EP0185236B1 - Drehkolbenmaschine - Google Patents

Drehkolbenmaschine Download PDF

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Publication number
EP0185236B1
EP0185236B1 EP85115187A EP85115187A EP0185236B1 EP 0185236 B1 EP0185236 B1 EP 0185236B1 EP 85115187 A EP85115187 A EP 85115187A EP 85115187 A EP85115187 A EP 85115187A EP 0185236 B1 EP0185236 B1 EP 0185236B1
Authority
EP
European Patent Office
Prior art keywords
rotary piston
sleeves
shafts
shaft
rotary
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
EP85115187A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0185236A3 (en
EP0185236A2 (de
Inventor
Kurt Jauch
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to ES85550024A priority Critical patent/ES8701296A1/es
Publication of EP0185236A2 publication Critical patent/EP0185236A2/de
Publication of EP0185236A3 publication Critical patent/EP0185236A3/de
Application granted granted Critical
Publication of EP0185236B1 publication Critical patent/EP0185236B1/de
Expired 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
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/126—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with elements extending radially from the rotor body not necessarily cooperating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • Rotary piston machines of this type have long been known, for example from DE-PS 23 243, GB-PS 575 350 and DE-AS 1 002 562.
  • each of the rotary pistons has a peripheral surface which completely surrounds the associated shaft and is composed of at least one cylindrical head surface, at least one likewise cylindrical foot surface and flanks which are, for example, involute-shaped and connect adjacent ends of associated head and foot surfaces with one another.
  • the two rotary pistons mesh with one another in the manner of a gear and their peripheral surfaces roll against each other when either one of the two shafts is driven so that the rotary piston machine pumps a fluid as a pump or blower, or when a fluid is supplied to the machine under pressure that drives the two rotary pistons , so that the machine releases a torque to the outside as a motor.
  • the gear-type intermeshing rotary pistons of known generic machines can only slip against one another without slip in those points in which imaginary pitch circles of the two rotary pistons touch each other. If, as is customary, the two shafts are connected to one another by gears of equal size that mesh directly with one another, then their pitch circles and also the pitch circles of the two rotary pistons are of the same size; their diameter corresponds to the center distance of the two shafts. In all points of the two rotary pistons that are not on the associated pitch circle, a slip is superimposed on their pitching motion, which increases with increasing distance from the pitch circle and reaches a maximum amount when a cylindrical head surface of a rotary piston rolls on the cylindrical base surface of another rotary piston.
  • the invention is therefore based on the object of developing a rotary piston machine in such a way that the flow losses are reduced and, insofar as they are unavoidable, less adversely affect the control behavior of the machine than before.
  • the invention keeps frictional resistances and the signs of wear caused thereby extremely low, since the rotatability of the sleeves according to the invention ensures this. that their lateral surfaces serving as foot surfaces roll on the top surfaces of the rotary pistons essentially without slip. A slight slippage can occur at the beginning of the engagement of a head surface with a foot surface until this foot surface has been accelerated to a peripheral speed which corresponds to that of the head surface.
  • each of the shafts is connected to each sleeve supported on it by a freewheel. This prevents the sleeves from being periodically braked to an angular velocity by frictional resistance, which is smaller than that of the associated shaft.
  • FIG. 1 to 3 has a housing 10 which is essentially composed of an upper, glasses-like cover plate 11 in FIG. 1 with two bearing inserts 12, only one of which is shown, a frame-like gear plate 13, also a frame-like one Cylinder plate 14 and a lower cover plate 15.
  • a shaft journal 16 of a shaft 17 extends through the illustrated bearing insert 12.
  • the shaft 17 and a shaft 18 are mounted parallel to each other in one of the bearing inserts 12 and in the lower cover plate 15.
  • An essentially annular sector-shaped rotary piston 27 or 28 is fastened to each of the webs 23, 24 with screws 25 or 26 or by brazing or spot welding or the like.
  • Each of the rotary pistons 27, 28 has a circular cylindrical head surface 29 or 30, which rests on the wall of the associated cylinder space 21 or 22 almost without play and thus in a sealing manner. 3 extends over an arc of 180 ° and is delimited in the circumferential direction by two involute flanks 31 and 32, respectively.
  • Each rotary piston 27, 28, as shown in FIG. 1, has a flat end face sealingly against the gear plate 13 or the lower cover plate 15.
  • a roller bearing 33 or 34 designed as a needle bearing in the illustrated example, is arranged, on which a sleeve 35 or 36 made of hardened steel is mounted.
  • the sleeves 35, 36 each have a circular cylindrical outer surface, which is essentially free of play and thus sealingly rests on a corresponding inner surface of the associated rotary piston 27 or 28 and is referred to below as the base surface 37 or 38.
  • the sleeves 37 and 38 are completely the same; their foot surfaces 37 and 38 have a diameter.
  • the two shafts 17, 18 rotate in the direction of arrow 41 and 42; a pneumatic or hydraulic delivery or working medium passes through an inlet 43 into the overlap region of the two cylinder spaces 21, 22 and flows out through an outlet 44.
  • a pneumatic or hydraulic delivery or working medium passes through an inlet 43 into the overlap region of the two cylinder spaces 21, 22 and flows out through an outlet 44.
  • inlet 43 and outlet 44 are separated from one another by the rotary pistons 27, 28 and sleeves 35, 36.
  • Each of the rotary pistons 27, 28 lies with its radially inner cylindrical surface on the base surface 37 or 38 of the associated sleeve 35 or 36 in such a way that it strives to take it along at the angular velocity of the two shafts 17, 18.
  • the top surface 29 or 30 of each rotary piston 27, 28 comes into engagement with the base surface 38 or 37 of the opposite sleeve 36 or 35; the sleeve in question is accelerated in such a way that the foot surface formed on it assumes the peripheral speed of the head surface rolling on it, so that the rolling takes place without slippage.
  • the angular velocity of the sleeve 35 or 36 concerned thus increases temporarily - in the embodiment according to FIGS. 1 to 3 for half a revolution.
  • the angular velocity of the sleeve 35 or 36 in question drops again to the amount of the angular velocity of the shaft 17 or 18, which is coaxial with it.
  • the periodic acceleration of the sleeves 35 and 36, which is carried out on the rotary piston 28 or 27 is required, takes place almost instantaneously, since the sleeves have only a low inertial mass and since the rolling, as described, takes place under radial prestress and is therefore capable of transmitting sufficient circumferential forces.
  • the sleeves 35 and 36 rest with one of their end faces on the gear plate 13 and on the cover plate 15, respectively.
  • the sleeves 35 and 36 should be fitted particularly closely between the gear plate 13 and cover plate 15 so that they seal in the desirable manner. Then, however, there are frictional resistances which endeavor to brake the sleeves 35 and 36 to a standstill in the time intervals in which they are not driven by a rotary piston 28 or 27 which is rolling on them.
  • each of the roller bearings 33 and 34 is preferably designed as a freewheel, via which each of the shafts 17 and 18 forces each of the associated sleeves 35 and 36 in the direction of the arrow 41 and 42, respectively takes along.
  • the rotary piston machine according to FIG. 4 differs from that shown in FIGS. 1 to 3 essentially in that each of the two rotary pistons 27 and 28 is divided into two sections of the same size as annular sectors. which are diametrically opposed to each other on the associated shaft 17 or 18. As a result, the shafts 17, 18 are free from imbalance, and the rotary piston machine is therefore suitable for higher speeds.
  • the two sections of the rotary piston 27 each extend over approximately 150 °, while the two sections of the rotary piston 28 each extend over approximately 30 ".
  • the two rotary pistons 27 and 28 thus complement each other as in the embodiment according to FIG 1 to 3 to a total of 360 ° minus a small angle which corresponds to a slight play between the intermeshing flanks 31 and 32.
  • the machine shown in Fig. 4 is primarily intended as a motor operated by compressed air.
  • FIG. 5 shows a further variant which is particularly suitable for high-speed, oil-operated engines.
  • This variant can be referred to as a synthesis from the two previous variants. It is common to the variant shown in FIGS. 1 to 3 that the two shafts 17, 18 are assigned the same size rotary lobes; the commonality with Fig. 4 is that each of the shafts 17, 18 are assigned two diametrically opposite rotary pistons 27 and 28 respectively. 5 each rotary piston 27 or 28 thus extends over 90 °. This ensures that the rotary piston machine runs particularly smoothly even at high speeds, for example 6000 per minute.
  • a fitting piece 45 shown in FIGS. 1 and 3 can be installed between each web 23, 24 and the associated rotary piston 27 and 28, respectively, which fixes the rotary piston in a precisely determined position .
  • the shafts 17 and 18 can be sealed directly axially next to the cylinder spaces 21 and 22. however, it is more advantageous if shaft seals 46 and 47 are each arranged at an axial distance from the two cylinder spaces 21 and 22 and a pressure relief duct 48 or 49 is worked into the gear plate 13 or the lower cover plate 15 in between. Depending on the type of working or delivery medium of the rotary lobe machine, the pressure relief ducts 48, 49 lead into the free environment, as shown in FIG. 1, into an oil reservoir or the like.
  • channels 50 which emanate from the head surfaces 29 and 30 in the area of the cylinder spaces 21, 22 under higher pressure and which open out on the adjacent flanks 31 and 32, respectively .
  • Such channels 50 have the course shown in FIG. 3 using the example of the rotary piston 27 when the rotary piston machine operates as a motor and is accordingly supplied with pressure oil or the like from the inlet 43.
  • flanks 31 and 32 which are preferably involute in profile, are preferably arc-shaped or arrow-shaped in the longitudinal direction, that is to say are designed like curved or arrow teeth, so that they do not come into contact with one another suddenly, but as gently as possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Reciprocating Pumps (AREA)
EP85115187A 1984-12-17 1985-11-29 Drehkolbenmaschine Expired EP0185236B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
ES85550024A ES8701296A1 (es) 1984-12-17 1985-12-17 Perfeccionamientos en maquinas de embolos giratorios

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3445979A DE3445979C1 (de) 1984-12-17 1984-12-17 Drehkolbenmaschine
DE3445979 1984-12-17

Publications (3)

Publication Number Publication Date
EP0185236A2 EP0185236A2 (de) 1986-06-25
EP0185236A3 EP0185236A3 (en) 1988-02-03
EP0185236B1 true EP0185236B1 (de) 1989-09-27

Family

ID=6252991

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85115187A Expired EP0185236B1 (de) 1984-12-17 1985-11-29 Drehkolbenmaschine

Country Status (4)

Country Link
US (1) US4697999A (enrdf_load_stackoverflow)
EP (1) EP0185236B1 (enrdf_load_stackoverflow)
JP (1) JPS61182422A (enrdf_load_stackoverflow)
DE (2) DE3445979C1 (enrdf_load_stackoverflow)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3627962A1 (de) * 1986-08-18 1988-03-17 Kurt Jauch Drehkolbenbrennkraftmaschine
EP3144494B1 (de) * 2015-09-21 2018-11-07 Fuelsave GmbH Abgasenergierückgewinnungssystem und verfahren zur abgasenergierückgewinnung

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE246546C (enrdf_load_stackoverflow) *
US1257744A (en) * 1917-03-08 1918-02-26 Robert Schorr Rotary pump or compressor.
GB207065A (en) * 1922-12-29 1923-11-22 Alfred Hugh Tyler Improvements in or relating to rotary pumps, blowers, and the like
US2451603A (en) * 1944-10-04 1948-10-19 Virgil D Barker Rotary pump
DE1255848B (de) * 1961-12-27 1967-12-07 Daimler Benz Ag Drehkolbenmaschine
US3799713A (en) * 1972-03-22 1974-03-26 Waukesha Foundry Co Positive displacement pump

Also Published As

Publication number Publication date
US4697999A (en) 1987-10-06
DE3573290D1 (en) 1989-11-02
JPS61182422A (ja) 1986-08-15
JPH0252096B2 (enrdf_load_stackoverflow) 1990-11-09
EP0185236A3 (en) 1988-02-03
DE3445979C1 (de) 1986-01-30
EP0185236A2 (de) 1986-06-25

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