CN103348197B - Refrigerating circulatory device - Google Patents

Refrigerating circulatory device Download PDF

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Publication number
CN103348197B
CN103348197B CN201280007707.4A CN201280007707A CN103348197B CN 103348197 B CN103348197 B CN 103348197B CN 201280007707 A CN201280007707 A CN 201280007707A CN 103348197 B CN103348197 B CN 103348197B
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CN
China
Prior art keywords
temperature
gas
throttling arrangement
liquid separation
cold
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CN201280007707.4A
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Chinese (zh)
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CN103348197A (en
Inventor
小须田修
嘉久和孝
冈市敦雄
奥村拓也
谷口和宏
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2400/01—Heaters
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • 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
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • 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
    • 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
    • F25B2700/2101—Temperatures in a bypass
    • 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
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • F25B2700/2109—Temperatures of a separator

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The invention provides a kind of refrigerating circulatory device (100), possess: the refrigerant loop (1) comprising upstream side throttling arrangement (14,18), gas-liquid separator (16) and downstream throttling arrangement (18,14); Jet path (22); Control device (30).Jet path (22) is provided with heater (24).Control device (30) carries out middle pressure-controlled running, in this middle pressure-controlled running, after becoming the mode aperture at least one party in upstream side throttling arrangement and downstream throttling arrangement less than setting with the temperature difference between the gas-liquid separation temperature making to be pressed by centre temperature sensor (26) to detect and the injection temperation detected by degree of superheat temperature sensor (28) and adjusting, increase the aperture of downstream throttling arrangement, until gas-liquid separation temperature reduces set point of temperature from temperature now.

Description

Refrigerating circulatory device
Technical field
The present invention relates to a kind of refrigerating circulatory device for hot water supply device, hot-water heater or air-conditioner etc.
Background technology
In the past, there will be a known and possessed compressor, cross valve, indoor heat exchanger, indoor throttling arrangement, gas-liquid separator, outside throttling arrangement, outdoor heat exchanger and can to refrigeration and the refrigerating circulatory device that switch of heating.Such as Patent Document 1 discloses refrigerating circulatory device 500 as shown in Figure 9.
In this refrigerating circulatory device 500, compressor 501 is connected with indoor heat exchanger 512 and outdoor heat exchanger 520 via cross valve 532, and indoor heat exchanger 512 is connected via indoor throttling arrangement 514, gas-liquid separator 516 and outside throttling arrangement 518 with outdoor heat exchanger 520.In addition, between gas-liquid separator 516 with compressor 510, be provided with the jet path 522 supplied to compressor 510 by the gas refrigerant of pressing in the middle of after being separated by gas-liquid separator 516.And then, in order to voltage-controlled for centre being made as is become desired value, be provided with in refrigerating circulatory device 500 heat-exchange temperature sensor 544,546 that condensation temperature and the evaporating temperature of cold-producing medium are detected and to the temperature of the cold-producing medium in gas-liquid separator 516 namely in the middle of pressure temperature detect in the middle of pressure temperature sensor 526.
About the refrigerating circulatory device 500 formed as mentioned above, below its action is described.When heating, the cold-producing medium sprayed from compressor 510, by after cross valve 532, carries out heat exchange in indoor heat exchanger 512, and be middle pressure by indoor throttling arrangement 514 from high pressure relief.The cold-producing medium of middle pressure is separated into gas refrigerant and liquid refrigerant in gas-liquid separator 516, and the gas refrigerant of middle pressure is supplied to compressor 510 by jet path 522.On the other hand, the liquid refrigerant of middle pressure is reduced pressure further by outside throttling arrangement 518, and the cold-producing medium of post-decompression low pressure carries out heat exchange in outdoor heat exchanger 520, after have passed cross valve 532, is inhaled in compressor 510.When freezing, the cold-producing medium sprayed from compressor 510, by after cross valve 532, carries out heat exchange in outdoor heat exchanger 520, and be middle pressure by outside throttling arrangement 518 from high pressure relief.The cold-producing medium of middle pressure is separated into gas refrigerant and liquid refrigerant in gas-liquid separator 516, and the gas refrigerant of middle pressure is supplied to compressor 510 by jet path 522.On the other hand, the liquid refrigerant of middle pressure is reduced pressure further by indoor throttling arrangement 514, and the cold-producing medium of post-decompression low pressure carries out heat exchange in indoor heat exchanger 512, after have passed cross valve 532, is inhaled in compressor 510.
In addition, in refrigerating circulatory device 500, control device 530 determines the middle pressure temperature of target according to the condensation temperature detected by heat-exchange temperature sensor 544,546 and evaporating temperature, and with make by centre press temperature sensor 526 to detect in the middle of pressure temperature become target in the middle of the aperture of throttling arrangement (during heating be outside throttling arrangement 516, and when freezing be indoor throttling arrangement 514) of mode to the downstream being positioned at gas-liquid separator 516 of pressure temperature adjust.
[look-ahead technique document]
[patent document]
[patent document 1]: Japan Patent No. 3317170 description
[brief summary of the invention]
[inventing problem to be solved]
But the refrigerating circulatory device 500 shown in Fig. 9 has the leeway of further improved efficiency.
Summary of the invention
The disclosure is made in view of such situation, its object is to, the efficiency of refrigerating circulatory device is improved.
[for solving the mechanism of problem]
The disclosure provides a kind of refrigerating circulatory device, possesses: refrigerant loop, and it makes cold-producing medium to be circulated by the mode of compressor, condenser, upstream side throttling arrangement, gas-liquid separator, downstream throttling arrangement and evaporimeter successively; Jet path, it supplies by the gas refrigerant after described gas-liquid separator separates to described compressor; Heater, it is located at described jet path; Middle pressure temperature sensor, it detects the temperature of the cold-producing medium flowed into described jet path from described refrigerant loop and gas-liquid separation temperature; Degree of superheat temperature sensor, it is detected by the temperature of the cold-producing medium after described heater heating and injection temperation in described jet path; Control device, it carries out middle pressure-controlled running, in this middle pressure-controlled running, to make the temperature difference between described gas-liquid separation temperature and described injection temperation become after the aperture of mode at least one party in described upstream side throttling arrangement and described downstream throttling arrangement less than setting adjust, increase the aperture of described downstream throttling arrangement, until described gas-liquid separation temperature reduces set point of temperature from temperature now.
[invention effect]
According to above-mentioned structure, by the fiducial temperature adopting heater and degree of superheat temperature sensor to determine gas-liquid separation temperature, and the temperature of set point of temperature lower than this fiducial temperature is set to the target temperature of gas-liquid separation temperature, the evaluated error of middle pressure temperature sensor can be eliminated thus.Thereby, it is possible to value for the purpose of centre pressure more precisely being controlled, thus the efficiency of refrigerating circulatory device is improved.
Accompanying drawing explanation
Fig. 1 is the structure chart of the refrigerating circulatory device involved by the first embodiment of the present invention.
Fig. 2 is the flow chart of the control method of the middle pressure-controlled running represented in the first embodiment.
Fig. 3 is the curve map of the change of the aperture representing upstream side throttling arrangement in the first embodiment and downstream throttling arrangement and the change of ejection temperature, injection temperation and gas-liquid separation temperature.
Fig. 4 is the figure of the heater represented involved by a variation.
Fig. 5 is the structure chart of the refrigerating circulatory device involved by another variation.
Fig. 6 is the structure chart of the refrigerating circulatory device again involved by a variation.
Fig. 7 is the structure chart of the refrigerating circulatory device involved by the second embodiment of the present invention.
Fig. 8 is the flow chart of the control method of the middle pressure-controlled running represented in the second embodiment.
Fig. 9 is the structure chart of existing refrigerating circulatory device.
Detailed description of the invention
In the refrigerating circulatory device 500 shown in Fig. 9, compress into row according to the centre of the temperature detected by three temperature sensors 544,546,526 to the cold-producing medium supplied to compressor 510 by jet path 522 from gas-liquid separator 516 to control, therefore the deviation of precision that temperature sensor has becomes problem.In normally used temperature sensor, at least there is the evaluated error of ± 1.5 DEG C.When refrigerating circulatory device 500 as shown in Figure 9 uses multiple temperature sensor to control like that, with the number of temperature sensor correspondingly, evaluated error is also accumulated (if each is ± 1.5 DEG C, being then ± 4.5 DEG C during use three).Therefore, in the middle of working control, pressure deviates from from desired value, often causes the efficiency of refrigerating circulatory device to reduce.
First method of the present disclosure provides a kind of refrigerating circulatory device, wherein, possess: refrigerant loop, it makes cold-producing medium to be circulated by the mode of compressor, condenser, upstream side throttling arrangement, gas-liquid separator, downstream throttling arrangement and evaporimeter successively; Jet path, it supplies by the gas refrigerant after described gas-liquid separator separates to described compressor; Heater, it is located at described jet path; Middle pressure temperature sensor, it detects the temperature of the cold-producing medium flowed into described jet path from described refrigerant loop and gas-liquid separation temperature; Degree of superheat temperature sensor, it is detected by the temperature of the cold-producing medium after described heater heating and injection temperation in described jet path; Control device, it carries out middle pressure-controlled running, in this middle pressure-controlled running, to make the temperature difference between described gas-liquid separation temperature and described injection temperation become after the aperture of mode at least one party in described upstream side throttling arrangement and described downstream throttling arrangement less than setting adjust, increase the aperture of described downstream throttling arrangement, until described gas-liquid separation temperature reduces set point of temperature from temperature now.
Second method of the present disclosure is on the basis of first method, a kind of refrigerating circulatory device is provided, wherein, also possesses temperature sensor after condensation, after this condensation, temperature sensor detects the temperature of the cold-producing medium flowed out from described condenser and condensation side outlet temperature, described control device is in described middle pressure-controlled running, described gas-liquid separation temperature when using the temperature difference between described gas-liquid separation temperature and described injection temperation to become less than setting and described condensation side outlet temperature, the calculating formula of the gas-liquid separation temperature used in steady running is revised.
According to second method, in middle pressure-controlled running, gas-liquid separation temperature when the temperature difference between gas-liquid separation temperature and described injection temperation can be used to become less than setting and condensation side outlet temperature, thus the calculating formula of the gas-liquid separation temperature used in steady running is revised.
Third Way of the present disclosure is on the basis of second method, a kind of refrigerating circulatory device is provided, wherein, also possesses the front temperature sensor of evaporation, the temperature of cold-producing medium that before this evaporation, evaporimeter described in temperature sensor subtend flows into and evaporation side inlet temperature detect, when the calculating formula of the gas-liquid separation temperature that described control device uses in steady running is revised, described evaporation side inlet temperature when also using the temperature difference between described gas-liquid separation temperature and described injection temperation to become less than setting.
According to Third Way, in middle pressure-controlled running, gas-liquid separation temperature when the temperature difference between gas-liquid separation temperature and described injection temperation can be used to become less than setting, condensation side outlet temperature and evaporation side inlet temperature, thus the calculating formula of the gas-liquid separation temperature used in steady running is revised.
Fourth way of the present disclosure, on the basis of second method or Third Way, provides a kind of refrigerating circulatory device, and wherein, described control device is used in the calculating formula of revised gas-liquid separation temperature in described middle pressure-controlled running to carry out steady running.
According to fourth way, the more high-precision middle pressure-controlled of the evaluated error also contemplating temperature sensor etc. can be carried out in steady running.
On the basis of the either type of the 5th mode of the present disclosure in first ~ fourth way, provide a kind of refrigerating circulatory device, wherein, described control device carries out described middle pressure-controlled running when starting operation.
According to the 5th mode, refrigerating circulatory device can shift to steady running from starting operation with the state of the best.
On the basis of the either type of the 6th mode of the present disclosure in the first ~ five mode, provide a kind of refrigerating circulatory device, wherein, described control device carries out described middle pressure-controlled running in the midway of steady running.
According to the 6th mode, also carry out middle pressure-controlled running in the midway of steady running, be more precisely worth for the purpose of middle pressure-controlled.
7th mode of the present disclosure is on the basis of the 5th mode, a kind of refrigerating circulatory device is provided, wherein, also possesses ejection temperature sensor, namely this ejection temperature sensor sprays temperature to the temperature of the cold-producing medium sprayed from described compressor and detects, described control device adjusts with the aperture of mode to described upstream side throttling arrangement near the ejection temperature making described ejection temperature remain on target, and reduce the aperture of described downstream throttling arrangement simultaneously, until the temperature difference between described gas-liquid separation temperature and described injection temperation becomes less than setting, then the aperture of described downstream throttling arrangement is increased.
According to the 7th mode, by utilizing upstream side throttling arrangement to control ejection temperature, and utilizing downstream throttling arrangement to control gas-liquid separation temperature, easy control can be realized thus.
On the basis of the either type of eighth mode of the present disclosure in the first ~ seven mode, a kind of refrigerating circulatory device is provided, wherein, described refrigerant loop comprises the indoor heat exchanger and the outdoor heat exchanger that play function as described condenser and described evaporimeter, and comprise the indoor throttling arrangement and the outside throttling arrangement that play function as described upstream side throttling arrangement and described downstream throttling arrangement, in described refrigerant loop, be provided with the cross valve that the flow direction of cold-producing medium is switched.
According to eighth mode, achieve the refrigerating circulatory device that can carry out the switching of freezing and heating.
On the basis of the either type of the 9th mode of the present disclosure in first ~ eighth mode, provide a kind of refrigerating circulatory device, wherein, described heater is electric heater.
According to the 9th mode, electric heater easily carries out connecting-cutting-off controlling, therefore, it is possible to only needing to heat the cold-producing medium flowed in jet path when heating the cold-producing medium flowed in jet path.
On the basis of the either type of the tenth mode of the present disclosure in first ~ eighth mode, a kind of refrigerating circulatory device is provided, wherein, described heater is accumulate the heat of discharging from described compressor, and utilizes the thermal storage unit that the heat of this accumulation heats cold-producing medium.
According to the tenth mode, utilize the used heat of compressor and the cold-producing medium flowed in jet path is heated.
On the basis of the either type of the 11 mode of the present disclosure in first ~ eighth mode, a kind of refrigerating circulatory device is provided, wherein, described heater is the heat exchanger comprising the first heat exchanging part and the second heat exchanging part, the cold-producing medium flowed in described jet path imports described first heat exchanging part, flowing in described refrigerant loop and import described second heat exchanging part with the cold-producing medium that described gas-liquid separation temperature is in a ratio of high temperature, in described heat exchanger, described second heat exchanging part heats described first heat exchanging part.
According to the 11 mode, utilize the heat that the cold-producing medium flowed in refrigerant loop has, the cold-producing medium flowed in jet path is heated.
12 mode of the present disclosure, on the basis of the 11 mode, provides a kind of refrigerating circulatory device, wherein, guides to described second heat exchanging part the cold-producing medium flowed between described compressor and described condenser.
According to the 12 mode, utilize the heat for having than the cold-producing medium of higher temperatures flowed in refrigerant loop, the cold-producing medium flowed in jet path is heated.
13 mode of the present disclosure, on the basis of the 11 mode, provides a kind of refrigerating circulatory device, wherein, guides to described second heat exchanging part the cold-producing medium flowed between described condenser and described upstream side throttling arrangement.
According to the 13 mode, utilize the heat that the cold-producing medium flowed in refrigerant loop has, the cold-producing medium of flowing in jet path 22 is heated.In addition, the degree of subcooling of the cold-producing medium of the condensator outlet side of refrigerant loop raises, therefore the ability of refrigerating circulatory device is improved.
Below, about embodiments of the present invention, limit is described in detail with reference to accompanying drawing limit.It should be noted that, the following description is the explanation about an example of the present invention, and the present invention is defined not by these contents.
(the first embodiment)
Fig. 1 represents the refrigerating circulatory device 100 involved by the first embodiment of the present disclosure.This refrigerating circulatory device 100 possesses the refrigerant loop 1 and control device 30 that make refrigerant circulation.
Refrigerant loop 1 comprises compressor 10, cross valve 32, indoor heat exchanger 12, indoor throttling arrangement 14, gas-liquid separator 16, outside throttling arrangement 18 and outdoor heat exchanger 20.Four mouths of cross valve 32 are connected with the suction inlet of compressor 10 and ejiction opening and indoor heat exchanger 12 and outdoor heat exchanger 20 by refrigerant piping.In addition, indoor heat exchanger 12, indoor throttling arrangement 14, gas-liquid separator 16, outside throttling arrangement 18 and outdoor heat exchanger 20 are connected in series by refrigerant piping.
The flow direction of cold-producing medium switches to by the first direction shown in solid arrow when heating by cross valve 32, switches to by the second direction shown in dotted arrow when freezing.In a first direction, the ejiction opening of compressor 10 is connected with indoor heat exchanger 12, and the suction inlet of compressor 10 is connected with outdoor heat exchanger 20.In a second direction, the ejiction opening of compressor 10 is connected with outdoor heat exchanger 20, and the suction inlet of compressor 10 is connected with outdoor heat exchanger 12.Namely, the cold-producing medium of circulation in refrigerant loop 1 successively by compressor 10, indoor heat exchanger 12, indoor throttling arrangement 14, gas-liquid separator 16, outside throttling arrangement 18 and outdoor heat exchanger 20, successively passes through compressor 10, outdoor heat exchanger 20, outside throttling arrangement 18, gas-liquid separator 16, indoor throttling arrangement 14 and indoor heat exchanger 12 when freezing when heating.
Indoor heat exchanger 12 plays function when heating as condenser, plays function when freezing as evaporimeter.On the other hand, outdoor heat exchanger 20 plays function when heating as evaporimeter, plays function when heating as condenser.
As indoor throttling arrangement 14 and outside throttling arrangement 18, such as, adopt the electric expansion valve that can adjust aperture.Control device 30 to indoor throttling arrangement 14 and outside throttling arrangement 18 pipage control signal, and adjusts their aperture.
In addition, between gas-liquid separator 16 with compressor 10, be provided with the jet path 22 supplied to compressor 10 by the middle gas refrigerant of pressing be separated by gas-liquid separator 16.Jet path 22 is such as linked by the gas blanket side of one end and gas-liquid separator 16, and the other end is formed with the refrigerant piping of pressing suction inlet to link in the middle of the discharge chambe opening of compressor 10 in compression process.Be provided with heater 24 in the midway of jet path 22, the intermediate pressure gas cryogen of flowing in jet path 22 is by spraying to compressor 10 afterwards of heating.
As heater 24, such as, can adopt heater (heater), i.e. electric heater.As electric heater, resistance heater, induction heater etc. can be enumerated.Heater 24 is non-essential to be heated the cold-producing medium of flowing in jet path 22 all the time, such as also by the connection-cutting-off controlling of electric heater, only when middle pressure-controlled running described later, the cold-producing medium of flowing in jet path 22 can be heated.
And then, be provided with in refrigerating circulatory device 100: namely the ejection temperature sensor 34 that temperature Td detects is sprayed to the temperature of the cold-producing medium sprayed from compressor 10; To the outdoor temperature sensor 36 that outdoor temperature To detects; To the indoor temperature transmitter 38 that indoor temperature Ti detects; To the middle pressure temperature sensor 26 that temperature and the gas-liquid separation temperature Tm of the cold-producing medium flowed into from refrigerant loop 1 to jet path 22 detect; To the degree of superheat temperature sensor 28 that temperature and the injection temperation Tinj of the cold-producing medium after being heated by heater 24 in jet path 22 detect.The main temperature according to being detected by various temperature sensor of control device 30, controls indoor throttling arrangement 14 and the aperture of outside throttling arrangement 18 and the rotating speed of compressor 10.
It should be noted that, middle pressure temperature sensor 26 both can be arranged on gas-liquid separator 16, also can be arranged on the position of the ratio heater 24 upstream side of the refrigerant piping forming jet path 22.Or middle pressure temperature sensor 26 also can be arranged on the refrigerant piping that is connected with indoor throttling arrangement 14 by gas-liquid separator 16 or on the refrigerant piping that is connected with outside throttling arrangement 18 by gas-liquid separator 16.Degree of superheat temperature sensor 28 is arranged on the position of ratio heater 24 side farther downstream of the refrigerant piping forming jet path 22.
Then, the action of refrigerating circulatory device 100 is described.
When heating, by cross valve 32, the flow direction of cold-producing medium is switched to by the first direction shown in solid arrow.In this state, guided by indoor heat exchanger 12 from after compressor 10 sprays by the cold-producing medium after compressor 10 compresses.The cold-producing medium being directed to indoor heat exchanger 12, is guided to after room air heat radiation by indoor throttling arrangement 14 at this.The cold-producing medium being directed to indoor throttling arrangement 14 is depressurized in indoor throttling arrangement 14, becomes the middle compression refrigerant of the pressure of the centre with condensing pressure and evaporating pressure and is guided by gas-liquid separator 16.The middle compression refrigerant being directed to gas-liquid separator 16 is separated in gas-liquid separator 16, and the liquid refrigerant among middle compression refrigerant is guided by outside throttling arrangement 18, and gas refrigerant flows into jet path 22.The middle press liquid cold-producing medium being directed to outside throttling arrangement 18 is depressurized in outside throttling arrangement 18, and is guided by outdoor heat exchanger 20, and afterwards, air heat absorption outdoor, then returns compressor 10.After the intermediate pressure gas cryogen flowed into jet path 22 is heated by heater 24, sprayed by compressor 10.
When freezing, by cross valve 32, the flow direction of cold-producing medium is switched to by the second direction shown in dotted arrow.In this state, guided by outdoor heat exchanger 20 from after compressor 10 sprays by the cold-producing medium after compressor 10 compresses.The cold-producing medium being directed to outdoor heat exchanger 20, is guided to after outdoor air heat radiation by outside throttling arrangement 18 at this.The cold-producing medium being directed to outside throttling arrangement 18 is depressurized in outside throttling arrangement 18, becomes the middle compression refrigerant of the pressure of the centre with condensing pressure and evaporating pressure and is guided by gas-liquid separator 16.The middle compression refrigerant being directed to gas-liquid separator 16 is separated in gas-liquid separator 16, and the liquid refrigerant among middle compression refrigerant is guided by indoor throttling arrangement 14, and gas refrigerant flows into jet path 22.The middle press liquid cold-producing medium being directed to indoor throttling arrangement 14 is depressurized in indoor throttling arrangement 14, and is guided by indoor heat exchanger 12, and afterwards, air heat absorption indoor, then returns compressor 10.After the intermediate pressure gas cryogen flowed into jet path 22 is heated by heater 24, sprayed by compressor 10.
Time when heating with refrigeration, the flow direction of the cold-producing medium in refrigerant loop 1 is different, but cold-producing medium flows to equidirectional in jet path 22, therefore can adopt when heating and when freezing as the method for pressing in the middle of control and use the same method.Below, outdoor heat exchanger 20 when the indoor heat exchanger 12 during heating and refrigeration is called condenser, indoor heat exchanger 12 when the outdoor heat exchanger 20 during heating and refrigeration is called evaporimeter, outside throttling arrangement 18 when the indoor throttling arrangement 14 during heating and refrigeration is called upstream side throttling arrangement, indoor throttling arrangement 14 when the outside throttling arrangement 18 during heating and refrigeration is called downstream throttling arrangement, and is not described with being distinguished with during refrigeration during heating.
In the present embodiment, control device 30 carries out middle pressure-controlled running when starting operation.So-called " middle pressure-controlled running " refers to, to make to be pressed by centre the temperature difference between the gas-liquid separation temperature Tm that detects of the temperature sensor 26 and injection temperation Tinj detected by degree of superheat temperature sensor 28 to become after the aperture of mode at least one party in upstream side throttling arrangement and downstream throttling arrangement less than setting Δ Ti adjust, increase the aperture of downstream throttling arrangement, until gas-liquid separation temperature Tm reduces the running of set point of temperature Δ Tm from temperature now.Below, explain with reference to the flow chart of figure 2 the middle pressure-controlled running that control device 30 carries out.
First, control device 30 adjusts with the aperture of mode to upstream side throttling arrangement near the ejection temperature TD making to remain on target by the ejection temperature Td that detects of ejection temperature sensor 34, reduce the aperture of downstream throttling arrangement, until the temperature difference between gas-liquid separation temperature Tm and injection temperation Tinj becomes less than setting Δ Ti simultaneously.
Specifically, control device 30 utilizes outdoor temperature sensor 36 couples of outdoor temperature To detect, and utilizes indoor temperature transmitter 38 couples of indoor temperature Ti to detect (step S1).Then, control device 30, according to the outdoor temperature To detected and indoor temperature Ti, determines the ejection temperature TD (step S2) of target.Then, control device 30 utilizes ejection temperature sensor 34 to detect (step S3) ejection temperature Td, and the difference of the ejection temperature Td of itself and target and predetermined permissible value Δ Td (such as, 1.5 DEG C) are compared (step S4).
When the difference of the ejection temperature TD of the ejection temperature Td detected and target is feasible value more than Δ Td (being no in step S4), the aperture of control device 30 pairs of upstream side throttling arrangements adjusts (step S5).Specifically, control device 30 reduces the aperture of upstream side throttling arrangement when the ejection temperature Td detected is lower than the ejection temperature TD of target, and increases the aperture of upstream side throttling arrangement when the ejection temperature TD height of the ejection temperature Td detected than target.After step S5, return step S1.By repeatedly carrying out step S1 ~ S5, within making the fixed temperature of actual ejection temperature Td close to the ejection temperature TD of target.Consequently, if the difference of the ejection temperature TD of the ejection temperature Td detected and target is less than feasible value Δ Td (being yes in step S4), then step S6 is entered.
In step s 6, control device 30 utilizes the gas-liquid separation temperature Tm of middle pressure temperature sensor 26 to middle compression refrigerant to detect, and utilizes the injection temperation Tinj of degree of superheat temperature sensor 28 to the cold-producing medium that have passed after heater 24 to detect (step S6).Then, control device 30 judges whether the temperature difference between gas-liquid separation temperature Tm and injection temperation Tinj is less than predetermined setting Δ Ti (such as, 3 DEG C) (step S7).
Temperature difference between gas-liquid separation temperature Tm and injection temperation Tinj is the degree of superheat of sprayed gas refrigerant.In prior art, be not provided with heater 24 at jet path 22, therefore the intermediate pressure gas cryogen sprayed can not obtain the degree of superheat.Correspondingly thereto, in the present embodiment, by arranging heater 24 at jet path 22, as long as only gas refrigerant flows in jet path 22, then the intermediate pressure gas cryogen that have passed after heater 24 can obtain the degree of superheat.
When being no in the step s 7, namely when the degree of superheat obtains more than fixed temperature, control device 30 reduces the aperture (step S8) of downstream throttling arrangement, and makes gas-liquid separation temperature Tm increase.After step S8, return step S1.Control device 30 carries out step S1 ~ S8 repeatedly, until become in the step s 7 is.
When reducing the aperture of downstream throttling arrangement, the pressure differential of the front and back of downstream throttling arrangement becomes large, is accompanied by this, and middle pressure uprises.In addition, the ratio of the flow of the cold-producing medium sprayed also increases.When centre press rise time, the aridity of the middle compression refrigerant in gas-liquid separator 16 reduces.As mentioned above, when continuing the aperture reducing downstream throttling arrangement, aridity continues to reduce, and the flow of the cold-producing medium sprayed continues to increase, therefore flows into jet path 22 at a certain stage liquid cold-producing medium.
When liquid refrigerant flows into jet path 22, heated by heater 24 pairs of liquid refrigerants and make it evaporate, therefore under the effect of latent heat at this moment, the injection temperation Tinj that have passed the cold-producing medium after heater 24 reduces sharp.Step S7 is the step detected for reducing this situation sharp to injection temperation Tinj.
When being yes in the step s 7, namely when injection temperation Tinj is reduced sharp and failed by the gas refrigerant after heater 24 to obtain the degree of superheat more than fixed temperature, gas-liquid separation temperature Tm is now recorded as Tm0 (step S9) by control device 30.
By improving intermediate pressure, the amount of work of second compression again in compressor 10 can be reduced, therefore the electric power consumption of compressor 10 can be reduced.But when liquid refrigerant starts to flow to jet path 22, the amount of the liquid refrigerant flowed in evaporimeter also reduces, evaporability reduces, and the performance of kind of refrigeration cycle also reduces.Thus, in order to obtain higher performance in the refrigerating circulatory device 100 carrying out spraying, need the state being formed as by jet path 22 only having gas refrigerant to flow.Therefore, the gas-liquid separation temperature Tm1 (step S10) of target determined by control device 30.Specifically, the situation that control device 30 flows into jet path 22 to reliably prevent liquid refrigerant, gas-liquid separation temperature Tm0 the state that gas refrigerant after being in by heater 24 cannot obtain the degree of superheat of more than fixed temperature deducts the set point of temperature that pre-determines out (such as, 1 DEG C), calculate the gas-liquid separation temperature Tm1 of target thus.
After step S10, again the aperture of downstream throttling arrangement adjusted and middle pressure and gas-liquid separation temperature Tm are declined, thus becoming the state only having gas refrigerant to flow in jet path 22.Specifically, control device 30 utilizes middle pressure temperature sensor 26 to detect (step S11) the gas-liquid separation temperature Tm that centre press, and itself and the gas-liquid separation temperature Tm1 of target that determines in step slo is compared (step S12).When the gas-liquid separation temperature Tm detected is more than the gas-liquid separation temperature Tm1 of target (being no in step S12), increases the aperture (step S13) of downstream throttling arrangement, make middle drops.Increase the aperture of downstream throttling arrangement and gas-liquid separation temperature Tm1 lower than target time (being yes in step S12), to keep the ejection temperature of target, the steady running carrying out controlling of the mode of the gas-liquid separation temperature of target shifts (step S14).
After steady running transfer, in the middle of control device 30 also utilizes, pressure temperature sensor 26 and ejection temperature sensor 34 detect gas-liquid separation temperature Tm and ejection temperature Td, and to make them not adjust away from the aperture of mode to upstream side throttling arrangement and downstream throttling arrangement of desired value.
The control of gas-liquid separation temperature Tm is undertaken by the adjustment of the aperture of downstream throttling arrangement.Specifically, adjust with the aperture of mode to downstream throttling arrangement making the gas-liquid separation temperature Tm1 of the gas-liquid separation temperature Tm distance target detected become within fixed temperature Δ Tms.When gas-liquid separation temperature Tm is lower than Tm1-Δ Tms, reduces the aperture of downstream throttling arrangement, make gas-liquid separation temperature Tm increase, and make Tm close to Tm1.On the contrary, when gas-liquid separation temperature Tm is higher than Tm1+ Δ Tms, increases the aperture of downstream throttling arrangement, gas-liquid separation temperature Tm is declined, and makes Tm close to Tm1.The adjustment amount of the aperture of the downstream throttling arrangement during this adjustment both can be fixing, also more more can reduce the adjustment amount of aperture close to desired value.
The control of ejection temperature Td is undertaken by the adjustment of the aperture of upstream side throttling arrangement.Specifically, adjust with the aperture of mode to upstream side throttling arrangement making the ejection temperature TD of the ejection temperature Td distance target detected become within fixed temperature Δ Tds.When spraying temperature Td and being lower than TD-Δ Tds, reduce the aperture of upstream side throttling arrangement, make ejection temperature Td increase, and make Td close to TD.On the contrary, when spraying temperature Td and being higher than Td+ Δ Tds, increase the aperture of upstream side throttling arrangement, ejection temperature Td is declined, and makes Td close to TD.The adjustment amount of the aperture of the upstream side throttling arrangement during this adjustment both can be fixing, also more more can reduce the adjustment amount of aperture close to desired value.
As shown in Figure 1, gas-liquid separator 16 is configured between upstream side throttling arrangement and downstream throttling arrangement, therefore gas-liquid separation temperature Tm is subject to the very large impact of the adjustment of the aperture of upstream side throttling arrangement.Specifically, when reducing the aperture of upstream side throttling arrangement, the differential pressure before and after upstream side throttling arrangement becomes large, and be accompanied by this, middle pressure drop is low, and gas-liquid separation temperature Tm reduces.On the contrary, when increasing the aperture of upstream side throttling arrangement, the differential pressure before and after upstream side throttling arrangement diminishes, and is accompanied by this, and centre presses liter, and gas-liquid separation temperature Tm rises.So, the adjustment of the aperture of upstream side throttling arrangement not only gives impact for ejection temperature Td, also gives impact for gas-liquid separation temperature Tm.This situation is not limited to upstream side throttling arrangement, and when carrying out the adjustment of aperture of downstream throttling arrangement, to the amount change of the cold-producing medium of evaporimeter flowing, the suction condition change of compressor 10, therefore the adjustment of the aperture of downstream throttling arrangement not only gives impact for gas-liquid separation temperature Tm, also give impact for ejection temperature Td.
So, the aperture adjustment separately of upstream side throttling arrangement and downstream throttling arrangement gives impact to ejection temperature Td and gas-liquid separation temperature Tm respectively, but, when utilizing upstream side throttling arrangement to control ejection temperature Td, and utilize downstream throttling arrangement to control gas-liquid separation temperature Tm such each throttling arrangement is had respectively control as land used time, can realize controlling more easily.
Fig. 3 shows in above-mentioned middle pressure-controlled running, the situation how aperture of upstream side throttling arrangement and downstream throttling arrangement and ejection temperature Td, injection temperation Tinj and gas-liquid separation temperature Tm change.As shown in Figure 3, in the present embodiment, first, the aperture of upstream side throttling arrangement is little by little reduced, and spray temperature Td and little by little rise.Then, the aperture of downstream throttling arrangement is reduced, until injection temperation Tinj reduces sharp, then the aperture of downstream throttling arrangement is increased.
In middle pressure-controlled running described above, heater 24 and degree of superheat temperature sensor 28 is adopted to determine the fiducial temperature Tm0 of gas-liquid separation temperature Tm, and the temperature than this fiducial temperature Tm0 low set point of temperature Δ Tm is set to the target temperature Tm1 of gas-liquid separation temperature, the evaluated error of middle pressure temperature sensor 26 can be eliminated thus.Thereby, it is possible to value for the purpose of centre pressure more precisely being controlled, thus the efficiency of refrigerating circulatory device 100 can be made to improve.
In addition, in the present embodiment, when starting operation, middle pressure-controlled running is carried out, therefore, it is possible to shift to steady running from starting operation with the state of the best.
< variation >
In said embodiment, when starting operation, middle pressure-controlled running has been carried out.Therefore, adjust to make the temperature difference between gas-liquid separation temperature Tm and injection temperation Tinj become the aperture of mode to upstream side throttling arrangement and downstream these both sides of throttling arrangement less than setting.But control device 30 also can carry out middle pressure-controlled running in the midway of steady running.In this case, also can adjust the aperture of either party in upstream side throttling arrangement and downstream throttling arrangement to make the temperature difference between gas-liquid separation temperature Tm and injection temperation Tinj become the mode less than setting.
Flow chart when carrying out the running of middle pressure-controlled in the midway of steady running is identical with Fig. 2.That is, step S1 is entered when meeting some decision condition in steady running.Such as, step S1 can be entered when gas variations in temperature, cycling condition change greatly outside etc., also can enter step S1 according to the change of the requirement of user side.Or, also can enter step S1 according to the elapsed time from operating and starting.
In said embodiment, electric heater is employed as heater 24.But heater 24 is not limited to the outside from refrigerant loop 1 such as electric heater applies heat mechanism to cold-producing medium.Such as, also can be direct or indirectly contact by making the closed container of a part for the refrigerant piping of formation jet path 22 and the compressor 10 of the cold-producing medium of pressing than centre (gas-liquid separation temperature) high temperature that temperature is high or spraying pipe arrangement etc., a part for refrigerant loop 1 forms heater 24 thus.Below, the variation of heater 24 is described in detail.It should be noted that, variation shown below, except the situation of special instruction, is all formed in the same manner as described embodiment.
Fig. 4 represents the heater 24A of the variation as heater 24.Heater 24A accumulates the heat of discharging from compressor 10, and utilizes the thermal storage unit that the cold-producing medium of the heat of this accumulation to flowing in jet path 22 heats.Specifically, heater 24A has: the heat accumulation member 50 configured in the mode wrapped into by compressor 10; The serpentine pipe 52 snaked through in the inside of heat accumulation member 50.Serpentine pipe 52 forms a part for jet path 22.Thus, the cold-producing medium flowed into from gas-liquid separator 16 to jet path 22 is heated by flowing serpentine pipe 52.And then the cold-producing medium that have passed serpentine pipe 52 is sprayed by compressor 10.Thereby, it is possible to utilize the used heat of compressor 10, the cold-producing medium of flowing in jet path 22 is heated.Due to without the need in order to heat the cold-producing medium of flowing in jet path 22 and arrange independently electric heater, therefore the saving electrification of refrigerating circulatory device can be realized.
Fig. 5 represents the refrigerating circulatory device 100A of the heater 24B of another variation possessed as heater 24.Heater 24B be have to first heat exchanging part 60 that guides of cold-producing medium of flowing in jet path 22 and from refrigerant loop 1 branch to the heat exchanger of the second heat exchanging part 62 that the cold-producing medium of flowing refrigerant loop 1 guides.First heat exchanging part 60 is also a part for jet path 22.The temperature being directed to the cold-producing medium of the second heat exchanging part 62 is higher than gas-liquid separation temperature.Second heat exchanging part 62 is connected with the refrigerant loop 1 between condenser 12 with upstream side throttling arrangement 14.Specifically, the second heat exchanging part 62 has one end that same condenser 12 is connected with the refrigerant loop 1 between upstream side throttling arrangement 14 and than this one end other end of being connected with the refrigerant loop 1 between condenser 12 with upstream side throttling arrangement 14 of side place farther downstream.Thus, guide to the second heat exchanging part 62 cold-producing medium flowed between condenser 12 and upstream side throttling arrangement 14.In addition, the second heat exchanging part 62 is configured to heat the first heat exchanging part 60.Thus, the cold-producing medium of flowing in jet path 22 is heated.Thus, the heat that the cold-producing medium of flowing in refrigerant loop 1 has can be utilized, the cold-producing medium of flowing in jet path 22 is heated.Without the need to arranging independently electric heater to heat the cold-producing medium of flowing in jet path 22, therefore the saving electrification of refrigerating circulatory device can be realized.In addition, the degree of subcooling of the cold-producing medium of the outlet side of the condenser 12 of refrigerant loop 1 can be improved, therefore the refrigerating circulatory device 100A that refrigerating capacity is improved can be realized.
Heater 24B is the double-tube type heat exchanger be such as made up of interior pipe and the outer tube concentric with interior pipe.In this case, the inside of interior pipe is equivalent to either party in the first heat exchanging part 60 and the second heat exchanging part 62.In addition, the space be formed between the inner peripheral surface of outer tube and the outer peripheral face of interior pipe is equivalent to the opposing party of the first heat exchanging part 60 and the second heat exchanging part 62.In addition, by such as making as the pipe arrangement of the first heat exchanging part 60 and configuring contiguously as the pipe arrangement of the second heat exchanging part 62, also heater 24B can be formed thus.In addition, as long as the second heat exchanging part 62 can heat the first heat exchanging part 60, then the structure of heater 24B is not particularly limited.
Valve 64 is arranged on the upstream side of the second heat exchanging part 62.In addition, in refrigerant loop 1, be connected with the second heat exchanging part 62 one end position and be connected with the second heat exchanging part 62 the other end position between be provided with valve 66.Valve 64,66 is the motor-driven valve that such as can adjust aperture.Can control the heating of the cold-producing medium of flowing in jet path 22 by controlling the opening and closing of valve 64,66.Such as, also can to make only to control the opening and closing of mode to valve 64,66 that the cold-producing medium of flowing in jet path 22 heats when middle pressure-controlled running.It should be noted that, valve 64,66 can omit.In addition, the second heat exchanging part 62 also can be from the unbranched form of refrigerant loop 1.In other words, the second heat exchanging part 62 also can be made up of a part for the refrigerant loop 1 between condenser 12 and upstream side throttling arrangement 14.
Fig. 6 represents the refrigerating circulatory device 100B of the heater 24C of the variation again possessed as heater 24.Heater 24C has first heat exchanging part 70 that guides of cold-producing medium of flowing in jet path 22 and the heat exchanger from refrigerant loop 1 branch and to the second heat exchanging part 72 that the cold-producing medium of flowing refrigerant loop 1 guides.First heat exchanging part 70 is also a part for jet path 22.Second heat exchanging part 72 is connected with the refrigerant loop 1 between compressor 10 with condenser 12.Specifically, the second heat exchanging part 72 has one end that same compressor 10 is connected with the refrigerant loop 1 between condenser 12 and than this one end other end of being connected with the refrigerant loop 1 between compressor 10 with condenser 12 of side place farther downstream.Thus, to guide in refrigerant loop 1 to the second heat exchanging part 72 among the cold-producing medium of flowing for than higher temperatures, the cold-producing medium that flows between compressor 10 and condenser 12.The temperature being directed to the cold-producing medium of the second heat exchanging part 72 is higher than gas-liquid separation temperature.In addition, the second heat exchanging part 72 is configured to heat the first heat exchanging part 70.Thus, the cold-producing medium of flowing in jet path 22 is heated.Thus, the heat for having than the cold-producing medium of higher temperatures among the cold-producing medium that can to utilize in refrigerant loop 1 flowing, heats the cold-producing medium flowed in jet path 22.Due to without the need in order to heat the cold-producing medium of flowing in jet path 22 and arrange independently electric heater, therefore the saving electrification of refrigerating circulatory device can be realized.
First heat exchanging part 70 and the second heat exchanging part 72 structure same by the first heat exchanging part 60 and the second heat exchanging part 62 with heater 24B are formed.In addition, the motor-driven valve that such as can adjust aperture also can be arranged on the second heat exchanging part 72 upstream side and be connected with the second heat exchanging part 72 one end position and be connected with the second heat exchanging part 72 the other end position between refrigerant loop 1 on.Second heat exchanging part 72 also can be from the unbranched form of refrigerant loop 1.In other words, the second heat exchanging part 72 also can be made up of a part for the refrigerant loop 1 between compressor 10 and condenser 12.
(the second embodiment)
Fig. 7 represents the refrigerating circulatory device 200 involved by the second embodiment of the present invention.It should be noted that, in the present embodiment, same-sign is marked with for the structure identical with the first embodiment, and the description thereof will be omitted.
In the present embodiment, indoor heat exchanger 12 in refrigerant loop 1 and be provided with indoor heat exchanger side temperature sensor 40 between indoor throttling arrangement 14, and between outside throttling arrangement 18 and outdoor heat exchanger 20, be provided with outdoor heat exchanger side temperature sensor 42.It should be noted that, the action of the refrigerating circulatory device 200 of present embodiment is identical with the action of the refrigerating circulatory device 100 of the first embodiment.
When heating, indoor heat exchanger side temperature sensor 40 detects the temperature of the cold-producing medium of heat exchanger (condenser) 12 outflow indoor and condensation side outlet temperature Tc, and the temperature of the cold-producing medium that outdoor heat exchanger side temperature sensor 42 subtend outdoor heat exchanger (evaporimeter) 20 flows into and evaporation side inlet temperature Te detect.When freezing, outdoor heat exchanger side temperature sensor 42 detects the temperature of the cold-producing medium of heat exchanger (condenser) 20 outflow outdoor and condensation side outlet temperature Tc, and the temperature of the cold-producing medium that indoor heat exchanger side temperature sensor 40 subtend indoor heat exchanger (evaporimeter) 12 flows into and evaporation side inlet temperature Te detect.Below, outdoor heat exchanger side temperature sensor 42 when the indoor heat exchanger side temperature sensor 40 during heating and refrigeration is called temperature sensor after condensation, indoor heat exchanger side temperature sensor 40 when the outdoor heat exchanger side temperature sensor 42 during heating and refrigeration is called the front temperature sensor of evaporation, is not described with being distinguished when heating and when freezing in the same manner as the first embodiment.
Control device 30 carries out the middle pressure-controlled substantially same with the first embodiment and operates, but now, gas-liquid separation temperature Tm, condensation side outlet temperature Tc and evaporation side inlet temperature Te when using the temperature difference between gas-liquid separation temperature Tm and injection temperation Tinj to become less than setting Δ Ti, revise the calculating formula of the gas-liquid separation temperature used in steady running.Below, explain with reference to the flow chart of figure 8 the middle pressure-controlled running that control device 30 carries out.
The step S9 of the flow chart shown in Fig. 2 is changed to step S21 ~ S23 by the flow chart shown in Fig. 8, and other step S1 ~ S8, S10 ~ S14 is identical with the first embodiment.Therefore, below, be described centered by present embodiment step S21 alone ~ S23.
In the step s 7, when the temperature difference of control device 30 between the gas-liquid separation temperature Tm being judged to press temperature sensor 26 to detect by centre and the injection temperation Tinj detected by degree of superheat temperature sensor 28 is less than predetermined setting Δ Ti, after utilizing condensation, temperature sensor detects condensation side outlet temperature Tc, and before utilizing evaporation, temperature sensor detects (step S21) evaporation side inlet temperature Te.Then, the gas-liquid separation temperature Tm become in the step s 7 when being is recorded as Tm0 by control device 30, and the condensation side outlet temperature Tc detected in the step s 21 and evaporation side inlet temperature Te is stored as Tc0 and Te0 (step S22) respectively.Then, control device 30 uses Tm0, Tc0, Te0 of storing, revises (step S23) the calculating formula of the gas-liquid separation temperature used in steady running.
At this, so-called " calculating formula of the gas-liquid separation temperature used in steady running ", for for according to condensation side outlet temperature Tc and evaporation side inlet temperature Te or the calculating formula only estimating gas-liquid separation temperature according to condensation side outlet temperature Tc, such as, as following formula (1) represents.
Tm2＝αTc+β···(1)
It should be noted that, when using formula (1), in other words when only estimating gas-liquid separation temperature according to condensation side outlet temperature, detect evaporation side inlet temperature Te without using temperature sensor before evaporation in the step s 21.That is, the calculating formula of Tm0 and Tc0 to gas-liquid separation temperature can be only used to revise.Below, illustrate, assuming that use formula (1) is described for ease of understanding.
In step S23, the Tc0 stored in step S22 is substituted into formula (1) by control device 30, calculates presumption temperature Tm2.The presumption temperature Tm2 calculated and the Tm0 that stores in step S22 compare by control device 30, using its difference after centre pressure temperature sensor 26 and condensation temperature sensor evaluated error and the calculating formula of mode to gas-liquid separation temperature that be eliminated is rewritten.Such as, when Tm0 is larger relative to Tm2, in calculating formula, add its residual quantity (Tm0-Tm2) as correction value, when Tm0 is less relative to Tm2, in calculating formula, deduct its residual quantity (Tm2-Tm0) as correction value.Or, the factor alpha in above-mentioned formula (1), β are changed.
Then, control device 30, through step S10 ~ S13, shifts (step 814) to steady running.In steady running, control device 30 is used in the calculating formula of revised gas-liquid separation temperature in the running of middle pressure-controlled to carry out steady running.Specifically, after control device 30 utilizes middle pressure temperature sensor 26, ejection temperature sensor 34, condensation, temperature sensor and the front temperature sensor of evaporation are to detect gas-liquid separation temperature Tm, ejection temperature Td, condensation side outlet temperature Tc, evaporation side inlet temperature Te, and to make them not adjust away from the aperture of mode to upstream side throttling arrangement and downstream throttling arrangement of desired value.
In the first embodiment, the gas-liquid separation temperature Tm1 of target is fixing, but in the present embodiment, the presumption temperature Tm2 that the calculating formula being used in the gas-liquid separation temperature that have modified in step S23 calculates is set as the gas-liquid separation temperature of target.The control of ejection temperature Td and gas-liquid separation temperature Tm, in the same manner as the first embodiment, is undertaken by the adjustment of the aperture of upstream side throttling arrangement and downstream throttling arrangement.
So, in middle pressure-controlled running, the calculating formula of the thermometer measuring point presumption gas-liquid separation temperature Tm according to other is revised, and this revised calculating formula is used in steady running, in steady running, also can realize the more high-precision middle pressure-controlled of the evaluated error also contemplating temperature sensor etc. thus.
< variation >
It should be noted that, in the flow chart shown in Fig. 8, detect the step S21 configuration of condensation side outlet temperature Tc and evaporation side inlet temperature Te after step s 7, but also can step S21 be configured between step S6 and step S7, and configure the step of the gas-liquid separation temperature Tm3 determining target according to condensation side outlet temperature Tc and evaporation side inlet temperature Te afterwards, in step s 8, increase the adjustment amount of aperture when the difference of the gas-liquid separation temperature Tm3 of the gas-liquid separation temperature Tm detected and target is larger, and reduce the adjustment amount of aperture when its difference is less.
In addition, in step slo, when determining the gas-liquid separation temperature Tm1 of target, also can replace using Tm0, and use the presumption temperature Tm2 obtained by calculating formula revised in step S23.
In addition, the heater 24 of the second embodiment also can carry out the change same with the variation of the first embodiment.
(other embodiment)
It should be noted that, in said embodiment, in refrigerant loop 1, be provided with cross valve 32, and the switching of refrigeration and heating can be realized, but refrigerating circulatory device of the present invention also can for refrigeration is special or heat special.
[industrial aspect utilizability]
Refrigerating circulatory device of the present invention can utilize as the heat pump assembly of hot water supply device, hot-water heater, refrigeration or air-conditioning equipment etc.

Claims (13)

1. a refrigerating circulatory device, wherein, possesses:
Refrigerant loop, it makes cold-producing medium to be circulated by the mode of compressor, condenser, upstream side throttling arrangement, gas-liquid separator, downstream throttling arrangement and evaporimeter successively;
Jet path, it supplies by the gas refrigerant after described gas-liquid separator separates to described compressor;
Heater, it is located at described jet path;
Middle pressure temperature sensor, it detects the temperature of the cold-producing medium flowed into described jet path from described refrigerant loop and gas-liquid separation temperature;
Degree of superheat temperature sensor, it is detected by the temperature of the cold-producing medium after described heater heating and injection temperation in described jet path;
Control device, it carries out middle pressure-controlled running, in this middle pressure-controlled running, described control device is to make the temperature difference between described gas-liquid separation temperature and described injection temperation become after the aperture of mode at least one party in described upstream side throttling arrangement and described downstream throttling arrangement less than setting adjust, increase the aperture of described downstream throttling arrangement, until described gas-liquid separation temperature reduces set point of temperature from temperature now.
2. refrigerating circulatory device as claimed in claim 1, wherein,
Also possess temperature sensor after condensation, after this condensation, temperature sensor detects the temperature of the cold-producing medium flowed out from described condenser and condensation side outlet temperature,
Described control device is in described middle pressure-controlled running, described gas-liquid separation temperature when using the temperature difference between described gas-liquid separation temperature and described injection temperation to become less than setting and described condensation side outlet temperature, revise the calculating formula of the gas-liquid separation temperature used in steady running, the calculating formula of the described gas-liquid separation temperature used in steady running is the calculating formula for only estimating described gas-liquid separation temperature according to described condensation side outlet temperature.
3. refrigerating circulatory device as claimed in claim 1, wherein,
Also possess:
Temperature sensor after condensation, after this condensation, temperature sensor detects the temperature of the cold-producing medium flowed out from described condenser and condensation side outlet temperature;
Temperature sensor before evaporation, the temperature of cold-producing medium that before this evaporation, evaporimeter described in temperature sensor subtend flows into and evaporation side inlet temperature detect,
Described control device is in described middle pressure-controlled running, described gas-liquid separation temperature when using the temperature difference between described gas-liquid separation temperature and described injection temperation to become less than setting, described condensation side outlet temperature and described evaporation side inlet temperature, revise the calculating formula of the gas-liquid separation temperature used in steady running, the calculating formula of the described gas-liquid separation temperature used in steady running is the calculating formula for estimating described gas-liquid separation temperature according to described condensation side outlet temperature and described evaporation side inlet temperature.
4. refrigerating circulatory device as claimed in claim 2, wherein,
Described control device is used in the calculating formula of revised gas-liquid separation temperature in described middle pressure-controlled running to carry out steady running.
5. refrigerating circulatory device as claimed in claim 1, wherein,
Described control device carries out described middle pressure-controlled running when starting operation.
6. refrigerating circulatory device as claimed in claim 1, wherein,
Described control device carries out described middle pressure-controlled running in the midway of steady running.
7. refrigerating circulatory device as claimed in claim 5, wherein,
Also possess ejection temperature sensor, namely this ejection temperature sensor sprays temperature to the temperature of the cold-producing medium sprayed from described compressor and detects,
Described control device adjusts with the aperture of mode to described upstream side throttling arrangement near the ejection temperature making described ejection temperature remain on target, and reduce the aperture of described downstream throttling arrangement simultaneously, until the temperature difference between described gas-liquid separation temperature and described injection temperation becomes less than setting, then increase the aperture of described downstream throttling arrangement.
8. refrigerating circulatory device as claimed in claim 1, wherein,
Described refrigerant loop comprises the indoor heat exchanger and the outdoor heat exchanger that play function as described condenser and described evaporimeter, and comprise the indoor throttling arrangement and the outside throttling arrangement that play function as described upstream side throttling arrangement and described downstream throttling arrangement
The cross valve that the flow direction of cold-producing medium is switched is provided with in described refrigerant loop.
9. refrigerating circulatory device as claimed in claim 1, wherein,
Described heater is electric heater.
10. refrigerating circulatory device as claimed in claim 1, wherein,
Described heater is accumulate the heat of discharging from described compressor, and utilizes the thermal storage unit that the heat of this accumulation heats cold-producing medium.
11. refrigerating circulatory devices as claimed in claim 1, wherein,
Described heater is the heat exchanger comprising the first heat exchanging part and the second heat exchanging part, the cold-producing medium flowed in described jet path imports described first heat exchanging part, flowing in described refrigerant loop and import described second heat exchanging part with the cold-producing medium that described gas-liquid separation temperature is in a ratio of high temperature
In described heat exchanger, described second heat exchanging part heats described first heat exchanging part.
12. refrigerating circulatory devices as claimed in claim 11, wherein,
The cold-producing medium flowed between described compressor and described condenser is imported to described second heat exchanging part.
13. refrigerating circulatory devices as claimed in claim 11, wherein,
The cold-producing medium flowed between described condenser and described upstream side throttling arrangement is imported to described second heat exchanging part.
CN201280007707.4A 2011-07-05 2012-07-03 Refrigerating circulatory device Expired - Fee Related CN103348197B (en)

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Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015006925A1 (en) * 2013-07-16 2015-01-22 广东美芝制冷设备有限公司 Air-supplying enthalpy-adding air-conditioning system and control method therefor
JP2015083894A (en) * 2013-10-25 2015-04-30 ダイキン工業株式会社 Refrigeration unit
CN104990397B (en) * 2015-07-10 2017-03-08 康景安 Condense many association types high-efficiency multi-function drying integral machine and its method of work
CN105115183A (en) * 2015-09-23 2015-12-02 湖南华强电气有限公司 Bus air conditioner system and energy conservation method thereof
KR101706865B1 (en) * 2015-10-19 2017-02-15 엘지전자 주식회사 Air conditioning system
CN105258378B (en) * 2015-11-09 2017-11-10 安徽美芝精密制造有限公司 refrigeration system and its control method
WO2018006569A1 (en) * 2016-07-08 2018-01-11 广东美的制冷设备有限公司 Air-conditioning system
CN106247666A (en) * 2016-08-24 2016-12-21 广东美芝制冷设备有限公司 Refrigerating plant
CN106247652A (en) * 2016-09-29 2016-12-21 广东美的制冷设备有限公司 Air conditioning system and control method thereof
KR102354891B1 (en) 2017-05-31 2022-01-25 삼성전자주식회사 Air conditioner and control method thereof
JP2020118317A (en) * 2019-01-21 2020-08-06 パナソニックＩｐマネジメント株式会社 Air conditioner
CN114761743A (en) * 2019-12-04 2022-07-15 三菱电机株式会社 Outdoor unit and refrigeration loop device
EP3901538B1 (en) 2020-04-24 2024-04-10 Copeland Europe GmbH Flash tank-based control of refrigerant injection into a compressor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05302767A (en) * 1992-04-27 1993-11-16 Matsushita Refrig Co Ltd Space cooling and heating device
JP3317170B2 (en) * 1996-12-24 2002-08-26 ダイキン工業株式会社 Refrigeration equipment
JP2005214442A (en) * 2004-01-27 2005-08-11 Sanyo Electric Co Ltd Refrigerator
AU2007223486A1 (en) * 2006-03-06 2007-09-13 Daikin Industries, Ltd. Refrigeration system
JP2010223542A (en) * 2009-03-25 2010-10-07 Mitsubishi Electric Corp Refrigerating air-conditioning device

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0633910B2 (en) * 1983-11-21 1994-05-02 三菱電機株式会社 Heat pump refrigeration system
JP2964705B2 (en) * 1991-06-13 1999-10-18 ダイキン工業株式会社 Air conditioner
JPH0633910A (en) * 1992-07-20 1994-02-08 Komatsu Ltd Two-speed cylinder device
JP2001033117A (en) * 1999-05-19 2001-02-09 Daikin Ind Ltd Refrigerating device
JP3600108B2 (en) * 2000-03-10 2004-12-08 三洋電機株式会社 Refrigeration equipment
JP2005147456A (en) * 2003-11-13 2005-06-09 Daikin Ind Ltd Air conditioner
JP2009180427A (en) * 2008-01-30 2009-08-13 Daikin Ind Ltd Refrigerating device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05302767A (en) * 1992-04-27 1993-11-16 Matsushita Refrig Co Ltd Space cooling and heating device
JP3317170B2 (en) * 1996-12-24 2002-08-26 ダイキン工業株式会社 Refrigeration equipment
JP2005214442A (en) * 2004-01-27 2005-08-11 Sanyo Electric Co Ltd Refrigerator
AU2007223486A1 (en) * 2006-03-06 2007-09-13 Daikin Industries, Ltd. Refrigeration system
CN101384862A (en) * 2006-03-06 2009-03-11 大金工业株式会社 Refrigeration device
JP2010223542A (en) * 2009-03-25 2010-10-07 Mitsubishi Electric Corp Refrigerating air-conditioning device

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