EP0351690A1 - Compresseur rotatif à spirales pour fluides compressibles - Google Patents

Compresseur rotatif à spirales pour fluides compressibles Download PDF

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Publication number
EP0351690A1
EP0351690A1 EP89112618A EP89112618A EP0351690A1 EP 0351690 A1 EP0351690 A1 EP 0351690A1 EP 89112618 A EP89112618 A EP 89112618A EP 89112618 A EP89112618 A EP 89112618A EP 0351690 A1 EP0351690 A1 EP 0351690A1
Authority
EP
European Patent Office
Prior art keywords
displacement
disc
disks
housing
pressure chamber
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
EP89112618A
Other languages
German (de)
English (en)
Other versions
EP0351690B1 (fr
Inventor
Frank Güttinger
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.)
Aginfor AG
Original Assignee
Aginfor AG fuer industrielle Forschung
Aginfor AG
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 Aginfor AG fuer industrielle Forschung, Aginfor AG filed Critical Aginfor AG fuer industrielle Forschung
Publication of EP0351690A1 publication Critical patent/EP0351690A1/fr
Application granted granted Critical
Publication of EP0351690B1 publication Critical patent/EP0351690B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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

  • the invention relates to a rotating spiral loader for compressible media, consisting essentially of a housing in which two symmetrically constructed displacement disks are rotatably arranged by means of drive elements. - for which purpose the displacement disks are loosely mounted on stub axles arranged in the housing, the longitudinal axes of which are offset from one another, in which loader the two displacement disks are each provided on one side with spirally extending ribs which interlock to form a conveying space and which seal with their free end faces against the opposite displacement disk, - And in order to maintain the sealing effect, a pressure chamber is provided which communicates with the outlet of the charger and via which an axially displaceable annular disc can be acted upon, which is in operative connection with an likewise axially displaceable displacement disc.
  • 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 necessary, 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-501 838. It is the ge in Figs. 8 and 9 showed a 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 A further 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 make a spiral charger of the type mentioned switchable, 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 for rotating both 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 disk 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)
EP89112618A 1988-07-20 1989-07-11 Compresseur rotatif à spirales pour fluides compressibles Expired - Lifetime EP0351690B1 (fr)

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 true EP0351690A1 (fr) 1990-01-24
EP0351690B1 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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0747597A3 (fr) * 1995-06-07 1999-01-20 Copeland Corporation Machine à spirales avec modulation de la capacité

Families Citing this family (12)

* Cited by examiner, † Cited by third party
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
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
JP7042364B2 (ja) 2018-05-04 2022-03-25 エア・スクエアード・インコーポレイテッド 固定スクロール及び旋回スクロールのコンプレッサー、エキスパンダー、又は真空ポンプの液体冷却
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

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1031667A (en) * 1962-04-05 1966-06-02 Cessna Aircraft Co Hydraulic motor system with delayed pressure loading
CH501838A (de) * 1968-07-22 1971-01-15 Leybold Heraeus Verwaltung Verdrängerpumpe
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2475247A (en) * 1944-05-22 1949-07-05 Mikulasek John Planetary piston fluid displacement mechanism
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

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1031667A (en) * 1962-04-05 1966-06-02 Cessna Aircraft Co Hydraulic motor system with delayed pressure loading
CH501838A (de) * 1968-07-22 1971-01-15 Leybold Heraeus Verwaltung Verdrängerpumpe
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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0747597A3 (fr) * 1995-06-07 1999-01-20 Copeland Corporation Machine à spirales avec modulation de la capacité
USRE40400E1 (en) 1995-06-07 2008-06-24 Emerson Climate Technologies, Inc. Capacity modulated scroll machine
USRE40554E1 (en) 1995-06-07 2008-10-28 Emerson Climate Technologies, Inc. Capacity modulated scroll machine having one or more pin members movably disposed for restricting the radius of the orbiting scroll member

Also Published As

Publication number Publication date
EP0351690B1 (fr) 1991-09-25
CH675896A5 (fr) 1990-11-15
DE58900320D1 (de) 1991-10-31
JP2740274B2 (ja) 1998-04-15
JPH0267487A (ja) 1990-03-07
US4990072A (en) 1991-02-05

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