WO2007080994A1 - Refrigeration apparatus - Google Patents

Refrigeration apparatus Download PDF

Info

Publication number
WO2007080994A1
WO2007080994A1 PCT/JP2007/050372 JP2007050372W WO2007080994A1 WO 2007080994 A1 WO2007080994 A1 WO 2007080994A1 JP 2007050372 W JP2007050372 W JP 2007050372W WO 2007080994 A1 WO2007080994 A1 WO 2007080994A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigeration
refrigerant
refrigerators
temperature
evaporator
Prior art date
Application number
PCT/JP2007/050372
Other languages
French (fr)
Japanese (ja)
Inventor
Naoyuki Inoue
Original Assignee
Ebara Corporation
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
Priority to JP2006002977A priority Critical patent/JP5096678B2/en
Priority to JP2006-002977 priority
Application filed by Ebara Corporation filed Critical Ebara Corporation
Publication of WO2007080994A1 publication Critical patent/WO2007080994A1/en

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B1/00Compression machines, plant, or systems with non-reversible cycle
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06Several compression cycles arranged in parallel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13Economisers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT-PUMP SYSTEMS
    • F25B9/00Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06Compression machines, plant, or systems, in which the refrigerant is air or other gas of low boiling point using expanders

Abstract

A cooling apparatus having multiple refrigeration units (20-1, 20-2) each including evaporator (21-1, 21-2) structured to deprive cold water of heat and cause a refrigerant to evaporate, thereby exerting refrigerating effect; compressor (23-1, 23-2) for compressing of refrigerant vapor into high-pressure vapor; and condenser (25-1, 25-2) for cooling of the high-pressure vapor with cooling water to thereby achieve condensation. The cold water is connected in series with the evaporators (21-1,21-2) of the multiple refrigeration units (20-1, 20-2), and is sequentially cooled by the heat of evaporation of the refrigerant of the multiple evaporators (21-1, 21-2). The cooling water is connected in series with the condensers (25-1, 25-2) of the multiple refrigeration units (20-1, 20-2), and sequentially cools the refrigerant of the multiple condensers (25-1, 25-2).

Description

 Refrigeration equipment technical field

 The present invention relates to a refrigeration system that uses a fluid that changes sensible heat as a cooling fluid (cooling water, cooling air such as cooling air), and uses a fluid that changes sensible heat, such as cold water or plain, as the fluid to be cooled. In particular, the present invention relates to a refrigerator having a plurality of refrigerators. Bright

Background art

 Conventionally, there is a refrigeration system configured by installing a plurality of freezers composed of rice, an evaporator, a compressor, a condenser and the like (see, for example, Japanese Patent Application Laid-Open Publication No. 2003-130428). FIG. 19 is a block diagram showing an example of this type of refrigeration system, and FIG. 20 is a diagram showing supply of cold water and cooling water in this refrigeration system. The refrigeration system shown in both figures is equipped with two freezers 200-1, 200-2, and the evaporators 201-1, 201-2, the compressors 203-1, 203-2 and the Units 205-1 and 205-2 and expansion valves 207-1 and 207_2 are connected by cold water pipes 209-1 and 209-2 to form a closed system for circulating the refrigerant in the closed circuit. ing. And conventionally, cold water (fluid to be cooled) is supplied in parallel to each of the evaporators 201-1, 201-2, and each condenser 205-1, 205-2 is arranged in parallel with each other. Cooling water (cooling fluid) was supplied. With this method of supplying cold water and cooling water, it is possible to control the number of operating chillers 200-1, 200-2 when the refrigeration capacity is small, and also to match the capacity of cold water and cooling water. It can be increased or decreased, and it can handle partial loads.

 However, in the conventional refrigeration system described above, the evaporators 201-1 and 201-2 and the condensers 205-1 and 205 of the stopped freezers 200-1 and 200-2 at the time of partial load (during number control). Since -2 is suspended, these can not contribute to heat transfer, and there is a problem that the efficiency improvement at the time of partial load of the refrigeration system can not be achieved. Disclosure of the invention

The present invention has been made in view of the above-described points, and an object thereof is to provide a refrigeration system using a plurality of refrigerators, in which the efficiency at full load is enhanced and the case of partial load Another objective is to provide a refrigeration system that can maintain high partial load efficiency while always using multiple evaporators and condensers.

 One aspect of the present invention is an evaporator in which heat is taken from a fluid to be cooled and the refrigerant is evaporated to exhibit a refrigeration effect, a compressor for compressing the refrigerant vapor to form high pressure steam, and high pressure steam as a cooling fluid. The refrigeration system includes a plurality of refrigerators having a condenser for cooling and condensing, the fluid to be cooled is connected in series to the evaporators of the plurality of refrigerators, and is sequentially cooled by the heat generation of the refrigerant of the plurality of evaporators. The refrigeration fluid is serially connected to the condensers of the plurality of refrigerators, and sequentially cools the refrigerants of the plurality of condensers.

 A preferred aspect of the present invention is characterized in that a plurality of compressors of the plurality of refrigerators are driven by the same electric motor.

 In a preferred embodiment of the present invention, at least, a evaporator for installing the plurality of refrigerators in each section defining one can body, or a condenser for the plurality of refrigerators, In each of the compartments.

 In a preferred aspect of the present invention, the refrigerant pipe connecting the condenser and the evaporator of the plurality of refrigerators is provided with a power recovery expander that recovers the energy of the flow of the refrigerant from the condenser to the evaporator. It is characterized by

 In a preferred aspect of the present invention, the power recovery expander recovers power by driving a generator with energy of the flow of refrigerant.

 Since the fluid to be cooled is connected in series to the evaporators of the plurality of refrigerators and the cooling fluid is connected in series to the condensers of the plurality of refrigerators, the sensible heat change of the cooling fluid and the sensible heat of the fluid to be cooled Both the efficiency at full load and the efficiency at partial load can be maintained high by utilizing the change, and from this, the efficiency of the entire refrigeration system can be improved.

 According to the preferred embodiment of the present invention described above, the compressor structure can be simplified. According to the preferred embodiment of the present invention described above, the evaporator structure and / or the condenser structure can be simplified.

 According to the above-described preferred embodiment of the present invention, power (energy possessed by the flow of the refrigerant from the condenser to the evaporator) can be recovered during expansion of the refrigerant, and at the same time, the refrigeration effect can be increased.

According to the preferred embodiment of the present invention described above, since the generator is used as the power recovery expander, the rotation speed of the power recovery expander can be changed by the amount of electricity taken out, and the rotation of the power recovery expander can be easily performed. Speed control can be performed. Brief description of the drawings

 FIG. 1 is a diagram showing a refrigeration cycle of the refrigerator 20. As shown in FIG.

 FIG. 2 is a block diagram of the refrigerator 20. As shown in FIG.

 FIG. 3 is a diagram showing a refrigeration cycle of the refrigerator 2 OA.

 FIG. 4 is a block diagram of the refrigerator 20A.

 FIG. 5 is a diagram showing a refrigeration cycle of the refrigerator 20B.

 FIG. 6 is a block diagram of the refrigerator 2 OB.

 FIG. 7 is a block diagram showing a refrigeration apparatus according to the first embodiment of the present invention.

 FIG. 8 is a diagram showing a supply state of cold water and cooling water of the refrigeration apparatus according to the first embodiment.

 FIG. 9 is a diagram showing a refrigeration cycle of each of the refrigerators 20-1 and 20-2 according to the first embodiment.

 FIG. 10 is a diagram showing a refrigeration cycle of the respective refrigerator 200-1, 200-2 of the conventional refrigeration system shown in FIG.

 FIG. 11 is a view showing the evaporation temperature with respect to the cold water temperature and the condensation temperature with respect to the cooling water temperature of the refrigerators 20-1 and 20-2 of the refrigerating apparatus according to the first embodiment. FIG. 12 is a view showing the evaporation temperature with respect to the cold water temperature and the condensation temperature with respect to the cooling water temperature of the respective refrigerators 00-1 and 200-2 of the conventional refrigeration system shown in FIG. FIG. 13 is a view showing supply states of cold water and cooling water of the refrigeration apparatus according to the second embodiment. FIG. 14 is a diagram showing a refrigeration cycle of each of the refrigerators 20-1 and 20-2 of the refrigeration apparatus according to the second embodiment.

 FIG. 15 is a view showing the evaporating temperature with respect to the cold water temperature of each of the refrigerators 20-1 and 20-2 of the refrigerating apparatus according to the second embodiment and the condensing temperature with respect to the cooling water temperature. FIG. 16 is a block diagram of a refrigeration apparatus according to a third embodiment of the present invention.

 FIG. 17 is a view showing supply states of cold water and cooling water of the refrigeration apparatus according to the third embodiment.

FIG. 18 is a configuration diagram of a modified example of the refrigeration apparatus according to the third embodiment of the present invention. Figure 19 is a block diagram showing an example of a conventional refrigeration system b

FIG. 20 is a diagram showing a supply state of cold water and cooling water of the refrigeration system shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION

 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

 Since the refrigerator according to the present invention is composed of a plurality of refrigerators (compression refrigerator performing a vapor compression type refrigeration cycle), a specific example of a single refrigerator used in the present invention will be described in advance. Figures 2, 4 and 6 are block diagrams showing refrigerators 20, 2 OA and 2 OB which can be used in the refrigeration system of the present invention, and Figures 1, 3 and 5 respectively show them. It is a figure which shows the refrigerating cycle of refrigerator 20, 2 OA, 20 B. FIG. The chiller 20 shown in FIG. 2 is a closed system in which a refrigerant is sealed, and more specifically, an evaporator that takes heat from cold water (fluid to be cooled) and evaporates the refrigerant to exhibit a refrigeration effect. 2 1, a compressor 23 for compressing the refrigerant vapor into high-pressure vapor, a condenser 25 for cooling and condensing high-pressure vapor with cooling water (cooling fluid), and decompressing the condensed refrigerant A refrigerant pipe 29 is connected to an expansion valve 27 that is to be expanded.

 The refrigerator 2 OA shown in FIG. 4 is also configured as a closed system in which the refrigerant is sealed, and the difference with the refrigerator 20 shown in FIG. 2 is that in order to achieve higher efficiency compared to the refrigerator 20. A plurality of (two) economizers (gas-liquid separators) 31 and 31 'are installed between the condenser 25 and the evaporator 21 and the compressors 2 3 2 3 1 2 3 This is a point in which the refrigerant vapor from the economizer 1, 3 1, 3 1 1 ′ is drawn in the middle of each compression stage by making the stage into a multistage (3rd stage). Thus, a two-stage economizer as shown in FIG. A cycle is formed: expansion between the condenser 25 and the economizer 31 1, between the economizer 1 31 and the economizer 1 31 1, and between the economizer 1 31 1 and the evaporator 21 respectively. Generally, a valve is provided, Note that in Fig. 4 the expansion valve 2 7 is shown only between the economizer 1 3 1 'and the evaporator 2 1 .

 There is a single stage economizer 1 cycle that combines 2 stages of compressors and 1 stage economizer, or an N stage economizer 1 cycle etc. that combines a compressor (N + 1) stage and N stages of economizers. As the number of stages increases, the efficiency improves. For the application of the present invention, a single-stage or N-stage economizer may be used instead of the two-stage economizer 1 shown in FIG.

Further, the refrigerator 20 B shown in FIG. 6 is also configured as a closed system in which the refrigerant is sealed, and the difference with the refrigerator 20 shown in FIG. 2 is that a power recovery expander is used instead of the expansion valve 27. It is the point where 2 8 was attached. The power recovery expander 28 expands the condensate and sends it to the evaporator 21 and recovers power by the power recovery unit (generator) 2 81. According to this configuration, as shown by line a 1 shown in FIG. 5, the enthalpy decreases during expansion, and the power (the flow of the refrigerant from the condenser 25 to the evaporator 21 is maintained). Energy) can be recovered, and at the same time the refrigeration effect is enormous. This refrigerator

In the case of 20 B, the efficiency can be improved to the same extent as that of the refrigerator 20 A shown in FIG. 4, and in addition, there is no need to install the compressor 23 in multiple stages, so the structure is simplified. . As in this embodiment, it is desirable to recover the recovered power as electricity, and the recovered power is used as part of the drive power of the compressor 23, or a cold water pump, a cooling water pump, a cooling tower, etc. This system is used as part of the drive power of the refrigeration system of the above-mentioned refrigeration system, or linked to other power systems and used as a system drive power etc. of various devices not related to the refrigeration system. When the generator 281 is used as the power recovery expander 28 as in this embodiment, the rotational speed of the power recovery expander 28 can be changed according to the amount of electricity taken out. The rotation speed control of 2 8 becomes easy.

 The power recovery cycle shown in FIG. 6 is provided with a power recovery expander 2 8 instead of the expansion valve 27 shown in FIG. 2. For example, in one cycle of a single stage cycle, a condenser 25 and an economizer 1 3 1 The present invention may be applied to improve the efficiency as a power recovery cycle in which a power recovery expansion device 28 is provided between the power recovery expansion device 28 and between the light source and the evaporator 31 and the evaporator 21 respectively.

 FIG. 7 is a block diagram showing a refrigeration system according to the first embodiment of the present invention, and FIG. 8 is a diagram showing supply of cold water and cooling water in this refrigeration system. The refrigeration system shown in both figures comprises two refrigerators 2 0-1 and 2 0-2 having the same configuration as the freezer 20 shown in FIG. 2 and, as described above, each refrigerator 2 0 — 1 and 2 0-2 are all composed of a closed system with a sealed refrigerant, and evaporators 2 1-1 and 2 1-2 and compressors 2 3-1 and 2 '

3-2 is configured by connecting a condenser 2 5 -1,2 5-2 and an expansion valve 2 7-1 and 2 7-2 by refrigerant piping 2 9-1 and 2 9-2. ing.

 And the cold water (fluid to be cooled) supplied to this refrigeration system is connected in series to the evaporators 2 1-1 and 2 1-2 of each refrigerator 2 0 1 and 2 0 2 by a pipe 4 1 Cooling water (cooling fluid) that is connected and supplied to the refrigeration system is also connected in series to the condensers 25-1 and 25-2 by a pipe 43. Therefore, the cold water is sequentially cooled by the heat of evaporation of the refrigerant in each of the evaporators 2 1-1 and 2 1-2, and the cooling water is used to sequentially cool the refrigerant vapor in each of the condensers 2 5 -1 and 2 5-2 Become. In the case of this embodiment, the flows of cold water and cooling water are both parallel flows flowing from the refrigerator 20 1 to the refrigerator 2 2 in the same direction.

Thus, since the cold water and the cooling water are supplied in series to the plurality of refrigerators 20-1 and 20-2, the average evaporation temperature can be increased and the average condensation temperature can be decreased. In other words, compression can lower the required head and increase efficiency. The following This will be described specifically. FIG. 9 is a diagram showing the refrigeration cycle of each of the refrigerators 20-1 and 20-2 of the refrigeration system according to this embodiment, and FIG. 10 is a diagram of each refrigerator of the conventional refrigeration system shown in FIG. It is a figure which shows a 1,200-2 refrigerating cycle. Fig. 11 is a diagram showing the evaporation temperature with respect to the chilled water temperature of each refrigerator 20-1, 20-2 of the refrigeration system according to this embodiment, and the condensation temperature with respect to the cooling water temperature. FIG. 20 is a diagram showing the evaporation temperature for the chilled water temperature of each of the refrigerators 200-1 and 200-2 of the conventional refrigerator shown in FIG. 19 and the condensation temperature for the cooling water temperature.

 In evaporators 1-1 and 2 1-2, a pinch temperature is formed by the chilled water outlet temperature and the evaporation temperature, while in condensers 25-1 and 25-2, a pinch temperature is formed by the condensation temperature and the coolant outlet temperature. Ru. And in the case of the conventional refrigeration system, since cold water and cooling water are supplied in parallel to each of the refrigerators 200-1 and 200-2, as shown in FIG. 10, the refrigeration cycle of the refrigerator 200-1 and 200-2 Are identical, and as shown in FIG. 12, the pinch temperatures at each evaporator 201-1 and 201-2 and each condenser 205-1 and 205-2 are identical. The temperature of the cold water passing through 1, 20 1-2 and the temperature of the cooling water passing through each condenser 20 5-1, 205-2 become equal. '

On the other hand, in the case of the above embodiment, since cold water and cooling water are supplied in series (and in parallel) to each of the refrigerators 20-1 and 20-2, sensible heat change of cold water and cooling water is used Can increase the efficiency of the refrigeration cycle. That is, as shown in Fig. 11, cold water is supplied in series to each evaporator 21-1 and 21-2 and cooling water is supplied in series to each condenser 25-1 and 25-2. , Both evaporators 21— :! , 2 1-2 and both condensations 25-1 and 25-2 are made to differ in the pinch temperature, the average evaporation temperature is raised, and the average condensation temperature is lowered. At this time, the temperature difference between the condensation temperature and the evaporation temperature shown in Fig. 12 is the same as the temperature difference between the condensation temperature on the condenser 25-2 side and the evaporation temperature on the evaporator 21 side shown in Fig. 1 1. 11 The condensation temperature of the condenser 25-1 shown in 1 and the evaporation of the evaporator 21-1 and the temperature difference between the two can be made smaller compared to the conventional case shown in Fig. 12 and that amount is necessary for compression The compression head (temperature head) can be reduced, the necessary power of the compressor 23-1 can be reduced, and the efficiency of the refrigeration system can be increased. The above is the case of full load, but maintain the partial load efficiency of the compressors 23-1 and 23-2 (ie, use the rotational speed control of the compressor 2-3-1 and 2-3-2 and As shown in Fig. 7, all compressors 23-1, 23-2 are provided by providing suction guide vanes 23a_1, 2 3a-2 at the inlets of the compressors 23-1 and 23-2. It is possible to operate with high efficiency even at partial load, and to stop the heat transfer surface of all evaporators 2 1-1 and 2 1-2 and condensers 25-1 and 25-2 even if partial load is achieved. Not useful It is like that. At this time, the flow rate of the cold water and the flow rate of the cooling water may be controlled to the flow rate matched to the volume by controlling the rotational speed of the pump that circulates these. That is, by making all heat transfer surfaces of the evaporator 21-1 and 21-2 and the condenser 25-1 and 25-2 effective, the average evaporation temperature rises and the average condensation temperature Also from this point, the compression head (temperature head) required for compression decreases, the required power decreases, and the efficiency increases.

 FIG. 13 is a view showing supply states of cold water and cooling water in the refrigeration apparatus according to the second embodiment of the present invention. In the refrigeration system shown in the figure, the same or corresponding parts as in the refrigeration system of the first embodiment shown in FIGS. The items other than the items described below are the same as in the first embodiment. The difference between this embodiment and the first embodiment is only in that the directions of cold water and water supply are different. That is, also in the refrigeration apparatus according to this embodiment, the supplied cold water (fluid to be cooled) is connected in series to the evaporators 21-1 and 21-2 of the respective refrigerator 20-1 and 20-2 by the pipe 41. The cooling water (cooling fluid) supplied to this refrigeration system and supplied to this refrigeration system is also connected in series to the respective condensers 25-1 and 25-2 by the pipe 43, so that the cold water is supplied to the respective evaporators. 21-1 and 21-2 are sequentially cooled by the heat of vaporization of the refrigerant, and the cooling water sequentially cools the refrigerant vapor in each of the condensers 25-2 and 25-1, but in the case of this embodiment, Cold water flows from the evaporator 21-1 to the evaporator 2 1-2, while cooling water flows from the condenser 25-2 to the condenser 25-1 in the opposite direction. Even with this configuration, it will not change to supply cold water and cooling water in series to multiple chillers 20-1 and 20-2, so increase the average evaporation temperature and lower the average condensation temperature. be able to. In other words, the compression head (temperature head) required for compression can be lowered and the efficiency increases. The action will be specifically described below. FIG. 14 is a diagram showing a refrigeration cycle of each of the refrigerators 20-1 and 20-2 of the refrigeration apparatus according to this embodiment. FIG. 15 is a view showing the evaporation temperature with respect to the cold water temperature and the condensation temperature with respect to the cooling water temperature of the respective refrigerators 20 1 and 20 2 of the refrigeration apparatus according to this embodiment.

Evaporation as described above unit 21 1, 21 can one 2, pin Chi temperature and coolant outlet temperature and the evaporation temperature, whereas the condenser 25 1, the pinch temperature 25 2, and the condensing temperature and the cooling water outlet temperature In this embodiment, since cold water and cooling water are supplied in series and in opposite flows to the respective refrigerators 20-1 and 20-2, sensible heat change of cold water and cooling water is used. Can increase the efficiency of the refrigeration cycle. That is, it is shown in FIG. Thus, by supplying cold water in series to the respective evaporators 21-1 and 21-2, the pinch temperatures in the two evaporators 21-1 and 21-2 and the two condensers 25-1 and 25-2 are made different. Disperse, raise the average evaporation temperature, and lower the average condensation temperature. At this time, the condensation temperature of the conventional example shown in FIG. 12 is equivalent to the condensation temperature of the condenser 25-2 shown in FIG. 15, and the evaporation temperature of the conventional example shown in FIG. 12 is the evaporator 25 shown in FIG. Equivalent to the evaporation temperature of That is, the condensation temperature of the condenser 25-1 shown in FIG. 15 decreases, and the evaporation temperature of the evaporator 25-2 shown in FIG. 15 rises. That is, the temperature difference between the condensation temperature of the condenser 25-1 and the evaporation temperature of the evaporator 21-1 and the temperature difference between the condensation temperature of the condenser 25-2 and the evaporation temperature of the evaporator 21-2 shown in FIG. Both can be made smaller than in the conventional example shown in FIG. 12, and the compression heads (temperature heads) required for compression can be reduced accordingly in both compressors 23-1 and 23-2. 3-1, 23-2 The required power can be reduced, and the efficiency of the refrigeration system can be increased. FIG. 16 is a block diagram of a refrigeration apparatus according to a third embodiment of the present invention, and FIG. 17 is a diagram showing supply of cold water and cooling water in this refrigeration apparatus. The refrigeration system shown in both figures comprises two refrigerators 20B-1 and 20 having the same configuration as the refrigerator 20B shown in FIG. 6 described above, and each refrigerator 20B-1 as described above , 20B-2 each consist of a closed system in which a refrigerant is enclosed, and the evaporators 21-1 and 21-2; the compressors 23-1 and 23-2; and the condensers 25-1 and 25-2 The power recovery expanders 28-1 and 28-2 are connected by refrigerant pipes 29-1 and 29-2. In the case of this embodiment, the motor M for driving the two compressors 23-1 and 23-2 is used as * to simplify the electrical instrumentation relationship. In addition, the motor M is a closed type, and it moves in a refrigerant atmosphere, and a labyrinth seal is performed between the motor M and both compressors 23-1 and 23-2. By the way, if two compressors 23-1 and 23-2 are connected to one motor M as in this embodiment, one of the refrigerators 20B-1 or 20B-2 to the other refrigerator 20B- Refrigerant may leak toward 2 or 2 OB-1, and when the refrigeration system is operated for a long time, the refrigerant may be biased into any of the freezers 20B-1 or 20B-2. Therefore, in this embodiment, the condenser 25-1 of one refrigerator 20B-1 and the evaporator 21-2 of the other refrigerator 20B-2 and the condenser 25-2 of the other refrigerator 20B-2 are provided. And the evaporator 21 21 of one of the refrigerators 20 B- 1 are connected by a pipe 33 having an on-off valve 35 so as to eliminate the above-mentioned deviation. Specifically, the liquid level rise of the condenser 25-1 or 25-2 is measured to detect excess refrigerant, and the piping 33 on the side connected to the condenser 25-1 or 25-2 is opened or closed. Open the valve 35 and use an excess amount to the other evaporator 21-2 or 21-1 Send the refrigerant liquid. Since the pressure of the condenser 25-1 or 25-2 is higher than that of the evaporator 21-2 or 21-1, transfer of the refrigerant liquid can be easily performed. Since the total amount of refrigerant charged in the refrigerating apparatus is constant, if the initial filling amount is appropriate, the refrigerant on the excess side of the refrigerator 20B-1 or 20B-2 is used as the other refrigerator 20. If it sends to B-2 or 20 B-1 and the bias of the refrigerant is eliminated, the amount of refrigerant of the other refrigerator 20B-2 or 20B is also corrected.

 Further, in this embodiment, the evaporators 21-1 and 21-2 of each of the two refrigerators 20B-1 and 20B-2 constituting the refrigeration system are connected to one can barrel 37 (two Divided into sections, heat transfer surfaces (heat transfer tubes) are installed in each of the divided sections, and at the same time, each condenser 25-1 and 25-2 and a single can barrel 39 (two) The heat transfer surface (heat transfer tube) was installed in each of the divided sections. If configured in this way, it is possible to achieve compactness of the controlled freezing device. The above-mentioned can and barrel may be applied to either one of the evaporators 21-1 and 21-2 or the condensers 25-1 and 25-2.

 In the third embodiment, the power recovery expanders 28-1 and 28-2 installed respectively for the plurality of (two) refrigerators 2 OB-1 and 20B-2 are different generators (see FIG. Although a power recovery device 281) shown in 6 is connected, one generator (power recovery device) is connected to multiple power recovery expanders 23-1 and 28-2 to share the generator. You may configure it.

 i 8 is a block diagram of a modification of the refrigeration apparatus according to the third embodiment. In the refrigeration system shown in the figure, the same or corresponding parts as in the refrigeration system of the third embodiment are designated by the same reference numerals. The items other than the items described below are the same as in the third embodiment. The difference between the refrigeration system shown in the figure and the refrigeration system according to the third embodiment is that two stages of compressors 23-1 and 23-2 are provided on both sides of one electric motor M, and the refrigeration system is configured. Two refrigeration units 20 B- 1 and 20 B- 2 are equipped with an evaporator 31-1 and 31-2 respectively, and condensers 25-1 and 25-2 and an economizer 31-1 and 31-2 The power recovery expanders 28-1 and 28-2 are respectively provided between the economizers 31-1 and 31-2 and the evaporators 21-1 and 21-2. As described above, a plurality of power recovery expanders 28-1 and 28-2 may be provided to configure the power recovery cycle in multiple stages. The refrigerant amount adjustment circuit corresponding to the pipe 33 having the on-off valve 35 shown in FIG. 16 and FIG. 17 of the third embodiment is omitted from FIG.

Although the embodiment of the present invention has been described above, the present invention is limited to the above embodiment. Rather, various modifications are possible within the scope of the claims and the technical concept described in the specification and the drawings. Note that any shape, structure, or material not described in the specification and drawings is within the scope of the technical idea of the present invention as long as the effects of the present invention are exhibited. For example, although one refrigerator is configured by two refrigerators in the above embodiment, one refrigerator may be configured by a plurality of three or more refrigerators. In that case, cold water (fluid to be cooled) is connected in series to flow in each evaporator of these multiple refrigerators, and cooling water (cooling fluid) is connected in series to each condenser of the multiple refrigerators. Flow.

 In the above embodiment, two compressors of two refrigerators are driven by one motor, but when one refrigerator is composed of three or more refrigerators, each refrigerator The compressor may be driven by one or more motors. In each of the above embodiments, an example using the refrigerator 20 shown in FIG. 2 and the refrigerator 2 OB shown in FIG. 6 as the refrigerator used in the refrigerator has been described, but of course the refrigerator 2 OA shown in FIG. It is good. Furthermore, a refrigerator having a configuration other than these refrigerators 20, 2 O A, 2 O B may be used.

 In the above embodiment, two compressors of two refrigerators are driven by one motor, but as shown in FIG. 7, each compressor is provided with a motor, and the load can be extremely reduced. In case of surge or surging, control of the number of compressors may be supported. That is, in general, it is more efficient to use all the heat transfer areas of the evaporator and the condenser, but if the load is extremely small and the efficiency of the compressor is significantly reduced, the heat transfer area should be at least the compression area. In some cases it may be better to increase the refrigerant flow per unit. It is also possible to control the number by efficiency comparison by calculation. Industrial applicability

 The present invention uses a fluid that changes sensible heat as a cooling fluid (cooling water, cooling air such as cooling air), and a refrigeration system that uses a fluid that changes sensible heat, such as cold water or brine, as the fluid to be cooled. It is applicable to the freezing device which has a freezer.

Claims

The scope of the claims
1. An evaporator that removes heat from the fluid to be cooled and evaporates the refrigerant to exhibit a refrigeration effect, a compressor that compresses the refrigerant vapor into high-pressure vapor, and cools and condenses high-pressure vapor with a cooling fluid Equipped with a plurality of refrigerators having a condenser;
 The fluid to be cooled is connected in series to the evaporators of the plurality of refrigerators, and sequentially cooled by the heat of vaporization of the refrigerant of the plurality of evaporators,
 The refrigeration system according to claim 1, wherein the cooling fluid is connected in series to the condensers of the plurality of refrigerators to sequentially cool refrigerants of the plurality of condensers.
2. The refrigeration apparatus according to claim 1, wherein a plurality of compressors of the plurality of refrigerators are driven by the same electric motor.
3. At least the evaporators of the plurality of refrigerators are installed in each section divided into one can body, or
 Alternatively, the refrigeration apparatus according to claim 1 or 2, wherein the condensers of the plurality of refrigerators are installed in respective sections in which one can body is partitioned.
4. The refrigerant piping that connects the condensers and the evaporator of each of the plurality of refrigerators should be provided with a power recovery expander that recovers the energy possessed by the flow of refrigerant from the condenser to the evaporator. The refrigeration apparatus according to any one of claims 1 or 2 or 3.
5. The refrigeration system according to claim 4, wherein the power recovery expander recovers power by driving a generator with the energy of the flow of refrigerant.
PCT/JP2007/050372 2006-01-10 2007-01-09 Refrigeration apparatus WO2007080994A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2006002977A JP5096678B2 (en) 2006-01-10 2006-01-10 Refrigeration equipment
JP2006-002977 2006-01-10

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN2007800022390A CN101371082B (en) 2006-01-10 2007-01-09 Refrigeration apparatus

Publications (1)

Publication Number Publication Date
WO2007080994A1 true WO2007080994A1 (en) 2007-07-19

Family

ID=38256397

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2007/050372 WO2007080994A1 (en) 2006-01-10 2007-01-09 Refrigeration apparatus

Country Status (3)

Country Link
JP (1) JP5096678B2 (en)
CN (1) CN101371082B (en)
WO (1) WO2007080994A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011023352A3 (en) * 2009-08-31 2011-06-23 Karsten Uitz Heat pump
JP2011169532A (en) * 2010-02-19 2011-09-01 Mitsubishi Heavy Ind Ltd Refrigerator unit and method of controlling the same
GB2480861A (en) * 2010-06-04 2011-12-07 M F Refrigeration Ltd Refrigeration plant with multiple refrigeration units
WO2020014032A1 (en) * 2018-07-09 2020-01-16 Carrier Corporation Device and method for chiller plant management, computer readable storage device and chiller plant

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100946136B1 (en) * 2008-04-25 2010-03-10 엘에스엠트론 주식회사 Dual Centrifugal Chiller
JP5543093B2 (en) * 2008-06-09 2014-07-09 荏原冷熱システム株式会社 Compressive refrigerator and operation method thereof
JP2012532305A (en) * 2009-06-29 2012-12-13 ジョンソン コントロールズ テクノロジー カンパニーJohnson Controls Technology Company System for limiting the pressure differential in a double compressor chiller.
JP5478983B2 (en) * 2009-08-17 2014-04-23 荏原冷熱システム株式会社 Compressive refrigerator and operation method thereof
JP5352399B2 (en) * 2009-09-25 2013-11-27 荏原冷熱システム株式会社 Compression refrigerator
JP5371660B2 (en) * 2009-09-25 2013-12-18 荏原冷熱システム株式会社 Compression refrigerator
EP3264003A1 (en) * 2010-02-08 2018-01-03 Johnson Controls Technology Company Vapor compression system
JP5754935B2 (en) * 2010-12-24 2015-07-29 荏原冷熱システム株式会社 Compression refrigerator
JP6053405B2 (en) * 2012-09-12 2016-12-27 三菱重工業株式会社 Parallel type refrigerator control device, method and program
JP6472379B2 (en) * 2013-05-16 2019-02-20 康之 池上 Energy Conversion System
JP6272364B2 (en) * 2014-02-14 2018-01-31 三菱電機株式会社 Refrigeration cycle equipment
JP6272365B2 (en) * 2014-02-14 2018-01-31 三菱電機株式会社 Refrigeration cycle equipment
WO2015189948A1 (en) * 2014-06-12 2015-12-17 三菱電機株式会社 Refrigeration cycle device
CN105890226B (en) * 2015-07-09 2018-07-20 广东申菱环境系统股份有限公司 A kind of water source cold-heat alliance grade hot type water chiller-heater unit and its control method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6038561A (en) * 1983-08-11 1985-02-28 Daikin Ind Ltd Heater for composite heat pump
JPS63311055A (en) * 1987-06-15 1988-12-19 Seiko Seiki Kk Air conditioner
JPH04350468A (en) * 1991-04-23 1992-12-04 Asahi Breweries Ltd Liquid cooler
JPH0593550A (en) * 1991-04-11 1993-04-16 Ebara Corp Freezing system
JP2003130428A (en) * 2001-08-17 2003-05-08 Ebara Corp Connection type cold/hot water device
JP2004138333A (en) * 2002-10-18 2004-05-13 Matsushita Electric Ind Co Ltd Refrigeration cycle device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58183428U (en) * 1982-05-28 1983-12-07
JPS6387560A (en) * 1986-09-30 1988-04-18 Aisin Seiki Operation controller for air conditioner
JPH03148566A (en) * 1989-11-06 1991-06-25 Hitachi Ltd Refrigerating plant
JPH07174422A (en) * 1993-12-20 1995-07-14 Mitsubishi Electric Corp Heat accumulation air-conditioning device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6038561A (en) * 1983-08-11 1985-02-28 Daikin Ind Ltd Heater for composite heat pump
JPS63311055A (en) * 1987-06-15 1988-12-19 Seiko Seiki Kk Air conditioner
JPH0593550A (en) * 1991-04-11 1993-04-16 Ebara Corp Freezing system
JPH04350468A (en) * 1991-04-23 1992-12-04 Asahi Breweries Ltd Liquid cooler
JP2003130428A (en) * 2001-08-17 2003-05-08 Ebara Corp Connection type cold/hot water device
JP2004138333A (en) * 2002-10-18 2004-05-13 Matsushita Electric Ind Co Ltd Refrigeration cycle device

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011023352A3 (en) * 2009-08-31 2011-06-23 Karsten Uitz Heat pump
JP2011169532A (en) * 2010-02-19 2011-09-01 Mitsubishi Heavy Ind Ltd Refrigerator unit and method of controlling the same
GB2480861A (en) * 2010-06-04 2011-12-07 M F Refrigeration Ltd Refrigeration plant with multiple refrigeration units
GB2480861B (en) * 2010-06-04 2012-05-30 M F Refrigeration Ltd Refrigeration Plant
WO2020014032A1 (en) * 2018-07-09 2020-01-16 Carrier Corporation Device and method for chiller plant management, computer readable storage device and chiller plant

Also Published As

Publication number Publication date
CN101371082A (en) 2009-02-18
JP2007183077A (en) 2007-07-19
CN101371082B (en) 2011-06-15
JP5096678B2 (en) 2012-12-12

Similar Documents

Publication Publication Date Title
DE112009000608B4 (en) An ejector-type refrigeration cycle device
Arpagaus et al. Multi-temperature heat pumps: A literature review
CN1129750C (en) Refrigerating device
KR100958399B1 (en) Hvac system with powered subcooler
JP3102651U (en) Refrigerator refrigerator with two evaporators
EP1347251B1 (en) Method for increasing efficiency of a vapor compression system by evaporator heating
CN100371656C (en) Refrigeration cycle apparatus
Jensen et al. Optimal operation of simple refrigeration cycles: Part I: Degrees of freedom and optimality of sub-cooling
CN103842747B (en) Refrigerating circulatory device
US5079929A (en) Multi-stage refrigeration apparatus and method
KR101155496B1 (en) Heat pump type speed heating apparatus
EP2019272B1 (en) Combined receiver and heat exchanger for a secondary refrigerant
CN101535745B (en) Apparatus for refrigeration cycle and refrigerator
JP3343142B2 (en) refrigerator
US9395106B2 (en) System and method for cooling power electronics using heat sinks
US3675441A (en) Two stage refrigeration plant having a plurality of first stage refrigeration systems
KR20120052302A (en) A jet pump system for heat and cold management, apparatus, arrangement and methods of use
US7104084B2 (en) Heat pump and structure of extraction heat exchanger thereof
JP4553964B2 (en) Cooling device for communication equipment and control method thereof
US8297065B2 (en) Thermally activated high efficiency heat pump
CN101371082B (en) Refrigeration apparatus
US8447432B2 (en) Refrigerator and control method for the same
US6519967B1 (en) Arrangement for cascade refrigeration system
JP5195364B2 (en) Ejector refrigeration cycle
US20050044882A1 (en) Condenser

Legal Events

Date Code Title Description
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: 200780002239.0

Country of ref document: CN

NENP Non-entry into the national phase in:

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 6733/DELNP/2008

Country of ref document: IN

122 Ep: pct application non-entry in european phase

Ref document number: 07706714

Country of ref document: EP

Kind code of ref document: A1