EP0381682A1 - Drehkolbenverdichter. - Google Patents
Drehkolbenverdichter.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
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)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Rotary Pumps (AREA)
Description
Claims
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 (de) | 1990-08-16 |
EP0381682B1 EP0381682B1 (de) | 1991-12-04 |
Family
ID=25860442
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP88908150A Expired - Lifetime EP0381682B1 (de) | 1987-10-02 | 1988-09-30 | Drehkolbenverdichter |
Country Status (5)
Country | Link |
---|---|
US (1) | US5076768A (de) |
EP (1) | EP0381682B1 (de) |
JP (1) | JPH02502035A (de) |
DE (2) | DE3744637A1 (de) |
WO (1) | WO1989002985A1 (de) |
Families Citing this family (5)
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 |
EP2612035A2 (de) | 2010-08-30 | 2013-07-10 | Oscomp Systems Inc. | Kompressor mit flüssigkeitseinspritzkühlung |
US9267504B2 (en) | 2010-08-30 | 2016-02-23 | Hicor Technologies, Inc. | Compressor with liquid injection cooling |
Family Cites Families (14)
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 |
-
1987
- 1987-12-31 DE DE19873744637 patent/DE3744637A1/de not_active Withdrawn
-
1988
- 1988-09-30 EP EP88908150A patent/EP0381682B1/de not_active Expired - Lifetime
- 1988-09-30 US US07/466,306 patent/US5076768A/en not_active Expired - Fee Related
- 1988-09-30 DE DE8888908150T patent/DE3866706D1/de not_active Expired - Lifetime
- 1988-09-30 JP JP63507552A patent/JPH02502035A/ja active Granted
- 1988-09-30 WO PCT/DE1988/000601 patent/WO1989002985A1/de active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO8902985A1 * |
Also Published As
Publication number | Publication date |
---|---|
JPH0357308B2 (de) | 1991-08-30 |
WO1989002985A1 (en) | 1989-04-06 |
DE3866706D1 (de) | 1992-01-16 |
JPH02502035A (ja) | 1990-07-05 |
DE3744637A1 (de) | 1989-04-13 |
EP0381682B1 (de) | 1991-12-04 |
US5076768A (en) | 1991-12-31 |
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Legal Events
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