CN102032698A - Refrigeration cycle apparatus and hot water heater - Google Patents
Refrigeration cycle apparatus and hot water heater Download PDFInfo
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- CN102032698A CN102032698A CN2010105093428A CN201010509342A CN102032698A CN 102032698 A CN102032698 A CN 102032698A CN 2010105093428 A CN2010105093428 A CN 2010105093428A CN 201010509342 A CN201010509342 A CN 201010509342A CN 102032698 A CN102032698 A CN 102032698A
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
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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
- F25B2500/00—Problems to be solved
- F25B2500/08—Exceeding a certain temperature value in a refrigeration component or 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
- F25B2500/00—Problems to be solved
- F25B2500/31—Low ambient temperatures
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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
- F25B2700/21—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
- F25B2700/2103—Temperatures near a heat exchanger
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A refrigeration cycle apparatus 1A includes: a refrigerant circuit 2 provided with a subcooling heat exchanger 23; a bypass passage 3 extending through the subcooling heat exchanger 23; and a controller 4 for controlling a main expansion means 24 in the refrigerant circuit 2 and a bypass expansion means 31 in the bypass passage 3. The bypass expansion means 31 is controlled so that a bypass side outlet temperature conforms to a saturation temperature at a pressure of a refrigerant to be drawn into a compressor 21, and a degree of superheat at an outlet of an evaporator 25 calculated based on an evaporator outlet temperature is equal to or lower than a predetermined degree of superheat.
Description
Technical field
The present invention relates to a kind of the cold-producing medium that flows out from condenser is carried out overcooled freezing cycle device and uses the hot-water central heating device of this freezing cycle device.
Background technology
There is a kind of freezing cycle device in past, and it is provided with the supercooling heat exchanger in a dirty side of the condenser of refrigerant line, and the cold-producing medium of expansion is flowed in this supercooling heat exchanger, with this cold-producing medium that comes supercooling to flow out from condenser.For example, freezing cycle device shown in Figure 6 100 is disclosed in patent documentation 1.
This freezing cycle device 100 comprises refrigerant line 110 and the bypass 120 that makes the cold-producing medium circulation.Refrigerant line 110 constitutes by using pipe arrangement that compressor 111, condenser 112, supercooling heat exchanger 113, main expansion valve 114 and evaporimeter 115 are connected to form ring-type.Bypass 120 from refrigerant line 110 branches, via supercooling heat exchanger 113, links to each other with refrigerant line 110 between evaporimeter 115 and compressor 111 between condenser 112 and supercooling heat exchanger 113 then.In addition, in bypass 120, be provided with bypass expansion valve 121 comparing more close upper reaches one side with supercooling heat exchanger 113.
In freezing cycle device 100, be provided with: the pressure sensor 131 that detects the pressure that is inhaled into the cold-producing medium in the compressor 111; Detect the temperature sensor 141 of temperature (evaporator outlet temperature) Teo of the cold-producing medium that flows out from evaporimeter 115; Detect in bypass 120 temperature sensor 142 of temperature (the bypass pipe one side outlet temperature) Tbo of the cold-producing medium that flows out from supercooling heat exchanger 113.
In patent documentation 1, calculate saturation temperature Ts under this pressure according to the pressure that in pressure sensor 131, detects, control main expansion valve 114 is so that the degree of superheat (Teo-Ts) in evaporimeter 115 outlets becomes the target degree of superheat, and control bypass expansion valve 121 is so that the degree of superheat (Tbo-Ts) in 113 outlets of supercooling heat exchanger becomes the target degree of superheat.
Patent documentation 1 Japanese kokai publication hei 10-68553 communique
Invent technical task to be solved
But, as described in patent documentation 1, controlling bypass expansion valve 121 so that the degree of superheat (Tbo-Ts) in 113 outlets of supercooling heat exchanger becomes under the situation of the target degree of superheat, more cold-producing medium is evaporated in supercooling heat exchanger 113, therefore, can't maximally utilise the performance of supercooling heat exchanger 113.That is, the heat exchange that can not improve to greatest extent by main flow cold-producing medium and bypass flow cold-producing medium increases the effect of the enthalpy in the evaporimeter 115 and the effect that reduces the pressure loss of low pressure one side refrigerant flow path by the bypass of cold-producing medium.And, if the cold-producing medium of bypass evaporimeter 115 by overheated (superheat), so, is inhaled into the volume ratio increase of the cold-producing medium in the compressor 111, the phenomenon that circulating mass of refrigerant reduces not only can take place, and the discharge temperature of compressor can increase also.Therefore, when the outside air that requires big heating efficiency is low temperature, from the control discharge temperature, guarantee the viewpoint of reliability, can not too much increase the rotating speed of compressor, heating efficiency might be not enough.
The present invention In view of the foregoing produces, its purpose is, a kind of not only can be the to greatest extent actual effect of the enthalpy in the evaporimeter and effect that reduces the pressure loss of low pressure one side refrigerant flow path of increasing is provided, and the hot-water central heating device that can obtain the freezing cycle device of sufficient heating efficiency and use this freezing cycle device during for low temperature at outside air.
Summary of the invention
In order to solve above-mentioned problem, the invention provides a kind of freezing cycle device, it comprises: compressor, condenser, supercooling heat exchanger, main expansion mechanism and evaporimeter are connected to form the refrigerant line of ring-type; Between described condenser and the described supercooling heat exchanger or between described supercooling heat exchanger and the described main expansion mechanism, from described refrigerant line branch, via described supercooling heat exchanger, the bypass that between described evaporimeter and described compressor, links to each other then with described refrigerant line; Comparing the bypass expansion mechanism that more close upper reaches one side is provided with the described supercooling heat exchanger of described bypass; Detect in described bypass the 1st temperature sensor of the temperature of the cold-producing medium that flows out from described supercooling heat exchanger; Detect in described refrigerant line the 2nd temperature sensor of the temperature of the cold-producing medium that flows out from described evaporimeter; Control device, control described bypass expansion mechanism, so that the temperature that detects in described the 1st temperature sensor is the saturation temperature that is inhaled under the pressure of the cold-producing medium in the described compressor, and to make the degree of superheat of calculating in the described evaporator outlet according to the temperature that detects in described the 2nd temperature sensor be below the degree of superheat of predefined regulation.
In addition, the invention provides a kind of hot-water central heating device, it is the hot-water central heating device that the warm water that heating arrangements generates is used to heat, and it is equipped with described freezing cycle device as described heating arrangements.
The invention effect
According to above-mentioned structure, the temperature of the cold-producing medium that flows out from the supercooling heat exchanger in bypass is maintained at the saturation temperature under the pressure that is inhaled into the cold-producing medium the compressor, therefore, the cold-producing medium that flows out from the supercooling heat exchanger can be remained on moisture state or saturated gas state.And, the degree of superheat in the evaporator outlet is controlled in below the degree of superheat of regulation, therefore, the flow of cold-producing medium of bypass of flowing through is too much, it is low excessively to be inhaled into cold-producing medium in the compressor (cold-producing medium of the bypass of flowing through and by the cold-producing medium behind the cold-producing medium interflow of evaporimeter) aridity, and the aridity that is inhaled into the cold-producing medium in the compressor can be controlled at the scope (for example, more than 0.8 less than 1.0) of expection.The heat exchange that so just can improve to greatest extent by main flow cold-producing medium and bypass flow cold-producing medium increases the effect of the enthalpy in the evaporimeter and the effect that reduces the pressure loss of low pressure one side refrigerant flow path by the bypass of cold-producing medium.In addition, the discharge temperature of compressor is controlled, and therefore, when outside air is low temperature, can increase the rotating speed of compressor, and can obtain sufficient heating efficiency.
Description of drawings
Fig. 1 is the structure overview of the freezing cycle device of the 1st embodiment of the present invention.
Fig. 2 is the mollier diagram of freezing cycle device shown in Figure 1.
Fig. 3 is the flow chart of the control that control device carried out in the 1st embodiment.
Fig. 4 is the structure overview of the freezing cycle device of the 2nd embodiment of the present invention.
Fig. 5 is the flow chart of the control that control device carried out in the 2nd embodiment.
Fig. 6 is the structure overview of traditional freezing cycle device.
Symbol description
1A, 1B freezing cycle device
2 refrigerant lines
21 compressors
22 condensers
23 supercooling heat exchangers
24 main expansion valves (main expansion mechanism)
25 evaporimeters
3 bypasses
31 bypass expansion valves (bypass expansion mechanism)
4 control device
51 pressure sensors
61 the 1st temperature sensors
62 the 2nd temperature sensors
63 the 3rd temperature sensors
The specific embodiment
(the 1st embodiment)
Fig. 1 represents the freezing cycle device 1A of the 1st embodiment of the present invention.This freezing cycle device 1A comprises: the refrigerant line 2 that makes the cold-producing medium circulation; Bypass 3; And control device 4.Cold-producing medium for example can use approximate azeotropic refrigerants such as mixed non-azeotropic refrigerant, R410A such as R407C or unitary system cryogen etc.
In the present embodiment, freezing cycle device 1A constitutes the heating arrangements of the hot-water central heating device that will be used to heat by the warm water that heating arrangements generated, and condenser 22 is to carry out the heat exchanger that heat exchange adds hot water then between cold-producing medium and water.Specifically, connect supply pipe 71 and recovery tube 72 in condenser 22, water is supplied to condenser 22 by supply pipe 71, and heated water (warm water) is recovered by recovery tube 72 in condenser 22.Be recovered warm water that pipe 72 reclaims and be sent to heating machines such as radiator directly or by water tank, heat according to the method described above.
In turning round usually, the cold-producing medium of discharging from compressor 21 is sent to condenser 22 by cross valve 28, and in the defrosting running, the cold-producing medium of discharging from compressor 21 is sent to evaporimeter 25 by cross valve 28.In Fig. 1, the flow direction of the cold-producing medium when representing to turn round usually with arrow.Below, the state variation of the cold-producing medium when running usually is described.
The high-pressure refrigerant of discharging from compressor 21 flows into condenser 22, dispels the heat in the water by condenser 22.The high-pressure refrigerant that flows out from condenser 22 flows into supercooling heat exchanger 23, by the low pressure refrigerant supercooling of decompression in bypass expansion valve 31.The high-pressure refrigerant shunting of flowing out from supercooling heat exchanger 23 forms main expansion valve 24 1 sides and bypass expansion valve 31 1 sides.
The high-pressure refrigerant that shunting forms main expansion valve 24 1 sides by main expansion valve 24 puffings after, inflow evaporator 25.The low pressure refrigerant of inflow evaporator 25 absorbs heat from air herein.On the other hand, the high-pressure refrigerant that shunting forms bypass expansion valve 31 1 sides by bypass expansion valve 31 puffings after, flow into supercooling heat exchanger 23.The low pressure refrigerant that flows into supercooling heat exchanger 23 is heated by the high-pressure refrigerant that flows out from condenser 22.Then, from supercooling heat exchanger 23 low pressure refrigerant that flows out and the low pressure refrigerant interflow of flowing out, sucked once more in the compressor 21 from evaporimeter 25.
The purpose of the structure of the freezing cycle device 1A of employing present embodiment is, prevents when outside air is low temperature, and the pressure that is inhaled into the cold-producing medium in the compressor 21 descends, and circulating mass of refrigerant reduces, and the heating efficiency of condenser 22 descends.In order to realize this purpose, increase enthalpy difference in the evaporimeter 25 by supercooling, simultaneously, make refrigerant bypass by bypass 3, control the flow of the little vapor phase refrigerant of the endothermic effect of low pressure one side part of the refrigerant line 2 of flowing through like this, reduce the pressure loss of the low pressure one side part of refrigerant line 2, this point is extremely important.If the pressure loss of low pressure one side of refrigerant line 2 part reduces, so, the pressure that is inhaled into the cold-producing medium in the compressor 21 also correspondingly rises, and specific volume reduces, and therefore, circulating mass of refrigerant increases.In addition, if the enthalpy difference in the increase evaporimeter 25 so, descends even pass through the mass flow of the cold-producing medium of evaporimeter 25 by bypass pipe, also can guarantee the caloric receptivity in the evaporimeter 25.Promptly, if the supercooling degree of cold-producing medium and bypass amount reach to greatest extent, COP (Coefficient of Performance, the coefficient of performance) effect that so, just can obtain to improve the heating efficiency effect of condenser 22 to greatest extent and improve freezing cycle device 1A.
In the present embodiment, its detailed condition will be set forth in the back, control bypass expansion valve 31, thus the cold-producing medium that makes the bypass 3 of flowing through can overheated in supercooling heat exchanger 23 (superheat).Therefore, in bypass 3, the state of the cold-producing medium that flows out from supercooling heat exchanger 23 becomes the saturation state shown in Fig. 2 mid point a.On the other hand, in evaporimeter 25, because cold-producing medium is by overheated, therefore, the state of the cold-producing medium that flows out from evaporimeter 25 is shown in the some b Fig. 2.The cold-producing medium that is inhaled into compressor 21 is the cold-producing medium behind these cold-producing mediums interflow, and therefore, it becomes the state shown in the some c between an a and the some b.
The 1st temperature sensor 61 that detects from refrigerant temperature (the bypass pipe one side outlet temperature) Tbo of supercooling heat exchanger 23 outflows is set in bypass 3.In refrigerant line 2, be provided with the pressure sensor 51 that detects pressure (suction pressure) Ps that is inhaled into the cold-producing medium in the compressor 21; Detect the discharge temperature sensor 65 of temperature (discharge temperature) Td of the cold-producing medium of discharging from compressor 21; And the 2nd temperature sensor 62 that detects temperature (evaporator outlet temperature) Teo of the cold-producing medium that flows out from evaporimeter 25.
The detected value that control device 4 bases detect in various sensors 51,61,62,65 etc., rotating speed, the switching of cross valve 28 and the aperture of main expansion valve 24 and bypass expansion valve 31 of control compressor 21.In the present embodiment, control device 4 is control bypass expansion mechanism 31 when turning round usually, so that the bypass pipe one side outlet temperature T bo that detects in the 1st temperature sensor 61 becomes the saturation temperature STs under the refrigerant pressure that is inhaled into compressor 21, and, make according to the degree of superheat SHe in evaporimeter 25 outlets that the evaporator outlet temperature Teo that the 2nd temperature sensor 62 detects calculates to become below the predefined regulation degree of superheat.
Below, the flow chart with reference to shown in Figure 3 explains the control of common running timed unit 4.
At first, control device 4 detects discharge temperature Td (step S1) in discharge temperature sensor 65, and the aperture (step S2) of adjusting main expansion valve 24 is so that this discharge temperature Td becomes desired value.
Then, control device 4 detects suction pressure Ps in pressure sensor 51, detects bypass pipe one side outlet temperature T bo (step S3) simultaneously in the 1st temperature sensor 61.Control device 4 is calculated saturation temperature STs (step S4) under the pressure that is inhaled into the cold-producing medium in the compressor 21 according to the detected suction pressure Ps that comes.Calculating this saturation temperature STs is to use cold-producing medium rerum natura formula to carry out.Then, control device 4 judges whether bypass pipe one side outlet temperature T bo equates (step S5) with saturation temperature STs.
If bypass pipe one side outlet temperature T bo and saturation temperature STs unequal (being NO in step S5), so, in supercooling heat exchanger 23, can make more cold-producing medium evaporation, therefore, control device 4 is the aperture (step S6) of degree raising bypass expansion valve 31 according to the rules, returns step S1 then.
If bypass pipe one side outlet temperature T bo equates (being YES in step S5) with saturation temperature STs, so, the performance of supercooling heat exchanger 23 can be applied in the evaporation of cold-producing medium to greatest extent, and therefore, control device 4 becomes the control of the aperture that is used for revising bypass expansion valve 31.
That is, control device 4 detects evaporator outlet temperature Teo (step S7) in the 2nd temperature sensor 62, calculates degree of superheat SHe (step S8) in evaporimeter 25 outlet according to following formula.
SHe＝Teo-STs
Then, control device 4 judges whether the degree of superheat SHe in evaporimeter 25 outlets of calculating is the degree of superheat following (step S9) of predefined regulation.If be NO in step S9, so, the some c shown in Fig. 2 too take over (because of underfed, the degree of superheat is excessive), that is some a represent too to take back (too much because of flow, humidity is much),, therefore, degree reduces the aperture (step S10) of bypass expansion valve 31 according to the rules, returns step S1.On the other hand, if be YES in step S9, so, the aperture of bypass expansion valve 31 just in time, therefore, control device 4 intactly returns step S1.
As discussed above, in the present embodiment, because bypass pipe one side outlet temperature T bo is maintained at the saturation temperature STs under the pressure that is inhaled into the cold-producing medium in the compressor 21, therefore, the cold-producing medium that flows out from supercooling heat exchanger 23 can be remained on moisture state or saturated gas state.And, degree of superheat SHe in evaporimeter 25 outlets is controlled in below the degree of superheat of regulation, therefore, the flow of cold-producing medium of bypass 3 of flowing through is too much, thereby the aridity that can prevent to be inhaled into cold-producing medium in the compressor 21 (cold-producing medium of the bypass 3 of flowing through and by the cold-producing medium behind the cold-producing medium interflow of evaporimeter 25) is low excessively, and the aridity that is inhaled into the cold-producing medium in the compressor 21 can be controlled at the scope (for example more than 0.8 less than 1.0) of expection.The heat exchange that so just can improve to greatest extent by main flow cold-producing medium and bypass flow cold-producing medium increases the effect of the enthalpy in the evaporimeter 25 and the effect that reduces the pressure loss of low pressure one side refrigerant flow path by the bypass of cold-producing medium.In addition, the discharge temperature Td of compressor 21 is controlled, and therefore, when outside air is low temperature, can increase the rotating speed of compressor 21, and can obtain sufficient heating efficiency.
Herein, the aridity that " degree of superheat of regulation " used in step S9 preferably is inhaled into the cold-producing medium in the compressor 21 is less than 1.0 the degree of superheat more than 0.8.So just can be under state the most efficiently running freezing cycle device 1A.In addition, the aridity that is inhaled into the cold-producing medium in the compressor 21 is calculated by following formula.
X＝(ha-hl)/(hv-hl)
X: the aridity that is inhaled into the cold-producing medium of compressor 21
Ha: the enthalpy that is inhaled into the cold-producing medium of compressor 21
Hl: be inhaled into the saturated gas enthalpy under the pressure of cold-producing medium of compressor 21
Hv: be inhaled into the saturated liquid enthalpy under the pressure of cold-producing medium of compressor 21
In addition, " degree of superheat of regulation " preferably determine according to outside air temperature, and to guarantee that outside air temperature is low more, the aridity of cold-producing medium that is inhaled into compressor 21 is more little.Like this, reduce the evaporating pressure that causes according to outside air temperature and descend, rise on one side can suppress discharge temperature to exceed correct scope, Yi Bian improve the rotating speed of compressor 21, and can obtain sufficient heating efficiency.In the case, as long as detect outside air temperature, control simultaneously and get final product with ambient air temperature sensor.
Perhaps, " degree of superheat of regulation " preferably recently set according to the compression of cold-producing medium, so that the compression ratio of the refrigeration machine of compressor 21 is high more, the aridity of cold-producing medium that is inhaled into compressor 21 is more little.So just can suppress on one side to raise because of compression ratio improves the discharge temperature that causes, Yi Bian improve the rotating speed of compressor 21, and can obtain sufficient heating efficiency.In the case, as long as detect the discharge pressure and the suction pressure of compressor 21, control simultaneously and get final product with pressure sensor.
From other viewpoint, " degree of superheat of regulation " preferably according to the speed setting of compressor 21, so that the rotating speed of compressor 21 is high more, the aridity that is inhaled into the cold-producing medium in the compressor 21 is low more.So just can suppress on one side to raise because of rotating speed improves the discharge temperature that causes, Yi Bian improve the rotating speed of compressor 21, and can obtain sufficient heating efficiency.
(variation)
In Fig. 1, pressure sensor 51 is set between the position and main reservoir 27 that the bypass 32 in the refrigerant line 2 links to each other, still, so long as between evaporimeter 25 and compressor 21, so, pressure sensor 51 also can be set at the optional position in the refrigerant line 2.Perhaps, pressure sensor 51 also can be set at the position of comparing more close dirty side with the supercooling heat exchanger 23 of bypass 3.
(the 2nd embodiment)
Fig. 4 represents the freezing cycle device 1B of the 2nd embodiment of the present invention.In the present embodiment, the member mark identical symbol identical with the 1st embodiment, and omit its explanation.
Also same in the present embodiment with the 1st embodiment, control device 4 is control bypass expansion mechanism 31 when turning round usually, so that the bypass pipe one side outlet temperature T bo that detects in the 1st temperature sensor 61 becomes the saturation temperature STs under the pressure that is inhaled into the cold-producing medium in the compressor 21, and the degree of superheat SHe in evaporimeter 25 outlets of calculating according to the evaporator outlet temperature Teo that detects in the 2nd temperature sensor 62 is become below the degree of superheat of predefined regulation.But, in the present embodiment, control device 4 bases bypass pipe one side outlet temperature T bo that detects in the 1st temperature sensor 61 and the temperature that detects in the 3rd temperature sensor 63 are about equally, become saturation temperature STs under the pressure that is inhaled into the cold-producing medium in the compressor 21 thereby detect the bypass one side outlet temperature T bo that detects in the 1st temperature sensor 61, this point is different with the 1st embodiment.
Specifically, as shown in Figure 4, in the present embodiment, pressure sensor 51 (with reference to Fig. 1) is not set in refrigerant line 2, but in bypass 3, is provided with the 3rd temperature sensor 63 of temperature (the bypass pipe one side entrance temperature) Tbi that is used for detecting the cold-producing medium that flows into supercooling heat exchanger 23.
Below, the flow chart with reference to shown in Figure 5 explains the control of common running timed unit 4.
At first, same with the 1st embodiment, control device 4 detects discharge temperature Td (step S21) in discharge temperature sensor 65, adjusts the aperture of main expansion valve 24, so that this discharge temperature Td becomes desired value (step S22).
Then, control device 4 detects bypass one side outlet temperature T bo in the 1st temperature sensor 61, detects bypass one side entrance temperature T bi (step S23) simultaneously in the 3rd temperature sensor 63.Then, control device 4 judge bypass one side outlet temperature T bo whether with bypass one side entrance temperature T bi (step S24) about equally.Said herein " about equally " be meant, because the influence of the loss that in fact is under pressure, bypass one side outlet temperature T bo also not exclusively equates with bypass one side entrance temperature T bi, and therefore, it is to consider this point and the notion that proposes.For example, if the temperature difference of bypass one side outlet temperature T bo and bypass one side entrance temperature T bi below 3K, so, can think that also they about equally.
If bypass one side outlet temperature T bo and bypass pipe one side entrance temperature T bi be (being NO in step S24) about equally, so, in supercooling heat exchanger 23, can make more cold-producing medium evaporation, therefore, control device 4 returns step S21 with the aperture (step S25) of the amount raising bypass expansion valve 31 of regulation.
On the other hand, if bypass one side outlet temperature T bo and bypass one side entrance temperature T bi be (being YES in step S24) about equally, so, the performance of supercooling heat exchanger 23 just can be applied in the evaporation of cold-producing medium to greatest extent, therefore, control device 4 becomes the control of the aperture that is used for revising bypass expansion valve 31.
That is, control device 4 detects evaporator outlet temperature Teo (step S26) in the 2nd temperature sensor 62, calculates degree of superheat SHe (step S27) in evaporimeter 25 outlet according to following formula.
SHe＝Teo-Tbi
Then, control device 4 judges whether the degree of superheat SHe in evaporimeter 25 outlets of calculating is the degree of superheat following (step S28) of predefined regulation.If be NO in step S28, so, the some c among Fig. 2 too takes over, and promptly puts a and too takes back, and therefore, reduces the aperture (step S29) of bypass expansion valve 31 with the amount of regulation, returns step S21.On the other hand, if be YES in step S28, so, the aperture of bypass expansion valve 31 is suitable, and therefore, control device 4 intactly returns step S21.
Even carry out the control shown in the present embodiment, also can obtain the effect same with the 1st embodiment.
(variation)
In the present embodiment, used the 3rd temperature sensor 63 that is used for detecting bypass one side entrance temperature T bi, but the 3rd temperature sensor of the present invention also can be used for detecting temperature (evaporator inlet temperature) Tei of the cold-producing medium of inflow evaporator 25 in refrigerant pipe 2.The flow chart of this moment is the flow chart after the bypass one side entrance temperature T bi with flow chart shown in Figure 5 makes evaporator inlet temperature T ei into, and in step S27, the degree of superheat SHe that calculates in evaporimeter 25 outlets by following formula gets final product.
SHe＝Teo-Tei
(other embodiment)
In the described the 1st and the 2nd embodiment, control main expansion valve 24, so that discharge temperature Td becomes desired value, still, the method for control main expansion valve 24 is not limited thereto.For example, also can control main expansion valve 24, so that the pressure of the cold-producing medium of discharging from compressor 21 becomes desired value.Perhaps, also can control main expansion valve 24 according to the supercooling degree in the degree of superheat in compressor 21 outlets or condenser 22 outlets.
And main expansion mechanism of the present invention and bypass expansion mechanism may not be expansion valves, also can be the decompressors from the refrigerant-recovery power that expands.In the case, come change of load by the generator with the decompressor binding, the rotating speed of controlling decompressor like this gets final product.
Industrial applicibility
The present invention generates warm water for the use freezing cycle device, and the hot-water central heating device that this warm water is used for heating is particularly useful.
Claims (9)
1. a freezing cycle device is characterized in that, comprising:
Compressor, condenser, supercooling heat exchanger, main expansion mechanism and evaporimeter ring-type connect and the refrigerant line of formation;
Between described condenser and the described supercooling heat exchanger or between described supercooling heat exchanger and the described main expansion mechanism, from described refrigerant line branch, via described supercooling heat exchanger, the bypass that between described evaporimeter and described compressor, links to each other with described refrigerant line;
Comparing the bypass expansion mechanism that more close upper reaches one side is provided with the described supercooling heat exchanger of described bypass;
Detect in described bypass the 1st temperature sensor of the temperature of the cold-producing medium that flows out from described supercooling heat exchanger;
Detect in described refrigerant line the 2nd temperature sensor of the temperature of the cold-producing medium that flows out from described evaporimeter; With
Control device, control described bypass expansion mechanism, so that the temperature that detects in described the 1st temperature sensor is the saturation temperature that is inhaled under the pressure of the cold-producing medium in the described compressor, and to make the degree of superheat of calculating in the described evaporator outlet according to the temperature that detects in described the 2nd temperature sensor be below the degree of superheat of predefined regulation.
2. freezing cycle device as claimed in claim 1 is characterized in that:
Also comprise the pressure sensor that detects the pressure that is inhaled into the cold-producing medium in the described compressor,
The pressure that described control device basis detects in described pressure sensor is calculated the saturation temperature under the pressure that is inhaled into the cold-producing medium in the described compressor.
3. freezing cycle device as claimed in claim 1 is characterized in that:
Also comprise detecting the temperature that in described bypass, flows into the cold-producing medium of described supercooling heat exchanger, perhaps detect the 3rd temperature sensor of the temperature of the cold-producing medium that in described refrigerant line, flows into described evaporimeter,
Described control device detects the temperature that detects and becomes saturation temperature under the pressure that is inhaled into the cold-producing medium in the described compressor according to the temperature that detects in described the 1st temperature sensor and the temperature that detects in described the 3rd temperature sensor about equally in described the 1st temperature sensor.
4. freezing cycle device as claimed in claim 1 is characterized in that, the degree of superheat of described regulation be the aridity that is inhaled into the cold-producing medium in the described compressor be more than 0.8 1.0 less than the degree of superheat.
5. freezing cycle device as claimed in claim 4 is characterized in that the degree of superheat of described regulation is set according to outside air temperature, and to guarantee that outside air temperature is low more, the aridity that is inhaled into the cold-producing medium in the described compressor is more little.
6. freezing cycle device as claimed in claim 4, it is characterized in that, the degree of superheat of described regulation is recently set according to the compression of cold-producing medium, and high more with the compression ratio of the cold-producing medium that guarantees described compressor, the aridity that is inhaled into the cold-producing medium in the described compressor is more little.
7. freezing cycle device as claimed in claim 4 is characterized in that the degree of superheat of described regulation is set according to the rotating speed of compressor, and high more with the rotating speed that guarantees described compressor, the aridity that is inhaled into the cold-producing medium in the described compressor is more little.
8. freezing cycle device as claimed in claim 1 is characterized in that, yet described condenser is to make to carry out the heat exchanger that heat exchange adds hot water between cold-producing medium and the water.
9. a hot-water central heating device is characterized in that, it is the hot-water central heating device that the warm water that will be generated by heating arrangements is used to heat,
It is equipped with the described freezing cycle device of claim 8 as described heating arrangements.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009231659A JP5421717B2 (en) | 2009-10-05 | 2009-10-05 | Refrigeration cycle apparatus and hot water heater |
| JP2009-231659 | 2009-10-05 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102032698A true CN102032698A (en) | 2011-04-27 |
| CN102032698B CN102032698B (en) | 2014-12-17 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201010509342.8A Active CN102032698B (en) | 2009-10-05 | 2010-10-08 | Refrigeration cycle apparatus and hot water heater |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2320165B1 (en) |
| JP (1) | JP5421717B2 (en) |
| CN (1) | CN102032698B (en) |
| DK (1) | DK2320165T3 (en) |
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| CN102829568A (en) * | 2011-06-17 | 2012-12-19 | 松下电器产业株式会社 | Refrigeration cycle apparatus and hydronic heater having the refrigeration cycle apparatus |
| CN105715320A (en) * | 2014-12-22 | 2016-06-29 | 株式会社神户制钢所 | Thermal energy recovery device |
| CN105972717A (en) * | 2016-05-11 | 2016-09-28 | 珠海格力电器股份有限公司 | Variable refrigerant volume air conditioning system and control method thereof |
| CN104457072B (en) * | 2014-11-20 | 2017-02-22 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device and refrigerating/heating system |
| CN107036352A (en) * | 2017-05-05 | 2017-08-11 | 重庆美的通用制冷设备有限公司 | Economizer gas supply control method and apparatus |
| CN108135430A (en) * | 2015-07-31 | 2018-06-08 | 伊利诺斯工具制品有限公司 | Ware wash machine with heat recovery system |
| WO2023142498A1 (en) * | 2022-01-26 | 2023-08-03 | 广东美的制冷设备有限公司 | Air conditioner and controller thereof, control method, and computer readable storage medium |
| CN117136288A (en) * | 2021-03-31 | 2023-11-28 | 大金工业株式会社 | Refrigeration cycle device |
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| JP5824628B2 (en) * | 2011-06-29 | 2015-11-25 | パナソニックＩｐマネジメント株式会社 | Refrigeration cycle apparatus and hot water generating apparatus having the same |
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| CN104457072B (en) * | 2014-11-20 | 2017-02-22 | 珠海格力电器股份有限公司 | Electronic expansion valve control method and device and refrigerating/heating system |
| CN105715320A (en) * | 2014-12-22 | 2016-06-29 | 株式会社神户制钢所 | Thermal energy recovery device |
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| CN107036352A (en) * | 2017-05-05 | 2017-08-11 | 重庆美的通用制冷设备有限公司 | Economizer gas supply control method and apparatus |
| CN117136288A (en) * | 2021-03-31 | 2023-11-28 | 大金工业株式会社 | Refrigeration cycle device |
| WO2023142498A1 (en) * | 2022-01-26 | 2023-08-03 | 广东美的制冷设备有限公司 | Air conditioner and controller thereof, control method, and computer readable storage medium |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2320165A3 (en) | 2015-02-25 |
| JP2011080633A (en) | 2011-04-21 |
| DK2320165T3 (en) | 2018-07-23 |
| EP2320165B1 (en) | 2018-04-11 |
| CN102032698B (en) | 2014-12-17 |
| EP2320165A2 (en) | 2011-05-11 |
| JP5421717B2 (en) | 2014-02-19 |
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