CN1168943C - Supercritical refrigerating apparatus - Google Patents
Supercritical refrigerating apparatus Download PDFInfo
- Publication number
- CN1168943C CN1168943C CNB021415927A CN02141592A CN1168943C CN 1168943 C CN1168943 C CN 1168943C CN B021415927 A CNB021415927 A CN B021415927A CN 02141592 A CN02141592 A CN 02141592A CN 1168943 C CN1168943 C CN 1168943C
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- Prior art keywords
- compressor
- pressure
- aforementioned
- side compressor
- refrigerant
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Classifications
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
- F24H4/04—Storage heaters
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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
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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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
- F25B2400/13—Economisers
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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
- F25B2600/021—Inverters therefor
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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
- F25B2600/17—Control issues by controlling the pressure of the condenser
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Combustion & Propulsion (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
To provide a supercritical refrigeration unit having a bypass device capable of preventing pressure difference between high pressure and low pressure of a high stage side compressor from increasing and a heat pump water heater using such a supercritical refrigeration unit. A two-stage compressor having a low stage side compressor and the high side compressor 11b as its components, a high pressure side heat exchanger for cooling gas discharged from the compressor of the compressor , an expansion device and an evaporator for effecting heat exchange with outdoor air are connected sequentially so as to form a refrigerant circuit to turn high pressure side pressure into a supercritical state. The refrigerant circuit is provided with a bypass circuit so as to bypass to the discharge side of the low stage side compressor the high pressure refrigerant which has been cooled in the high pressure side heat exchanger when outdoor temperature becomes low.
Description
Technical field
The present invention relates to a kind of overcritical refrigerating plant, particularly relate to a kind of with ambient atmos as the heat source fluid of evaporimeter, adopt the overcritical refrigerating plant of two-stage compressor as compressor.
Background technology
For with ambient atmos as the heat source fluid of evaporimeter, adopt the overcritical refrigerating plant of two-stage compressor as compressor, usually, under the situation that extraneous gas temperature reduces, evaporating pressure, be that low-pressure lateral pressure reduces.And, follow the reduction of this low-pressure lateral pressure, the discharge lateral pressure of rudimentary side compressor, be that intermediate pressure also reduces.Relative therewith, the discharge pressure of senior side compressor, be high side pressure, because the discharge side gas of senior side compressor uses as the thermal source that utilizes the side heat exchange media of heating water and air etc., so exist in the situation that the discharge side gas temperature that must make senior side compressor keeps high temperature, promptly, must keep high side pressure is the situation (for example, high-pressure situation about not descending) of very high pressure.In this case, in the refrigerating plant that adopts aforementioned two-stage compressor, it is big that the pressure differential of high side pressure and intermediate pressure becomes simultaneously with the ambient atmos decrease of temperature.
But, when the pressure differential of high side pressure and intermediate pressure becomes big simultaneously with the ambient atmos decrease of temperature, because the height pressure differential of senior side compressor becomes big, so compression efficiency variation, simultaneously, the power that acts on each parts becomes big, the problem that exists durability to descend.For example, when the height pressure differential becomes big, exist leaf valve in the senior side compressor or the dump valve breakage etc. may.
The present invention proposes in view of problems of the prior art.Its purpose is that a kind of overcritical refrigerating plant of being furnished with the bypass circulation of the height pressure differential increase that prevents senior side compressor is provided.And, a kind of heat-pump water heater that adopts this overcritical refrigerating plant is provided.
Summary of the invention
A kind of overcritical refrigerating plant of the present invention, have and to be furnished with the two-stage compressor of rudimentary side compressor and senior side compressor as the structure important document, cooling is from the high-pressure side heat exchanger of the gas of the senior side compressor discharge of this two-stage compressor, expansion gear, carry out the refrigerant loop that the evaporimeter of heat exchange couples together in turn with ambient atmos, this refrigerant loop is that the mode of supercriticality forms with the high side pressure, this refrigerant loop further has bypass circulation, this bypass circulation is when ambient atmos reduces, make the discharge side that is diverted to aforementioned rudimentary side compressor by the pressurized gas refrigerant after the cools down of high-pressure side, it is characterized in that: aforementioned two-stage compressor, when the ambient atmos temperature descends, carry out volume controlled in the mode that suppresses compressor capacity decline, aforementioned expansion gear, when extraneous gas temperature descends, carry out aperture control in the mode that the discharge pressure that suppresses senior side compressor descends.
To achieve these goals, according to overcritical refrigerating plant of the present invention, have and to be furnished with the two-stage compressor of rudimentary side compressor and senior side compressor as the structure important document, cooling is from the high-pressure side heat exchanger of the gas of the senior side compressor discharge of this two-stage compressor, expansion gear, carry out the refrigerant loop that the evaporimeter of heat exchange couples together in turn with ambient atmos, this refrigerant loop is that the mode of supercriticality forms with the high side pressure, this refrigerant loop further has bypass circulation, this bypass circulation makes the discharge side that is diverted to aforementioned rudimentary side compressor by the pressurized gas refrigerant after the cools down of high-pressure side when ambient atmos reduces.
Adopt this structure, because the ambient atmos temperature descends, the on high-tension side gas coolant of senior side compressor rises intermediate pressure by being diverted in the intermediate pressure part, and the compression ratio in the senior side compressor reduces.And, because the cold media gas of shunting is by the cold media gas after the cools down of high-pressure side, so it is little to suck the degree of superheat of cold media gas of senior side compressor.Thereby, owing to reduced the height pressure differential of senior side compressor,, can improve the durability of compressor so needn't worry the breakage of dump valve or leaf valve.And along with the compression ratio of senior side compressor reduces, the degree of superheat that sucks gas reduces, thereby has improved its running efficiency.
And aforementioned two-stage compressor is when the ambient atmos temperature descends, carry out volume controlled in the mode that suppresses compressor capacity decline, aforementioned expansion valve device, when extraneous gas temperature descended, the mode that can descend with the discharge pressure that suppresses senior side compressor was carried out aperture control.
Adopt this structure, when extraneous gas temperature descends, keep higher high side pressure, can keep the effluent air temp of higher senior side compressor.
And, aforementioned refrigerant loop can filling arbon dioxide as refrigerant.
Adopt this structure, both used do not have combustibility, the refrigerant of toxicity, can be used for the higher overcritical refrigerant circulation of the discharge side gas temperature of senior side compressor again.And,, when preventing that high side pressure from descending, can keep the discharge side gas temperature of higher senior side compressor by the effect of aforementioned bypass circulation.
And, aforementioned two-stage compressor, in the closed shell of the discharge gas that imports aforementioned rudimentary side compressor, can built-in aforementioned rudimentary side compressor, senior side compressor and drive motor.
Adopt this structure, intermediate pressure acts in the compressor housing, and two-stage compressor cylinder body pressure differential inside and outside and the compression case inside and outside is reduced by half, and the power that acts on each position is reduced.As a result, combine, further improved the durability of two-stage compressor with prevent the effect that the height pressure differential increases by aforementioned bypass circulation.
And, according to heat-pump water heater of the present invention, owing to adopted above-mentioned overcritical refrigerating plant, so under the situation that extraneous gas temperature descends, the height pressure differential that can prevent senior side compressor increases, and can not make the durability of device worsen ground acquisition high-temperature-hot-water.
Description of drawings
Fig. 1 is the loop diagram according to the hot-water supply device of the invention process form.
Fig. 2 is the pressure control key diagram according to the invention process form.
Concrete form of implementation
Below, describe the form of implementation that the present invention is embodied as heat-pump water heater in detail with reference to accompanying drawing.Fig. 1 is the loop diagram according to the hot-water supply device of the invention process form, and Fig. 2 is the pressure control key diagram according to the invention process form.
As shown in Figure 1, according to the hot-water supply device of form of implementation 1, be furnished with: overcritical freezing cycle device 1, hot water feeding unit 2 and control device 3.In addition, in this form of implementation, control device 3 is arranged in the overcritical freezing cycle device 1.And overcritical freezing cycle device 1 and hot water feeding unit 2 are coupled together with connecting pipings 5,6 by water.
Overcritical freezing cycle device 1 is furnished with the refrigerant loop that connects reverse drive formula two-stage compressor 11, high-pressure side heat exchanger 12, electric expansion valve 13, evaporimeter 14, storage heater 15 in turn.And refrigerant in this refrigerant loop flows to, when constant running shown in the solid arrow among Fig. 1.
Reverse drive formula two-stage compressor 11 is that rudimentary side compressor 11a, senior side compressor 11b, the public motor 11c that drives these compressors 11a and 11b are built in compressor in the closed shell, and the suction side of the discharge side of rudimentary side compressor 11a and senior side compressor 11b is coupled together by connecting pipings 11d.And, the space in the closed shell by intermediate-pressure gas, be that the discharge gas of rudimentary side compressor 11a is full of.
And reverse drive formula two-stage compressor 11 utilizes the described control device 3 control operating frequencys in back, control rotating speed in overcritical cool cycles running.In addition, in the discharge pipe arrangement of senior side compressor 11b, be provided with the effluent air temp detector 31 that is used to detect from the effluent air temp of senior side compressor 11b discharge.
The water that the hot water that high-pressure side heat exchanger 12 is sent from the water storage boxes 21 that are configured in the hot water feeding unit 2 with heat-exchange tube 12a and importing from the refrigerant of the high pressure refrigerant of senior side compressor 11b discharge by importing is supplied water constitutes with heat-exchange tube 12b, and both form heat exchange relationship.Therefore, from the hot water supply water cooling that the HTHP cold media gas of senior side compressor 11b discharge is sent from water storage box 21, this hot water supply water is by the contained heat heating of the gas of discharging from senior side compressor 11b.
13 pairs of pressurized gas refrigerants by 12 coolings of high-pressure side heat exchanger of electric expansion valve reduce pressure, and it utilizes impulse motor to drive.And, in overcritical cool cycles running, utilize the described control device 3 in back that it is carried out aperture control.
Evaporimeter 14 makes the low-pressure gas-liquid mixing refrigerant that reduced pressure by electric expansion valve 13 and ambient atmos as the thermal source medium carry out heat exchange, makes this refrigerant gasification.In addition, in this evaporimeter 14, the additional ambient atmos Temperature Detector 32 that is used to detect the ambient atmos temperature that is provided with.
And, according to said structure, in being furnished with the refrigerant loop of said structure equipment, be provided with bypass circulation 16 from the outlet side pipe arrangement of high-pressure side heat exchanger 12 to the connecting pipings 11d that connects rudimentary side compressor 11a and senior side compressor 11b, in this bypass circulation 16, be provided with electromagnetic switch valve 17 and capillary 18.
And, be filled with the carbon dioxide (CO of refrigerant as an alternative in the inside in above-mentioned refrigerant loop
2).As the representational natural refrigerant of cooling, idle call, can enumerate hydrocarbon (HC: propane or iso-butane etc.), ammonia, air and CO
2Deng.But as the characteristic of refrigerant, hydrocarbon and ammonia energy efficiency are good but have negative issues such as having flammable and toxicity, and air exists in ultralow temperature zone problem such as energy efficiency variation in addition.Comparatively speaking, carbon dioxide does not have combustibility and toxicity, is safe.
Hot water feeding unit 2 is furnished with: water storage box 21, hot water circulating pump 22, hot water supply pipe arrangement 23, feedwater pipe arrangement 24.And the upper and lower of water storage box 21 with respect to aforementioned water heat-exchange tube 12b, utilizes to comprise to connect water and couple together with the hot water circulation loop P of pipe arrangement 5,6.
Hot water circulation loop P is to send into the lower water of the temperature of water storage box 21 bottoms, will be constituted with the mode that the higher water of the temperature of heat-exchange tube 12b heating imports the top of water storage box 21 by water with heat-exchange tube 12b to water.And, hot water circulating pump 22 is installed in hot water circulation loop P.In addition, in water storage box 21, utilize difference in specific gravity, store the higher hot water of temperature on top, store the lower water of temperature in the bottom.And, utilize the heating-up temperature detector 33 be arranged on water storage box 21 tops to measure top hot water temperature in the water storage boxes 21, be heating-up temperature.
Hot water supply pipe arrangement 23 is used for to hot-water supplies such as hot water tap, bathtubs, and it is connected to the top of water storage box 21, can supply the temperature in the water storage box 21 higher hot water.In addition, in this hot water supply loop, switch valve 25 is installed.
Hot water supply pipe arrangement 24 can be supplied common running water in water storage box 21, be connected to the bottom of water storage box 21 by check-valves 26, pressure-reducing valve 27.
Control device 3 in constant running, according to the operating frequency of the sequential control reverse drive formula two-stage compressor of stipulating and the aperture of electric expansion valve 13, but is controlled when extraneous gas temperature descends in the following manner.Promptly, ambient atmos Temperature Detector 32 detected ambient atmos temperature are in set point of temperature, for example below 0 ℃, relatively with the ambient atmos decrease of temperature, control the aperture of dwindling electric expansion valve 13 in the mode that suppresses high side pressure decline, simultaneously, increase with the rotating speed (operating frequency) that keeps the constant mode of compressor capacity cardinal principle to control reverse drive formula two-stage compressor 11.And control device 3 when above-mentioned ambient atmos temperature drops to afore mentioned rules temperature (0 ℃), is opened electromagnetic switch valve 17.By opening electromagnetic switch valve 17, pressurized gas refrigerant is diverted on the connecting pipings 11d of intermediate pressure in the mode shown in the dotted arrow among Fig. 1.
By controlling in the manner described above, as shown in Figure 2, to keep controlling high side pressure with respect to descend the keep-up pressure mode of constant of ambient atmos temperature.And intermediate pressure when not having bypass circulation 16 resembling prior art, descends as shown in phantom in Figure 2, and is relative therewith, and under the situation of this form of implementation, like that, this pressure descends and is suppressed shown in the solid line among the same figure.Therefore, the increase of the height pressure differential of senior side compressor 11b is suppressed.And at this moment, because the high-pressure side cold media gas of shunting is reduced so suck the degree of superheat of the cold media gas of high side compressors 11b by 12 coolings of high-pressure side heat exchanger.
In addition, for intermediate pressure, in the present invention and prior art, with respect to the reduction of ambient atmos temperature, the pressure differential of the intermediate pressure of prior art enlarges, and the present invention has then utilized the effect of capillary 18.And in Fig. 2, pressure curve is only represented the ambient atmos temperature till-10 ℃, still, this just luckily the running allowed band of this hot-water supply device be decided to be-10 ℃.
Adopt the form of implementation of said structure, when the ambient atmos temperature descends, in high side compressors 11b,,, can improve the durability of compressor so needn't worry dump valve or leaf valve breakage because the height pressure differential reduces.And when the compression ratio of senior side compressor reduced, the degree of superheat that sucks gas reduced, thereby, improved running efficiency.
And, when the ambient atmos temperature descends, because the high side pressure maintenance is higher, so the maintenance of the discharge side gas temperature of senior side compressor is higher.Especially as shown in Figure 2, under the certain situation of high side pressure maintenance, the hot water supply can keep certain substantially setting in this case with hot water.And, in this form of implementation,,, be easy to handle so there are not problems such as flammable and toxicity in cold media gas owing to adopt carbon dioxide as refrigerant.
And reverse drive formula two-stage compressor 11 in the closed shell of the discharge gas that imports rudimentary side compressor 11a, is built-in with rudimentary side compressor 11a, senior side compressor 11b and drive motor 11c, thereby, be intermediate pressure in the compressor housing.Therefore, cylinder body pressure differential inside and outside and the compression case inside and outside reduces by half, and the power that acts on each position is very little.As a result, combine, can further improve the durability of reverse drive formula two-stage compressor 11 with the effect that the height pressure differential increases that prevents of bypass circulation 16.
In addition, the present invention can carry out following modification so that concrete enforcement.
(1) in above-mentioned form of implementation, bypass circulation 16 is open in the time of 0 ℃, but this temperature can be carried out suitable variation by the design of refrigerating plant.
(2) and, in bypass circulation 16, be provided with electromagnetic switch valve 17 and capillary 18, still, replace these, also can adopt motor-driven valve, according to the ambient atmos decrease of temperature its aperture is increased.Adopt this mode, when bypass circulation is open, pressure is sharply changed, can control reposefully.
(3) and, the electromagnetic switch valve 17 in the bypass circulation 16 and the order of connection of capillary 18 also can be by conversely.That is, the cold media gas of being shunted can be again by electromagnetic switch valve 17 after passing through capillary 18.But, in this case, because electromagnetic switch valve 17 is circulations of the cold media gas after the switch decompression, so there is the shortcoming that the specific volume of handling gas is big, need the big electromagnetic switch valve of bore.
(4) in above-mentioned form of implementation, adopt reverse drive formula two-stage compressor 11 as compressor, but also can adopt the two-stage compressor of the volume-variable of other form.
(5) and, in the above-mentioned form of implementation, overcritical refrigerating plant according to the present invention specifically is used for heat-pump water heater, still, this overcritical freezing cycle device also can specifically be used for other heater, for example heats the heating machine of room air.
Because the present invention consists of in a manner described, so have following effect.
Adopt the according to a first aspect of the invention overcritical freezing cycle device of described invention, tool Have will as the structure important document be furnished with rudimentary side compressor and senior side compressor two-stage compressor, The high-pressure side heat exchanger of the gas that cooling is discharged from the senior side compressor of this two-stage compressor, Expansion gear, carry out the refrigerant loop that the evaporimeter of heat exchange couples together in turn with ambient atmos, This refrigerant loop mode take high side pressure as supercriticality forms, and this refrigerant loop advances one Step has bypass circulation, and this bypass circulation makes by the high-pressure side heat exchange when ambient atmos reduces The cooled pressurized gas refrigerant of device is diverted to the discharge side of aforementioned rudimentary side compressor, thereby, In senior side compressor, the high-low pressure difference diminishes, and needn't worry dump valve and leaf valve breakage, Improved durability. And, in senior side compressor, because the gas superheat degree that sucks is little, So improved its running efficiency.
And, adopt the described invention of a second aspect of the present invention, in a first aspect of the present invention In the described invention, aforementioned two-stage compressor is when the ambient atmos drop in temperature, to suppress pressure The mode that contracting function power descends is controlled capacity, and aforementioned expansion valve device is at ambient atmos During drop in temperature, in the mode that the discharge pressure that suppresses senior side compressor descends aperture is carried out Control, thereby, when extraneous gas temperature descends, can keep higher high side pressure, Can keep higher senior side compressor to discharge the side gas temperature.
And, adopt the described invention of a third aspect of the present invention, of the present invention first and second In the described invention in aspect, be filled with carbon dioxide as refrigerant in the refrigerant loop, thereby, both The refrigerant with combustibility, toxicity can be used, the row of senior side compressor can be used for again Go out the higher overcritical freeze cycle of side gas temperature. And, by the work of aforementioned bypass circulation With, can prevent the decline of high side pressure, simultaneously, can keep higher senior side pressure contracting Machine is discharged the side gas temperature.
And, adopting the described invention of a fourth aspect of the present invention, aforementioned two-stage compressor is It is aforementioned that aforementioned rudimentary side compressor, senior side compressor and drive motor are built in importing Compressor in the closed shell of rudimentary side compressor Exhaust Gas, thereby, two-stage compressor Cylinder body pressure differential inside and outside and the compression case inside and outside reduces by half, act on each position power very Little. As a result, prevent that with aforementioned bypass circulation the effect that the high-low pressure difference increases from combining, and advances one Step has been improved the durability of two-stage compressor.
And, adopt the heat pump hot water supply of according to a fifth aspect of the invention described invention to fill Put, any one is described overcritical freezing owing to used in first to fourth aspect of the present invention Device is so in the situation that extraneous gas temperature descends, can prevent senior side compressor The high-low pressure difference increases, and can install durability and can not obtain high-temperature-hot-water with worsening.
Claims (4)
1. overcritical refrigerating plant, have and to be furnished with the two-stage compressor of rudimentary side compressor and senior side compressor as the structure important document, cooling is from the high-pressure side heat exchanger of the gas of the senior side compressor discharge of this two-stage compressor, expansion gear, carry out the refrigerant loop that the evaporimeter of heat exchange couples together in turn with ambient atmos, this refrigerant loop is that the mode of supercriticality forms with the high side pressure, this refrigerant loop further has bypass circulation, this bypass circulation is when ambient atmos reduces, make the discharge side that is diverted to aforementioned rudimentary side compressor by the pressurized gas refrigerant after the cools down of high-pressure side
It is characterized in that: aforementioned two-stage compressor, when the ambient atmos temperature descends, carry out volume controlled, aforementioned expansion gear in the mode that suppresses compressor capacity decline, when extraneous gas temperature descends, carry out aperture control in the mode that the discharge pressure that suppresses senior side compressor descends.
2. overcritical refrigerating plant as claimed in claim 1 is characterized in that: aforementioned refrigerant loop filling arbon dioxide is as refrigerant.
3. overcritical refrigerating plant as claimed in claim 1 or 2 is characterized in that: aforementioned two-stage compressor, and in the closed shell of the discharge gas that imports aforementioned rudimentary side compressor, built-in aforementioned rudimentary side compressor, senior side compressor and drive motor.
4. a heat-pump water heater adopts as any one described overcritical refrigerating plant in the claim 1～3.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001267605A JP2003074997A (en) | 2001-09-04 | 2001-09-04 | Supercritical refrigeration unit |
| JP267605/2001 | 2001-09-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1403769A CN1403769A (en) | 2003-03-19 |
| CN1168943C true CN1168943C (en) | 2004-09-29 |
Family
ID=19093712
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB021415927A Expired - Fee Related CN1168943C (en) | 2001-09-04 | 2002-09-03 | Supercritical refrigerating apparatus |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2003074997A (en) |
| KR (1) | KR100500617B1 (en) |
| CN (1) | CN1168943C (en) |
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| CN102109261A (en) * | 2009-12-25 | 2011-06-29 | 三洋电机株式会社 | Refrigerating apparatus |
| CN102109260A (en) * | 2009-12-25 | 2011-06-29 | 三洋电机株式会社 | Refrigerating apparatus |
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| US7600390B2 (en) | 2004-10-21 | 2009-10-13 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
| JP4657087B2 (en) * | 2005-11-14 | 2011-03-23 | 三洋電機株式会社 | Heat pump water heater |
| JP5068477B2 (en) * | 2006-05-16 | 2012-11-07 | 三菱電機株式会社 | Compressor and heat pump water heater |
| JP2011133208A (en) * | 2009-12-25 | 2011-07-07 | Sanyo Electric Co Ltd | Refrigerating apparatus |
| CN107202422A (en) * | 2017-05-25 | 2017-09-26 | 海宁金能热水器有限公司 | The air source water heater that a kind of hot and cold water is quickly mixed |
| CN115200180A (en) * | 2022-06-29 | 2022-10-18 | 山东雅士股份有限公司 | High-stability variable-frequency heated water heater control system |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63210568A (en) * | 1987-02-27 | 1988-09-01 | 株式会社東芝 | Air conditioner |
| JPH024164A (en) * | 1988-06-22 | 1990-01-09 | Toshiba Corp | Freezing cycle device |
| JPH11304269A (en) * | 1998-04-23 | 1999-11-05 | Nippon Soken Inc | Refrigerating cycle |
| JP3738414B2 (en) * | 1999-06-30 | 2006-01-25 | 株式会社日立製作所 | Heat pump air conditioner |
| JP4258944B2 (en) * | 1999-10-28 | 2009-04-30 | 株式会社デンソー | Supercritical vapor compressor refrigeration cycle |
-
2001
- 2001-09-04 JP JP2001267605A patent/JP2003074997A/en active Pending
-
2002
- 2002-09-03 KR KR10-2002-0052664A patent/KR100500617B1/en not_active IP Right Cessation
- 2002-09-03 CN CNB021415927A patent/CN1168943C/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102109261A (en) * | 2009-12-25 | 2011-06-29 | 三洋电机株式会社 | Refrigerating apparatus |
| CN102109260A (en) * | 2009-12-25 | 2011-06-29 | 三洋电机株式会社 | Refrigerating apparatus |
| CN101852489A (en) * | 2010-05-10 | 2010-10-06 | 冼泰来 | Technique of water supply, heat supply and cold supply power plant by trans-critical carbon dioxide to absorb air, water and solar heat |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2003074997A (en) | 2003-03-12 |
| CN1403769A (en) | 2003-03-19 |
| KR100500617B1 (en) | 2005-07-14 |
| KR20030020836A (en) | 2003-03-10 |
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