CN115885139A - Refrigerating device - Google Patents
Refrigerating device Download PDFInfo
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- CN115885139A CN115885139A CN202180048552.8A CN202180048552A CN115885139A CN 115885139 A CN115885139 A CN 115885139A CN 202180048552 A CN202180048552 A CN 202180048552A CN 115885139 A CN115885139 A CN 115885139A
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- heat
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- side refrigerant
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- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
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- 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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- 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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
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- 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
- F25B2400/00—General 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
- F25B2400/12—Inflammable refrigerants
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- 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
- F25B2400/00—General 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
- F25B2400/12—Inflammable refrigerants
- F25B2400/121—Inflammable refrigerants using R1234
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- 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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
Abstract
The present invention addresses the problem of providing a novel multistage refrigeration device. The refrigeration device is provided with: a usage-side heat transfer cycle that has a usage-side compressor, a usage-side heat exchanger, a usage-side pressure reducing device, and a usage-side cascade heat exchanger, and circulates a usage-side refrigerant; a heat-source-side heat-transfer cycle that includes a heat-source-side compressor, a heat-source-side heat exchanger, a heat-source-side pressure reducing device, and a heat-source-side cascade heat exchanger, and circulates a heat-source-side refrigerant; a cascade heat exchanger that exchanges heat between the usage-side refrigerant of the usage-side condenser and the heat-source-side refrigerant of the heat-source-side evaporator; and a controller for controlling the use-side refrigerant to have a boiling point of-30 ℃ or higher and 25 ℃ or lower, and for controlling the heat-source-side refrigerant to have a boiling point of-55 ℃ or higher and lower than-30 ℃. The refrigerating apparatus is used as a solution.
Description
Technical Field
The present invention relates to a refrigeration apparatus.
Background
A so-called two-stage refrigeration apparatus having a two-stage refrigerant cycle including a usage-side heat transfer cycle and a heat-source-side heat transfer cycle has been proposed (patent documents 1 and 2).
Documents of the prior art
Patent document
Patent document 1: international publication No. WO2015/140872
Patent document 2: international publication No. WO2015/140873
Disclosure of Invention
Problems to be solved by the invention
The subject of the application is to provide a novel multistage refrigeration device.
Means for solving the problems
A refrigeration device according to item 1, comprising:
a usage-side heat transfer cycle that circulates a usage-side refrigerant;
a heat source-side heat-transfer cycle that circulates a heat source-side refrigerant;
a cascade heat exchanger that exchanges heat between the usage-side refrigerant and the heat-source-side refrigerant,
the usage-side refrigerant has a boiling point of-30 ℃ or higher and 25 ℃ or lower, and the heat-source-side refrigerant has a boiling point of-55 ℃ or higher and lower than-30 ℃.
Item 2. The refrigeration apparatus according to item 1, wherein,
the heat source-side heat transfer cycle is a vapor compression refrigeration cycle including a heat source-side compressor, a heat source-side heat exchanger, a heat source-side pressure reducing device, and a heat source-side cascade heat exchanger.
Item 3. The refrigeration apparatus according to item 1 or 2, wherein,
the use-side heat transfer cycle is a vapor compression refrigeration cycle including a use-side compressor, a use-side heat exchanger, a use-side decompressor, and a use-side cascade heat exchanger.
Item 4. The refrigeration apparatus according to item 1 or 2, wherein,
the use-side heat transfer cycle is a heat transfer cycle including a pump, a use-side heat exchanger, and a use-side cascade heat exchanger.
Item 5 the refrigeration apparatus according to any one of items 1 to 4, wherein,
the heat-source-side refrigerant and the usage-side refrigerant flow in the cascade heat exchanger in a counter-flow direction.
The refrigeration apparatus according to any one of claims 1 to 5, wherein,
the heat-source-side refrigerant has a combustion velocity of 10cm/s or less, and the usage-side refrigerant has a combustion velocity of 3cm/s or less.
Item 7 the refrigeration apparatus according to any one of items 1 to 6, wherein,
the heat-source-side refrigerant is a refrigerant classified by ASHRAE into 2L class, and the usage-side refrigerant is a refrigerant classified by ASHRAE into A1 class.
The refrigeration apparatus according to any one of claims 1 to 5, wherein,
the above-mentioned heat source-side refrigerant contains HFO-1123 and/or HFO-1132.
Item 9 the refrigeration apparatus according to any one of items 1 to 7, wherein,
the heat-source-side refrigerant is R32, R452B, or R454B, and the usage-side refrigerant is at least one selected from the group consisting of R513A, R515B, R1224, R1234yf, R1234ze, R1233, and R1336.
the heat-source-side refrigerant is a refrigerant containing HFO-1132, and the usage-side refrigerant is at least one selected from the group consisting of R513A, R515B, R471A, R1224, R1234yf, R1234ze, R1233, and R1336.
The refrigeration apparatus according to any one of items 1 to 10, which is an air conditioner, a refrigerator, an ice chest, a water chiller, an ice maker, a showcase freezer, a refrigerator freezer for a refrigerator freezer or freezer, an air conditioner for a vehicle, a turbo refrigerator, or a screw refrigerator.
The refrigeration apparatus according to any one of claims 1 to 10, which is a household air conditioner, a commercial air conditioner, an industrial air conditioner, or a multi-functional air conditioner for a building.
Effects of the invention
According to the present invention, a novel multistage refrigeration apparatus can be provided which can safely use a refrigerant having a low boiling point, a high pressure, a high density, and a high refrigeration capacity.
Drawings
Fig. 1 is a diagram for explaining the configuration of a refrigeration apparatus according to the present invention.
Fig. 2 is a diagram for explaining the configuration of the refrigeration apparatus according to the present invention.
Detailed Description
The refrigeration device of the present invention includes:
a usage-side heat transfer cycle that circulates a usage-side refrigerant;
a heat source-side heat-transfer cycle that circulates a heat source-side refrigerant;
a cascade heat exchanger that exchanges heat between the usage-side refrigerant and the heat-source-side refrigerant,
the usage-side refrigerant has a boiling point of-30 ℃ or higher and 25 ℃ or lower, and the heat-source-side refrigerant has a boiling point of-55 ℃ or higher and lower than-30 ℃.
The heat source side is the outdoor unit side, and is also described as the high-stage side, the high-temperature side, and the primary side. From the viewpoint of performance improvement, it is preferable to use a refrigerant having excellent refrigerant characteristics on the heat source side. The use side is the indoor unit side, and is also described as the low stage side, the load side, the low temperature side, and the secondary side. From the viewpoint of directly cooling a person or an object, it is preferable to use a refrigerant having high safety on the use side.
The refrigeration apparatus of the present invention is a so-called multistage refrigeration apparatus including at least a two-stage heat transfer cycle of a utilization-side heat transfer cycle (a heat medium circuit for load) and a heat-source-side heat medium circuit. The refrigeration apparatus of the present invention may be provided with a heat transfer cycle of 3 stages or more.
The cascade heat exchanger includes a heat source side cascade heat exchanger and a use side cascade heat exchanger, and performs heat exchange in a cooling operation as described later. Specifically, in the cooling operation, the refrigerant is condensed in the usage-side cascade heat exchanger, and the refrigerant is evaporated in the heat-source-side cascade heat exchanger, so that heat moves from the usage side to the heat-source side.
The usage-side heat transfer cycle circulates a usage-side refrigerant. The utilization-side heat transfer cycle may also be a vapor compression refrigeration cycle. A usage-side refrigeration cycle, which is a vapor compression refrigeration cycle, includes a usage-side compressor, a usage-side heat exchanger, a usage-side pressure reducer, and a usage-side cascade heat exchanger.
The utilization-side heat transfer cycle may be a pump heat transfer cycle. A utilization-side heat transfer cycle, which is a pump-type heat transfer cycle, includes a pump, a utilization-side heat exchanger, and a utilization-side cascade heat exchanger.
For example, as shown in fig. 1, an expansion valve 13 or the like can be used as the use-side pressure reducing device. Alternatively, as the use-side pressure reducing device, another pressure reducing device such as a capillary tube may be used. In addition, the use-side heat exchanger can also be used as a cold source.
For example, in the case where the amount of refrigerant required for the use-side heat transfer cycle greatly varies depending on changes in the operating conditions, the liquid receiver 15 may be disposed in a pipe that communicates between the use-side cascade heat exchanger 12 and the use-side expansion valve 13, as shown in fig. 2, for example.
The use-side heat transfer cycle preferably includes use-side high-pressure detection means for detecting the high-pressure of the use-side heat transfer cycle, and use-side low-pressure detection means for detecting the low-pressure of the use-side heat transfer cycle. In addition, the usage-side heat transfer cycle preferably includes usage-side discharge temperature detection means for detecting the temperature of the usage-side refrigerant discharged from the usage-side compressor.
The usage-side high pressure detection device and the usage-side low pressure detection device may be any devices as long as they substantially detect pressure. That is, the usage-side high-pressure detection device and the usage-side low-pressure detection device may detect the pressure of the usage-side refrigerant itself, or may detect other physical quantities that can be converted into the pressure of the usage-side refrigerant.
The side-ejection temperature detection device may be any device that substantially detects a temperature. That is, the usage-side discharge temperature detection device may detect the discharge temperature of the usage-side refrigerant itself, or may detect another physical quantity that can be converted into the discharge temperature of the usage-side refrigerant.
For example, as shown in fig. 1, the use-side heat transfer cycle 10 includes a use-side high-pressure sensor 21 as use-side high-pressure detection means, a use-side low-pressure sensor 22 as use-side low-pressure detection means, and a use-side discharge temperature sensor 23 as use-side discharge temperature detection means. The use-side high-pressure sensor 21 is preferably disposed in a pipe that communicates between the use-side cascade heat exchanger 12 and the use-side expansion valve 13. The use-side low-pressure sensor 22 is preferably disposed in a pipe that communicates between the use-side heat exchanger 14 and the use-side compressor 11. The usage-side discharge temperature sensor 23 is preferably disposed in a pipe that communicates between the usage-side compressor 11 and the usage-side condenser 12. In addition, when the use-side heat transfer cycle is unnecessary, a part or all of the sensors may not be provided.
The refrigeration device of the invention may also have a control device. A detection signal of the use-side high-pressure detection device, a detection signal of the use-side low-pressure detection device, and a detection signal of the use-side discharge temperature detection device are input to the control device. The control device controls the overall operation of the refrigeration device of the present invention. All or a part of the control device may be constituted by a microcomputer, a microprocessor unit, or the like; software that can update firmware, etc.; or a program module executed in accordance with an instruction from a CPU or the like.
The use-side refrigerant has a boiling point of-30 ℃ to 25 ℃.
The heat source side heat-transfer cycle circulates a heat source side refrigerant. The heat source-side heat-transfer cycle is preferably a vapor compression refrigeration cycle. A heat-source-side refrigeration cycle, which is a vapor compression refrigeration cycle, includes a heat-source-side compressor, a heat-source-side heat exchanger, a heat-source-side pressure reduction device, and a heat-source-side cascade heat exchanger.
The heat source side compressor is of a variable capacity type. As the heat source side pressure reducing device, an expansion valve or the like can be used. Alternatively, another pressure reducing device such as a capillary tube may be used as the heat source side pressure reducing device.
The heat-source-side refrigerant has a boiling point of-55 ℃ or higher and lower than-30 ℃.
In the case of the cooling operation, the usage-side condenser and the heat-source-side evaporator are incorporated in the cascade heat exchanger. When a zeotropic refrigerant mixture is used, the usage-side refrigerant of the usage-side condenser exchanges heat with the heat-source-side refrigerant of the heat-source-side evaporator in the cascade heat exchanger. In view of preventing a decrease in heat exchange efficiency due to a temperature gradient, it is preferable that the heat-source-side refrigerant and the usage-side refrigerant flow in opposite directions in the cascade heat exchanger.
In the case of heating operation, the usage-side evaporator and the heat-source-side condenser are incorporated in the cascade heat exchanger. When a zeotropic refrigerant mixture is used, the usage-side refrigerant of the usage-side evaporator exchanges heat with the heat-source-side refrigerant of the heat-source-side condenser in the cascade heat exchanger. In view of preventing a decrease in heat exchange efficiency due to a temperature gradient, it is preferable that the heat-source-side refrigerant and the usage-side refrigerant flow in opposite directions in the cascade heat exchanger.
According to the present invention, by using a refrigerant having a high density and good performance, such as a refrigerant having a boiling point of-55 ℃ or higher and lower than-30 ℃, as the heat source side refrigerant, the efficiency of the refrigeration cycle can be maintained within a preferable range, and a refrigerant having a boiling point of-30 ℃ or higher and 25 ℃ or lower can be used as the usage side refrigerant. As described above, according to the present invention, by using a refrigerant having high performance on the heat source side, even if a refrigerant having the same level of performance as that of the refrigerant is not used on the usage side, the performance of the entire cycle can be ensured within a good range. Further, since the refrigerant has a boiling point of from-30 ℃ to 25 ℃ but is excellent in terms of low GWP and low combustibility, these refrigerants can be suitably used in the present invention.
According to the present invention, since such a refrigerant excellent in low GWP can be used as the usage-side refrigerant, the total GWP of the refrigerants used can be reduced while maintaining the performance of the entire apparatus. In this regard, the GWP of the heat-source-side refrigerant is preferably 750 or less, more preferably 500 or less, still more preferably 300 or less, and most preferably 150 or less. The GWP of the usage-side refrigerant is preferably 750 or less, more preferably 500 or less, still more preferably 300 or less, and most preferably 150 or less.
Alternatively, since a refrigerant excellent in low combustibility as described above can be used as the usage-side refrigerant, the risk of personnel loss due to a fire when refrigerant leaks can be further reduced while maintaining performance in the entire apparatus by disposing the usage-side heat transfer cycle in a region where personnel loss is likely to occur. The combustion rate of the heat-source-side refrigerant is preferably 10cm/s or less, more preferably 9cm/s or less, even more preferably 8cm/s or less, and most preferably 7cm/s or less, in terms of enabling the use of a safer refrigerant on the use side that may cause a loss of people. The combustion speed of the use-side refrigerant is preferably 5cm/s or less, more preferably 3cm/s or less, still more preferably 2cm/s or less, and most preferably 1.5cm/s or less.
In order to make the refrigeration apparatus of the present invention suitable for practical use, it is preferable to use a refrigerant having a boiling point of 25 ℃ or lower as the use-side refrigerant because the saturated vapor pressure can be made to be at least atmospheric pressure. In this regard, the saturation pressure of the usage-side refrigerant at 25 ℃ is preferably 0.0MPaG or more, more preferably 0.01MPaG or more, still more preferably 0.03MPaG or more, and most preferably 0.05MPaG or more. The saturation pressure of the use-side refrigerant at 25 ℃ is preferably 5MPaG or less, more preferably 4MPaG or less, still more preferably 3MPaG or less, and most preferably 2MPaG or less.
In order to make the refrigeration apparatus of the present invention suitable for practical use, the use-side refrigerant can be maintained at a pressure not exceeding the pressure-resistant limit of the piping by using a refrigerant having a boiling point of-30 ℃ or higher. In this regard, as the use-side refrigerant, a refrigerant having a boiling point of-30 ℃ or higher is preferably used, a refrigerant having a boiling point of-25 ℃ or higher is more preferably used, and a refrigerant having a boiling point of-20 ℃ or higher is even more preferably used.
In addition, from the viewpoint of reducing the effect on the global environment due to the amount of electricity consumed when the refrigeration cycle is used, the COP of the heat-source-side refrigerant is preferably 95% or more, more preferably 100% or more, still more preferably 101% or more, and still more preferably 102% or more, compared to R410A.
From the viewpoint of reducing the size of the equipment and reducing the influence on the global environment due to the equipment manufacturing, the refrigeration capacity of the heat-source-side refrigerant is preferably 60% or more, more preferably 70% or more, still more preferably 80% or more, still more preferably 90% or more, and most preferably 100% or more, as compared with R410A.
In order to further reduce the risk of loss of people due to a fire when refrigerant leaks, examples of combinations of the heat-source-side refrigerant and the usage-side refrigerant include combinations in which the heat-source-side refrigerant has a burning velocity of 10cm/s or less and the usage-side refrigerant has a burning velocity of 3cm/s or less. Alternatively, as an example of a combination of the heat-source-side refrigerant and the usage-side refrigerant in the above case, a combination may be mentioned in which the heat-source-side refrigerant is a refrigerant classified into 2L class by the american society for heating, cooling, and air conditioning (ASHRAE), and the usage-side refrigerant is a refrigerant classified into A1 class by the ASHRAE.
As an example of the heat source side refrigerant, in the case of a refrigerant consisting of substantially only a single compound, HFO-1123, HFO-1132 and R32 are exemplified. Examples of the heat-source-side refrigerant include a mixture of a plurality of compounds, at least two mixtures selected from the group consisting of HFO-1123, HFO-1132, R1234yf and R32, and R452B and R454B. Here, R452B is a mixture of R32, R125, and R1234yf (R32: R125: R1234yf (mass ratio) = 26), and R454B is a mixture of R32 and R1234yf (R32: R1234yf (mass ratio) = 68.9.
Specific examples of the heat-source-side refrigerant and the use-side refrigerant include combinations shown in the following tables.
[ Table 1]
Mixtures with HFO-1132 may also contain a material selected from HFC32, HFO1234yf, HFO1234ze (E), and CO 2 At least one of (1).
Of the above, preferred HFO-1132 is preferably HFO-1132 (E), HFO-1132 (z) or HFO-1132a, and most preferred is HFO-1132 (E). Mixtures with HFO-1123 may also contain a material selected from HFC32, HFO1234yf, HFO1234ze (E), and CO 2 At least one of (a).
Examples of the combination of the heat-source-side refrigerant and the usage-side refrigerant include a combination in which the heat-source-side refrigerant is R32, R452B, or R454B, and the usage-side refrigerant is at least one selected from the group consisting of R513A, R515B, R1224, R1234yf, R1234ze, R1233, and R1336. This combination is preferable in that the refrigerant used on the heat source side has a high refrigerating Capacity (Capacity).
An example of a combination of the heat-source-side refrigerant and the usage-side refrigerant is refrigeration in which the heat-source-side refrigerant is HFO-1132The use-side refrigerant is at least one combination selected from the group consisting of R513A, R515B, R471A, R1224, R1234yf, R1234ze, R1233, and R1336. The combination can reduce GWP (CO) of the whole system 2 Ton) is preferred in this regard.
In this specification, HFO-1132 denotes any one of HFO-1132a, HFO-1132 (E) and HFO-1132 (Z). R1224 represents any of HCFO-1224yd (E), HCFO-1224yd (Z), HCFO-1224zb (E), HCFO-1224zb (Z), HCFO-1224xe (E) and HCFO-1224xe (Z). R1234 represents any one of HFO-1234yf, HFO-1234ze (E) and HFO-1234ze (Z). R1233 represents any one of HCFO-1233zd (E), HCFO-1233zd (Z) and HCFO-1233 xf. R1336 represents any of HFO-1336mzz (E), HFO-1336mzz (Z), HFO-1336mcy, HFO-1336mcz (E) and HFO-1336mez (Z). When these HFOs or HCFOs are used as a refrigerant, they may be described as "R.O" as R1234yf, without describing the HFOs or HCFOs.
The refrigeration apparatus of the present invention is preferably an air conditioner, a refrigerator, an ice chest, a water chiller, an ice maker, a refrigerator showcase, a freezer-refrigerator set, a refrigerator for a freezer-refrigerator warehouse, an air conditioner for a vehicle, a turbo refrigerator, or a screw refrigerator.
The refrigeration apparatus of the present invention is more preferably a household air conditioner, a commercial air conditioner, an industrial air conditioner, or a multi-functional air conditioner for a building.
Examples
The present invention will be described below by way of examples, but the present invention is not limited to these examples.
The GWP of the entire system is calculated by the following equation.
GWP (CO) of the System as a whole 2 Ton) = (GWP of heat-source-side refrigerant) × (charge amount of heat-source-side refrigerant) + (GWP of usage-side refrigerant) × (charge amount of usage-side refrigerant)
The lower of these values has less influence on global warming.
The usage-side refrigerant and the heat-source-side refrigerant shown in table 2 are circulated through the usage-side heat transfer cycle and the heat-source-side heat transfer cycle, respectively, as shown in fig. 1, whereby the refrigeration apparatus is operated. The COP ratio and the freezing capacity ratio on the heat source side (both ratios (%) to the value of R410A), the combustion speeds (cm/s) of the heat source side refrigerant and the usage side refrigerant, and the saturation vapor pressure (gauge pressure) at 25 ℃ of the usage side refrigerant (MPaG) were obtained and are shown in tables 2 and 3.
[ Table 2]
[ Table 3]
The boiling points of the refrigerants used in the comparative examples and examples are as follows.
R410A：－51℃
R32：－52℃
R452B：－51℃
R452B：－51℃
R454C：－46℃
R513A：－29℃
R515B：－19℃
R1234ze(E)：－19℃
R1336mcy：+1℃
R1224yd(Z)：+14℃
R1336mzz(E)：+7℃
As is clear from the refrigeration apparatus shown in fig. 1, by using a refrigerant having a high density and good performance, such as a refrigerant having a boiling point of-55 ℃ or higher and lower than-30 ℃, as the heat source side refrigerant, even when a refrigerant having a boiling point of-30 ℃ or higher and 25 ℃ or lower is used as the usage side refrigerant, the efficiency of the refrigeration cycle becomes COP100% or higher and the refrigeration capacity becomes 60% or higher, and the refrigeration cycle efficiency can be maintained within a preferable range.
It was also found that the saturated vapor pressure can be made to be equal to or higher than atmospheric pressure by using a refrigerant having a boiling point of 25 ℃. It was also found that by using a refrigerant having a boiling point of-30 ℃ or higher as the use-side refrigerant, the pressure can be maintained at a level not exceeding the pressure-resistant limit of the piping.
Description of the reference numerals
1: refrigerating device
10: utilization side heat transfer cycle
11: by side compression machines
12: using side cascade heat exchangers
13: using side expansion valves
14: utilization-side heat exchanger
15: by side liquid receiver
15a: soluble suppository
21: using side high pressure sensors
22: using side low pressure sensors
23: temperature sensor using side ejection
30: heat source side heat transfer cycle
31: heat source side compressor
32: heat source side heat exchanger
33: heat source side expansion valve
34: heat source side cascade heat exchanger
35: cooling part
40: cascade heat exchanger
50: control device
Claims (12)
1. A refrigeration device is characterized by comprising:
a usage-side heat transfer cycle that circulates a usage-side refrigerant;
a heat source-side heat-transfer cycle that circulates a heat source-side refrigerant;
a cascade heat exchanger that exchanges heat between the usage-side refrigerant and the heat-source-side refrigerant,
the usage-side refrigerant is a refrigerant having a boiling point of-30 ℃ or higher and 25 ℃ or lower, and the heat-source-side refrigerant is a refrigerant having a boiling point of-55 ℃ or higher and lower than-30 ℃.
2. The refrigeration unit of claim 1,
the heat source-side heat transfer cycle is a vapor compression refrigeration cycle having a heat source-side compressor, a heat source-side heat exchanger, a heat source-side pressure reduction device, and a heat source-side cascade heat exchanger.
3. A cold appliance according to claim 1 or 2,
the use-side heat transfer cycle is a vapor compression refrigeration cycle having a use-side compressor, a use-side heat exchanger, a use-side pressure reducing device, and a use-side cascade heat exchanger.
4. A cold appliance according to claim 1 or 2,
the utilization-side heat transfer cycle is a heat transfer cycle having a pump, a utilization-side heat exchanger, and a utilization-side cascade heat exchanger.
5. A refrigerating device as recited in any one of claims 1 to 4,
the heat-source-side refrigerant and the usage-side refrigerant flow in the cascade heat exchanger in a counter-current direction.
6. A refrigerating device as recited in any one of claims 1 to 5,
the heat-source-side refrigerant is a refrigerant having a combustion velocity of 10cm/s or less, and the usage-side refrigerant is a refrigerant having a combustion velocity of 3cm/s or less.
7. A refrigerating device as recited in any one of claims 1 to 6,
the heat-source-side refrigerant is a refrigerant classified by ASHRAE into 2L class, and the usage-side refrigerant is a refrigerant classified by ASHRAE into A1 class.
8. A refrigerating device as recited in any one of claims 1 to 5,
the heat source-side refrigerant comprises HFO-1123 and/or HFO-1132.
9. A refrigerating device as recited in any one of claims 1 to 7,
the heat-source-side refrigerant is R32, R452B, or R454B, and the usage-side refrigerant is at least one selected from the group consisting of R513A, R515B, R1224, R1234yf, R1234ze, R1233, and R1336.
10. A refrigerating device as recited in any one of claims 1 to 8,
the heat-source-side refrigerant is a refrigerant containing HFO-1132, and the usage-side refrigerant is at least one selected from the group consisting of R513A, R515B, R471A, R1224, R1234yf, R1234ze, R1233, and R1336.
11. A cold appliance according to any one of claims 1-10,
it is an air conditioning apparatus, a refrigerator, an ice chest, a water chiller, an ice maker, a showcase for refrigerator, a showcase for freezer, a refrigerating and refrigerating unit, a refrigerator for freezer and refrigerating warehouse, an air conditioning apparatus for vehicle, a turbo refrigerator or a screw refrigerator.
12. A cold appliance according to any one of claims 1-10,
the air conditioner is a household air conditioner, a commercial air conditioner, an industrial air conditioner, or a multi-functional air conditioner for a building.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020116676 | 2020-07-06 | ||
| JP2020-116676 | 2020-07-06 | ||
| PCT/JP2021/025511 WO2022009898A1 (en) | 2020-07-06 | 2021-07-06 | Refrigeration device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115885139A true CN115885139A (en) | 2023-03-31 |
Family
ID=79553204
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202180048552.8A Pending CN115885139A (en) | 2020-07-06 | 2021-07-06 | Refrigerating device |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20230135967A1 (en) |
| EP (1) | EP4177539A1 (en) |
| JP (2) | JP7216151B2 (en) |
| CN (1) | CN115885139A (en) |
| WO (1) | WO2022009898A1 (en) |
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|---|---|---|---|---|
| GB2615111A (en) * | 2022-01-28 | 2023-08-02 | Agilent Technologies Inc | Cooling arrangements for analytical device |
| US20230375230A1 (en) * | 2022-05-21 | 2023-11-23 | Honeywell International Inc. | Nonflammable refrigerants having low gwp, and systems for and methods of providing refrigeration |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3199419B2 (en) * | 1991-11-13 | 2001-08-20 | 松下冷機株式会社 | Air conditioning |
| JP5133649B2 (en) | 2007-10-16 | 2013-01-30 | 京セラドキュメントソリューションズ株式会社 | Electronic device and memory management program |
| CN103635761A (en) * | 2011-08-04 | 2014-03-12 | 三菱电机株式会社 | Refrigeration device |
| TW201413192A (en) * | 2012-08-01 | 2014-04-01 | Du Pont | Use of E-1,1,1,4,4,4-hexafluoro-2-butene in heat pumps |
| JP2014196869A (en) * | 2013-03-29 | 2014-10-16 | パナソニックヘルスケア株式会社 | Cascade refrigeration system |
| EP3121541B1 (en) * | 2014-03-17 | 2021-11-10 | Mitsubishi Electric Corporation | Refrigerating device and refrigerating device control method |
| EP3128260A4 (en) * | 2014-03-17 | 2017-12-20 | Mitsubishi Electric Corporation | Refrigeration device |
| JP2016166714A (en) * | 2015-03-10 | 2016-09-15 | パナソニックＩｐマネジメント株式会社 | Heat generation unit |
| WO2019123805A1 (en) * | 2017-12-18 | 2019-06-27 | ダイキン工業株式会社 | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| WO2020066922A1 (en) * | 2018-09-28 | 2020-04-02 | ダイキン工業株式会社 | Refrigerant filling method |
-
2021
- 2021-07-06 JP JP2021111974A patent/JP7216151B2/en active Active
- 2021-07-06 WO PCT/JP2021/025511 patent/WO2022009898A1/en unknown
- 2021-07-06 CN CN202180048552.8A patent/CN115885139A/en active Pending
- 2021-07-06 EP EP21838192.9A patent/EP4177539A1/en active Pending
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2022
- 2022-07-11 JP JP2022111190A patent/JP2022125358A/en active Pending
- 2022-12-27 US US18/088,991 patent/US20230135967A1/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JP2022014455A (en) | 2022-01-19 |
| US20230135967A1 (en) | 2023-05-04 |
| JP2022125358A (en) | 2022-08-26 |
| JP7216151B2 (en) | 2023-01-31 |
| WO2022009898A1 (en) | 2022-01-13 |
| EP4177539A1 (en) | 2023-05-10 |
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