/ou dans une surface (43e, 44e) au fond d'un intervalle interdentaire.
  6. Moteur à pistons axiaux selon la revendication 5, caractérisé en ce que dans plusieurs canaux traversants (45) agencés de façon répartie sur la périphérie sont agencées des tiges de pression (48) respectives à titre de partie d'un dispositif mécanique de traversée ou de liaison, dont la longueur est de préférence supérieure à l'accouplement à dents multiples (19).
  7. Moteur à pistons axiaux selon la revendication 6, caractérisé en ce que les tiges de pression (28) sont précontraintes par la force d'un ressort (42) contre un dispositif de rétraction (33) pour des patins coulissants (29).
  8. Moteur à pistons axiaux selon la revendication 6 ou 7, caractérisé en ce que la forme et la taille de section transversale des canaux traversants (45) sont adaptées à la forme et à la taille de section transversale des tiges de pression (48).
  9. Moteur à pistons axiaux selon l'une quelconque des revendications 6 à 8, caractérisé en ce que les canaux traversants (45) et les tiges de pression (48) agencées dans ceux-ci présentent des formes de section transversale différentes.
  10. Moteur à pistons axiaux selon l'une quelconque des revendications 6 à 9, caractérisé en ce que les tiges de pression (48) présentent une forme de section transversale arrondie.
  11. Moteur à pistons axiaux selon l'une quelconque des revendications 6 à 10, caractérisé en ce que, entre les extrémités des tiges de pression (48) tournées vers le dispositif de rétraction (33) et un ressort de compression (48) formé en particulier par un ressort à boudin, est agencée une bague de pression (49).
  12. Moteur à pistons axiaux selon la revendication 11, caractérisé en ce que la bague de pression (49) et les tiges de pression (48) sont réalisées d'une seule pièce.
EP01915304A 2000-06-08 2001-02-28 Moteur a piston axial Expired - Lifetime EP1287232B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10028336 2000-06-08
DE10028336A DE10028336C1 (de) 2000-06-08 2000-06-08 Axialkolbenmaschine
PCT/EP2001/002255 WO2001094751A1 (fr) 2000-06-08 2001-02-28 Moteur a piston axial

Publications (2)

Publication Number Publication Date
EP1287232A1 EP1287232A1 (fr) 2003-03-05
EP1287232B1 true EP1287232B1 (fr) 2006-12-27

Family

ID=26006018

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01915304A Expired - Lifetime EP1287232B1 (fr) 2000-06-08 2001-02-28 Moteur a piston axial

Country Status (4)

Country Link
US (1) US6796774B2 (fr)
EP (1) EP1287232B1 (fr)
DE (1) DE10028336C1 (fr)
WO (1) WO2001094751A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4111901B2 (ja) * 2003-09-26 2008-07-02 株式会社日本自動車部品総合研究所 流体機械
US9752570B2 (en) 2014-02-13 2017-09-05 S-RAM Dynamics Variable displacement compressor and expander
ES2777213T3 (es) * 2014-11-11 2020-08-04 Danfoss As Máquina de pistón axial

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2776628A (en) 1952-07-10 1957-01-08 Vickers Inc Power transmission
DE1405856A1 (de) * 1960-05-27 1969-01-02 Daimler Benz Ag Drehfeste Verbindung zwischen drehmomentuebertragenden Teilen von Kraftfahrzeuggetrieben,z.B. Verbindung von Zahnraedern mit ihren Wellen
US3139038A (en) * 1961-07-17 1964-06-30 Applied Power Ind Inc Engine
US3675539A (en) * 1970-08-07 1972-07-11 Parker Hannifin Corp Hydraulic motor
US3698287A (en) * 1970-12-09 1972-10-17 Cessna Aircraft Co Axial piston device
DE3222210A1 (de) * 1982-06-12 1983-12-15 Linde Ag, 6200 Wiesbaden Schraegscheiben-axialkolbenmaschine
DE4206087C2 (de) * 1992-02-27 1994-01-27 Linde Ag Hydromechanischer Radantrieb
US5784949A (en) * 1997-06-25 1998-07-28 Sauer Inc. Retaining system for slipper holddown pins

Also Published As

Publication number Publication date
EP1287232A1 (fr) 2003-03-05
US6796774B2 (en) 2004-09-28
WO2001094751A1 (fr) 2001-12-13
DE10028336C1 (de) 2002-04-04
US20030010195A1 (en) 2003-01-16

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