CN103836847A - Refrigeration cycle apparatus and warm water producing apparatus having refrigeration cycle apparatus - Google Patents
Refrigeration cycle apparatus and warm water producing apparatus having refrigeration cycle apparatus Download PDFInfo
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- CN103836847A CN103836847A CN201310611273.5A CN201310611273A CN103836847A CN 103836847 A CN103836847 A CN 103836847A CN 201310611273 A CN201310611273 A CN 201310611273A CN 103836847 A CN103836847 A CN 103836847A
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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
- 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
- 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
- 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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
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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
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction 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
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
- F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
Abstract
The refrigeration cycle apparatus includes a refrigerant circuit 2, a refrigerant/refrigerant heat exchanger 23 and a control device 4. The refrigerant/refrigerant heat exchanger 23 includes an outer pipe 23a through which high pressure refrigerant flows, and an inner pipe 23b which is disposed in the outer pipe 23a and through which low pressure refrigerant flows. At least a portion of air flowing through the evaporator 25 is induced by the refrigerant/refrigerant heat exchanger 23. Therefore, the high pressure refrigerant is cooled by the air, a supercooling degree of refrigerant is increased, temperature of air flowing into the evaporator 25 is made to rise, and a heat exchanging amount in the evaporator 25 is increased. Therefore, it is possible to enhance energy efficiency.
Description
Technical field
The present invention relates to a kind of hot water generating device that carries out the overcooled refrigerating circulatory device of cold-producing medium and possess this cooling cycle system.
Background technology
In existing refrigerating circulatory device, in the downstream of condenser, supercooling heat exchanger is set, make this supercooling heat exchanger be make from condenser flow out cold-producing medium with expand cold-producing medium carry out heat exchange cold-producing medium to refrigerant heat exchanger, to from condenser flow out cold-producing medium carry out supercooling.This refrigerating circulatory device is applicable to refrigerating plant and conditioner etc. (for example, with reference to patent documentation 1).
In addition, as supercooling heat exchanger, have and flowing through the cold-producing medium of inner tube and flowing through the double-tube heat exchanger (for example, with reference to patent documentation 2) that carries out heat exchange between the cold-producing medium of outer tube.
Fig. 7 represents the summary construction diagram of the refrigerant loop of the existing conditioner of recording in patent documentation 1.Conditioner 100 comprises outdoor unit 200 and indoor unit 300.Refrigerant loop possesses the main refrigerant circuit 110 and the bypass circulation 120 that make refrigerant circulation.
For the effect of this refrigerating circulatory device, the skeleton diagram of the supercooling heat exchanger 114 shown in refrigerant loop figure and Fig. 8 that use Fig. 7 represents operates as example with heating and describes.
In warming operation, the stream of cross valve 112 is set as cold-producing medium and flows in the solid line direction of Fig. 7.The gas refrigerant of the HTHP of discharging from compressor 111 flow into the indoor heat converter 113 as condenser via cross valve 112.Flow through the cold-producing medium of indoor heat converter 113 and carry out heat exchange and condensation liquefaction with the ambient air of the indoor unit 300 attracting by indoor fan 118.The cold-producing medium of condensation liquefaction flow into outdoor unit 200, is divided into the main refrigerant that flows through main refrigerant circuit 110 and the bypass cold-producing medium that flows through bypass circulation 120 in the upstream of supercooling heat exchanger 114.
Fig. 8 is the summary construction diagram of the supercooling heat exchanger 114 recorded of patent documentation 2.
In the supercooling heat exchanger 114 shown in Fig. 8, flow and the main refrigerant that become the bypass cold-producing medium of low pressure and flow through main refrigerant circuit 110 by 121 decompressions of bypass expansion valve carries out heat exchange at bypass circulation 120.Main refrigerant by 114 supercooling of supercooling heat exchanger after, reduce pressure by main expansion valve 115.
Then, main refrigerant flows into the outdoor heat converter 116 as evaporimeter.Flow through the main refrigerant of outdoor heat converter 116, absorb heat and evaporation gasification, be inhaled into compressor 111 via cross valve 112 and the gas-liquid separator 119 that carries out gas-liquid separation from outdoor unit 200 ambient airs that attracted by outdoor fan 117.
On the other hand, after bypass cold-producing medium reduces pressure by bypass expansion valve 121, by main refrigerant being carried out to the cooling gasification of evaporating in supercooling heat exchanger 114.Afterwards, bypass cold-producing medium confluxes with main refrigerant between cross valve 112 and gas-liquid separator 119.
Its result, carries out supercooling by supercooling heat exchanger 114 to main refrigerant.Compared with not carrying out overcooled main refrigerant, the more main refrigerant of liquid component flows into evaporimeter (outdoor heat converter 116) evaporation, so the enthalpy difference in evaporimeter increases.Thus, realize the caloric receptivity that increases evaporimeter.
In addition, make the vapor phase refrigerant branch evaporation not being contributed as bypass cold-producing medium by evaporimeter 116, make evaporimeter 116 bypass, can reduce the pressure loss producing at the refrigerant loop 110 of gas-liquid separator 119 from evaporimeter 116 thus.Therefore, make the suction pressure of compressor 111 increase, that is, make refrigerant density increase, realize the raising as the refrigerating capacity of system.
Look-ahead technique document
Patent documentation
Patent documentation 1: No. 4036288 communique of Japanese Patent
Patent documentation 2: Unexamined Patent 10-54616 communique
Summary of the invention
The problem that invention will solve
But, in above-mentioned existing structure, there is following problem, only undertaken by the bypass cold-producing medium (low pressure refrigerant) of the inside of flowing through inner tube 114a in the supercooling of flowing through the main refrigerant of outer tube 114b as cold-producing medium in to the supercooling heat exchanger 114 of refrigerant heat exchanger, so can not fully guarantee the supercooling degree of main refrigerant.
The present invention is the invention that solves above-mentioned existing problem, its object is to provide a kind of refrigerating circulatory device, it fully guarantees the supercooling degree of cold-producing medium, and effectively utilizes the thermal energy of cold-producing medium to the high-pressure refrigerant in refrigerant heat exchanger, thereby improves energy efficiency.
For solving the method for problem
In order to solve above-mentioned problem, the invention provides a kind of refrigerating circulatory device, it is characterized in that, comprise: refrigerant loop, its utilize refrigerant piping by carrying out the radiator of heat exchange between the compressor of compressed refrigerant, above-mentioned cold-producing medium after being compressed by above-mentioned compressor and thermal medium, the expansion gear that above-mentioned cold-producing medium is reduced pressure and the evaporimeter that carries out heat exchange between above-mentioned cold-producing medium and air be in turn connected into ring-type; Cold-producing medium is to refrigerant heat exchanger, and it is disposed in the above-mentioned refrigerant loop between above-mentioned radiator and above-mentioned expansion gear, utilizes at the mobile low pressure refrigerant of above-mentioned refrigerant loop cooling the high-pressure refrigerant flowing out from above-mentioned radiator; And control device, above-mentioned cold-producing medium comprises refrigerant heat exchanger: outer tube, and above-mentioned high-pressure refrigerant flows in this outer tube; And inner tube, it is disposed in the inside of above-mentioned outer tube, and above-mentioned low pressure refrigerant flows in this inner tube, and at least a portion that flows through the air of above-mentioned evaporimeter is directed to above-mentioned cold-producing medium to refrigerant heat exchanger.
Thus, in adding in heat run of thermal medium (heating agent), the high-pressure refrigerant of crossing the outer tube of cold-producing medium to refrigerant heat exchanger by the cross-ventilation being guided by evaporimeter carries out cooling, and the supercooling degree of cold-producing medium increases.In addition, due to the air to evaporimeter guiding from high-pressure refrigerant heat absorption, so flow through the cold-producing medium of evaporimeter and the increase of the temperature difference of air.
Invention effect
According to the present invention, a kind of refrigerating circulatory device can be provided, it can increase the increase that realizes enthalpy difference by the supercooling degree of cold-producing medium, and realizes the compression ratio decline of compressor by the rising of evaporating pressure, so improved energy efficiency.
Accompanying drawing explanation
Fig. 1 is the summary construction diagram of the refrigerating circulatory device of embodiments of the present invention 1.
Fig. 2 (a) be the cold-producing medium of this refrigerating circulatory device to the summary construction diagram of refrigerant heat exchanger, be (b) that the cold-producing medium of this refrigerating circulatory device is to the sectional view of refrigerant heat exchanger.
Fig. 3 is the P-h line chart (Mollier line chart) that the variation of the kind of refrigeration cycle to this refrigerating circulatory device describes.
Fig. 4 is the flow chart of the flow-control of the bypass cold-producing medium of this refrigerating circulatory device.
Fig. 5 is the flow chart of the flow-control of the main refrigerant of this refrigerating circulatory device.
Fig. 6 is the summary construction diagram of the refrigerating circulatory device of embodiments of the present invention 2.
Fig. 7 is the summary construction diagram of existing conditioner.
Fig. 8 is the summary construction diagram of existing cold-producing medium to refrigerant heat exchanger.
Reference numeral explanation
1 refrigerating circulatory device
2 refrigerant loops
3 bypass circulations
4 control device
21 compressors
22 condensers (radiator)
23 cold-producing mediums are to refrigerant heat exchanger
23a outer tube
23b inner tube
24 main expansion valves (expansion gear)
25 evaporimeters
30 heat transfer promotion divisions
31 bypass expansion valves (bypass expansion gear)
40 air suction inlets
51 suction pressure sensors (the first degree of superheat test section, the second degree of superheat test section)
61 evaporator outlet temperature sensors (the second degree of superheat test section)
62 bypass circulation outlet temperature sensors (the first degree of superheat test section)
The specific embodiment
The first invention provides a kind of refrigerating circulatory device, it is characterized in that, comprise: refrigerant loop, its utilize refrigerant piping by carrying out the radiator of heat exchange between the compressor of compressed refrigerant, above-mentioned cold-producing medium after being compressed by above-mentioned compressor and thermal medium, the expansion gear that above-mentioned cold-producing medium is reduced pressure and the evaporimeter that carries out heat exchange between above-mentioned cold-producing medium and air be in turn connected into ring-type; Cold-producing medium is to refrigerant heat exchanger, and it is disposed in the above-mentioned refrigerant loop between above-mentioned radiator and above-mentioned expansion gear, utilizes at the mobile low pressure refrigerant of above-mentioned refrigerant loop cooling the high-pressure refrigerant flowing out from above-mentioned radiator; And control device, above-mentioned cold-producing medium comprises refrigerant heat exchanger: outer tube, and above-mentioned high-pressure refrigerant flows in this outer tube; And inner tube, it is disposed in the inside of above-mentioned outer tube, and above-mentioned low pressure refrigerant flows in this inner tube, and at least a portion that flows through the air of above-mentioned evaporimeter is directed to above-mentioned cold-producing medium to refrigerant heat exchanger.
Thus, in adding in heat run of thermal medium, be directed to the air (low temperature extraneous air) of evaporimeter by the outer surface of the outer tube of the double-tube heat exchanger to refrigerant heat exchanger as cold-producing medium.Therefore, cooling to carrying out at the mobile high-temperature high-pressure refrigerant of outer tube, the supercooling degree of cold-producing medium is increased.
On the other hand, air absorbs heat from high-temperature high-pressure refrigerant to the outer tube of refrigerant heat exchanger via cold-producing medium, so temperature rise and being guided by evaporimeter.Therefore, increase at the low-temperature refrigerant of evaporimeter internal flow and the temperature difference of air, the heat exchange amount of evaporimeter increases.
Its result, can increase by cold-producing medium the increase that realizes enthalpy difference, and increase by the heat exchange amount of evaporimeter the increase that realizes evaporating pressure to the supercooling degree of the cold-producing medium in refrigerant heat exchanger.Therefore, reduce by the compression ratio of compressor, thereby compressor power reduces, and can realize energy-saving.
The second invention particularly on the basis of the first invention, is characterized in that, has and makes the heat transfer promotion division that increases with the contact area of above-mentioned air at the outer surface of above-mentioned outer tube.
Thus, this double hose cold-producing medium to refrigerant heat exchanger in, the surface area of the outer tube by the cold-producing medium at internal flow HTHP increases, the thermal discharge from outer tube to air increases.
Its result, carries out overcooled degree increase to refrigerant heat exchanger to cold-producing medium by cold-producing medium, and the liquid component that flow into the cold-producing medium of evaporimeter increases, and can further increase the refrigeration of evaporimeter.
The 3rd invention is particularly on the basis of the first or second invention, it is characterized in that, comprise: bypass circulation, it is from the above-mentioned refrigerant loop branch between above-mentioned radiator and above-mentioned expansion gear, comprise that bypass expansion gear and above-mentioned cold-producing medium are to refrigerant heat exchanger, and be connected with the above-mentioned refrigerant loop between discharge chambe or above-mentioned evaporimeter and the above-mentioned compressor of above-mentioned compressor, above-mentioned cold-producing medium is to refrigerant heat exchanger, utilize from above-mentioned bypass expansion gear and flow out and carry out cooling at the mobile above-mentioned low pressure refrigerant of above-mentioned inner tube to the above-mentioned high-pressure refrigerant flowing out from above-mentioned radiator and flow at above-mentioned outer tube.
Thus, utilize by the post-decompression low pressure refrigerant of bypass expansion gear, cooling to carrying out from the high-pressure refrigerant of radiator outflow, can increase the supercooling degree of cold-producing medium and reduce condensing pressure.And then the vapor phase refrigerant that the pressure loss is large flows into bypass circulation, the refrigerant pressure loss in evaporimeter reduces, so can realize energy-saving.
The 4th invention is particularly on the basis of the 3rd invention, it is characterized in that, have the first degree of superheat test section that the refrigerant superheat degree of the outlet side to above-mentioned bypass circulation detects, the above-mentioned bypass expansion gear of above-mentioned control device control becomes setting with the detected value that makes above-mentioned the first degree of superheat test section.
Thus, the refrigerant superheat degree SH that the excessive and not enough degree of the flow of the bypass cold-producing medium from refrigerant loop to bypass circulation branch can export by bypass circulation judges.That is, the in the situation that of bypass flow deficiency, the ability that cold-producing medium is possessed refrigerant heat exchanger is relatively large, so the refrigerant superheat degree SH of bypass circulation outlet is excessive.On the other hand, in the situation that bypass flow is too much, the ability that cold-producing medium is possessed refrigerant heat exchanger is relatively little, so can not guarantee refrigerant superheat degree SH.
Therefore, utilize control device control bypass expansion gear to become 0～1K degree with the refrigerant superheat degree of the outlet side that makes bypass circulation, thus can not can make cold-producing medium to refrigerant heat exchanger ability occur excessive with draw to greatest extent insufficiently.
The 5th aspect is on the basis of the 3rd or the 4th invention, it is characterized in that, have the second degree of superheat test section that the refrigerant superheat degree of the outlet side to above-mentioned evaporimeter detects, the above-mentioned expansion gear of above-mentioned control device control becomes setting with the detected value that makes above-mentioned the second degree of superheat test section.
Excessive and the not enough degree of the refrigerant flow flowing through at refrigerant loop thus, can be judged by the outlet degree of superheat SHe of evaporimeter.That is, in the case of the ability of possessing with respect to evaporimeter, refrigerant flow deficiency, the ability of possessing of evaporimeter is relatively large, so evaporimeter can be to cold-producing medium excessive vaporization, so the degree of superheat of evaporator outlet increases.
On the other hand, in the situation that refrigerant flow is too much, the ability of possessing of radiator is relatively little, thus can not be with the abundant vaporized refrigerant of evaporimeter, and flow out from evaporimeter under the state of wet cold-producing medium, so can not fully guarantee the degree of superheat.
Therefore, the aperture of utilizing control device control expansion gear, to make the outlet degree of superheat of evaporimeter become the scope of 0K～setting, can be brought into play the ability of evaporimeter thus to greatest extent.
The 6th invention is on the basis of the first or second invention, it is characterized in that, above-mentioned cold-producing medium, to refrigerant heat exchanger, utilizes from above-mentioned evaporimeter and flows out and carry out cooling at the mobile above-mentioned low pressure refrigerant of above-mentioned inner tube to the above-mentioned high-pressure refrigerant flowing out from above-mentioned radiator and flow at above-mentioned outer tube.
The liquid refrigerant of the HTHP flowing out from condenser thus, and the low-temp low-pressure gas-liquid two-phase cold-producing medium flowing out from evaporimeter carry out heat exchange.And liquid refrigerant is by supercooling, the supercooling degree of cold-producing medium increases, and on the other hand, gas-liquid two-phase cold-producing medium is heated, and the degree of superheat of cold-producing medium increases.
Consequently, by the simple structure without bypass circulation, with cold-producing medium, refrigerant heat exchanger is carried out coolingly to cold-producing medium, can reduce condensing pressure, so can reduce the compression ratio of compressor, alleviate compressor power, can realize at low cost energy-saving.
In the hot water generating device that possesses refrigerating circulatory device that the 7th invention is particularly invented in the first～six any one, it is characterized in that, above-mentioned thermal medium is water or anti-icing fluid, and the above-mentioned thermal medium by after above-mentioned radiators heat is used for to supplying hot water or heating.
Thus, radiator is not only applicable to the situation of cold-producing medium to air heat exchanger, can be applicable to cold-producing medium yet and use heat exchanger and cold-producing medium to anti-icing fluid heat exchanger to water, does not limit.
Its result, can extensively be used in the heating equipments such as convection type, radiant type, hot conduction-type and supplying hot water equipment etc. by the thermal medium by after radiators heat (air, water, anti-icing fluid etc.).
Below, with reference to accompanying drawing, embodiments of the present invention are described.But, and can't help present embodiment limit the present invention.
(embodiment 1)
Fig. 1 represents the refrigerating circulatory device 1 of embodiment of the present invention 1.This refrigerating circulatory device 1 be configured to possess make refrigerant circulation refrigerant loop 2, make by high-temperature high-pressure refrigerant heat generate the thermal medium stream 43 of hot water circuit and the hot water generating device of control device 4.As cold-producing medium, can use the unitary system such as the near azeotropic mixed refrigerant such as mixed non-azeotropic refrigerant, R410A or R32 and the R290 cryogens such as such as R407C etc.
In the present embodiment, refrigerating circulatory device 1 possesses: refrigerant loop 2, the bypass circulation 3 of bypass flow of refrigerant and the housing 44 of formation outline that main refrigerant is mobile, refrigerant loop 2 utilizes refrigerant piping that compressor 21, condenser (radiator) 22, cold-producing medium are in turn connected into ring-type formation to refrigerant heat exchanger 23, main expansion valve (main expansion gear) 24 and evaporimeter 25.
In addition, in order to switch cool/heat running, be provided with the cross valve 28 of the flow direction that switches cold-producing medium at refrigerant loop 2.And then, also be provided with suction pressure sensor 51(the first degree of superheat test section, the second degree of superheat test section of suction side refrigerant pressure Ps that detects compressor 21 at refrigerant loop 2), detect temperature sensor 61(the second degree of superheat test section of the outlet side refrigerant temperature Teo of evaporimeter 25), in order to detect the refrigerant superheat degree SHby of outlet side of bypass circulation 3, be provided with bypass circulation outlet temperature sensor 62(first degree of superheat test section of the refrigerant temperature of the outlet side that detects bypass circulation 3 at bypass circulation 3).
On the other hand, bypass circulation 3 between cold-producing medium is to refrigerant heat exchanger 23 and evaporimeter 25 from refrigerant loop 2 branches, via bypass expansion valve (bypass expansion gear) 31, cold-producing medium to refrigerant heat exchanger 23 at cross valve 28 be arranged between the gas-liquid separator 27 of suction side of compressor 21 and be connected with refrigerant loop 2.
The detected value control main expansion valve 24 that control device 4 detects based on various sensors 51,61,62 and the aperture of bypass expansion valve 31.
In addition, be connected with supply pipe 41 and recovery tube 42 at thermal medium stream 43.The water that is supplied to thermal medium pipe 43a by supply pipe 41 carries out heat exchange with the cold-producing medium that flows through refrigerant pipe 2a, is heated as hot water, is recovered by recovery tube 42.
Skeleton diagram and the sectional view of the cold-producing medium that Fig. 2 represents present embodiment to refrigerant heat exchanger 23.Cold-producing medium is double-tube heat exchanger to refrigerant heat exchanger 23, possesses outer tube 23a and inner tube 23b.The cross section of outer tube 23a and inner tube 23b is formed as cylindric.The low-temp low-pressure gas-liquid two-phase cold-producing medium that flows out bypass expansion valve 31 is the inside that bypass cold-producing medium flow into inner tube 23b.The high-temperature high-pressure liquid cryogen flowing out from condenser 22 is that main refrigerant flows into the annulus between outer tube 23a and inner tube 23b.Main refrigerant and bypass cold-producing medium flow toward each other, carry out heat exchange., cold-producing medium plays a role for the mode that the high-pressure refrigerant to flow out from condenser 22 and high-pressure refrigerant carry out heat exchange by the low pressure refrigerant of expansion valve (bypass expansion valve 31) decompression generation to refrigerant heat exchanger 23.
In addition, the outer surface of the outer tube 23a at cold-producing medium to refrigerant heat exchanger 23, with respect to tubular axis concentric circles be provided with circular heat-exchange fin as for realizing the heat transfer promotion division 30 promoting with the heat exchange of air.At this, heat transfer promotion division 30, as long as the structure for the surface area of outer tube 23a is increased is just not particularly limited, also can be used the recess (Dimple) of the part depression formation that for example makes outer tube 23a etc.
Below, the action to refrigerating circulatory device configured as described above, effect describe.Fig. 3 is the P-h line chart (Mollier line chart) that represents the refrigerant pressure P of refrigerant loop and the relation of cold-producing medium enthalpy h.
In the heat run that adds of the thermal medium for supplying hot water or heating, be inhaled into the saturation state of compressor 21 or the cold-producing medium of superheat state is compressed into high temperature and high pressure gas by compressor 21, this gas refrigerant is fed to condenser 22 via cross valve 28, in condenser 22, high temperature refrigerant and water (thermal medium) carry out heat exchange, thereby generating hot water, is used to supplying hot water or heating.The flow direction of the cold-producing medium while representing to add heat run with arrow in Fig. 1 and hot water (thermal medium).
The hot water reclaiming by recovery tube 42 is admitted to the heat exchange units (not shown) such as such as radiator (Radiator) or storage hot water tank (not shown), thus, is used to supplying hot water or heating.
Adding in heat run, the gas refrigerant of the HTHP of discharging from compressor 21 flow into condenser 22, the water that is supplied to condenser 22 by supply pipe 41 is heated, and it dispels the heat and liquefaction condensation in water, becomes saturated liquid state or supercooling state.The liquid refrigerant (main refrigerant) of the HTHP flowing out from condenser 22, flow into the inside (annulus) of the outer tube 23a of cold-producing medium to refrigerant heat exchanger 23, is flow through the bypass refrigerant cools of inner tube 23b.
And then, because cold-producing medium is disposed in from air suction inlet 40 and flows to the air flow circuit that the extraneous air of the low temperature of evaporimeter 25 passes through the outer tube 23a of refrigerant heat exchanger 23, so via the heat transfer promotion division (heat-exchange fin) 30 of outer surface side that is located at the outer tube 23a of cold-producing medium to refrigerant heat exchanger 23, extraneous air carries out heat exchange with the cold-producing medium of the inside (annulus) of flowing through outer tube 23a, and the cold-producing medium that flows through the inside (annulus) of outer tube 23a is further cooled.
Its result, the cold-producing medium enthalpy by cold-producing medium after to refrigerant heat exchanger 23 as shown in Figure 3, compared with prior art, is down to C point (enthalpy hsc2) from c point (enthalpy hsc1).
On the other hand, the outer tube 23a heating to refrigerant heat exchanger 23 and the temperature rise guided by evaporimeter 25 by cold-producing medium of the air of the outer surface side by outer tube 23a, so increase with the temperature difference of the low-temperature refrigerant of the internal flow at evaporimeter 25.Its result, the evaporating pressure Pe of the refrigerant side of evaporimeter 25 rises compared to existing technology.
Then, main refrigerant by cold-producing medium to refrigerant heat exchanger 23 after, at cold-producing medium, the outlet side of refrigerant heat exchanger 23 is branched into refrigerant loop 2 and bypass circulation 3.
The high-pressure refrigerant that flows through main expansion valve 24 is reduced pressure by main expansion valve 24 and expands.Afterwards, flow into evaporimeter 25, flow into the cold-producing medium enthalpy of evaporimeter 25 compared with prior art, the d point (enthalpy hsc1) from Fig. 3 is reduced to D point (enthalpy hsc2), and the cold-producing medium aridity that flow into evaporimeter 25 diminishes., in evaporimeter 25, carry out phase transformation from liquid phase to gas phase and the ratio that produces the liquid refrigerant of evaporation latent heat will increase.
At this, flow into evaporimeter 25(fin-tube heat exchanger) the gas-liquid two-phase cold-producing medium of low pressure conventionally branch into many refrigerant flow paths (refrigerant path) by current divider.
While being branched into many refrigerant flow paths (refrigerant path), the cold-producing medium aridity of inflow is higher, and the gas phase composition of cold-producing medium is more, larger to the inequality of the bypass flow of each refrigerant path, and partition characteristic worsens.On the other hand, the cold-producing medium aridity of inflow is lower, and the liquid phase ingredient of cold-producing medium is more, and less to the inequality of the bypass flow of each refrigerant path, partition characteristic is good.
Therefore, in the present embodiment, the cold-producing medium aridity that flow into evaporimeter 25 compared with prior art reduces, so in many refrigerant path, can suppress the phenomenon too much as the refrigerant flow in part of refrigerant path, the shunting performance of evaporimeter 25 improves, and the pressure loss of the cold-producing medium of whole evaporimeter 25 reduces.Cold-producing medium, from being heated and evaporating from air (extraneous air of low temperature) heat absorption in this evaporimeter 25, becomes saturated gas or overheated gas state.
On the other hand, the high-pressure refrigerant of crossing at bypass circulation 3 affluent-dividings is become the cold-producing medium of low-temp low-pressure by 31 decompressions of bypass expansion valve, to at cold-producing medium, the saturated liquid state of the internal flow of the outer tube 23a to refrigerant heat exchanger 23 or the cold-producing medium of cooled liquid state carry out coolingly, low pressure refrigerant self is heated and become saturated gas state or overheated gas state.
The low pressure refrigerant that flows out bypass circulation 3 confluxes at evaporimeter 25 with the low pressure refrigerant that air carries out heat exchange, and is drawn into compressor 21 via gas-liquid separator 27.
At this, as mentioned above, the air that flow into evaporimeter 25 rises from the high-pressure refrigerant endothermic temperature that flows through outer tube 23a, and thus, the evaporating pressure in evaporimeter 25 rises.In addition, as mentioned above, the refrigerant pressure loss in evaporimeter 25 declines, so make condensing pressure necessarily not compared with prior art, as shown in Figure 3, the cold-producing medium suction pressure that is drawn into compressor 21 can rise to Ps2 from Ps1.
The suction pressure of compressor 21 is higher, and refrigerant density rises faster.In the case of the operating frequency of compressor 21 is identical, main refrigerant mass flow mobile in kind of refrigeration cycle increases to Gr2 from Gr1, so can increase the heating efficiency of condenser 22.
Then, below with reference to the flow chart shown in Fig. 4, the bypass flow control of bypass expansion valve 31 is at length described.
First, at step S11, the refrigerant temperature Tbyo of the outlet side of the suction pressure Ps to compressor 21 and bypass circulation 3 detects.
Then, calculate the cold-producing medium saturation temperature Tsat take above-mentioned suction pressure Ps as benchmark at step S12, and by with the difference of the outlet side refrigerant temperature Tbyo of bypass circulation 3, calculate the outlet side refrigerant superheat degree SHby of bypass circulation 3., form the first degree of superheat test section by suction pressure sensor 51 and bypass circulation outlet temperature sensor 62.
And, at step S13, the relatively magnitude relationship of the outlet side refrigerant superheat degree SHby of bypass circulation 3 and the higher limit SHo of the target degree of superheat.If SHby >=SHo,, in step S14, carries out the aperture PLS1 of bypass expansion valve 31 to open after the action of the first regulation aperture dP1, proceed to step S17.The higher limit SHo of the target degree of superheat is now less, more preferred at aspect of performance, if but consider control stability, be preferably set to 1～3K degree.
On the other hand, if SHby<SHo, in step S15, the relatively outlet side refrigerant superheat degree SHby of bypass circulation 3 and the lower limit 0(zero of the target degree of superheat) magnitude relationship.If SHby≤0(SHby ≈ 0),, in step S16, carry out the aperture PLS1 of bypass expansion valve 31 to close after the action of the first regulation aperture dP1, proceed to step S17.
If SHby > 0, the lower limit 0(zero of the outlet side refrigerant superheat degree SHby of bypass circulation 3 in the target degree of superheat) and higher limit SHo between, judge and be controlled in OK range, no matter carry out which kind of action, all proceed to step S17, guarantee, after the control interval of (standby) regulation, to return to step S11, the action of repeating step S11～step S17.
Then, at length describe below with reference to the refrigerant flow control of pair main expansion valve relevant with the present invention 24 of the flow chart shown in Fig. 5.
First, at step S21, the refrigerant temperature Teo of the outlet side of the suction pressure Ps to compressor 21 and evaporimeter 25 detects.
Then, calculate cold-producing medium saturation temperature Tsat at step S22 based on suction pressure Ps, by calculating the outlet side refrigerant superheat degree SHe of evaporimeter 25 with the difference of the outlet side refrigerant temperature Teo of evaporimeter 25., form the second degree of superheat test section by suction pressure sensor 51 and evaporator outlet temperature sensor 61.
And, at step S23, the relatively magnitude relationship of the outlet side refrigerant superheat degree SHe of evaporimeter 25 and the higher limit SHoe of the target degree of superheat.If SHe >=SHoe, carries out the aperture PLS2 of main expansion valve 24 to open after the action of the second regulation aperture dP2 at step S24, proceed to step S27.The higher limit SHoe of the target degree of superheat is now less, more preferred at aspect of performance, if but consider control stability, be preferably set to 1～3K degree.
On the other hand, if SHe<SHoe, at the relatively outlet side refrigerant superheat degree SHe of evaporimeter 25 and the lower limit 0(zero of the target degree of superheat of step S25) magnitude relationship.If SHe≤0(SHby ≈ 0), carry out the aperture PLS2 of main expansion valve 24 to close after the action of the second regulation aperture dP2 at step S26, proceed to step S27.
If SHe > 0, the lower limit 0(zero of the outlet side refrigerant superheat degree SHe of evaporimeter 25 in the target degree of superheat) and higher limit SHoe between, judge and can be controlled in OK range, no matter carry out which kind of action, all proceed to step S27, guarantee, after (standby) regulation control interval, to return to step S21, the action of repeating step S21～step S27.
As mentioned above, the refrigerating circulatory device of present embodiment possesses: refrigerant loop 2, and it comprises that cold-producing medium is to refrigerant heat exchanger 23; Bypass circulation 3, its thermal medium add heat run time from cold-producing medium the downstream branch of the outer tube 23a to refrigerant heat exchanger 23, and via bypass expansion valve 31 and cold-producing medium, the inner tube 23b of refrigerant heat exchanger 23 is confluxed with refrigerant loop 2 between evaporimeter 25 and gas-liquid separator 27.Making cold-producing medium is double-tube heat exchanger to refrigerant heat exchanger 23, and evaporimeter 25 is that cold-producing medium is to air heat exchanger.And, and the air flow circuit that carries out between air suction inlet 40 and the evaporimeter 25 of heat exchange of evaporimeter 25 cold-producing medium is set to refrigerant heat exchanger 23.
Thus, particularly adding in heat run of thermal medium in the winter time, be guided to the air (low temperature extraneous air) of evaporimeter 25 by the outer surface of the outer tube 23a of double-tube heat exchanger, thus, via outer tube 23a, the high-temperature high-pressure refrigerant of the internal flow at outer tube 23a is carried out coolingly, increase the supercooling degree of cold-producing medium.
In addition, air is the outer tube 23a heat absorption to refrigerant heat exchanger 23 via cold-producing medium, and temperature rise is also guided by evaporimeter 25, so increase with the temperature difference of the low-temperature refrigerant in evaporimeter internal flow, the heat exchange amount of evaporimeter 25 increases.
In addition, by detect compressor 21 suction side refrigerant pressure Ps suction pressure sensor 51, detect evaporimeter 25 outlet side refrigerant temperature Teo evaporator outlet temperature sensor 61 and detect the bypass circulation outlet temperature sensor 62 of refrigerant temperature of the outlet side of bypass circulation 3, calculate the refrigerant superheat degree SHby of outlet side of bypass circulation 3 and the refrigerant superheat degree SHe of the outlet side of evaporimeter 25.And, by control device 4, become mode control bypass expansion valve 31 and the main expansion valve 24 of setting with each value.
Thus, excessive and the not enough degree of the bypass flow from refrigerant loop 2 to bypass circulation 3 branches can be judged by the size of the refrigerant superheat degree SHby of the outlet of bypass circulation 3, the excessive and not enough degree of the main refrigerant flow that flows through refrigerant loop 2 can also be judged by the outlet degree of superheat SHe of evaporimeter 25.
Its result, control bypass flow and main refrigerant flow, to make the refrigerant superheat degree SHby of outlet side of bypass circulation 3 and the refrigerant superheat degree SHe of the outlet side of evaporimeter 25 respectively in prescribed limit, there will not be excessive and farthest bring into play insufficiently the ability of cold-producing medium to refrigerant heat exchanger 23, and can maximally utilise the ability of evaporimeter 25.Therefore, the reduction of the compression ratio of compressor 21 can be realized, so the power of compressor 21 reduces, energy-saving can be realized.
In addition, bypass circulation 3 may not be from refrigerant loop 2 branches between cold-producing medium is to refrigerant heat exchanger 23 and main expansion valve 24, also can be from refrigerant loop 2 branches between condenser 22 and cold-producing medium are to refrigerant heat exchanger 23.
And then main expansion valve 24 of the present invention and bypass expansion valve 31 need not be expansion valve, it can be also the decompressor of the refrigerant-recovery power from expanding.In this case, for example, by making load variations with the generator of decompressor link, control the rotating speed of decompressor.
In addition, the heated fluid being heated by condenser 22 need not be water, can be also air., the present invention also can be applicable to aircondition.
(embodiment 2)
Fig. 6 represents the refrigerating circulatory device 1 of embodiment of the present invention 2.In the present embodiment, the functional part identical with embodiment 1 marked to identical symbol, its detailed explanation is omitted.In the present embodiment, cold-producing medium is located at the inner tube 23b of refrigerant heat exchanger 23 between the outlet side and compressor 21 of evaporimeter 25 of refrigerant loop 2.
The gas-liquid heat exchanger that, the refrigerant loop 2 of present embodiment carries out heat exchange to refrigerant heat exchanger 23 as the high-pressure side cold-producing medium at refrigerant loop 2 and low-pressure side cold-producing medium using cold-producing medium plays a role.In addition, be provided with the inlet temperature sensor 63 of the suction pressure sensor 51 of the suction side refrigerant pressure Ps that detects compressor 21 and the suction side refrigerant temperature Ts of detection compressor 21 at refrigerant loop 2.The detected value control main expansion valve 24 of control device 4 based on suction pressure sensor 51 and inlet temperature sensor 63 etc.
To action, the effect of refrigerating circulatory device describe as constructed as above.
In adding in heat run of thermal medium, the condensation condenser 22 of the gas refrigerant of the HTHP of discharging from compressor 21, the liquid refrigerant of the HTHP flowing out from condenser 22 flows into the inside (annulus) of the outer tube 23a of cold-producing medium to refrigerant heat exchanger, is undertaken cooling by the low-temperature low-pressure refrigerant that flows through inner tube 23b flowing out from evaporimeter 25.The mode that the low pressure refrigerant that, cold-producing medium generates via expansion valve (main expansion valve 24) decompression for the high-pressure refrigerant to flow out from condenser 22 and high-pressure refrigerant refrigerant heat exchanger 23 carries out heat exchange plays a role.
In addition, via the heat transfer promotion division (heat-exchange fin) 30 of outer surface that is located at the outer tube 23a of cold-producing medium to refrigerant heat exchanger, extraneous air and the cold-producing medium that flows through outer tube 23a carry out heat exchange, and the cold-producing medium that flows through outer tube 23a is further cooled.
In addition, the air of the outer surface side of the outer tube 23a by cold-producing medium to refrigerant heat exchanger is via the cold-producing medium heating of flowing through outer tube 23a, and temperature rise is also guided by evaporimeter 25.Therefore, increase with the temperature difference of the low-temperature refrigerant of the internal flow at evaporimeter 25.Heat exchange amount in evaporimeter 25 is identical, the evaporating pressure Pe of the refrigerant side of evaporimeter 25 compared with prior art rises.
In addition, compared with prior art can reduce the cold-producing medium aridity that flow into evaporimeter 25, so the shunting performance of evaporimeter 25 improves., the assignment of traffic inequality of multiple refrigerant path reduces, and can reduce the refrigerant pressure loss of evaporimeter 25.
As above, the refrigerating circulatory device 1 of present embodiment by by the air that flow into evaporimeter 25 by flowing through the high-pressure refrigerant of inside of outer tube 23a the heat up rising of the evaporating pressure of realizing the temperature rise of following air and the cold-producing medium shunting resulting improvement at evaporimeter 25, obtain the effect of the pressure loss that reduces cold-producing medium.Therefore, make condensing pressure necessarily compare, can improve the suction pressure of compressor 21.In the case of the operating frequency of compressor 21 is identical, in kind of refrigeration cycle, the mass flow of mobile main refrigerant increases, and can increase the heating efficiency of condenser 22.
Its result, by not having the simple structure of bypass circulation, the compression ratio that can realize compressor reduces, so the power of compressor reduces, can realize energy-saving.
In industry, utilize possibility
The present invention to by refrigerating circulatory device to as utilizing the thermal mediums such as the water of side thermal medium to heat, and it is particularly useful that this thermal medium is used in to the hot water generating device of supplying hot water and heating.
Claims (7)
1. a refrigerating circulatory device, is characterized in that, comprising:
Refrigerant loop, it utilizes refrigerant piping to carry out the radiator of heat exchange, the expansion gear that described cold-producing medium is reduced pressure by the compressor of compressed refrigerant, between the described cold-producing medium by after described compressor compresses and thermal medium and the evaporimeter that carries out heat exchange between described cold-producing medium and air is in turn connected into ring-type;
Cold-producing medium is to refrigerant heat exchanger, and it is disposed in the described refrigerant loop between described radiator and described expansion gear, utilizes at the mobile low pressure refrigerant of described refrigerant loop cooling the high-pressure refrigerant flowing out from described radiator; With
Control device,
Described cold-producing medium comprises refrigerant heat exchanger:
Outer tube, described high-pressure refrigerant flows in this outer tube; With
Inner tube, it is disposed in the inside of described outer tube, and described low pressure refrigerant flows in this inner tube,
And at least a portion that flows through the air of described evaporimeter is directed to described cold-producing medium to refrigerant heat exchanger.
2. refrigerating circulatory device as claimed in claim 1, is characterized in that:
Have and make the heat transfer promotion division that increases with the contact area of described air at the outer surface of described outer tube.
3. refrigerating circulatory device as claimed in claim 1 or 2, is characterized in that, comprising:
Bypass circulation, it is from the described refrigerant loop branch between described radiator and described expansion gear, comprise that bypass expansion gear and described cold-producing medium are to refrigerant heat exchanger, and be connected with the described refrigerant loop between discharge chambe or described evaporimeter and the described compressor of described compressor
Described cold-producing medium, to refrigerant heat exchanger, utilizes from described bypass expansion gear and flows out and carry out cooling at the mobile described low pressure refrigerant of described inner tube to the described high-pressure refrigerant flowing out from described radiator and flow at described outer tube.
4. refrigerating circulatory device as claimed in claim 3, is characterized in that:
There is the first degree of superheat test section that the refrigerant superheat degree of the outlet side to described bypass circulation detects,
Described in described control device control, bypass expansion gear becomes setting with the detected value that makes described the first degree of superheat test section.
5. the refrigerating circulatory device as described in claim 3 or 4, is characterized in that:
There is the second degree of superheat test section that the refrigerant superheat degree of the outlet side to described evaporimeter detects,
Described in described control device control, expansion gear becomes setting with the detected value that makes described the second degree of superheat test section.
6. refrigerating circulatory device as claimed in claim 1 or 2, is characterized in that:
Described cold-producing medium, to refrigerant heat exchanger, utilizes from described evaporimeter and flows out and carry out cooling at the mobile described low pressure refrigerant of described inner tube to the described high-pressure refrigerant flowing out from described radiator and flow at described outer tube.
7. a hot water generating device, is characterized in that:
Have the refrigerating circulatory device described in any one in claim 1～6, wherein said thermal medium is water or anti-icing fluid, and the described thermal medium by after described radiators heat is used for to supplying hot water or heating.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
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| JP2012-257049 | 2012-11-26 | ||
| JP2012257049A JP2014105890A (en) | 2012-11-26 | 2012-11-26 | Refrigeration cycle device and hot-water generating device including the same |
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| CN103836847A true CN103836847A (en) | 2014-06-04 |
| CN103836847B CN103836847B (en) | 2017-08-11 |
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| CN201310611273.5A Active CN103836847B (en) | 2012-11-26 | 2013-11-26 | Refrigerating circulatory device and the hot water generating device for possessing the refrigerating circulatory device |
Country Status (3)
| Country | Link |
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| EP (1) | EP2735819B1 (en) |
| JP (1) | JP2014105890A (en) |
| CN (1) | CN103836847B (en) |
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Also Published As
| Publication number | Publication date |
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| CN103836847B (en) | 2017-08-11 |
| JP2014105890A (en) | 2014-06-09 |
| EP2735819B1 (en) | 2019-01-09 |
| EP2735819A2 (en) | 2014-05-28 |
| EP2735819A3 (en) | 2016-06-22 |
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