WO2014006364A1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
WO2014006364A1
WO2014006364A1 PCT/GB2013/051517 GB2013051517W WO2014006364A1 WO 2014006364 A1 WO2014006364 A1 WO 2014006364A1 GB 2013051517 W GB2013051517 W GB 2013051517W WO 2014006364 A1 WO2014006364 A1 WO 2014006364A1
Authority
WO
WIPO (PCT)
Prior art keywords
scroll
pumping
circular
scroll wall
wall
Prior art date
Application number
PCT/GB2013/051517
Other languages
English (en)
Inventor
Ian David Stones
Alan Ernest Kinnaird Holbrook
Original Assignee
Edwards Limited
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 Edwards Limited filed Critical Edwards Limited
Priority to US14/412,905 priority Critical patent/US20150167672A1/en
Priority to JP2015519323A priority patent/JP2015522119A/ja
Publication of WO2014006364A1 publication Critical patent/WO2014006364A1/fr

Links

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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • 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
    • F04C18/0215—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 only one member is 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
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • 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
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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
    • F04C18/04—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 of internal-axis type
    • F04C18/045—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 of internal-axis type having a C-shaped piston
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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

Definitions

  • the present invention relates to a scroll compressor.
  • a prior art scroll compressor, or pump, 100 is shown in Figure 4.
  • the pump 100 comprises a pump housing 102 and a drive shaft 104 having an eccentric shaft portion 106.
  • the shaft 104 is driven by a motor 108 and the eccentric shaft portion is connected to an orbiting scroll 110 so that during use rotation of the shaft imparts an orbiting motion to the orbiting scroll relative to a fixed scroll 112 for pumping fluid along a fluid flow path between a pump inlet 114 and pump outlet 116 of the compressor.
  • the fixed scroll 112 comprises a scroll wall 118 which extends perpendicularly to a generally circular base plate 120.
  • the orbiting scroll 110 comprises a scroll wall 124 which extends perpendicularly to a generally circular base plate 126.
  • the orbiting scroll wall 124 co-operates, or meshes, with the fixed scroll wall 118 during orbiting movement of the orbiting scroll. Relative orbital movement of the scrolls causes a volume of gas to be trapped between the scrolls and pumped from the inlet to the outlet.
  • Figure 5 shows the fixed scroll wall 118 and the orbiting scroll wall 124.
  • the fixed scroll wall has inner 128 and outer 130 scroll wall surfaces which co-operate with respective outer 132 and inner 134 scroll wall surfaces of the orbiting scroll wall.
  • This arrangement provides two pairs 128, 132; 130, 134 of co-operating scroll wall surfaces which, on relative orbiting motion of the scrolls, pump fluid from the inlet 136, 137 to the outlet 138 of the arrangement.
  • the scroll walls 118, 124 have a respective plurality of wraps I, II, III, IV, V between the inlet and the outlet.
  • the co-operating scroll wall surfaces 128, 132; 130, 134 are involute from the inlet to the outlet.
  • twin start arrangement having two inlets 136, 137 which in this example are located at the same circumferential angle but at different radii.
  • Two parallel pumping channels extend from the inlets and converge to a single pumping channel after approximately 360 degrees.
  • a twin start arrangement is generally provided for increasing capacity.
  • FIG. 6 shows a more detailed view of the fixed scroll 112.
  • the fixed scroll comprises an annular flange 140 having a plurality of through holes 142 for fixing the fixed scroll to the remainder of the pump housing (not shown).
  • An annular recess 144 receives an o-ring (not shown) for sealing between the fixed scroll and the pump housing.
  • the annular recess is located between the flange 140 and an annular raised portion 146.
  • the outer wrap V of the fixed scroll has radially inner co-operating surface 128 which is an involute or spiral.
  • the outer wrap V of the orbiting scroll wall fits between wraps IV and V of the fixed scroll wall. Therefore, the outer wrap V of the fixed scroll does not have an outer co-operating scroll wall surface.
  • the present invention provides a scroll compressor comprising a scroll pumping arrangement comprising two scrolls each having a scroll wall with inner and outer scroll wall surfaces which co-operate with respective outer and inner scroll wall surfaces of the other scroll wall providing two pairs of co-operating surfaces which, on relative orbiting motion of the scrolls, pump fluid from an inlet to an outlet of the arrangement, the scroll walls having a respective plurality of wraps between the inlet and the outlet and wherein the co-operating scroll wall surfaces of one of said pairs of at least one wrap are generally circular.
  • the present invention also provides a scroll compressor comprising a scroll pumping arrangement comprising two scrolls each having a scroll wall with inner and outer scroll wall surfaces which co-operate with respective outer and inner scroll wall surfaces of the other scroll wall providing two pairs of co-operating surfaces which, on relative orbiting motion of the scrolls, pump fluid from an inlet to an outlet of the arrangement, the scroll walls having a respective plurality of wraps between the inlet and the outlet and wherein the co-operating scroll wall surfaces of one of said pairs of at least one wrap have a rate of change of radius with respect to the angle which is less than said rate of change of the other wraps so that the compression ratio of said one of said pairs is less than for the other wraps.
  • Figure 1 shows schematically a scroll pump
  • Figure 2 shows a first scroll pumping arrangement for the pump shown in Figure i ;
  • Figure 3 shows a second scroll pumping arrangement for the pump shown in Figure 1;
  • Figure 4 shows a prior art scroll pump
  • Figure 5 shows a prior art scroll pumping arrangement of the pump shown in
  • Figure 6 shows a fixed scroll of a prior art pump in more detail.
  • a scroll compressor, or pump, 10 is shown in Figure 1.
  • the pump 10 comprises a pump housing 12 and a drive shaft 14 having an eccentric shaft portion 16.
  • the shaft 14 is driven by a motor 18 and the eccentric shaft portion is connected to an orbiting scroll 20 so that during use rotation of the shaft imparts an orbiting motion to the orbiting scroll relative to a fixed scroll 22 for pumping fluid along a fluid flow path between a pump inlet 24 and pump outlet 26 of the compressor.
  • the fixed scroll 22 comprises a scroll wall 28 which extends perpendicularly to a generally circular base plate 30.
  • the orbiting scroll 20 comprises a scroll wall 34 which extends perpendicularly to a generally circular base plate 36.
  • the orbiting scroll wall 34 co-operates, or meshes, with the fixed scroll wall 28 during orbiting movement of the orbiting scroll. Relative orbital movement of the scrolls causes a volume of gas to be trapped between the scrolls and pumped from the inlet to the outlet.
  • the fixed scroll wall 28 has inner 38 and outer 40 scroll wall surfaces which co-operate with respective outer 42 and inner 44 scroll wall surfaces of the orbiting scroll wall 34 providing two pairs of co-operating surfaces 38, 42; 40, 44.
  • scroll walls On relative orbiting motion of the scrolls 20, 22, fluid is pumped from an inlet 46, 48 to an outlet 50 of the arrangement.
  • the scroll walls have a respective plurality of wraps I, II, III, IV, V between the inlet and the outlet.
  • the co-operating scroll wall surfaces 38, 42; 40, 44 of one of the pairs of at least one wrap are circular.
  • the co-operating scroll wall surfaces of a scroll pump are involute, or spiral. Since the volume of fluid trapped by each pair of co-operating surfaces reduces as the volume approaches the outlet 26 the pump compresses the fluid. As indicated above with reference to the prior art, many attempts have been made to increase pumping capacity, or the amount of fluid that can be pumped. These attempts have produced increased capacity but suffer from disadvantages such as reduced compression or increased back leakage. In the present invention, one pair of scroll wall surfaces is not involute but instead is substantially circular.
  • dr/d0 for at least one of the pairs of scroll surfaces 38, 42; 40, 44 for at least one wrap I, II, II, IV, V is reduced such that the spiral tends towards a circular path and departs from a geometrical spiral or involute as defined above. That is, if dr/d0 equals 'a' for a spiral and 0 for a circle, then for embodiments of the invention dr/d0 equals a value between 'a' and 0, preferably approaching 0.
  • the scroll wall surfaces are circular, although benefits of the invention can be achieved by decreasing dr/d0 thereby increasing the trapped volume between the scroll wall surfaces. Therefore, decreasing dr/d0 increases pumping capacity and decreases compression.
  • the circular or generally circular scroll wall surfaces may be located at any one of the wraps I, II, III, IV, V, or may be located at more than one wrap or at all of the wraps, the latter of which is shown in the example described in more detail below with reference to Figure 3.
  • the fixed scroll wall 28 of the outer wrap V has only one co-operating surface 40, the other surface 41 being outside the pumped volume.
  • the co-operating surface 40 is circular.
  • the orbiting scroll wall 34 of the outer wrap V has two co-operating surfaces 43, 45 both of which are circular.
  • the outer surface 43 co-operates with the inner surface 40 of the fixed scroll wall, whilst the inner surface 45 co-operates with the outer surface 47 of wrap IV of the fixed scroll wall.
  • the other radially inward wall surfaces of the pump in this example are involute.
  • the transition between circular and involute surfaces is formed by the fixed scroll wall of wrap 4.
  • This scroll wall increases in radial thickness between a first portion 49 and a second portion 51 thereby defining an outer surface 47 which is circular and an inner surface 53 which is involute.
  • the fixed scroll casing 140, 144, 146 148 is generally circular so that the fixed scroll has a small overall volume and foot-print.
  • the inner scroll wall surface 128 of the fixed scroll wall 118 is spiral. Therefore, referring to prior art Figure 5, a region between circle 152 and the outer wrap V of the fixed scroll is lost and not usefully available for pumping fluid. It is an advantageous feature of the present embodiment in Figure 2 that the lost pumping region is brought within the pumping volume of the scrolls. In this regard, instead of having a transition between circular and spiral which is outside a pumping volume, the transition is brought within the pumping volume. Accordingly, as shown, the inner scroll surface 40 of the fixed scroll wall 28 is circular and the transition between the circular and spiral surfaces occurs at wrap IV of the fixed scroll. Therefore, the pumping capacity of the pump is increased without an increase in the overall volume or foot-print of the pump.
  • wraps I to III are involute, wrap V is circular and wrap IV is transitional between circular and spiral.
  • the fixed scroll wall of wrap IV has an outer scroll wall surface 47 which is circular and an inner scroll wall surface 53 which is spiral.
  • the transition necessitates a relatively thick scroll wall and therefore it is advantageous that the transition takes place on the stationary fixed scroll, since a thicker orbiting scroll wall would increase the weight of the moving components of the pump.
  • the transition may take place on the orbiting scroll, and in this case the orbiting scroll may be hollow to reduce the amount of mass which must be moved during orbiting motion.
  • the outer wrap V of the orbiting scroll may have an outer scroll wall surface which is circular and an inner scroll wall surface which is spiral. In this arrangement, only the co-operating surfaces at the outer wrap of the scroll walls are circular. In other words, only an outer most pumping channel is circular.
  • transition between circular and spiral pumping surfaces may take place on any of the wraps of the orbiting scroll or any of the wraps of the fixed scroll (except the outer wrap of the fixed scroll).
  • the inlet 24 to the scroll pumping arrangement shown in Figure 2 is sub-divided into inlets 46, 48 to respective pumping channels 50, 52.
  • a two-start or multi-start arrangement is often used to increase pumping capacity.
  • the example shown comprises two inlets 46, 48 on different radii, although in other examples, the inlets may be provided on the same radius at different circumferential positions.
  • the present invention encompasses all such examples.
  • the pumping channels 50, 52 converge at 54 and the convergence is a source of some pumping inefficiency as the tip seals are discontinuous thereby reducing the capacity of the pump.
  • the increased pumping capacity produced by the circular pumping channel 50 at least partially and preferably fully compensates for the back-leakage at the convergence 54.
  • pumping channel 50 has two pairs of co-operating surfaces formed on both sides of the outer wrap V of the orbiting scroll wall 34. Accordingly, the embodiment provides a multi-start scroll pumping arrangement which does not suffer from reduced efficiency.
  • the fixed scroll wall may define one pumping channel between successive wraps (as in a single start arrangement) or more than one pumping channel between successive wraps of the scroll wall which may converge.
  • a multi-start or single start scroll arrangement comprises one or more circular pumping channels and one or more involute pumping channels and the circular pumping channels are deeper than the involute pumping channels.
  • the transition from deep to shallow channels in prior art pumps can often be a cause of inefficiency because the tip seals are not continuous.
  • the circular nature of the deeper pumping channels compensates for the back-leakage caused at the transition.
  • a flow intersection between the circular pumping channels and the involute pumping channels is in flow communication with a blow-off valve for releasing over pressure from the scroll arrangement.
  • the intersection is a suitable location for the blow-off valve as it is located at the transition between a high capacity region and a low capacity region and when running at high inlet pressures substantial over-pressure may occur.
  • the fixed scroll 22 comprises a scroll wall 60 having four discrete generally circular sections.
  • the orbiting scroll 20 comprises a scroll wall 62 having four discrete generally circular sections.
  • the orbiting scroll wall 62 co-operates, or meshes, with the fixed scroll wall 60 during orbiting movement of the orbiting scroll. Relative orbital movement of the scrolls causes a volume of gas to be trapped between the scrolls and pumped from the inlet 64 to the outlet 66.
  • the fixed scroll wall and the orbiting scroll wall each have four wraps I, II, II, IV which in this example are formed by four circular wall sections.
  • the fixed scroll wall sections of successive wraps form therebetween four circular pumping channels 68, 70, 72, 74.
  • the fixed scroll wall sections of wraps III and IV form pumping channel 68.
  • the four sections of the orbiting scroll wall are located within respective pumping channels.
  • the fixed scroll wall sections of wraps III and IV form outer 76 and inner 78 scroll wall surfaces respectively.
  • the orbiting scroll wall section of wrap IV forms inner 80 and outer 82 scroll wall surfaces which co-operate with respective outer 76 and inner 78 of the fixed scroll wall surfaces forming two pairs of co-operating surfaces 76, 80; 78, 82 in pumping channel 68.
  • fluid in the outer pumping channel 68 is trapped between both pairs of co-operating surfaces and pumped from a channel inlet 84 to a channel outlet 86.
  • Each pumping channel extends through less than 360° (although not substantially less than 360°, e.g. about 350°) so that the pumping channel forms an incomplete circle.
  • the ends of each pumping channel are closed by one or more wall closures 88, 90 thereby separating the inlet from the outlet in a pumping channel.
  • the closures are arcuate so that an end of an orbiting scroll wall section sweeps across its face during orbiting motion. This arrangement allows fluid to be trapped efficiently by the orbiting scroll wall.
  • each channel is connected by a duct (shown by arrows 92) to an inlet 84 of the next inward pumping channel. Trapped fluid in channel 68 is forced along a duct 92 entering channel 70 and so on until fluid is forced through the outlet of the most inward channel 74 to the outlet 66 of the pumping arrangement. As fluid is pumped from one channel to the next it becomes compressed because the trapped volume becomes progressively smaller. Accordingly, compression occurs even though all the pumping channels, and co-operating surfaces are circular.
  • Circular wall profiles are easier to design, manufacture and inspect. The simple profile allows better tolerances to be achieved. Having all the wraps as circular avoids over compression between any of the stages, which maximises pumping efficiency.
  • an outer pumping channel is circular and the remaining pumping channels are spiral. This arrangement reduces dead space in the pump and thereby increases capacity.
  • a circular pumping channel achieves increased capacity without compression.
  • all the pumping channels are circular.
  • the invention also encompasses any arrangement between these two examples, such as where one, two or three wraps or pumping channels are circular. Therefore, the invention covers arrangements in which only one pair of co-operating scroll wall surfaces are circular or at least generally circular, and in which all of the co-operating surfaces are circular and all possibilities in between.
  • one pumping channel at a first start may be circular, a plurality of pumping channels at more than one start may be circular or all of the pumping channels at all of the starts may be circular.

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)

Abstract

La présente invention concerne un compresseur à spirales (10) comprenant un agencement de pompage à spirales pourvu de deux spirales (20, 22), chacune présentant une paroi (28, 34) dotée de surfaces interne et externe qui coopèrent avec les surfaces respectives externe et interne de l'autre paroi de spirale formant deux paires de surfaces coopérantes qui, lors du mouvement relatif orbital des spirales, pompent le fluide d'un orifice d'admission à un orifice d'évacuation de l'agencement, les parois des spirales présentant une pluralité respective d'enroulements I, II, III, IV, V entre l'orifice d'admission (24) et l'orifice d'évacuation (26), les surfaces coopérantes des parois des spirales de l'une des paires d'au moins un enroulement étant généralement circulaires.
PCT/GB2013/051517 2012-07-06 2013-06-10 Compresseur à spirales WO2014006364A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US14/412,905 US20150167672A1 (en) 2012-07-06 2013-06-10 Scroll compressor
JP2015519323A JP2015522119A (ja) 2012-07-06 2013-06-10 スクロールコンプレッサ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1212026.7 2012-07-06
GB1212026.7A GB2503728A (en) 2012-07-06 2012-07-06 Scroll compressor with circular wrap

Publications (1)

Publication Number Publication Date
WO2014006364A1 true WO2014006364A1 (fr) 2014-01-09

Family

ID=46766236

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2013/051517 WO2014006364A1 (fr) 2012-07-06 2013-06-10 Compresseur à spirales

Country Status (4)

Country Link
US (1) US20150167672A1 (fr)
JP (1) JP2015522119A (fr)
GB (1) GB2503728A (fr)
WO (1) WO2014006364A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112567135A (zh) * 2018-08-02 2021-03-26 蒂艾克思股份有限公司 液态制冷剂泵
DE102020133438A1 (de) * 2020-12-14 2022-06-15 Bitzer Kühlmaschinenbau Gmbh Scrollmaschine, insbesondere Scrollkompressor oder -expander und Kälteanlage
CN116624388B (zh) * 2023-07-19 2023-10-24 珠海凌达压缩机有限公司 一种涡旋盘组件、压缩机和空调器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4389171A (en) * 1981-01-15 1983-06-21 The Trane Company Gas compressor of the scroll type having reduced starting torque
WO1999015763A1 (fr) * 1997-09-25 1999-04-01 Scroll Technologies Element spirale a diametre minimum generalise
US5938417A (en) * 1995-12-13 1999-08-17 Hitachi, Ltd. Scroll type fluid machine having wraps formed of circular arcs
US20060228244A1 (en) * 2003-08-19 2006-10-12 Goodwin David J Scroll compressor multipile isolated intel ports

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US940817A (en) * 1908-11-16 1909-11-23 William T Mclean Pump.
JPS5979090A (ja) * 1982-10-27 1984-05-08 Mitsubishi Electric Corp スクロ−ル圧縮機
JP2919550B2 (ja) * 1990-04-19 1999-07-12 三洋電機株式会社 スクロール圧縮機
GB9408653D0 (en) * 1994-04-29 1994-06-22 Boc Group Plc Scroll apparatus
US5836752A (en) * 1996-10-18 1998-11-17 Sanden International (U.S.A.), Inc. Scroll-type compressor with spirals of varying pitch
US6309196B1 (en) * 2000-06-01 2001-10-30 Westinghouse Air Brake Technologies Corporation Oiless rotary scroll air compressor antirotation lubrication mechanism
US6413058B1 (en) * 2000-11-21 2002-07-02 Scroll Technologies Variable capacity modulation for scroll compressor
JP2002266777A (ja) * 2001-03-07 2002-09-18 Anest Iwata Corp 多段式流体圧縮部を備えたスクロール流体機械
GB0912162D0 (en) * 2009-07-14 2009-08-26 Edwards Ltd Scroll compressor

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4389171A (en) * 1981-01-15 1983-06-21 The Trane Company Gas compressor of the scroll type having reduced starting torque
US5938417A (en) * 1995-12-13 1999-08-17 Hitachi, Ltd. Scroll type fluid machine having wraps formed of circular arcs
WO1999015763A1 (fr) * 1997-09-25 1999-04-01 Scroll Technologies Element spirale a diametre minimum generalise
US20060228244A1 (en) * 2003-08-19 2006-10-12 Goodwin David J Scroll compressor multipile isolated intel ports

Also Published As

Publication number Publication date
GB201212026D0 (en) 2012-08-22
JP2015522119A (ja) 2015-08-03
GB2503728A (en) 2014-01-08
US20150167672A1 (en) 2015-06-18

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