WO2013084618A1 - Mécanisme de détente à volute - Google Patents

Mécanisme de détente à volute Download PDF

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Publication number
WO2013084618A1
WO2013084618A1 PCT/JP2012/077754 JP2012077754W WO2013084618A1 WO 2013084618 A1 WO2013084618 A1 WO 2013084618A1 JP 2012077754 W JP2012077754 W JP 2012077754W WO 2013084618 A1 WO2013084618 A1 WO 2013084618A1
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WO
WIPO (PCT)
Prior art keywords
subport
expansion
suction
valve
sub
Prior art date
Application number
PCT/JP2012/077754
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English (en)
Japanese (ja)
Inventor
耕二郎 田丸
井口　雅夫
英文 森
榎島　史修
裕之 武井
Original Assignee
株式会社豊田自動織機
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社豊田自動織機 filed Critical 株式会社豊田自動織機
Publication of WO2013084618A1 publication Critical patent/WO2013084618A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0215—Rotary-piston machines or engines 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a variable-capacity scroll expander, and in particular, to a type in which the two expansion chambers have different suction volumes.
  • the scroll expander is used to expand the refrigerant in the Rankine cycle or the like, sucks the refrigerant from the suction port, expands it in the expansion chamber, and discharges it from the discharge port.
  • the variable capacity type includes a sub suction port as a suction port in addition to the main suction port, and changes the capacity by opening and closing the sub suction port.
  • Patent Document 1 An example of a scroll expander having a plurality of sub suction ports and changing the capacity in multiple stages is described in Patent Document 1.
  • Patent Documents 2 and 3 describe examples of scroll compressors that change capacity by opening and closing a plurality of bypass ports.
  • the ratio of the discharge volume to the suction volume can be designed for each expansion chamber.
  • the discharge volumes of the two expansion chambers may be different from each other.
  • the volume ratio can be kept the same.
  • An example of such a configuration relates to a scroll compressor, but is described in Patent Document 4.
  • the fluid in the expansion chamber acts in the direction of peeling the movable scroll due to the pressure. Therefore, in order to properly expand the fluid in the expansion chamber, it is necessary to apply a back pressure of an appropriate magnitude from the side of the movable scroll opposite to the expansion chamber.
  • the appropriate back pressure is determined by the equivalent load and the load point determined by the pressure distribution in the expansion chamber.
  • the load point is away from the center of the fixed scroll, the moment for peeling the movable scroll increases, so that a larger back pressure is required than when the load point is at the center of the fixed scroll. Therefore, when the suction volumes of the two expansion chambers are different, the degree of unbalance, which is the ratio of the suction volumes, is important as an appropriate back pressure index.
  • the present invention has been made to solve such problems, and an object thereof is to provide a scroll expander that can reduce the required back pressure and improve the efficiency of the expander.
  • a scroll expander includes at least one expansion chamber, a main suction port provided in common to the two expansion chambers, and at least one expansion chamber.
  • a scroll expander that includes two sub-suction ports and a sub-port valve that opens and closes the sub-suction port, and the sub-port valve opens and closes to change the suction volume of the corresponding expansion chamber.
  • the subport valve In at least one opening / closing operation of the subport valve, When opening the subport valve, open the subport valve provided in the smaller one of the two expansion chambers just before the opening / closing operation, When closing the subport valve, the subport valve provided on the larger one of the two expansion chambers immediately before the opening / closing operation is closed.
  • the two expansion chambers may have different suction volumes. Regardless of whether the subport valve is open or closed, the two expansion chambers may have different suction volumes.
  • opening / closing operation of all sub-port valves When opening the subport valve, open the subport valve provided in the smaller one of the two expansion chambers just before the opening / closing operation, When closing the subport valve, the subport valve provided on the larger one of the two expansion chambers immediately before the opening / closing operation may be closed.
  • Each of the two expansion chambers may include at least one sub suction port.
  • Each of the two expansion chambers may include a plurality of sub suction ports. With all the subport valves closed, the two expansion chambers may have an equal expansion ratio.
  • the degree of unbalance between the suction volumes in the two expansion chambers can be kept relatively small, the required back pressure can be reduced, and the expander efficiency can be improved.
  • FIG. 3 is a sectional view taken along line III-III in FIG. 2.
  • 3 is a diagram showing a state in which the movable scroll is in a position different from that in FIG. 3 in the cross-sectional view taken along the line III-III in FIG.
  • 3 is a figure which shows the specific example of the control regarding the suction
  • FIG. 3 shows the structure which provided multiple subport valves in each expansion chamber.
  • FIG. 1 shows a configuration of a Rankine cycle R including an expander 100 according to Embodiment 1 of the present invention.
  • Rankine cycle R is mounted on a vehicle, for example.
  • the expander 100 is a scroll-type variable capacity expander, and sucks, expands and discharges the refrigerant flowing through the Rankine cycle R.
  • the Rankine cycle R forms a circulation path that connects the pump 1, the boiler 2, the expander 100, and the condenser 3 in this order in an annular manner, and a refrigerant as a working fluid flows therethrough.
  • the pump 1 is driven by a motor 4 to pump a liquid refrigerant to the boiler 2.
  • the boiler 2 heats the refrigerant by exchanging heat between the refrigerant sent by the pump 1 and the exhaust gas of the exhaust system 6 of the engine 5 of the vehicle.
  • the expander 100 expands the high-temperature and high-pressure refrigerant after being heated by the boiler 2 in the inside thereof, thereby taking out the rotational driving force.
  • This rotational driving force is transmitted to the engine 5 through the power transmission mechanism 7 and assists the rotational driving force of the engine 5.
  • the power transmission mechanism 7 is constituted by a pulley and a belt, for example.
  • the condenser 3 circulates the refrigerant discharged from the expander 100 and exchanges heat with the air around the condenser 3 to cool and condense the refrigerant.
  • the pump 1 pumps the condensed liquid refrigerant again and circulates the Rankine cycle R.
  • FIG. 2 shows the configuration of the expander 100.
  • the expander 100 includes an expansion unit 101 and a power generation unit 102.
  • the expander 100 includes an expansion unit housing 10 that forms a housing of the expansion unit 101 and a power generation unit housing 20 that forms a housing of the power generation unit 102.
  • the expansion part housing 10 includes a first expansion part housing 10a and a second expansion part housing 10b. The first expansion section housing 10a and the power generation section housing 20 are connected to both sides of the second expansion section housing 10b.
  • the inflating part 101 has a fixed scroll 11 inside the first inflating part housing 10a.
  • the fixed scroll 11 is fixed to the first expansion portion housing 10a.
  • the fixed scroll 11 is formed by a plate-like substrate 11a and a spiral wall 11b.
  • the spiral wall 11b is formed in a spiral shape on the substrate 11a and protrudes in the direction from the substrate 11a toward the second expansion portion housing 10b.
  • the inflating portion 101 has a movable scroll 12 so as to face the fixed scroll 11 from the inside of the second inflating portion housing 10b to the inside of the first inflating portion housing 10a.
  • the movable scroll 12 is disposed on the second expansion portion housing 10b side with respect to the fixed scroll 11, and is formed by a substrate 12a disposed substantially parallel to the substrate 11a of the fixed scroll 11 and a spiral wall 12b.
  • the spiral wall 12 b is formed in a spiral shape on the substrate 12 a and protrudes from the substrate 12 a toward the substrate 11 a of the fixed scroll 11.
  • the cylindrical shaft support part 12d protrudes and is formed in the opposite side to the spiral wall 12b from the board
  • the movable scroll 12 is arranged such that the spiral wall 12b is fitted between the spiral walls 11b of the fixed scroll 11.
  • the spiral wall 12 b of the movable scroll 12 can form a crescent-shaped expansion chamber 40 that is a closed space by contacting the spiral wall 11 b of the fixed scroll 11.
  • a suction chamber 10 c is formed on the opposite side of the movable scroll 12 with respect to the fixed scroll 11 inside the first expansion portion housing 10 a.
  • the suction chamber 10c communicates with the outside of the expander 100 via a suction passage 10d that penetrates the first expansion portion housing 10a.
  • a discharge passage 10e extending through the outermost portion of the spiral wall 11b and the first expansion portion housing 10a is formed in the first expansion portion housing 10a and the spiral wall 11b.
  • the expansion chamber 40 communicates with the outside of the expander 100 via the discharge passage 10e.
  • the discharge passage 10e is actually located at a position that does not appear in the cross section of FIG. 2 (see FIGS. 3 and 4), but is shown as being located at a position passing through this cross section for convenience of explanation.
  • the inflating portion 101 has a drive shaft 13 on the shaft support portion 12d side of the movable scroll 12.
  • the drive shaft 13 includes a diameter-expanded portion 13b that is rotatably supported by a bearing 14 in the second expansion portion housing 10b, a main shaft portion 13a that extends from the diameter-expanded portion 13b toward the power generation unit housing 20, and a diameter-expanded portion 13b.
  • an eccentric shaft portion 13c extending into the shaft support portion 12d of the movable scroll 12 from the same.
  • the main shaft portion 13a, the enlarged diameter portion 13b, and the eccentric shaft portion 13c are all substantially cylindrical, and the central axis of the main shaft portion 13a and the central axis of the enlarged diameter portion 13b are on the same straight line. Further, the central axis of the eccentric shaft portion 13c is arranged at a position that is parallel to the central axes of the main shaft portion 13a and the enlarged diameter portion 13b but not on the same straight line. That is, the central axis of the eccentric shaft portion 13c is eccentric.
  • the eccentric shaft portion 13c is rotatably fitted to the shaft support portion 12d via the bush 15 and the outer peripheral bearing 16 thereof.
  • the eccentric shaft portion 13c can rotate so as to turn around the central axes of the main shaft portion 13a and the enlarged diameter portion 13b.
  • the movable scroll 12 revolves around the central axes of the main shaft portion 13a and the enlarged diameter portion 13b, thereby moving the main shaft portion 13a and the enlarged diameter portion 13b around the central axis via the eccentric shaft portion 13c. Can be rotated. Further, when the movable scroll 12 revolves, the expansion chamber 40 is formed so as to communicate with the main suction port 30, and is then isolated from the main suction port 30 and moved to the peripheral edge of the substrate 11 a of the fixed scroll 11. Increase.
  • An end portion of the main shaft portion 13a is rotatably supported by a bearing 20b provided in the power generation unit housing 20, and further protrudes from the power generation unit housing 20 and is connected to a pulley (see FIG. 1) of the power transmission mechanism 7. .
  • a rotor 21 is provided around the main shaft portion 13a, and is fixed so as to rotate integrally with the main shaft portion 13a.
  • a stator 22 having a coil 22 a is fixed to the inner peripheral surface of the power generation unit housing 20 so as to surround the rotor 21.
  • the power generation unit housing 20, the main shaft portion 13a, the rotor 21, and the stator 22 constitute a power generation unit 102.
  • the power generation unit 102 is a coil of the stator 22 by rotating the main shaft portion 13a and rotating the rotor 21. A current can be generated in 22a.
  • FIG. 3 and 4 are sectional views taken along line III-III in FIG. 3 and FIG. 4 are different in the position of the movable scroll 12 and are not necessarily aligned with the position of the movable scroll 12 in FIG.
  • the substrate 11a of the fixed scroll 11 is formed with a single main suction port 30 and a plurality of sub suction ports 31a and 31b as suction ports for communicating the suction chamber 10c and the expansion chamber 40.
  • the main suction port 30 is provided, for example, through the center of the substrate 11a.
  • the main suction port 30 is always open at least during the expansion operation of the expander 100.
  • At least two expansion chambers 40 are defined by the fixed scroll 11 and the movable scroll 12. Some of these expansion chambers 40 can be regarded as having the same expansion chamber in different phases during the expansion stroke. For example, in FIG. 3, two expansion chambers 40a corresponding to the sub suction ports 31a and two expansion chambers 40b corresponding to the sub suction ports 31b are formed.
  • the main suction port 30 is provided in common for both expansion chambers.
  • the sub suction ports 31a and 31b are respectively provided with corresponding sub port valves (not shown), and the sub suction ports 31a and 31b are opened and closed by opening and closing these sub port valves.
  • the sub suction port 31a is a first sub suction port
  • the sub suction port 31b is a second sub suction port
  • the sub port valve of the sub suction port 31a is a first sub port valve
  • the sub suction port 31b This subport valve is defined as a second subport valve.
  • All the subport valves are connected to the ECU 8 (FIG. 1) and open and close in response to a control signal from the ECU 8.
  • the specific configuration of the subport valve is not particularly shown, but those skilled in the art can configure an appropriate subport valve using a known technique.
  • a subport valve as described in Patent Documents 1 to 3 may be used.
  • FIG. 3 shows a state in which the outer one of the expansion chambers 40a (that is, the most advanced phase in the expansion stroke) is in the discharge start phase (that is, the expansion stroke completion phase).
  • FIG. 4 shows a state in which the outer one of the expansion chambers 40b is in the discharge start phase. Since the number of scroll turns is different between the fixed scroll 11 and the movable scroll 12, the volumes (discharge volumes) of the two expansion chambers in the discharge start phase are different, and the discharge volume (FIG. 4) of the expansion chamber 40b is the same as that of the expansion chamber 40a. It is larger than the discharge volume (FIG. 3).
  • the suction volume of the expander 100 is variable by opening / closing the subport valve corresponding to each subport.
  • FIG. 1 during operation of the vehicle engine 5, exhaust gas discharged from the engine 5 to the exhaust system 6 flows through the boiler 2 and then is discharged to the outside of the vehicle. At this time, the rotational driving force of the engine 5 is transmitted to the expander 100 via the power transmission mechanism 7, whereby the expansion unit 101 and the power generation unit 102 are rotationally driven.
  • the pump 1 is driven by the motor 4 while the engine 5 is operating. As a result, the pump 1 pumps the liquid refrigerant toward the boiler 2.
  • the refrigerant subjected to the adiabatic pressurizing action by the pump 1 is heated at the same pressure by exchanging heat with the exhaust gas in the boiler 2 to become high-temperature and high-pressure superheated steam, and is sucked into the expander 100 and adiabatically expanded and flows out. .
  • the refrigerant that has flowed out flows into the condenser 3, where it is cooled by isobaric cooling by exchanging heat with the surrounding air, that is, outside air, and condensed to flow out. Further, the refrigerant flowing out of the condenser 3 is sucked into the pump 1 and pumped again, and circulates through the Rankine cycle R.
  • the high-temperature and high-pressure refrigerant that has flowed out of the boiler 2 flows into the suction chamber 10 c through the suction passage 10 d of the expansion portion 101. Furthermore, it flows into the expansion chamber 40 from the suction chamber 10c through the main suction port 30 (and the sub suction ports 31a and 31b when opened).
  • the refrigerant in the expansion chamber 40 imparts a rotational driving force to the movable scroll 12 in the direction of increasing the volume of the expansion chamber 40 by the expansion force, so that the expansion chamber 40 is centered on the substrate 11a of the fixed scroll 11.
  • the volume of the movable scroll 12 is increased with the rotation of the movable scroll 12, and it moves toward the peripheral edge of the substrate 11 a to communicate with the discharge passage 10 e. Then, the refrigerant expanded in the expansion chamber 40 whose volume has been increased is discharged to the outside of the expansion unit 101.
  • the rotational driving force of the movable scroll 12 due to the expansion force of the refrigerant is transmitted via the drive shaft 13, thereby rotating the rotor 21 of the power generation unit 102 and assisting the rotational driving force of the engine 5.
  • an alternating current is generated in the coil 22a of the stator 22, and the generated alternating current is converted into a direct current by a converter (not shown) and then charged to a battery or the like.
  • FIG. 5 shows a specific example of control related to the suction volumes of the expansion chambers 40a and 40b and the opening / closing operations of the subport valves.
  • the ECU 8 controls the suction volume of the expander 100 in three stages: state 1 (suction volume: small), state 2 (suction volume: medium), and state 3 (suction volume: large).
  • state 1 suction volume: small
  • state 2 suction volume: medium
  • state 3 suction volume: large
  • the positions and shapes of the main suction port 30 and the sub suction ports 31a and 31b are designed to realize the suction volume shown in FIG. In a state where the subport valves of both the expansion chambers are closed (state 1), the suction volume 0.9 of the first expansion chamber 40a is smaller than the suction volume 1.1 of the second expansion chamber 40b.
  • the suction volume in state 1 is designed to correspond to the discharge volume of each expansion chamber, and the expansion ratio of the expansion chamber 40a and the expansion ratio of the expansion chamber 40b are equal to each other.
  • “equal” is not necessarily limited to a strictly equal configuration, and may be within a predetermined error range. For example, it may be within an error range of ⁇ 10% based on the smaller expansion ratio. As a specific example, even when the expansion ratio of the expansion chamber 40a is 10.0 and the expansion ratio of the expansion chamber 40b is 11.0, these expansion ratios can be regarded as being equal to each other.
  • the suction volume 1.8 of the first expansion chamber 40a is greater than the suction volume 1.1 of the second expansion chamber 40b.
  • the suction volume ratio (degree of unbalance) is [1.8 / 1.1 ⁇ 1.6].
  • the degree of unbalance is suppressed to a lower level as compared with the state in which the second subport valve is opened first (reference state not realized in the present embodiment; degree of unbalance 2.4). For this reason, compared with the reference state, a suction volume of substantially the same degree can be realized with a lower back pressure, and the efficiency of the expander can be improved.
  • the suction volume 1.8 of the first expansion chamber 40a is smaller than the suction volume 2.2 of the second expansion chamber 40b.
  • the suction volume in the state 3 is designed corresponding to the discharge volume of each expansion chamber, and the expansion ratio of the expansion chamber 40a and the expansion ratio of the expansion chamber 40b are equal to each other.
  • “equal” is not necessarily limited to an exactly equal configuration, and may be within an error range of ⁇ 10% based on, for example, a smaller expansion ratio.
  • the ECU 8 opens and closes each subport valve in order to increase or decrease the suction volume of the expander 100 as appropriate according to the operating state of the expander 100. Note that the conditions for triggering the opening / closing operation can be determined as appropriate by those skilled in the art, and a specific description thereof will be omitted.
  • the ECU 8 increases the suction volume of the expander 100, that is, when one of the subport valves is opened, the subport valve provided in the smaller one of the two expansion chambers immediately before the opening / closing operation is opened.
  • the suction volume of the first expansion chamber 40a is smaller in the state 1
  • the first subport valve is opened when shifting from the state 1 to the state 2.
  • the second expansion chamber 40b has a smaller suction volume, so the second subport valve is opened when shifting from the state 2 to the state 3.
  • the ECU 8 decreases the suction volume of the expander 100, that is, when one of the subport valves is closed, the subport valve provided in the larger one of the two expansion chambers immediately before the opening / closing operation. Close.
  • the second expansion chamber 40b has a larger suction volume. Therefore, when the state 3 is shifted to the state 2, the second subport valve is closed.
  • the first expansion chamber 40a has a larger suction volume. Therefore, when the state 2 is shifted to the state 1, the first subport valve is closed.
  • the expansion chamber 40a and the expansion chamber 40b have different suction volumes regardless of the open / closed state of each subport valve.
  • the expander 100 when the suction volume is increased, the expansion chamber having a small suction volume is expanded, and when the suction volume is decreased, the suction volume is reduced. Shrink large expansion chamber. As a result, the degree of unbalance between the suction volumes in the two expansion chambers can be kept relatively small, the required back pressure can be reduced, and the efficiency of the expander can be improved.
  • the sub suction port is provided at a position where the suction volume is doubled by opening the sub suction port.
  • the position of the sub suction port is not limited to this.
  • an operation of “increase the smaller one when increasing the suction volume and reduce the larger one when decreasing the suction volume” is performed. However, this need not be performed for every opening and closing operation. If the opening / closing operation is performed at least once, the effect of the present invention can be obtained for that portion. For example, when the suction volume is increased, control is performed from state 1 to state 3 via state 2 as in the first embodiment, while when the suction volume is decreased, the reference state is changed from state 3. Control may be performed to transition to the state 1 via, or control may be performed to transition directly to the state 1 by closing both subport valves simultaneously from the state 3.
  • the expansion chamber 40a and the expansion chamber 40b have different suction volumes regardless of the open / closed state of each subport valve.
  • the suction volumes of the expansion chamber 40a and the expansion chamber 40b may be equal depending on the open / closed state of each subport valve.
  • the suction volumes may be different when all subport valves are closed or when all subport valves are open. Even in such a case, the control according to the present invention can be performed in a state where the suction volumes are different.
  • the number of sub suction ports is two, but the number of sub suction ports may be one or three or more.
  • the control state of the expander is only two states corresponding to the state 1 and the state 2 in FIG. 5, or 2 corresponding to the state 2 and the state 3 in FIG. There will be only one state. In any case, this corresponds to the control described in the first embodiment: “when the suction volume is increased, the smaller one is enlarged, and when the suction volume is reduced, the larger one is reduced”.
  • the plurality of sub-suction ports may be simultaneously opened and closed by one valve body for a part of the plurality of sub-suction ports.
  • a plurality of subport valves may be provided in each expansion chamber.
  • the position and shape of these subport valves may be designed in any way, but for example, they can be arranged so that the magnitude relationship of the suction volume of each expansion chamber is reversed each time one subport valve is opened.
  • a specific example of control in such a configuration is as follows. With all subport valves closed, first the first subport valve of the first expansion chamber is opened, then the first subport valve of the second expansion chamber is opened, and then the second subport valve of the first expansion chamber is opened. The subport valve is opened, then the second subport valve of the second expansion chamber is opened, and the subport valves are alternately opened in the same manner.
  • the expander 100 may be configured only by the expansion unit 101 and may not include the power generation unit 102.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un mécanisme de détente à volute de capacité variable, où la contre-pression requise peut être réduite pour améliorer l'efficacité. Des chambres de détente (40a, 40b) sont dotées de sous-orifices d'admission (31a, 31b) respectifs. Les sous-orifices d'admission (31a, 31b) sont dotés de soupapes de sous-orifice correspondantes respectives. Lorsque le volume d'admission doit augmenter, une unité de calcul électronique (8) ouvre la soupape de sous-orifice de la chambre de détente ayant un volume d'admission inférieur afin d'augmenter le volume d'admission, et lorsque le volume d'admission doit être réduit, l'unité de calcul électronique (8) ferme la soupape de sous-orifice de la chambre de détente ayant un volume d'admission supérieur afin de réduire le volume d'admission.
PCT/JP2012/077754 2011-12-05 2012-10-26 Mécanisme de détente à volute WO2013084618A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011265761A JP2013117207A (ja) 2011-12-05 2011-12-05 スクロール膨張機
JP2011-265761 2011-12-05

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WO2013084618A1 true WO2013084618A1 (fr) 2013-06-13

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005030386A (ja) * 2003-06-20 2005-02-03 Denso Corp 流体機械
JP2008106668A (ja) * 2006-10-25 2008-05-08 Matsushita Electric Ind Co Ltd 膨張機、膨張機一体型圧縮機、およびそれを用いた冷凍サイクル装置
WO2008072575A1 (fr) * 2006-12-08 2008-06-19 Daikin Industries, Ltd. Appareil de congélation et détendeur

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005030386A (ja) * 2003-06-20 2005-02-03 Denso Corp 流体機械
JP2008106668A (ja) * 2006-10-25 2008-05-08 Matsushita Electric Ind Co Ltd 膨張機、膨張機一体型圧縮機、およびそれを用いた冷凍サイクル装置
WO2008072575A1 (fr) * 2006-12-08 2008-06-19 Daikin Industries, Ltd. Appareil de congélation et détendeur

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