WO2012144308A1 - Expanseur à vis - Google Patents

Expanseur à vis Download PDF

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Publication number
WO2012144308A1
WO2012144308A1 PCT/JP2012/058820 JP2012058820W WO2012144308A1 WO 2012144308 A1 WO2012144308 A1 WO 2012144308A1 JP 2012058820 W JP2012058820 W JP 2012058820W WO 2012144308 A1 WO2012144308 A1 WO 2012144308A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow path
exhaust
exhaust pressure
pressure
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2012/058820
Other languages
English (en)
Japanese (ja)
Inventor
昇 壷井
松村　昌義
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kobe Steel Ltd
Original Assignee
Kobe Steel Ltd
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 Kobe Steel Ltd filed Critical Kobe Steel Ltd
Priority to CN201280019181.1A priority Critical patent/CN103492675B/zh
Priority to KR20137027496A priority patent/KR101511890B1/ko
Publication of WO2012144308A1 publication Critical patent/WO2012144308A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F01C20/26—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 using bypass channels
    • 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 screw expander.
  • Non-Patent Document 1 In small-scale facilities, for example, as described in Non-Patent Document 1, it is known that it is more efficient to use a screw expander instead of a turbine.
  • the ratio of the volume during expansion and the volume during exhaust of an expansion space obtained by dividing the space in the rotor chamber by the screw rotor is determined by the mechanical shape.
  • the internal expansion ratio which is the ratio between the pressure in the expansion space at the time of isolation (at the start of expansion) and the pressure in the expansion space at the time of communication with the exhaust flow path (at the completion of expansion), is constant.
  • Non-Patent Document 1 when the internal expansion ratio of the screw expander does not coincide with the operation expansion ratio that is the ratio of the pressure on the air supply side and the pressure on the exhaust side, the loss is reduced. Arise. Specifically, in the screw expander, when the internal expansion ratio is larger than the operation expansion ratio and the pressure in the expansion space at the completion of expansion is lower than the pressure in the exhaust passage, the rotational force of the screw rotor is reduced. A negative force (negative work) acts to reduce the loss.
  • Patent Document 1 As a means for adjusting the internal expansion ratio of the screw expander, there is a method of changing the exhaust position by a slide valve as described in Patent Document 1. However, Patent Document 1 does not clarify in detail how to adjust the slide valve based on what information can reduce the loss caused by the mismatch between the internal expansion ratio and the operation expansion ratio.
  • the supply pressure of the screw expander is the amount of heat (exhaust heat) of the working medium body such as surplus steam supplied to the evaporator disposed upstream of the screw expander.
  • the exhaust pressure of the screw expander is determined largely depending on the amount of heat (cold heat) of the cooling medium such as cooling water supplied to the condenser disposed downstream of the screw expander. Is done. Therefore, the binary power generation system has a problem that a loss caused by the mismatch between the internal expansion ratio and the operation expansion ratio is likely to occur.
  • the present invention has a loss caused by a mismatch between the internal expansion ratio and the operation expansion ratio, particularly a loss caused when the pressure in the expansion space when the expansion is completed is lower than the pressure in the exhaust passage. It is an object to provide a screw expander that can be reduced.
  • a screw expander accommodates a pair of male and female screw rotors that mesh with each other in a rotor chamber formed in a casing, and divides the space in the rotor chamber by the screw rotor.
  • An expansion space whose volume increases with the rotation of the screw rotor is formed, a high-pressure gas is supplied to the expansion space from an air supply passage, and the gas is expanded in the expansion space to rotate the screw rotor.
  • a screw expander that exhausts the low-pressure gas expanded in the exhaust flow path, and an internal exhaust pressure detector that detects the pressure in the expansion space immediately before communicating with the exhaust flow path; and An operating exhaust pressure detector for detecting pressure; the expansion space at a position that can be isolated from the air supply flow path and the exhaust flow path; and The valve mechanism based on a bypass flow path communicating with an air flow path, a valve mechanism capable of blocking the bypass flow path, a detection value of the internal exhaust pressure detection means, and a detection value of the operating exhaust pressure detection means And the control device closes the bypass flow path to the valve mechanism when the detected value of the internal exhaust pressure detecting means is equal to or higher than the detected value of the operating exhaust pressure detecting means. When the detected value of the internal exhaust pressure detecting means is smaller than the detected value of the operating exhaust pressure detecting means, the bypass mechanism is opened by the valve mechanism.
  • the detection value of the internal exhaust pressure detection means is greater than the detection value of the operating exhaust pressure detection means. Is smaller than the operating expansion ratio, the gas is excessively expanded. In that case, by opening the bypass channel, high-pressure gas is supplied from the air supply channel to the expansion space whose volume is larger than the position communicating with the air supply channel, and the internal expansion ratio is substantially reduced. Let This reduces the loss caused by the difference between the internal expansion ratio and the operating expansion ratio.
  • the valve mechanism has a functional end surface communicating with the expansion space and the bypass flow path, and the air supply flow path is provided via an air supply valve on the side opposite to the functional end face.
  • a columnar space that communicates with the exhaust flow path via an exhaust valve, and is fitted in the columnar space and abuts against the functional end surface to isolate the expansion space and the bypass flow path.
  • the control device when the detected value of the internal exhaust pressure detecting means is equal to or higher than the detected value of the operating exhaust pressure detecting means, opens the air supply valve and closes the exhaust valve, When the detected value of the internal exhaust pressure detecting means is smaller than the detected value of the operating exhaust pressure detecting means, the air supply valve may be closed and the exhaust valve opened.
  • valve mechanism since the valve mechanism is driven by the pressure of the air supply passage and the pressure of the exhaust passage, a drive source for the valve mechanism is unnecessary.
  • the functional end surface may be opened at a margin of an air supply side end surface of the rotor chamber.
  • valve mechanism can be incorporated relatively easily into a casing having a general divided configuration, and the screw expander does not increase in size.
  • FIG. 2 is a partial cross-sectional view in the direction perpendicular to the axis of the screw expander of FIG. 1.
  • FIG. 2 is a development view of the screw rotor when the valve mechanism of the screw expander of FIG. 1 is closed. It is a screw rotor expansion
  • It is a block diagram of the binary electric power generation system which has the screw expander of FIG. It is a block diagram of the binary power generation system which has the screw expander of 2nd Embodiment of this invention.
  • FIG. 1 the screw expander 1 which is 1st Embodiment of this invention is shown.
  • the screw expander 1 has an expander body 6 in which a pair of male and female screw rotors 4 and 5 that mesh with each other are housed in a rotor chamber 3 formed in a casing 2. High pressure gas is supplied to the rotor chamber 3 from an air supply flow path 8 to which an external flow path 7 is connected. Then, gas is exhausted from the rotor chamber 3 through the exhaust passage 9.
  • the screw rotors 4 and 5 partition the space in the rotor chamber 3 by their teeth, and define a plurality of expansion spaces between the supply air flow path 8 and the exhaust flow path 9.
  • the volume of the expansion space gradually increases from the air supply flow path 8 toward the exhaust flow path 9 as the screw rotors 4 and 5 rotate. For this reason, the high-pressure gas supplied from the air supply flow path 8 to the expansion space expands in the expansion space, thereby rotating the screw rotors 4 and 5. Therefore, the gas with reduced pressure is exhausted into the exhaust passage 9.
  • a valve mechanism 10 is formed at a portion that seals the air supply side end face of the rotor chamber 3 of the casing 2.
  • the valve mechanism 10 includes a columnar space 11 formed in the casing 2 so as to open to the edge of the rotor chamber 3 and a piston 12 slidably fitted in the columnar space 11.
  • the end face that opens to the rotor chamber 3 in the columnar space 11 is referred to as a functional end face 11a.
  • the functional end surface 11a opens to the expansion space, and also opens to the bypass flow path 13 formed by extending in the axial direction on the casing 2 radially outside the rotor chamber 3.
  • the expansion space and the bypass channel 13 communicate with each other via the columnar space 11, but are isolated by the piston 12 being in close contact with the functional end surface 11a.
  • the bypass channel 13 is connected to the air supply channel 8 by being connected to the external channel 7 via the connection channel 14. That is, the bypass flow path 13 communicates the air supply flow path 8 and the expansion space at a position that can be isolated from the air supply flow path 8, but can be blocked by the valve mechanism 10.
  • the columnar space 11 is connected to the operation flow path 15 in the driving portion 11b on the side opposite to the functional end surface 11a.
  • the operation channel 15 includes a high pressure channel 17 that communicates with the connection channel 14 (and thus the supply channel 8) via the air supply valve 16, and a low pressure channel that communicates with the exhaust channel 9 via the exhaust valve 18. 19 is connected.
  • FIG. 2 shows a cross section in the direction perpendicular to the axis of the screw expander 1 at the air supply side end face of the rotor chamber 3.
  • the compression space in which the columnar space 11 communicates is a space in the tooth gap that is isolated from the air supply flow path 8 by the teeth of the screw rotor 5.
  • the compression space in which the columnar space 11 communicates can communicate with the air supply flow path 8 depending on the rotation angle of the screw rotor 5.
  • the screw expander 1 includes an internal exhaust pressure detector 20 that detects the pressure (internal exhaust pressure Pf) in the expansion space immediately before communicating with the exhaust flow path 9, and an exhaust flow path 9.
  • An operating exhaust pressure detector 21 that substantially detects the pressure of the exhaust passage 9 (operating exhaust pressure Pd) in the communicating low pressure passage 19, a detected value Pf of the internal exhaust pressure detector 20, and an operating exhaust pressure detector 21.
  • a control device 22 for controlling the opening and closing of the intake valve 15 and the exhaust valve 18.
  • a supply pressure detector 23 for detecting the pressure in the connection flow path 14, that is, the supply pressure Ps which is substantially the pressure in the supply flow path 8 is illustrated.
  • the operation exhaust pressure detector 21 may be provided in the exhaust passage 9 or a passage connected to the exhaust passage 9.
  • the internal exhaust pressure Pf depends on the supply air pressure Ps, the ratio of the instantaneous expansion space volume connected to the exhaust flow passage 9 to the instantaneous expansion space volume isolated from the supply air flow passage 8, and the physical properties of the gas. It is determined. On the other hand, the operating exhaust pressure Pd becomes equal to the pressure in the external flow path connected to the exhaust flow path 9.
  • the control device 22 closes the air supply valve 16 and opens the exhaust valve 18 when the detection value Pf of the internal exhaust pressure detector 20 is smaller than the detection value Pd of the operation exhaust pressure detector 21. Then, the pressure in the drive portion 11b of the columnar space 11 becomes equal to the exhaust pressure Pd, and the bypass passage 13 having the same pressure Ps as the air supply passage 8 and the same pressure Ps or gas as the air supply passage 8 are slightly expanded.
  • the pressure is lower than the pressure of the functional end surface 11a communicating with the expansion space having a pressure slightly lower than Ps.
  • the piston 12 moves in the direction away from the functional end surface 11a, ensures communication between the bypass flow path 13 and the expansion space, and allows gas to flow from the bypass flow path 13 into the expansion space. Then, even when the expansion space is isolated from the supply air flow path 8 by the teeth of the screw rotor 5, the pressure in the expansion space is maintained at the supply air pressure Ps.
  • the control device 22 opens the air supply valve 16 and closes the exhaust valve 18 when the detection value Pf of the internal exhaust pressure detector 20 is equal to or greater than the detection value Pd of the operation exhaust pressure detector 21. Then, the pressure of the drive unit 11b in the columnar space 11 becomes equal to the supply air pressure Ps.
  • the expansion space is isolated from the supply air flow path 8 by the teeth of the screw rotor 5, the gas in the expansion space is slightly expanded and the pressure is reduced from the supply air pressure Ps. Thereby, the pressure on the functional end surface 11a side of the columnar space 11 is slightly lower than the pressure on the drive unit 11b side, and the piston 12 is moved toward the functional end surface 11a.
  • the piston 12 abuts on the functional end surface 11a, the piston 12 seals the functional end surface 11a and isolates the bypass flow path 13 and the expansion space. Thereby, the screw expander 1 becomes the same structure as the normal expander without the bypass flow path 13.
  • FIG. 3 is a development view of the screw rotors 4 and 5 in a state in which the valve mechanism 10 is closed (the functional end surface 11a is sealed with the piston 12).
  • the gas having the air supply pressure Ps is supplied to the tooth grooves of the screw rotors 4 and 5.
  • the tooth gap volume Vs1 at the moment when the tooth grooves of the screw rotors 4 and 5 are separated from the air supply flow path 8 by the casing 2 is the volume at which the gas of the pressure Ps starts to expand in the screw expander 1.
  • the volume Vd of the tooth gap at the moment when it is released from the casing 2 on the discharge side and communicates with the exhaust passage 9 is the volume at the time when the gas ends the expansion.
  • FIG. 4 is a development view of the screw rotors 4 and 5 in a state where the valve mechanism 10 is opened (the piston 12 is moved to the drive unit 11b side).
  • the gas at the supply air pressure Ps is supplied to the tooth groove communicating with the valve mechanism 10 via the bypass flow path 13. That is, when the valve mechanism 10 is opened, there is substantially the same effect as expanding the air supply passage 8. Therefore, the instant tooth gap volume Vs2 isolated from the valve mechanism 10 is the volume at which the gas of the pressure Ps starts to expand in the screw expander 1.
  • the volume Vd when the gas finishes expanding is the same as when the valve mechanism 10 is closed.
  • the valve mechanism 10 is opened to substantially expand the supply air flow path 8.
  • the internal expansion ratio is reduced.
  • the internal exhaust pressure Pf is made higher than the operation exhaust pressure Pd, and loss caused by recompressing the gas when flowing out from the expansion space into the exhaust passage 9 is prevented. That is, the internal expansion ratio ⁇ i is brought close to the operation expansion ratio Ps / Pd to increase the conversion efficiency of thermal energy into rotational energy.
  • the apparatus since the screw expander 1 changes the internal expansion ratio ⁇ i by the simple valve mechanism 10, the apparatus does not become large and can be provided at a relatively low cost.
  • FIG. 5 shows a configuration of a binary power generation system using the screw expander 1 of the present embodiment.
  • the binary power generation system includes a Rankine cycle heat engine in which a working medium circulation channel 27 including a screw expander 1, a condenser 24, a pump 25, and an evaporator 26 is sealed with a working medium such as R245fa. It is.
  • a part of the working medium circulation flow path 27 is the external flow path 7 at the upstream side of the screw expander 1.
  • a generator 28 is connected to the output shaft of the screw expander 1.
  • the condenser 24 is a heat exchanger that cools and condenses the low-pressure working medium exhausted from the screw expander 1 with a cooling medium supplied from the outside (for example, inexpensive cooling water supplied from a river or a cooling tower). It is.
  • the pump 25 pressurizes the working medium that has become liquid in the condenser 24 and supplies the pressurized working medium to the evaporator 26.
  • the evaporator 26 is heated and evaporated by a heating medium (for example, steam collected from a well or steam produced by a boiler) supplied from the outside.
  • the working medium evaporated in the evaporator 26 into a high-pressure gas is supplied to the screw expander 1 and drives the screw expander 1.
  • the binary power generation system generates power by turning the generator 28 by the rotational force of the screw expander 1.
  • the screw expander 1 operates the valve mechanism 10 to expand Since the loss caused by recompressing the working medium when flowing out from the space to the exhaust passage 9 is prevented, the power generation efficiency can be kept high.
  • FIG. 6 shows a binary power generation system having the screw expander 1a of the second embodiment of the present invention.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
  • the screw expander 1a includes two expander bodies 6a and 6b connected in series.
  • the bypass passages 13a and 13b that connect the expansion space at a position that can be isolated from the air supply passages of the expander main bodies 6a and 6b and the air supply passage are configured by external piping
  • the valve mechanisms 10 a and 10 b that can block 13 b are motor valves that are provided in external piping and can be driven by the control voltage of the control device 22.
  • the screw expander 1a includes a first-stage internal exhaust pressure detector 20a that detects a pressure Pf1 in the expansion space immediately before communicating with the exhaust passage of the first-stage expander body 6a, and a first-stage expander.
  • a first stage operation exhaust pressure detector 21a that detects the pressure (intermediate pressure Pm) in the intermediate pressure flow path 29 that is the operation exhaust pressure of the main body 6a and is also the supply pressure of the second stage expander body 6b;
  • a second-stage internal exhaust pressure detector 20b that detects the pressure Pf2 in the expansion space immediately before communicating with the exhaust flow path of the second-stage expander body 6b, and immediately after the exhaust flow path of the second-stage expander body 6b.
  • the working medium circulation passage 27 has a second-stage operation exhaust pressure detector 21b that substantially detects the operation exhaust pressure Pd of the second-stage expander body 6b.
  • the control device 22 of the present embodiment closes the valve mechanism 10a.
  • the valve mechanism 10a is opened and the internal expansion of the first-stage compressor body 6a is performed. Reduce the ratio.
  • the control device 22 closes the valve mechanism 10b and sets the second stage.
  • the valve mechanism 10b is opened and the internal expansion ratio of the second stage compressor body 6b is set. Reduce.
  • the present invention can be applied not only to a screw expander configured with a single-stage expander body but also to a screw expander configured with a two-stage expander body. Moreover, if the screw expander of this invention is used, the power generation efficiency of a binary power generation device can be improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

Afin de réduire la perte due à une différence entre un taux de détente interne et un taux de détente opérationnel, un expanseur à vis (1) selon l'invention comporte : un détecteur de pression de gaz de refoulement interne (20) permettant de détecter la pression (Pf) dans un espace de dilatation mesurée immédiatement avant que l'espace de dilatation soit connecté à un canal de refoulement de gaz (9) ; un détecteur de pression de gaz de refoulement de fonctionnement (21) permettant de détecter la pression (Pd) au sein du canal de refoulement de gaz (9) ; un canal de dérivation (13) permettant de connecter un canal d'alimentation en gaz (8) et l'espace de dilatation situé à une position à laquelle l'espace de dilatation peut être séparé du canal d'alimentation en gaz (8) et du canal de refoulement de gaz (9) ; un mécanisme de soupape (10) qui peut fermer le canal de dérivation (13) ; et un dispositif de commande (22) qui ferme le mécanisme de soupape (10) lorsqu'une valeur de détection (Pf) détectée par le moyen de détection de pression de gaz de refoulement interne (20) est supérieure ou égale à une valeur de détection (Pd) détectée par le moyen de détection de pression de gaz de refoulement de fonctionnement (21), et qui ouvre le mécanisme de soupape (10) lorsque la valeur de détection (Pf) détectée par le moyen de détection de pression de gaz de refoulement interne (20) est inférieure à la valeur de détection (Pd) détectée par le moyen de détection de pression de gaz de refoulement de fonctionnement (21).
PCT/JP2012/058820 2011-04-19 2012-04-02 Expanseur à vis Ceased WO2012144308A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201280019181.1A CN103492675B (zh) 2011-04-19 2012-04-02 螺杆膨胀机
KR20137027496A KR101511890B1 (ko) 2011-04-19 2012-04-02 스크류 팽창기

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011093019A JP5597589B2 (ja) 2011-04-19 2011-04-19 スクリュ膨張機
JP2011-093019 2011-04-19

Publications (1)

Publication Number Publication Date
WO2012144308A1 true WO2012144308A1 (fr) 2012-10-26

Family

ID=47041423

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/058820 Ceased WO2012144308A1 (fr) 2011-04-19 2012-04-02 Expanseur à vis

Country Status (4)

Country Link
JP (1) JP5597589B2 (fr)
KR (1) KR101511890B1 (fr)
CN (1) CN103492675B (fr)
WO (1) WO2012144308A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015100364A (ja) * 2013-11-20 2015-06-04 株式会社大一商会 遊技機
JP6403271B2 (ja) * 2015-03-23 2018-10-10 株式会社神戸製鋼所 熱回収型発電システム
JP6403282B2 (ja) * 2015-09-11 2018-10-10 株式会社神戸製鋼所 熱エネルギー回収装置
TWI658199B (zh) 2017-06-23 2019-05-01 復盛股份有限公司 螺旋式膨脹機
JP2020045864A (ja) * 2018-09-20 2020-03-26 株式会社神戸製鋼所 膨張機およびバイナリ発電装置
CN111058898B (zh) * 2019-12-10 2021-12-14 泰能天然气有限公司 一种螺杆膨胀机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61122301U (fr) * 1985-01-18 1986-08-01
JPS6260902A (ja) * 1985-09-10 1987-03-17 Kobe Steel Ltd サイドストリ−ム付スライド弁形スクリユ膨張機
JP2006046223A (ja) * 2004-08-05 2006-02-16 Daikin Ind Ltd スクロール型膨張機
WO2007052510A1 (fr) * 2005-10-31 2007-05-10 Matsushita Electric Industrial Co., Ltd. Expanseur et pompe de chaleur l'utilisant
JP2007522389A (ja) * 2004-02-17 2007-08-09 スベンスカ・ロツタア・マスキナア・アクチボラグ エキスパンダを介する流量の制御方法及び手段
JP2009133319A (ja) * 2009-03-03 2009-06-18 Daikin Ind Ltd 容積型膨張機及び流体機械

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0228599D0 (en) * 2002-12-07 2003-01-15 Energetix Group Ltd Electrical power supply system
JP4946840B2 (ja) * 2006-12-08 2012-06-06 ダイキン工業株式会社 冷凍装置
JP4353311B1 (ja) * 2008-08-08 2009-10-28 三浦工業株式会社 蒸気システム

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61122301U (fr) * 1985-01-18 1986-08-01
JPS6260902A (ja) * 1985-09-10 1987-03-17 Kobe Steel Ltd サイドストリ−ム付スライド弁形スクリユ膨張機
JP2007522389A (ja) * 2004-02-17 2007-08-09 スベンスカ・ロツタア・マスキナア・アクチボラグ エキスパンダを介する流量の制御方法及び手段
JP2006046223A (ja) * 2004-08-05 2006-02-16 Daikin Ind Ltd スクロール型膨張機
WO2007052510A1 (fr) * 2005-10-31 2007-05-10 Matsushita Electric Industrial Co., Ltd. Expanseur et pompe de chaleur l'utilisant
JP2009133319A (ja) * 2009-03-03 2009-06-18 Daikin Ind Ltd 容積型膨張機及び流体機械

Also Published As

Publication number Publication date
KR20130137684A (ko) 2013-12-17
CN103492675A (zh) 2014-01-01
JP5597589B2 (ja) 2014-10-01
CN103492675B (zh) 2015-08-19
JP2012225241A (ja) 2012-11-15
KR101511890B1 (ko) 2015-04-13

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