WO1996028699A1 - Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration - Google Patents

Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration Download PDF

Info

Publication number
WO1996028699A1
WO1996028699A1 PCT/JP1995/000399 JP9500399W WO9628699A1 WO 1996028699 A1 WO1996028699 A1 WO 1996028699A1 JP 9500399 W JP9500399 W JP 9500399W WO 9628699 A1 WO9628699 A1 WO 9628699A1
Authority
WO
WIPO (PCT)
Prior art keywords
temperature
chilled water
chiller
compression
absorption
Prior art date
Application number
PCT/JP1995/000399
Other languages
English (en)
Japanese (ja)
Inventor
Ryohei Minowa
Kenichi Kuwabara
Shuichiro Uchida
Original Assignee
Hitachi, 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 Hitachi, Ltd. filed Critical Hitachi, Ltd.
Priority to PCT/JP1995/000399 priority Critical patent/WO1996028699A1/fr
Priority to JP08527435A priority patent/JP3125796B2/ja
Priority to KR1019970706268A priority patent/KR100307071B1/ko
Publication of WO1996028699A1 publication Critical patent/WO1996028699A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/02—Compression-sorption machines, plants, or systems

Definitions

  • the present invention relates to a chilled water production apparatus and a method for controlling the refrigeration capacity thereof, and more particularly to an apparatus S for producing chilled water by combining a compression refrigerator and an absorption refrigerator.
  • the temperature difference between the cooling water and the cooling water of the compression refrigerator is the same as when the compression refrigerator is used alone, and the operation method is such that the absorption refrigerator and the compression refrigerator are flowed in series.
  • the power consumption per unit cooling capacity of the compression refrigerator does not decrease.
  • the absorption chiller is located on the side where the chilled water temperature is high, so the amount of ripening per unit cooling capacity is reduced, but as shown in Fig. 4, the reduction rate is smaller than that of the compression chiller.
  • the operation is small and responds to the beak load, and the operation time is short.
  • An object of the present invention is to provide a chilled water production apparatus S that combines a compression chiller and an absorption chiller to achieve energy saving and low operating cost, and a method for controlling the refrigeration capacity thereof.
  • a first feature of the present invention is that a compressor, a condenser, and an evaporator are connected by a refrigerant pipe to form a refrigerating cycle; It has an absorption-type refrigerator in which a refrigeration cycle is constructed by connecting an absorber, a condenser, and a regenerator by pipes and flow paths. The two refrigerators are connected in series by chilled water piping.
  • a chilled water production system in which chilled water flows in the order of a compression chiller and an absorption chiller, means for detecting the temperature of the chilled water at the inlet of the absorption chiller, and compression refrigeration based on the load of the absorption chiller
  • Control means for setting the temperature of the cold water so as to increase the load on the refrigerator, and controlling the refrigerating capacities of the two refrigerators so that the temperature of the cold water detected by the means becomes the set temperature. Is to have.
  • a second feature of the present invention is that a compressor, a condenser, and an evaporator are connected by a refrigerant pipe to form a refrigerating cycle, And an absorption refrigerator in which a refrigeration cycle is configured by connecting a chiller, an absorber, a condenser, and a regenerator with piping and flow paths, and connecting the two chillers in series with chilled water piping.
  • the chilled water flows in the order of a compression chiller and an absorption chiller
  • the compression chiller comprises: a means for detecting a chilled water outlet temperature of the compression chiller; Control means for controlling the refrigeration capacity of the compression chiller so that the detected chilled water outlet temperature becomes a set temperature at which the load on the compression chiller becomes greater than the load on the absorption chiller.
  • the absorption refrigerator has means for detecting a chilled water inlet temperature of the absorption chiller, and the chilled water inlet temperature detected by the means is more effective for the load of the compression chiller than the load of the absorption chiller. Cool the absorption refrigerator so that the set temperature increases. In that a control means for controlling the capacity.
  • a third feature of the present invention is that a compressor, a condenser, and an evaporator are connected to each other by a refrigerant pipe to form a refrigeration cycle, and that an evaporator, an absorber, and a condenser are provided. And a regenerator connected by pipes and channels to form a refrigerating cycle.
  • the two refrigerating machines are connected in series by a chilled water pipe so that the chilled water is compressed by a refrigeration cycle.
  • the compression chiller includes a means for detecting a chilled water outlet temperature of the compression chiller, and a chilled water outlet temperature detected by the means.
  • Control means for controlling the refrigeration capacity of the compression chiller so that the set temperature is such that the load on the compression chiller is greater than the load on the absorption chiller.
  • a means to detect the chilled water inlet temperature of an absorption refrigerator The refrigeration capacity of the absorption chiller is controlled so that the chilled water inlet temperature detected by this means becomes a set temperature that makes the load of the compression chiller larger than the load of the absorption chiller.
  • a fourth feature of the present invention is that a compressor, a condenser, and an evaporator are connected to each other by a refrigerant pipe to constitute a refrigeration cycle; And an absorption refrigerator in which a refrigeration cycle is configured by connecting a condenser, a condenser, and a regenerator by piping and flow paths, and connecting both refrigerators in series by a chilled water pipe.
  • a refrigeration cycle is configured by connecting a condenser, a condenser, and a regenerator by piping and flow paths, and connecting both refrigerators in series by a chilled water pipe.
  • the configuration is such that the chilled water used for cooling flows in the order of the compression chiller and the absorption chiller, and then to the air-conditioning load.
  • the temperature of the chilled water at the compression chiller outlet (chilled water at the absorption chiller inlet) is detected, and both chillers are controlled so that the detected temperature becomes the set temperature.
  • the temperature is set so that the load of the chiller is always greater than the load of the absorption chiller.
  • compression chillers use electricity, but electricity rates tend to fall sharply as usage increases.
  • the compression type refrigerator is used in preference to the absorption type refrigerator. The combined overall operating cost can be reduced.
  • the air-conditioning load changes approximately in proportion to the atmospheric temperature.
  • the cooling water that receives waste heat from the refrigerator is cooled by a cooling tower, so the cooling water inlet temperature of the refrigerator is also the atmospheric temperature. Up and down according to. Therefore, the cooling water inlet temperature of the refrigerator has the characteristic that it rises and falls according to the air conditioning load.
  • the cooling water inlet temperature of the refrigerator has the characteristic that it rises and falls according to the air conditioning load.
  • the present invention having the third feature described above, when the air load is reduced, the chilled water intermediate between the compression chiller and the absorption chiller according to the cooling water inlet or outlet temperature of the compression chiller. Since the temperature is controlled so as to decrease, the compression chiller can be used for full-load long-term rotation, and the absorption chiller can be used for short-time peak load.
  • compression chillers are operated by electricity, and absorption chillers are operated by gas.Thus, such compression chillers are operated at full load for a long time, and the compression chillers are given priority. By using this, the cost of driving can be kept low.
  • FIG. 1 is a system diagram of a cold water production apparatus according to one embodiment of the present invention.
  • FIG. 2 is a system diagram of a cold water producing apparatus according to another embodiment of the present invention.
  • FIG. 3 is a system diagram of a cold water producing apparatus according to still another embodiment of the present invention.
  • FIG. 4 is a graph showing a relationship between a temperature drop and an input to a refrigerator.
  • Fig. 5 is a graph showing the relationship between the operating point and the surging point of the turbo compressor.
  • FIG. 6 is a graph showing the relationship between the operating point and efficiency of the turbo compressor.
  • FIG. 7 is a graph showing the relationship between load sharing between a compression refrigerator and an absorption refrigerator and chilled water temperature.
  • Fig. 8 is a graph showing the relationship between cooling energy unit price and operation time.
  • chilled water is flowed in series in the order of the compression chiller and the absorption chiller, and the temperature of the chilled water between the compression chiller and the absorption chiller is detected. If each chiller is controlled so that the cooling water temperature is constant, the compression chiller controls the chilled water outlet temperature to be constant, which is the same as the control of a general chiller, and if the cooling water temperature is below the design specification, The compression ratio of the compressor of the compression refrigerator does not become excessive. Also, when the outside air temperature is not as high as in summer and the cooling water temperature drops in the middle period, etc., the set temperature of the controller that controls the compression chiller is adjusted according to the temperature difference from the specified cooling water temperature. Even if it is lowered, the compression ratio of the compressor can be kept below the design value, so that safe and stable operation can be achieved.
  • the load is first applied to the compression chiller, and it cannot be cooled by the compression chiller. If the chilled water outlet temperature of the compression chiller exceeds the set temperature of the control device, the absorption The control device of the refrigerator is activated, and a load is applied to the absorption refrigerator.
  • the absorption chiller When the load is small, only the compression chiller is operated, and when the load increases and the output of the compression chiller reaches 100%, the absorption chiller is started and the output of the compression chiller is reduced to 10%. When it is fixed to 0%, the compression chiller runs at full load, and the shortfall is compensated for by the absorption chiller. Actually, there is a minimum refrigeration capacity at which the absorption chiller can be operated continuously. If the opening of the fuel control system of the absorption chiller or the output of the control device is less than the minimum capacity, the compression chiller will not operate. Activate the control device and adjust the capacity of the two refrigerators to match the load. The load increases, the output of the compression refrigerator becomes 100%, and the output of the absorption refrigerator becomes the minimum capacity. At this point, the output of the compression refrigerator is fixed at 100%, and the control unit S of the absorption refrigerator is operated to an output corresponding to the load, so that the load is It is called.
  • 1 is the evaporator of the compression refrigerator
  • 2 is the compressor
  • 3 is the electric motor
  • 4 is the condenser of the compression refrigerator
  • 5 is the compressor gas control vane flowing into the compressor
  • 6 is the control.
  • Vane drive unit 7 is a refrigerant expansion valve of a compression refrigerator
  • 8 is an evaporator of an absorption refrigerator
  • 9 is an absorber of an absorption refrigerator
  • 10 is a condenser of an absorption refrigerator
  • 1 1 is a regenerator for an absorption refrigerator
  • 1 is a fuel control valve
  • 13 is a fuel control valve drive
  • 14 is a fuel pipe
  • 15 is cooling water for a compression refrigerator
  • 16 is a cooling system inlet.
  • Chilled water 17 is intermediate temperature chilled water, 18 is chilled water at the cooling unit outlet, 19 is a temperature controller for compression chillers, 20 is an absorption chiller inlet temperature controller, and 21 is an absorption chiller outlet Temperature controller, 2 2 is a compression chiller cooling water temperature controller, 2 3 is a selection calculator, 2 4 is a compression chiller chilled water outlet temperature sensor, 2 5 is an absorption chiller chilled water inlet temperature sensor, 2 6 is compression type Freezing machine cooling water inlet temperature sensor, 2 7 is an absorption refrigerator chilled water Atsushi Ideguchi sensor.
  • the chilled water at the cooling device inlet 16 first enters the evaporator 1 of the compression refrigerator, is cooled to become intermediate-temperature chilled water 17, enters the evaporator 8 of the absorption refrigerator, and is further cooled and cooled. It flows out as cold water 18 at the outlet.
  • the temperature controller 19 for the compression chiller detects the temperature of the intermediate-temperature chilled water 17 that is cooled and flows out by the compression chiller with the compression chiller chilled water outlet temperature sensor 24 and detects the refrigerant gas flowing into the compressor.
  • a control output that opens and closes the control vane 5 A control output is supplied to the drive unit 6, and the compressor inflow refrigerant gas control vane 5 operates so that the temperature of the intermediate-temperature chilled water 17 becomes the given set value. .
  • the compression vane capacity control is performed by changing the flow path cross-sectional ridge on the compressor suction side by the control vane, but by changing the compressor rotation speed, the compressor rotation speed is changed. Control can also be performed to control the capacity of the compression refrigerator.
  • the absorption chiller inlet temperature controller 20 detects the temperature of the intermediate temperature chilled water 17 with the absorption chiller chilled water inlet temperature sensor 25, and opens and closes the fuel control valve 12 of the absorption chiller.
  • the control output is supplied to the control valve drive device 13 via the arbitration calculator 23, and the fuel control valve drive device 13 operates so that the temperature of the intermediate-temperature cold water 17 becomes the given set value.
  • the absorption chiller outlet temperature controller 21 detects the temperature of the chiller outlet chilled water 18 with the absorption chiller outlet water temperature sensor 27 and selects the close signal when the temperature falls below the set temperature. Give to.
  • the selection calculator 23 compares the output signal of the absorption chiller inlet temperature controller 20 and 21 with the output signal of the absorption chiller outlet temperature meter, selects the lower signal, and 13 Give to control valve drive.
  • the compression chiller cooling water temperature controller 22 detects the inlet temperature of the compression chiller cooling water 15 with a compression chiller cooling water inlet temperature sensor 26, and the compression chiller cooling water 15
  • the set value of the temperature controller for the compression refrigerator 19 and the absorption refrigerator inlet temperature controller 20 is changed by stimulating the determined ratio to the changed value of the inlet temperature of the compressor.
  • the set value of the temperature controller for the compression refrigerator 19 that controls the intermediate temperature chilled water 17 that is the chilled water outlet temperature of the compression refrigerator to the set temperature is changed to the inlet of the cooling water 15 of the compression refrigerator.
  • turbo compressor is designed to support the compression ratio at which the compression and absorption chillers cool to the temperature of the intermediate temperature chilled water 17 when operating at full load, the characteristics of the turbo compressor will be As shown by the dotted line in Fig. 6, all negative The efficiency of the operating point D during loading greatly increases from d to d ', and the power decreases almost in proportion to the temperature drop.
  • the air-conditioning load changes roughly in proportion to the atmospheric temperature.
  • cooling water is cooled by a cooling tower, so the cooling water temperature also rises and falls with the atmospheric temperature. Therefore, when the air-conditioning load decreases and the temperature of the cooling device inlet cooling water 16 returning from the air-conditioning load side decreases, the cooling water temperature also decreases.
  • the compression chiller is always operated at almost the full load.
  • the absorption chiller detects the temperature of the intermediate-temperature chilled water 17 with the absorption chiller chilled water inlet temperature sensor 25, and uses the absorption chiller chilled water inlet temperature controller 20 so that this temperature becomes constant. Controlled. Therefore, when the load is reduced, the temperature of the chilled water 18 at the cooling device outlet rises and approaches the temperature of the intermediate-temperature chilled water 17. With such control, the absorption chiller also reduces the temperature difference between the chilled water and the chilled water, so that the driving force is reduced and energy is saved. As with the temperature controller for compression chillers 19, the set value of the absorption chiller chilled water inlet temperature controller 20 can be changed depending on the temperature of the cooling water 15 of the compression chiller.
  • the temperature of the absorption chiller cold water inlet temperature controller 20 is set to a slightly higher temperature than the set value of the machine temperature controller 19. In this case, first, the compression refrigerator becomes full load, the load is larger than the capacity of the compression refrigerator, and the temperature of the intermediate-temperature cold water 17 becomes lower than that of the compression refrigerator. After the temperature of the refrigerator temperature controller 19 becomes equal to or higher than the set value, the absorption chiller chilled water inlet temperature controller 20 operates to increase the amount of fuel flowing through the fuel piping 14 of the absorption refrigerator. The operation will be performed so as to compensate for the insufficient capacity of the compression chiller against the load.
  • the chilled water outlet temperature controller 21 of the absorption chiller detects the temperature of the chilled water at the cooling outlet S 18 with the absorption chilled water outlet temperature sensor 27, and when the temperature falls below the set value, the fuel control valve Outputs a control signal in the direction to close 1 2.
  • Selector 23 compares the output signal of the absorption chiller chilled water inlet temperature controller 20 with the output signal of the absorption chiller chilled water outlet temperature controller 21 to determine whether to close the fuel control valve 1 2.
  • FIG. 7 shows what has been described above.
  • chilled water is sent to the air conditioning load at 7 (point R) and returns from the air conditioning load at 14 ° C (point P).
  • the load is 0%
  • chilled water is sent to the air conditioning load at 8 ° C and returns from the air conditioning load at the same temperature of 8 ° C (point Z).
  • the chilled water (point P) returned at 14 ° C from the air-conditioning load is reduced by 3.5 at its maximum capacity to 10.5 ° C. Then, the absorption chiller reaches its maximum capacity of 10.5 and drops it by 3.5 to 7'C and sends it to the air conditioning load (point R).
  • the temperature of the chilled water returned from the air conditioning load becomes lower than when the load is 100% (for example, point S). Then, as in the case of 100% load, the maximum capacity of the compression chiller is lowered by about 3.5'C to the T point, and the absorption chiller is cooled to the U point by controlling the capacity of the absorption chiller. Send to load. Therefore, according to the present invention, a load is preferentially applied to the compression refrigerator.
  • the capacity is controlled only for the compression refrigerator (for example, from point X to point Y).
  • the load is applied preferentially to the compression refrigerator in the entire operation range, and the compression refrigerator operates for a long time under high load.
  • the absorption chiller will be operated only during peak load, and will be short-time operation. In places located in the middle tanning degree, such as Japan, the annual average cooling load in summer is about 40% of the peak load. Therefore, if the capacity of the compression chiller is selected to be 40% to 50% of the total capacity of the compression chiller and the absorption chiller, the compression chiller operates at about half of the annual operating time at full load. The overall efficiency will be higher.
  • FIG. 2 is a view showing another embodiment of the present invention.
  • the outlet temperature of the cooling water 15 of the compression refrigerator is detected by the compression refrigerator cooling water outlet temperature sensor 28 and controlled in the same manner as in the embodiment of FIG. 1. 19.
  • the set value of the absorption chiller chilled water inlet temperature controller 20 By changing the set value of the absorption chiller chilled water inlet temperature controller 20 according to the outlet temperature of the cooling water 15, the same effect as in the embodiment of FIG. 1 can be obtained.
  • FIG. 3 is a view showing another embodiment of the present invention.
  • An absorption chiller that uses steam as the driving source is used to control the steam flowing through the steam pipe 31 with the steam control valve 29 and the steam control valve driving device 30. The same effect as that of the embodiment shown in FIG. 1 can be obtained.
  • compression refrigeration and absorption chiller Combination of cooling and absorption chiller in this order reduces the temperature drop (cooling water inlet temperature-chilled water outlet temperature) of the compression chiller and increases the power Can be made smaller.
  • FIG. 8 is the power in the 3 0 0 RT refrigerator 1. O k WZRT, the gas is obtained by 0. Estimated assuming at 6 5 N m 3 ZRT.
  • compression chillers use electricity, but electricity rates tend to fall sharply as usage increases, so load is used by giving priority to compression chillers over absorption chillers. This can reduce the overall operating cost of both refrigerators.
  • Another characteristic is that changes in air conditioning load and cooling water temperature are linked.
  • air-conditioning load decreases, control is exercised to lower the cold water temperature between the compression and absorption chillers in accordance with the cooling water temperature of the compression chiller, so that the compression chiller operates at full load for a long time.
  • absorption chillers can be used for short-time peak load. Comparing the energy unit costs for electricity and gas, which are the energy sources of refrigerators, shows that The unit price of lug is lower than that of gas if it turns fast for a long time. It is common practice to operate a chiller refrigerator with electricity and an absorption chiller with gas. By using it, the operating cost can be kept low.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Abstract

Cette invention concerne un appareil pour la production d'eau froide par une machine réfrigérante. Dans la présente invention, l'eau froide passe dans un évaporateur (1) d'un réfrigérateur du type à compression et ensuite dans un évaporateur (8) d'un réfrigérateur du type à absorption, la température de cette eau froide à l'entrée du réfrigérateur du type à absorption est mesurée (c'est aussi la température de sortie du réfrigérateur du type à compression) et cette mesure sert à commander les deux réfrigérateurs, pour que la charge sur le réfrigérateur du type à compression soit toujours plus importante que celle sur le réfrigérateur du type à absorption. Dans cet appareil, la charge peut être appliquée de manière préférentielle à un réfrigérateur du type à compression et une économie d'énergie peut être obtenue en tirant profit des caractéristiques des réfrigérateurs respectifs.
PCT/JP1995/000399 1995-03-10 1995-03-10 Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration WO1996028699A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP1995/000399 WO1996028699A1 (fr) 1995-03-10 1995-03-10 Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration
JP08527435A JP3125796B2 (ja) 1995-03-10 1995-03-10 冷水製造装置
KR1019970706268A KR100307071B1 (ko) 1995-03-10 1995-03-10 냉수제조장치및그의냉동용량제어방법

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1995/000399 WO1996028699A1 (fr) 1995-03-10 1995-03-10 Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration

Publications (1)

Publication Number Publication Date
WO1996028699A1 true WO1996028699A1 (fr) 1996-09-19

Family

ID=14125729

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1995/000399 WO1996028699A1 (fr) 1995-03-10 1995-03-10 Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration

Country Status (3)

Country Link
JP (1) JP3125796B2 (fr)
KR (1) KR100307071B1 (fr)
WO (1) WO1996028699A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011169532A (ja) * 2010-02-19 2011-09-01 Mitsubishi Heavy Ind Ltd 冷凍機ユニットおよびその制御方法
JP2013160440A (ja) * 2012-02-06 2013-08-19 Hitachi Appliances Inc ターボ冷凍機

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5849872A (ja) * 1981-09-18 1983-03-24 株式会社日立製作所 ヒ−トポンプ装置
JPS58129172A (ja) * 1982-01-29 1983-08-02 株式会社日立製作所 冷却設備

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58129172U (ja) * 1982-02-24 1983-09-01 三菱電機株式会社 レ−ザレ−ダ装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5849872A (ja) * 1981-09-18 1983-03-24 株式会社日立製作所 ヒ−トポンプ装置
JPS58129172A (ja) * 1982-01-29 1983-08-02 株式会社日立製作所 冷却設備

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011169532A (ja) * 2010-02-19 2011-09-01 Mitsubishi Heavy Ind Ltd 冷凍機ユニットおよびその制御方法
JP2013160440A (ja) * 2012-02-06 2013-08-19 Hitachi Appliances Inc ターボ冷凍機

Also Published As

Publication number Publication date
KR100307071B1 (ko) 2001-11-17
KR19980702861A (ko) 1998-08-05
JP3125796B2 (ja) 2001-01-22

Similar Documents

Publication Publication Date Title
US4471630A (en) Cooling system having combination of compression and absorption type units
KR101383526B1 (ko) 열원 시스템
CN102865646B (zh) 空气调节器
JP3574447B2 (ja) 空気調和機の起動制御システム及びその制御方法
EP2313709B1 (fr) Refroidisseur avec réglage du point de consigne
US8701424B2 (en) Turbo chiller, heat source system, and method for controlling the same
US7721559B2 (en) Multi-type air conditioner and method for controlling the same
US20040098997A1 (en) Air conditioner and method for controlling electronic expansion valve of air conditioner
KR20080112670A (ko) 동시 냉난방형 멀티 공기조화기 및 그 제어방법
JP6788007B2 (ja) 長時間エジェクタモードで蒸気圧縮システムを制御するための方法
US20120131935A1 (en) Air conditioner and method for operating same
WO2009147826A1 (fr) Dispositif à cycle de réfrigération
CA2536757C (fr) Pompe a chaleur avec entree d'air surcomprime
US20040107709A1 (en) Method for operating compressors of air conditioner
CN110822545A (zh) 变频空调系统及其低频运行的控制方法
CN103842736A (zh) 制冷装置
JP4273493B2 (ja) 冷凍空調装置
CN211204223U (zh) 变频空调系统
JPH0827082B2 (ja) 冷凍システムの容量均衡制御システム及びその運転方法
JPH043865A (ja) 冷凍サイクル装置
WO1996028699A1 (fr) Appareil de production d'eau froide et procede pour reguler sa capacite de refrigeration
JPH11264625A (ja) 冷水製造装置及びその冷凍容量制御方法
JPH04251164A (ja) 冷凍サイクル装置
JP7080801B2 (ja) ターボ冷凍機
CN113513852A (zh) 一种冷却系统、制冷设备及冷却方法

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): CN JP KR US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): DE FR IT

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 1019970706268

Country of ref document: KR

122 Ep: pct application non-entry in european phase
WWP Wipo information: published in national office

Ref document number: 1019970706268

Country of ref document: KR

WWG Wipo information: grant in national office

Ref document number: 1019970706268

Country of ref document: KR