EP0064563B1 - Disposition de patin glissant pour machine à pistons radiaux - Google Patents

Disposition de patin glissant pour machine à pistons radiaux Download PDF

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Publication number
EP0064563B1
EP0064563B1 EP19810103470 EP81103470A EP0064563B1 EP 0064563 B1 EP0064563 B1 EP 0064563B1 EP 19810103470 EP19810103470 EP 19810103470 EP 81103470 A EP81103470 A EP 81103470A EP 0064563 B1 EP0064563 B1 EP 0064563B1
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EP
European Patent Office
Prior art keywords
piston
shoe
pressure fluid
pivot
rotor
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
Application number
EP19810103470
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German (de)
English (en)
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EP0064563A1 (fr
Inventor
Karl Eickmann
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.)
Breinlich Richard Dr
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Breinlich Richard Dr
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Filing date
Publication date
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Priority to EP19810103470 priority Critical patent/EP0064563B1/fr
Publication of EP0064563A1 publication Critical patent/EP0064563A1/fr
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Publication of EP0064563B1 publication Critical patent/EP0064563B1/fr
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0428—Supporting and guiding means for the pistons

Definitions

  • the invention relates to a piston or a piston shoe assembly in a radial piston machine with one-piece H-shaped piston shoes, with radial webs with extended partial cylinder surfaces for guiding the pistons on the rotor, with pivotable mounting of the piston shoe swivel part on a bearing bed in the piston and with the central web above the swivel part Slits between the side guide parts of the piston.
  • H-shaped piston shoes also known as plunging or deep-diving piston shoes
  • DE-PS 14-03 748, 13 03 469, 25 00 779 and 25 01 158 are known from DE-PS 14-03 748, 13 03 469, 25 00 779 and 25 01 158. From these publications one also knows the rotor with its radial webs, on the partial cylinder surfaces of which the pistons are guided, and the radially inward sliding of the piston shoe side parts past the outer diameter of the rotor webs radially inwards. This results in the long piston stroke of these units for a given size.
  • the piston shoe is mounted in the piston with a swivel joint.
  • the radially outer edges of the piston with respect to the rotor axis are arranged radially within the lateral guide part of the H-shaped piston shoe.
  • the piston shoe swivel roller is thus encompassed by the piston by more than 180 degrees, for example about 240 degrees. The manufacture of the piston and the piston shoe are therefore time-consuming and expensive.
  • S / da the efficiency and the stroke ratio of a pump are not as important as in the engine. This is because the pump can also work with lower efficiency, while good efficiency and high torque for a given friction ratio are essential for the motor.
  • a stroke ratio of at least 0.12 or even 0.20 is desired.
  • the relative swiveling (swivel angle) of the piston shoe on or in the piston increases in accordance with the stroke ratio.
  • the swiveling angle of the piston shoe which increases with the increasing stroke ratio, increases the crimping component in the direction of rotation. This force component in the direction of rotation is particularly desirable in motors for generating the torque.
  • the outer surface of the piston is also extended accordingly, so that a long contact surface of the piston is formed on its guide surface in the cylinder and on the rotor web. This larger contact surface allows a greater load capacity for the force component in the direction of rotation and thus a greater torque.
  • the piston arms can slide into an annular groove or recess protrude guide and accordingly at least partially appear outside the piston guide surfaces.
  • At least one pressure fluid pocket which is periodically acted upon by the pivoting part and its recesses with its control edges with pressure fluid with respect to the rotor axis, approximately at a radial height of the pivot center between the piston and piston shoe, through the outer surface of the piston and into the piston in the direction the torque force component is arranged. Due to the long piston arms, the arrangement of this pressure fluid pocket on the outer surface of the piston at the level of the pivot axis between the piston and piston shoe is easily possible. A pressure field can be generated with the pressure fluid pocket, which acts on the piston against the transverse forces so that the transverse forces do not lead to mechanical friction between the piston and the cylinder surface or piston guide surface. Since the piston can be supported radially far outwards in relation to the rotor axis by means of the pressure fluid pocket, the torque can possibly act on a long lever arm relative to the rotor axis.
  • the radial piston motor according to the invention is in principle superior in efficiency and performance to a corresponding axial piston motor with the same stroke ratio, the low power to weight ratio of the motor according to the invention being particularly remarkable.
  • about 100 HP with a weight of less than 12 kg are possible with a motor according to the invention.
  • the manufacture of the piston, the piston shoe and the swivel joint between the piston and the piston shoe can advantageously be simplified.
  • the bearing surface of the swivel bed receiving the swivel part of the piston shoe in the piston is guided at most by a 180 ° arc around the swivel center.
  • this arrangement offers the possibility of inserting the piston shoe with its swivel part in the direction of the piston axis into the bearing bed on the piston during assembly, both the swivel part and the lateral guide parts of the H-shaped piston shoe automatically taking their correct position.
  • the extended piston arms counteract a rotation of the piston relative to the associated piston shoe, so that the piston is locked against rotation. This ensures that the pressure fluid pockets which may be provided on the outer surface of the pistons always remain in the correct position and the pressure fields generated by means of the pressure fluid pockets absorb the transverse loading of the piston or the torque.
  • piston shoes are used in the prior art that do not have an "H-shape" and which are therefore called “outer piston shoes” in the inventor's writings. Such can be found, for example, in DE-PS 23 07 997, in US Pat. Nos. 3,828,653; 4,095,510; 3,885,457; 3,893,376; 3,874,272; 3,875,852; 3,874,273; 3,985,065 and others. With these piston shoes, the guide surfaces of the piston shoes are always outside the circumference of the rotor.
  • Such piston shoes appear in particular about ten years after Invention of the H-shaped piston shoes on and with them, in contrast to the H-shaped, deep-diving piston shoes used by the invention, whose outer guide surface can lie radially below the rotor circumference during the inward stroke, a large piston stroke cannot be achieved.
  • Corresponding motors have a low efficiency.
  • a rotation lock between the piston and the piston shoe cannot be achieved in a simple manner, since, in contrast to H-shaped piston shoes, there are no slots in this piston shoe into which piston arms or the like could be inserted.
  • Hele-Shaw pump which is used today in ship rudder systems, the invention of which dates back to the beginning of our century and which has sliding shoes that can be swiveled around the cross pin axis at the ends of a cross pin by the piston on the cross pin.
  • radial piston machines therefore serve differently directed swivels and have nothing in common with the radial piston machines of the invention, so that they cannot be used in the present invention.
  • they lack the bearing beds in the pistons with parts of the piston shoes that are pivotable about the pivot axis parallel to the rotor axis.
  • the piston shoe 10 has a roller-shaped piston shoe central web 12 with a pivot axis 22 and pivot surface 23 with a constant radius 100 and the outer sliding surface 16.
  • the inner surfaces 17 may occasionally be omitted from motors or pumps without self-priming.
  • FIG. 2 shows the top view of the piston shoe 10 from above, so that the "H-shape" of the piston shoe 10 is visible. Between the lateral guide parts 14, one can see the slots 93, 94 which extend as far as the central piston shoe web 12.
  • this one-piece "H-shaped" piston shoe dipping "or” deep diving “piston shoe is called because its outer surface is immersed in the rotor 24 up to the outer diameter 29 of the rotor webs, see FIGS. 8, 9 (immersed shoe) or deeply immerses the outer surface 16 past the outer diameter 29 of the rotor webs radially inward into the turned-off rotor parts (deep-seated piston shoe).
  • An advantage of the piston shoe 10 of FIG. 1 is that the pivot axis 22 is located high up, as a result of which the torque application force in the motor is relatively far radially outward and the motor achieves a correspondingly high torque with force application on a long lever arm.
  • Another advantage of this embodiment of the invention is that the piston shoe is easy to manufacture and cheap. Because the slots 93, 94 and the bearing surface 23 can be easily produced with the lathe when clamping at the ends of the pivot axis 22.
  • the piston shoe central web 21 has a swivel part 20, the swivel axis 22 of which can be somewhat lower here, and the recesses 19, which serve to ensure that the securing pins 96 of the piston 3, see FIG. 4, into the recesses 19 intervene and the animal pins 96 can secure the piston shoe of FIG. 3 against falling out of the piston of FIG. 4.
  • the Ausnhemisme 19 are dimensioned so that the pivoting movement can take place undisturbed despite the locking pins 96.
  • the upper part of the piston 3, the axis of which is numbered 101, has the bearing or pivoting bed 4 with the bearing surface 6 for receiving the pivoting part 20 of the piston shoe 10 or the pivoting surface 23.
  • the Bearing surface 6 formed only as a 180 ° bend with respect to the pivot axis 22, with the advantage that the bearing surface 6 can be produced with simple radius cutters or grinding wheels.
  • the piston arms 1 and 2 extend radially outward from the bearing surface 6 of the piston 3 and can be extended radially outward so far that after the piston shoe 10 has been inserted into the swivel bed 4, it extends radially over the outer sliding surface 16 stick out of the piston shoe.
  • the piston arms 1, 2 must be sufficiently narrow to be able to engage in the slots 93, 94 of the piston shoes 10 or to reach through them. If the cable guide surface 17 of the piston shoe 10 has a recess (not shown), the width of the arms 1, 2 can also be wider than the slots 93, 94.
  • the piston arms 1, 2 are an essential part of the invention. Because they form a long piston guide surface, which extends radially outward beyond the pivot axis 22. In addition, the design of the swivel bed 4 and the arms 1, 2 according to FIGS. 4 and 5 makes it possible to insert the piston shoe central web 12, 21 into the piston 3 radially from the outside.
  • the locking pins 96 can be arranged in the upper piston part in order to engage in the recesses 19 of the piston shoe 10 or to otherwise secure the piston shoe against falling out of the swivel bed 4.
  • pin (s) 7 can be arranged high in the upper piston part above the sliding surface 16 of the piston shoe 10 when the piston shoe 10 is inserted into the bearing bed 4 in the piston.
  • reference number 5 shows the slot which extends radially outward from the bearing bed 4 and which, together with the bearing bed 4, has the advantage that these parts can be machined together with the pivot bearing surface 6.
  • each swivel bearing surface 6 of each individual piston had to be clamped, ground and measured individually.
  • the locking pin 96 can also be dispensed with if the piston arms 1, 2, as shown in Figure 7 on the left, are provided with extensions 8 which, as Figure 7 shows on the right and below, after the insertion of the Piston shoe 10 bends into the bed 4, as shown in the right and lower part of Figure 7.
  • the extensions 8 then fulfill the function of the holding pin 96 of FIGS. 4, 5.
  • the pins 96 are prevented from being able to come loose.
  • FIGS. 8 and 9 a part of the rotor 24 can be seen in radial section with two cylinders 25, 26.
  • the rotor axis is labeled “C”.
  • the pistons 53, 63 run radially outwards and inwards in the cylinders 25, 26, executing the piston stroke S.
  • the outer sliding surfaces 16 of the piston shoes 10 slide on the inner guide surface 27 of the piston lifting ring 35.
  • the piston lifting ring 35 has an annular groove in deep-diving piston shoes 34, which, breaking through and dividing the guide surface 27, extends radially from the inside into the piston lifting ring 35.
  • the outer diameter of the rotor 24 is designated 29.
  • FIG. 8 shows the rotor rotation angle a between the zero plane and the radial axis of the relevant cylinder and piston.
  • the data of the diagram in FIG. 20 are based on this angle a.
  • FIGS. 8 and 9 The slots 5 and the piston arms 1 and 2 can also be seen in FIGS. 8 and 9. It can also be seen how the piston shoes 10 pivot with their piston shoe central web 12, 21 in the slots 5 of the piston. The angle y shows the pivoting of the piston shoes 10 in question from the normal position, this angle also appears in the diagram in FIG. 20. In FIGS. 8 and 9 it can also be seen that the piston arms 1 and 2 according to the invention engage in the annular groove 34 of the piston lifting ring 35.
  • the piston lifting ring 35 can also be designed as part of the housing or as a housing part with the guide surface 27, so that a separate piston lifting ring can be saved.
  • FIGS. 8 and 9 show the long guidance of the pistons 53, 63 between the rotor radial webs and in the rotor 24.
  • FIG. 8 the piston shoes of FIG. 1 are installed and in FIG. 9 the piston shoes of FIG. 3 with their associated pistons.
  • the piston shoe 10 in FIG. 10 essentially corresponds to that of FIG. 3, but without the recesses 19.
  • the holder for the piston shoe central web 21 in the coals 73 is here effected by a self-tensioning plate part, the clamping plate 9, which in corresponding slots 77 in the piston arms 1 , 2 is arranged self-retaining.
  • This clamping plate 9 is shown again separately in FIGS. 13 and 17. It has the clamping arch 78 between the holding ends 79.
  • Figure 13 shows that the holding ends 79 project laterally from a recess, the holding ends 79 engaging around the parts 102, 102 'of the piston in FIG. 11, so that the clamping plate 9 is relative to the piston arms 1, 2 cannot twist.
  • the end pieces between the holding ends 79 engage in the slots 77 of the arms 1, the piston 3 of FIG. 11, as is also shown on the left in FIG. 10.
  • the clamping arch 78 can be provided in order to press the piston shoe 10 firmly onto the swivel bearing surface 6 by means of the clamping plate 9 and to smoothly follow the outer surface of the piston shoe during the swiveling movement.
  • FIG. 10 shows the piston 73 in the cylinder 26 of the rotor 24.
  • the left part of the figure is a section through the right part of the figure along the section line, which makes it clear how the piston arms 1, 2 and the others Place parts between the rotor radial webs 124.
  • FIG. 11 shows the piston of FIG. 10 in separate drawings, but on a scale like that of FIGS. 14 to 18, so that the pistons can be compared with one another.
  • the description of FIG. 10 should therefore also apply to FIG. 11 and be read together with it.
  • the important parts of the piston stroke guide, such as 27, 34, 35, can also be seen in FIG. 10 and also the slot 5 between the piston arms 1 and 2.
  • the pistons of the now described FIGS. 10 and 11 have the pressure fluid pockets 54, 55 and / or 71, 72, approximately at the radial height of the pivot axis 22, which are incorporated from the outside into the piston outer surface and outer parts.
  • the channels 51 and 56, 66 are known in principle from the aforementioned patent specification 14 53 433, from which the control edges which limit the control pockets 60, 59 in the pivoting part of the piston shoe are also known.
  • the control pockets 59, 60 act and control the loading of the channels 56, 66 and thus the pressure fluid pockets 54 and 55. This loading takes place periodically alternately with each revolution of the rotor.
  • the special feature of this invention is that the pressure fluid pockets 54, 55, due to the arrangement of the piston arms 1, 2 according to the invention, are now arranged according to the invention at the radial height of the pivot axis 22, while in the previous technology they were too deep radially inside and were not effective there could become. They were outside the current force application component and caused the pistons to tilt instead of relieving them of pressure fluid.
  • the cross section of the connecting pocket 74 or 75 also acts on the piston wall and the cylinder wall as a force component in the torque direction or vice versa.
  • the pressure fluid connection pockets 74 or 75 connect to the further pressure fluid pockets 72 or 71 in FIG Outer surface of the piston in question, for example 73. This position is drawn on the right in FIG. 10. This is the third stage of the connection of the pressure fluid pockets in the torque direction or in the opposite direction.
  • the pressure fluid pockets switch off one after the other in reverse order.
  • the edge of the control pocket 60 controls the pressure fluid pockets on the opposite half of the piston and the control pocket 59 switches the side of the piston described above from the application of pressure fluid to the pressure fluid pockets concerned.
  • the pockets are then connected to the low-pressure area of the unit in stages and switched off.
  • FIG. 10 shows a longitudinal section through the piston shoe, as it results from the section through the central axis of the piston or shoe of the lower figure of FIG. 10. It is noteworthy in the upper figure that this shows the piston shoe in the 1: 1 ratio of a test device.
  • the control pockets 59, 60 can be seen with dashed lines, since they lie in front of and behind the cut surface.
  • the recesses 57 connect the control pockets 59 and 60, which are also pressure fluid relief pockets.
  • the channels 58 direct the pressurized fluid into the pressurized fluid pockets 61, 62 in the outer surface of the piston shoes, i.e. in the sliding surfaces 16 which slide on the sliding surface (the sliding surfaces) 27 of the piston lifting ring 35.
  • pressure fluid pockets 61, 62 are partially radially above the pivot part 20, so that the pivot part 20 forms a radial support for the pressure fluid pockets 61, 62 and thus also for the sealing surface parts of the sliding surface 16 surrounding the pockets 61, 62.
  • FIG. 11 shows the piston in sections and in a view, to be precise on the scale which gives the data of FIG. 20.
  • FIG. 12 shows a cross section through the piston 83 of the prior art, as is known from the patents mentioned at the beginning. Since the bottoms and pivot axes of the pistons 3 and 83 of FIGS. 11 and 12 are on the same plane, it can clearly be seen here that the piston 83 of the previous technology is much shorter at the top, that is to say it had a much smaller piston guide, and that there was no space for the piston 83 of the previous technology to arrange the torque pressure fluid pockets 54, 55, 71 and 72 at the level of the pivoting center.
  • the swivel center is the center point of the respective partial spherical surfaces of the joint in the swivel joint with spherical part shape, in the case of a roller-shaped swivel part, as in the invention, the swivel axis 22.
  • the swivel center and swivel axis are each designated 22.
  • FIGS. 14 and 18 show essentially the same as FIG. 10, but on a scale that gives the data of FIG. 20, that is to say pistons with a diameter of 20 mm, the unit in a test device at 130 mm having a piston stroke “S” "of 20 mm.
  • the left longitudinal section figure is drawn to the right longitudinal section figure through the relevant part of the unit.
  • FIG. 14 shows the pistons of FIG. 11 with their piston shoes.
  • the pistons of FIG. 15 with their piston shoes of FIG. 16 are shown in the same rotor part of FIG.
  • the pivot bearing bed 104 is not designed in the form of a roller part, that is to say not in the form of a hollow cylinder part with a cylindrical partial surface around the pivot axis 22, as in FIG around the swivel center 22. This makes it necessary to mill the slot 91, 92 into the upper piston part radially above the swivel center 22, which was not necessary with the piston of FIG. 11.
  • the associated piston shoe of FIG. 16 accordingly has a spherical swivel part 20 which can be inserted into the bearing bed 104 in the piston 3 of FIG. 15.
  • the piston shoe requires the tapering of the piston shoe central rod 21 with the radius figures according to 20, 23, 21 of the lower figure in FIG. 16.
  • FIG. 15 also shows that a single pair of tangential pressure fluid pockets 54, 55 with control channels 56, 66 can be arranged in the piston 3 instead of the two torque pressure fluid pocket groups for the purpose of simplification or for lower efficiency of the unit.
  • FIG. 15 show the design of the upper piston arms 1, 2, with the slots 77 and the narrowed outer parts 102, 102 'for fastening and securing against rotation of the holding plate of FIGS. 13 and 17.
  • the piston part above the pivot bearing must be narrowed to one dimension by the processing 91, 92 so that the lateral guide parts 14 of the piston shoe, see FIG. 1, can pivot into these operations 91, 92 or partially enter them.
  • FIG. 19 shows that instead of the holding plate or clamping plate 9 of FIGS. 13 and 17, a pin or several pins 96 can also simply be arranged radially above the piston shoe in order to hold it in the piston.
  • the radial outer parts of the outer diameter of the piston arms 1, 2 are advantageously turned off or drilled to allow riveting of the pins 96 without them being able to touch and damage the cylinder wall or the guide surface on the rotor segments.
  • FIG. 20 shows the values of an assembly with 130 mm “da”, 20 mm piston stroke “S” and 20 mm diameter of the pistons. The individual meanings of the curves are entered below the diagram.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (9)

1. Disposition de piston et de patin glissant dans une machine à pistons radiaux, avec des patins glissants (10) en une pièce en forme de H, avec des nervures radiales (124) présentant des surfaces de partie cylindrique prolongées pour guider le piston (3) sur le rotor (24), avec montage en pivotement -autour d'une axe de pivotement (22) parallèle à l'axe du rotor (C), et au moyen d'une surface de pivotement (23) présentant un rayon constant autour d'un centre commun au palier en creux (4) prévu dans le piston- de la partie de pivotement (20) du patin glissant sur une surface d'appui (6) prévue à cet effet sur le palier en creux (4) pratiqué dans le piston (3), et avec des entailles (93, 94) prévues dans le patin glissant, lesdites entailles partant des extrémités périphériques de ce dernier et allant jusqu'à la traverse centrale du patin glissant, au-dessus de la partie de pivotement (20) du patin, et lesdites entailles étant pratiquées entre les parties de guidage latérales (14) du patin glissant (10), qui constituent les branches du H, caractérisée en ce que les bars de piston (1,2) sont disposés en étant par endroits, au niveau de leur base et par l'intermédiaire de la surface d'appui (6), en contact avec la surface de pivotement. (23) de la partie de pivotement (20) du patin glissant (10), en s'étendant vers l'extérieur radialement à l'axe du rotor, et en glissant au moins par endroits sur les pervures radiales (124) du rotor (24), lesquels bras de piston (1, 2) s'étendent radialement vers l'extérieur à partir de la partie du piston (3) qui forme le palier en creux (4), pour longer l'assise de pivotement (20, 23) du patin glissant (10) et pénétrer dans les entailles (93, 94) du patin glissant (10).
2. Disposition selon la revendication 1, caractérisée en ce que les bras de piston (1, 2) s'étendent jusqu'à la surface de glissement extérieure (16) du patin glissant (10), et que l'on dispose un élément de retenue (7, 9, 96) entre lesdits bras (1, 2,101,102) afin d'empêcher que le patin glissant ne tombe hors du piston (3, 33, 73).
3. Disposition selon la revendication 2, caractérisée en ce que les bras de piston (1,2,101,102) et l'élément de retenue (7, 9, 96) pénètrent dans une rainure annulaire ou un évidement (34) d'un guidage de piston (35), et émergent ainsi, au moins partiellement, radialement à l'extérieur des surfaces de guidage de piston (27).
4. Disposition selon la revendication 1, caractérisé en ce qu'au moins une poche de fluide sous pression (54, 55, 71, 72), alimentée périodiquement en fluide sous pression par les bords d'attaque des évidements (59, 60) de la partie de pivotement (20), est disposée apparoxi- mativement -par rapport à l'axe du rotor- à hauteur radiale du centre de pivotement (22), et traverse la surface extérieure du piston pour pénétrer dans le piston (3, 33, 73) en direction de la composante de force du couple de rotation.
5. Disposition selon la revendication 4, caractérisée en ce que la poche de fluide sous pression (54, 55, 71, 72) présente une possibilité de régulation par paliers, ou encore est réalisée en plusieurs parties, ce grâce à l'emploi connexe d'une poche de liaison (74, 75) disposée dans la paroi de cylindre correspondante, la surface active de la poche de fluide sous pression (54, 55) étant ainsi modifiée pendant la course du piston afin de s'adapter à la composante de force du couple de rotation.
6. Disposition selon la revendication 4, caractérisée en ce que la poche de fluide sous pression (54, 55) est constituée de deux poches séparées (54, 55, 71, 72) décalées radialement l'une par rapport à l'autre, qui peuvent être périodiquement et successivement ouvertes et fermées au fluide sous pression présent dans le cylindre (26).
7. Disposition selon la revendication 1, caractérisée en ce que la traverse centrale (21) du patin glissant et la partie de pivotement (20) du patin glissant sont configurées avec un même rayon (100) autour de l'axe de pivotement (22).
8. Disposition selon la revendication 1, caractérisée en ce qu'une goupille (30), flottant perpendiculairement à l'axe du piston (101) dans des entailles (31, 32) pratiquées dans le piston (3, 53), empêche le démontage du patin glissant (10).
9. Disposition selon la revendication 1, caractérisée en ce que des évidements (19, 77) sont prévus au-dessus de la surface de pivotement (23) du patin glissant (10), évidements dans lesquels s'engagent des éléments de retenue (9, 96) fixés aux dits bras de piston (1, 2).
EP19810103470 1981-05-07 1981-05-07 Disposition de patin glissant pour machine à pistons radiaux Expired EP0064563B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP19810103470 EP0064563B1 (fr) 1981-05-07 1981-05-07 Disposition de patin glissant pour machine à pistons radiaux

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19810103470 EP0064563B1 (fr) 1981-05-07 1981-05-07 Disposition de patin glissant pour machine à pistons radiaux

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EP0064563A1 EP0064563A1 (fr) 1982-11-17
EP0064563B1 true EP0064563B1 (fr) 1985-10-30

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US9638100B2 (en) 2015-04-16 2017-05-02 Mabrouk Telahigue Engine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191213993A (en) * 1912-06-15 1913-07-15 Henry Selby Hele-Shaw Improvements in Hydraulic Motors.
GB232373A (en) * 1924-02-19 1925-04-23 Hans Thoma Improvements in revolving-cylinder pumps or motors for hydraulic transmission of power
US1647309A (en) * 1926-06-23 1927-11-01 Andrew Slavin Rotary pump
US2101829A (en) * 1934-05-10 1937-12-07 Elek K Benedek Hydraulic motor
GB545217A (en) * 1941-01-05 1942-05-15 Aircraft Hydraulic Appliances Improvements in hydraulic motors and pumps
CH274337A (de) * 1947-06-24 1951-03-31 Limited Dowty Equipment Hochdruckpumpe.
GB829241A (en) * 1957-09-09 1960-03-02 Dowty Fuel Syst Ltd Improvements in reciprocating pumps
DE2360181A1 (de) * 1972-12-15 1974-07-04 Breinlich Richard Dr Fluid durchstroemte radialkolben-maschine, bzw. radialkammernmaschine mit zwei mit gleicher drehzahl umlaufende rotoren
CS212800B2 (en) * 1976-07-15 1982-03-26 Ivan J Cyphelly Delivery apparatus with hydrostatic torque transfer by cylindrical pistons

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