EP0064563A1 - 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
EP0064563A1
EP0064563A1 EP19810103470 EP81103470A EP0064563A1 EP 0064563 A1 EP0064563 A1 EP 0064563A1 EP 19810103470 EP19810103470 EP 19810103470 EP 81103470 A EP81103470 A EP 81103470A EP 0064563 A1 EP0064563 A1 EP 0064563A1
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EP
European Patent Office
Prior art keywords
piston
shoe
rotor
piston shoe
arms
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.)
Granted
Application number
EP19810103470
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German (de)
English (en)
Other versions
EP0064563B1 (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
Original Assignee
Breinlich Richard Dr
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Publication date
Application filed by Breinlich Richard Dr filed Critical Breinlich Richard Dr
Priority to EP19810103470 priority Critical patent/EP0064563B1/fr
Publication of EP0064563A1 publication Critical patent/EP0064563A1/fr
Application granted granted Critical
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 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 slots reaching the central web above the swivel part between the side guide parts of the piston.
  • H- shaped piston shoes also called plunging or deep-diving piston shoes
  • H-PS 14 03 748, 13 02 469, 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 parts of the H-shaped piston shoe.
  • Radial piston machines can also open up new areas of application as motors, with the rotors of the motors being able to drive and carry at the same time, for example.
  • the use of the units as motors has therefore increased.
  • a large relative piston stroke is of particular importance for engines in order to obtain a high torque with a small engine size.
  • a high stroke ratio "S / da” must be aimed for.
  • the efficiency and the stroke ratio of a pump are not as important as in the engine. 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 stroke ratio, increases the force 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 pistons is also correspondingly ver lengthened 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 area allows a greater load capacity for the force component in the direction of rotation and thus a bigger D deer moment to.
  • the piston arms can protrude into an annular groove or recess in the piston stroke guide and accordingly at least partially emerge outside the piston guide surfaces.
  • At least one pressure fluid pocket is periodically acted upon by pressure fluid through the pivoting part and its recesses with its control edges is arranged with respect to the rotor axis approximately at the radial height of the pivot center between the piston and piston shoe through the outer surface of the piston into the piston in the direction of the torque force component. 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. With the pressure fluid pocket, a pressure field can be generated 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 low output weight of the engine according to the invention is particularly remarkable. For example, 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 pivot portion of the piston shoe receiving pivot bed is guided in the piston at most a 180 0- arc around the pivotal 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.
  • the piston shoe 10 has a roller-shaped piston shoe central web 12 with a pivot axis 22 and bearing 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 piston shoe is called “immersed” or “deep-immersed” piston shoe 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 the outer surface 16 on the outer diameter 29 the rotor webs penetrate radially inwards into the turned-off rotor parts (deep-diving 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 pivoting part 20, the pivot axis 22 of which may be somewhat lower here, and the recesses 19, which serve for the locking pins 96 of the piston 3, see FIG. 4, to engage in the recesses 19 and the locking pins 96 can secure the piston shoe of FIG. 3 against falling out of the piston of FIG. 4.
  • the recesses 19 are dimensioned so that the pivoting movement can take place undisturbed despite the locking pins 96.
  • the upper part has the K ol bens 3, the axis of which is designated 101, the bearing or pivot bed 4 with the bearing surface 6 for receiving the pivoting part 20 of the piston shoe 10 and the bearing surface 23.
  • the Invention is the bearing surface 6 only as a 180 ° arc, based on the pivot axis 22, formed, 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 to such an extent that after the piston shoe 10 is 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 that 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 part of the piston 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 pivoting 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, in the case of deeply diving piston shoes, an annular groove 34 which is the guide Surface 27 breaking through and dividing, 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 ⁇ 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 ⁇ .
  • 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 Kolbenhubring 35 may also be a part of the casing, or a G-e formed as a housing part with the guide surface 27, so that a separate Kolbenhubring 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.
  • the piston shoes of FIGS. 1, 2 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 piston 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.
  • FIG. 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 in the arms 1, 2 of the pistons 3 in FIG. 11, as is also shown on the left in FIG. 10.
  • the arch 78 can be provided to press the piston shoe 10 firmly onto the pivot bearing surface 6 by means of the clamping plate 9 and to smoothly follow the outer surface of the piston shoe during the pivoting 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 other parts lie 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 the control pockets 60, 59 in the Limit swivel part of the piston shoe are 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 are now arranged according to the invention at the radial height of the pivot axis 22 due to the inventive arrangement of the piston arms 1, 2, while they were too deep radially inward in the prior art 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 field in the circumferential direction in analogy to the radial piston movement and to the data in FIG Outer surface of the piston in question, for example 73.
  • This position is shown 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.
  • 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 guide the pressure fluid into the pressure fluid pockets 61, 62 in the outer surface of the piston shoes, ie 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, on the scale that gives the data in 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 when piston 83 of the V ortechnik no space was provided to the torque-pressure fluid pockets 54, 55 to be arranged at the level of the pivot center 71 and 72nd It can also be seen how the bearing bed surface 6 had to be formed by more than 180 degrees (about 240 degrees around the swivel axis in the case of the piston 83 of the pre-technology in order to encompass the corresponding swivel part of the piston shoe of the pre-technology in places, which means individual clamping, machining and individual measurements the manufacture of surface 6 and which made the piston of the preliminary technology expensive T eilkugel lake of the joint, when barrel shaped pivoting part,
  • 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 swivel bearing bed 104 is not 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 swivel 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.
  • Figure 15 also shows that in the piston 3, instead of the two torque-pressure fluid pocket groups for the purpose of simplification or lower efficiencies of the unit even a single pair of T angential horrfluidtaschen 54, 55 may be arranged with control channels 56, 66th
  • 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. It should also be noted, like the drawing right in Fig. 15 shows that in this embodiment, however 11, as the right view drawing shows, 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. 2, into this processing 91 , 92 can pivot into or partially enter them.
  • FIG. 19 shows that instead of the holding plate or clamping plate 9 of FIGS. 13 and 17, one or more 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)
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 true EP0064563A1 (fr) 1982-11-17
EP0064563B1 EP0064563B1 (fr) 1985-10-30

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9638100B2 (en) 2015-04-16 2017-05-02 Mabrouk Telahigue Engine

Citations (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
FR2358566A1 (fr) * 1976-07-15 1978-02-10 Cyphelly Ivan J Machine a refoulement a transmission de couple hydrostatique au moyen de pistons a rouleaux

Patent Citations (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
FR2358566A1 (fr) * 1976-07-15 1978-02-10 Cyphelly Ivan J Machine a refoulement a transmission de couple hydrostatique au moyen de pistons a rouleaux

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9638100B2 (en) 2015-04-16 2017-05-02 Mabrouk Telahigue Engine

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EP0064563B1 (fr) 1985-10-30

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