EP0381682A1 - Compresseur cellulaire a piston rotatif. - Google Patents

Compresseur cellulaire a piston rotatif.

Info

Publication number
EP0381682A1
EP0381682A1 EP88908150A EP88908150A EP0381682A1 EP 0381682 A1 EP0381682 A1 EP 0381682A1 EP 88908150 A EP88908150 A EP 88908150A EP 88908150 A EP88908150 A EP 88908150A EP 0381682 A1 EP0381682 A1 EP 0381682A1
Authority
EP
European Patent Office
Prior art keywords
rotor
inner rotor
compressor according
shaft
rotary piston
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
EP88908150A
Other languages
German (de)
English (en)
Other versions
EP0381682B1 (fr
Inventor
Renate Ruf
Rudolf Bierling
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
Publication of EP0381682A1 publication Critical patent/EP0381682A1/fr
Application granted granted Critical
Publication of EP0381682B1 publication Critical patent/EP0381682B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump

Definitions

  • the invention relates to a rotary compressor according to the preamble of claim 1.
  • the invention has for its object to provide a rotary compressor according to the preamble of claim 1, which is characterized by a high flow rate at low drive speeds.
  • the proposed rotary piston compressor also has significant advantages over the prior art with regard to the mounting of the external rotor.
  • the bearings of the outer rotor must have a large diameter, since the shaft of the inner rotor, which is eccentric to the axis of rotation of the outer rotor, extends outwards.
  • large diameter bearings are expensive and subject to high loads at high speeds.
  • the external rotor is not stored in a large bearing, but rather via three symmetrically arranged rollers. This solves the problem of the high peripheral speed of the large bearing, but at the expense of a complex construction.
  • the outer rotor can be mounted with its side walls axially outside the bearings of the inner rotor, the diameter of these bearings being relatively small since the shaft of the inner rotor ends axially within these bearings.
  • the mass balance can be achieved by one or more heavy metal pins e.g. made of tungsten in a nickel-iron binder, which extend through the inner rotor parallel to the axis of rotation and one of which can be used at the same time for rotationally fixing the inner rotor on its shaft.
  • the shaft with the counterweight can consist of one piece and be inserted with a press fit into a corresponding recess in the inner rotor.
  • phase position between the internal and external rotor is set extremely precisely. This phase position is maintained by the gear between the inner and outer rotor. While the external gear can be screwed directly onto the inner rotor in the case of compressors that do not dry out, this is not possible due to the need to lubricate the gearbox in dry-running compressors.
  • the groove which receives the heavy metal pin used for rotation, beyond the inner rotor and the external gear outside the interior of the outer rotor on the Arrange the shaft and connect it to the shaft by means of a pin or projection that engages in the groove in the shaft.
  • a single pin can also be provided on the shaft to prevent rotation of the inner rotor and the outer gear.
  • radially inward projections can be formed on the inside of the outer peripheral wall of the inner rotor in the area diametrically opposite the hub, from which material can be removed for the purpose of balancing the rotor. If the end faces of the inner rotor are closed off by covers to prevent flow around the sides and to keep the leakage small, these projections are arranged near the end faces and the covers are provided in the area of the projections with openings through which a tool for removing material from the protrusions can be passed.
  • the housing component in which the transmission-side end of the shaft is mounted can have a disk-shaped extension which extends between the inner rotor and the outer gear, has a bore for the shaft to pass through and, with its outer circumference, seals into a corresponding circular recess in the adjacent end wall of the outer rotor is used.
  • very tight tolerances are usually required to maintain small sealing gaps, which cause high manufacturing accuracy and correspondingly high costs.
  • both housing components in which the ends of the shaft are mounted and which extend through the end walls of the external rotor are provided with disk-shaped approaches, which are inserted in corresponding circular recesses in the end walls of the outer rotor, and plates are attached to the inner end walls of the outer rotor such that their inner surfaces are flush with the inner surfaces of the disc-shaped projections.
  • a compensating disk of suitable thickness can be provided between one of the housing components and a shaft extension.
  • Fig. 1 shows a longitudinal section of a rotary compressor
  • FIG. 2 shows a section along line II-II in FIG. 1
  • FIG. 3 shows a section along line III-III in FIG. 1
  • Fig. 4 is an end view of the inner rotor in a modification
  • FIG. 5 shows a section along line V-V in FIG. 4.
  • the parallel and inner-axis rotary piston compressor shown has a housing which is composed of a peripheral wall 1 and side parts 2 and 3 attached to it laterally, the left side part comprising a bearing plate 4 with a hub 5, an intermediate plate 6 and a hub 5 penetrating has bearing extension 7, while the right side part 3 consists only of a bearing plate 8 with a hub 9 and this penetrating bearing extension 10.
  • an outer rotor 12 is mounted on the bearing hubs 5 and 8 via maintenance-free and encapsulated ball bearings 11, which has a cylindrical outer surface 1 3 and rotates with a small sealing gap in the corresponding cylindrical interior 14 of the housing, as can be seen from FIG. 2 .
  • the interior 14 communicates with an inlet duct 15 and an outlet duct 16.
  • a compressor chamber 17 is provided in the form of an arena, which is connected to control openings 18 and 19 in the peripheral surface of the external rotor.
  • an inner rotor 20 with a circular cross section is arranged eccentrically on a shaft 21.
  • the diameter of the inner rotor 20 corresponds, except for tight sealing gaps in the order of 50 to 100 ⁇ m, to the diameter of the semicircular end sections of the compressor chamber 17.
  • the inner rotor shaft 21 is, as shown in FIG. 1, via bearings 22 in the bearing extensions 7 or 10 stored.
  • the axis of rotation D 1 of the inner rotor shaft 21 runs parallel to the axis of rotation D 2 of the outer rotor 12.
  • the inner and outer rotors are at a certain speed ratio to one another, which in the exemplary embodiment is 2: 1 and by a gear, consisting of an outer gear arranged on the inner rotor shaft 21 23 and an internal gear 24 fastened to the external rotor 12,
  • the outer rotor 12 is composed of a central part 25 and side walls 26 and 27, which are provided with circular openings 28 and 29, into which the bearing extensions 7 and 10 protrude.
  • a drive pulley 30 is connected to the left side wall 27 of the external rotor 12 in FIG. 1.
  • the bearing extension 10 is provided with a disk-shaped extension 31, which is sealingly inserted into the opening 28 in the outer rotor side wall 26 via a sealing ring 32 is »is on the opposite side. the outer runner side wall 27 sealingly inserted via seals 33 into a corresponding circular opening 34 in the intermediate housing part 6.
  • the inner rotor 20 is made as light as possible.
  • it is hollow and made of light metal and consists of an outer peripheral wall 40 and a hub 41 through which the shaft 21 passes.
  • Heavy metal pins 42 and 43 are provided, which extend over the entire length of the inner rotor 20.
  • the heavy metal pins consist of a material with a high specific weight, for example of tungsten in a nickel iron binder. As a result, a full mass balance of the inner rotor 20 is achieved in each plane running perpendicular to its longitudinal central axis M.
  • the heavy metal pin 43 also serves for the rotationally fixed connection of the inner rotor 20 to the shaft 21, and a groove 44 and 45, which is semicircular in cross section, is provided in the hub 41 and in the shaft 21 for receiving it.
  • the groove 44 extends in Fig. 1 to the right beyond the inner rotor 20 and at the same time serves for rotation fixed and correct arrangement of the external gear 23, which engages with a corresponding nose 47 (Fig. 3) in the groove 44.
  • the pin 43 could be extended to the right in FIG. 1 and establish the rotationally fixed connection between the shaft 21 and the external gear 23.
  • a balancing option is provided.
  • radially inwardly directed projections 46 are provided on the inside of the outer peripheral wall 40 of the inner rotor 20 in the area diametrically opposite the hub 41.
  • the inner rotor 20 can be completely balanced by removing material from the projections 40. If the end sides of the inner rotor 20 are completed by covers, who provided the openings in these covers, through which the projections 46 can be processed.
  • Narrow sealing gaps usually result in tight tolerances, which require a high manufacturing effort.
  • 12 plates 50 are provided on the inner surfaces of the side walls 26, 27 of the outer rotor, the thickness of which is selected so that its inner surfaces are aligned with the inner surfaces of the disk-shaped projections 31 and 31a after assembly.
  • the inside diameter of the plate 50 on the right in FIG. 1 is smaller than the diameter of the opening 28, so that lubricant which passes through the seal 32 cannot get into the compressor chamber 17.
  • the axial position of the inner rotor 20 relative to the outer rotor 12 is achieved by a shim 51 between the bearing 22 for the shaft 21 and the outer gear 23.
  • a particularly useful and obvious modification is to manufacture the inner rotor 20 and the shaft 21 in one piece from light metal, so that the heavy metal pin 43 only contributes to the mass balance.
  • the number, shape and arrangement of the heavy metal pins 42, 43 depend on the respective conditions.
  • an inner rotor 20 ' is shown, the shaft 21' is in one piece with a counterweight 65 and consists, for example, of a precision-drawn steel part.
  • This steel part is inserted with a press fit into an opening 66 of the inner rotor 20 'and bears with a fit at the points 67 of the opening.
  • the balance weight 65 extends, as shown in FIG. 5, over the entire length of the inner rotor 20 ', so that, as with the inner rotor 20 of FIG. 1, there is a full mass balance in each transverse plane of the inner rotor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

Un compresseur cellulaire à piston rotatif à axes parallèles et internes comprend un induit externe mené (12) pourvu d'un espace de compression (17) dans lequel est rotativement monté un induit interne (20). L'induit interne (20) est creux, construit en métal léger, et est monté sur un arbre (21). Un équilibrage parfait des masses de l'induit interne (20) est assuré par des goupilles en métal lourd (42, 43) qui s'étendent sur toute la longueur de l'induit interne (20). La goupille (43) en métal lourd sert en même temps à empêcher l'induit interne (20) de tourner par rapport à l'arbre (21), au cas où ces deux pièces ne forment pas ensemble une seule pièce.
EP88908150A 1987-10-02 1988-09-30 Compresseur cellulaire a piston rotatif Expired - Lifetime EP0381682B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3733398 1987-10-02
DE3733398 1987-10-02
DE19873744637 DE3744637A1 (de) 1987-10-02 1987-12-31 Drehkolbenverdichter
DE3744637 1987-12-31

Publications (2)

Publication Number Publication Date
EP0381682A1 true EP0381682A1 (fr) 1990-08-16
EP0381682B1 EP0381682B1 (fr) 1991-12-04

Family

ID=25860442

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88908150A Expired - Lifetime EP0381682B1 (fr) 1987-10-02 1988-09-30 Compresseur cellulaire a piston rotatif

Country Status (5)

Country Link
US (1) US5076768A (fr)
EP (1) EP0381682B1 (fr)
JP (1) JPH02502035A (fr)
DE (2) DE3744637A1 (fr)
WO (1) WO1989002985A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR920700352A (ko) * 1989-03-31 1992-02-19 원본미기재 회전식 피스톤 압축기
JP2000027772A (ja) * 1998-07-08 2000-01-25 Matsushita Electric Ind Co Ltd 密閉型圧縮機
ITTV20030089A1 (it) * 2003-06-19 2003-09-17 Orlando Canal Meccanismo per gas-dinamica azione volumetrica alterno rotativa a 60 grado, "gavara-60", per uso generale e particolarmente per motori endotermic
US9267504B2 (en) 2010-08-30 2016-02-23 Hicor Technologies, Inc. Compressor with liquid injection cooling
US8794941B2 (en) 2010-08-30 2014-08-05 Oscomp Systems Inc. Compressor with liquid injection cooling

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US883271A (en) * 1907-09-16 1908-03-31 George Wilson Rotary pump.
US1753476A (en) * 1927-06-29 1930-04-08 Joseph R Richer Rotary pump or blower
US1887884A (en) * 1929-07-18 1932-11-15 Powerplus 1927 Ltd Rotary pump machine
US1897190A (en) * 1930-04-22 1933-02-14 Powerplus 1927 Ltd Rotary pump machine
DE1000029B (de) * 1955-03-30 1957-01-03 Gerhard Von Der Heyde Drehkolbenmaschine
US3012550A (en) * 1958-10-07 1961-12-12 Nsu Motorenwerke Ag Rotary mechanism bearing arrangement
US3311094A (en) * 1964-08-18 1967-03-28 Kehl Henry Rotary engine
BE794675A (fr) * 1972-02-08 1973-05-16 Renault Distribution de machine rotative
DE2544795A1 (de) * 1975-10-07 1977-04-21 Gerhard Von Der Heyde Drehkolbenmaschine
DE2604665A1 (de) * 1976-02-06 1977-08-11 Sullair Europ Corp Drehkolbenmaschine
CH664193A5 (de) * 1982-03-03 1988-02-15 Wankel Felix Abgasbetriebener rotationskolbenlader.
KR840007619A (ko) * 1983-02-04 1984-12-08 미다가쓰시게 압축기의 용량제어방법 및 그 장치
DE3445653A1 (de) * 1984-12-14 1986-06-19 Wankel Gmbh, 1000 Berlin Auswuchtung eines parallel- und aussenachsigen im kaemmeingriff arbeitenden rotationskolbengeblaeses
US4915596A (en) * 1988-10-24 1990-04-10 Mccall William B Pure rotary positive displacement device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8902985A1 *

Also Published As

Publication number Publication date
EP0381682B1 (fr) 1991-12-04
DE3866706D1 (de) 1992-01-16
JPH0357308B2 (fr) 1991-08-30
US5076768A (en) 1991-12-31
WO1989002985A1 (fr) 1989-04-06
DE3744637A1 (de) 1989-04-13
JPH02502035A (ja) 1990-07-05

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