US3802809A - Completely dry and fluid-tight vacuum pumps - Google Patents

Completely dry and fluid-tight vacuum pumps Download PDF

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US3802809A
US3802809A US00257247A US25724772A US3802809A US 3802809 A US3802809 A US 3802809A US 00257247 A US00257247 A US 00257247A US 25724772 A US25724772 A US 25724772A US 3802809 A US3802809 A US 3802809A
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fixed
disc
spiral
mobile
vacuum pump
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P Vulliez
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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump

Definitions

  • ABSTRACT A completely dry and fluid-tight vacuum pump havin a cycle of circular translation movement and com COMPLETELY DRY AND FLUID-TIGHT VACUUM PUMPS 21?. mm m 0 0.
  • a fixed body having a fixed disc provided on at least one of its sides with a projection in the form of a spiral, a mobile disc mounted opposite said fixed disc and also provided with at least one projection in the form of a spiral intercalated with the spiral of said fixed disc and having the same angular amplitude, a mechanism by which said mobile disc is coupled to and supported by said body, said mechanism comprising at least three crank handles having the same degree of eccentricity and coupled to each other in a synchronized manner in order to produce a movement of circular translation of said mobile disc with respect to the body during the operation of said for driving said mobile disc and for causi out said movement, the spirals of said fixed and mobile discs being spaced apart by a small constant clearance irrespective of the position of said mobile disc, and fluid-tight bellows means, the extremities of which are respectively fixed to said mobile disc and to said body, said pump being further characterized in that said mobile disc is directly coupled at its peri the three crank-handles
  • the active pumping parts comprise friction zones which are lubricated.
  • the present invention relates to vacuum pumps of the type comprising a fixed body having an inlet and an outlet for a working fluid, a passage for the said working fluid which extends between the said inlet and the said oulet, and which is arranged in the interior of the said body, mobile means for effecting a displacement of the working fluid from the said inlet to the said oulet, a mechanism by which the said mobile means are coupled to the said body and are supported by it, the said mechanism comprising at least three crank-handles of equal eccentricity, coupled in a synchronized manner to each other, so as to control a precise circular movement of translation of the said mobile means with respect to the said body during the operation of the pump, means for driving the said mobile means and for causing them to carry out the said movement, the said passage having walls which are shaped so as to follow the configuration of the envelope of the space swept by the said mobile means during their movement, the said mobile means and the walls closest to the said passage being separated by a small constant clearance, irrespective of the position of the said mobile means, and fluid-t
  • the Applicant attributes this disadvantage to the fact that the movement imparted by the crank-handles to the mobile disc passes through the intermediary of a central member, which may cause a whipping action, the amplitude of which may be small at the centre but increases towards the periphery of the disc, thus involving risk of accidental contacts.
  • the present invention has for its object improvements in vacuum pumps which are completely dry and fluid-tight and which have a circular translation cycle, making it possible to obtain a simple and robust construction and also a very great precision of operation and excellent performances, and this without any risk of pollution or leakage or excessive heating, or seizure by incorrect contact, and under good conditions for the suction and delivery.
  • a vacuum pump is characterized in that the crank-handles which determine the circular translation movement and which are arranged at the periphery, directly drive the mobile disc which occupies a central position circumscribed by the said crank-handles, while the fixed disc is coupled to the fixed body by a fixed central barrel surrounded by the bellows, one extremity of which is directly or indirectly connected to the mobile disc while its other extremity is coupled to the fixed body.
  • this result is obtained by the provision of a fixed body preferably made in one single piece and having its central portion surrounded by the bellows, while the peripheral portion comprises three slots arranged for the strictly accurate positioning of the shafts.
  • This arrangement gives great rigidity to the assembly, preventing bending deformations due to the effect of pressure in the central delivery zone of the fixed spiral, and permitting a high precision of the circular translation cycle generated by the three crankshaft's which thus work without any overhang, and therefore without bending deformation.
  • the fact of providing a fixed central barrel surrounded by the bellows in order to support the fixed spiral facilitates the suction and delivery conditions of the fluid to be pumped. More particularly, the suction maybe effected in a simple manner in the annular space included between the fixed central barrel and the bellows which surrounds it, while a. delivery conduit with its valve may readily be placed along the axis of the fixed central barrel. It will also be noted that a vertical position is favourable to the blowing-out and the expulsion of any liquid which may originate from condensable vapours in the interior of the spirals.
  • the body, the active pumping members, the mechanical transmission and movement members are preferably chosen from materials which have the same coefficient of expansion and the same thermal conductivity. Also, fromthe time of starting-up, means for the circulation of a cooling fluid come into action in such manner that the heat produced by the pumping effect and the mechanical movement is uniformly distributed between the body, the active pumping members and the movement transmission members. Under these conditions, the working clearance of the pump remains constant both during operation and at each setting to work, even if the starting operations are carried out at different ambient temperatures.
  • the mobile disc is provided in two parts, of which the spiral projections are placed facing each other in a spaced-apart manner, and between which is mounted the fixed disc having spiral projections on each side intended to cooperate respectively with the spiral projections of the two parts of the mobile disc so as thereby to form two active pumping members.
  • the two spirals along which the fluid to be pumped first passes are spirals without a central bulb in which the fluid is subjected to a centrifugal effect which improves at low pressures the vacuum production of the working assembly of the pump.
  • These spirals are practically not subjected to any heating, as their compression ratio is only considerable at low pressures.
  • the type of pump with a single pair of spirals is capable, when delivering directly at an atmospheric pressure of 760 torr, of producing in the case of air a limiting vacuum in the close proximity of one onehundredth torr, measured on the McLeod gauge.
  • the limiting vacuum reached by the type of pump having two pairs of spirals is located at a value better than oneonethousandth torr.
  • a dry pump of conventional type for example with a deformable diaphragm or equivalent device, and a pair of spirals with or without bulb.
  • the deformable diaphragm pump delivers directly at atmospheric pressure and sucks at the central delivery of the spirals, the peripheral suction of which is coupled to the chamber in which the vacuum is to be created.
  • the work of the second active pumping member constituted by the pair of spirals sucking directly from the chamber makes it possible to improve substantially the limiting value of the vacuum in this chamber.
  • thermo-dynamic pumping effect of the pair of spirals becomes negligible. It is thus easily possible to preserve the strict dimensions of the assembly by avoiding any differential expansion which adversely affects the operation.
  • a single incorporated fan, directly driven by the control of the pump permits the necessary cooling to be effected and provides stabilization of the temperatures of the mechanical parts and of the internal portion of the body.
  • FIG. 1 is a view in vertical cross-section, taken along the line II of FIG. 2, of a vacuum pump with a single pair of spirals;
  • FIG. 2 is a view of the same pump in horizontal crosssection taken along the line IIII of FIG. 1, the spirals
  • FIG. 4 is a view of an alternative form of vacuum pump having two pairs of spirals, shown in vertical cross-section taken along the line IVIV of FIG. 5, in a different angular position;
  • FIG. 5 is a view in horizontal cross-section, taken along the line VV of FIG. 4;
  • FIG. 6 is a view in cross-section taken along the line VIVI of FIG. 7 of another alternative form of vacuum pump in accordance with the invention, with one pair of spirals and a diaphragm pump;
  • FIG. 7 is a view of this further alternative form in cross-section, taken along the line VII-VII of FIG. 6, the spirals being shown in the instantaneous position corresponding to the end of the suction phase and to half delivery.
  • FIGS. 1, 2, 2a and 3 there is seen a vacuum pump which is completely dry and fluid-tight and having a circular cycle of translation.
  • This pump comprises a fixed body 10 having a fixed disc 13' provided on one of its sides with a projection in the form of a spiral 13.
  • a mobile disc 23 is opposite-to the fixed disc 13, and is also provided with a projection in the form of a spiral 23, intercalated with the projection 13 of the fixed disc 13' and having the same angular amplitude.
  • a mechanism is provided for coupling the mobile disc 23 to the body 10 and serves to supportthe disc. This mechanism comprises at least three crank-handles 20 having equal eccentricity E and coupled to each other in a synchronized manner so as to effect a circular movement of translation of the mobile disc 23' with respect to the fixed body 10 during the operation of the pump.
  • Driving means 19 which are described later in more detail, are provided so as to drive the mobile disc 23' and to cause it to carry out the said movement.
  • the spirals l3 and 23 are separated by a small constant clearance which is independent of the position of the mobile disc 23'.
  • a fluid-tight bellows 11 has its extremities fixed respectively to the mobile disc 23' at 28, and to a base 10" of the fixed body 10 at 30.
  • the mobile disc 23 is directly coupled at its periphery to the-three crank-handles 20, while a fixed central barrel 10' couples the fixed disc l3' to the fixed base 10" of the fixed body 10, and is surrounded by the bellows 11.
  • the metallic bellows ll employed in order to obtain complete fluid-tightness of the system is positively protected against any torsion force, operational or accidental, due to the kinematics of the driving system with three synchronized crank-handles 20.
  • the pump is of the type having a single pair of spirals 13 and 23. It is provided with a shaft A and its fixed body 10 is made of one piece and is composed of the central portion or barrel 10', the base 10" and a peripheral portion 10'. This latter surrounds the bellows 11 which in turn surrounds the barrel 10.
  • the peripheral portion 10" is provided with three openings 12 located at with respect to each other.
  • the three portions of the body located in the vertical axis of the openings 12 are machined so as to receive guiding bearings 16 and 17 and an axial thrustbearing 18, which serve to ensure the accurate positioning of each of the three shafts 19, of which the crank-handles 20 drive a transfer member 21 with an eccentricity having a value E, through the intermediary of bearings 22.
  • the mobile disc 23' which carries the spiral 23 is made fixed to the transfer member 21 by a series of bolts 24.
  • the mobile disc 23' comprises on its upper face reinforcing ribs 25 which are intended to prevent deformation due to the effects of pressure.
  • balancing weights 26 On the shafts 19 are keyed balancing weights 26, and on the crank-handles 20 are provided other balancing weights 27. These various weights are calculated and positioned in such manner as to obtain a perfect static and dynamic balancing of the members having a circular translation movement. 1
  • the bellows 11 is welded to a bell 28, in which the clamping by bolts 24 on the transfer member 21 compresses a static joint 29 which thus ensures fluid-tightness between thisbell 28 and the mobile spiral 23.
  • the bellows 11 is welded to an annular member 30 which is in turn clamped on the body by means of the countersunk-head bolts'3l, with the interposition of a static-fluid-tight joint 32.
  • the suction pipe of the pump which is rigidly fixed to the body and at 35 is seen the delivery conduit which comprises a valve 34 and forms part of a member 36.
  • the delivery conduit which comprises a valve 34 and forms part of a member 36.
  • This latter passes through the centralbarrel 10' of the body 10 and is clamped on this barrel with the interposition of fluidtig'htness joints 37 and 38, intended to prevent leakages of cooling oil towards the exterior.
  • the conduit 35, the valve 34 and the member 36 are coaxial with the shaft A of the pump.
  • the chamber in which the vacuum is to be created is connected to the suction pipe 33 rigidly fixed to the body 10.
  • the gaseous fluid to be pumped is subjected to the continuous and progressive effect of compression due to the displacement in a-movement of circular translation of the mobile spiral 23 with respect to the fixed spiral 13.
  • the spirals 13 and 23 are shown in a position preceding the end of the suction phase.
  • the two first volumes imprisoned at V1 are subjected to a first compression after a first cycle of circular translation, reducing them to the two volumes V2.
  • these latter volumes are subjected to a second compression and are combined in the same volume V3 which, during the course of the third cycle, is subjected to the efiect of the final compression so as to be completely expelled (apart from the leakages) through the valve 34, the spirals being then located in the instantaneous position of the end of delivery and full suction, as shown in FIG. 20.
  • each spiral l3 and 23 in addition to the advantage of being provided with an external cavity 43, 45 for cooling purposes, permits by its thick shape a reduction of the radial and lateral leakages in the zone at which the compression is highest.
  • the common volume of final compression V3 (FIG. 2) will increase in size as and when the two bulbs between which this volume is defined, are themselves larger, which especially facilitates the choice of an optimum size for the exhaust orifice 34.
  • an oil tank in which is immersed the pump 40 driven by one of the shafts 19.
  • the cavities 43 and 45 of the bulb can be extended into the whole or part of the development of the spirals.
  • the drive of the pump (not shown on the drawings) is effected either directly or indirectly by one of the three vertical shafts 19 which pass out of the hood 39.
  • a second shaft 19 may actuate directly the member 40 intended to pulsate the cooling fluid.
  • this fluid may be air driven by a centrifugal fan into sections of passage suitably formed for that purpose.
  • FIGS. 4 and 5 in which the arrangement is similar to that which has just been described with reference to FIGS. 1 to 3, but in which the pump is of the type having two active pumping members each provided with a pair of spirals.
  • the vacuum pump shown in FIG. 4 is i a machine the construction of which is similar to that of FIG. 1, but which comprises on the one hand a first pair of spirals 46 and 47 without a central bulb (see FIG. 5) and on the other hand a second pair of spirals l3 and 23 with a hollow central bulb towards the exterior, which is similar to the pair of spirals which have been described with reference to FIGS. 1 to 3, and of which the view in cross-section taken along the line a-a of FIG. 4 corresponds to the angular position of FIG. 2.
  • the primary limiting vacuum is improved by causing the fluid to be pumped to pass into the first pair of spirals 46 and 47, which have no central bulb.
  • Suction through the orifice 33 is effected by the internal zones 48 and 49, and the delivery is made by the peripheral zones 50 and 51, which both open directly into the suction zones of the two spirals 13 with bulb and 23 also with bulb, which, as in the case of FIGS. 1 and 2, ensure directly delivery to atmospheric pressure.
  • the two spirals 46 and 47 have a generated volume which is chosen to be very close to that of the spirals l3 and 23.
  • the suction volume at 33 is pulsated from the interior towards the exterior of the spirals 46 and 47 and, as in the case of the spirals l3 and 23, with a constant separation between the enclosed volumes and the suction and delivery zones.
  • the performances of the pump shown in FIGS. 4 and 5 are due to bringing up to speed at low pressures of the molecules of the fluid to be pumped, this bringing up to speed resulting simultaneously from the volumetric effect and the centrifugal effect produced by the movement in circular translation of the mobile spiral 46 with respect to the fixed spiral 47.
  • the two spirals 46 and 47 Due to the act that their efficiency is only effective at low pressures, the two spirals 46 and 47 generate practically no heat and can give good results with a working clearance having a value greater than that of the spirals 13 and 23.
  • This fixed spiral l3 belongs to a single member 13, in the form of a disc, in the lower part of which is machined the second fixed spiral 47 in which there is intercalated the second mobile spiral 46.
  • the two discs 23' and 46' of the mobile spirals 23 and 46 are fixed by the annular member 52 to each other, the member 52 replacing the bell 28 of FIG. 1 and beingpowerfully clamped simultaneously to the transfer member 21 and to the disc 46' of the second mobile spiral 46.
  • FIGS. 6 and 7, in which is shown another alternative form, concerning more particularly, but not exclusively, a miniaturized construction.
  • FIGS. 6 and 7 a completely dry and fluid-tight pumping unit consisting of a diaphragm pump P delivering to atmosphere through the conduit 53 and taking its suction through the conduit 54 and the orifice 35 in the annular space comprised between the interior of the bellows 11 and the central barrel 10' of the body 10.
  • a diaphragm pump P delivering to atmosphere through the conduit 53 and taking its suction through the conduit 54 and the orifice 35 in the annular space comprised between the interior of the bellows 11 and the central barrel 10' of the body 10.
  • Into this annular space opens the delivery orifice 34 of the fixed and mobile spirals l3 and 23, in which the peripheral suction is delimited by the bell 28.
  • This suction is connected to the chamber to be exhausted by the conduit 33 arranged inside the central barrel 10 and the member 14. This latter serves to fix the fixed spiral 13 on the said central barrel 10'.
  • the diaphragm pump P the pumping action of which is obtained by the alternating deformation of an elastic wall subjected to an eccentric action from the driving shaft, is a dry and fluid-tight machine, of which the constructional technique is known per se and will therefore not necessitate any particular description.
  • its best performances are situated at a limiting pressure of the order of a few torrs.
  • the bell 28 is forcibly clamped against the inner face of the disc 23' with the interposition of the static fluidtight joint 29, by the bolts 24 acting on the three ring segments 56.
  • the connecting member 57 welded to the extremity of the bellows 11 is then blocked by the bolts 58 with the interposition of the fluid-tight static joint 29, on the outer face of the disc 23' of the mobile spiral 23.
  • the bellows 11 is welded to an annular member 30 which is in turn clamped on the body by the bolts 31 with the interposition of the static fluid-tight joint 32.
  • the disc 23 which is of small size, comprises three extensions 23' arranged at 120 from each other and machined in order to receive'the bearings 22 in which 1 pivot, the eccentrics 20 which are rigidly fixed to the shafts'l9. These three eccentrics 20 thus drive the assembly of the mobile spiral 23, 23' and 23' in a strictly circular translation movement following an eccentricone-piece construction, constituted by the central barrel 10', the base and its peripheral extension 10''.
  • a second member 10" adjusts itself and becomes fixed on the machined face of the peripheral portion 10" by means of the bolts 59 (see FIG. 7).
  • This second portion of the body 10" comprises three cylindrical housings arranged ar 120 with respect to each other, machined in order to receive the bearings with oblique contacts 16 and 17 which serve simultaneously as a guide and an abutment for the strictly accurate positioning of each of the shafts 19, on which are keyed on the one hand the eccentrics 20 driving the mobile spiral 23, and on the other hand the masses 26 and 27 serving to effect the static and dynamic balancing of the moving system.
  • the drive may be effected as shown in FIGS. 6 and 7 by direct coupling of one of the shafts 19 to an electric motor 55.
  • a second shaft 19 also drives directly the diaphragm pump P.
  • At the end of the third shaft 19 there may be mounted a small built-in fan (not shown) intended to reduce and to stabilize in case of need the temperature of the mechanical portion and of the portions of the body 10" and 10".
  • valves are mounted on the suction and on the delivery of the diaphragm pump and it is possible with the mounting of the spirals l3 and 23, ,to provide an additional valve on the delivery 34.
  • a completely dry and fluid-tight vacuum pump having a circular translation cycle and comprising: a fixed body having a fixed disc provided on at least one of its sides with a projection in the form of a spiral, a mobile disc mounted opposite said fixed disc and also having at least one projection in the form of a spiral intercalated with the spiral of said fixed disc and having the same angularamplitude, a mechanism by which said mobile disc is connected to and supported by said body, said mechanism comprising at least three crankhandles of equal eccentricity coupled in a synchronized manner to each other in order to effect a movement of circular translation of said mobile disc with respect to the body during the operation of said pump, means for driving said mobile disc and causing it to carry out said movement, the spirals of said fixed and mobile discs being spaced apart by a small constant clearance irrespective of the position of said mobile disc, and fluidtight bellows means, the extremities of which are respectively fixed to said mobile disc and to said body; the further characteristic features that said mobile disc is directly coupled at its periphery to the at least
  • a vacuum pump as claimed in claim 1 in which a preliminary vacuum pump is adapted to deliver to atmosphere and has its suction located at the delivery of said pair of spirals, the suction of which is connected to the chamber in which the vacuum is to be created.
  • a vacuum pump as claimed in claim 1 in which said pump has a single active pumping member with a single projection of spiral form on said fixed disc and a single spiral projection on said mobile disc.
  • each of said cooling cavities is formed by hollowed portion of said spiral, open towards the exterior.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US00257247A 1971-06-01 1972-05-26 Completely dry and fluid-tight vacuum pumps Expired - Lifetime US3802809A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR717119699A FR2141402B1 (fr) 1971-06-01 1971-06-01
FR7132376A FR2153129B2 (fr) 1971-06-01 1971-09-08

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US3802809A true US3802809A (en) 1974-04-09

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US00257247A Expired - Lifetime US3802809A (en) 1971-06-01 1972-05-26 Completely dry and fluid-tight vacuum pumps

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US (1) US3802809A (fr)
AT (1) AT316721B (fr)
BE (1) BE783710A (fr)
CA (1) CA968766A (fr)
CH (1) CH553333A (fr)
DE (1) DE2225327C3 (fr)
FR (1) FR2153129B2 (fr)
GB (1) GB1367986A (fr)
IT (1) IT959019B (fr)
NL (1) NL151776B (fr)

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US3989422A (en) * 1975-02-07 1976-11-02 Aginfor Ag Fur Industrielle Forschung Displacement machine for compressible media
DE2801206A1 (de) * 1977-01-24 1978-07-27 Little Inc A Spiralartige einrichtung mit einem festen gekroepften kurbelantriebsmechanismus
US4129405A (en) * 1977-06-17 1978-12-12 Arthur D. Little, Inc. Scroll-type liquid pump with transfer passages in end plate
US4192152A (en) * 1978-04-14 1980-03-11 Arthur D. Little, Inc. Scroll-type fluid displacement apparatus with peripheral drive
WO1982003429A1 (fr) * 1981-04-03 1982-10-14 Little Inc A Compresseur compact a piston rotatif
US4382754A (en) * 1980-11-20 1983-05-10 Ingersoll-Rand Company Scroll-type, positive fluid displacement apparatus with diverse clearances between scroll elements
US4464100A (en) * 1981-06-24 1984-08-07 Hitachi, Ltd. Scroll fluid apparatus handling compressible fluid
US4490099A (en) * 1980-10-03 1984-12-25 Sanden Corporation Scroll type fluid displacement apparatus with thickened center wrap portions
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US4547137A (en) * 1982-09-26 1985-10-15 Sanden Corporation Scroll type fluid compressor with thickened spiral elements
JPS61182401A (ja) * 1985-02-06 1986-08-15 Shin Meiwa Ind Co Ltd スクロ−ル形流体機械
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
US4650405A (en) * 1984-12-26 1987-03-17 Nippon Soken, Inc. Scroll pump with axially spaced pumping chambers in series
US4718836A (en) * 1984-07-23 1988-01-12 Normetex Reciprocating completely sealed fluid-tight vacuum pump
US4781549A (en) * 1985-09-30 1988-11-01 Copeland Corporation Modified wrap scroll-type machine
US5154592A (en) * 1989-10-20 1992-10-13 Tokico Ltd. Scroll type fluid apparatus with rotation restraining mechanism
EP0549952A1 (fr) * 1991-12-20 1993-07-07 Hitachi, Ltd. Machine à volutes pour fluides, élément de volute et procédé de traitement
US5346376A (en) * 1993-08-20 1994-09-13 General Motors Corporation Axial thrust applying structure for the scrolls of a scroll type compressor
US5358391A (en) * 1986-08-22 1994-10-25 Copeland Corporation Hermetic compressor with heat shield
US5366359A (en) * 1993-08-20 1994-11-22 General Motors Corporation Scroll compressor orbital scroll drive and anti-rotation assembly
WO1995027143A1 (fr) * 1994-04-05 1995-10-12 Puritan-Bennett Corporation Compresseur a helices
US5616015A (en) * 1995-06-07 1997-04-01 Varian Associates, Inc. High displacement rate, scroll-type, fluid handling apparatus
DE19603110A1 (de) * 1995-11-06 1997-05-07 Bitzer Kuehlmaschinenbau Gmbh Kompressor
US5649816A (en) * 1986-08-22 1997-07-22 Copeland Corporation Hermetic compressor with heat shield
US5674062A (en) * 1986-08-22 1997-10-07 Copeland Corporation Hermetic compressor with heat shield
US5743719A (en) * 1995-07-21 1998-04-28 Anest Iwata Corporation Oil-free scroll vacuum pump having a gas ballast part
WO1999015764A1 (fr) * 1997-09-22 1999-04-01 Mind Tech Corp. Dispositif de deplacement de fluide du type a volutes, dote d'un deflecteur de flux, de plusieurs joints d'extremite et d'un mecanisme semi-radial flexible
WO1999047813A2 (fr) * 1998-03-18 1999-09-23 Haldex Financial Services Corporation Appareil de deplacement de fluide monte sur rouleau comprenant un mecanisme a manivelle excentrique presentant un axe allonge
US6022202A (en) * 1995-02-24 2000-02-08 S.B.P.V. (Societe Des Brevets P. Vulliez) Spiral vacuum pump having a toothed circular translation movement limiter device
US6158990A (en) * 1997-04-10 2000-12-12 Sanden Corporation Scroll member for a scroll type of fluid machinery and scroll type of fluid machinery produced thereby
US6193487B1 (en) 1998-10-13 2001-02-27 Mind Tech Corporation Scroll-type fluid displacement device for vacuum pump application
FR2809141A1 (fr) * 2000-05-16 2001-11-23 Sanden Corp Compresseur a volutes
US6461129B2 (en) 2001-02-23 2002-10-08 Mat Automotive Inc. Scroll type compressor apparatus with adjustable axial gap
US6511308B2 (en) 1998-09-28 2003-01-28 Air Squared, Inc. Scroll vacuum pump with improved performance
US6758659B2 (en) 2002-04-11 2004-07-06 Shimao Ni Scroll type fluid displacement apparatus with fully compliant floating scrolls
US20040148951A1 (en) * 2003-01-24 2004-08-05 Bristol Compressors, Inc, System and method for stepped capacity modulation in a refrigeration system
US20050063850A1 (en) * 2003-09-18 2005-03-24 Liepert Anthony G. Scroll pump using isolation bellows and synchronization mechanism
WO2005045249A1 (fr) * 2003-10-27 2005-05-19 The Boc Group Plc Pompe a vide du type a spirale
US20050220647A1 (en) * 2004-03-30 2005-10-06 Liepert Anthony G Scroll pump with load bearing synchronization device
US20070172373A1 (en) * 2006-01-26 2007-07-26 Scroll Laboratories, Llc Scroll-type fluid displacement apparatus with fully compliant floating scrolls
US20070189912A1 (en) * 2006-02-14 2007-08-16 Shaffer Robert W Advanced scroll compressor, vacuum pump, and expander
US20070231174A1 (en) * 2006-03-28 2007-10-04 Yuki Ishizuki Scroll fluid machine
US20080124236A1 (en) * 2004-12-08 2008-05-29 Nigel Paul Schofield Scroll-Type Apparatus
JP2008528853A (ja) * 2005-01-21 2008-07-31 ヴェ．ジェ．ベ．（ヴュリーズ ジェスティオン ブルヴェ） 旋回並進サイクル式マルチシャフト真空ポンプ
US20100284846A1 (en) * 2007-11-08 2010-11-11 Enjiu Ke Scroll Type Fluid Machinery
US20110076172A1 (en) * 2009-09-25 2011-03-31 John Calhoun Scroll pump with isolation barrier
US20110176948A1 (en) * 2010-01-16 2011-07-21 Shaffer Robert W Semi-hermetic scroll compressors, vacuum pumps, and expanders
US8523544B2 (en) 2010-04-16 2013-09-03 Air Squared, Inc. Three stage scroll vacuum pump
US8764424B2 (en) 2010-05-17 2014-07-01 Tuthill Corporation Screw pump with field refurbishment provisions
US20140301879A1 (en) * 2013-04-05 2014-10-09 Agilent Technologies, Inc. Angular Synchronization of Stationary and Orbiting Plate Scroll Blades in a Scroll Pump Using a Metallic Bellows
US9366255B2 (en) 2013-12-02 2016-06-14 Agilent Technologies, Inc. Scroll vacuum pump having external axial adjustment mechanism
US9404491B2 (en) 2013-03-13 2016-08-02 Agilent Technologies, Inc. Scroll pump having bellows providing angular synchronization and back-up system for bellows
US10221852B2 (en) 2006-02-14 2019-03-05 Air Squared, Inc. Multi stage scroll vacuum pumps and related scroll devices
US10508543B2 (en) 2015-05-07 2019-12-17 Air Squared, Inc. Scroll device having a pressure plate
US10519815B2 (en) 2011-08-09 2019-12-31 Air Squared, Inc. Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle
US10683865B2 (en) 2006-02-14 2020-06-16 Air Squared, Inc. Scroll type device incorporating spinning or co-rotating scrolls
US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
US11047389B2 (en) 2010-04-16 2021-06-29 Air Squared, Inc. Multi-stage scroll vacuum pumps and related scroll devices
US11067080B2 (en) 2018-07-17 2021-07-20 Air Squared, Inc. Low cost scroll compressor or vacuum pump
EP3848586A4 (fr) * 2018-12-06 2021-11-17 Gree Green Refrigeration Technology Center Co. Ltd. of Zhuhai Compresseur
US11319955B2 (en) * 2017-12-14 2022-05-03 Mouvex Positive displacement pump with improved cleaning
EP3978755A4 (fr) * 2019-07-10 2022-08-10 Daikin Industries, Ltd. Compresseur à spirale
US11454241B2 (en) 2018-05-04 2022-09-27 Air Squared, Inc. Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump
US11473572B2 (en) 2019-06-25 2022-10-18 Air Squared, Inc. Aftercooler for cooling compressed working fluid
US11530703B2 (en) 2018-07-18 2022-12-20 Air Squared, Inc. Orbiting scroll device lubrication
US11885328B2 (en) 2021-07-19 2024-01-30 Air Squared, Inc. Scroll device with an integrated cooling loop
US11898557B2 (en) 2020-11-30 2024-02-13 Air Squared, Inc. Liquid cooling of a scroll type compressor with liquid supply through the crankshaft
US11933299B2 (en) 2018-07-17 2024-03-19 Air Squared, Inc. Dual drive co-rotating spinning scroll compressor or expander

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US3924977A (en) * 1973-06-11 1975-12-09 Little Inc A Positive fluid displacement apparatus
DE2831179A1 (de) * 1978-07-15 1980-01-24 Leybold Heraeus Gmbh & Co Kg Verdraengermaschine nach dem spiralprinzip
DE2927690A1 (de) * 1979-07-09 1981-01-29 Leybold Heraeus Gmbh & Co Kg Verdraengermaschine nach dem spiralprinzip
US4715796A (en) * 1985-05-16 1987-12-29 Mitsubishi Denki Kabushiki Kaisha Scroll-type fluid transferring machine with loose drive fit in crank shaft recess
DE3642116A1 (de) * 1986-12-10 1988-06-23 Agintec Ag Federelastische exzenterlagerung fuer verdraengermaschinen
CH672351A5 (fr) * 1986-12-24 1989-11-15 Bbc Brown Boveri & Cie
DE3719950A1 (de) * 1987-06-15 1989-01-05 Agintec Ag Verdraengermaschine
DE3729319C2 (de) * 1987-09-02 1995-11-16 Bock Gmbh & Co Kaeltemaschinen Spiralverdichter
FR2764347B1 (fr) * 1997-06-05 1999-07-30 Alsthom Cge Alcatel Machine du type scroll
FR2764346B1 (fr) * 1997-06-05 1999-07-30 Alsthom Cge Alcatel Machine a deplacement de fluide du type scroll
JP2000145669A (ja) * 1998-11-05 2000-05-26 Toyota Autom Loom Works Ltd スクロール型圧縮機における旋回スクロールの回転バランス機構
US20040086407A1 (en) * 2002-11-04 2004-05-06 Enjiu Ke Scroll type of fluid machinery

Cited By (99)

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US3884599A (en) * 1973-06-11 1975-05-20 Little Inc A Scroll-type positive fluid displacement apparatus
US3989422A (en) * 1975-02-07 1976-11-02 Aginfor Ag Fur Industrielle Forschung Displacement machine for compressible media
US3986799A (en) * 1975-11-03 1976-10-19 Arthur D. Little, Inc. Fluid-cooled, scroll-type, positive fluid displacement apparatus
JPS6112901U (ja) * 1975-11-03 1986-01-25 ア−サ−・デイ・リトル・インコ−ポレ−テツド 容積式流体装置
DE2801206A1 (de) * 1977-01-24 1978-07-27 Little Inc A Spiralartige einrichtung mit einem festen gekroepften kurbelantriebsmechanismus
US4129405A (en) * 1977-06-17 1978-12-12 Arthur D. Little, Inc. Scroll-type liquid pump with transfer passages in end plate
US4192152A (en) * 1978-04-14 1980-03-11 Arthur D. Little, Inc. Scroll-type fluid displacement apparatus with peripheral drive
US4490099A (en) * 1980-10-03 1984-12-25 Sanden Corporation Scroll type fluid displacement apparatus with thickened center wrap portions
US4382754A (en) * 1980-11-20 1983-05-10 Ingersoll-Rand Company Scroll-type, positive fluid displacement apparatus with diverse clearances between scroll elements
US4892469A (en) * 1981-04-03 1990-01-09 Arthur D. Little, Inc. Compact scroll-type fluid compressor with swing-link driving means
WO1982003429A1 (fr) * 1981-04-03 1982-10-14 Little Inc A Compresseur compact a piston rotatif
US4464100A (en) * 1981-06-24 1984-08-07 Hitachi, Ltd. Scroll fluid apparatus handling compressible fluid
US4547137A (en) * 1982-09-26 1985-10-15 Sanden Corporation Scroll type fluid compressor with thickened spiral elements
US4522574A (en) * 1982-10-27 1985-06-11 Hitachi, Ltd. Balancing weight device for scroll-type fluid machine
US4609334A (en) * 1982-12-23 1986-09-02 Copeland Corporation Scroll-type machine with rotation controlling means and specific wrap shape
US4718836A (en) * 1984-07-23 1988-01-12 Normetex Reciprocating completely sealed fluid-tight vacuum pump
US4650405A (en) * 1984-12-26 1987-03-17 Nippon Soken, Inc. Scroll pump with axially spaced pumping chambers in series
JPS61182401A (ja) * 1985-02-06 1986-08-15 Shin Meiwa Ind Co Ltd スクロ−ル形流体機械
JPH0447121B2 (fr) * 1985-02-06 1992-08-03 Shinmeiwa Kogyo Kk
US4781549A (en) * 1985-09-30 1988-11-01 Copeland Corporation Modified wrap scroll-type machine
US5649816A (en) * 1986-08-22 1997-07-22 Copeland Corporation Hermetic compressor with heat shield
US5674062A (en) * 1986-08-22 1997-10-07 Copeland Corporation Hermetic compressor with heat shield
US5358391A (en) * 1986-08-22 1994-10-25 Copeland Corporation Hermetic compressor with heat shield
US5487654A (en) * 1986-08-22 1996-01-30 Copeland Corporation Hermetic compressor with heat shield
US5154592A (en) * 1989-10-20 1992-10-13 Tokico Ltd. Scroll type fluid apparatus with rotation restraining mechanism
EP0549952A1 (fr) * 1991-12-20 1993-07-07 Hitachi, Ltd. Machine à volutes pour fluides, élément de volute et procédé de traitement
US5346376A (en) * 1993-08-20 1994-09-13 General Motors Corporation Axial thrust applying structure for the scrolls of a scroll type compressor
US5366359A (en) * 1993-08-20 1994-11-22 General Motors Corporation Scroll compressor orbital scroll drive and anti-rotation assembly
US5466134A (en) * 1994-04-05 1995-11-14 Puritan Bennett Corporation Scroll compressor having idler cranks and strengthening and heat dissipating ribs
WO1995027143A1 (fr) * 1994-04-05 1995-10-12 Puritan-Bennett Corporation Compresseur a helices
US6022202A (en) * 1995-02-24 2000-02-08 S.B.P.V. (Societe Des Brevets P. Vulliez) Spiral vacuum pump having a toothed circular translation movement limiter device
US5616015A (en) * 1995-06-07 1997-04-01 Varian Associates, Inc. High displacement rate, scroll-type, fluid handling apparatus
US5743719A (en) * 1995-07-21 1998-04-28 Anest Iwata Corporation Oil-free scroll vacuum pump having a gas ballast part
DE19603110A1 (de) * 1995-11-06 1997-05-07 Bitzer Kuehlmaschinenbau Gmbh Kompressor
US6158990A (en) * 1997-04-10 2000-12-12 Sanden Corporation Scroll member for a scroll type of fluid machinery and scroll type of fluid machinery produced thereby
US6071101A (en) * 1997-09-22 2000-06-06 Mind Tech Corp. Scroll-type fluid displacement device having flow diverter, multiple tip seal and semi-radial compliant mechanism
WO1999015764A1 (fr) * 1997-09-22 1999-04-01 Mind Tech Corp. Dispositif de deplacement de fluide du type a volutes, dote d'un deflecteur de flux, de plusieurs joints d'extremite et d'un mecanisme semi-radial flexible
CN1117209C (zh) * 1997-09-22 2003-08-06 迈德技术公司 具有流动转向器、多个尖端密封件和半径向顺应式机构的涡卷式流体排出装置
WO1999047813A3 (fr) * 1998-03-18 1999-11-04 Haldex Financial Services Corp Appareil de deplacement de fluide monte sur rouleau comprenant un mecanisme a manivelle excentrique presentant un axe allonge
GB2340552A (en) * 1998-03-18 2000-02-23 Haldex Financial Services Corp Scroll-type fluid displacement apparatus including an eccentric crank mechanism having an elongated shaft
WO1999047813A2 (fr) * 1998-03-18 1999-09-23 Haldex Financial Services Corporation Appareil de deplacement de fluide monte sur rouleau comprenant un mecanisme a manivelle excentrique presentant un axe allonge
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
GB2340552B (en) * 1998-03-18 2001-12-12 Haldex Financial Services Corp Scroll-type fluid displacement apparatus including an eccentric crank mechanism having an elongated shaft
US6511308B2 (en) 1998-09-28 2003-01-28 Air Squared, Inc. Scroll vacuum pump with improved performance
EP1129294A4 (fr) * 1998-10-13 2004-07-14 Mind Tech Corp Dispositif volumetrique a rampe helico dale pour pompes a vide
EP1129294A1 (fr) * 1998-10-13 2001-09-05 Mind Tech Corp. Dispositif volumetrique a rampe helico dale pour pompes a vide
US6193487B1 (en) 1998-10-13 2001-02-27 Mind Tech Corporation Scroll-type fluid displacement device for vacuum pump application
DE10123398B4 (de) * 2000-05-16 2004-08-26 Sanden Corp., Isesaki Spiralkompressor
US6379134B2 (en) * 2000-05-16 2002-04-30 Sanden Corporation Scroll compressor having paired fixed and moveable scrolls
FR2809141A1 (fr) * 2000-05-16 2001-11-23 Sanden Corp Compresseur a volutes
US6461129B2 (en) 2001-02-23 2002-10-08 Mat Automotive Inc. Scroll type compressor apparatus with adjustable axial gap
US6758659B2 (en) 2002-04-11 2004-07-06 Shimao Ni Scroll type fluid displacement apparatus with fully compliant floating scrolls
US20040148951A1 (en) * 2003-01-24 2004-08-05 Bristol Compressors, Inc, System and method for stepped capacity modulation in a refrigeration system
US20050063850A1 (en) * 2003-09-18 2005-03-24 Liepert Anthony G. Scroll pump using isolation bellows and synchronization mechanism
WO2005045249A1 (fr) * 2003-10-27 2005-05-19 The Boc Group Plc Pompe a vide du type a spirale
US7261528B2 (en) * 2004-03-30 2007-08-28 Varian, Inc. Scroll pump with load bearing synchronization device
US20050220647A1 (en) * 2004-03-30 2005-10-06 Liepert Anthony G Scroll pump with load bearing synchronization device
US20080124236A1 (en) * 2004-12-08 2008-05-29 Nigel Paul Schofield Scroll-Type Apparatus
JP2008528853A (ja) * 2005-01-21 2008-07-31 ヴェ．ジェ．ベ．（ヴュリーズ ジェスティオン ブルヴェ） 旋回並進サイクル式マルチシャフト真空ポンプ
US20070172373A1 (en) * 2006-01-26 2007-07-26 Scroll Laboratories, Llc Scroll-type fluid displacement apparatus with fully compliant floating scrolls
US7467933B2 (en) 2006-01-26 2008-12-23 Scroll Laboratories, Inc. Scroll-type fluid displacement apparatus with fully compliant floating scrolls
US20070189912A1 (en) * 2006-02-14 2007-08-16 Shaffer Robert W Advanced scroll compressor, vacuum pump, and expander
US10683865B2 (en) 2006-02-14 2020-06-16 Air Squared, Inc. Scroll type device incorporating spinning or co-rotating scrolls
US7942655B2 (en) * 2006-02-14 2011-05-17 Air Squared, Inc. Advanced scroll compressor, vacuum pump, and expander
US10221852B2 (en) 2006-02-14 2019-03-05 Air Squared, Inc. Multi stage scroll vacuum pumps and related scroll devices
US20070231174A1 (en) * 2006-03-28 2007-10-04 Yuki Ishizuki Scroll fluid machine
US7377759B2 (en) * 2006-03-28 2008-05-27 Anest Iwata Corporation Scroll fluid machine with a self-rotation-preventing device having ears for an orbiting scroll
US20100284846A1 (en) * 2007-11-08 2010-11-11 Enjiu Ke Scroll Type Fluid Machinery
US8764421B2 (en) * 2007-11-08 2014-07-01 Shanghai Universoon AutoParts Co. Scroll type fluid machinery
US8622724B2 (en) * 2009-09-25 2014-01-07 Agilent Technologies, Inc. Scroll pump with isolation barrier
US20110076172A1 (en) * 2009-09-25 2011-03-31 John Calhoun Scroll pump with isolation barrier
US8668479B2 (en) * 2010-01-16 2014-03-11 Air Squad, Inc. Semi-hermetic scroll compressors, vacuum pumps, and expanders
US20110176948A1 (en) * 2010-01-16 2011-07-21 Shaffer Robert W Semi-hermetic scroll compressors, vacuum pumps, and expanders
US8523544B2 (en) 2010-04-16 2013-09-03 Air Squared, Inc. Three stage scroll vacuum pump
US11047389B2 (en) 2010-04-16 2021-06-29 Air Squared, Inc. Multi-stage scroll vacuum pumps and related scroll devices
US9028230B2 (en) 2010-04-16 2015-05-12 Air Squared, Inc. Three stage scroll vacuum pump
US8764424B2 (en) 2010-05-17 2014-07-01 Tuthill Corporation Screw pump with field refurbishment provisions
US10519815B2 (en) 2011-08-09 2019-12-31 Air Squared, Inc. Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump or combined organic rankine and heat pump cycle
US10774690B2 (en) 2011-08-09 2020-09-15 Air Squared, Inc. Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle
US9404491B2 (en) 2013-03-13 2016-08-02 Agilent Technologies, Inc. Scroll pump having bellows providing angular synchronization and back-up system for bellows
US20160201670A1 (en) * 2013-04-05 2016-07-14 Agilent Technologies, Inc. Angular Synchronization of Stationary and Orbiting Plate Scroll Blades in a Scroll Pump Using a Metallic Bellows
US10294939B2 (en) * 2013-04-05 2019-05-21 Agilent Technologies, Inc. Angular synchronization of stationary and orbiting plate scroll blades in a scroll pump using a metallic bellows
US9328730B2 (en) * 2013-04-05 2016-05-03 Agilent Technologies, Inc. Angular synchronization of stationary and orbiting plate scroll blades in a scroll pump using a metallic bellows
US20140301879A1 (en) * 2013-04-05 2014-10-09 Agilent Technologies, Inc. Angular Synchronization of Stationary and Orbiting Plate Scroll Blades in a Scroll Pump Using a Metallic Bellows
US9366255B2 (en) 2013-12-02 2016-06-14 Agilent Technologies, Inc. Scroll vacuum pump having external axial adjustment mechanism
US10508543B2 (en) 2015-05-07 2019-12-17 Air Squared, Inc. Scroll device having a pressure plate
US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
US11692550B2 (en) 2016-12-06 2023-07-04 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
US11319955B2 (en) * 2017-12-14 2022-05-03 Mouvex Positive displacement pump with improved cleaning
US11454241B2 (en) 2018-05-04 2022-09-27 Air Squared, Inc. Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump
US11067080B2 (en) 2018-07-17 2021-07-20 Air Squared, Inc. Low cost scroll compressor or vacuum pump
US11933299B2 (en) 2018-07-17 2024-03-19 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
EP3848586A4 (fr) * 2018-12-06 2021-11-17 Gree Green Refrigeration Technology Center Co. Ltd. of Zhuhai Compresseur
US11661940B2 (en) 2018-12-06 2023-05-30 Gree Green Refrigeration Technology Center Co., Ltd. Of Zhuhai Scroll compressor having cooling pipe moving synchronously with orbiting scroll and rotating with respect to crankshaft
US11473572B2 (en) 2019-06-25 2022-10-18 Air Squared, Inc. Aftercooler for cooling compressed working fluid
EP3978755A4 (fr) * 2019-07-10 2022-08-10 Daikin Industries, Ltd. Compresseur à spirale
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

Also Published As

Publication number Publication date
NL151776B (nl) 1976-12-15
CA968766A (en) 1975-06-03
DE2225327C3 (de) 1978-08-03
IT959019B (it) 1973-11-10
BE783710A (fr) 1972-09-18
DE2225327A1 (de) 1972-12-14
DE2225327B2 (de) 1977-12-01
FR2153129B2 (fr) 1974-01-04
FR2153129A2 (fr) 1973-05-04
NL7207406A (fr) 1972-12-05
GB1367986A (en) 1974-09-25
CH553333A (fr) 1974-08-30
AT316721B (de) 1974-07-25

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