EP0767864B1 - Moteur a pistons axiaux pourvu d'un circuit de refroidissement pour les cylindres et les pistons - Google Patents

Moteur a pistons axiaux pourvu d'un circuit de refroidissement pour les cylindres et les pistons Download PDF

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Publication number
EP0767864B1
EP0767864B1 EP95921838A EP95921838A EP0767864B1 EP 0767864 B1 EP0767864 B1 EP 0767864B1 EP 95921838 A EP95921838 A EP 95921838A EP 95921838 A EP95921838 A EP 95921838A EP 0767864 B1 EP0767864 B1 EP 0767864B1
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EP
European Patent Office
Prior art keywords
axial piston
cooling
piston machine
cylinders
machine according
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
EP95921838A
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German (de)
English (en)
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EP0767864A1 (fr
Inventor
Heinz Berthold
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Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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Publication of EP0767864A1 publication Critical patent/EP0767864A1/fr
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    • 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
    • F01B3/0052—Cylinder barrel

Definitions

  • the invention relates to an axial piston machine according to the preamble of Claim 1.
  • Such axial piston machines are known from practice. Especially at Swashplate machines contain the piston that supports each piston on the swashplate Normal force a radial component that acts like one in the cylinder drum clamped beam acts on the piston and this within the cylinder canted. This leads in particular to the lack of piston lubrication, such as occurs during the start-up phase, for metallic contact between the piston and Cylinder wall with the result of corresponding heating by the occurring Frictional forces and risk of piston seizure.
  • GB-A-1 029 910 an axial piston machine according to the preamble of Claim 1 out.
  • the subject of this document is a lubrication device for hydraulic pumps and motors. Some are aligned in the radial direction Inlet and outlet channels provided to the lubricating oil for lubricating the pistons and to promote the storage of the cylinder drum. A connection between the am Outer circumference of the cylinder drum formed with the leak inside the Leakage fluid receiving space provided in the cylinder drum does not exist, so that none closed but an open lubrication circuit is present.
  • the solution according to the invention is based on the principle of cooling the piston critical points of metallic contact between the piston and cylinder and can thus not only in oil-operated axial piston machines, but also in those are used, which are intended for operation with a non-lubricating fluid are.
  • This cooling takes place by means of a cooling circuit which is connected to the leakage space connected, that is, completely separate from the working circuit of the axial piston machine is and in this way does not affect their efficiency.
  • the leakage fluid in the Leakage has its strongest cooling effect in the start-up phase, if so Risk of piston seizure is greatest because in this phase its temperature is roughly corresponds to the ambient room temperature.
  • This cooling device can be in the form of a another leakage fluid receiving space in a pressure and attached to the housing Suction channel of the connecting block containing the axial piston machine.
  • the cooling areas are preferably designed as annular spaces that the cylinders with surrounded by a small radial distance.
  • the cooling areas are advantageous to use as annular grooves in the cylinder walls form, so that the leak oil not only for cooling, but also for additional lubrication of the pistons.
  • the arrangement and number of Annular spaces or annular grooves can depend on the respective conditions of use Axial piston machine can be matched. So it can with axial piston machines low performance, each cylinder has a single cooling area, preferably in the end region of the cylinder drum facing the lifting disk, assign.
  • At least preferably an upper and a lower cooling area are provided, which are separated by a distribution channel or a distributor groove can be connected to each other.
  • the Leakage oil flow through an inlet channel and into one of the cooling areas maintain a discharge channel opening out of the respective other cooling area will.
  • suction channel of the axial piston machine Connect the cooling circuit via a dossel.
  • the one forced over the throttle Forced flow improves the cooling properties because relatively cool oil from the Inflow channel flows.
  • the axial piston machine shown in Figures 1 to 4 is in Swashplate design with adjustable displacement and one Current direction executed and includes in a known manner as essential components hollow cylindrical housing 1 with an open end (upper end in Figure 1) attached to the housing 1, the open end closing Terminal block 2, a lifting or swash plate 3, a control body 4, a Drive shaft 5, a cylinder drum 6 and a cooling circuit 7.1 according to the invention until 7.4.
  • the swash plate 3 is a so-called swivel cradle with a semi-cylindrical one Cross-section (see Figure 5) formed and supported with two, with mutual Distance parallel to the swivel direction bearing surfaces under hydrostatic Relief on two appropriately shaped bearing shells 8, which on the inner surface the housing end wall 9 opposite the connection block 2 are fastened.
  • the hydrostatic discharge takes place in a known manner via pressure pockets 10, which in the Bearing shells 8 are formed and supplied with pressure medium via connections 11 will.
  • actuator 13 engages in the direction of Terminal block 2 extending arm 14 of the swash plate 3 and is used for Swiveling the same about a swivel axis perpendicular to the swivel direction.
  • the control body 4 is on the inner surface of the housing interior facing the Terminal blocks 2 attached and with two through openings 15 in the form of kidney-shaped control slots which are connected via a pressure channel 16D or Suction channel 16S in the connection block 2 to a pressure and suction line, not shown are connected.
  • the pressure channel 16D has a smaller flow cross section than the suction channel 16S.
  • the spherical facing the interior of the housing Trained control surface of the control body 4 serves as a bearing surface for the Cylinder drum 6.
  • the drive shaft 5 protrudes through a through hole in the housing end wall 9 in the housing 1 and is in this through hole by means of a bearing 17 and by means of a further bearing 18 in a narrower bore section blind bore 19 at the end in the connection block 2 and one closer to it Bore section adjacent region of a central through hole 20 in Control body 4 rotatably mounted.
  • the drive shaft 5 penetrates inside the Housing also a central through hole 21 in the swash plate 3, whose diameter corresponds to the largest swash deflection of the swash plate 3 is dimensioned, as well as a central through bore in the cylinder drum 6 two hole sections.
  • One of these bore sections is formed on a cylinder drum 6, projecting beyond the end face 22 facing the swash plate 3 sleeve-shaped extension 23, via which the cylinder drum 6 by means of a keyway connection 24 is rotatably connected to the drive shaft 5.
  • the remaining bore section is conical; it tapers based on its cross section of largest diameter close to the first Bore section up to its cross section of smallest diameter close to the Control body 4 adjacent end face or bearing surface of the cylinder drum 6.
  • the of the Drive shaft 5 and this conical bore section is defined annular space designated by the reference numeral 25.
  • the cylinder drum 6 has generally axially extending, stepped Cylinder bores 26 which are even on a coaxial to the drive shaft axis Pitch circle are arranged on the cylinder drum end face 22 directly and on the Control body 4 facing cylinder drum bearing surface via outlet channels 27 open out in the same pitch circle as the control slots.
  • a bushing 28 is used in the on the Cylinder drum end face 22 directly opening cylinder bore sections a larger diameter.
  • the cylinder bores 26 including the bushings 28 are referred to here as cylinders.
  • Within this Cylinders 26, 28 are displaceably arranged pistons 29 on their swash plate 3 facing ends with ball heads 30 which are mounted in sliding shoes 31 and via this to an annular slide disk 32 fastened to the swash plate 5 are stored hydrostatically.
  • Each slide shoe 31 is on its slide plate 32 facing sliding surface with a pressure pocket, not shown, which over a through hole 33 in the shoe 31 to a stepped axial Through channel 34 connected in the piston 29 and in this way with the Piston 29 in the cylinder bore 26 delimited working space of the cylinder connected is.
  • a stepped axial Through channel 34 connected in the piston 29 and in this way with the Piston 29 in the cylinder bore 26 delimited working space of the cylinder connected is.
  • In each axial through channel 34 is in the area of the associated Ball head 30 formed a throttle.
  • the one in the interior of the housing of the components 3 to 6 etc. contained therein The space taken up serves as a leakage space 37 which is used in the operation of the Axial piston machine through all gaps, such as between the Cylinders 26, 28 and the piston 29, the control body 4 and the cylinder drum 6, the swash plate 3 and the sliding plate 32 and the bearing shells 8, etc., emerging Leakage fluid picks up.
  • the axial piston machine is designed for operation with oil as a fluid.
  • the cylinder drum 6 together with the piston 29 is rotated. If the swash plate 3 in a by actuating the actuator 13 Inclination (see FIG. 5) is pivoted relative to the cylinder drum 6, so all pistons perform 29 strokes; when rotating the Cylinder drum 6 through 360 °, each piston 29 passes through a suction and one Compression stroke, whereby corresponding oil flows are generated, their inflow and Dissipation via the mouth channels 27, the control slots 15 and the pressure and Suction channel 16D, 16S.
  • the swash plate 3 exerts a normal force F n on each slide shoe 31, which is perpendicular to the swash plate 3 with negligible friction.
  • This normal force is broken down into a piston force F k and a radial or transverse force F q in the spherical piston 30.
  • the transverse force F q acts in the ball head 30 on the piston 29 as on a beam clamped in the cylinder drum 6, which causes the axial reaction forces F r shown in FIG.
  • the piston 29 comes into metallic contact with the liner 28, and very high surface pressures can occur, which are the cause of correspondingly high frictional forces and thus heating at the contact points.
  • the cooling circuit 7.1 to 7.4 is connected to the leakage space 37 and includes the conical annulus 25 (so-called leakage fluid receiving space), the Through hole 20 in the control body 4, the blind hole 19 (so-called further Leakage fluid receiving space), a connecting this with the leakage space 37 Connection line 38, which is in a circumferential groove 39 in the inner surface of the Terminal block 2 opens out, as well as the cylinders 26, 28 all around Cooling areas connected to the conical annular space 25 via inlet channels 40 are and via drainage channels 41 on the cylindrical boundary surface 42 of the Open cylinder drum 6 into leakage space 37. All inlet channels 40 open in the conical annular space 25 at its cross-section of the largest diameter and Like all drainage channels 41, they run essentially radially through the Cylinder drum 6.
  • each cylinder 26, 28 is in the form of a cooling area an annular space 43 assigned as a circumferential groove in the wall of the Cylinder bore section of larger diameter and formed by the Liner 28 is covered.
  • the annular space 43 extends from near Mouth area of the cylinder bore 26 over about two thirds of the length the same in the direction of the mouth channels 27 and thus represents one of the upper Dead center position of the piston 29 associated upper cooling area.
  • One each Inlet channel 40 and an outlet channel 41 open approximately centrally in the annular space 43 and run coaxially with each other.
  • the heating leakage oil in the leakage space 37 is cooled as it flows through the blind bore 19 in the connection block 2, since this is exposed to the room temperature and is therefore cooler than the leakage oil in the leakage space 37.
  • the leakage oil in the cooling circuit 7.1 can be kept at correspondingly low temperatures by appropriately designing the connection block 2 and the blind bore 19 and, if appropriate, additionally cooling them by means of a separate coolant.
  • the cooling circuit 7.1 serves only as a cooling circuit due to the lack of connection to the cylinders 26, 28 (due to the closed annular spaces 43).
  • the cooling circuit 7.1 can additionally assume a lubricating function if, for example, the annular spaces 43 are connected to the cylinders 26, 28 via corresponding bores through the bushings 28.
  • the axial piston machine equipped with the cooling circuit 7.1 is designed for medium outputs due to the arrangement of the annular spaces 43 in the mouth area of the cylinders 26, 28.
  • the cooling circuit 7.2 according to FIG. 2 differs in otherwise the same Construction and cooling function of that of Figure 1 in that its Cooling areas have the shape of annular grooves 44 which are in the bushings 28 formed and open to the interior of the cylinders 26, 28.
  • the one with the Cooling circuit 7.2 equipped axial piston machine is due to the compared to the annular spaces 43 smaller axial width of the annular grooves 44 for smaller Services designed and performed as the axial piston machine according to Figure 1 at the same time additional lubrication of the pistons 29.
  • the cooling circuit 7.3 according to FIG. 3 differs in otherwise the same Construction and function of that of Figure 2 in that each Annular groove 44 is connected to a distributor groove 45 which is in the bushing 28 spirally surrounding, is formed and on the end face 22 of the cylinder drum 6 flows out.
  • the area of action of the ring grooves 44 with regard to cooling and Lubrication is made from them via the distributor grooves 45 into the leakage space 37 flowing leakage oil up to the mouth of the cylinders 26, 28 expanded.
  • the cooling circuit 7.4 according to FIG. 4 comprises the one in FIG. 1 for each cylinder 26, 28 shown upper annular space 43, but with a smaller axial width, and one another, lower annular space 46 of the same dimensions, which in the lower end region of the Liner 28, that is in the region of the cylinder 26, 28 above the Piston base 47 is formed at the bottom dead center position of the piston 29.
  • To the upper annular space 43 is an inlet channel 40 and to the lower annular space 46 Drain channel 41 connected.
  • a Distribution channel 48 is provided, which connects the two annular spaces 43, 46 together.
  • the cooling circuit 7.4 according to FIG. 4 like that according to FIG. 1, is not shown in FIG Connection with the cylinders 26, 28 and thus has only the function of a Cooling.
  • the cooling circuit 7.4 is very high performance for axial piston machines intended.
  • This cooling circuit can be used for high performance axial piston machines Find use when the annular spaces 43, 46 and possibly the Distribution channel 48 through corresponding holes through the bushings 28 with the Cylinders 26, 28 are connected. The same effect is achieved if the Annuli 43, 46, the distribution channel 48 and the holes mentioned Ring grooves and distributor grooves according to Figure 3 are replaced.
  • FIG. 6 shows the cooling circuit 7.1 already shown in FIG. 1.
  • the embodiment shown in Figure 6 differs from that Figure 1 in that between the suction channel 16S and the blind bore 19 a Through bore 51 is provided, the suction channel 16S of the axial piston machine connects to the cooling circuit 7.1.
  • the bore 51 is an anti-pulsation throttle 50 arranged in the bore 51. This flows under pre-compression via the anti-pulsation throttle 50 standing fluid of the suction channel 16S in the cooling circuit 7.1, causing leakage be balanced. The fluid flowing in via the throttle 50 causes a certain forced flow in the cooling circuit 7.1 reached, whereby the cooling properties of the cooling circuit can be improved.
  • the inflow from the suction channel 16S can at various points in the Axial piston machine can be arranged and in different areas of the cooling circuit flow into.
  • the arrangement of the throttle 50 in the is particularly advantageous Terminal block 2, where it between the blind bore 19 and the suction channel 16S in can be easily integrated.
  • the invention can also be implemented in inclined axis machines, since here too radial forces that jam the pistons in the cylinders can occur due to an inclined position of the pistons or piston rods as a result of Deviations between the part circle of the spherical seats in the Drive pulley and the pitch circle of the cylinder.

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

Abstract

L'invention concerne un moteur à piston axiaux comportant un carter (1) dont l'espace intérieur comprend une chambre de trop-plein (37) et un disque d'excentrique (3), ainsi qu'un tambour (6) monté rotatif qui comporte des cylindres (26, 28) et des pistons (29) animés d'un mouvement alternatif dans ces derniers. Les extrémités des pistons (29) qui font saillie des cylindres (26, 28) s'appuient sur le disque d'excentrique (3). Afin d'éviter le grippage des pistons tout en maintenant le rendement du moteur à pistons axiaux, il est prévu un circuit de refroidissement (7,1 à 7,4) qui comprend: une chambre collectrice du fluide de trop-plein (25) raccordée à la chambre de trop-plein (37) et formée dans la partie du tambour (6) entourée par les cylindres (26, 28); des canaux d'alimentation et d'évacuation (40, 41) dont au moins un constituant radial traverse le tambour (6); et des zones de refroidissement (43, 44, 46) qui s'étendent autour des cylindres (26, 28) et sont raccordées à la chambre collectrice du fluide de trop-plein (25) par l'intermédiaire des canaux d'alimentation (40) et débouchent dans la chambre de trop-plein (37), au niveau d'une surface extérieure de délimitation (42) du tambour (6), par l'intermédiaire des canaux d'évacuation (41).

Claims (15)

  1. Machine à pistons axiaux comportant un carter (1) dont le volume intérieur comprend une chambre de fuite (37), ainsi qu'un plateau oblique (3) et un tambour cylindrique (6) monté tournant avec des cylindres (26, 28) et qui loge des pistons se déplaçant dans ceux-ci dans un mouvement de va-et-vient, dont les extrémités, ressortant des cylindres (26, 28), s'appuient contre le plateau oblique (3), dans laquelle une chambre de réception de fluide de fuite (25) est formée dans la partie du tambour cylindrique (6), entourée par les cylindres (26, 28) et dans le tambour cylindrique (6) sont formés des canaux d'arrivée et de départ (40, 41), qui s'étendent avec au moins une composante radiale à travers le tambour cylindrique (6), caractérisée par une conduite de branchement (38) reliant la chambre de réception de fluide de fuite (25) à la chambre de fuite (37) pour former un circuit de refroidissement (7.1 à 7.4), des zones de refroidissement (43, 44, 46) associées de manière rotative aux cylindres (26, 28) pour leur refroidissement, qui sont raccordées à la chambre de réception de fluide de fuite (25), par les canaux d'arrivée (40) faisant partie du circuit de refroidissement (7.1 à 7.4), et débouchent, par les canaux de départ (41) faisant partie du circuit de refroidissement (7.1 à 7.4), dans la chambre de fuite (37), sur une surface de délimitation (41) extérieure, et un dispositif de refroidissement (19) pour le refroidissement du fluide de fuite dans le circuit de refroidissement (7.1 à 7.4).
  2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que la chambre de réception de fluide de fuite (25) s'élargit à la manière d'un diffuseur, dans le sens d'écoulement, jusqu'à la zone où les canaux d'arrivée (40) débouchent dans les zones de refroidissement (43, 44, 46).
  3. Machine à pistons axiaux selon la revendication 2, caractérisée en ce que le dispositif de refroidissement (19) se présente sous la forme d'une autre chambre de réception de fluide de fuite dans un bloc de branchement (2), rapporté sur le carter (1), contenant le canal de refoulement et le canal d'aspiration (16D, 16S) de la machine à pistons axiaux
  4. Machine à pistons axiaux selon la revendication 2 ou 3, caractérisée en ce que les deux chambres de réception de fluide de fuite (19, 25) sont coaxiales l'une par rapport à l'autre et communiquent entre elles, et en ce que le tambour cylindrique (6) est monté solidairement en rotation sur un arbre moteur (5), qui traverse au moins la chambre de réception de fluide de fuite (25) dans le tambour cylindrique (6).
  5. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que les zones de refroidissement sont des chambres annulaires (43, 46), qui entourent les cylindres (26, 28) à faible distance radiale.
  6. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que les zones de refroidissement sont des rainures annulaires (44) dans les parois des cylindres (26, 28).
  7. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce qu'à chaque zone de refroidissement (44) est raccordée une rainure de distribution (45) ou un canal de distribution, qui entoure le cylindre (26, 28) correspondant, sensiblement en spirale et qui débouche sur le côté frontal (22) du tambour cylindrique (6), tourné vers le plateau oblique (3).
  8. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce qu'à chaque cylindre est associée au moins une zone de refroidissement supérieure (43) dans la zone d'extrémité, tournée vers le plateau oblique (3), du tambour cylindrique (6) et/ou une zone de refroidissement inférieure (46), dans sa zone au-dessus du fond de piston (47), lorsque le piston (46) est dans sa position de point mort bas.
  9. Machine à pistons axiaux selon la revendication 9, caractérisée en ce qu'un autre canal de distribution (48) ou une autre rainure de distribution relie entre elles la zone de refroidissement inférieure et la zone de refroidissement supérieure (43, 46).
  10. Machine à pistons axiaux selon la revendication 10, caractérisée en ce qu'au moins un canal d'arrivée (41) est associé à l'une des deux zones de refroidissement (43) et au moins un canal de départ (41), à l'autre zone de refroidissement (46).
  11. Machine à pistons axiaux selon l'une au moins des revendications 1 à 10, caractérisée en ce qu'au moins un canal d'arrivée (40) et un canal de départ (41) sont associés à chaque zone de refroidissement (43, 44).
  12. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en que les canaux d'arrivée (40) et les canaux de départ (41) s'étendent sensiblement radialement.
  13. Machine à pistons axiaux selon l'une au moins des revendications précédentes, caractérisée en ce que le circuit de refroidisseanent (7.1 à 7.4) est relié au canal d'aspiration (16S) de la machine à pistons axiaux, par un organe d'étranglement (50).
  14. Machine à pistons axiaux selon la revendicaion 13, caractérisée en que l'organe d'étranglement (50) débouche dans le circuit de refroidissement (7.1 à 7.4), dans une zone entre la chambre de fuite (37) et la chambre de réception de fluide de fuite (25).
  15. Machine à pistons axiaux selon la revendication 13 ou 14, caractérisée en que l'organe d'étranglement (50) est formé dans un bloc de branchement (2) rapporté sur le carter (1), contenant le canal de refoulement et le canal d'aspiration (16D, 16S) de la machine à pistons axiaux.
EP95921838A 1994-06-30 1995-06-07 Moteur a pistons axiaux pourvu d'un circuit de refroidissement pour les cylindres et les pistons Expired - Lifetime EP0767864B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4423023 1994-06-30
DE4423023A DE4423023C2 (de) 1994-06-30 1994-06-30 Axialkolbenmaschine mit einem Kühlkreislauf für die Zylinder und Kolben
PCT/EP1995/002180 WO1996000838A1 (fr) 1994-06-30 1995-06-07 Moteur a pistons axiaux pourvu d'un circuit de refroidissement pour les cylindres et les pistons

Publications (2)

Publication Number Publication Date
EP0767864A1 EP0767864A1 (fr) 1997-04-16
EP0767864B1 true EP0767864B1 (fr) 1998-08-12

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EP95921838A Expired - Lifetime EP0767864B1 (fr) 1994-06-30 1995-06-07 Moteur a pistons axiaux pourvu d'un circuit de refroidissement pour les cylindres et les pistons

Country Status (5)

Country Link
US (1) US5971717A (fr)
EP (1) EP0767864B1 (fr)
JP (1) JP3570517B2 (fr)
DE (2) DE4423023C2 (fr)
WO (1) WO1996000838A1 (fr)

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CN105201816B (zh) * 2015-09-07 2017-03-22 福州大学 一种斜盘式柱塞泵的缸体自冷却结构
CN105332875B (zh) * 2015-11-17 2017-12-19 四川嘉泉科技有限公司 一种多功能水油两用电动泵
DE102016114148A1 (de) * 2016-08-01 2018-02-01 L'orange Gmbh Hochdruckpumpe, insbesondere zur Kraftstoffeinspritzung
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WO2011054409A2 (fr) 2009-11-03 2011-05-12 Robert Bosch Gmbh Moteur à pistons axiaux à plateau incliné

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DE4423023C2 (de) 1998-07-09
JP3570517B2 (ja) 2004-09-29
WO1996000838A1 (fr) 1996-01-11
DE4423023A1 (de) 1996-01-04
DE59503183D1 (de) 1998-09-17
US5971717A (en) 1999-10-26
JPH10502148A (ja) 1998-02-24
EP0767864A1 (fr) 1997-04-16

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