CN100578114C - Freezing device - Google Patents
Freezing device Download PDFInfo
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- CN100578114C CN100578114C CN200710152898A CN200710152898A CN100578114C CN 100578114 C CN100578114 C CN 100578114C CN 200710152898 A CN200710152898 A CN 200710152898A CN 200710152898 A CN200710152898 A CN 200710152898A CN 100578114 C CN100578114 C CN 100578114C
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- freeze cycle
- refrigerant
- compressor
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- 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
- 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
- F25B2400/22—Refrigeration systems for supermarkets
Abstract
A freezing apparatus is provided to maintain the freezing ability even replaced to the freezing apparatus used by the HFC series refrigerant in the current indoor device and the indoor tubing used by the HCFC series refrigerant, and also prevent the decrease of the operation efficiency due to the pressure loss increase by inhibiting the increase the flow speed of the refrigerant. The refrigerant of the main freezing cycle uses the refrigerant with an evaporating temperature below the 0 DEG C. The refrigerant of the secondary freezing cycle uses the refrigerant, better than the refrigerant COP of the main freezing cycle, with an evaporating temperature above the 0 DEG C. Thus, the invention can over-cool the refrigerant of the main freezing cycle by a secondary freezing cycle with a good COP and improve the operation efficiency of the entire freezing apparatus.
Description
Technical field
The present application relates to a kind of refrigerating plant, its by raceway and gondola and air conditioner etc. within doors equipment be connected use, with the further supercooling of cold-producing medium after the liquefaction.
Background technology
At present, use the refrigerating plant of HCFC series coolant such as R22 to be used for convenience store (CVS) and mega-store more.These refrigerating plants have to separate and the divergence type of condenser shown in Figure 1 are set or make condenser and that refrigerating plant becomes one is one-piece type.But,, therefore become the object of restriction because the HCFC series coolant that uses in these refrigerating plants has the character that damages the ozone layer.
Therefore, consider to increase the refrigerating plant of the HFC series coolant of R32, R407A that use do not damage the ozone layer, R410A etc. from now on.Because the restriction stage of HCFC series coolant is carried out, therefore, consider with respect to having used the HCFC series coolant equipment of both having deposited also to carry out displacement (with reference to patent documentation 1) to the HFC series coolant.
Patent documentation 1: the spy opens the 2001-201215 communique
But, because the HFC series coolant is different with HCFC series coolant physical property, so the refrigerating plant that has used the HCFC series coolant directly can not be migrated the HFC series coolant with on the refrigerating plant.Therefore, when the HFC series coolant being used for the HCFC series coolant using refrigerating plant, must be corresponding with its physical property.
For example, the HFC series coolant is compared with the HCFC series coolant, and under same evaporating temperature, therefore the operating pressure height, should be noted that the withstand voltage properties of pipe arrangement etc.And the HFC series coolant is compared with the HCFC series coolant, and the refrigerating capacity of per unit volume is low, so in order to obtain the refrigerating capacity with HCFC series coolant par, need to increase refrigerant flow.
Therefore, in CVS and megastore, utilize towards the raceway of both having established of HCFC series coolant device design, replace with refrigerating plant to the HFC series coolant, in this case, in order to ensure the refrigerating capacity of par when using the HCFC series coolant, the flow velocity that needs to increase cold-producing medium also increases refrigerant flow.But, when increasing the flow velocity of cold-producing medium, will cause the pressure loss in the raceway to increase, therefore, the energy loss of cold-producing medium circulation time strengthens, thereby causes sport efficiency to reduce.
Keep refrigerating capacity for the flow velocity that does not increase cold-producing medium, its method is to strengthen the internal diameter of raceway, increases sectional area, thereby increase refrigerant flow, but,, just need the very expense and the time of great number in order on the equipment of both having established within doors, to lay raceway again.
Summary of the invention
So, the purpose of the present application is, in being designed to the equipment of both having established within doors and raceway that the HCFC series coolant uses, even be replaced as the HFC series coolant with under the situation of refrigerating plant, also can keep refrigerating capacity, and suppress the increase of the flow velocity of cold-producing medium, prevent the decline of the running efficiency that the increase because of the pressure loss causes thus.
In addition, the present application is not limited to utilize the equipment within doors both established and the situation of raceway, when the refrigerating plant of use HFC series coolant newly developed, utilize and use the refrigerating plant of the refrigerating plant same degree size of HCFC series coolant, can guarantee the refrigerating capacity that needs.
The present application is put in view of the above problems and is developed, first aspect present invention provides a kind of main freeze cycle, by possessing main freeze cycle refrigerating plant with compressor, main freeze cycle condenser, possess in the main freeze cycle of main freeze cycle with the formation of equipment within doors of decompressor and evaporimeter, possess secondary freeze cycle with condenser and described main freeze cycle between with decompressor in described main freeze cycle, this pair freeze cycle possesses the overcooled supercooling heat exchanger of cold-producing medium that flows out with condenser from this main freeze cycle, described secondary freeze cycle possesses secondary freeze cycle compressor, secondary freeze cycle condenser, secondary freeze cycle decompressor, described supercooling heat exchanger, described refrigeration system possesses the raceway that the described pipe arrangement of equipment is within doors connected, described raceway is become the specification of HCFC series coolant by PIPING DESIGN, and the cold-producing medium that described main freeze cycle and described secondary freeze cycle are used is the HFC series coolant.
Second aspect present invention is on the basis of first aspect, and described main freeze cycle is separated setting or integrated setting with condenser with described refrigerating plant.
Third aspect present invention provides a kind of refrigeration system on the basis of first aspect or second aspect, it is characterized in that, the evaporating temperature of described main freeze cycle is lower than the evaporating temperature of described secondary freeze cycle.
Fourth aspect present invention provides a kind of refrigeration system on the basis of first aspect or second aspect, it is characterized in that, the described condenser and the described refrigerating plant of described main freeze cycle are provided with separately.
According to the present application, lower by the evaporating temperature of setting main freeze cycle than the evaporating temperature of secondary freeze cycle, the cold-producing medium of the good secondary freeze cycle supercooling master freeze cycle of COP can be passed through, and the running efficiency of refrigeration system integral body can be improved.In addition, by appending secondary freeze cycle, can be not the refrigerating plant of main freeze cycle is not maximized and can increase refrigerating capacity.
Use is designed to the raceway of both having established of specification of the HCFC series coolant of main freeze cycle, when main freeze cycle is used the HFC series coolant, because cold-producing medium physical property difference, thereby causes the cold-producing medium ability drop of per unit volume.According to the present application, by the cold-producing medium of secondary freeze cycle supercooling master freeze cycle, increase the refrigerating capacity of per unit volume, thus, the flow and the flow velocity of the liquid refrigerant of raceway can be reduced to flow through, the pressure loss in the raceway can be reduced.Thereby, can improve the running efficiency of refrigeration system integral body.
Description of drawings
Fig. 1 is the refrigerant loop figure of existing refrigerating plant;
Fig. 2 is the refrigerant loop figure that has used the refrigerating plant of the present application;
Fig. 3 is the refrigerant loop figure that possesses the refrigerating plant of the inner heat exchanger of having used the present application.
Symbol description
100,101 compressors
102 oil eliminators
103 reservoirs
104 filters
105 storage heaters
106 filters (oil is used)
107,108 magnetic valves (oil is used)
109,112 filters (liquid sprays and uses)
110,113 expansion valves (liquid sprays and uses)
111,114 magnetic valves (liquid sprays and uses)
200 condensers
300 compressors
301 oil eliminators
302 condensers
303 reservoirs
304 expansion valves
305 cascade heat exchangers
306 accumulators
307 filters (oil is used)
308 magnetic valves (oil is used)
309 filters (liquid sprays and uses)
310 expansion valves (liquid sprays and uses)
311 magnetic valves (liquid sprays and uses)
312 high pressure temperature sensors
313 high-pressure sensors
314 secondary freeze cycle side entrance temperature sensors
315 secondary freeze cycle side outlet temperature sensors
316 low-pressure sensors
317 main freeze cycle side entrance temperature sensors
318 main freeze cycle side outlet temperature sensors
319 main freeze cycle side outlet pressure sensors
320 inner heat exchangers
The specific embodiment
Below, with reference to the implementation method of accompanying drawing detailed description the present application.
Embodiment
Fig. 2 is the refrigerant loop figure that has used the refrigerating plant of the present application, is made of refrigerating plant 1, condensation unit 2, supercooling unit 3 (secondary freeze cycle).Flow into to the refrigerant inlet C of supercooling unit 3 from refrigerant outlet B after the gas refrigerant that flows into from the refrigerant inlet A of refrigerating plant 1 becomes liquid refrigerant, the liquid refrigerant after the supercooling flows out to the indoor tube (not shown) that possesses gondola and air conditioner etc. from refrigerant outlet D.
Above-mentioned raceway is the pipe arrangement in be laid in CVS and the mega-store, still utilizes the pipe arrangement of HCFC series coolant for object designs pipe arrangement footpath.In addition, in the present application, the pipe arrangement that this raceway is not limited to both establish also can be suitable for the pipe arrangement of newly establishing with refrigerating plant, and the pipe arrangement diameter also is not limited to be designed to the pipe arrangement diameter that the HCFC series coolant is used.
In the present embodiment, suppose to be provided within doors indoor units as refrigerating plant 1, the condenser that employing will be carried out heat exchange separates setting formation without as condensation unit 2 with refrigerating plant 1.In addition, the present application is not limited thereto, and also can be suitable in the incorporate one-piece type refrigerating plant of condenser and refrigerating plant.
In addition, be assumed to be R407A as the cold-producing medium of refrigerating plant 1, but be not limited thereto, just can be suitable for if can set the evaporating temperature cold-producing medium lower than the evaporating temperature of secondary freeze cycle.
Formation and the mobile of cold-producing medium to refrigerating plant 1 describe.Remove impurity from the gas refrigerant that refrigerant inlet A flows into through filter 104, be separated into liquid refrigerant and gas refrigerant by accumulator 105.Liquid refrigerant stores in accumulator 105, and only gas refrigerant is attracted by compressor 100,101, sprays after being compressed into HTHP.
Need to prove, in the present embodiment, the speed changeable compressor of compressor 100 service firing changeable frequencies, the certain constant speed compressor of compressor 101 service firing frequencies, but also equal certain constant speed compressor of service firing frequency of compressor 100 and compressor 101.
The gas refrigerant that is compressed into HTHP by compressor 100, compressor 101 is comprising the lubricating oil ejection in the compressor.The gas refrigerant that gushes out flows into oil eliminator 102, after oil content is separated, flows into the condenser 200 that is provided in the condensation unit 2.
The lubricating oil that is separated in oil eliminator 102 turns back to compressor 100,101 by magnetic valve 107,108 respectively after removing impurity by filter 106.At this moment, to the switching of each compressor control magnetic valve 107,108, so that the lubricating oil in the compressor reaches more than the certain value.
Liquid refrigerant in condenser 200 behind the cooling condensation turns back to refrigerating plant 1 from condensation unit 2, stores in reservoir 103.The liquid refrigerant that stores in reservoir 103 flows into to the refrigerant inlet C of supercooling unit 3 from the refrigerant outlet B of refrigerating plant 1, after in heat exchanger 305, carrying out supercooling, flow out by the equipment within doors of raceway to gondola and air conditioner etc. from the refrigerant outlet D of supercooling unit 3.
In addition, produce high temperature in order to prevent compressor 100,101, and be provided with the liquid spray circuits.In the liquid spray circuits, the liquid refrigerant that extracts from reservoir 103 is removed impurity filter 109,112 after, supply to compressor 100,101 by expansion valve 110,113 and magnetic valve 111,114 successively, cool off by each compressor.The control switching degree of expansion valve 110,113 and the switching of magnetic valve 111,114 are so that be in the certain limit from the temperature of the cold-producing medium of compressor 100,101 ejections.
The method for controlling of operation of refrigerating plant 1 is described.The method for controlling of operation of relevant refrigerating plant 1 is not limited to the method shown in the present embodiment, and existing method for controlling of operation also has no relations, and any method for controlling of operation all can access the effect of the present application of supercooling unit 3.
The attraction lateral pressure (low pressure) of the compressor of refrigerating plant 1 is by pressure sensor (not shown) instrumentation, by relatively this low pressure and predetermined authorized pressure I, authorized pressure II, and the control of turning round thus.The value of authorized pressure II is bigger than the value of authorized pressure I.
During less than authorized pressure I, compressor 100 and compressor 101 shut down simultaneously at low pressure.Low pressure becomes authorized pressure I when above, and speed changeable compressor 100 is with minimum operating frequency entry into service.
When low pressure was positioned at the scope of the above discontented authorized pressure II of authorized pressure I, along with the increase of low pressure, operating frequency increased.Low pressure becomes authorized pressure II when above, and speed changeable compressor 100 is once more with minimum operating frequency running, constant speed compressor 101 entrys into service.Thereafter, constant speed compressor 101 remains in operation, and along with the increase of low pressure, the operating frequency of speed changeable compressor 100 increases.
In addition, low pressure reduces, and becomes authorized pressure II when following, and constant speed compressor 101 shuts down, and speed changeable compressor 100 is with the transport maximum frequency run.Thereafter, the operating frequency of speed changeable compressor 100 reduces with the minimizing of low pressure, becomes authorized pressure I up to low pressure, and low pressure becomes authorized pressure I when following, and speed changeable compressor 100 shuts down.
Formation and the mobile of cold-producing medium to supercooling unit 3 describe.Supercooling unit 3 constitutes and is independent of by refrigerating plant 1, condensation unit 2, raceway, secondary freeze cycle, main freeze cycle and the secondary freeze cycle thermal bonding of the main freeze cycle that constitutes of equipment within doors.
Cold-producing medium as supercooling unit 3 is assumed to be R410A, but is not limited thereto, and just can be suitable for if evaporating temperature is set the cold-producing medium of the evaporating temperature that is higher than main freeze cycle.
In supercooling unit 3, the cold-producing medium that gushes out by compressor 300 compressions flows into oil eliminator 301.Because the cold-producing medium that gushes out includes the lubricating oil in the compressor, so flow into condenser 302 after in oil eliminator 301, removing lubricating oil.The temperature of ejection cold-producing medium and pressure are by temperature sensor 312 and pressure sensor 313 instrumentations.
Need to prove that the speed changeable compressor of service firing changeable frequency but also can the certain constant speed compressor of service firing frequency as compressor 300 in the present embodiment.
The lubricating oil of separating in oil eliminator 301 turns back to compressor 300 by magnetic valve 308 after this removes impurity at filter 307.Need to prove, because the freeze cycle of supercooling unit 3 for having closed, so the lubricating oil that remains in the refrigerating circuit is few.In addition, owing to only load a compressor, so even the amount of adjusting the lubricating oil that turns back to compressor 300 by magnetic valve 308 does not have no relations yet.
Cooling condensation in condenser 302 and the cold-producing medium that becomes liquid store in reservoir 303.A part that stores the liquid refrigerant in reservoir 303 is used in the liquid injection that is used for the temperature of compressor 300 is remained on certain limit.
In the liquid spray circuits, the cold-producing medium that extracts from reservoir 303 is removed impurity filter 309 after, flow into compressors 300, cooling compressor 300 by expansion valve 310 and magnetic valve 311.The control aperture of expansion valve 310 and the switching of magnetic valve 311 are so that be in the certain limit from the temperature of the cold-producing medium of compressor 300 ejections.
Store in reservoir 303 liquid refrigerant by expansion valve 304 decompressions, flow into the secondary freeze cycle side and the evaporation of cascade heat exchanger 305 (supercooling heat exchangers), thus, the high-temperature fluid cold-producing medium of the main freeze cycle side of cascade heat exchanger 305 is flow through in cooling (supercooling).In addition, the refrigerant temperature of the secondary freeze cycle side entrance of cascade heat exchanger 305 is by temperature sensor 314 instrumentations, and the refrigerant temperature of main freeze cycle side entrance is by temperature sensor 317 instrumentations.
The cold-producing medium that flows out owing to the secondary freeze cycle side outlet from cascade heat exchanger 305 comprises a part of liquid refrigerant, so be separated into liquid refrigerant and gas refrigerant in accumulator 306.Liquid refrigerant stores in accumulator 306, and only gas refrigerant is attracted in the compressor 300.In addition, the cold-producing medium that flows out from the main freeze cycle side outlet of cascade heat exchanger 305 flows out to the equipment within doors of gondola and air conditioner etc. by raceway from the refrigerant outlet D of supercooling unit 3.
Need to prove, the refrigerant temperature of the secondary freeze cycle side outlet of cascade heat exchanger 305 is by temperature sensor 315 instrumentations, the refrigerant temperature of main freeze cycle side outlet is by temperature sensor 318 instrumentations, the refrigerant pressure of main freeze cycle side outlet is by pressure sensor 319 instrumentations, and the low-pressure lateral pressure of compressor 300 is by pressure sensor 316 instrumentations.
In the present embodiment,, establish condenser 302 for one-piece type as the formation of supercooling unit 3, therefore, be assumed to be provided in can with the outdoor unit outside the room of outer gas heat exchange.But the present application is not limited thereto, as with condenser as the formation that the condenser unit is provided with separately, also supercooling unit 3 can be set as be arranged within doors indoor units.
In addition, as shown in Figure 3,, can make that the liquid refrigerant before the supercooling and the liquid refrigerant after the supercooling carry out heat exchange in cascade heat exchanger 305 by inner heat exchanger 320 is set.Thus, can reduce the temperature difference of the liquid refrigerant of cascade heat exchanger 305 between the gateway of main freeze cycle side, therefore can realize the long lifetime of cascade heat exchanger 305.
Below, the method for controlling of operation of supercooling unit 3 is described.
(1) the certain operation mode of supercooling degree
In supercooling unit 3, the refrigerant pressure of the main freeze cycle side outlet by pressure sensor 319 instrumentation cascade heat exchangers 305 calculates saturation temperature (cold-producing medium saturation temperature) ST of the cold-producing medium of this refrigerant pressure.In the present embodiment, in the calculating of saturation temperature ST, the correspondence table of refrigerant pressure and cold-producing medium saturation temperature ST is stored in (not shown) in the control device in advance, obtains the approximation of cold-producing medium saturation temperature ST from this correspondence table.In addition, about the calculating of cold-producing medium saturation temperature ST, also can obtain by the approximate expression of the relation of representing refrigerant pressure and cold-producing medium saturation temperature ST.
The refrigerant temperature T1 of the main freeze cycle side outlet by temperature sensor 318 instrumentation cascade heat exchangers 305, the numerical expression 1 below utilizing are calculated the supercooling degree SC of cold-producing medium of the main freeze cycle side outlet of cascade heat exchanger 305 by this refrigerant temperature T1 and cold-producing medium saturation temperature ST.
Number 1:SC=ST-T1
The supercooling degree that equipment is within doors needed is set in advance in the control device as regulation supercooling degree CSC, and cold-producing medium supercooling degree SC and regulation supercooling degree CSC are compared.Numerical expression 2 below utilizing calculates the poor DSC of cold-producing medium supercooling degree SC and regulation supercooling degree CSC.
Number 2:DSC=SC-CSC
Cold-producing medium supercooling degree SC is during greater than regulation supercooling degree CSC, and promptly DSC was greater than 0 o'clock, and the main freeze cycle side of cascade heat exchanger 305 is carried out excessive supercooling.So, by closing the cooling of expansion valve 304 inhibition cascade heat exchangers 305.In the present embodiment, the valve opening of expansion valve 304 is corresponding with DSC, and the aperture of the big more expansion valve 304 of DSC is more little.In addition, DSC is that setting is closed expansion valve 304 when above.
Cold-producing medium supercooling degree SC is during less than regulation supercooling degree CSC, and promptly DSC is less than 0 o'clock, the main freeze cycle side supercooling deficiency of cascade heat exchanger 305.So, by opening the cooling of expansion valve 304 promotion cascade heat exchangers 305.As mentioned above, in the present embodiment, the valve opening of expansion valve 304 is corresponding with DSC, and the aperture of the more little expansion valve 304 of DSC is big more.
When cold-producing medium supercooling degree SC equals regulation supercooling degree CSC, because the supercooling that realize to need, so, do not change the aperture of expansion valve 304.In addition, the control of the valve opening of expansion valve 304 is not limited to this method, also can utilize the ratio of cold-producing medium supercooling degree SC and regulation supercooling degree CSC.
Also can the temperature difference of this entrance side temperature and this outlet side temperature be carried out above-mentioned control as cold-producing medium supercooling degree SC by the cold refrigerant temperature of freezing circulation side inlet and outlet of the master of TEMP 317 and 318 instrumentation cascade heat exchangers 305.
(2) the above operation mode of dew point
Humidity sensor within doors (not shown) instrumentation by instrumentation raceway ambient humidity, light and temperature is humidity within doors, calculates this saturation temperature (steam-laden temperature) WT of the steam in the humidity within doors.In the present embodiment, the calculating of the saturation temperature WT of steam will be within doors the correspondence table of saturation temperature WT of humidity and steam remember in control device (not shown) in advance, obtain the approximation of steam-laden temperature WT by this correspondence table.In addition, the calculating of the saturation temperature WT of steam also can be by representing that the approximate expression of the relation of humidity and steam-laden temperature WT is obtained within doors.
The computational methods of steam-laden temperature WT also can for, the inner temperature of room sensor (not shown) of instrumentation raceway temperature on every side is set, the correspondence table of humidity and steam-laden temperature WT is within doors remembered in control device (not shown) in advance, obtain the approximation of steam-laden temperature WT by the inner temperature of room that measures.In addition, the calculating of the saturation temperature WT of relevant steam also can be by representing that the approximate expression of the relation of the saturation temperature WT of humidity and steam is obtained within doors.
The refrigerant temperature T1 of the main freeze cycle side outlet by temperature sensor 318 instrumentation cascade heat exchangers 305 compares refrigerant temperature T1 and the steam-laden temperature WT that calculates.Numerical expression 3 below utilizing calculates the poor DWT of refrigerant temperature T1 and steam-laden temperature WT.
Number 3:DWT=T1-WT
Consider when refrigerant temperature T1 is higher than steam-laden temperature WT, be that DWT was greater than 0 o'clock, be difficult to take place dewfall in doors on the pipe arrangement, and the high refrigerating capacity deficiency of refrigerant temperature, therefore, the main freeze cycle side of the valve opening cooling cascade heat exchanger 305 by increasing expansion valve 304 improves refrigerating capacity thus.The valve opening of expansion valve 304 is corresponding with DWT, and the valve opening of the big more expansion valve 304 of DWT is big more.
On the other hand, when refrigerant temperature T1 was lower than steam-laden temperature WT, promptly DWT was less than 0 o'clock, produce dewfall on the pipe arrangement in doors, therefore, suppress the cooling of the main freeze cycle side of cascade heat exchanger 305 by the valve opening that reduces expansion valve 304, improve refrigerant temperature T1, prevent dewfall thus.As mentioned above, the valve opening of expansion valve 304 is corresponding with DWT, and the more little expansion valve 304 of DWT cuts out more, and DWT closes expansion valve 304 during less than setting.
(3) the certain operation mode of refrigerant temperature
The refrigerant temperature T1 of the main freeze cycle side outlet by temperature sensor 318 instrumentation cascade heat exchangers 305.Can export within doors the refrigerant temperature of the needed refrigerating capacity of equipment and remember in control device (not shown) in advance, calculate the poor DCT of refrigerant temperature T1 and set point of temperature CT by following numerical expression 4 as set point of temperature TC.
Number 4:DCT=T1-CT
When refrigerant temperature T1 was lower than set point of temperature CT, promptly DCT was 0 when following, and the refrigerating capacity surplus so reduce the valve opening of expansion valve 304, suppresses the cooling of the main freeze cycle side of cascade heat exchanger 305 thus.The valve opening of expansion valve 304 is corresponding with DCT, and the more little expansion valve 304 of DCT cuts out more, during less than setting, closes expansion valve 304 at DCT.
On the other hand, when refrigerant temperature T1 was higher than set point of temperature CT, promptly DCT was 0 when above, and the refrigerating capacity deficiency so increase the valve opening of expansion valve 304, promotes the cooling of the main freeze cycle side of cascade heat exchanger 305 thus.As mentioned above, the valve opening of expansion valve 304 is corresponding with DCT, and DCT is big more, and expansion valve 304 is opened more.
In above-mentioned any operation mode, compressor 300 all can be by being controlled by the low pressure of pressure sensor 316 instrumentations.The operating frequency of compressor 300 is controlled to be this low pressure in prescribed limit, the proportional increase of the rising of low pressure, and the ratio that is declined to become of low pressure reduces.
In addition, the running of compressor 300 control is not limited to this method, also can with the valve opening interlock of expansion valve 304 in above-mentioned each operation mode, operating frequency increased when valve opening increased, operating frequency reduced when valve opening reduced.
Need to prove, when compressor 300 is constant speed compressor, is positioned at the lower limit of afore mentioned rules scope at low pressure and shuts down entry into service when the lower limit of prescribed limit is above when following.In addition, the running of compressor 300 control is not limited to this method, also can be that the valve opening of the expansion valve 304 in above-mentioned each operation mode turns round when above to setting, and valve opening is the method that setting shuts down when following.
Below, control describes to the co-operation of refrigerating plant 1 and supercooling unit 3.In the equipment within doors of main freeze cycle, during freezing energy surplus,,, in main freeze cycle, become the state that cold-producing medium does not circulate so the compressor 100 and 101 of refrigerating plant 1 shuts down because the suction side pressure of the compressor of refrigerating plant 1 reduces greatly.
The temperature or the pressure of the main freeze cycle side of supercooling unit 3 instrumentation cascade heat exchangers 305, thereby turn round control, therefore, under the state that the cold-producing medium of main freeze cycle does not circulate, there is the possibility of individual operation (idle running) in the refrigerating capacity that can not instrumentation master freeze cycle needs.
For corresponding therewith, the compressor 300 of supercooling unit 3 in supercooling unit 3 do not shut down and the compressor 100 and 101 of refrigerating plant 1 when shutting down, the authorized pressure I that will be used to control the running of refrigerating plant 1 is set at the value lower than original value again, thus the stopping of the compressor of freezing-inhibiting device 1.Thus, cold-producing medium circulates in main freeze cycle, so supercooling unit 3 can carry out and the present corresponding running of refrigerating capacity that needs of main freeze cycle.In addition, the suction side pressure of the compressor of refrigerating plant 1 makes the value of authorized pressure I turn back to original value during greater than original authorized pressure I.
Have, same, the compressor 300 of supercooling unit 3 does not shut down and the compressor 100 and 101 of refrigerating plant 1 when shutting down again, and the prescribed limit of low pressure that supercooling unit 3 will be used to control the running of compressor 300 transforms to higher scope.Thus, compressor 300 is lower than common output, thus can suppress the supercooling of cold-producing medium in the main freeze cycle of supercooling unit 3, thus promote the running of main freeze cycle.Thereby, owing to cold-producing medium circulates in main freeze cycle, so, the corresponding running of refrigerating capacity that supercooling unit 3 can carry out and main freeze cycle needs now.In addition, compressor 300 low pressures are gone up in limited time greater than original prescribed limit, and the value of prescribed limit is turned back to original value.
Need to prove, because when the compressor of main freeze cycle shuts down, mostly be the situation of the refrigerating capacity surplus of main freeze cycle, according to the operational situation that is judged as the supercooling unit 3 of refrigerating capacity surplus compressor 300 shut down so also can control not operate as.
Claims (4)
1, a kind of refrigeration system is characterized in that:
By possess the refrigerating plant of main freeze cycle with compressor, main freeze cycle with condenser, possess in the main freeze cycle that main freeze cycle constitutes with the equipment within doors of decompressor and evaporimeter,
Possess secondary freeze cycle with condenser and described main freeze cycle between with decompressor in described main freeze cycle, this pair freeze cycle possesses the overcooled supercooling heat exchanger of cold-producing medium that flows out with condenser from this main freeze cycle,
Described secondary freeze cycle possesses secondary freeze cycle compressor, secondary freeze cycle condenser, secondary freeze cycle decompressor, described supercooling heat exchanger,
Described refrigeration system possesses the raceway that the described pipe arrangement of equipment is within doors connected,
Described raceway is become the specification of HCFC series coolant by PIPING DESIGN,
The cold-producing medium that described main freeze cycle and described secondary freeze cycle are used is the HFC series coolant.
2, refrigeration system as claimed in claim 1 is characterized in that:
Described main freeze cycle is separated setting or integrated setting with condenser with described refrigerating plant.
3, refrigeration system as claimed in claim 1 or 2 is characterized in that;
The evaporating temperature of described main freeze cycle is lower than the evaporating temperature of described secondary freeze cycle.
4, refrigeration system as claimed in claim 1 or 2 is characterized in that, described main freeze cycle is provided with separately with condenser and described refrigerating plant.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006266556A JP2008082674A (en) | 2006-09-29 | 2006-09-29 | Supercooling device |
| JP266556/06 | 2006-09-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101153752A CN101153752A (en) | 2008-04-02 |
| CN100578114C true CN100578114C (en) | 2010-01-06 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200710152898A Expired - Fee Related CN100578114C (en) | 2006-09-29 | 2007-09-21 | Freezing device |
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| Country | Link |
|---|---|
| JP (1) | JP2008082674A (en) |
| CN (1) | CN100578114C (en) |
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| JP5517333B2 (en) * | 2009-11-02 | 2014-06-11 | 中野冷機株式会社 | Refrigeration apparatus and operation method thereof |
| CN101706171B (en) * | 2009-11-16 | 2012-08-22 | 高秀明 | Air supplement heat recovery heat pump device |
| CN103023277B (en) * | 2011-09-26 | 2016-08-17 | 艾默生网络能源有限公司 | The anti-condensation control method of water-cooled current transformer and device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE3032357C1 (en) * | 1980-08-28 | 1982-04-01 | Messer Griesheim Gmbh, 6000 Frankfurt | Process for cutting a pipe fitting with a weld joint preparation |
| JP2002286310A (en) * | 2001-03-28 | 2002-10-03 | Tokyo Gas Co Ltd | Compressive refrigerating machine |
| JP4488712B2 (en) * | 2003-10-08 | 2010-06-23 | 三菱電機株式会社 | Air conditioner |
| JP2005221194A (en) * | 2004-02-09 | 2005-08-18 | Mitsubishi Heavy Ind Ltd | Air conditioning, refrigerating and freezing facility |
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2006
- 2006-09-29 JP JP2006266556A patent/JP2008082674A/en active Pending
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- 2007-09-21 CN CN200710152898A patent/CN100578114C/en not_active Expired - Fee Related
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| Publication number | Publication date |
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| CN101153752A (en) | 2008-04-02 |
| JP2008082674A (en) | 2008-04-10 |
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