EP0351690B1 - Compresseur rotatif à spirales pour fluides compressibles - Google Patents
Compresseur rotatif à spirales pour fluides compressibles Download PDFInfo
- Publication number
- EP0351690B1 EP0351690B1 EP89112618A EP89112618A EP0351690B1 EP 0351690 B1 EP0351690 B1 EP 0351690B1 EP 89112618 A EP89112618 A EP 89112618A EP 89112618 A EP89112618 A EP 89112618A EP 0351690 B1 EP0351690 B1 EP 0351690B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- displacement
- housing
- disc
- discs
- scroll compressor
- 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
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
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
- F04C28/265—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
-
- 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
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
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- 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
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
Definitions
- a spiral loader with rotating displacement disks is known from DE-C-2603462, Fig. 5. It is characterized by an almost pulsation-free delivery of the gaseous working medium, which consists, for example, of air or an air-fuel mixture, and can therefore be used with advantage for charging purposes of internal combustion engines.
- the gaseous working medium which consists, for example, of air or an air-fuel mixture
- several, approximately sickle-shaped work spaces are enclosed along the conveying space between the spirally shaped ribs. These move from an inlet to an outlet, their volume constantly decreasing and the pressure of the working fluid being increased accordingly.
- the delivery rate for a given delivery rate and the maximum boost pressure are determined by the drive ratio, especially since the internal pressure ratio is fixed by the selected spiral geometry.
- the charger also conveys in those operating states in which charging is not required, for example at partial load or even at idle. This would result in a loss of performance and possibly unfavorable temperature increases if the conveyed equipment was relaxed and returned to the inlet of the loader.
- a loader of the type mentioned is known from CH-A-501838. It is the one in FIGS. 8 and 9 shown variant around a two-speed, single-stage machine, in which the two movable displacement disks are loosely arranged on fixed eccentric axes. One of the axes is hollow in order to lead the work equipment to be conveyed out of the machine.
- the displacement disks are provided with toothed rings on their circumference, in which a common gearwheel arranged on a drive shaft engages.
- FIGS. 5 and 6 of this same document Another variant of this working principle is shown in FIGS. 5 and 6 of this same document.
- one of the two discs is also connected to a central drive shaft. When this one disk is rotated, the second disk is taken along in the same direction of rotation by means of power transmission via the spiral ribs.
- an axially movable annular disk which is firmly attached to the back of one of the disks is provided.
- Via a pressure compensation chamber which is connected to the machine outlet and a disc spring, the ring disc presses the two displacement discs together.
- the disadvantage of this arrangement is that the ring disk must be sealed against the housing, which can only be done on the outer circumference with a large diameter and thus high sliding speeds.
- the invention has for its object to design a spiral charger of the type mentioned above to be switched off, i.e. to at least largely prevent the promotion of the work equipment.
- the object is achieved in that the pressure chamber can be connected to the atmosphere via a valve.
- a drive shaft with an exchangeable toothed belt gear is arranged outside the displacement disks, belt pulleys being connected in a rotationally fixed manner to the hubs of the displacement disks. Due to this non-centric drive type, the interior of the displacement disks remains free and the pumped medium can flow freely through a hollow stub axle.
- the two-speed, single-stage machine is shown in approximately natural size.
- the direction of flow of the working fluid is indicated by arrows.
- 1 denotes the housing composed of two halves.
- the two halves are connected to one another via fastening eyes, not shown, for receiving screw connections.
- Axle stub 2 or 2 are in the housing halves on both sides. 3 arranged, which protrude into the interior of the housing.
- the longitudinal axes 4 respectively. 5 of the 2 stub axles are offset from each other by the eccentricity e.
- the rotatable displacement disks 6 and 7 are placed loosely on this axle stub.
- the hub 9 of the right displacement disk 7 is mounted on the axle stub 3 by means of two ball bearings 11 and is axially secured.
- the left displacement disk 6 is designed to be axially displaceable.
- the displacement discs 6 and 7 are constructed symmetrically. They consist essentially of a flat plate 13, which run parallel to each other in the assembled state and from Ribs 14 which are held vertically on the respective plate 13. These ribs 14 run in a spiral (FIG. 2), ie they can either be classic spirals or can be composed of a plurality of circular arcs adjoining one another.
- the ribs 14 have an arc length of one and a half turns, which the machine enters the name "one stage".
- Each plate 13 is equipped with two such ribs 14, the ribs being offset from one another by 180 °. This leads to the designation "two-course”.
- four parallel working spaces 15 are formed, which represent the actual conveying space. On the occasion of the operation, these working spaces open at a 1/4 turn against the outlet 16. At the outer diameter, the spirals open toward the inlet 17, from which they draw in fresh air.
- the system is driven by a drive shaft 18 which is mounted outside the displacement disks in the housing 1 by means of ball bearings 19. On this shaft sit pulleys 20 which drive the pulleys 22 and 23 via toothed belts 21, which in turn with the hubs 8 and. 9 of the displacement disks are connected in a rotationally fixed manner.
- a pressure chamber 26 is therefore formed between the axially displaceable displacement disk 6 and the housing wall, which is acted upon by the pressure of the working medium in the outlet 16.
- the hollow stub shaft 2 is connected to the pressure chamber 26 via a removal tube 27.
- the pressure in the chamber acts on an annular disc 28 which is attached to the housing 1 by means of bellows 29 in an airtight manner using suitable means.
- the annular disk 28 slides with its hub 30 on the stub axle 2. In doing so, it displaces the inner cage of the axial bearing 12 the plates opposite each other.
- the seal 31 is advantageously installed in a rotating manner, so that its lip seals against the standing ring disk hub on the smallest possible diameter.
- a valve 32 is screwed into the housing wall to vent the pressure chamber 26. This can either be operated manually or it opens automatically via a motor-specific or loader-specific parameter. If the valve 32 opens, atmospheric pressure enters the pressure chamber 26 and pressure is equal on both sides of the annular disk 28. The internal pressure in the outlet 16 moves the displacement disk 6 with hub 8 / axial bearing 12 / annular disk 28 functional unit to the left. Since the sealing strips 25 are as a rule firmly inserted in the grooves of the end faces 24 (and are not spring-supported), the axial sealing effect is canceled at the slightest displacement, which interrupts the pressure build-up within the spirals and the conveying process.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Supercharger (AREA)
Claims (3)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH2786/88 | 1988-07-20 | ||
CH2786/88A CH675896A5 (fr) | 1988-07-20 | 1988-07-20 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0351690A1 EP0351690A1 (fr) | 1990-01-24 |
EP0351690B1 true EP0351690B1 (fr) | 1991-09-25 |
Family
ID=4241564
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP89112618A Expired - Lifetime EP0351690B1 (fr) | 1988-07-20 | 1989-07-11 | Compresseur rotatif à spirales pour fluides compressibles |
Country Status (5)
Country | Link |
---|---|
US (1) | US4990072A (fr) |
EP (1) | EP0351690B1 (fr) |
JP (1) | JP2740274B2 (fr) |
CH (1) | CH675896A5 (fr) |
DE (1) | DE58900320D1 (fr) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5342186A (en) * | 1993-06-02 | 1994-08-30 | General Motors Corporation | Axial actuator for unloading an orbital scroll type fluid material handling machine |
US5741120A (en) | 1995-06-07 | 1998-04-21 | Copeland Corporation | Capacity modulated scroll machine |
US5616015A (en) * | 1995-06-07 | 1997-04-01 | Varian Associates, Inc. | High displacement rate, scroll-type, fluid handling apparatus |
US6106247A (en) * | 1998-03-18 | 2000-08-22 | Haldex Brake Corporation | Scroll-type fluid displacement apparatus including an eccentric crank mechanism having an elongated shaft |
GB2401398A (en) * | 2003-05-08 | 2004-11-10 | Automotive Motion Tech Ltd | Pump with output through central bore in journal bearing |
US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
JP2018119522A (ja) * | 2017-01-27 | 2018-08-02 | 三菱重工オートモーティブサーマルシステムズ株式会社 | スクロール型圧縮機 |
WO2019212598A1 (fr) | 2018-05-04 | 2019-11-07 | Air Squared, Inc. | Refroidissement par liquide de compresseur, de détendeur ou de pompe à vide à volute fixe et orbitale |
US20200025199A1 (en) | 2018-07-17 | 2020-01-23 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
US11530703B2 (en) | 2018-07-18 | 2022-12-20 | Air Squared, Inc. | Orbiting scroll device lubrication |
US11473572B2 (en) | 2019-06-25 | 2022-10-18 | Air Squared, Inc. | Aftercooler for cooling compressed working fluid |
US11898557B2 (en) | 2020-11-30 | 2024-02-13 | Air Squared, Inc. | Liquid cooling of a scroll type compressor with liquid supply through the crankshaft |
US11885328B2 (en) | 2021-07-19 | 2024-01-30 | Air Squared, Inc. | Scroll device with an integrated cooling loop |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2475247A (en) * | 1944-05-22 | 1949-07-05 | Mikulasek John | Planetary piston fluid displacement mechanism |
US3175468A (en) * | 1962-04-05 | 1965-03-30 | Cessna Aircraft Co | Fluid motor with delayed pressure loading |
DE1935621A1 (de) * | 1968-07-22 | 1970-01-29 | Leybold Heraeus Gmbh & Co Kg | Verdraengerpumpe |
US4178143A (en) * | 1978-03-30 | 1979-12-11 | The United States Of America As Represented By The Secretary Of The Navy | Relative orbiting motion by synchronoously rotating scroll impellers |
JPS60247082A (ja) * | 1984-05-19 | 1985-12-06 | Tokico Ltd | スクロ−ル式圧縮機 |
JPS618488A (ja) * | 1984-06-20 | 1986-01-16 | Tokico Ltd | スクロ−ル式流体機械 |
US4610610A (en) * | 1984-08-16 | 1986-09-09 | Sundstrand Corporation | Unloading of scroll compressors |
JPS63173870A (ja) * | 1987-01-09 | 1988-07-18 | Kashiyama Kogyo Kk | 全系回転スクロ−ル流体機械 |
-
1988
- 1988-07-20 CH CH2786/88A patent/CH675896A5/de not_active IP Right Cessation
-
1989
- 1989-07-11 EP EP89112618A patent/EP0351690B1/fr not_active Expired - Lifetime
- 1989-07-11 DE DE8989112618T patent/DE58900320D1/de not_active Expired - Fee Related
- 1989-07-18 US US07/380,886 patent/US4990072A/en not_active Expired - Fee Related
- 1989-07-18 JP JP1183845A patent/JP2740274B2/ja not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP0351690A1 (fr) | 1990-01-24 |
CH675896A5 (fr) | 1990-11-15 |
US4990072A (en) | 1991-02-05 |
JPH0267487A (ja) | 1990-03-07 |
DE58900320D1 (de) | 1991-10-31 |
JP2740274B2 (ja) | 1998-04-15 |
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