CN102971592A - Two-stage pressure buildup refrigeration cycle system - Google Patents
Two-stage pressure buildup refrigeration cycle system Download PDFInfo
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- CN102971592A CN102971592A CN2011800336229A CN201180033622A CN102971592A CN 102971592 A CN102971592 A CN 102971592A CN 2011800336229 A CN2011800336229 A CN 2011800336229A CN 201180033622 A CN201180033622 A CN 201180033622A CN 102971592 A CN102971592 A CN 102971592A
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- 239000003507 refrigerant Substances 0.000 claims abstract description 193
- 230000007246 mechanism Effects 0.000 claims abstract description 127
- 238000007599 discharging Methods 0.000 claims description 47
- 238000001816 cooling Methods 0.000 claims description 27
- 230000006835 compression Effects 0.000 claims description 19
- 238000007906 compression Methods 0.000 claims description 19
- 238000006073 displacement reaction Methods 0.000 claims description 10
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/025—Motor control arrangements
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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
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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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
- F25B2600/11—Fan speed control
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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
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
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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
- F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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Abstract
Disclosed is a two-stage pressure buildup refrigeration cycle system which includes a higher-stage compressor mechanism (11a) and a lower-stage compressor mechanism (12a), the refrigerant delivery capacities of which are independently controllable. The refrigerant delivery capacity of the lower-stage compressor mechanism (12a) is determined on the basis of an outside air temperature (Tam), an air temperature (Tfr), and a temperature setting (Tset). The refrigerant delivery capacity of the higher-stage compressor mechanism (11a) is determined based on the determined refrigerant delivery capacity of the lower-stage compressor mechanism (12a) so that the effective capacity ratio is equal to or greater than one and equal to or less than three. This simplified construction and control can provide an improved COP for the two-stage pressure buildup refrigeration cycle system.
Description
The cross reference of related application
The application is based on the Japanese patent application of filing an application on July 7th, 2010 2010-154680 number, and the content of described patent application is incorporated in full at this by reference.
Technical field
The present invention relates to a kind of low-pressure side compressing mechanism and high side compressors structure of comprising with the two-stage pressurization refrigerating circulatory device of the pressure by multistage increase cold-producing medium.
Background technology
Traditionally, patent documentation 1 discloses a kind of two-stage pressurization refrigerating circulatory device of the pressure for increase cold-producing medium multistagely.This refrigerating circulatory device comprises low pressure refrigerant compression and arranges into the low-pressure side compressing mechanism of intermediate pressure refrigerant and be used for and will and arrange into the high side compressors structure of high-pressure refrigerant from the intermediate pressure refrigerant compression of low-pressure side compressing mechanism discharging.
More specifically, disclosed two-stage pressurization refrigerating circulatory device comprises that a part be used to the high-pressure refrigerant that distributes from the radiator of the heat of the high-pressure refrigerant of high side compressors structure discharging and be used for flowing out from radiator reduces pressure and expand into the intermediate pressure expansion valve of intermediate pressure refrigerant in the patent documentation 1.This two-stage pressurization refrigerating circulatory device is so-called economical refrigerating circulatory device, and this economical refrigerating circulatory device will be directed to by the intermediate pressure refrigerant that the intermediate pressure expansion valve reduces pressure the suction side of high side compressors structure.
In this economical refrigerating circulatory device, the high side compressors structure can suck the intermediate pressure refrigerant that is depressurized by the intermediate pressure expansion valve and from the mixture of the intermediate pressure refrigerant of low-pressure side compressing mechanism discharging.Therefore therefore, the low-temperature mixed cold-producing medium can be inhaled in the high side compressors structure, compares with situation about only sucking from the intermediate pressure refrigerant of low-pressure side compressing mechanism discharging, can improve the compression efficiency of high side compressors structure.
In addition, in this economical refrigerating circulatory device, high side compressors structure and low-pressure side compressing mechanism have roughly the same compression ratio each other.The pressure of intermediate pressure refrigerant (intermediate refrigerant pressure) is designed to approach the target intermediate refrigerant pressure of the geometric mean between the pressure (low-pressure side refrigerant pressure) of the pressure (high-pressure side refrigerant pressure) be defined as high-pressure refrigerant and low pressure refrigerant, thereby improves the coefficient of performance (COP) that circulates.
In patent documentation 1, in the disclosed two-stage pressurization refrigerating circulatory device, change the throttling arrangement aperture of intermediate pressure expansion valve, so that intermediate refrigerant pressure is near target intermediate refrigerant pressure, thereby improve COP.
[correlation technique document]
[patent documentation]
[patent documentation 1]
Japanese unexamined patent discloses 2006-242557 number
Yet disclosed two-stage pressurization refrigerating circulatory device is determined target intermediate refrigerant pressure according to high-pressure side refrigerant pressure and low-pressure side refrigerant pressure in the patent documentation 1.Therefore, must provide pressure-detecting device to detect high-pressure side refrigerant pressure and low-pressure side refrigerant pressure, therefore may increase the manufacturing cost of two-stage pressurization refrigerating circulatory device.
When the throttling arrangement aperture that changes the intermediate pressure expansion valve so that intermediate refrigerant pressure during near target intermediate refrigerant pressure, may change high-pressure side refrigerant pressure and low-pressure side refrigerant pressure, thereby so that be used for stablizing the control complicated of the cold-producing medium discharge capacity of each compressing mechanism.
The intermediate pressure refrigerant that flows out from middle pressure expansion valve usually only the throttling arrangement aperture by changing the intermediate pressure expansion valve so that intermediate refrigerant pressure is converted into liquid phase or gas-liquid two-phase attitude near target intermediate refrigerant pressure.Therefore, produce the high side compressors structure and forced the liquid compression problem of compression incompressible fluid, thereby reduced the reliability of high side compressors structure, that is, reduced the reliability of whole two-stage pressurization refrigerating circulatory device.
Summary of the invention
Considered that the problems referred to above make the present invention, and the first purpose of the present invention provides a kind of two-stage pressurization refrigerating circulatory device that can improve with simple structure and control COP.
The second purpose of the present invention provides a kind of two-stage pressurization refrigerating circulatory device that high reliability can be provided with simple structure and control.
In order to realize described purpose, according to a first aspect of the invention two-stage pressurization refrigerating circulatory device comprises: the low-pressure side compressing mechanism, and described low-pressure side compressing mechanism is compressed into intermediate pressure refrigerant and the cold-producing medium after the described low-pressure side compressing mechanism discharging compression with low pressure refrigerant; High side compressors structure, described high side compressors structure will be compressed into from the intermediate pressure refrigerant of low-pressure side compressing mechanism discharging high-pressure refrigerant with the cold-producing medium after described high side compressors structure discharging compression; Radiator, described radiator outdoor air and from heat-shift between the high-pressure refrigerant of high side compressors structure discharging to distribute the heat of cold-producing medium; The intermediate pressure expansion valve, described intermediate pressure expansion valve will reduce pressure from the high-pressure refrigerant that radiator flows out and expand into intermediate pressure refrigerant so that intermediate pressure refrigerant flow into the suction side of high side compressors structure; The inflated with low pressure valve, described inflated with low pressure valve will reduce pressure from the high-pressure refrigerant that radiator flows out and expand into low pressure refrigerant; And evaporimeter, described evaporimeter is by evaporating the low pressure refrigerant that is reduced pressure and expand by the inflated with low pressure valve with the air exchange heat that will be blown in the cooling space, and makes cold-producing medium after the evaporation flow into the suction side of low-pressure side compressing mechanism.In addition, two-stage pressurization refrigerating circulatory device comprises the first discharging capacity control and the second discharging capacity control.The first discharging capacity control is configured to determine at least one the cold-producing medium discharge capacity in high side compressors structure and the low-pressure side compressing mechanism, so that the cold-producing medium discharge capacity increases at the external air temperature of the outdoor air of radiator place and high-pressure refrigerant heat-shift with at least one the increase in the air themperature of the air of evaporimeter place and low pressure refrigerant heat-shift according to being used for.The second discharging capacity control is configured to determine according to the cold-producing medium discharge capacity of a described compressing mechanism of determining the cold-producing medium discharge capacity of another compressing mechanism in high side compressors structure and the low-pressure side compressing mechanism.In addition, the second discharging capacity control is determined the cold-producing medium discharge capacity of another compressing mechanism, so that when V1 be the discharge capacity of high side compressors structure, N1 is the revolution of high side compressors structure, V2 is the discharge capacity of low-pressure side compressing mechanism, and N2 is defined as the available capacity of N2 * V2/N1 * V1 than in the predetermined reference scope when being the revolution of low-pressure side compressing mechanism.
Because the first discharging capacity control is determined the cold-producing medium discharge capacity of a described compressing mechanism according in the air themperature at external air temperature and evaporimeter place at least one, and the cold-producing medium discharge capacity of the described compressing mechanism that the second discharging capacity control basis is determined is determined the cold-producing medium discharge capacity of described another compressing mechanism, and the cold-producing medium discharge capacity of each compressing mechanism can easily be determined.
At this moment, the second discharging capacity control is determined the cold-producing medium discharge capacity of described another compressing mechanism, so that available capacity is than in predetermined term of reference.Therefore, only by suitably setting term of reference, intermediate refrigerant pressure can approach basically with high-pressure side refrigerant pressure and low-pressure side refrigerant pressure between the corresponding value of geometric mean.
Therefore, can under the condition that does not need expensive pressure-detecting device, improve by simple structure the COP of two-stage pressurization refrigerating circulatory device with very easy control.
Irrelevant with the cold-producing medium discharge capacity of each compressing mechanism, can determine that the throttle opening of intermediate pressure expansion valve will be converting gas phase to from the intermediate pressure refrigerant that middle pressure expansion valve flows out.Therefore, can avoid the problem of the liquid compression at high side compressors structure place.
Therefore, the present invention can improve with simple structure the reliability of high side compressors structure,, improves the reliability of whole two-stage pressurization refrigerating circulatory device that is.Each theoretical discharge flow that turns of term used herein " discharge capacity of compressing mechanism " expression compressing mechanism represents the flow that calculates geometrically particularly.
For example, in two-stage pressurization refrigerating circulatory device according to a second aspect of the invention, the decompression of intermediate pressure expansion valve and a high-pressure refrigerant stream that expands and shunted at the distributary division place, shunted described distributary division from the high-pressure refrigerant that radiator flows out, and the inflated with low pressure valve reduces pressure and another high-pressure refrigerant shunted at the distributary division place that expands flows.Refrigerating circulatory device also comprises intermediate heat exchanger, in described intermediate heat exchanger, and heat-shift between the low pressure refrigerant that is reduced pressure by the intermediate pressure expansion valve and expand and another high-pressure refrigerant of being shunted by distributary division.
Two-stage pressurization refrigerating circulatory device of the present invention comprises intermediate heat exchanger, and described intermediate heat exchanger can heat the intermediate pressure refrigerant that flows out from middle pressure expansion valve, easily to convert described cold-producing medium to vapor phase refrigerant.Therefore, can improve definitely the reliability of two-stage pressurization refrigerating circulatory device.
Because another high-pressure refrigerant stream of being shunted at the distributary division place is cooled to enlarge the difference of the heat content between the cold-producing medium in the entrance of evaporimeter and exit, therefore can increase the refrigerating capacity that evaporimeter presents.Therefore, can further improve the COP of two-stage pressurization refrigerating circulatory device.
For example, in two-stage pressurization refrigerating circulatory device according to a third aspect of the invention we, a described compressing mechanism is the low-pressure side compressing mechanism, and described another compressing mechanism is the high side compressors structure.
Therefore, the first discharging capacity control can be determined the cold-producing medium discharge capacity of low-pressure side compressing mechanism according in the air themperature at external air temperature and evaporimeter place at least one, thereby directly controls the cold-producing medium evaporating pressure of evaporimeter.Therefore, be blown into the temperature that the interior air themperature of cooling space trends towards being adjusted to expectation.
In two-stage pressurization refrigerating circulatory device according to a forth aspect of the invention, when the absolute value of the temperature difference between the target chilling temperature of the air themperature at evaporimeter place and cooling space was equal to or less than the predetermined reference temperature difference, the second discharging capacity control was determined the cold-producing medium discharge capacity of described another compressing mechanism according to the cold-producing medium discharge capacity of a described compressing mechanism.
In this case, the second discharging capacity control can be controlled the cold-producing medium discharge capacity of described another compressing mechanism, and no matter the cold-producing medium discharge capacity of a described compressing mechanism, until the absolute value of the difference between the target chilling temperature of the air themperature at evaporimeter place and cooling space is equal to or less than the predetermined reference temperature difference.Therefore, for example, can when starting two-stage pressurization refrigerating circulatory device, carry out the operator scheme that is used for quick cooling cooling space.
In two-stage pressurization refrigerating circulatory device according to a fifth aspect of the invention, when the air themperature at evaporimeter place is higher than the target chilling temperature, and when the absolute value of the temperature difference between the target chilling temperature of the air themperature at evaporimeter place and cooling space was equal to or less than the predetermined reference temperature difference, the second discharging capacity control can be determined according to the cold-producing medium discharge capacity of a described compressing mechanism cold-producing medium discharge capacity of described another compressing mechanism.In this case, can effectively carry out the volume controlled of two compressing mechanisms.
In two-stage pressurization refrigerating circulatory device according to a sixth aspect of the invention, each in high side compressors structure and the low-pressure side compressing mechanism can be formed by the fixed displacement compressing mechanism structure with fixed discharge capacity.In addition, refrigerating circulatory device can also comprise the high-pressure side motor that rotatably drives the high side compressors structure and the low-pressure side motor that rotatably drives the low-pressure side compressing mechanism.In addition, the revolution of the revolution of high-pressure side motor and low-pressure side motor can independently be controlled.
In this case, the discharge capacity of the discharge capacity of high side compressors structure and low-pressure side compressing mechanism becomes respectively constant, so that only at least one in the revolution of the revolution by changing the high side compressors structure and low-pressure side compressing mechanism come easily the available capacity ratio to be arranged in the term of reference.
In addition, in two-stage pressurization refrigerating circulatory device according to a seventh aspect of the invention, in high side compressors structure and the low-pressure side compressing mechanism each can be formed by the compressor with variable displacement structure structure with variable discharge capacity, and the discharge capacity of the discharge capacity of high side compressors structure and low-pressure side compressing mechanism can independently be controlled.
In this case, the discharge capacity of the discharge capacity of high side compressors structure and low-pressure side compressing mechanism can independent variation.Even the revolution of two compressing mechanisms is set to identical level, also available capacity can be set in the term of reference than easily.Therefore, two compressing mechanisms can be driven by the drive unit that shares.
In addition, in above any two-stage pressurization refrigerating circulatory device, the second discharging capacity control can be determined the cold-producing medium discharge capacity of described another compressing mechanism, so that available capacity is than satisfying following formula:
1≤N2×V2/N1×V1≤3。
Description of drawings
Fig. 1 is the overall structure schematic diagram of the two-stage pressurization refrigerating circulatory device among the first embodiment;
Fig. 2 is the flow chart that shows the control procedure of the two-stage pressurization refrigerating circulatory device among the first embodiment;
Fig. 3 (a) is presented at the variation of COP ratio under the predetermined condition A with respect to the curve map of the variation of available capacity ratio;
Fig. 3 (b) is presented at the variation of COP ratio under the predetermined condition B with respect to the curve map of the variation of available capacity ratio; And
Fig. 4 is the overall structure schematic diagram of the two-stage pressurization kind of refrigeration cycle among the second embodiment.
The specific embodiment
(the first embodiment)
With reference to Fig. 1-3, the first embodiment of the present invention is described below.Fig. 1 has shown the overall structure schematic diagram of the two-stage pressurization refrigerating circulatory device of present embodiment.This two-stage pressurization refrigerating circulatory device 10 is applied to refrigeration machine, and is blown into as being used for for example being cooled to the approximately interior blow air of the refrigerator in the space of-30 ℃ to-10 ℃ ultralow temperature for cooling.
As shown in Figure 1, two-stage pressurization refrigerating circulatory device 10 comprises two compressors, that is, and and high side compressors 11 and low-pressure side compressor 12.EGR 10 is used for increasing the pressure of the cold-producing medium that cycles through EGR multistagely.Employed cold-producing medium can be common fluorohydrocarbon cold-producing medium (for example, R404A).The refrigerator oil (oil) that is used for the sliding part of lubricated low-pressure side compressor 12 and high side compressors 11 is mixed to cold-producing medium, so that the part of refrigerator oil cycles through EGR with cold-producing medium.
Low-pressure side compressor 12 is motor compressors, described motor compressor comprise for low pressure refrigerant is compressed into intermediate pressure refrigerant bleed off pressure side by side contracting intermediate pressure refrigerant low-pressure side compressing mechanism 12a and be used for rotatably driving the low-pressure side motor 12b of low-pressure side compressing mechanism 12a.Low-pressure side compressing mechanism 12a is made of the fixing fixed displacement compressing mechanism of discharge capacity V2.Particularly, low-pressure side compressing mechanism 12a can adopt various types of compressing mechanisms, comprises spiral type compressor structure, vane compressor structure, rolling piston compressor structure etc.
Low-pressure side motor 12b is the AC motor, and the operation of described AC motor (revolution) is by the AC current control from 22 outputs of low-pressure side transverter.Low-pressure side transverter 22 output has corresponding to from the AC of the frequency of the control signal of described refrigerating device controller 20 outputs subsequently.Under the control of frequency, the cold-producing medium discharge capacity of low-pressure side compressor 12 (particularly, low-pressure side compressing mechanism 12a) is changed.
Therefore, in the present embodiment, the low-pressure side motor 12b discharge capacity modifier that acts on low-pressure side compressor 12.Significantly, low-pressure side motor 12b can adopt the DC motor, and the revolution of described DC motor is by the control Control of Voltage from refrigerating device controller 20 outputs.The discharge port of low-pressure side compressor 12 (particularly, low-pressure side compressing mechanism 12a) is connected to the suction ports of high side compressors 11.
High side compressors structure 11a is made of the fixed displacement compressing mechanism, and the discharge capacity V1 of described fixed displacement compressing mechanism fixes.The revolution of high-pressure side motor 11b is subject to from the control of the alternating current of high-pressure side transverter 21 outputs.In the present embodiment, the compression ratio with low-pressure side compressing mechanism 12a is identical basically for the compression ratio of high side compressors structure 11a.
The discharge port of high side compressors 11 (particularly, high side compressors structure 11a) is connected to the refrigerant inlet side of radiator 13.Radiator 13 is the heat exchangers for heat radiation, described heat exchanger from the high-pressure refrigerant of high side compressors 11 discharging and the air (outdoor air) that is blowed by cooling fan 13a outside the refrigerator thus between heat-shift to distribute the heat cooling refrigeration agent from high-pressure refrigerant.
Be used for shunting is connected to radiator 13 from the distributary division 14 of radiator 13 inflows cold-producing medium stream wherein refrigerant outlet.Distributary division 14 comprises the three-way connection structure with three inlet/outlet ports.In the inlet/outlet port one as refrigerant inlet, and in the inlet/outlet port two other is as refrigerant outlet.This distributary division 14 can form by tube connector, perhaps can form by a plurality of coolant channels are set in metal or resin mass.
An entrance side that is connected to intermediate pressure expansion valve 15 in the refrigerant outlet of distributary division 14, and another outlet of distributary division 14 is connected to the entrance side of the high-pressure refrigerant flow path 16a of intermediate heat exchanger 16.Intermediate pressure expansion valve 15 is to become from radiator 13 mobile high-pressure refrigerant compression and expansions the thermal expansion valve of intermediate pressure refrigerant.
More specifically, intermediate pressure expansion valve 15 has the temperature sensing section of the outlet side of the intermediate pressure refrigerant flow path 16b that is arranged on intermediate heat exchanger 16.Expansion valve 15 is according to the degree of superheat of the cold-producing medium of the outlet side of the temperature and pressure sensing intermediate pressure refrigerant flow path 16b of the cold-producing medium of the outlet side of intermediate pressure refrigerant flow path 16b.Expansion valve 15 is by the opening degree (refrigerant flow) of mechanical mechanism control valve, so that the degree of superheat becomes default predetermined value.The outlet side of intermediate pressure expansion valve 15 is connected to the entrance side of intermediate pressure refrigerant flow path 16b.
Particularly, intermediate heat exchanger 16 adopts plate heat exchangers, and described plate heat exchanger comprises stacked a plurality of heat transfer plates and alternately is arranged in intermediate pressure refrigerant flow path 16b and high-pressure refrigerant flow path 16a between each heat transfer plate.Heat exchanger is designed to by heat transfer plate heat-shift between high-pressure refrigerant and intermediate pressure refrigerant.
Alternatively, heat exchanger 16 can adopt the double pipe heat exchanger structure, and described double pipe heat exchanger structure comprises the exterior tube that forms high-pressure refrigerant flow path 16a and the inner tube that is positioned at the formation intermediate pressure refrigerant flow path 16b of flow path 16a inside.Apparently, high-pressure refrigerant flow path 16a can form inner tube, and intermediate pressure refrigerant flow path 16b can form exterior tube.In addition, the refrigerant pipe of formation high-pressure refrigerant flow path 16a and intermediate pressure refrigerant flow path 16b can interconnect with heat-shift between described high-pressure refrigerant flow path 16a and intermediate pressure refrigerant flow path 16b.
The outlet side of the intermediate pressure refrigerant flow path 16b of intermediate heat exchanger 16 is connected to the suction ports side of above-mentioned high side compressors 11 (particularly, high side compressors structure 11a) via the check-valves (not shown).Therefore, the high side compressors structure 11a of present embodiment sucks the intermediate pressure refrigerant that flows from middle pressure refrigerant flowpath 16b and from the mixture of the intermediate pressure refrigerant of low-pressure side compressor 12 dischargings.
On the contrary, the outlet side of the high-pressure refrigerant flow path 16a of intermediate heat exchanger 16 is connected to the entrance side of inflated with low pressure valve 17.Inflated with low pressure valve 17 is for will reduce pressure and expand into the thermal expansion valve of low pressure refrigerant from the high-pressure refrigerant that radiator 13 flows out.Inflated with low pressure valve 17 has the basic structure identical with the basic structure of intermediate pressure expansion valve 15.
More specifically, inflated with low pressure valve 17 has the subsequently temperature sensing section of the refrigerant outlet side of described evaporimeter 18 that is arranged on.Expansion valve 17 is according to the degree of superheat of the cold-producing medium of the outlet side of the temperature and pressure sensing evaporimeter 18 of the cold-producing medium of the outlet side of evaporimeter 18, and the opening degree (refrigerant flow) by the mechanical mechanism control valve, so that the degree of superheat becomes default predetermined value.
The outlet side of inflated with low pressure valve 17 is connected to the cold-producing medium inflow side of evaporimeter 18.Evaporimeter 18 is the heat exchangers for heat absorption, described heat exchanger is heat-shift between the low pressure refrigerant that is depressurized by inflated with low pressure valve 17 and expands and the blow air that blowed and cycled through refrigerator by blower fan 18a, thereby shows endothermic effect by the evaporation low pressure refrigerant.Blower fan 18a is electric blower, and the revolution of described electric blower (amount of blow air) is by the control Control of Voltage from refrigerating device controller 20 outputs.
In addition, the refrigerant outlet port of evaporimeter 18 is connected to the suction ports side of low-pressure side compressor 12 (particularly, low-pressure side compressing mechanism 12a).
Next, the electric controller of present embodiment is described subsequently.Refrigerating device controller 20 by comprise for carry out that control is processed or the known microcomputer of the CPU of computing and be used within it storage program and data the memory circuit such as ROM or RAM, be used for control signal or control Voltage-output are formed to the output circuit of the device that is used for controlling, the input circuit and the power circuit that are transfused in it from the detection signal of each sensor.
The outlet side of refrigerating device controller 20 is connected to low-pressure side transverter 22, high-pressure side transverter 21, cooling fan 13a, the blower fan 18a etc. that controlled device is wanted in above conduct.Refrigerating device controller 20 is suitable for controlling these and wants each operation in the controlled device.
Refrigerating device controller 20 comprises the combination of wanting each control device of controlled device for control.The control that is used in the refrigerating device controller 20 wants each structure (hardware and software) of the operation of controlled device to be formed for controlling the control device of controlled each device.
In the present embodiment, the first discharging capacity control 20a has for the structure (hardware and software) of controlling the cold-producing medium discharge capacity of low-pressure side compressing mechanism 12a by the operation of control low-pressure side transverter 22.In addition, the second discharging capacity control 20b has for the structure (hardware and software) of controlling the cold-producing medium discharge capacity of high side compressors structure 11b by the operation of control high-pressure side transverter 21.
Therefore, can independently control the revolution of low-pressure side motor 12b and the revolution of high-pressure side motor 11b by the first discharging capacity control 20a and the second discharging capacity control 20b.Apparently, the first discharging capacity control 20a can be made of the different controllers that are used for refrigerating device controller 20 with the second discharging capacity control 20b.
On the contrary, the input side of refrigerating device controller 20 is connected to external air temperature sensor 23, the interior temperature sensor 24 of refrigerator etc.External air temperature sensor 23 is as the external air temperature checkout gear, and described external air temperature checkout gear is for detection of the external air temperature Tam at the air (outdoor air) of the refrigerator outside of radiator 13 places and high-pressure refrigerant heat-shift.Temperature sensor 24 is as temperature-detecting device in the refrigerator in the refrigerator, and temperature-detecting device is for detection of the air themperature Tfr in the blow air of evaporimeter 18 places and low pressure refrigerant heat-shift in the described refrigerator.Detection signal from these sensors is input to refrigerating device controller 20.
The input side of refrigerating device controller 20 is connected to guidance panel 30.Guidance panel 30 be provided with the operation request signal that acts on the output refrigeration machine or stop request signal the request signal output device operation/shutdown switch and with the temperature setting switch of the target temperature setting device that acts on setting freezing built-in temperature (target chilling temperature) Tset.Operation signal from these switches is input to refrigerating device controller 20.
The operation of the two-stage pressurization refrigerating circulatory device 10 with above structure in the present embodiment is described according to Fig. 2 next.At first, Fig. 2 has shown the flow chart of the control procedure of being carried out by refrigerating device controller 20.When the operation/shutdown switch of guidance panel 30 was opened (ON) with the output function request signal, control procedure began.
At first, in step S1, initialization tag, timer etc.Then, in following steps S2, be read into from the detection signal of temperature sensor 24 in external air temperature sensor 23 and the refrigerator with from the operation signal of the temperature setting switch of guidance panel 30 etc., then determine operator scheme according to the temperature T set that is set by temperature setting switch.Particularly, when target chilling temperature Tset is-10 ℃ or when higher, wherein the refrigeration pattern that is cooled under the temperature that the freshness that suppresses food reduces of FF is set.When target chilling temperature Tset is lower than-10 ℃, wherein carries out freezing freezing mode and be set.
Subsequently, operation proceeds to the step S3 that determines control model.Control model is that refrigeration pattern and frozen mode are common, therefore following explanation of omitting the control model of each operator scheme.
Particularly, in step S3, when deducting temperature difference T that the target chilling temperature Tset that set by temperature setting switch obtains greater than predetermined reference temperature difference KT from the air themperature Tfr that among step S2, reads, need to determine large capacity.On the contrary, when temperature difference T is equal to or less than predetermined reference temperature difference KT, determine the temperature of refrigerator inside near preset temperature Tset, therefore need to carry out the concrete control of capacity.
In most of the cases, after just starting refrigeration machine, be higher than target chilling temperature Tset as the temperature of the refrigerator inside of cooling space.Therefore, employed temperature difference T is the value that obtains by deduct target chilling temperature Tset from air themperature Tfr in the present embodiment.Yet, can be used as temperature difference T by the absolute value that deducts air themperature Tfr acquisition from target chilling temperature Tset.
When determining to need large capacity in step S3, operation proceeds to the step S4 that wherein carries out the operation under the refrigerating mode.In step S4, determine the revolution of high-pressure side motor 11b and low-pressure side motor 12b, so that the cold-producing medium discharge capacity of the cold-producing medium discharge capacity of low-pressure side compressor 12 and high side compressors 11 is maximized basically.
In following steps S5, determine that other wants the state of a control of controlled device in the refrigerating mode of refrigeration machine.For example, determine the revolution of cooling fan 13a and blower fan 18a, so that the ability that blows of cooling fan 13a and blower fan 18a is maximized basically.Then, operation proceeds to step S9.
On the contrary, when determining specifically to control the capacity of refrigeration machine in step S3, operation proceeds to the step S6 that wherein carries out the operation under the volume controlled pattern.In step S6, determine the cold-producing medium discharge capacity of low-pressure side compressor 12 according to the detection signal that in this step S2, reads and operation signal.
More specifically, in step S6, according to comprising that control temperature and the deviation of preset temperature, the key element of integration and differentiation determine the revolution of low-pressure side motor 12b, that is, and the revolution N2 of low-pressure side compressing mechanism 12a.
In following steps S7, determine the cold-producing medium discharge capacity of high side compressors 11 according to the cold-producing medium discharge capacity of the low-pressure side compressor 12 of in step S6, determining.
Particularly, in step S7, determine the revolution N1 of high side compressors structure 11a, so that the available capacity of being determined by following formula F 1 compares in the predetermined reference scope by following formula F 2 expressions:
Available capacity ratio=N2 * V2/N1 * V1 ... (F1)
1≤N2×V2/N1×V1≤3…(F2)
Wherein V1 is the discharge capacity of high side compressors structure 11a, and N1 is the revolution of high side compressors structure 11a, and V2 is the discharge capacity of low-pressure side compressing mechanism 12a, and N2 is the revolution of low-pressure side compressing mechanism 12a.
In following steps S8, determine the state of a control that other wants controlled device.For example, determine each the revolution among cooling fan 13a and the blower fan 18a, increase along with the increase of the revolution N2 of the low-pressure side compressing mechanism 12a that in step S6, determines so that it blows ability that then operation proceeds to step S9.
Then, in step S9, control signal is outputed to the controlled device of wanting of the output that is connected to controller from refrigerating device controller 20, and with the state of a control that obtains to determine in step S4-S8, then operation proceeds to step S10.
In step S10, when stopping request signal and outputed to refrigerating device controller 20 from guidance panel 30, each wants the operation of controlled device to be stopped, thereby stops the whole system of refrigeration machine fully.On the contrary, when output did not stop request signal, operation turned back to S2 after predetermined control circulation τ stops.
Therefore, when the operation/shutdown switch of guidance panel 30 is opened, the mixture of the intermediate pressure refrigerant that the high side compressors 11 in the two-stage pressurization refrigerating circulatory device 10 sucks, compression and discharging are flowed out from the intermediate pressure refrigerant of low-pressure side compressor 12 dischargings with from the intermediate pressure refrigerant flow path 16b of middle heat exchanger 16.
In addition, flow into the radiator 13 from the high-temperature high-pressure refrigerant of high side compressors 11 discharging, thereby and be cooled with the air exchange heat of the refrigerator outside that is blowed by cooling fan 13a.Shunted by distributary division 14 from the high-pressure refrigerant stream that radiator 13 flows out.Then, flowing to high-pressure refrigerant the intermediate pressure expansion valve 15 from distributary division 14 is depressurized and expands until this high-pressure refrigerant becomes intermediate pressure refrigerant.
At this moment, regulate the throttle opening of intermediate pressure expansion valve 15, so that the degree of superheat of the cold-producing medium in the exit of the intermediate pressure refrigerant flow path 16b of intermediate heat exchanger 16 becomes default predetermined value.In addition, flow among the intermediate pressure refrigerant flow path 16b of intermediate heat exchanger 16 by the intermediate pressure refrigerant of intermediate pressure expansion valve 15 decompressions.This cold-producing medium and the high-pressure refrigerant heat-shift that flow into from distributary division 14 the high-pressure refrigerant flow path 16a of intermediate heat exchanger 16, thus be heated, then be inhaled in the high side compressors 11.
On the contrary, the high-pressure refrigerant that flow into the high-pressure refrigerant flow path 16a of intermediate heat exchanger 16 from distributary division 14 is cooled by intermediate heat exchanger 16.The high-pressure refrigerant that flows from high-pressure refrigerant flow path 16a flow into the inflated with low pressure valve 17, and is depressurized and expands until this high-pressure refrigerant becomes low pressure refrigerant.At this moment, regulate the throttle opening of inflated with low pressure valve 17, so that the degree of superheat of the cold-producing medium in the exit of evaporimeter 18 becomes default predetermined value.
In addition, flow in the evaporimeter 18 by the low pressure refrigerant of inflated with low pressure valve 17 decompression, and from the blow air absorbing heat that cycles through described evaporimeter 18 and blowed by blower fan 18a to evaporate this low pressure refrigerant.Therefore, be blown into as the blow air in the refrigerator of cooling space and be cooled.The cold-producing medium that flows out from evaporimeter 18 is inhaled into the low-pressure side compressor 12.
The two-stage pressurization refrigerating circulatory device 10 of present embodiment operates as mentioned above, thereby forms above-mentioned economical refrigerating circulatory device, so that this refrigerating circulatory device not only can improve the compression efficiency of high side compressors structure, and can show following excellent effect.
At first, in the present embodiment, determine the cold-producing medium discharge capacity of low-pressure side compressing mechanism 12a according to external air temperature Tam, air themperature Tfr and predetermined temperature Tset, and determine in addition the cold-producing medium discharge capacity of high side compressors structure 11a according to the cold-producing medium discharge capacity of the low-pressure side compressing mechanism 12a that determines.Therefore, can easily determine the cold-producing medium discharge capacity of each compressing mechanism 11b and 12b.
At this moment, determine the cold-producing medium discharge capacity of high side compressors structure 11a, so that the available capacity ratio satisfies above-mentioned formula F 2.Therefore, can improve the coefficient of refrigerating performance (COP) of circulation with very easy control by simple structure, and need to be for detection of the pressure-detecting device of high-pressure side refrigerant pressure, intermediate pressure side refrigerant pressure or low-pressure side refrigerant pressure.
This at length is described at following use Fig. 3.Fig. 3 has shown that the variation of COP ratio is with respect to the curve map of the variation of available capacity ratio.Fig. 3 (a) is the curve map under the condition A of external air temperature Tam=38 ℃ and preset temperature Tset=-10 ℃.Fig. 3 (b) is the curve map under the condition B of external air temperature Tam=10 ℃ and preset temperature Tset=-25 ℃.
The ratio of the COP of the two-stage pressurization refrigerating circulatory device 10 of the COP that term used herein " COP ratio " expression obtains when middle refrigerant pressure is set to the predetermined value that is different from the geometric mean between high-pressure side refrigerant pressure and the low-pressure side refrigerant pressure and present embodiment.
As can seeing from Fig. 3, at COP under any condition than being not less than 1 and be not more than the peak value that has the available capacity ratio in 3 the scope.This means that intermediate refrigerant pressure can be near the geometric mean between high-pressure side refrigerant pressure and the low-pressure side refrigerant pressure by being not less than 1 and be not more than and set effective Capacity Ratio in 3 the scope.
Therefore, the two-stage of present embodiment pressurization refrigerating circulatory device 10 can very easily improve COP with simple structure under the control.Even under any condition, at the peak value that has the COP ratio near 2 available capacity than the place.In control step S7, can be by being not less than 1.5 and be not more than and set effective Capacity Ratio in 2.5 the scope and further improve COP.
Be similar to this embodiment, for example, in being applied to the kind of refrigeration cycle of refrigeration machine, compare with the kind of refrigeration cycle that is applied to air regulator, pressure reduction between high-pressure side refrigerant pressure and the low-pressure side refrigerant pressure becomes larger, thereby trends towards increasing the consumed power of compressor.Therefore, the raising of COP is very useful in being applied to the kind of refrigeration cycle of refrigeration machine.
In this embodiment, no matter the cold-producing medium discharge capacity of high side compressors structure 11a and low-pressure side compressing mechanism 12a how, regulate the throttle opening of intermediate pressure expansion valve 15, so that the cold-producing medium in the exit of the intermediate pressure refrigerant flow path 16b of intermediate heat exchanger 16 has enough degrees of superheat.This layout can be avoided the problem of the liquid compression of high side compressors structure 11a.In addition, regulate the degree of superheat of inflated with low pressure valve 17, so that the cold-producing medium in the exit of evaporimeter 18 has enough degrees of superheat, therefore can also avoid the problem of the liquid compression of low-pressure side compressing mechanism 12a.
Therefore, even simple structure also can improve the reliability of high side compressors structure 11a and low-pressure side compressing mechanism 12a, that is, improve the reliability of whole two-stage pressurization refrigerating circulatory device.
In this embodiment, according to the cold-producing medium discharge capacity of definite low-pressure side compressing mechanism 12a such as external air temperature Tam, so that can directly determine according to external air temperature Tam etc. the cold-producing medium evaporating pressure of evaporimeter 18.Therefore, being blown into the air themperature Tfr of the blow air in the refrigerator can be easily near preset temperature Tset.
The two-stage pressurization refrigerating circulatory device 10 of present embodiment comprises intermediate heat exchanger 16, and the intermediate pressure refrigerant that flows from middle pressure expansion valve 15 by this can be heated easily to become vapor phase refrigerant by the high-pressure refrigerant by distributary division 14 shuntings.Therefore, can improve more reliably the reliability of two-stage pressurization refrigerating circulatory device.
Can be by the high-pressure refrigerant of the intermediate pressure refrigerant cooling of flowing out from middle pressure expansion valve 15 by distributary division 14 shuntings, thus increase heat content between the cold-producing medium in cold-producing medium and the exit of evaporimeter 18 of porch of evaporimeter 18 poor with increase by the shown refrigerating capacity of evaporimeter 18.Therefore, can further improve the COP of two-stage pressurization refrigerating circulatory device.
In this embodiment, when in control step S3, determining that refrigerating circulatory device is not to be in the lower time of state that just starts refrigeration machine, determine the cold-producing medium discharge capacity of high side compressors structure 11a according to the cold-producing medium discharge capacity of low-pressure side compressing mechanism 12a.Therefore, after just starting refrigeration machine, the cold-producing medium discharge capacity of the cold-producing medium discharge capacity of low-pressure side compressing mechanism 12a and high side compressors structure 11a is maximized basically, so that can carry out for the operator scheme of cooling off fast cooling space.
In this embodiment, adopt the fixed displacement compressing mechanism as high side compressors structure 11a and low-pressure side compressing mechanism 12a, so that the discharge capacity V1 of compressing mechanism and V2 can be constant.Therefore, after the revolution N2 that determines low-pressure side compressing mechanism 12a, can only easily make available capacity than in the scope of expectation by the revolution N1 that regulates high side compressors structure 11a.
(the second embodiment)
Shown in the overall structure schematic diagram of Fig. 4, below in the mode of example the second embodiment is described, be different from the first embodiment, described the second embodiment comprises high side compressors structure 11a and the low-pressure side compressing mechanism 12a that is configured to by compressor with variable displacement.In addition, in this embodiment, high-pressure side motor 11b and low-pressure side motor 12b are removed, so that two compressing mechanism 11a and 12a are rotatably driven by share motor 19.In Fig. 4, the parts identical or equivalent with the parts of the first embodiment are represented by identical Reference numeral.
More specifically, in this embodiment, high side compressors structure 11a and low-pressure side compressing mechanism 12a adopt variable swash plate capacity compressors structure.Variable swash plate capacity compressors structure changes the controlled pressure Pc of swash plate chamber by slant plate type compressor, thereby changes the inclination angle of swash plate, in order to change the stroke of piston, discharge capacity is roughly changing in 0 to 100% the scope continuously by this.
Change the high-pressure refrigerant that will be introduced in the swash plate chamber and each the introducing amount in the low pressure refrigerant by changing each opening degree among electromagnetic capacity control valve 11c and the 12c, thereby regulate the controlled pressure Pc of the inside of the corresponding swash plate chamber among the high side compressors structure 11a low-pressure side compressing mechanism 12a each.The operation of electromagnetic capacity control valve 11c and 12c is subject to from the control of the control electric current of the first discharging capacity control 20a of refrigerating device controller 20 and the second discharging capacity control 20b output.
Be similar to high-pressure side motor 11b and low-pressure side motor 12b, motor 19 is AC motor, and the operation of described motor (revolution) is by the AC current control from transverter 25 outputs.Transverter 25 outputs have the alternating current of the frequency corresponding with the control signal of exporting from refrigerating device controller 20.
In addition, the rotary driving force of exporting from the motor 19 of this embodiment is delivered to compressing mechanism 11a and 12a via belt pulley and belt.Therefore, the ratio of the revolution N1 of the revolution N2 of low-pressure side compressing mechanism 12a and high side compressors structure 11a in the present embodiment, that is, N2/N1 is set to steady state value.In this embodiment, the ratio N2/N1 of revolution is set to and is essentially 1, so that the revolution N2 of low-pressure side compressing mechanism 12a is substantially equal to the revolution N1 of high side compressors structure 11a.
Other structure of present embodiment is identical with operation with the structure of the first embodiment with operation.Therefore, be similar to the first embodiment, the two-stage pressurization refrigerating circulatory device 10 of present embodiment also can very easily improve the coefficient of performance (COP) of circulation with simple structure under the control.In addition, the above-mentioned simple structure of present embodiment can improve the reliability of high side compressors structure 11a and low-pressure side compressing mechanism 12a,, improves the reliability of whole two-stage pressurization refrigerating circulatory device that is.
In this embodiment, the compressor with variable displacement structure is used as high side compressors structure 11a and low-pressure side compressing mechanism 12a, can independently change by this discharge capacity V1 and the V2 of compressing mechanism 11a and 12a.Even when the revolution N1 of compressing mechanism 11a and 12a is identical value with N2, also can be with available capacity than (N2 * V2/N1 * V1) easily changes to the value of expectation.
(other embodiment)
The present invention is not limited to above embodiment, and can carry out various modifications and change to these embodiment in the case of without departing from the spirit and scope of protection of the present invention.
(1) although the loop structure of two-stage pressurization refrigerating circulatory device adopts intermediate heat exchanger 16 in above embodiment, the present invention is not limited to this.For example, can remove intermediate heat exchanger 16, and the cold-producing medium that can be provided for flowing from middle pressure expansion valve 15 is separated into the middle gas-liquid separator of liquid and gas.
Can be inhaled in the high side compressors 11 by the vapor phase refrigerant of middle gas-liquid separator separates.In this case, intermediate pressure expansion valve 15 can be removed, as an alternative, the fixed restriction device can be adopted.In addition, distributary division 14 can be removed to allow the liquid phase refrigerant by middle gas-liquid separator separates to flow in the inflated with low pressure valve 17, in order to construct economical refrigerating circulatory device.
(2) in above embodiment, in control step S6 shown in Figure 2, according to the cold-producing medium discharge capacity of definite low-pressure side compressors 12 such as external air temperature Tam.In control step S7, in the mode of example, determine the cold-producing medium discharge capacity of high side compressors 11 according to the cold-producing medium discharge capacity of low-pressure side compressor 12.Alternatively, similarly, can in control step S6, determine the cold-producing medium discharge capacity of high side compressors 11, and can in control step S7, determine the cold-producing medium discharge capacity of low-pressure side compressor 12.
In control step S6, in the mode of example, determine the cold-producing medium discharge capacity of low-pressure side compressor 12 according to external air temperature Tam, air themperature Tfr and preset temperature Tset.Alternatively, can use among external air temperature Tam, air themperature Tfr and the preset temperature Tset at least one to determine the cold-producing medium discharge capacity of low-pressure side compressor 12.
(3) in above embodiment, in the mode of example, adopt thermal expansion valve as intermediate pressure expansion valve 15 and inflated with low pressure valve 17.Alternatively, electric expansion valve can be used as intermediate pressure expansion valve 15 and inflated with low pressure valve 17.
For example, in addition, checkout gear can be set with the temperature and pressure of the cold-producing medium of the outlet side of detection intermediate pressure refrigerant flow path 16b, and can control the operation of intermediate pressure expansion valve 15, so that the degree of superheat of the cold-producing medium of the outlet side of intermediate pressure refrigerant flow path 16b becomes default predetermined value.In addition, can increase another checkout gear with the temperature and pressure of the cold-producing medium of the outlet side of detection evaporimeter 18, and can control the operation of low-pressure side expansion valve 17, so that the degree of superheat of the cold-producing medium of the outlet side of evaporimeter 18 becomes default predetermined value.
(4) in above embodiment, in the mode of example, the two-stage of present embodiment pressurization refrigerating circulatory device 10 is applied to refrigeration machine, but cloth of the present invention is confined to this.For example, refrigerating circulatory device can be applied to air regulator, refrigerator etc.Alternatively, refrigerating circulatory device can be applied to refrigeration and the refrigerated container of mobile object (vehicle, ship) etc.
Still air adjuster, refrigerator and refrigerator are used for the energy of drive compression machine 11 and 12 easily from acquisitions such as commercial powers.Yet this refrigeration and the refrigerated container that is applied to mobile object has limited driving-energy.Therefore, it is very useful to fill the raising of 10 COP that realize by the two-stage among the present invention pressurization kind of refrigeration cycle.
(5) in above control step S3, by comparing temperature difference T and need determining whether large capacity with reference to temperature difference KT.Determine that mode is not limited to this.
For example, open (ON) afterwards at operation/shutdown switch, at first, determine the revolution of compressing mechanism 11a and 12a, so that the difference between air themperature Tfr and the target chilling temperature Tset reduces.In this control, as the variation delta Tfr of the air themperature Tfr of time per unit during greater than predetermined reference temperature variation delta KTfr, determine that refrigeration machine is in the state that just starts after the refrigeration machine.When Δ Tfr is equal to or less than predetermined reference temperature variation delta KTfr, can determine that refrigeration machine is in normal operating state.
(6) when using azeotropic cold-producing medium or false azeotropic cold-producing medium as cold-producing medium, can detect the temperature difference between the cold-producing medium in exit of the cold-producing medium of porch of intermediate pressure refrigerant flow path 16b and intermediate pressure refrigerant flow path 16b.Then, can regulate the opening degree (flow of cold-producing medium) of intermediate pressure expansion valve 15, so that the described temperature difference becomes default predetermined value.
Can use intermediate pressure refrigerant flow path 16b is connected to the surface temperature of refrigerant pipe of another parts as refrigerant temperature.
(7) in above the first embodiment, in step S5 and S7, other device except low-pressure side compressor and high side compressors (cooling fan 13a and blower fan 18a) is controlled according to control model, but can be controlled according to operator scheme.For example, can control described device so that the ability that blows of cooling fan 13a and blower fan 18a is maximized in the refrigeration pattern basically, and so that the ability that blows of cooling fan 13a and blower fan 18a under frozen mode, reduce.
(8) in above embodiment, in step S6, use control temperature and preset temperature, that is, under so-called PID control, the revolution of control low-pressure side motor 12b.Alternatively, can determine in the following manner the revolution of low-pressure side motor 12b according to external air temperature Tam, air themperature Tfr and preset temperature Tset with reference to pre-stored control chart in the memory circuit of refrigerating device controller 20, that is, the revolution N2 of low-pressure side compressing mechanism 12a.Can determine revolution N2, so that the cold-producing medium discharge capacity of low-pressure side compressor 12 is along with the reduction of the increase of the increase of external air temperature Tam, air themperature Tfr or preset temperature Tset and increase.
(9) in above the second embodiment, in the mode of example, high side compressors structure 11a and low-pressure side compressing mechanism 12a use a motor 19 driven as drive unit.Alternatively, different drive units can be used for corresponding compressing mechanism 11a and 12a, and engine (internal combustion engine) can be used as drive unit.
Claims (8)
1. two-stage pressurization refrigerating circulatory device comprises:
Low-pressure side compressing mechanism (12a), described low-pressure side compressing mechanism is compressed into intermediate pressure refrigerant with low pressure refrigerant, and the cold-producing medium after the described low-pressure side compressing mechanism discharging compression;
High side compressors structure (11a), described high side compressors structure will be compressed into from the intermediate pressure refrigerant of described low-pressure side compressing mechanism (12a) discharging high-pressure refrigerant with the cold-producing medium after described high side compressors structure discharging compression;
Radiator (13), described radiator outdoor air and from heat-shift between the high-pressure refrigerant of described high side compressors structure (11a) discharging to distribute the heat from cold-producing medium;
Intermediate pressure expansion valve (15), described intermediate pressure expansion valve will reduce pressure from the high-pressure refrigerant that described radiator (13) flows out and expand into intermediate pressure refrigerant, so that intermediate pressure refrigerant flow into the suction side of described high side compressors structure (11a);
Inflated with low pressure valve (17), described inflated with low pressure valve will reduce pressure from the high-pressure refrigerant that described radiator (13) flows out and expand into low pressure refrigerant;
Evaporimeter (18), described evaporimeter by with will be blown into air exchange heat in the cooling space and evaporate by described inflated with low pressure valve (17) decompression and the low pressure refrigerant that expands, and the cold-producing medium after the evaporation is flow in the suction side of described low-pressure side compressing mechanism (12a);
The first discharging capacity control (20a), described the first discharging capacity control is configured to determine at least one the cold-producing medium discharge capacity in described high side compressors structure (11a) and the described low-pressure side compressing mechanism (12a), so that described cold-producing medium discharge capacity is located to increase with the external air temperature (Tam) of the outdoor air of high-pressure refrigerant heat-shift with at least one the increase of locating at described evaporimeter (18) with the air themperature (Trf) of the air of low pressure refrigerant heat-shift at described radiator (13) according to being used for; And
The second discharging capacity control (20b), described the second discharging capacity control is configured to determine described high side compressors structure (11a) and described low-pressure side compressing mechanism (the cold-producing medium discharge capacity of another compressing mechanism among the 12a according to the cold-producing medium discharge capacity of a described compressing mechanism of determining
Wherein said the second discharging capacity control (20b) is determined the cold-producing medium discharge capacity of described another compressing mechanism, so that when V1 be the discharge capacity of high side compressors structure (11a), N1 is the revolution of described high side compressors structure (11a), V2 is the discharge capacity of described low-pressure side compressing mechanism (12a), and N2 is defined as the available capacity of N2 * V2/N1 * V1 than in the predetermined reference scope when being the revolution of described low-pressure side compressing mechanism (12a).
2. two-stage according to claim 1 pressurization refrigerating circulatory device, wherein:
Described intermediate pressure expansion valve (15) decompression and a high-pressure refrigerant stream that expands and locate to be shunted at distributary division (14) are shunted at described distributary division (14) from the high-pressure refrigerant that described radiator (13) flows out;
Described inflated with low pressure valve (17) decompression and another high-pressure refrigerant stream that expands and locate to be shunted at described distributary division (14);
Described refrigerating circulatory device also comprises intermediate heat exchanger (16), in described intermediate heat exchanger (16) between by described intermediate pressure expansion valve (15) decompression and the low pressure refrigerant that expands and another high-pressure refrigerant of being shunted by described distributary division (14) heat-shift.
3. two-stage according to claim 1 and 2 pressurization refrigerating circulatory device, wherein, a described compressing mechanism is low-pressure side compressing mechanism (12a), and described another compressing mechanism is high side compressors structure (11a).
4. each described two-stage pressurization refrigerating circulatory device according to claim 1-3, wherein, when the absolute value of the temperature difference (Δ T) between the target chilling temperature (Tset) of the air themperature (Tfr) at described evaporimeter place and described cooling space was equal to or less than the predetermined reference temperature difference (Δ KT), described the second discharging capacity control (20b) was determined the cold-producing medium discharge capacity of described another compressing mechanism according to the cold-producing medium discharge capacity of a described compressing mechanism.
5. two-stage according to claim 4 pressurization refrigerating circulatory device, wherein, when the air themperature (Trf) at described evaporimeter place is higher than described target chilling temperature (Tset), and when the absolute value of the temperature difference (Δ T) between the target chilling temperature (Tset) of the air themperature (Tfr) at described evaporimeter place and described cooling space was equal to or less than the described predetermined reference temperature difference (Δ KT), described the second discharging capacity control (20b) was determined the cold-producing medium discharge capacity of described another compressing mechanism according to the cold-producing medium discharge capacity of a described compressing mechanism.
6. each described two-stage pressurization refrigerating circulatory device according to claim 1-5, wherein, in described high side compressors structure (11a) and the described low-pressure side compressing mechanism (12a) each is by having fixed discharge capacity (V2, V1) fixed displacement compressing mechanism structure forms, and described refrigerating circulatory device also comprises:
Rotatably drive the high-pressure side motor (11b) of described high side compressors structure (11a); With
Rotatably drive the low-pressure side motor (12b) of described low-pressure side compressing mechanism (12a),
The revolution of the revolution of wherein said high-pressure side motor (11a) and described low-pressure side motor (12a) can independently be controlled.
7. each described two-stage pressurization refrigerating circulatory device according to claim 1-5, wherein, in described high side compressors structure (11a) and the described low-pressure side compressing mechanism (12a) each is by having variable discharge capacity (V2, V1) compressor with variable displacement structure structure forms, and
The discharge capacity (V1) of described high side compressors structure (11a) and the discharge capacity (V2) of described low-pressure side compressing mechanism (12a) can independently be controlled.
8. each described two-stage pressurization refrigerating circulatory device according to claim 1-7, wherein, described the second discharging capacity control (20b) is determined the cold-producing medium discharge capacity of described another compressing mechanism, so that described available capacity is than satisfying following formula:
1≤N2×V2/N1×V1≤3。
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010154680 | 2010-07-07 | ||
| JP2010-154680 | 2010-07-07 | ||
| PCT/JP2011/003857 WO2012004987A1 (en) | 2010-07-07 | 2011-07-06 | Two-stage pressure buildup refrigeration cycle system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102971592A true CN102971592A (en) | 2013-03-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011800336229A Pending CN102971592A (en) | 2010-07-07 | 2011-07-06 | Two-stage pressure buildup refrigeration cycle system |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20130104584A1 (en) |
| JP (1) | JPWO2012004987A1 (en) |
| CN (1) | CN102971592A (en) |
| DK (1) | DK201370039A (en) |
| WO (1) | WO2012004987A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105579793A (en) * | 2013-09-11 | 2016-05-11 | 株式会社电装 | Expansion valve |
| CN106796061A (en) * | 2014-09-05 | 2017-05-31 | 株式会社电装 | Two grades of boosting type refrigeration EGRs |
| CN110500801A (en) * | 2019-08-28 | 2019-11-26 | 西安陕鼓动力股份有限公司 | Industrial refrigeration system design method |
| CN110553834A (en) * | 2019-09-09 | 2019-12-10 | 广州兰石技术开发有限公司 | Accelerated life test system for refrigeration valve |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6396662B2 (en) * | 2013-03-15 | 2018-09-26 | ダイキン アプライド アメリカズ インコーポレィティッド | Refrigeration apparatus and control device for refrigerator |
| KR102122499B1 (en) * | 2013-07-02 | 2020-06-12 | 엘지전자 주식회사 | A cooling system and a control method the same |
| US9696067B2 (en) * | 2013-09-07 | 2017-07-04 | Trane International Inc. | Apparatus and method for controlling indoor airflow for heat pumps |
| JP6207958B2 (en) * | 2013-10-07 | 2017-10-04 | サンデンホールディングス株式会社 | Air conditioner for vehicles |
| CN108027176B (en) * | 2015-09-15 | 2020-01-21 | 株式会社电装 | Multistage compression refrigeration cycle device |
| CN106595107A (en) * | 2016-12-13 | 2017-04-26 | 湖南凯利制冷设备有限公司 | Intermediate cooling device and double-stage compression refrigerating system |
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| CN113983712B (en) * | 2021-10-22 | 2023-05-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Unit operation control method and device, two-stage unit and refrigeration equipment |
| JP7436727B1 (en) | 2023-04-24 | 2024-02-22 | コベルコ・コンプレッサ株式会社 | refrigeration system |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02140477A (en) * | 1988-11-18 | 1990-05-30 | Hitachi Ltd | Two-stage compressor |
| JPH06229637A (en) * | 1993-01-29 | 1994-08-19 | Sanyo Electric Co Ltd | Device for two-stage compression refrigeration |
| JP2002327690A (en) * | 2001-04-27 | 2002-11-15 | Daikin Ind Ltd | Two-stage compressor |
| JP2004183913A (en) * | 2002-11-29 | 2004-07-02 | Mitsubishi Electric Corp | Air conditioner |
| JP2004278824A (en) * | 2003-03-13 | 2004-10-07 | Hitachi Ltd | Refrigeration cycle device and air conditioner |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3164626B2 (en) * | 1992-01-27 | 2001-05-08 | 松下電器産業株式会社 | Two-stage compression refrigeration cycle device |
| KR100389271B1 (en) * | 2001-03-17 | 2003-06-27 | 진금수 | Heat pump apparatus |
| JP2004101145A (en) * | 2002-09-12 | 2004-04-02 | Denso Corp | Vapor compression type refrigerator and sticking detector for compressor |
| US6931871B2 (en) * | 2003-08-27 | 2005-08-23 | Shaw Engineering Associates, Llc | Boosted air source heat pump |
| JP2008032336A (en) * | 2006-07-31 | 2008-02-14 | Sanyo Electric Co Ltd | Two-stage expansion refrigeration apparatus |
| JP2008106738A (en) * | 2006-09-29 | 2008-05-08 | Fujitsu General Ltd | Rotary compressor and heat pump system |
| JP5018496B2 (en) * | 2008-01-16 | 2012-09-05 | ダイキン工業株式会社 | Refrigeration equipment |
-
2011
- 2011-07-06 CN CN2011800336229A patent/CN102971592A/en active Pending
- 2011-07-06 JP JP2012523527A patent/JPWO2012004987A1/en active Pending
- 2011-07-06 US US13/808,185 patent/US20130104584A1/en not_active Abandoned
- 2011-07-06 WO PCT/JP2011/003857 patent/WO2012004987A1/en active Application Filing
-
2013
- 2013-01-25 DK DKPA201370039A patent/DK201370039A/en not_active Application Discontinuation
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02140477A (en) * | 1988-11-18 | 1990-05-30 | Hitachi Ltd | Two-stage compressor |
| JPH06229637A (en) * | 1993-01-29 | 1994-08-19 | Sanyo Electric Co Ltd | Device for two-stage compression refrigeration |
| JP2002327690A (en) * | 2001-04-27 | 2002-11-15 | Daikin Ind Ltd | Two-stage compressor |
| JP2004183913A (en) * | 2002-11-29 | 2004-07-02 | Mitsubishi Electric Corp | Air conditioner |
| JP2004278824A (en) * | 2003-03-13 | 2004-10-07 | Hitachi Ltd | Refrigeration cycle device and air conditioner |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105579793A (en) * | 2013-09-11 | 2016-05-11 | 株式会社电装 | Expansion valve |
| CN106796061A (en) * | 2014-09-05 | 2017-05-31 | 株式会社电装 | Two grades of boosting type refrigeration EGRs |
| CN106796061B (en) * | 2014-09-05 | 2020-03-03 | 株式会社电装 | Two-stage boosting type refrigeration cycle device |
| CN110500801A (en) * | 2019-08-28 | 2019-11-26 | 西安陕鼓动力股份有限公司 | Industrial refrigeration system design method |
| CN110553834A (en) * | 2019-09-09 | 2019-12-10 | 广州兰石技术开发有限公司 | Accelerated life test system for refrigeration valve |
Also Published As
| Publication number | Publication date |
|---|---|
| US20130104584A1 (en) | 2013-05-02 |
| WO2012004987A1 (en) | 2012-01-12 |
| JPWO2012004987A1 (en) | 2013-09-02 |
| DK201370039A (en) | 2013-01-25 |
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