CN1202397C - Heat-pump type hot-water supplying device - Google Patents
Heat-pump type hot-water supplying device Download PDFInfo
- Publication number
- CN1202397C CN1202397C CNB021416737A CN02141673A CN1202397C CN 1202397 C CN1202397 C CN 1202397C CN B021416737 A CNB021416737 A CN B021416737A CN 02141673 A CN02141673 A CN 02141673A CN 1202397 C CN1202397 C CN 1202397C
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- Prior art keywords
- compressor
- aforementioned
- pressure
- heat
- ambient atmos
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Classifications
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- 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
Abstract
To raise endurance of a compressor by preventing high/low pressure difference from becoming too large in a low outdoor temperature region in a heat pump type water heater using outdoor air as a heat source. In a low outdoor temperature region, the opening of a motor- operated expansion valve is controlled so as to lower a high pressure side pressure according to decrease in the outdoor temperature. The rotational speed of the inverter single stage compressor may be controlled so as to keep the compressor capacity constant.
Description
Technical field
The present invention relates to a kind of compressor that utilizes and discharge the heat-pump water heater that gas heats the hot water of supplying.
Background technology
Heat-pump water heater, utilize the expansion valves such as high-pressure side heat exchanger, electric expansion valve of the discharge gas connect compressor, cooling compressor in turn, carry out the evaporimeter etc. of heat exchange with ambient atmos and the freezing cycle device that forms, in evaporimeter, draw heat from ambient atmos, the heat that is drawn is discharged into hot water supply water in the heat exchanger of high-pressure side, hot water supply water is heated.
And usually for the needs of hot water supply, the low more amount of high-temperature-hot-water that then needs of ambient atmos temperature is many more, and the temperature of ambient atmos is high more then to have the tendency that the hot water that can adopt low temperature and requirement also descend.To this, existing common heat-pump water heater, because the characteristic of freeze cycle, the temperature of the low hot water supply water that is then obtained in the heat exchanger of high-pressure side of the temperature of ambient atmos is step-down also.And, have the characteristic that the heating efficiency of hot water supply water also can descend.Therefore, the mutual opposite problem of ability characteristics that has required characteristic of hot water supply and heat-pump water heater.
Therefore, in order to address this problem, in order to obtain enough high temperature hot water in extraneous low outdoor temperature region, formation is the overcritical freeze cycle of refrigerant with the carbon dioxide, and, for the ability of compressor in extraneous low outdoor temperature region big, compressor capacity is little in the high zone of extraneous gas temperature, adopt the reverse drive compressor, corresponding to the ambient atmos decrease of temperature rotating speed of this reverse drive compressor is increased to increase heating efficiency, simultaneously, so that the method that high side pressure raises reduces the aperture of electric expansion valve.Thereby, in extraneous low outdoor temperature region, high side pressure is risen corresponding to the ambient atmos decrease of temperature, simultaneously, low-pressure lateral pressure is descended.
Therefore, in extraneous low outdoor temperature region, particularly in the zone of the low ambient atmos temperature below 0 ℃, the height pressure differential becomes big, the problem that exists the durability of compressor to be damaged.More particularly, the breakage of dump valve, the problems such as leaf valve damage that the hyperbaric chamber in the cylinder body and low-pressure chamber are separated under adopting the situation of rotary compressor can appear in worry.
The present invention proposes in view of existing problem in these prior aries.Its purpose is that a kind of excessive heat-pump water heater of height pressure differential in extraneous low outdoor temperature region that prevents is provided.
Summary of the invention
A kind of heat-pump water heater of the present invention, be furnished with: with reverse drive formula single-stage compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula single-stage compressor with water cooling, electric expansion valve, carry out the freezing cycle device that the evaporimeter of heat exchange is connected in turn and forms with ambient atmos, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water with at 0 ℃--control the control device of the aperture of aforementioned electric expansion valve in the low temperature zone of 10 ℃ ambient atmos in the mode that high side pressure is descended.
To achieve these goals, a first aspect of the present invention is furnished with: with reverse drive formula single-stage compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula single-stage compressor with water cooling, electric expansion valve, the evaporimeter that carries out heat exchange with ambient atmos couples together the freezing cycle device that forms in turn, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water and in extraneous low outdoor temperature region, control the control device of the aperture of aforementioned electric expansion valve in the mode that high side pressure is descended.
Adopt this structure, the height pressure differential of compressor reduces, and needn't worry dump valve and leaf valve breakage, can improve the durability of compressor.And the required intensity of compressor housing can reduce, and can reduce cost.
A kind of heat-pump water heater of the present invention, be furnished with: the reverse drive formula two-stage compressor that will have rudimentary side compressor and senior side compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula two-stage compressor with water cooling, electric expansion valve, carry out the freezing cycle device that the evaporimeter of heat exchange is connected in turn and forms with ambient atmos, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water with at 0 ℃--control the control device of the aperture of aforementioned electric expansion valve in the low temperature zone of 10 ℃ ambient atmos in the mode that high side pressure is descended.
And, a second aspect of the present invention is furnished with: the reverse drive formula two-stage compressor that will have rudimentary side compressor and senior side compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula two-stage compressor with water cooling, electric expansion valve, the evaporimeter that carries out heat exchange with ambient atmos couples together the freezing cycle device that forms in turn, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water and in extraneous low outdoor temperature region, control the control device of the aperture of aforementioned electric expansion valve in the mode that high side pressure is descended.
Adopt this structure, the height pressure differential of each stage compressor significantly reduces, and needn't have the worry of the breakage of dump valve and leaf valve, can improve the durability of compressor.And the necessary intensity of compressor housing can reduce further, can save cost.
A third aspect of the present invention is furnished with: with reverse drive formula single-stage compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula single-stage compressor with water cooling, electric expansion valve, the evaporimeter that carries out heat exchange with ambient atmos couples together the freezing cycle device that forms in turn, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water and in extraneous low outdoor temperature region, control the aperture of aforementioned electric expansion valve in the mode that high side pressure is descended, control the control device of the rotating speed of aforementioned inverse type single-stage compressor simultaneously in the substantially invariable mode of compressor capacity.
Adopt this structure, both can suppress the decline of hot water heating efficiency, the same with aforementioned a first aspect of the present invention again, improved the durability of compressor, the necessary intensity of compressor housing can be reduced, can reduce cost.
And, a fourth aspect of the present invention is furnished with: the reverse drive formula two-stage compressor that will have rudimentary side compressor and senior side compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula two-stage compressor with water cooling, electric expansion valve, the evaporimeter that carries out heat exchange with ambient atmos couples together the freezing cycle device that forms in turn, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water and in extraneous low outdoor temperature region, control the aperture of aforementioned electric expansion valve in the mode that high side pressure is descended, control the control device of the rotating speed of aforementioned reverse drive formula two-stage compressor simultaneously in the substantially invariable mode of compressor capacity.
Adopt this structure, both can suppress the decline of hot water heating efficiency, the same with aforementioned a second aspect of the present invention again, improved the durability of compressor, the necessary intensity of compressor housing can be reduced, can reduce cost.
And a fifth aspect of the present invention is, aforementioned the present invention first～4th in any one, the low zone of aforementioned ambient atmos temperature is below 0 ℃.
Adopt this structure, can control the ambient atmos temperature province that particularly has the height differential pressure problem in the prior art effectively.
And a sixth aspect of the present invention is, aforementioned second or fourth aspect in, aforementioned two-stage compressor in the seal casinghousing of the discharge gas that imports aforementioned rudimentary side compressor, is built-in with aforementioned rudimentary side compressor, senior side compressor and drive motor.
Adopt this structure, intermediate pressure acts in the compressor housing, and compressor casing pressure differential inside and outside and the compression case inside and outside reduces by half, and the power that acts on each position reduces.Thereby, further having improved the durability of compressor, the intensity of housing can further reduce.
And a seventh aspect of the present invention is that according to aforementioned first～the 6th aspect of the present invention, aforementioned freezing cycle device forms as the carbon dioxide of refrigerant and the mode that turns round under overcritical freeze cycle to fill.
Adopt this structure, in extraneous low outdoor temperature region, the effluent air temp of freeze cycle uprises, thereby, even carry out as previously described control, also can obtain the high-temperature-hot-water of the required degree of user.
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 curve map according to the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form.
Fig. 3 is the control curve map according to the electric expansion valve in the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form.
Fig. 4 is the compressor rotary speed control curve map according to the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form.
Fig. 5 is the control curve map according to the compressor capacity in the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form.
Concrete form of implementation
Below, the form of implementation that present invention will be described in detail with reference to the accompanying.Fig. 1 is the loop diagram according to the hot-water supply device of the invention process form, Fig. 2 is according to the control of the pressure in the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form curve map, Fig. 3 is the control curve map according to electric expansion valve in the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form, Fig. 4 is the control curve map according to compressor rotary speed in the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form, and Fig. 5 is the control curve map according to the compressor capacity in the low zone of the ambient atmos temperature of the hot-water supply device of the invention process form.In addition, in Fig. 1, solid arrow is represented the flow direction of refrigerant, and dotted arrow is represented the flow direction of temperature.
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 closed-loop path (refrigerant loop) that connects two-stage compressor 11, high-pressure side heat exchanger 12, electric expansion valve 13, evaporimeter 14, storage heater 15 in turn.Be filled with carbon dioxide (CO in this inside, closed-loop path
2), as alternative refrigerant by overcritical freeze cycle running.As the representative natural refrigerant of refrigeration, 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.
Two-stage compressor, exploitation is used for overcritical freezing cycle device, be built-in with rudimentary side compressor 11a, senior side compressor 11b in seal casinghousing, drive the common motor 11c of these compressors 11a and 11b, the suction side of the discharge side of rudimentary side compressor 11a and senior side compressor 11b is coupled together by pipe arrangement 11d.And, the space in the closed shell by intermediate-pressure gas, be that the discharge gas of rudimentary side compressor is full of.In addition, because effect has intermediate pressure in closed shell, acting on power on each position of each compressor and the closed shell pressure differential between inside and outside remains in the suitable scope, avoid acting on bigger power, therefore, can be used as the high and low vibration of reliability, low noise, high efficiency compressor.
And the motor of this two-stage compressor 11 is the reverse drive formula, utilizes the described control device 3 control operating frequencys in back, the control rotating speed.In addition, in the discharge pipe arrangement of senior side compressor 11b, be provided for detecting effluent air temp detector 31 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, the hot water supply water cooling that the cold media gas of the HTHP of discharging from senior side compressor 11b is sent from water storage box 21, this hot water supply water is heated by the heat that the HTHP refrigerant produces.
13 pairs of pressurized gas refrigerants by 12 coolings of high-pressure side heat exchanger of electric expansion valve reduce pressure, and it is driven by impulse motor.And, utilize the described control device 3 in back to carry out aperture control.
Hot water feeding unit 2 is furnished with water storage box 21, hot water circulating pump 22, hot water supply pipe arrangement 23, hot water supply pipe arrangement 24.
The upper and lower of water storage box 21 utilizes with heat exchanger 12b with respect to aforementioned water and comprises water and couple together with the hot water circulation loop P of connecting pipings 5,6.And, in water storage box 21, because gravitational difference makes that the temperature by top hot water is high more more.Therefore, the lower water of temperature of water storage box 21 bottoms is sent into water heat-exchange tube 12b, be directed at the top of water storage box 21 with the higher water of temperature of heat-exchange tube 12b heating by water, when forming hot water circulation loop P by this way, hot water circulating pump 22 is installed in this hot water circulation loop P.In addition, utilize the heating-up temperature detector 33 that is arranged on water storage box 21 tops to measure the top hot water temperature in the water storage box 21, the temperature that promptly heats.
Hot water supply pipe arrangement 23 is pipe arrangements that hot water is provided in hot water tap, bathtub etc., is connected the top of water storage box 21, can supply the hot water of the higher temperature in the water storage box 21.In addition, in this hot water supply loop, switch valve 25 is installed.
In addition, at extraneous gas temperature below-10 ℃ the time, because the chance of running seldom, so be beyond the running allowed band.And, more than 0 ℃ the time, owing to follow the rising low-pressure lateral pressure of ambient atmos temperature to rise, so rising along with the ambient atmos temperature of the mode that does not rise too high with high side pressure, it is big that the aperture of electric expansion valve 13 becomes, and simultaneously, the rotating speed of two-stage compressor 11 descended.
More particularly, reduce, high side pressure, the intermediate pressure that is equivalent to rudimentary side discharge pressure and low-pressure lateral pressure are controlled, they are descended shown in the dotted line among Fig. 2 corresponding to the ambient atmos temperature.In addition, the solid line among Fig. 2 is represented the pressure control curve in the existing heat-pump water heater.In addition, in the prior art, shown in the solid line among Fig. 2, by the aperture of control electric expansion valve 13 and the rotating speed of two-stage compressor 11, the control high side pressure makes it rise corresponding to the ambient atmos decrease of temperature.
And in order to obtain such pressure, the aperture of control electric expansion valve 13 shown in the dotted line of Fig. 3, makes it more gently dwindle than the existing mode shown in the solid line among the same figure.And the rotating speed of control reverse drive formula two-stage compressor 11 shown in the dotted line of Fig. 4, makes it more gently increase than the existing mode shown in the solid line among the same figure.Usually, when the ambient atmos temperature descends, suction pressure descends and compressor capacity descends, but under the situation of this form of implementation, shown in the dotted line of Fig. 4, owing to the part that low-pressure lateral pressure decline reduces compressor capacity is replenished, with the mode rev up of compressor capacity constant.Relative therewith, in the prior art, shown in the solid line of Fig. 5, be to control in the mode that increases compressor capacity corresponding to the ambient atmos decrease of temperature, corresponding to the ambient atmos decrease of temperature shown in the solid line of Fig. 4, biglyyer than the rotating speed that can increase compressor under the situation of this form of implementation.
According to above-mentioned control result, high side pressure and intermediate pressure poor, under the situation of prior art, increase with the ambient atmos decrease of temperature in the mode shown in the Δ P1a of Fig. 2, but, under the situation of this form of implementation, change hardly corresponding to the ambient atmos decrease of temperature in the mode shown in the Δ P1b of Fig. 2.In addition, no matter be Δ P2a under the prior art situation or the Δ P2b under this form of implementation situation, the difference of intermediate pressure and low-pressure lateral pressure changes hardly corresponding to the ambient atmos variation of temperature.Intermediate pressure and low-pressure lateral pressure are under prior art and any situation of this form of implementation, and all the decline owing to ambient atmos descends.
Like this, in the past, corresponding to the ambient atmos decrease of temperature, poor and the high side pressure of high side pressure and intermediate pressure and the difference of low-pressure lateral pressure become big corresponding to the ambient atmos decrease of temperature, thereby, become the power that acts on each position of compressor and become the reason that durability big, compressor descends, the compression efficiency of compressor descends.
Relative therewith, adopt this form of implementation, owing to these pressure differentials change hardly corresponding to the ambient atmos decrease of temperature, thus can improve the durability of compressor, and avoid the compression efficiency of compressor to descend.
And thinking of the present invention is not limited to the hot-water supply device of the overcritical freezing cycle device of above-mentioned employing, also goes for adopting the hot-water supply device of common freezing cycle device.But, in the hot-water supply device that adopts overcritical freezing cycle device, compare with the situation of the hot-water supply device that adopts common freezing cycle device, because high side pressure becomes very big, the difference of the poor and high side pressure of high side pressure and low-pressure lateral pressure and intermediate pressure becomes big, so be easy to generate the compressor durability problem that is caused by this pressure differential.Therefore, compare with the situation of the hot-water supply device that the present invention is used for the common freezing cycle device of existing employing, under the situation that the present invention is resembled the hot-water supply device that is used to adopt overcritical freezing cycle device this form of implementation, can obtain significant more effect.
And in this form of implementation, compressor is a two-stage compressor, is under the situation of single-stage compressor at compressor still, also can adopt the present invention.But, compare with single-stage compressor, owing to two-stage compressor height pressure differential at different levels diminishes, so can further improve the durability of compressor and improve compression efficiency.
Because the present invention adopts said structure, so can obtain following effect.
Adopt of the present invention first and the third aspect, compressor is single-stage compressor, at extraneous gas In the low zone of temperature, make the high pressure side pressure owing to be furnished with the decline corresponding to the ambient atmos temperature The mode that power descends is controlled the control device of electric expansion valve aperture, so the high-low pressure of compressor Difference diminishes, and needn't worry dump valve and leaf valve breakage, can improve the durability of compressor. And And the required intensity of compressor housing can reduce, and can reduce cost.
And, adopting of the present invention second and fourth aspect, compressor is for having rudimentary side pressure contracting The reverse drive formula two-stage compressor of machine and senior side compressor is in the low zone of extraneous gas temperature In, control aforementioned electric in the mode that the decline corresponding to the ambient atmos temperature descends high side pressure The aperture of moving expansion valve, thereby, with above-mentioned first and third party of compressor employing single-stage compressor The face situation is compared, and the high-low pressure difference of each stage compressor significantly reduces, and needn't worry dump valve or leaf The plate valve breakage can improve the durability of compressor. And the required intensity of compressor housing can Further to reduce, can reduce cost.
And, adopt third and fourth aspect of the present invention, because with corresponding to the ambient atmos temperature The substantially invariable mode of degree decline compressor capacity is controlled aforementioned reverse drive formula two-stage compressor Rotating speed was so in the situation that extraneous gas temperature descends, both suppressed the heating of hot water supply water The decline of ability has prevented that again the high-low pressure difference of compressor from increasing, and can improve the anti-of compressor The property used, and then the required intensity of compressor housing can reduce, and can reduce cost.
And, adopt a fifth aspect of the present invention, because first～the 4th in any one, The low zone of aforementioned ambient atmos temperature is below 0 ℃, so can be in the prior art particularly Effectively control in the in-problem ambient atmos temperature province of high-low pressure difference.
And, adopt a sixth aspect of the present invention and since aforementioned first～the 4th any one In, aforementioned two-stage compressor is with aforementioned rudimentary side compressor, senior side compressor and drives usefulness Motor is built in the interior two-stage of closed shell of the Exhaust Gas that imports aforementioned rudimentary side compressor Compressor is so intermediate pressure acts in the compressor housing compressor cylinder inside and outside and compression The inside and outside pressure differential of engine housing reduces by half, and the power that acts on each position reduces. Thereby, further carry The high durability of compressor, the intensity of housing also can further reduce.
And, adopt a seventh aspect of the present invention, aforementioned first～the 6th in any one, Aforementioned freezing cycle device is to advance as refrigerant and with overcritical freeze cycle with filling arbon dioxide The mode of row running forms, thereby, in the low zone of extraneous gas temperature, even before carrying out State the hot water supply water that control also can obtain high temperature.
Claims (7)
1. heat-pump water heater, be furnished with: with reverse drive formula single-stage compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula single-stage compressor with water cooling, electric expansion valve, carry out the freezing cycle device that the evaporimeter of heat exchange is connected in turn and forms with ambient atmos, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water with at 0 ℃--control the control device of the aperture of aforementioned electric expansion valve in the low temperature zone of 10 ℃ ambient atmos in the mode that high side pressure is descended.
2. heat-pump water heater, be furnished with: the reverse drive formula two-stage compressor that will have rudimentary side compressor and senior side compressor, utilize the high-pressure side heat exchanger of the gas that the hot water supply discharges from this reverse drive formula two-stage compressor with water cooling, electric expansion valve, carry out the freezing cycle device that the evaporimeter of heat exchange is connected in turn and forms with ambient atmos, can store by the water storage box of the hot water of aforementioned high-pressure side heat exchanger heats supply water with at 0 ℃--control the control device of the aperture of aforementioned electric expansion valve in the low temperature zone of 10 ℃ ambient atmos in the mode that high side pressure is descended.
3. heat-pump water heater as claimed in claim 1 is characterized in that: this control device is controlled the rotating speed of aforementioned inverse type single-stage compressor in the substantially invariable mode of compressor capacity in the aperture of the aforementioned electric expansion valve of described control.
4. heat-pump water heater as claimed in claim 2 is characterized in that: this control device is controlled the control device of the rotating speed of aforementioned reverse drive formula two-stage compressor in the substantially invariable mode of compressor capacity in the aperture of the aforementioned electric expansion valve of described control.
5. as any one described heat-pump water heater in the claim 1～4, it is characterized in that: the low zone of aforementioned ambient atmos temperature is below 0 ℃.
6. as claim 2 or 4 described heat-pump water heaters, it is characterized in that: aforementioned two-stage compressor, in the seal casinghousing of the discharge gas that imports aforementioned rudimentary side compressor, be built-in with aforementioned rudimentary side compressor, senior side compressor and drive motor.
7. as any one described heat-pump water heater in the claim 1～6, it is characterized in that: aforementioned freezing cycle device forms as the carbon dioxide of refrigerant and the mode that turns round under overcritical freeze cycle to fill.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP278523/2001 | 2001-09-13 | ||
| JP2001278523A JP4693308B2 (en) | 2001-09-13 | 2001-09-13 | Heat pump type water heater |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1405519A CN1405519A (en) | 2003-03-26 |
| CN1202397C true CN1202397C (en) | 2005-05-18 |
Family
ID=19102878
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB021416737A Expired - Fee Related CN1202397C (en) | 2001-09-13 | 2002-09-10 | Heat-pump type hot-water supplying device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP4693308B2 (en) |
| KR (1) | KR100500618B1 (en) |
| CN (1) | CN1202397C (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7802441B2 (en) | 2004-05-12 | 2010-09-28 | Electro Industries, Inc. | Heat pump with accumulator at boost compressor output |
| US7849700B2 (en) | 2004-05-12 | 2010-12-14 | Electro Industries, Inc. | Heat pump with forced air heating regulated by withdrawal of heat to a radiant heating system |
| JP4857866B2 (en) * | 2006-03-31 | 2012-01-18 | ダイキン工業株式会社 | Refrigeration equipment |
| KR100695974B1 (en) * | 2006-08-10 | 2007-03-16 | 주식회사 스코넷 | Heating equipment of heat pump type |
| WO2008018698A1 (en) * | 2006-08-10 | 2008-02-14 | Sconet Co., Ltd. | Heat pump-type heating apparatus |
| KR100695975B1 (en) * | 2006-08-21 | 2007-03-16 | 주식회사 스코넷 | Heat-pump type heating apparatus used as gas and water |
| WO2008023889A1 (en) * | 2006-08-21 | 2008-02-28 | Sconet Co., Ltd. | Heat pump-type heating apparatus of both air cooling and water cooling |
| JP5157224B2 (en) * | 2007-04-05 | 2013-03-06 | 東京電力株式会社 | Steam generation system |
| JP5113447B2 (en) * | 2007-08-09 | 2013-01-09 | 東芝キヤリア株式会社 | Control method for heat pump water heater |
| JP5228023B2 (en) * | 2010-10-29 | 2013-07-03 | 三菱電機株式会社 | Refrigeration cycle equipment |
| KR20120136854A (en) * | 2011-06-10 | 2012-12-20 | 삼성전자주식회사 | Water supply apparatus |
| JP5789535B2 (en) * | 2012-02-09 | 2015-10-07 | 日立アプライアンス株式会社 | Heat pump water heater |
| CN109028573B (en) * | 2018-06-05 | 2020-09-01 | 广东芬尼克兹节能设备有限公司 | Method and system for controlling working frequency of heat pump water heater compressor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63231132A (en) * | 1987-03-18 | 1988-09-27 | Hitachi Ltd | Defrosting control of variable capacity type airconditioning machine |
| JPH10220845A (en) * | 1997-02-07 | 1998-08-21 | Matsushita Electric Ind Co Ltd | Air conditioner |
| JP2000120572A (en) * | 1998-10-12 | 2000-04-25 | Sanyo Electric Co Ltd | Rotary compressor |
| JP3703995B2 (en) * | 1999-06-01 | 2005-10-05 | 松下電器産業株式会社 | Heat pump water heater |
| JP3700474B2 (en) * | 1999-06-01 | 2005-09-28 | 松下電器産業株式会社 | Heat pump water heater |
| JP3738637B2 (en) * | 2000-01-19 | 2006-01-25 | ダイキン工業株式会社 | Heat pump water heater |
-
2001
- 2001-09-13 JP JP2001278523A patent/JP4693308B2/en not_active Expired - Fee Related
-
2002
- 2002-09-10 CN CNB021416737A patent/CN1202397C/en not_active Expired - Fee Related
- 2002-09-12 KR KR10-2002-0055193A patent/KR100500618B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| JP2003090631A (en) | 2003-03-28 |
| KR20030023531A (en) | 2003-03-19 |
| JP4693308B2 (en) | 2011-06-01 |
| CN1405519A (en) | 2003-03-26 |
| KR100500618B1 (en) | 2005-07-18 |
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