CN103348197A - Refrigeration cycle device - Google Patents
Refrigeration cycle device Download PDFInfo
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- CN103348197A CN103348197A CN2012800077074A CN201280007707A CN103348197A CN 103348197 A CN103348197 A CN 103348197A CN 2012800077074 A CN2012800077074 A CN 2012800077074A CN 201280007707 A CN201280007707 A CN 201280007707A CN 103348197 A CN103348197 A CN 103348197A
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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
- F25B13/00—Compression machines, plants or systems, with 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
- 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
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/01—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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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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
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2101—Temperatures in a bypass
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2109—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
A refrigeration cycle device (100) comprises a refrigerant circuit (1), an injection pathway (22), and a control device (30). The refrigerant circuit (1) includes an upstream side throttle device (14, 18), a gas-liquid separator (16), and a downstream side throttle device (18, 14). The injection pathway (22) is provided with a heater (24). The control device (30) performs an intermediate pressure control operation in which at least one of the opening degrees of the upstream side throttle device and the downstream side throttle device is adjusted so that the temperature difference between the gas-liquid separation temperature detected by an intermediate pressure temperature sensor (26) and the injection temperature detected by an overheat-degree temperature sensor (28) becomes smaller than a predetermined value, after which the opening degree of the downstream side throttle device is increased until the gas-liquid separation temperature is decreased by a predetermined temperature from the detected temperature.
Description
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, known have possessed compressor, cross valve, indoor heat exchanger, indoor throttling arrangement, gas-liquid separator, outside throttling arrangement, outdoor heat exchanger and the refrigerating circulatory device that can switch refrigeration and heating.Refrigerating circulatory device 500 is as shown in Figure 9 for example disclosed in patent documentation 1.
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 and compressor 510, be provided with the jet path 522 that the gas refrigerant of pressing in the middle of after being separated by gas-liquid separator 516 is supplied with to compressor 510.And then, for voltage-controlled being made as in centre become desired value, in refrigerating circulatory device 500, be provided with heat exchange temperature sensor 544 that condensation temperature and evaporating temperature to cold-producing medium detect, 546 and to the temperature of the cold-producing medium in the gas-liquid separator 516 press namely that temperature detects in the middle of press temperature sensor 526.
About the refrigerating circulatory device 500 that constitutes as mentioned above, below its action is described.When heating, by after the cross valve 532, in indoor heat exchanger 512, carry out heat exchange from the cold-producing medium of compressor 510 ejection, and be middle pressure by indoor throttling arrangement 514 from high pressure relief.Middle cold-producing medium of pressing is separated into gas refrigerant and liquid refrigerant in gas-liquid separator 516, middle gas refrigerant of pressing is supplied with to compressor 510 by jet path 522.On the other hand, the decompression further by outside throttling arrangement 518 of middle liquid refrigerant of pressing, the cold-producing medium of post-decompression low pressure carries out heat exchange in outdoor heat exchanger 520, after having passed through cross valve 532, be inhaled in the compressor 510.When freezing, by after the cross valve 532, in outdoor heat exchanger 520, carry out heat exchange from the cold-producing medium of compressor 510 ejection, and be middle pressure by outside throttling arrangement 518 from high pressure relief.Middle cold-producing medium of pressing is separated into gas refrigerant and liquid refrigerant in gas-liquid separator 516, middle gas refrigerant of pressing is supplied with to compressor 510 by jet path 522.On the other hand, the decompression further by indoor throttling arrangement 514 of middle liquid refrigerant of pressing, the cold-producing medium of post-decompression low pressure carries out heat exchange in indoor heat exchanger 512, after having passed through cross valve 532, be inhaled in the compressor 510.
In addition, in refrigerating circulatory device 500, control device 530 is according to the middle temperature of pressing of being determined target by heat exchange temperature sensor 544,546 detected condensation temperatures and evaporating temperature, and so that by the centre press temperature sensor 526 press in the middle of detected temperature become target in the middle of press temperature mode the aperture of the throttling arrangement in the downstream that is positioned at gas-liquid separator 516 (be outside throttling arrangement 516 during heating, and be indoor throttling arrangement 514 during refrigeration) is adjusted.
[look-ahead technique document]
[patent documentation]
[patent documentation 1]: No. 3317170 specification of Japan Patent
[brief summary of the invention]
[inventing problem to be solved]
But refrigerating circulatory device 500 shown in Figure 9 has the leeway of further improved efficiency.
Summary of the invention
The disclosure is made in view of such situation, and its purpose is, the efficient of refrigerating circulatory device is improved.
[being used for solving the mechanism of problem]
The disclosure provides a kind of refrigerating circulatory device, possesses: refrigerant loop, and it makes cold-producing medium circulate in the mode by compressor, condenser, upstream side throttling arrangement, gas-liquid separator, downstream throttling arrangement and evaporimeter successively; Jet path, it will be supplied with to described compressor by the gas refrigerant after the described gas-liquid separator separates; Heater, it is located at described jet path; The middle temperature sensor of pressing, its temperature to the cold-producing medium to described jet path inflow from described refrigerant loop is that the gas-liquid separation temperature detects; Degree of superheat temperature sensor, it is to being that injection temperation detects by the temperature of the cold-producing medium after the heating of described heater in described jet path; Control device, it carries out centre pressure-controlled running, in this centre pressure-controlled running, after little mode is adjusted the aperture of at least one side in described upstream side throttling arrangement and the described downstream throttling arrangement so that the temperature difference between described gas-liquid separation temperature and the described injection temperation becomes than setting, increase the aperture of described downstream throttling arrangement, reduced set point of temperature until described gas-liquid separation temperature from temperature at this moment.
[invention effect]
According to above-mentioned structure, determine the fiducial temperature of gas-liquid separation temperature by adopting heater and degree of superheat temperature sensor, and will be made as the target temperature of gas-liquid separation temperature than the temperature of the low set point of temperature of this fiducial temperature, press the evaluated error of temperature sensor in the middle of can eliminating thus.Thus, the centre can be pressed and be controlled to be the purpose value more accurately, thereby the efficient of refrigerating circulatory device is improved.
Description of drawings
Fig. 1 is the structure chart of the related refrigerating circulatory device of first embodiment of the present invention.
Fig. 2 is the flow chart of the control method of the middle pressure-controlled running in expression first embodiment.
Fig. 3 is upstream side throttling arrangement and the variation of the aperture of downstream throttling arrangement and the curve map of ejection temperature, injection temperation and gas-liquid separation variation of temperature of expression in first embodiment.
Fig. 4 is the figure of the related heater of expression one variation.
Fig. 5 is the structure chart of the related refrigerating circulatory device of another variation.
Fig. 6 is again the structure chart of the related refrigerating circulatory device of a variation.
Fig. 7 is the structure chart of the related refrigerating circulatory device of second embodiment of the present invention.
Fig. 8 is the flow chart of the control method of the middle pressure-controlled running in expression second embodiment.
Fig. 9 is the structure chart of existing refrigerating circulatory device.
The specific embodiment
In refrigerating circulatory device shown in Figure 9 500, according to the temperature that detected by three temperature sensors 544,546,526 row control is compressed in the centre of the cold-producing medium supplied with to compressor 510 by jet path 522 from gas-liquid separator 516, so the deviation of the precision that temperature sensor has becomes problem.In normally used temperature sensor, there is ± 1.5 ℃ evaluated error at least.Use like that under the situation that a plurality of temperature sensors control at as shown in Figure 9 refrigerating circulatory device 500, with the number of temperature sensor correspondingly, evaluated error is also accumulated (if each is ± 1.5 ℃, being ± 4.5 ℃ when then using three).Therefore, press in the middle of the working control and deviate from from desired value, tend to cause the efficient of refrigerating circulatory device to reduce.
First mode of the present disclosure provides a kind of refrigerating circulatory device, wherein, possess: refrigerant loop, it makes cold-producing medium circulate in the mode by compressor, condenser, upstream side throttling arrangement, gas-liquid separator, downstream throttling arrangement and evaporimeter successively; Jet path, it will be supplied with to described compressor by the gas refrigerant after the described gas-liquid separator separates; Heater, it is located at described jet path; The middle temperature sensor of pressing, its temperature to the cold-producing medium to described jet path inflow from described refrigerant loop is that the gas-liquid separation temperature detects; Degree of superheat temperature sensor, it is to being that injection temperation detects by the temperature of the cold-producing medium after the heating of described heater in described jet path; Control device, it carries out centre pressure-controlled running, in this centre pressure-controlled running, after little mode is adjusted the aperture of at least one side in described upstream side throttling arrangement and the described downstream throttling arrangement so that the temperature difference between described gas-liquid separation temperature and the described injection temperation becomes than setting, increase the aperture of described downstream throttling arrangement, reduced set point of temperature until described gas-liquid separation temperature from temperature at this moment.
Second mode of the present disclosure is on the basis of first mode, a kind of refrigerating circulatory device is provided, wherein, also possesses temperature sensor after the condensation, temperature sensor is that the condensation side outlet temperature detects to the temperature of the cold-producing medium that flows out from described condenser after this condensation, described control device is in described middle pressure-controlled running, use temperature difference between described gas-liquid separation temperature and the described injection temperation to become than described gas-liquid separation temperature and the described condensation side outlet temperature of setting hour, the calculating formula of the gas-liquid separation temperature used in steady running is revised.
According to second mode, in middle pressure-controlled running, can use temperature difference between gas-liquid separation temperature and the described injection temperation to become than gas-liquid separation temperature and the condensation side outlet temperature of setting hour, thereby 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 mode, a kind of refrigerating circulatory device is provided, wherein, also possesses the preceding temperature sensor of evaporation, the temperature of the cold-producing medium that the described evaporimeter of temperature sensor subtend flows into before this evaporation is that the evaporation side inlet temperature detects, when the calculating formula of the gas-liquid separation temperature that described control device uses in to steady running is revised, also use temperature difference between described gas-liquid separation temperature and the described injection temperation to become than the described evaporation side inlet temperature of setting hour.
According to Third Way, in middle pressure-controlled running, can use temperature difference between gas-liquid separation temperature and the described injection temperation to become than gas-liquid separation temperature, condensation side outlet temperature and the evaporation side inlet temperature of setting hour, thereby the calculating formula of the gas-liquid separation temperature used in steady running is revised.
Cubic formula of the present disclosure provides a kind of refrigerating circulatory device on the basis of second mode or Third Way, wherein, described control device uses the calculating formula of revised gas-liquid separation temperature in described middle pressure-controlled running to carry out steady running.
According to cubic formula, in steady running, can also consider pressure-controlled in the middle of evaluated error etc. more high-precision of temperature sensor.
On the basis of arbitrary mode of the 5th mode of the present disclosure in the first～the cubic formula, 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 arbitrary mode of the 6th mode of the present disclosure in first～the 5th mode, provide a kind of refrigerating circulatory device, wherein, described control device turns round in the described middle pressure-controlled of carrying out of steady running midway.
According to the 6th mode, steady running also carry out the running of centre pressure-controlled midway, more accurately with the voltage-controlled purpose value that is made as in centre.
The 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 the ejection temperature sensor, this ejection temperature sensor namely sprays temperature to the temperature from the cold-producing medium of described compressor ejection and detects, described control device so that near the mode that described ejection temperature remains on the ejection temperature of target the aperture of described upstream side throttling arrangement is adjusted, and reduce the aperture of described downstream throttling arrangement simultaneously, temperature difference between described gas-liquid separation temperature and described injection temperation becomes littler than setting, increases the aperture of described downstream throttling arrangement then.
According to the 7th mode, by utilizing the upstream side throttling arrangement ejection temperature is controlled, and utilized the downstream throttling arrangement that the gas-liquid separation temperature is controlled, can realize easy control thus.
On the basis of arbitrary mode of all directions formula of the present disclosure in first～the 7th mode, a kind of refrigerating circulatory device is provided, wherein, described refrigerant loop comprises indoor heat exchanger and the outdoor heat exchanger as described condenser and described evaporimeter performance function, and comprise indoor throttling arrangement and outside throttling arrangement as described upstream side throttling arrangement and described downstream throttling arrangement performance function, in described refrigerant loop, be provided with the cross valve that the flow direction to cold-producing medium switches.
According to the formula from all directions, realized the refrigerating circulatory device of the switching that can freeze and heat.
On the basis of arbitrary mode of the 9th mode of the present disclosure in the first～all directions formula, provide a kind of refrigerating circulatory device, wherein, described heater is electric heater.
According to the 9th mode, control is connected-cut off to electric heater easily, therefore, can only heat the cold-producing medium that flows in jet path under the situation that need heat the cold-producing medium that flows in jet path.
On the basis of arbitrary mode of the tenth mode of the present disclosure in the first～all directions formula, a kind of refrigerating circulatory device is provided, wherein, described heater is that the heat of discharging from described compressor is accumulated, and the thermal storage unit that utilizes this heat of accumulating that cold-producing medium is heated.
According to the tenth mode, utilize the used heat of compressor and the cold-producing medium that flows in jet path is heated.
On the basis of arbitrary mode of the 11 mode of the present disclosure in the first～all directions formula, a kind of refrigerating circulatory device is provided, wherein, described heater is the heat exchanger that comprises the first heat exchange portion and the second heat exchange portion, the cold-producing medium that flows in described jet path imports the described first heat exchange portion, in described refrigerant loop, flow and import the described second heat exchange portion with cold-producing medium that described gas-liquid separation temperature is in a ratio of high temperature, in described heat exchanger, the described second heat exchange portion heats the described first heat exchange portion.
According to the 11 mode, the heat that utilizes cold-producing medium mobile in refrigerant loop to have comes the cold-producing medium that flows in jet path is heated.
The 12 mode of the present disclosure provides a kind of refrigerating circulatory device on the basis of the 11 mode, wherein, guide the cold-producing medium that flows to the described second heat exchange portion between described compressor and described condenser.
According to the 12 mode, the heat that utilizes the cold-producing medium for than higher temperatures mobile in refrigerant loop to have comes the cold-producing medium that flows in jet path is heated.
The 13 mode of the present disclosure provides a kind of refrigerating circulatory device on the basis of the 11 mode, wherein, guide the cold-producing medium that flows to the described second heat exchange portion between described condenser and described upstream side throttling arrangement.
According to the 13 mode, the heat that utilizes cold-producing medium mobile in refrigerant loop to have comes the cold-producing medium that flows in jet path 22 is heated.In addition, the supercooling degree of the cold-producing medium of the condensator outlet side of refrigerant loop raises, so the ability of refrigerating circulatory device is improved.
Below, about embodiments of the present invention, limit limit with reference to the accompanying drawings is described in detail.Need to prove that the following description is the explanation about an example of the present invention, the present invention is defined by these contents.
(first embodiment)
Fig. 1 represents the refrigerating circulatory device 100 that first embodiment of the present disclosure is related.This refrigerating circulatory device 100 possesses refrigerant loop 1 and the control device 30 that makes the cold-producing medium circulation.
As indoor throttling arrangement 14 and outside throttling arrangement 18, for example adopt the electric expansion valve that to adjust aperture.Control device 30 is carried control signal to indoor throttling arrangement 14 and outside throttling arrangement 18, and their aperture is adjusted.
In addition, between gas-liquid separator 16 and compressor 10, be provided with will be separated by gas-liquid separator 16 in the middle of the jet path 22 supplied with to compressor 10 of the gas refrigerant of pressing.Jet path 22 is for example linked by the gas blanket side of an end and gas-liquid separator 16, and the other end and the refrigerant piping formation of pressing suction inlet to link in the middle of the discharge chambe opening of compressor 10 in compression process.Jet path 22 be provided with heater 24 midway, spray to compressor 10 after the intermediate pressure gas cryogen that flows in jet path 22 is heated.
As heater 24, for example can adopt heater (heater), be electric heater.As electric heater, can enumerate resistance heater, induction heater etc.Heater 24 is also nonessential to be heated the cold-producing medium that flows in jet path 22 all the time, for example also can only when middle pressure-controlled running described later, the cold-producing medium that flows in jet path 22 be heated by the connection-cut-out control of electric heater.
And then, in refrigerating circulatory device 100, be provided with: the temperature from the cold-producing medium of compressor 10 ejection is namely sprayed the ejection temperature sensor 34 that temperature T d detects; The outdoor temperature sensor 36 that outdoor temperature To is detected; The indoor temperature transmitter 38 that indoor temperature Ti is detected; Temperature to 22 cold-producing mediums that flow into from from refrigerant loop 1 to jet path is the middle temperature sensor 26 of pressing that gas-liquid separation temperature T m detects; To in jet path 22, being the degree of superheat temperature sensor 28 that injection temperation Tinj detects by the temperature of the cold-producing medium after heater 24 heating.Control device 30 is main according to the temperature that is detected by all temps sensor, and the aperture of indoor throttling arrangement 14 and outside throttling arrangement 18 and the rotating speed of compressor 10 are controlled.
Need to prove that the middle temperature sensor 26 of pressing both can be arranged on the gas-liquid separator 16, the ratio heater 24 that also can be arranged on the refrigerant piping that constitutes jet path 22 more leans on the position of upstream side.Perhaps, the middle temperature sensor 26 of pressing also can be arranged on gas-liquid separator 16 and the refrigerant piping that indoor throttling arrangement 14 is connected or with on gas-liquid separator 16 and the refrigerant piping that outside throttling arrangement 18 is connected.The ratio heater 24 that degree of superheat temperature sensor 28 is arranged on the refrigerant piping that constitutes jet path 22 is more by the position in downstream.
Then, the action to refrigerating circulatory device 100 describes.
When heating, switch to by the first direction shown in the solid arrow by the flow direction of cross valve 32 with cold-producing medium.In this state, guided to indoor heat exchanger 12 after compressor 10 ejections by the cold-producing medium after compressor 10 compressions.The cold-producing medium that is directed to indoor heat exchanger 12 at this after the room air heat radiation, by to 14 guiding of indoor throttling arrangement.The cold-producing medium that is directed to indoor throttling arrangement 14 is depressurized in indoor throttling arrangement 14, become the centre with condensing pressure and evaporating pressure pressure in the middle of compacting cryogen and by to gas-liquid separator 16 guiding.The middle compacting cryogen that is directed to gas-liquid separator 16 is separated in gas-liquid separator 16, and the liquid refrigerant among the middle compacting cryogen is guided to outside throttling arrangement 18, and gas refrigerant is to jet path 22 inflows.The middle press liquid cold-producing medium that is directed to outside throttling arrangement 18 is depressurized in outside throttling arrangement 18, and is guided to outdoor heat exchanger 20, afterwards, from the outdoor air heat absorption, returns compressor 10 then.The intermediate pressure gas cryogen that flows into to jet path 22 is sprayed to compressor 10 by after heater 24 heating.
When refrigeration, switch to by the second direction shown in the dotted arrow by the flow direction of cross valve 32 with cold-producing medium.In this state, guided to outdoor heat exchanger 20 after compressor 10 ejections by the cold-producing medium after compressor 10 compressions.The cold-producing medium that is directed to outdoor heat exchanger 20 at this after the outdoor air heat radiation, by to 18 guiding of outside throttling arrangement.The cold-producing medium that is directed to outside throttling arrangement 18 is depressurized in outside throttling arrangement 18, become the centre with condensing pressure and evaporating pressure pressure in the middle of compacting cryogen and by to gas-liquid separator 16 guiding.The middle compacting cryogen that is directed to gas-liquid separator 16 is separated in gas-liquid separator 16, and the liquid refrigerant among the middle compacting cryogen is guided to indoor throttling arrangement 14, and gas refrigerant is to jet path 22 inflows.The middle press liquid cold-producing medium that is directed to indoor throttling arrangement 14 is depressurized in indoor throttling arrangement 14, and is guided to indoor heat exchanger 12, afterwards, from the room air heat absorption, returns compressor 10 then.The intermediate pressure gas cryogen that flows into to jet path 22 is sprayed to compressor 10 by after heater 24 heating.
When heating and refrigeration, therefore the flow direction difference of the cold-producing medium in the refrigerant loop 1, but cold-producing medium flows to equidirectional in jet path 22 can adopt when the heating and during refrigeration as the method for pressing in the middle of the control and use the same method.Below among, outdoor heat exchanger 20 when the indoor heat exchanger 12 during with heating and refrigeration is called condenser, indoor heat exchanger 12 when the outdoor heat exchanger 20 during with heating and refrigeration is called evaporimeter, outside throttling arrangement 18 when the indoor throttling arrangement 14 during with heating and refrigeration is called the upstream side throttling arrangement, indoor throttling arrangement 14 during with the outside throttling arrangement 18 in when heating and refrigeration is called the downstream throttling arrangement, and describes during not to heating and during refrigeration with being distinguished.
In the present embodiment, control device 30 carries out centre pressure-controlled running when starting operation.So-called " middle pressure-controlled running " refers to, so that pressed temperature difference between the gas-liquid separation temperature T m that temperature sensor 26 detects and the injection temperation Tinj that is detected by degree of superheat temperature sensor 28 to become than setting Δ Ti by the centre after little mode is adjusted the aperture of at least one side in upstream side throttling arrangement and the downstream throttling arrangement, increase the aperture of downstream throttling arrangement, reduced the running of set point of temperature Δ Tm until gas-liquid separation temperature T m from the temperature of this moment.Below, explain the middle pressure-controlled running that control device 30 carries out with reference to the flow chart of figure 2.
At first, control device 30 so that near the mode that is remained on by the ejection temperature T d that detects of ejection temperature sensor 34 the ejection temperature T D of target the aperture of upstream side throttling arrangement is adjusted, reduce the aperture of downstream throttling arrangement simultaneously, it is littler than setting Δ Ti that the temperature difference between gas-liquid separation temperature T m and injection temperation Tinj becomes.
Particularly, control device 30 utilizes 36 couples of outdoor temperature To of outdoor temperature sensor to detect, and utilizes 38 couples of indoor temperature Ti of indoor temperature transmitter to detect (step S1).Then, control device 30 is determined the ejection temperature T D (step S2) of target according to detected outdoor temperature To and indoor temperature Ti.Then, control device 30 utilizes 34 pairs of ejections of ejection temperature sensors temperature T d to detect (step S3), and difference and the predetermined permissible value Δ Td (for example, 1.5 ℃) of the ejection temperature T d of itself and target compared (step S4).
Under the difference of the ejection temperature T D of detected ejection temperature T d and target is situation more than the feasible value Δ Td (among the step S4 for not), the aperture of 30 pairs of upstream side throttling arrangements of control device is adjusted (step S5).Particularly, control device 30 reduces the aperture of upstream side throttling arrangement when detected ejection temperature T d is lower than the ejection temperature T D of target, and increases the aperture of upstream side throttling arrangement when detected ejection temperature T d is higher than the ejection temperature T D of target.After the step S5, return step S1.By carrying out step S1～S5 repeatedly, make in the actual fixed temperature of ejection temperature T d near the ejection temperature T D of target.Consequently, if the difference of the ejection temperature T D of detected ejection temperature T d and target then enters step S6 less than feasible value Δ Td (among the step S4 for being).
In step S6, press the gas-liquid separation temperature T m of 26 pairs of middle compacting cryogens of temperature sensor to detect in the middle of control device 30 utilizations, and utilize 28 pairs of degree of superheat temperature sensors to pass through heater 24 injection of refrigerant temperature T inj afterwards and detect (step S6).Then, whether the temperature difference between control device 30 judgement gas-liquid separation temperature T m and the injection temperation Tinj is less than predetermined setting Δ Ti (for example, 3 ℃) (step S7).
Temperature difference between gas-liquid separation temperature T m and the injection temperation Tinj is the degree of superheat of the gas refrigerant that sprays.The intermediate pressure gas cryogen that sprays in the prior art, is not provided with heater 24 at jet path 22, so can not obtain the degree of superheat.Correspondingly thereto, in the present embodiment, by at jet path 22 heater 24 being set, as long as only gas refrigerant flows in jet path 22, then having passed through heater 24 intermediate pressure gas cryogen afterwards and can obtain the degree of superheat.
Be under the situation not, namely obtained under the situation more than the fixed temperature in the degree of superheat that control device 30 reduces the aperture (step S8) of downstream throttling arrangement, and gas-liquid separation temperature T m is risen in step S7.After the step S8, return step S1.Control device 30 carries out step S1～S8 repeatedly, until becoming in step S7 is.
When reducing the aperture of downstream throttling arrangement, it is big that the pressure differential of the front and back of downstream throttling arrangement becomes, and follows in this, and middle the pressure uprises.The ratio of the flow of the cold-producing medium that sprays in addition, also increases.When the centre presses when rising, in the gas-liquid separator 16 in the middle of the aridity of compacting cryogen reduce.As mentioned above, when continuing to reduce the aperture of downstream throttling arrangement, aridity continues to reduce, and the flow of the cold-producing medium that sprays continues to increase, so flow into jet path 22 at a certain stage liquid refrigerant.
When liquid refrigerant flows into jet path 22, heat and make its evaporation by 24 pairs of liquid refrigerants of heater, so under the effect of latent heat at this moment, the injection of refrigerant temperature T inj that has passed through after the heater 24 reduces sharp.Step S7 reduces the step that this situation detects for being used for sharp to injection temperation Tinj.
For under the situation that is, namely reduce sharp by the gas refrigerant after the heater 24 at injection temperation Tinj and fail to obtain under the situation of the degree of superheat more than the fixed temperature, the gas-liquid separation temperature T m that control device 30 will this moment are recorded as Tm0 (step S9) in step S7.
By improving intermediate pressure, can reduce the amount of work of in compressor 10, compressing again, so can reduce the electric power consumption of compressor 10.But when liquid refrigerant began to flow to jet path 22, the amount of flowing liquid cold-producing medium also reduced in evaporimeter, and evaporability reduces, and performance of refrigeration circulation also reduces.Thereby, in order in the refrigerating circulatory device 100 that sprays, to obtain higher performance, jet path 22 need be formed the state that only has gas refrigerant to flow.Therefore, control device 30 is determined the gas-liquid separation temperature T m1 (step S10) of target.Particularly, the situation of control device 30 in order to prevent that reliably liquid refrigerant from flowing into to jet path 22, can't obtain gas-liquid separation temperature T m0 under the state of the degree of superheat more than the fixed temperature by the gas refrigerant after the heater 24 and (for example deduct the set point of temperature that pre-determines out from being in, 1 ℃), the gas-liquid separation temperature T m1 that calculates target thus.
After step S10, again the aperture of downstream throttling arrangement is adjusted and pressure and gas-liquid separation temperature T m decline in the middle of making, thereby become the state that in jet path 22, only has gas refrigerant to flow.Particularly, press 26 couples of middle gas-liquid separation temperature T m that press of temperature sensor to detect (step S11) in the middle of control device 30 utilizes, and its gas-liquid separation temperature T m1 with the target of determining in step S10 is compared (step S12).Under the situation more than the gas-liquid separation temperature T m1 that detected gas-liquid separation temperature T m is target (being not among the step S12), increase the aperture (step S13) of downstream throttling arrangement, drops in the middle of making.When being lower than the gas-liquid separation temperature T m1 of target in the aperture that increases the downstream throttling arrangement (among the step S12 for being), to the steady running transfer of controlling in the mode of the gas-liquid separation temperature of the ejection temperature that keeps target, target (step S14).
After steady running is shifted, press temperature sensor 26 and ejection temperature sensor 34 to come gas-liquid separation temperature T m and ejection temperature T d are detected in the middle of control device 30 also utilizes, and so that they away from the mode of desired value the aperture of upstream side throttling arrangement and downstream throttling arrangement is not adjusted.
The control of gas-liquid separation temperature T m is undertaken by the adjustment of the aperture of downstream throttling arrangement.Particularly, so that detected gas-liquid separation temperature T m becomes fixed temperature Δ Tms apart from the gas-liquid separation temperature T m1 of target in interior mode the aperture of downstream throttling arrangement is adjusted.Gas-liquid separation temperature T m than the low situation of Tm1-Δ Tms under, reduce the aperture of downstream throttling arrangement, gas-liquid separation temperature T m is risen, and makes Tm near Tm1.On the contrary, gas-liquid separation temperature T m than the high situation of Tm1+ Δ Tms under, increase the aperture of downstream throttling arrangement, gas-liquid separation temperature T m is descended, and makes Tm near Tm1.The adjustment amount of the aperture of the downstream throttling arrangement during this adjustment both can also can more more reduce the adjustment amount of aperture for fixing near desired value.
The control of ejection temperature T d is undertaken by the adjustment of the aperture of upstream side throttling arrangement.Particularly, so that detected ejection temperature T d becomes fixed temperature Δ Tds apart from the ejection temperature T D of target in interior mode the aperture of upstream side throttling arrangement is adjusted.Ejection temperature T d than the low situation of TD-Δ Tds under, reduce the aperture of upstream side throttling arrangement, ejection temperature T d is risen, and makes Td near TD.On the contrary, ejection temperature T d than the high situation of Td+ Δ Tds under, increase the aperture of upstream side throttling arrangement, ejection temperature T d is descended, and makes Td near TD.The adjustment amount of the aperture of the upstream side throttling arrangement during this adjustment both can also can more more reduce the adjustment amount of aperture for fixing near desired value.
As shown in Figure 1, gas-liquid separator 16 is configured between upstream side throttling arrangement and the downstream throttling arrangement, so gas-liquid separation temperature T m is subjected to the very big influence of adjustment of the aperture of upstream side throttling arrangement.Particularly, when reducing the aperture of upstream side throttling arrangement, it is big that the differential pressure before and after the upstream side throttling arrangement becomes, and follows in this, and middle pressure drop is low, and gas-liquid separation temperature T m reduces.On the contrary, when increasing the aperture of upstream side throttling arrangement, the differential pressure before and after the upstream side throttling arrangement diminishes, and follows in this, and the centre presses liter, and gas-liquid separation temperature T m rises.So, the adjustment of the aperture of upstream side throttling arrangement is not only given influence for ejection temperature T d, and m also gives influence for the gas-liquid separation temperature T.This situation is not limited to the upstream side throttling arrangement, and when the adjustment of the aperture of carrying out the downstream throttling arrangement, quantitative changeization to the mobile cold-producing medium of evaporimeter, the suction condition of compressor 10 changes, so the adjustment of the aperture of downstream throttling arrangement is not only given influence for gas-liquid separation temperature T m, d also gives influence for the ejection temperature T.
So, the aperture adjustment separately of upstream side throttling arrangement and downstream throttling arrangement is given influence to ejection temperature T d and gas-liquid separation temperature T m respectively, but, control ejection temperature T d when utilizing the upstream side throttling arrangement, and utilize the downstream throttling arrangement control gas-liquid separation temperature T m such each throttling arrangement is had respectively control as land used the 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 T d, injection temperation Tinj and gas-liquid separation temperature T m change.As shown in Figure 3, in the present embodiment, at first, the aperture of upstream side throttling arrangement is little by little reduced, and ejection temperature T d little by little rises.Then, the aperture of downstream throttling arrangement is reduced, Tinj reduces sharp until injection temperation, and the aperture with the downstream throttling arrangement increases then.
In the middle pressure-controlled running of above explanation, adopt heater 24 and degree of superheat temperature sensor 28 to determine the fiducial temperature Tm0 of gas-liquid separation temperature T m, and will be made as the target temperature Tm1 of gas-liquid separation temperature than the temperature of the low set point of temperature Δ Tm of this fiducial temperature Tm0, press the evaluated error of temperature sensor 26 in the middle of can eliminating thus.Thus, the centre can be pressed and be controlled to be the purpose value more accurately, thereby the efficient of refrigerating circulatory device 100 is improved.
In addition, in the present embodiment, when starting operation, carry out centre pressure-controlled running, therefore can shift to steady running from starting operation with the state of the best.
＜variation 〉
In said embodiment, when starting operation, carried out middle pressure-controlled running.Therefore, so that the mode that the temperature difference between gas-liquid separation temperature T m and the injection temperation Tinj becomes littler than setting upstream side throttling arrangement and downstream these both sides' of throttling arrangement aperture is adjusted.But control device 30 also can turn round in the centre pressure-controlled of carrying out of steady running midway.In this case, also can so that the mode that the temperature difference between gas-liquid separation temperature T m and the injection temperation Tinj becomes littler than setting the aperture of the either party in upstream side throttling arrangement and the downstream throttling arrangement is adjusted.
Flow chart and Fig. 2 in the middle of midway the carrying out of steady running during the pressure-controlled running are identical.That is entering step S1 when, having satisfied some decision condition in steady running gets final product.For example, the temperature degree changes, enters when cycling condition changes greatly etc. step S1 outside, also can enter step S1 according to the variation of the requirement of user's side.Or, also can enter step S1 according to the elapsed time that begins from running.
In said embodiment, used electric heater as heater 24.But heater 24 is not limited to electric heater etc. applies heat to cold-producing medium from the outside of refrigerant loop 1 mechanism.For example, substantivity such as a part that also can be by making the refrigerant piping that constitutes jet path 22 and the closed container of the compressor 10 of cold-producing medium (gas-liquid separation temperature) high temperature that temperature is high of pressing than the centre or ejection pipe arrangement or contact to property indirectly, the part of refrigerant loop 1 formation heater 24 thus.Below, the variation of heater 24 is described in detail.Need to prove that variation shown below all similarly constitutes with described embodiment except situation about specifying.
Fig. 4 represents the heater 24A as a variation of heater 24.Heater 24A accumulates the heat of discharging from compressor 10, and utilizes this heat of accumulating to come the thermal storage unit that the cold-producing medium that flows is heated in jet path 22.Particularly, heater 24A has: the heat accumulation member 50 that disposes in the mode that compressor 10 is wrapped into; The serpentine pipe 52 that wriggles and pass through in the inside of heat accumulation member 50.Serpentine pipe 52 constitutes the part of jet path 22.Thereby 22 cold-producing mediums that flow into are heated by flowing serpentine pipe 52 from gas-liquid separator 16 to jet path.And then the cold-producing medium that has passed through serpentine pipe 52 is sprayed to compressor 10.Thus, can utilize the used heat of compressor 10, come the cold-producing medium that flows in jet path 22 is heated.Owing to need not for the cold-producing medium that flows is heated independently electric heater to be set in jet path 22, so can realize the saving electrification of refrigerating circulatory device.
Fig. 5 represents to possess the refrigerating circulatory device 100A as the heater 24B of another variation of heater 24.Heater 24B has to the first heat exchange portion 60 of the cold-producing medium channeling conduct of flowing in jet path 22 and from refrigerant loop 1 branch and to the heat exchanger of the second heat exchange portion 62 of the cold-producing medium channeling conduct of flowing refrigerant loop 1.The first heat exchange portion 60 also is the part of jet path 22.Be directed to the temperature of cold-producing medium of the second heat exchange portion 62 than gas-liquid separation temperature height.The second heat exchange portion 62 is connected with refrigerant loop 1 between the upstream side throttling arrangement 14 with condenser 12.Specifically, the second heat exchange portion 62 has the end that is connected with refrigerant loop 1 between the upstream side throttling arrangement 14 with condenser 12 and at the other end that more is connected with refrigerant loop 1 between the upstream side throttling arrangement 14 with condenser 12 by the place, downstream than this end.Thus, the cold-producing medium that between condenser 12 and upstream side throttling arrangement 14, flows to 62 guiding of the second heat exchange portion.In addition, the second heat exchange portion 62 is configured to the first heat exchange portion 60 is heated.Thus, the cold-producing medium that flows in jet path 22 is heated.Thereby the heat that can utilize cold-producing medium mobile in refrigerant loop 1 to have comes the cold-producing medium that flows in jet path 22 is heated.Need not for the cold-producing medium that flows in jet path 22 being heated and independently electric heater being set, so can realize the saving electrification of refrigerating circulatory device.In addition, can improve the supercooling degree of cold-producing medium of outlet side of the condenser 12 of refrigerant loop 1, so can realize the refrigerating circulatory device 100A that refrigerating capacity is improved.
Fig. 6 represents to possess the refrigerating circulatory device 100B as the heater 24C of a variation again of heater 24.Heater 24C has to the first heat exchange portion 70 of the cold-producing medium channeling conduct of flowing in jet path 22 and from refrigerant loop 1 branch and to the heat exchanger of the second heat exchange portion 72 of the cold-producing medium channeling conduct of flowing refrigerant loop 1.The first heat exchange portion 70 also is the part of jet path 22.The second heat exchange portion 72 is connected with refrigerant loop 1 between the condenser 12 with compressor 10.Specifically, the second heat exchange portion 72 has the end that is connected with refrigerant loop 1 between the condenser 12 with compressor 10 and at the other end that more is connected with refrigerant loop 1 between the condenser 12 with compressor 10 by the place, downstream than this end.Thus, among the cold-producing medium that in refrigerant loop 1, flows to the guiding of the second heat exchange portion 72 be than higher temperatures, between compressor 10 and condenser 12 mobile cold-producing medium.Be directed to the temperature of cold-producing medium of the second heat exchange portion 72 than gas-liquid separation temperature height.In addition, the second heat exchange portion 72 is configured to the first heat exchange portion 70 is heated.Thus, the cold-producing medium that flows in jet path 22 is heated.Thereby, can utilize in refrigerant loop 1 heat that has for the cold-producing medium than higher temperatures among the cold-producing medium that flows, come the cold-producing medium that flows in jet path 22 is heated.Owing to need not for the cold-producing medium that flows is heated independently electric heater to be set in jet path 22, so can realize the saving electrification of refrigerating circulatory device.
The first heat exchange portion 70 and the second heat exchange portion 72 are by constituting with the first heat exchange portion 60 of heater 24B and the second heat exchange portion 62 same structure.In addition, the motor-driven valve that for example can adjust aperture also can be arranged on the upstream side of the second heat exchange portion 72 and be connected with the second heat exchange portion 72 an end the position and be connected with on the refrigerant loop 1 between the position of the other end of the second heat exchange portion 72.The second heat exchange portion 72 also can be for from refrigerant loop 1 unbranched form.In other words, the second heat exchange portion 72 also can be made of the part of the refrigerant loop 1 between compressor 10 and the condenser 12.
(second embodiment)
Fig. 7 represents the refrigerating circulatory device 200 that second embodiment of the present invention is related.Need to prove, in the present embodiment, be marked with same-sign for the structure identical with first embodiment, and omit its explanation.
In the present embodiment, be provided with indoor heat exchanger side temperature sensor 40 between indoor heat exchanger 12 in refrigerant loop 1 and the 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.Need to prove that the action of the refrigerating circulatory device 200 of present embodiment is identical with the action of the refrigerating circulatory device 100 of first embodiment.
When heating, 40 pairs of temperature from the cold-producing medium of indoor heat exchanger (condenser) 12 outflows of indoor heat exchanger side temperature sensor are that condensation side outlet temperature Tc detects, and the temperature of the cold-producing medium that outdoor heat exchanger side temperature sensor 42 subtend outdoor heat exchangers (evaporimeter) 20 flow into is that evaporation side inlet temperature Te detects.When refrigeration, 42 pairs of temperature from the cold-producing medium of outdoor heat exchanger (condenser) 20 outflows of outdoor heat exchanger side temperature sensor are that condensation side outlet temperature Tc detects, and the temperature of the cold-producing medium that indoor heat exchanger side temperature sensor 40 subtend indoor heat exchangers (evaporimeter) 12 flow into is that evaporation side inlet temperature Te detects.Below, outdoor heat exchanger side temperature sensor 42 during with the indoor heat exchanger side temperature sensor 40 in when heating and refrigeration is called temperature sensor after the condensation, indoor heat exchanger side temperature sensor 40 during with the outdoor heat exchanger side temperature sensor 42 in when heating and refrigeration is called temperature sensor before the evaporation, describes during similarly not to heating and during refrigeration with first embodiment with being distinguished.
Flow chart shown in Figure 8 changes to step S21～S23 with the step S9 of flow chart shown in Figure 2, and other step S1～S8, S10～S14 are identical with first embodiment.Therefore, below, centered by present embodiment step S21～S23 alone, describe.
In step S7, control device 30 be judged to be by the centre press temperature sensor 26 detected gas-liquid separation temperature T m and by the temperature difference between the degree of superheat temperature sensor 28 detected injection temperation Tinj than predetermined setting Δ Ti hour, temperature sensor detects condensation side outlet temperature Tc after utilizing condensation, and temperature sensor detects (step S21) to evaporation side inlet temperature Te before utilizing evaporation.Then, the gas-liquid separation temperature T m that control device 30 will become in step S7 when being is recorded as Tm0, and will be in step S21 detected condensation side outlet temperature Tc and evaporation side inlet temperature Te be stored as Tc0 and Te0 (step S22) respectively.Then, control device 30 uses Tm0, Tc0, the Te0 of storage, and the calculating formula of the gas-liquid separation temperature used in steady running is revised (step S23).
At this, so-called " calculating formula of the gas-liquid separation temperature of in steady running, using ", for being used for according to condensation side outlet temperature Tc and evaporation side inlet temperature Te or only inferring the calculating formula of gas-liquid separation temperature according to condensation side outlet temperature Tc, for example as following formula (1) represent.
Tm2＝αTc+β···(1)
Need to prove that under the situation of use formula (1), only inferring under the situation of gas-liquid separation temperature according to the condensation side outlet temperature in other words, temperature sensor detects evaporation side inlet temperature Te before need not to utilize evaporation in step S21.That is, can only use Tm0 and Tc0 to come the calculating formula of gas-liquid separation temperature is revised.Below, in order to should be readily appreciated that explanation, suppose that use formula (1) describes.
In step S23, the Tc0 substitution formula (1) that control device 30 will be stored in step S22 is calculated and is inferred temperature T m2.Control device 30 will be calculated infers temperature T m2 and compares with the Tm0 that stores in step S22, presses the evaluated error of temperature sensor after temperature sensor 26 and the condensation as the centre and the mode that is eliminated is rewritten the calculating formula of gas-liquid separation temperature with its difference.For example, under the Tm0 situation bigger with respect to Tm2, in calculating formula, add its residual quantity (Tm0-Tm2) as correction value, under the Tm0 situation less with respect to Tm2, in calculating formula, deduct its residual quantity (Tm2-Tm0) as correction value.Or, factor alpha, β in the above-mentioned formula (1) are changed.
Then, control device 30 shifts (step 814) through step S10～S13 to steady running.In steady running, control device 30 uses the calculating formula of revised gas-liquid separation temperature in middle pressure-controlled running to carry out steady running.Particularly, press in the middle of control device 30 utilizes after temperature sensor 26, ejection temperature sensor 34, the condensation that temperature sensor detects gas-liquid separation temperature T m, ejection temperature T d, condensation side outlet temperature Tc, evaporation side inlet temperature Te before the temperature sensor and evaporation, and so that they away from the mode of desired value the aperture of upstream side throttling arrangement and downstream throttling arrangement is not adjusted.
In the first embodiment, the gas-liquid separation temperature T m1 of target is for fixing, but in the present embodiment, infers the gas-liquid separation temperature that temperature T m2 is set at target with what the calculating formula of using the gas-liquid separation temperature of having revised in step S23 was calculated.The control of ejection temperature T d and gas-liquid separation temperature T m and first embodiment similarly, the adjustment of the aperture by upstream side throttling arrangement and downstream throttling arrangement is carried out.
So, in middle pressure-controlled running, the calculating formula of inferring gas-liquid separation temperature T m according to other thermometer measuring point is revised, and should revised calculating formula in steady running, use, in steady running, also can realize also having considered pressure-controlled in the middle of evaluated error etc. more high-precision of temperature sensor thus.
＜variation 〉
Need to prove, in flow chart shown in Figure 8, the step S21 that detects condensation side outlet temperature Tc and evaporation side inlet temperature Te is configured in after the step S7, but also step S21 can be configured between step S6 and the step S7, and dispose the step of determining the gas-liquid separation temperature T m3 of target according to condensation side outlet temperature Tc and evaporation side inlet temperature Te afterwards, in step S8, when the difference of the gas-liquid separation temperature T m3 of detected gas-liquid separation temperature T m and target is big, increase the adjustment amount of aperture, and hour reduce the adjustment amount of aperture in its difference.
In addition, in step S10, when determining the gas-liquid separation temperature T m1 of target, also can replace using Tm0, infer temperature T m2 and use by what revised calculating formula in step S23 obtained.
In addition, the heater 24 of second embodiment also can carry out the change same with the variation of first embodiment.
(other embodiment)
Need to prove, in said embodiment, in refrigerant loop 1, be provided with cross valve 32, and can realize the switching of freezing and heating, but that refrigerating circulatory device of the present invention also can be freeze special use or heating is special-purpose.
[industrial aspect utilizability]
The heat pump assembly that refrigerating circulatory device of the present invention can be used as hot water supply device, hot-water heater, refrigeration or air-conditioning equipment etc. utilizes.
Claims (13)
1. refrigerating circulatory device wherein, possesses:
Refrigerant loop, it makes cold-producing medium circulate in the mode by compressor, condenser, upstream side throttling arrangement, gas-liquid separator, downstream throttling arrangement and evaporimeter successively;
Jet path, it will be supplied with to described compressor by the gas refrigerant after the described gas-liquid separator separates;
Heater, it is located at described jet path;
The middle temperature sensor of pressing, its temperature to the cold-producing medium to described jet path inflow from described refrigerant loop is that the gas-liquid separation temperature detects;
Degree of superheat temperature sensor, it is to being that injection temperation detects by the temperature of the cold-producing medium after the heating of described heater in described jet path;
Control device, it carries out centre pressure-controlled running, in this centre pressure-controlled running, described control device is after little mode is adjusted the aperture of at least one side in described upstream side throttling arrangement and the described downstream throttling arrangement so that the temperature difference between described gas-liquid separation temperature and the described injection temperation becomes than setting, increase the aperture of described downstream throttling arrangement, reduced set point of temperature until described gas-liquid separation temperature from temperature at this moment.
2. refrigerating circulatory device as claimed in claim 1, wherein,
Also possess temperature sensor after the condensation, temperature sensor is that the condensation side outlet temperature detects to the temperature of the cold-producing medium that flows out from described condenser after this condensation,
Described control device is in described middle pressure-controlled running, use temperature difference between described gas-liquid separation temperature and the described injection temperation to become than described gas-liquid separation temperature and the described condensation side outlet temperature of setting hour, the calculating formula of the gas-liquid separation temperature used in steady running is revised.
3. refrigerating circulatory device as claimed in claim 2, wherein,
Also possess the preceding temperature sensor of evaporation, the temperature of the cold-producing medium that the described evaporimeter of temperature sensor subtend flows into before this evaporation is that the evaporation side inlet temperature detects,
When the calculating formula of the gas-liquid separation temperature that described control device uses in to steady running is revised, also use temperature difference between described gas-liquid separation temperature and the described injection temperation to become than the described evaporation side inlet temperature of setting hour.
4. refrigerating circulatory device as claimed in claim 2, wherein,
Described control device uses 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 turns round in the described middle pressure-controlled of carrying out of steady running midway.
7. refrigerating circulatory device as claimed in claim 5, wherein,
Also possess the ejection temperature sensor, this ejection temperature sensor namely sprays temperature to the temperature from the cold-producing medium of described compressor ejection and detects,
Described control device so that near the mode that described ejection temperature remains on the ejection temperature of target the aperture of described upstream side throttling arrangement is adjusted, and reduce the aperture of described downstream throttling arrangement simultaneously, temperature difference between described gas-liquid separation temperature and described injection temperation becomes littler than setting, increases the aperture of described downstream throttling arrangement then.
8. refrigerating circulatory device as claimed in claim 1, wherein,
Described refrigerant loop comprises indoor heat exchanger and the outdoor heat exchanger as described condenser and described evaporimeter performance function, and comprise indoor throttling arrangement and outside throttling arrangement as described upstream side throttling arrangement and described downstream throttling arrangement performance function
In described refrigerant loop, be provided with the cross valve that the flow direction to cold-producing medium switches.
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 that the heat of discharging from described compressor is accumulated, and the thermal storage unit that utilizes this heat of accumulating that cold-producing medium is heated.
11. refrigerating circulatory device as claimed in claim 1, wherein,
Described heater is the heat exchanger that comprises the first heat exchange portion and the second heat exchange portion, the cold-producing medium that flows in described jet path imports the described first heat exchange portion, in described refrigerant loop, flow and import the described second heat exchange portion with cold-producing medium that described gas-liquid separation temperature is in a ratio of high temperature
In described heat exchanger, the described second heat exchange portion heats the described first heat exchange portion.
12. refrigerating circulatory device as claimed in claim 11, wherein,
Import the cold-producing medium that between described compressor and described condenser, flows to the described second heat exchange portion.
13. refrigerating circulatory device as claimed in claim 11, wherein,
Import the cold-producing medium that between described condenser and described upstream side throttling arrangement, flows to the described second heat exchange portion.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
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| JP2011148794 | 2011-07-05 | ||
| JP2011-148794 | 2011-07-05 | ||
| PCT/JP2012/004313 WO2013005424A1 (en) | 2011-07-05 | 2012-07-03 | Refrigeration cycle device |
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| CN103348197A true CN103348197A (en) | 2013-10-09 |
| CN103348197B CN103348197B (en) | 2016-02-10 |
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| CN201280007707.4A Active CN103348197B (en) | 2011-07-05 | 2012-07-03 | Refrigerating circulatory device |
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| EP (1) | EP2730859B1 (en) |
| JP (1) | JP5906440B2 (en) |
| CN (1) | CN103348197B (en) |
| WO (1) | WO2013005424A1 (en) |
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| 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 |
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- 2012-07-03 CN CN201280007707.4A patent/CN103348197B/en active Active
- 2012-07-03 WO PCT/JP2012/004313 patent/WO2013005424A1/en active Application Filing
- 2012-07-03 JP JP2013522469A patent/JP5906440B2/en not_active Expired - Fee Related
- 2012-07-03 EP EP12807481.2A patent/EP2730859B1/en not_active Not-in-force
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| 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 |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105593615A (en) * | 2013-10-25 | 2016-05-18 | 大金工业株式会社 | Refrigeration device |
| CN105546891A (en) * | 2015-09-23 | 2016-05-04 | 湖南华强电气股份有限公司 | Vehicle-mounted air-conditioning system and energy saving method thereof |
| CN106595105A (en) * | 2015-10-19 | 2017-04-26 | Lg电子株式会社 | Air conditioner |
| US10317113B2 (en) | 2015-10-19 | 2019-06-11 | Lg Electronics Inc. | Air conditioner |
| CN106595105B (en) * | 2015-10-19 | 2019-07-05 | Lg电子株式会社 | Air regulator |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2730859A1 (en) | 2014-05-14 |
| EP2730859B1 (en) | 2019-04-10 |
| CN103348197B (en) | 2016-02-10 |
| JP5906440B2 (en) | 2016-04-20 |
| EP2730859A4 (en) | 2014-11-12 |
| WO2013005424A1 (en) | 2013-01-10 |
| JPWO2013005424A1 (en) | 2015-02-23 |
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