WO2011001100A2 - Machine à volutes à étages multiples - Google Patents
Machine à volutes à étages multiples Download PDFInfo
- Publication number
- WO2011001100A2 WO2011001100A2 PCT/FR2010/051351 FR2010051351W WO2011001100A2 WO 2011001100 A2 WO2011001100 A2 WO 2011001100A2 FR 2010051351 W FR2010051351 W FR 2010051351W WO 2011001100 A2 WO2011001100 A2 WO 2011001100A2
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- WIPO (PCT)
- Prior art keywords
- stage
- volute
- pressure fluid
- fluid passage
- spiral
- Prior art date
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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
- 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
- F04C18/0276—Different wall heights
-
- 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
- F04C18/0253—Details concerning the base
- F04C18/0261—Details of the ports, e.g. location, number, 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
- 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
- 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
- F04C23/008—Hermetic pumps
-
- 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 present invention relates to a multistage scroll machine for compressing and / or expanding a fluid.
- Such scroll machine is in particular known from FR 2,400,625 which describes a scroll machine comprising a first and a second scroll describing a relative orbital movement, the first volute being equipped with at least one spiral and the second volute being equipped at least two spirals, the spirals of the second volute being engaged in the spiral of the first volute so as to define at least a first series of chambers of variable volume belonging to a first stage of compression or relaxation, and at least a second series of variable volume chambers belonging to a second compression or expansion stage, each compression or expansion stage comprising at least one high pressure fluid passage arranged to open into one of the chambers of the respective stage and at least one low pressure fluid passage arranged to open into one of the chambers of the respective stage.
- a cooling device may be disposed between the first stage high pressure fluid passage and the second stage low pressure fluid passage such that the compressed first compression stage is cooled before being conveyed to the second compression stage.
- Such a configuration makes it possible to prevent the compressed fluid discharged from the second compression stage from reaching an excessively high discharge temperature.
- a disadvantage of this type of scroll machine lies in the fact that the compressed and cooled fluid which is conveyed in the second compression stage is heated by the compressed fluid which is discharged from the first compression stage, because of the proximity of the passage high pressure fluid of the first stage and the low pressure fluid passage of the second stage.
- a heater may be arranged between the low pressure fluid passage of the first expansion stage and the high pressure fluid passage of the second stage of the second stage. relaxation, so that the fluid expanded in the first expansion stage is heated before being fed to the second expansion stage.
- Such a configuration makes it possible to increase the mechanical energy produced by the machine.
- a disadvantage of this type of scroll machine lies in the fact that the expanded and heated fluid which is fed into the second expansion stage is cooled by the expanded fluid which is discharged from the first expansion stage, because of the proximity of the high pressure fluid passage of the first stage and the low pressure fluid passage of the second stage.
- FR 2,400,625 comprises a first stage extending from the outer end of the spiral of the fixed scroll to the inner end of the spiral of the latter, and a second stage extending in the continuity of the first stage up to at the inner end of the spiral of the fixed scroll.
- the present invention aims to solve all or part of these disadvantages.
- the technical problem underlying the invention is therefore to provide a multistage scroll machine which is simple in structure, economical and to improve the performance of the latter, and which allows easy adjustment of the displacements and rates compression or expansion of the different stages of compression or relaxation.
- the invention relates to a multi-stage scroll machine for compressing and / or expanding a fluid, comprising first and second scrolls describing orbital relative movement, the first volute being equipped with at least one spiral and the second volute being equipped with at least two spirals, the spirals of the second volute being engaged in the spiral of the first volute so as to delimit at least a first series of chambers of variable volume belonging to a first stage of compression or expansion, and at least a second series of chambers of variable volume belonging to a second stage of compression or expansion, each stage of compression or expansion comprising at least one fluid passage to high pressure arranged to open into at least one of the chambers of the respective stage and at least one low pressure fluid passage arranged to open into at least one of the chambers of the respective stage, the fluid passage to high pressure of the first stage and the high pressure fluid passage of the second stage being configured so that the fluid passing through the fluid passage
- the first-stage high-pressure device has a lower pressure than the fluid passing through the second-stage high-pressure fluid passage, characterized
- Such positioning of the low-pressure fluid passage of the second stage significantly increases the possibilities of adjusting the displacement and the compression or expansion ratio of the different stages since it is no longer necessary to arrange the two stages in the second stage. continuity of one another.
- Such positioning of the low pressure fluid passage of the second stage also allows the latter to move away from the high pressure fluid passage of the first stage, and thus to avoid heat transfer between the fluids flowing through these two passages. of fluid.
- the passage of high pressure fluid belonging to a first compression or expansion stage may have a pressure substantially equal to that of the low pressure fluid passage belonging to the second compression or expansion stage, or a pressure substantially equal to that of the high pressure fluid passage belonging to the second stage of compression or expansion.
- each spiral of the same volute extends from the same side of said volute.
- the spirals of the second volute are nested one inside the other so that, in at least one radial section of the second volute, at least one alternation of the spirals of the second volute is made from the convergence of the spirals of the second volute.
- the convergence zone of the spirals of the second volute corresponds to the zone where the inner ends of these spirals converge if the latter were extended to their origin.
- alteration of the spirals of the second volute should be interpreted as meaning that one successively encounters at least one first spiral of the second volute, a second spiral of the second volute and again the first spiral of the second volute.
- variable volume chambers of at least one of the stages have a height different from that of the variable volume chambers of the other stages.
- at least one of the spirals of the second volute has a height different from that of the other spirals of the second volute.
- each spiral of the second volute has a height different from that of the other spirals of the second volute.
- the height of the spiral of the second volute partially delimiting the variable volume chambers of the first floor is larger than the height of the spiral of the second volute partially delimiting the variable-volume chambers of the second floor.
- the height of the spiral of the second volute partially delimiting the volume chambers variable of the first stage is larger than the height of the spiral of the second volute partially delimiting the variable volume chambers of the second stage.
- the height of the spiral of the second volute partially delimiting the variable volume chambers of the first stage. stage is advantageously smaller than the height of the spiral of the second volute partially delimiting the variable volume chambers of the second stage.
- the first volute and one of the spirals of the second volute are configured such that there is an axial clearance between the latter, and said spiral of the second volute comprises, on its side facing the first volute and over at least a portion of its length, a sealing segment.
- the seal between the top of the other spirals and the face of the volute facing is obtained by contact control.
- At least one of the spirals of the second volute has a thickness different from that of the other spirals of the second volute.
- each spiral of the second volute has a thickness different from that of the other spirals of the second volute.
- At least one of the spirals of the second volute has a longitudinally variable thickness.
- the machine comprises, on the one hand, connection means arranged to connect the high-pressure fluid passage of the first stage and the low-pressure fluid passage of the second stage, and on the other hand means for heating and / or coolers arranged to heat and / or cool the fluid flowing between the first stage high pressure fluid passage and the second stage low pressure fluid passage.
- the scroll machine comprises:
- a sealed enclosure delimited by a ferrule whose upper and lower ends are respectively closed by a cover and a base,
- connection extending through an opening in the shell and opening into the intermediate chamber, the connection being connected to the heating and / or cooling means, and
- At least one fluid circulation passage connecting the portion of the scroll machine housing the engine to a chamber defined by the fixed scroll and the cover.
- the low-pressure fluid passage belonging to the second compression or expansion stage opens into the chamber delimited by the cover and the fixed scroll, and the passage of high-pressure fluid belonging to the first compression stage or detent is connected directly to a fitting extending through an opening in the lid, said connector being connected to the heating means and / or cooling.
- the low-pressure fluid passage belonging to the second compression or expansion stage is connected directly to a coupling extending through an opening in the cover, said connection being connected to the heating means and / or cooling, and the high-pressure fluid passage belonging to the first compression or expansion stage opens into the chamber defined by the lid and the fixed scroll.
- the scroll machine is a scroll compressor
- the low pressure fluid passages of the different stages are fluid intake passages
- the high pressure fluid passages of the different stages are fluid discharge passages
- the fluid is to be compressed successively in the first stage and in the second stage.
- the scroll compressor comprises a refrigerant inlet opening into an intake chamber formed in the body and communicating with a suction chamber defined by the fixed and mobile scrolls.
- a refrigerant inlet opening into an intake chamber formed in the body and communicating with a suction chamber defined by the fixed and mobile scrolls.
- At least one of the stages comprises two variable volume chambers, called external chamber and internal chamber, delimited respectively internally and externally by one of the spirals of the second volute and arranged to open into the fluid passage to high pressure of the corresponding stage, and the machine comprises pressure balancing means configured so that the pressure in the outer chamber before it is in communication with the high pressure fluid passage of the corresponding stage is substantially equal to the pressure in the internal chamber before it is in communication with the high pressure fluid passage of the corresponding stage.
- the pressure equalizing means comprise a protrusion extending from the inner face of the spiral of the first volute and located at the level of the high pressure fluid passage of the corresponding stage, the protrusion preferably having a profile arranged to delay the communication of the outer chamber with the high pressure fluid passage of the corresponding stage.
- the profile of the projection is advantageously the conjugate profile of that of the inner end of the spiral of the second volute delimiting the outer and inner chambers.
- the projection has an arcuate profile of radius equal to the orbital radius of the orbital movement.
- the outer end of the spiral of the first volute and the outer end of the spiral of the second volute partially delimiting the variable volume chambers of the first stage are located asymmetrically with respect to the convergence zone of the spirals defining the variable volume chambers of the second stage, and the balancing means comprise a portion of the spiral of the first volute extending between a point diametrically opposite the outer end of the spiral of the second volute partially delimiting the variable volume chambers of the first stage with respect to the convergence zone of the spirals delimiting the variable volume chambers of the second stage and the outer end of the spiral of the first volute.
- each spiral of the second volute partially delimits the variable volume chambers of a single stage.
- the scroll machine is a volute expansion machine
- the low pressure fluid passages of the different stages are fluid discharge passages
- the high pressure fluid passages of the different stages are fluid intake passages
- the fluid is intended to be expanded successively in the second stage and in the first stage.
- the first volute is fixed and the second volute is movable.
- Figure 1 is a schematic longitudinal sectional view of a scroll machine according to a first embodiment.
- Figures 2 and 3 are cross-sectional views of the machine of Figure 1 showing the spirals of the scrolls fixed and movable in two distinct operating positions.
- Figure 4 is a sectional view along the line A-A of Figure 3.
- Figure 5 is a longitudinal sectional view of the fixed and mobile scrolls of a scroll machine according to a second embodiment.
- Figure 6 is a cross-sectional view of a scroll machine according to a third embodiment.
- Figure 7 is a cross-sectional view of the fixed and mobile scrolls of a scroll machine according to a fourth embodiment.
- Figures 8 to 1 1 are cross-sectional views of the volutes of Figure 7, in four different operating positions shifted respectively by a quarter turn.
- Figures 12 to 15 are cross-sectional views of the volutes of Figure 7, in four distinct operating positions respectively offset by a quarter turn.
- Figure 16 is a cross-sectional view of the fixed and mobile scrolls of a scroll machine according to a fifth embodiment.
- Figure 17 is a cross-sectional view of the fixed and mobile scrolls of a scroll machine according to a sixth embodiment.
- Figure 18 is a cross-sectional view of the fixed and mobile scrolls of a scroll machine according to a seventh embodiment.
- Figure 19 is a partial sectional view of the fixed and mobile scrolls of a scroll machine according to an eighth embodiment.
- Figure 20 is a top view of one of the spirals of the movable scroll of Figure 19.
- Figure 21 is a schematic longitudinal sectional view of a scroll machine according to a ninth embodiment.
- Figure 22 is a schematic longitudinal sectional view of a scroll machine according to a tenth embodiment.
- Figures 1 to 4 show a multistage scroll machine, according to a first embodiment of the invention, configured to operate as a compressor arranged to compress a refrigerant.
- Figure 1 depicts a scroll machine occupying a vertical position.
- the scroll machine according to the invention could occupy an inclined position, or a horizontal position, without its structure being significantly modified.
- the scroll machine shown in FIG. 1 comprises a sealed enclosure delimited by a shell 2 whose upper and lower ends are respectively closed by a cover 3 and a base 4.
- the assembly of this enclosure can be made in particular by means of cords. Welding.
- the scroll machine comprises a fixed scroll 5 having a plate 6 equipped with a spiral 7 intended to be turned downwards, and a movable scroll 8 having a plate 9 bearing against a body 11 contained in the casing of the scroll machine, the plate 9 being equipped with two spirals 12, 13 to be turned upwards.
- the scroll machine comprises a drive shaft 14 whose upper end is engaged in a sleeve-shaped part 15, which comprises the mobile volute 8. During its driving in rotation by an electric motor 16 contained in the envelope of the scroll machine, the drive shaft 14 drives the mobile scroll 8 in a circular orbital motion relative to the fixed scroll 5.
- the spiral 12 of the movable scroll 8 has a longitudinally variable thickness.
- the spiral 12 of the movable scroll 8 has a first portion 12a of constant thickness extending from its outer end, and a second portion 12b of variable thickness extending in the continuity of the first portion 12a and up to at the inner end of the spiral 12.
- the spiral 13 of the mobile scroll 8 has a constant thickness.
- spirals 12, 13 of the mobile scroll 8 if the latter were extended to their origin, converge towards a convergence zone located substantially at the center of the mobile scroll 8.
- the spirals 12, 13 of the movable scroll 8 are nested one inside the other so that, in at least one radial section of the mobile scroll 8, one meets, from the convergence zone of the spirals 12, 13, alternately the spirals 12, 13 of the movable scroll 8.
- the spiral 7 of the fixed scroll 5 has a longitudinally variable thickness.
- the spiral 7 of the fixed volute 5 has a first portion 7a of constant thickness extending from its outer end, and a second portion 7b of variable thickness extending in the continuity of the first portion 7a and up to at the inner end of the spiral 7.
- the second portion 7b of the spiral 7 of the fixed scroll comprises a housing 17 extending in a spiral arranged to receive the spiral 13 of the mobile scroll 8.
- the spirals 12, 13 of the movable scroll 8 and the spiral 7 of the fixed scroll has an identical height.
- the spirals 12, 13 of the mobile volute 8 are engaged in the spiral 7 of the fixed volute 5 so as to define a first series of variable volume chambers 18a to 18d belonging to a first compression stage, and a second series of chambers variable volume 18th to 18h belonging to a second compression stage.
- the spire 12 of the mobile scroll 8 partially delimits only the variable volume chambers 18a to 18d belonging to the first compression stage, whereas the spiral 13 of the mobile scroll 8 partially delimits only the variable volume chambers 18e to 18h. belonging to the second compression stage.
- Each compression stage comprises pairs of compression chambers of variable volume delimited respectively internally and externally by one of the spirals of the mobile volute 8, the compression chambers having a volume which decreases progressively from outside to inside when Orbital motion of the mobile scroll 8.
- spiral 7 of the fixed scroll 5 and the spiral 13 of the moving scroll 8 converge towards a convergence zone located substantially at the center of the fixed scroll.
- the outer end of the spiral 7 of the fixed volute 5 and the outer end of the spiral 12 of the movable scroll 8 are located symmetrically with respect to the convergence zone of the spirals 7, 13 delimiting the variable volume chambers from the second floor.
- the first compression stage comprises two fluid intake passages 19a, 19b connected to a refrigerant inlet 21 formed radially in the shell 2 via one side of two inlet channels 22 formed in the body 1 1, and on the other hand a suction chamber 23 delimited by the fixed scroll 5 and mobile 8 and communicating with the two inlet channels 22.
- the fluid intake passage 19a is delimited by a space between the outer end of the spiral 7 of the fixed volute 5 and the outer wall of the spiral 12 of the mobile volute 8.
- the fluid intake passage 19b is bounded by a space between the outer end of the spiral
- the fluid intake passages 19a, 19b are arranged to open respectively into the most variable volume chambers.
- first stage external chambers chambers 18a and 18b in FIG. 2 during the orbital movement of the mobile scroll 8.
- the first compression stage also comprises a fluid discharge passage 24 arranged to open respectively into the innermost variable volume chambers of the first stage (the chambers 18c, 18d in FIG. 2) during the orbital motion of the mobile scroll. 8.
- the fluid discharge passage 24 of the first stage is constituted by a through orifice formed in the plate 6 of the fixed volute 5 and opening at the inner end of the spiral 12 of the mobile volute 8.
- the through orifice 24 is connected directly to a refrigerant outlet 25 formed in the lid 3.
- the refrigerant outlet 25 preferably extends parallel to the axis of the machine.
- the second compression stage comprises a fluid intake passage 26 connected to a refrigerant inlet 27 formed in the cover 3 and arranged to open respectively into the outermost chambers of the second stage (chambers 18e and 18f in FIG. 2) during the orbital motion of the mobile scroll 8.
- the second compression stage also comprises a fluid discharge passage 28 arranged to open respectively into the innermost chambers of the second stage (the chambers 18g and 18h in FIG. 2) during the orbital movement of the mobile scroll 8.
- the fluid intake passage 26 is constituted by a through orifice formed in the plate 6 of the fixed volute 5 and opening at the outer end of the spiral 13 of the mobile volute 8.
- the fluid discharge passage 28 the second stage is constituted by a through hole formed in the plate 6 of the fixed volute 5 and opening at the inner end of the spiral 13 of the mobile volute 8.
- the through orifice 28 is relié an output of Refrigerant fl uid 29 formed radially in the lid 3 via a discharge chamber 31 delimited by the lid 3 and the fixed volute 5.
- the inlet and discharge ports 26 of the second stage and the discharge orifice 24 of the first stage extend substantially perpendicularly to the plate 6 of the fixed volute 5.
- the fluid inlet 26 of the second compression stage is further away from the center of the fixed scroll 5 that the discharge port 24 of the first compression stage. It should also be noted that the fluid inlet 26 of the second compression stage is further away from the convergence zone of the spiral 7 of the fixed scroll 5 and the spiral 13 of the moving scroll 8 than the discharge port 24 of the first compression stage.
- the scroll machine also comprises connecting means arranged to connect the fluid discharge passage 24 of the first stage to the fluid inlet passage 26 of the second stage, and on the other hand cooling means 33 arranged to cool the fluid. flowing from the fluid discharge passage 24 from the first stage to the fluid inlet passage 26 of the second stage.
- the connection means comprise, according to the embodiment shown in Figure 1, the refrigerant outlet 25, the refrigerant inlet 27 and two connecting portions 32 respectively connecting the refrigerant outlet 25 to the cooling means 33 and the refrigerant inlet 27 to the cooling means 33.
- FIG. 3 shows a position of the fixed and mobile scrolls 8 in which the two outer compression chambers of the first compression stage are respectively closed at the outer ends of the spirals 7 and 12. This position of the fixed and mobile scrolls 8 corresponds to in the so-called "engine displacement" position.
- the outer chambers of the first stage move inward in a clockwise direction and their capacity decreases, causing compression refrigerant contained therein.
- the refrigerant contained therein is discharged through this discharge orifice 24 and is conveyed to the cooling means 33 via the refrigerant outlet 25 and of one of the connecting portions 32.
- the compressed refrigerant is cooled and is then transported to the inlet port 26 of the second stage through the other connecting portion 32 and the refrigerant inlet 27 for compression. in variable-volume rooms on the second floor and in view of its discharge through the discharge port 28 formed substantially in the center of the fixed scroll 5.
- FIG. 5 represents a variant embodiment of the scroll machine that differs from that shown in FIG. 1 in that the spiral 13 of the mobile scroll 8 has a height h2 greater than the height h1 of the spiral 12 of the mobile scroll. 8 so that the variable volume chambers belonging to the second compression stage have a height greater than that of the variable volume chambers belonging to the first compression stage.
- FIG. 6 shows an alternative embodiment of the scroll machine which differs from that shown in FIG. 1 in that it furthermore comprises pressure equalization means configured such that the pressure in the volumetric chamber variable 18c before it is placed in communication with the fluid discharge passage 24 of the first stage is substantially equal to the pressure in the variable volume chamber 18d before it is in communication with the discharge passage 24 of fluid of the first stage.
- the balancing means comprise a projection 34 extending from the inner face of the spiral 7 of the fixed volute 5 and located at the level of the fluid discharge passage 24 of the first stage.
- the projection 34 has an arcuate profile 35 arranged to delay the communication of the variable volume chamber 18c with the fluid discharge passage 24 of the first stage.
- the outer end of the spiral 7 of the fixed scroll and the outer end of the spiral 12 of the mobile scroll could be located substantially asymmetrically with respect to the convergence zone of the spirals. 7, 13 delimiting the variable volume chambers of the second floor.
- the balancing means would be further constituted by a portion 36 of the spiral 7 extending between a point diametrically opposite to the outer end of the spiral 12 of the moving volute relative to the zone of convergence of the spirals 7, 13 and the outer end of the spiral 7 of the fixed scroll.
- FIG. 7 represents another variant embodiment of the flight machine which differs from that shown in FIG. 1, essentially in that the fixed scroll 5 comprises two spirals 7, T nested one inside the other and whose inner ends are connected one to the other by a partition 40, in that the spirals 12, 13 of the movable scroll 8 have the same constant thickness, and in that the first stage has only one fluid inlet passage 19.
- the fluid intake passage 19 is delimited by the outer end of the spiral 7 of the fixed volute 5 and the outer wall of the spiral T of the fixed volute 5, and is arranged to open respectively in the chambers with variable volute the outermost ones of the first stage (the chambers 18a and 18b in FIG. 7) during the orbital movement of the mobile scroll.
- the spirals 7, T of the fixed volute 5 are nested one inside the other so that, in a radial section of the fixed volute 5, one meets, from the spural convergence zone 7, 7 ', alternately the spirals 7, 7' of the fixed volute 5.
- the spirals 7, T of the fixed volute 5 have the same constant thickness.
- the outer end of the spiral T of the fixed volute 5 is connected to the outer wall of the spiral 7 of the fixed volute 5 at the inlet port 26 of the second stage.
- the spirals 12, 13 of the mobile volute 8 are engaged in the spirals 7, T of the fixed volute 5 so as to define a first series of chambers of variable volume 18a to 18d belonging to a first compression stage, and a second series Chambers of variable volume 18th to 18h belonging to a second compression stage.
- FIG. 8 shows the spirals of the fixed and mobile scrolls of FIG. 7 in angular positions such that the outer end of the spiral 12 of the mobile scroll 8 defines a sealing line of one of the chambers of the first stage.
- the points A to E shown in FIG. 8 represent the sealing lines between the spiral 12 of the mobile volute 8 and the spirals of the fixed volute 5, these sealing lines defining the variable volume chambers of the first stage.
- FIGS. 9 to 11 represent three distinct operating positions of the scroll machine offset by a quarter of a turn relative to the position shown in FIG. 8. These various figures make it possible to visualize the evolution of the variable volume chambers 18a at 18d of the first floor and points A to E during the orbital motion of the mobile scroll 8.
- FIG. 12 shows the spirals of the fixed and mobile scrolls of FIG. 7 in angular positions such that the outer end of the spiral 13 of the mobile scroll 8 defines a sealing line of one of the chambers of the second stage.
- the points F to I shown in FIG. 12 represent the sealing lines between the spiral 13 of the movable scroll 8 and the spirals of the fixed scroll 5, these sealing lines defining the variable volume chambers of the second stage.
- FIGS. 13 to 15 represent three distinct operating positions of the scroll machine offset by a quarter of a turn relative to the position shown in FIG. 12. These various figures make it possible to visualize the evolution of the chambers with variable volume 18 at 18h and points F to I during the orbital motion of the mobile scroll 8.
- FIG. 16 represents another variant embodiment of the scroll machine which differs from that shown in FIG. 7 in that the outer end of the spiral 7 of the fixed scroll 5 is connected to the outer wall of the spiral 7 ' of the fixed volute 5, and in that the first stage comprises a single passage of fluid inlet 19 constituted by a through opening in the plate 6 of the fixed volute 5 and opening at the outer end of the Spiral 7 of the fixed scroll 5.
- the through hole 19 is arranged to open respectively into the outermost variable chambers of the first stage during the orbital motion of the moving scroll.
- FIG. 17 represents another variant embodiment of the scroll machine which differs from that shown in FIG. 16 in that the spiral 12 of the mobile scroll 8 has a thickness less than that of the spiral 13 of the mobile scroll 8.
- FIG. 18 represents another variant embodiment of the scroll machine which differs from that shown in FIG. 17 in that the spiral 7 of the fixed scroll 5 has a thickness less than that of the spiral T of the fixed scroll 5.
- FIG. 19 represents yet another variant embodiment of the scroll machine which differs from that shown in FIG. 1 in that the fixed scroll 5 and the spiral 13 of the mobile scroll 8 are configured in such a way that there exists a axial clearance Ja between the latter, and in that the spiral 13 of the mobile volute 8 has, on its side facing the plate 6 of the fixed volute, a sealing segment 42.
- the sealing segment 42 extends only over the central portion of the spiral 13 of the movable scroll 8.
- the sealing segment 42 could extend over the entire length of the spiral 13 of the mobile scroll.
- the spiral 7 of the fixed scroll 5 could also comprise, on its side facing the plate 9 of the mobile scroll 8, a sealing segment.
- FIG. 21 represents yet another variant embodiment of the scroll machine which differs from that shown in FIG. 1 in that the refrigerant inlet 21 opens into an inlet chamber 43 formed in the body 1 1 and communicating with the suction chamber 23 delimited by the fixed and mobile scrolls 8, in that the fluid admission passage 26 opens into a chamber 44 defined by the cover 3 and the fixed volute 5, in that the exit of refrigerant 29 extends substantially parallel to the axis of the scroll machine, in that the fluid discharge passage 28 is directly connected to the refrigerant outlet 29, and in that the scroll machine comprises a connection 45 extending radially through the shell 2 and opening into an intermediate chamber 46 defined by the body 11, the motor 16 and a tubular casing 47 surrounding the latter, the connection 45 being connected to the means ns of cooling 33.
- the compressed refrigerant discharged through the discharge port 24 is conveyed to the cooling means 33 via the refrigerant outlet 25. and one of the connecting portions 32.
- the compressed refrigerant is cooled and is then transported to the connection 45 via the other of the connecting portions 32.
- the refrigerant passes into the intermediate chamber 46 and flows up and down through the engine 16, in particular by a space between the rotor and the stator of the latter.
- the refrigerant then flows from bottom to high in the annular volume 48 delimited by the tubular casing 47 and the shell 2 to the chamber 44 via at least one peripheral passage 49 formed between the shell 2 and the body 1 1.
- the refrigerant finally arrives at the inlet port 26 of the second stage, for compression in the variable volume chambers of the second stage.
- Such circulation of the refrigerant between the two stages of compression improves the cooling of the engine, since the latter is cooled by a higher density gas.
- a circulation of the refrigerant between the two compression stages has the consequence that the part of the scroll machine housing the motor 16 is at a pressure substantially identical to that of the refrigerant discharged through the discharge orifice 24 of the first compression stage, therefore at a higher pressure compared to the embodiment shown in Figure 1.
- This decrease in the pressure difference between the peripheral chambers of the second floor and the part of the machine. volutes housing the motor 16 also limits the forces exerted on the mobile scroll plate, so e limit the wear of the latter.
- FIG. 22 represents yet another variant embodiment of the scroll machine which differs from that shown in FIG. 21 in that the fluid admission passage 24 opens into the chamber 44 delimited by the cover 3 and the fixed scroll 5 , and in that the fluid inlet passage 26 is connected to a refrigerant inlet 27 formed in the cover 3.
- the compressed refrigerant discharged through the discharge orifice 24 passes into the chamber 44 delimited by the lid 3 and the fixed volute 5, and flows from top to bottom in the annular volume 48 delimited by the tubular casing 47 and the ferrule 2 via the peripheral passage 49.
- the refrigerant then flows from bottom to top through the motor 16, to the intermediate chamber 46. Then, the refrigerant is transported to the cooling means 33 via the coupling 45 and one of the connecting portions 32.
- the compressed refrigerant is cooled and is then transported to the inlet port 26 of the second stage through the other of the connecting portions 32 and the refrigerant inlet 27.
- Such circulation of the refrigerant between the two stages of compression improves the cooling of the engine, since the latter is cooled by a gas of higher density, and previously cooled.
- the scroll machine could be configured to function as a volute scroll machine, such as a scroll turbine.
- the intake passages would be discharge passages
- the discharge passages would be intake passages
- the refrigerant would be intended to be expanded successively in the second stage and in the first stage.
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201080038750.8A CN102483061B (zh) | 2009-06-30 | 2010-06-29 | 多段蜗管机器 |
US13/319,440 US8864479B2 (en) | 2009-06-30 | 2010-06-29 | Multi-stage scroll machine |
DE112010002770T DE112010002770T5 (de) | 2009-06-30 | 2010-06-29 | Mehrstufige Spiralmaschine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0954437A FR2947308B1 (fr) | 2009-06-30 | 2009-06-30 | Machine a volutes a etages multiples |
FR0954437 | 2009-06-30 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2011001100A2 true WO2011001100A2 (fr) | 2011-01-06 |
WO2011001100A3 WO2011001100A3 (fr) | 2011-09-15 |
Family
ID=41651529
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/FR2010/051351 WO2011001100A2 (fr) | 2009-06-30 | 2010-06-29 | Machine à volutes à étages multiples |
Country Status (5)
Country | Link |
---|---|
US (1) | US8864479B2 (fr) |
CN (1) | CN102483061B (fr) |
DE (1) | DE112010002770T5 (fr) |
FR (1) | FR2947308B1 (fr) |
WO (1) | WO2011001100A2 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103541770A (zh) * | 2012-07-10 | 2014-01-29 | 株式会社丰田自动织机 | 涡旋式膨胀机 |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9039396B2 (en) | 2012-07-03 | 2015-05-26 | Emerson Climate Technologies, Inc. | Piston and scroll compressor assembly |
CN105008824B (zh) * | 2013-02-26 | 2017-10-24 | 艾默生环境优化技术有限公司 | 包括高压侧压缩机和低压侧压缩机的系统 |
US10400770B2 (en) | 2016-02-17 | 2019-09-03 | Emerson Climate Technologies, Inc. | Compressor with Oldham assembly |
CN111868384B (zh) * | 2018-09-18 | 2022-06-03 | 富士电机株式会社 | 多级压缩机 |
US11136977B2 (en) | 2018-12-31 | 2021-10-05 | Emerson Climate Technologies, Inc. | Compressor having Oldham keys |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2400625A1 (fr) | 1977-08-15 | 1979-03-16 | Ingersoll Rand Co | Appareils tels que compresseurs, appareils de detente et pompes |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4157123A (en) * | 1978-03-06 | 1979-06-05 | Everest & Jennings, Inc. | Wheelchair electrical control circuit |
EP0579888B1 (fr) * | 1992-07-20 | 1996-08-21 | AGINFOR AG für industrielle Forschung | Pompe rotatif à spirale |
JP3806180B2 (ja) * | 1996-06-11 | 2006-08-09 | 三菱重工業株式会社 | スクロール流体機械 |
US6050792A (en) * | 1999-01-11 | 2000-04-18 | Air-Squared, Inc. | Multi-stage scroll compressor |
JP4618478B2 (ja) * | 2001-08-01 | 2011-01-26 | 株式会社豊田自動織機 | スクロール型圧縮機 |
US6922999B2 (en) * | 2003-03-05 | 2005-08-02 | Anest Iwata Corporation | Single-winding multi-stage scroll expander |
US20060099096A1 (en) * | 2004-11-08 | 2006-05-11 | Shaffer Robert W | Scroll pump system |
-
2009
- 2009-06-30 FR FR0954437A patent/FR2947308B1/fr active Active
-
2010
- 2010-06-29 DE DE112010002770T patent/DE112010002770T5/de not_active Withdrawn
- 2010-06-29 CN CN201080038750.8A patent/CN102483061B/zh not_active Expired - Fee Related
- 2010-06-29 US US13/319,440 patent/US8864479B2/en not_active Expired - Fee Related
- 2010-06-29 WO PCT/FR2010/051351 patent/WO2011001100A2/fr active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2400625A1 (fr) | 1977-08-15 | 1979-03-16 | Ingersoll Rand Co | Appareils tels que compresseurs, appareils de detente et pompes |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103541770A (zh) * | 2012-07-10 | 2014-01-29 | 株式会社丰田自动织机 | 涡旋式膨胀机 |
Also Published As
Publication number | Publication date |
---|---|
FR2947308B1 (fr) | 2014-04-18 |
DE112010002770T5 (de) | 2012-09-27 |
WO2011001100A3 (fr) | 2011-09-15 |
FR2947308A1 (fr) | 2010-12-31 |
US20120100025A1 (en) | 2012-04-26 |
CN102483061B (zh) | 2015-12-09 |
US8864479B2 (en) | 2014-10-21 |
CN102483061A (zh) | 2012-05-30 |
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