US3671153A - Rotary piston compressor - Google Patents

Rotary piston compressor Download PDF

Info

Publication number
US3671153A
US3671153A US66278A US3671153DA US3671153A US 3671153 A US3671153 A US 3671153A US 66278 A US66278 A US 66278A US 3671153D A US3671153D A US 3671153DA US 3671153 A US3671153 A US 3671153A
Authority
US
United States
Prior art keywords
eccentric
piston
outlet
medium
apertures
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
US66278A
Other languages
English (en)
Inventor
Friedrich Luck
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.)
Wankel GmbH
Borsig GmbH
Original Assignee
Wankel GmbH
Borsig GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wankel GmbH, Borsig GmbH filed Critical Wankel GmbH
Application granted granted Critical
Publication of US3671153A publication Critical patent/US3671153A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/10—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
    • 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
    • F01C1/22—Rotary-piston machines or engines of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth- equivalents than the outer member

Definitions

  • a circular piston compressor having a stationary housing with a trochoidal inner boundary and a rotary piston mounted on the eccentric of 'a shaft so that its axial centerline describes a circular path during its rotation.
  • Inlet apertures are provided in the end walls or cover of the housing or both for entry of the working medium and outlet apertures are provided in the flanks of the piston.
  • a passage adapted to communicate with the outlet aperture occupies virtually the inside diameter of the eccentric and diminishes spirally in the pin towards the outlet for outlet of the compressed medium.
  • the invention relates to a circular piston compressor having a trochoidal inner boundary or surface of its stationary housing and a rotary piston mounted on the eccentric of a eccentric shaft, so that its axial centerline describes a circular path during its rotation.
  • the problem of concern is to avoid such additional control members and to make possible passage cross sections of adequate size, and in particular, to construct the outlet passage to equalize and diminish outlet shocks.
  • Intake apertures are provided in the end walls and/or cover of the housing, in a manner known per se, for entry of the working medium.
  • apertures are present in the flanks of the piston and a passage is present in the eccentric and its pin. The passage in the eccentric occupying nearly its entire inside diameter, and constricting spirally in the eccentric pin towards the outlet.
  • the medium Due to the spiral shape of the interior of the eccentric, the medium is set in a rotation superimposed on the motion of the eccentric. With this rotation it traverses the cylindrical outflow passage in the eccentric pin and flows out of the compression chamber without undesirable eddy formation.
  • the rotary motion in the outflow passage is maintained, though in attenuated form, over the period during which delivery of the medium ceases until the beginning of the next delivery impulse. Therefore, when the new delivery impulse begins, the medium does not have to be accelerated from rest. Instead, a translatory motion need merely be imposed as a component upon its tangential motion. The reduction of shock may be gauged by unlike differences in velocities before and during the delivery impulse under the old and new systems.
  • the spirally constricting inner chamber of the eccentric be arranged so that the part of the eccentric shell serving as a baflie wall for the medium "ice is increasingly thickened towards the end away from the inlet aperture and has a tongue-like projection continuing the spiral curve of the inner wall of the eccentric and forming a cushion space not participating in the flow of the medium.
  • This tongue-shaped projection suppresses parasite circulations in the inner chamber of the eccentric.
  • the cushion space divided off by it owing to the elasticity of its contents, damps the oscillations of medium caused by outlet shocks.
  • the arrangement of the spiral baffle wall has the additional advantage that the kinetic energy of the medium flowing out in rotation is utilized towards the rotation of the shaft, thus reclaiming flow losses that would otherwise occur.
  • the direction of flow may be further influenced by various arrangements of the outlet apertures in the piston.
  • the outlet apertures may, as known per se, be shifted out of the centers of the flanks of the piston in direction of rotation, that is, asymmetrically arranged. This changes the proportions of flow to be drawn respectively from the posterior and anterior parts of the working chamber in question, so that the flow direction in the outlet port of the piston is likewise modified.
  • a displacement of the outlet aperture into the leading part of the flank lends the flow vector a more tangential direction, and a displacement into the trailing part, a more radial direction.
  • nozzles may be provided in the working chambers to inject cooling oil.
  • the nozzles may advantageously be arranged in the vicinity of the axial zones of the trochoids, either in the shell or in the end walls of the housing.
  • the cooling oil may serve to lubricate the sliding parts of the machine and help seal the working chambers.
  • FIG. 1 shows an axial section of a circular piston compressor according to the invention
  • FIG. 2 shows a radical section at the line IIII in FIG. 1,
  • FIG. 3 shows a partial cross section in the same plane with the rotary piston in a different position
  • FIG. 4 shows a partial cross section in the same plane with asymmetrical outlet apertures.
  • the stationary, multiply subdivided housing 1 of the machine contains a suction passage 3 leading to the lateral intake apertures 4.
  • a shaft 5 is mounted on bearings 6 and 7.
  • the shaft 5 is composed of drive pin 5a, hollow eccentric 5b, and tubular pins 5c, through which the compressed medium is carried off.
  • the piston 8 is mounted on the eccentric 5b. In its flanks, it has outlet apertures 9 through which the compressed medium is forced into the chamber of the eccentric 512 by way of the entrance 10 in the shelll of the eccentric.
  • the piston 8 is in the position of incipient outlet of medium from the working chamber 15.
  • the flow of medium forced out through the outlet aperture 9 is indicated by the arrow 16.
  • it is deflected by the spiral wall 5b of the eccentric and the adjoining tongue-shaped projection 17, and enters the eccentric pin 50 tangentially.
  • the space 5e formed on the side of the eccentric at the left of the drawing, between the entrance 10 and the tongue-shaped projection 17, is not in the flow field and so acts merely as a cushion.
  • FIG. 3 shows another position of the rotating parts.
  • the eccentric 5b has rotated onward through 60, while the piston 8 has revolved 40 back relative to the eccentric 5 and 20 forward relative to the housing 1, thus reaching top dead center, where delivery ceases and the outlet aperture 9 closes.
  • the compressed medium that has flowed into the hollow pin 5c of the eccentric assumes a pure rotary motion, which is maintained with decreasing intensity by the kinetic energy imparted until the new delivery impulse sets in.
  • the proper rotation of the pin may here be disregarded, as it is only the relative velocity that counts.
  • FIG. 4 shows the modification with outlet apertures 9 in piston 8 arranged asymmetrically; specifically the apertures are placed in the leading portion of the flank 8a of the piston.
  • the entrance 10 in eccentric 5b has suffered the like displacement, so that the same outlet aperture is still present in the same piston position.
  • the position of the piston in FIG. 4 is the same as in FIG. 2.
  • the flow direction in the outlet aperture 9 is indicated by the arrow 18.
  • the curvature of this arrow means that the delivery is eflFected predominantly from the posterior, enlarged portion 15a of the working chamber 15. In other words, the flow must be more tangentially directed. A more graphic representation of this fact is difficult because in the present examples, the flow has already been deflected by the edge 5 of the eccentric.
  • a circular piston compressor having a stationary housing with a trochoidal inner boundary and a shaft including an eccentric and a pin therefor and having a rotary piston mounted on'the eccentric so that the axial centerline of the piston describes a circular path during the rotation thereof; the housing having intake apertures therein for entry of the working medium, the piston flanks having outlet apertures and the eccentric and its pin having a passage therethrough adapted to communicate with said outlet apertures, the passage substantially occupying the full interior of the eccentric and diminishing spirally in the direction of rotation of the piston in radial section and funnel-fashion in the direction of exit flow of the medium in axial section.
  • a rotary piston compressor in accordance with claim 1 wherein the leading and trailing edges, in the direction of rotation of the piston, of the outlet apertures in the flanks of the piston, are slanted in adaptation to the angle of the spiral wall of the eccentric chamber at its entrance.
  • a circular piston compressor having a stationary housing with a trochoidal inner boundary and a shaft including an eccentric and a pin therefor and having a rotary piston mounted on the eccentric so that the axial centerline of the piston describes a circular path during the rotation thereof, the housing having intake apertures therein for entry of the working medium, the piston flanks having outlet apertures and the eccentric and its pin having a passage therethrough adapted to communicate with said outlet apertures, the passage occupying virtually the inside diameter of the eccentric and diminishing spirally in the pin toward the apertures for outlet of the compressed medium, part of the eccentric wall serving as baffle for the medium being increasingly thickened toward the side away from the entrance and having a tongue-shaped projection continuing the spiral curve of the eccentric wall, and the projection forming a cushion space not participating in the flow of the medium.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US66278A 1969-08-26 1970-08-24 Rotary piston compressor Expired - Lifetime US3671153A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19691943338 DE1943338A1 (de) 1969-08-26 1969-08-26 Kreiskolben-Verdichter

Publications (1)

Publication Number Publication Date
US3671153A true US3671153A (en) 1972-06-20

Family

ID=5743813

Family Applications (1)

Application Number Title Priority Date Filing Date
US66278A Expired - Lifetime US3671153A (en) 1969-08-26 1970-08-24 Rotary piston compressor

Country Status (6)

Country Link
US (1) US3671153A (de)
JP (1) JPS5110363B1 (de)
CH (1) CH524071A (de)
DE (1) DE1943338A1 (de)
FR (1) FR2058147A5 (de)
GB (1) GB1268999A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6146120A (en) * 1998-07-29 2000-11-14 Jenn Feng Industrial Co., Ltd. Rotary engine having an improved rotor structure
US6158992A (en) * 1996-03-21 2000-12-12 Unisia Jecs Corporation Rotary pump having a substantially triangular rotor
CN105201835A (zh) * 2015-10-19 2015-12-30 广西大学 一种摆动转子压缩机
WO2016137981A1 (en) * 2015-02-24 2016-09-01 Illinois Tool Works Inc. Compressor for discharging a medium

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62153502A (ja) * 1985-12-23 1987-07-08 ウアンケル・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング 回転ピストンエンジンの偏心軸

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6158992A (en) * 1996-03-21 2000-12-12 Unisia Jecs Corporation Rotary pump having a substantially triangular rotor
US6146120A (en) * 1998-07-29 2000-11-14 Jenn Feng Industrial Co., Ltd. Rotary engine having an improved rotor structure
WO2016137981A1 (en) * 2015-02-24 2016-09-01 Illinois Tool Works Inc. Compressor for discharging a medium
US20180023554A1 (en) * 2015-02-24 2018-01-25 Illinois Tool Works Inc. Compressor for discharging a medium
US10968906B2 (en) * 2015-02-24 2021-04-06 Illinois Tool Works Inc. Compressor for discharging a medium
CN105201835A (zh) * 2015-10-19 2015-12-30 广西大学 一种摆动转子压缩机

Also Published As

Publication number Publication date
SU380025A3 (de) 1973-04-20
DE1943338A1 (de) 1971-06-09
GB1268999A (en) 1972-03-29
CH524071A (de) 1972-06-15
FR2058147A5 (de) 1971-05-21
JPS5110363B1 (de) 1976-04-03

Similar Documents

Publication Publication Date Title
US2280100A (en) Fluid pressure apparatus
US2804260A (en) Engines of screw rotor type
US5004407A (en) Method of scavenging air and oil and gear pump therefor
US2111568A (en) Rotary compressor
US1668532A (en) Rotary machine
US3531227A (en) Gear compressors and expanders
US3744942A (en) Rotary sliding vane compressor with hydrostatic bearings
US2463080A (en) Interengaging impeller fluid pump
US3669579A (en) Compressors
US2831631A (en) Rotary compressor
US3671153A (en) Rotary piston compressor
US3760478A (en) Method for assembling a rotary sliding vane compressor
US3743453A (en) Compact rotary sliding vane compressor for an automotive air-conditioning system
KR900006402B1 (ko) 로우터리 베인기구 및 그 구동방법
MXPA96005345A (es) Entrada de portillo de valvula compresora giratoria mejorada.
JPS58135396A (ja) 可動翼型圧縮機
US3743443A (en) Vacuum pump
US3574491A (en) Gear-type rotary machine
JP2019056322A (ja) 圧縮機
US3173606A (en) Pump
JPH0261630B2 (de)
US2441771A (en) Yieldable drive for rotors
US3086474A (en) Screw pump
US3191853A (en) Rotary compressor
EP0746686A4 (de) Seitenkanalpumpe