CN107110586A - Refrigerating plant - Google Patents
Refrigerating plant Download PDFInfo
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- CN107110586A CN107110586A CN201580072558.3A CN201580072558A CN107110586A CN 107110586 A CN107110586 A CN 107110586A CN 201580072558 A CN201580072558 A CN 201580072558A CN 107110586 A CN107110586 A CN 107110586A
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- Prior art keywords
- refrigerant
- refrigerating plant
- heat source
- source side
- 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
- F25B45/00—Arrangements for charging or discharging refrigerant
-
- 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
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- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Refrigerating plant (1) has refrigerant loop (10), the refrigerant loop connects heat source side component (2) by pipe arrangement and at least one is formed using side component (4), and refrigerant is circulated wherein, the heat source side component has compressor (21), it is used as the heat source side heat exchanger (23) and subcooler (22) of condenser function, this has by the use of side expansion valve (41) by the use of side component and is used as the utilization side heat exchanger (42) of evaporator function, wherein, the refrigerating plant (1) possesses determining amount of refrigerant portions (3), it judges the refrigerant amount for being filled in refrigerant loop (10) using the temperature efficiency (T) of subcooler (22), the temperature efficiency of the subcooler is by value obtained from the degree of subcooling of the refrigerant in the exit of subcooler (22) divided by the maximum temperature difference of subcooler (22), determining amount of refrigerant portions (3) obtain the operating condition of the refrigerating plant (1), refrigerant amount be determined with may turn into erroneous judgement in the case of without refrigerant amount judgement.
Description
Technical field
The present invention relates to a kind of refrigerating plant for the refrigerant amount for judging refrigerant loop.
Background technology
In refrigerating plant, when producing the deficiency excessively of refrigerant amount, the ability for producing refrigerating plant can be caused to decline, tie
The damage of structure equipment.Therefore, in order to prevent the generation of such unfavorable condition, there is the refrigerant possessed to being filled in refrigerating plant
The refrigerating plant of the excessively not enough function of being judged of amount.
As the decision method of the lack of refrigerant in conventional refrigerating plant, for example, propose following refrigerating plant：
The refrigerating plant calculates the entrance refrigerant temperature of subcooler and the temperature difference of outlet refrigerant temperature, when the temperature difference phase
Than when setting value is reduced, being determined as refrigerant leakage (for example, referring to patent document 1).
Look-ahead technique document Prior Art
Patent document
Patent document 1：Japanese Unexamined Patent Publication 9-105567 publications
The content of the invention
The invention problem to be solved
But, in the conventional refrigerating plant described in patent document 1, due to being sentenced using the change of degree of subcooling
The deficiency of refrigerant amount is determined, so in the judgement that refrigerant is leaked, easily producing erroneous judgement.Because degree of subcooling can basis
The operating condition of refrigerating plant and significantly change.
The present invention is made using problem as described above as background, its object is to obtain one kind can precision it is good
Ground carries out the refrigerating plant of the judgement of refrigerant amount.
Means for solving the problems
The refrigerating plant of the present invention has refrigerant loop, and the refrigerant loop is by pipe arrangement connection heat source side component and at least
1 is formed using side component, and refrigerant is circulated wherein, and the heat source side component has compressor, sent out as condenser
The heat source side heat exchanger and subcooler of function are waved, it is described to have by the use of side component by the use of side expansion valve and be used as evaporator
The utilization side heat exchanger of function, wherein, the refrigerating plant possesses determining amount of refrigerant portions, the determining amount of refrigerant
Portion judges to be filled in the refrigerant amount of refrigerant loop, the temperature effect of the subcooler using the temperature efficiency of subcooler
Rate is by value obtained from the degree of subcooling of the refrigerant in the exit of subcooler divided by the maximum temperature difference of subcooler, system
Cryogen amount determination unit obtains the operating condition of the refrigerating plant, and the situation of erroneous judgement may be turned into being determined with for refrigerant amount
Under, without the judgement of refrigerant amount.
Invention effect
According to the refrigerating plant of the present invention, can precision carry out the judgement of refrigerant amount well.
Brief description of the drawings
Fig. 1 is an example of the refrigerant loop for the refrigerating plant for schematically describing embodiments of the present invention 1
Figure.
Fig. 2 is the figure of an example of the structure for the refrigerating plant for schematically describing embodiments of the present invention 1.
Fig. 3 be the refrigerating plant described in Fig. 1 refrigerant amount it is suitable when p-h line charts an example.
One example of p-h line charts when Fig. 4 is the short of refrigerant of the refrigerating plant described in Fig. 1.
Fig. 5 is refrigerant amount, the degree of subcooling and refrigeration of the 1st subcooler for illustrating the refrigerating plant described in Fig. 1
The figure of the relation of the operating condition of device.
Fig. 6 is illustrated in the refrigerating plant described in Fig. 1, and when refrigerant amount is appropriate amount, refrigerant presses heat source side
The figure of one example of the temperature change of refrigerant when heat exchanger, receiver, the sequential flowing of air subcooler.
Fig. 7 is refrigerant amount, the temperature efficiency and refrigeration of the 1st subcooler for illustrating the refrigerating plant described in Fig. 1
The figure of the relation of the operating condition of device.
Fig. 8 is for illustrating in the determining amount of refrigerant of present embodiment, in the situation that compressor is frequency-changeable compressor
The lower size according to low pressure and without the figure of determining amount of refrigerant.
Fig. 9 is for illustrating in the determining amount of refrigerant of present embodiment, in the situation that compressor is constant speed compressor
The lower size according to low pressure and without the figure of determining amount of refrigerant.
Figure 10 is the figure of the air quantity and an example of the relation of temperature efficiency threshold value that represent heat source side fan.
Figure 11 be illustrate before starting compressor and starting compressor after condensation temperature, external air temperature, the 1st supercooling
The figure of the outlet temperature of device and the relation of temperature efficiency.
Figure 12 is the figure of an example of the determining amount of refrigerant action for illustrating the refrigerating plant described in Fig. 1.
Figure 13 is Fig. 1 variation 1.
Embodiment
Hereinafter, referring to the drawings, embodiments of the present invention are illustrated.In addition, in the various figures, to identically or comparably
Part mark identical reference, suitably omit or simplify its explanation.In addition, for the structure described in each figure
Say, its shape, size and configuration etc. can be changed suitably within the scope of the invention.
Embodiment 1.
[refrigerating plant]
Fig. 1 is an example of the refrigerant loop for the refrigerating plant for schematically describing embodiments of the present invention 1
Figure.Refrigerating plant 1 described in Fig. 1 is operated by carrying out the kind of refrigeration cycle of steam compression type, so as to carry out such as room, storehouse
The indoor cooling such as storehouse, show cabinet or refrigerator.Refrigerating plant 1 for example including a heat source side component 2 and with heat source side component 2
Two be connected in parallel utilize side component 4.Heat source side component 2 with using side component 4 by liquid refrigerant extend pipe arrangement 6 and
Gas refrigerant extension pipe arrangement 7 is connected, so that being formed makes the refrigerant loop 10 of refrigerant circulation.It is filled in present embodiment
R410A of the refrigerant of refrigerant loop 10 for example as the mix refrigerant of HFC series.In addition, in the example in fig 1,
Describe a heat source side component 2 and two utilize side component 4, but heat source side component 2 can also be more than two, utilize side group
Part 4 can also be one or more than three.In the case where heat source side component 2 is many, the capacity of many heat source side components 2
Both can be with identical, can also be different.In addition, in the case where being many using side component 4, many capacity using side component 4
Both can be with identical, can also be different.In the following description, the refrigerating plant 1 that refrigerant carries out heat exchange with air is carried out
Illustrate the refrigerating plant that heat exchange is carried out but it is also possible to be fluids such as refrigerant and water, refrigerant or refrigerating mediums.
[utilizing side component]
The indoor assembly of interior is for example disposed on using side component 4, possesses a part for composition refrigerant loop 10
Utilize side refrigerant loop 10a and utilization side control unit 32.Using side refrigerant loop 10a using side expansion valve 41 and profit
With side heat exchanger 42.Adjusted using side expansion valve in the flow using the side refrigerant loop 10a refrigerants flowed for 41 pairs
It is whole, constituted such as by electric expansion valve or temperature-type expansion valve.In addition, thermal source can also be disposed in using side expansion valve 41
Side component 2, in this case, the 1st subcooler 22 and the hydraulic fluid side of heat source side component 2 is for example disposed in using side expansion valve 41
Between stop valve 28.It is, for example, to be configured to include the fin tube type heat exchange of heat-transfer pipe and multiple fins using side heat exchanger 42
Device, and it is used as the evaporator function for evaporating refrigerant.
It is equipped in the vicinity using side heat exchanger 42 using crosswind fan 43, utilization crosswind fan 43 is to utilizing side heat
Exchanger 42 blows air.Using crosswind fan 43 such as being configured to include centrifugal fan or multi blade fan, and by omitting
The motor driving of diagram.The air output to the air blowed using side heat exchanger 42 can be adjusted using crosswind fan 43.
[heat source side component]
The heat source side refrigerant loop 10b of a part of the heat source side component 2 for example including composition refrigerant loop 10, the 1st
Infusion circuit 71, the 2nd infusion circuit 73 and heat source side control unit 31.In addition, in the following description, to the 1st injection
The example of the infusion circuit 73 of loop 71 and the 2nd is illustrated, but refrigerating plant 1 can also be with the 1st infusion circuit 71 and
The structure of any one party in 2nd infusion circuit 73.
Heat source side refrigerant loop 10b includes compressor 21, heat source side heat exchanger 23, receiver 25, the 1st subcooler
22nd, hydraulic fluid side stop valve 28, gas side stop valve 29 and reservoir 24.1st infusion circuit 71 makes from heat source side heat exchanger
23 are returned to a part for the refrigerant conveyed using side heat exchanger 42 from heat source side refrigerant loop 10b branches
The middle splenium of compressor 21, including injection rate adjustment valve 72.2nd infusion circuit 73 makes from heat source side heat exchanger 23 to utilization
A part for the refrigerant that side heat exchanger 42 is conveyed makes it to the suction of compressor 21 from heat source side refrigerant loop 10b branches
Enter portion's inflow, including capillary 74 and suction injection magnetic valve 75.
Compressor 21 is, for example, the frequency-changeable compressor being controlled using frequency converter, operating frequency can be made arbitrarily to change
To make capacity (time per unit sends out the amount of refrigerant) change.In addition, compressor 21 can also be entered with 50Hz or 60Hz
The constant speed compressor that action is made.In addition, describing the example with a compressor 21 in Fig. 1, but it is also possible to according to utilization
Size of the load of side component 4 etc., is connected in parallel the compressor 21 of more than two.
Heat source side heat exchanger 23 is, for example, to be configured to include the fin tube type heat exchanger of heat-transfer pipe and multiple fins, and
It is used as the condenser function for condensing refrigerant.Heat source side fan 27 is equipped in the vicinity of heat source side heat exchanger 23,
The heat source side heat exchanger 23 of heat source side fan 27 blows air.Heat source side fan 27 is by from the outside of heat source side component 2
The blowing external air of suction is to heat source side heat exchanger 23.Heat source side fan 27 is for example configured to include centrifugal fan or many
Blade fan etc., and driven by the motor for eliminating diagram.Heat source side fan 27 can adjust heat source side heat exchanger 23 and blow
The air output of the air sent.
Receiver 25 is disposed between the subcooler 22 of heat source side heat exchanger 23 and the 1st, and stores remaining liq refrigeration
Agent, e.g. stores the container of remaining liq refrigerant.In addition, remaining liq refrigerant is, for example, according to utilization side component 4
The size of load, the condensation temperature of refrigerant, capacity of external air temperature or compressor 21 etc. and in refrigerant loop 10
Interior generation.
1st subcooler 22 makes refrigerant carry out heat exchange with air, and is integrally formed with heat source side heat exchanger 23.
That is, in the example of present embodiment, the part of heat exchanger is configured to heat source side heat exchanger 23, heat exchanger it is other
Part is configured to the 1st subcooler 22." subcooler " of 1st subcooler 22 equivalent to the present invention.In addition, the 1st supercooling
Device 22 and heat source side heat exchanger 23 can also be respectively constituted.In this case, the 1st subcooler 22 neighbouring arranging to
1 subcooler 22 blows the fan (not shown) of air.
Hydraulic fluid side stop valve 28 and gas side stop valve 29 are opened and closed such as ball valve, open and close valve or operation valve
The valve of action is constituted.For capillary 74, it can also be made up of the valve that can adjust flow.
In addition, in the example described in Fig. 1, the entrance of the 1st infusion circuit 71 and the 2nd infusion circuit 73 is connected to
Between 1 subcooler 22 and hydraulic fluid side stop valve 28, but the entrance of the 1st infusion circuit 71 and the 2nd infusion circuit 73 can also
It is connected between the subcooler 22 of receiver 25 and the 1st, receiver 25 can also be connected to, or heat source side can also be connected to
Between heat exchanger 23 and receiver 25.
[control unit and sensor class]
Next, the control unit and sensor class that possess to the refrigerating plant 1 of present embodiment are illustrated.Thermal source
Side component 2 possesses the heat source side control unit 31 being controlled to the entirety of refrigerating plant 1.Heat source side control unit 31 is configured to include
Microcomputer and memory etc..The utilization side being controlled using side component 4 is controlled in addition, possessing using side component 4
Portion 32.It is configured to include microcomputer and memory etc. using side control unit 32.Utilize side control unit 32 and heat source side control
Portion 31 processed can communicate through to be controlled the exchange of signal, for example, using side control unit 32 from heat source side control unit
31 receive instruction, carry out the control using side component 4.
The refrigerating plant 1 of present embodiment includes inlet temperature sensor 33a, discharge temperature sensor 33b, suction outside
Air temperature sensor 33c, subcooler high side outlet temperature sensor 33d, utilize side heat hand over inlet temperature sensor
33e, side heat is utilized to hand over outlet temperature sensor 33f, inhaled air temperature sensor 33g, suction pressure sensor 34a and row
Go out pressure sensor 34b.Inlet temperature sensor 33a, discharge temperature sensor 33b, suction external air temperature sensor
33c, subcooler high side outlet temperature sensor 33d, suction pressure sensor 34a and discharge pressure sensor 34b match somebody with somebody
It is connected located at heat source side component 2, and with heat source side control unit 31.Inlet temperature sensor 33e is handed over using side heat, handed over using side heat
Outlet temperature sensor 33f and inhaled air temperature sensor 33g are disposed in using side component 4, and with utilizing side control unit
32 connections.
The temperature for the refrigerant that inlet temperature sensor 33a detection compressors 21 are sucked.Discharge temperature sensor 33b is detected
The temperature for the refrigerant that compressor 21 is discharged.Subcooler high side outlet temperature sensor 33d detections pass through the 1st subcooler
The temperature of refrigerant after 22.Inlet temperature sensor 33e is handed over to detect to the gas flowed into using side heat exchanger 42 using side heat
The evaporating temperature of liquid two-phase system cryogen.Outlet temperature sensor 33f detections are handed over to be flowed out from using side heat exchanger 42 using side heat
The temperature of refrigerant afterwards.In addition, the sensor of the temperature of above-mentioned detection refrigerant is for example adapted to support with refrigerant piping
Refrigerant piping is connect or be inserted in, and the temperature of refrigerant is detected.
Temperature of the external air temperature sensor 33c detections by the air before heat source side heat exchanger 23 is sucked, from
And detect outdoor environment temperature.Inhaled air temperature sensor 33g is detected by using the air before side heat exchanger 42
Temperature, so as to detect the indoor environment temperature being provided with using side heat exchanger 42.
Suction pressure sensor 34a is disposed in the suction side of compressor 21, the refrigerant that detection is sucked by compressor 21
Pressure.In addition, suction pressure sensor 34a is disposed between gas side stop valve 29 and compressor 21.Discharge pressure is passed
Sensor 34b is disposed in the discharge side of compressor 21, the pressure for the refrigerant that detection compressor 21 is discharged.
In the example of present embodiment, the condensation temperature of heat source side heat exchanger 23 is by by discharge pressure sensor
What 34b conversion pressure was obtained into saturation temperature, but the condensation temperature of heat source side heat exchanger 23 also can be by by temperature
Sensor is disposed in heat source side heat exchanger 23 to obtain.
Fig. 2 is the figure of an example of the structure for the refrigerating plant for schematically describing embodiments of the present invention 1.Control
Portion 3 processed is controlled to the entirety of refrigerating plant 1, and the control unit 3 of the example of present embodiment is contained in heat source side control unit 31.
In addition, " determining amount of refrigerant portions " of the control unit 3 equivalent to the present invention.Control unit 3 includes acquisition unit 3a, operational part 3b, storage
Portion 3c and drive division 3d.Acquisition unit 3a, operational part 3b and drive division 3d are such as being configured to include microcomputer, storage
Portion 3c is such as being configured to include semiconductor memory.Acquisition unit 3a obtains the sensor such as pressure sensor and temperature sensor
The information such as temperature and pressure that class is detected.The information that operational part 3b is got using acquisition unit 3a come carry out computing, compare,
The processing such as judgement.The result that drive division 3d is calculated using operational part 3b is compressed the driving control of machine 21, valve class, fan etc.
System.Storage part 3c be stored with refrigerant physics value (saturation pressure, saturation temperature etc.), for operational part 3b carry out computing number
According to etc..Operational part 3b can carry out with reference to or update storage part 3c storage content as needed.
In addition, control unit 3 includes input unit 3e and output section 3f.Input unit 3e inputs come from remote control or Switch
Operation Deng (not shown) is inputted, or communication of the input from communication units (not shown) such as telephone line or LAN lines
Data.The result of control unit 3 is output to the display units such as LED, monitor (not shown) by output section 3f, and this is handled
As a result the reporting units such as loudspeaker (not shown) are output to, or the result is output to telephone line or LAN line
Deng communication unit (not shown).In addition, in the case of using communication unit to remote site output information, to refrigerating plant 1
The communication unit (not shown) with identical communication protocol is set with remote-control device (not shown) this both sides.
For example, can also use the deficiency of refrigerating plant 1 and remote-control device (not shown) to judge refrigerant amount etc..At this
In the case of, for example, operational part 3b carrys out the temperature efficiency T of the subcooler 22 of computing the 1st using the acquisition unit 3a information got, it is defeated
Go out portion 3f and the operational part 3b temperature efficiency T calculated are sent to remote-control device.Remote-control device possesses judgement refrigerant amount not
The lack of refrigerant identifying unit (not shown) of foot, and temperature in use efficiency T judges the deficiency of refrigerant amount.By by long-range
The not enough information of device to manage refrigerant etc., so as to find refrigerating plant 1 in advance in the place for being provided with remote-control device
It is abnormal etc., so when there occurs in refrigerating plant 1 in abnormal situation etc., the dimension of refrigerating plant 1 can be carried out in advance
Shield etc..
In addition, in the above description, the example that control unit 3 is contained in heat source side control unit 31 is illustrated, but
Control unit 3 can also be contained in can also be and heat source side control unit 31 and utilization using side control unit 32, or control unit 3
The separated structure of side control unit 32.
[action (when refrigerant amount is suitable) of refrigerating plant]
Fig. 3 be the refrigerating plant described in Fig. 1 refrigerant amount it is suitable when p-h line charts an example.First, it is right
The action of refrigerating plant 1 in the case of refrigerant amount is suitable is illustrated.The compression described in point K to point L, Fig. 1 in Fig. 3
Machine 21 is compressed to refrigerant.Fig. 3 point L to point M, the gas refrigeration of the HTHP compressed by Fig. 1 compressor 21
Agent condensation liquefaction using the progress heat exchange of heat source side heat exchanger 23 as condenser function.In addition, utilizing thermal source
The refrigerant that side heat exchanger 23 carries out heat exchange and condensation liquefaction is flowed into receiver 25, is provisionally remained in receiver 25
It is interior.The amount of refrigerant of receiver 25 is remained according to warm using the operating load of side component 4, external air temperature and condensation
Degree etc. and change.
In Fig. 3 point M to point N, Fig. 1 liquid refrigerant of receiver 25 is remained in by the supercooling of the 1st subcooler 22.
In addition, the degree of subcooling of the outlet of the 1st subcooler 22 is passed by subtracting subcooler high side outlet temperature from condensation temperature
Sensor 33d temperature is calculated.
In Fig. 3 point N to point O, ended by Fig. 1 overcooled liquid refrigerant of the 1st subcooler 22 via hydraulic fluid side
Valve 28 and liquid refrigerant extension pipe arrangement 6 are conveyed to using side component 4, and be utilized side expansion valve 41 depressurize and as low pressure
Gas-liquid two-phase refrigerant.
In Fig. 3 point O to point K, the gas-liquid two-phase refrigerant depressurized by Fig. 1 by the use of side expansion valve 41 is by the use of being used as evaporation
The utilization side heat exchanger 42 of device function and gasify.In addition, the degree of superheat of refrigerant from using side heat by surrendering mouth temperature
The temperature that degree sensor 33f is detected subtracts the evaporation temperature for the refrigerant for handing over inlet temperature sensor 33e to be detected using side heat
Spend to calculate.The gas refrigerant for being utilized the gasification of side heat exchanger 42 extends pipe arrangement 7, gas side cut-off via gas refrigerant
Valve 29, reservoir 24 return to compressor 21.
Next, being illustrated to infusion circuit.1st infusion circuit 71 is used to reduce the refrigeration of the discharge unit of compressor 21
Agent temperature.The entrance of 1st infusion circuit 71 is connected between outlet and the hydraulic fluid side stop valve 28 of the 1st subcooler 22, by the 1st
The part amount of the being injected into adjustment valve 72 of the overcooled high pressure liquid refrigerant of subcooler 22 depressurizes and turns into the two of intermediate pressure
Phase refrigerant, and flowed into the injection unit of compressor 21.
2nd infusion circuit 73 is used to reduce the refrigerator oil of the inside of compressor 21, the temperature of motor, the refrigeration of discharge unit
Agent temperature.The entrance of 2nd infusion circuit 73 is connected between outlet and the hydraulic fluid side stop valve 28 of the 1st subcooler 22, by the 1st
A part for the overcooled high pressure liquid refrigerant of subcooler 22 is depressurized by capillary 74 and turns into the two-phase system cryogen of low pressure,
And flowed into the sucting of compressor 21.
[action (during short of refrigerant) of refrigerating plant]
One example of p-h line charts when Fig. 4 is the short of refrigerant of the refrigerating plant described in Fig. 1.For example,
When refrigerating plant 1 described in refrigerant from Fig. 1 occurs leakage etc. and makes the amount reduction of refrigerant, retained when in receiver 25
During remaining liq refrigerant, the remaining liq refrigerant for remaining in receiver 25 is reduced.It is remaining when existing in receiver 25
During liquid refrigerant, refrigerating plant 1 in the same manner as when refrigerant amount is suitable as shown in figure 3, acted.
When refrigerant is further reduced and the remaining liq refrigerant in receiver 25 disappears, as shown in Fig. 4 point M1,
Enthalpy change as the outlet of the heat source side heat exchanger 23 of condenser function is big, the system of the outlet of heat source side heat exchanger 23
Cryogen state turns into two-phase state.In addition, as the enthalpy change of the outlet of heat source side heat exchanger 23 is big, the 1st subcooler 22 enters
The condensation liquefaction of row two-phase system cryogen and supercooling, so as shown in point N1, the enthalpy of the outlet of the 1st subcooler 22 also becomes big.
[comparative example 1]
In comparative example 1, the judgement of refrigerant amount is carried out using the degree of subcooling of refrigerant.For example when refrigerant occurs
Leakage etc. and during short of refrigerant, as shown in figure 4, degree of subcooling declines.Therefore, in comparative example 1, when degree of subcooling is than pre-
The threshold value hour first set, is determined as short of refrigerant.
Fig. 5 is refrigerant amount, the degree of subcooling and refrigeration of the 1st subcooler for illustrating the refrigerating plant described in Fig. 1
The figure of the relation of the operating condition of device.As shown in figure 5, operating of the degree of subcooling of the 1st subcooler 22 according to refrigerating plant 1
Condition (external air temperature, heat exchange amount, circulating mass of refrigerant etc.) and significantly change.Therefore, utilizing as the comparative example 1
In the case of not enough judgement of the degree of subcooling to carry out refrigerant amount, in order to avoid erroneous judgement is, it is necessary to which degree of subcooling threshold value S is set
Surely it is low.In variation 1, it is necessary to degree of subcooling threshold value S is set to it is low, so determining the deficiency of refrigerant amount
It is preceding, it is necessary to which longer time, such as in the case where refrigerant is leaked, the leakage quantitative change of refrigerant is more.
[judgement of refrigerant amount]
Therefore, in the present embodiment, using the change of the operating condition relative to refrigerating plant 1, supercooling is compared in variation
The temperature efficiency T of the 1st small subcooler 22 is spent to carry out the judgement of refrigerant amount.It is described below.
Fig. 6 is illustrated in the refrigerating plant described in Fig. 1, and when refrigerant amount is appropriate amount, refrigerant presses heat source side
The figure of one example of the temperature change of refrigerant when heat exchanger, receiver, the sequential flowing of air subcooler.This
Outside, in figure 6, the longitudinal axis represents temperature, and more top portion, temperature is higher.In addition, transverse axis represents heat source side heat exchanger 23, reception
The refrigerant path of device 25, the 1st subcooler 22.S1 is the condensation temperature of refrigerant, and s2 is the outlet of the 1st subcooler 22
Refrigerant temperature, s3 is external air temperature.
The temperature efficiency T of 1st subcooler 22 represents the efficiency of the 1st subcooler 22, the temperature that maximum can be obtained
Poor A is taken as denominator, and actual temperature difference B is taken as into molecule.In the 1st subcooler 22, the temperature difference A that maximum can be obtained is
Condensation temperature s1 and external air temperature s3 difference, the temperature difference B that can actually obtain are condensation temperature s1 and the 1st subcooler
The temperature s2 of 22 outlet difference.Temperature efficiency T is represented by following formula (formula 1).
The temperature difference A ... (formula 1) that the temperature difference B/ maximums that temperature efficiency T=can actually be obtained can be obtained
Fig. 7 is refrigerant amount, the temperature efficiency and refrigeration of the 1st subcooler for illustrating the refrigerating plant described in Fig. 1
The figure of the relation of the operating condition of device.In the figure 7, transverse axis is the refrigerant amount of refrigerant, and the longitudinal axis is the 1st subcooler 22
Temperature efficiency T.As shown in fig. 7, when refrigerant amount is reduced, as E, the remaining liq refrigerant of receiver 25 disappears refrigerant amount
During mistake, the temperature efficiency T of the 1st subcooler 22 declines.Therefore, in temperature efficiency T than predetermined temperature efficiency threshold T1
Hour, it is determined as that refrigerant is leaked.Temperature efficiency T represents the performance of supercooling heat exchanger 5, with degree of subcooling phase
Than temperature efficiency T's changes small as caused by the operating condition of refrigerating plant 1, so without each fortune for refrigerating plant 1
Turn condition given threshold, it becomes possible to improve the judgement precision of short of refrigerant.
[exceptional condition of determining amount of refrigerant]
In addition, in the case of refrigerant amount is proper amount of, the operating shape of the refrigerating plant 1 according to described in Fig. 1
State, still suffering from turns into erroneous judgement using the temperature efficiency T of the 1st subcooler 22 determining amount of refrigerant and is determined as refrigerant amount not
The situation of foot.In the case of refrigerant amount is proper amount of, when being determined as short of refrigerant, confusion can be caused.In addition,
In the presence of following situation：Although refrigerant amount is appropriate amount, when being determined as short of refrigerant, by supplementing refrigerant, from
And the result of determination of refrigerant amount is turned into proper amount of and judge.But, in this case, due to the refrigeration of amount being not necessarily required to
Agent is sealing into refrigerating plant 1, so the cost increase of refrigerating plant 1.In addition, when refrigerant amount unnecessarily becomes many, it is false
If when refrigerant there occurs leakage, can make that refrigerant can be being judged by using temperature efficiency T determining amount of refrigerant
Leakage rate increase before deficiency.Further, since refrigerant amount is excessive, it is also possible to the liquid capacity of returns when occurring liquid backflow
Increase, causes the unfavorable condition of compressor 21.Therefore, the exception bar of determining amount of refrigerant is provided with the example of present embodiment
Part, meet determining amount of refrigerant be possible to can turn into erroneous judgement exceptional condition in the case of, without use the 1st subcooler
22 temperature efficiency T determining amount of refrigerant.It is described below.
[exceptional condition 1 (during using crosswind fan delay control)]
Exceptional condition 1 is the situation for fanned using crosswind delay control.It is to prevent using crosswind fan delay control
The heating produced in defrosting operating blows out and carried out to cooling space.Defrosting operating terminate after until utilize side heat exchange
For example, a few minutes time only are reduced at a temperature of device 42, when just making utilization before the temperature drop using side heat exchanger 42
When crosswind fan 43 is acted, heating can be to the blowout of cooling space, so stopping fanning 43 action using crosswind, until utilizing side
The temperature drop of heat exchanger 42.Then, after the temperature drop using side heat exchanger 42, start again at and utilize crosswind fan 43
Action.
When stopping fanning 43 action using crosswind, it is suppressed using the heat exchange of side heat exchanger 42, so passing through
Turn into gas-liquid two-phase state sometimes using the refrigerant of side heat exchanger 42.That is, generally handed over gaseous state from using side heat
The refrigerant that parallel operation 42 flow to compressor 21 is flowed when carrying out using crosswind fan delay control with two-phase state, liquid refrigerant
Remain in reservoir 24.Therefore, when carrying out using crosswind fan delay control, the amount of the refrigerant of low-pressure side increases temporarily,
The amount of on high-tension side refrigerant declines temporarily.Its result is, when carrying out using crosswind fan delay control, temperature in use efficiency T
Determining amount of refrigerant be possible to can turn into erroneous judgement.Therefore, when using crosswind fan delay control, without temperature in use efficiency
T determining amount of refrigerant.In addition, when being terminated using crosswind fan delay control and making to operate using crosswind fan 43, from utilizing side
The refrigerant that heat exchanger 42 flow to compressor 21 turns into gaseous state, and on high-tension side lack of refrigerant is eliminated.
For example, control unit 3 judges that refrigerating plant 1 utilizes side in implementation by obtaining the operating condition of refrigerating plant 1
During fan delay control.Then, prolong in the implementation process for postponing control is fanned using crosswind or using crosswind fan
Fanned in the implementation process controlled late and using crosswind after delay control until flowing to compressor from using side heat exchanger 42
21 refrigerant turn into gaseous state untill certain time, control unit 3 without lack of refrigerant judgement.In addition, except
Fan beyond the situation that delay is controlled using crosswind, in the case where stopping fanning 43 action using crosswind, as described above
Ground, temperature in use efficiency T determining amount of refrigerant is also possible to that erroneous judgement can be turned into.Accordingly it is also possible to be configured to：Stopping utilizing
In the case of the action of crosswind fan 43, without temperature in use efficiency T determining amount of refrigerant.
It is further possible to exceed setting time set in advance in times of the temperature efficiency T less than temperature efficiency threshold value T1
In the case of, it is determined as lack of refrigerant.That is, it is, for example, 10 minutes or so that the maximum duration for postponing to control is fanned using crosswind,
Carry out using after crosswind fan delay control, until turning into gas from the refrigerant that compressor 21 is flow to using side heat exchanger 42
Maximum duration untill state is, for example, 10 minutes or so.Thus, for example also temperature efficiency threshold value can be less than in temperature efficiency T
T1 time exceed by " using crosswind fan postpone control maximum duration+progress using crosswind fan delay control after, up to from
Using side heat exchanger 42 flow to compressor 21 refrigerant turn into gaseous state untill maximum duration " determined by set when
Between in the case of (such as 20 minutes), be determined as lack of refrigerant.
[exceptional condition 2 is (in cooling (Japanese：プ Le ダ ウ Application) when evaporating temperature high situation)]
Exceptional condition 2 is the high situation of evaporating temperature in cooling.Generally, the cooling after refrigerating plant 1 stops for a long time
When storehouse temperature it is high in the case of, there is a situation where as follows：Although the short time, can be with the low pressure of refrigerant loop 10
The usual high state operating of the pressure ratio of side.In this case, it is from the sucting for playing compressor 21 using side expansion valve 41
Pressure only is uprised, and refrigerant density becomes big.Because required refrigerant amount is represented by density × volume, thus it is low
The required refrigerant amount of pressure side increases temporarily, the high pressure such as receiver 25, the 1st subcooler 22, heat source side heat exchanger 23
Side turns into the state of lack of refrigerant.Therefore, in the case that evaporating temperature is high when in cooling, without temperature in use efficiency T
Determining amount of refrigerant.
Fig. 8 is for illustrating in the determining amount of refrigerant of present embodiment, in the situation that compressor is frequency-changeable compressor
The lower size according to low pressure and without the figure of determining amount of refrigerant, Fig. 9 is for illustrating the refrigeration in present embodiment
During dosage judges, in the case where compressor is constant speed compressor according to the size of low pressure without determining amount of refrigerant
Figure.As shown in figure 8, compressor 21 be frequency-changeable compressor in the case of, make compressor 21 operating frequency increase or under
Drop, so that low pressure P1 of the actual low pressure close to the target being previously set.In addition, as shown in figure 9, being constant speed pressure in compressor 21
In the case of contracting machine, the low pressure for operating compressor 21 in the case of rising by being set in low pressure ends connection value P4, and sets
The low pressure cut-off cut off value P3 for stopping compressor 21 in the case that low pressure declines is scheduled on, compressor 21 is operated.That is, in compression
In the case that machine 21 is frequency-changeable compressor, compressor 21 is with the state of the low pressure of the substantially target of the low pressure in operation process
Operated, in addition, being generally the low pressure cut-off for operating compressor 21 in the case where compressor 21 is constant speed compressor
Operating below connection value.Therefore, as described below, target low-pressure or low pressure cut-off connection value are added in current low-pressure ratio
In the case of being worth height obtained from upper surplus, without the judgement of lack of refrigerant.That is, as shown in figure 8, being change in compressor 21
In the case of frequency compressor, in the case where current low-pressure ratio target low-pressure P1+ surpluses α pressure P2 is big, without refrigeration
The not enough judgement of agent.In addition, as shown in figure 9, compressor 21 be constant speed compressor in the case of, in current low-pressure ratio low pressure
In the case that the pressure P5 of cut-off connection value P4+ margin betas is big, without the judgement of lack of refrigerant.
[exceptional condition 3 (situation that suction injection is out with magnetic valve)]
Exceptional condition 3 is to open the situation of the suction injection magnetic valve 75 described in Fig. 1.Electricity consumption is injected when opening suction
During magnet valve 75, a part for high pressure liquid refrigerant is depressurized and flowed into the sucting of compressor 21 by capillary 74.Now, lead to
Be often gaseous state play the sucting of compressor 21 from the suction injection magnetic valve 75 of low-pressure side untill refrigerant into
For gas-liquid two-phase state, refrigerant amount increases temporarily in low-pressure side, so receiver 25, the 1st subcooler 22, heat source side heat are handed over
The grade of parallel operation 23 high-pressure side turns into the state of lack of refrigerant.In addition, it is long-term with the situation of magnetic valve 75 to open suction injection
During cooling after stopping etc., the progress such as when the suction gas temperature of compressor 21 rises singularly, this is rare situation.
Therefore, in the operation process of compressor 21, and in the case where opening suction injection with magnetic valve 75, Yi Ji
From the certain time from being opened to and closing of suction injection magnetic valve 75, compressor is played from suction injection magnetic valve 75
Refrigerant untill 21 sucting turns into gas-liquid two-phase state, and refrigerant amount increases temporarily in low-pressure side, receiver the 25, the 1st
The high-pressure sides such as subcooler 22, heat source side heat exchanger 23 turn into the state of lack of refrigerant, so without lack of refrigerant
Judgement.In addition, in the above, to when being injected using the 2nd infusion circuit 73 without lack of refrigerant
The example of judgement is illustrated, but it is also possible to be configured to when being injected using the 1st infusion circuit 71, without refrigeration
The not enough judgement of agent.In this case, as long as adjusting aperture of valve 72 etc. by injection rate to be made whether to carry out refrigerant not
The judgement of the judgement of foot.
[exceptional condition 4 (when the air quantity of heat source side fan declines)]
In above-mentioned 1~exceptional condition of exceptional condition 3, to not entering in the case of the interim deficiency of on high-tension side refrigerant
The example of row determining amount of refrigerant is illustrated.Exceptional condition 4 is the situation for declining the air quantity of heat source side fan 27.Make heat
The situation that the air quantity of source fan 27 declines refers to following situation：Pressed through for example, working as the height in the case of outside air drop
When degree declines, diminished using the pressure differential of side expansion valve 41 and the flow of refrigerant can not be ensured, therefore, in order to a certain degree
High pressure is maintained higher, declines the air quantity of heat source side fan 27.In addition, for example there is also following situation：In order to seek heat
The reduction of the noise of source fan 27, declines the air quantity of heat source side fan 27.
For temperature efficiency T, when the air quantity of heat source side fan 27 declines, condensation temperature is uprised, therefore, condensation temperature
The difference of degree and external air temperature is that the maximum temperature difference A that can be obtained becomes big.Now, due under the air quantity of heat source side fan 27
Drop, therefore, compared with the temperature difference A that maximum can be obtained, condensation temperature and the temperature difference of the outlet of the 1st subcooler 22 are
The temperature difference B that can actually obtain does not become big.Therefore, when making the air quantity decline of heat source side fan 27, under temperature efficiency T
Drop., it is necessary to turn on/off heat source side fan 27, generally particularly when temperature is -15 DEG C or so of low extraneous air etc.
The temperature difference A that can be obtained for 7K~15K or so maximum is changed into 30K~50K, and temperature efficiency T declines.Therefore, thermal source is made
In the case of the air quantity decline of crosswind fan 27, in the case where the difference of external air temperature and condensation temperature becomes big or outside
In the case that portion's air themperature is lower than a certain temperature, without the judgement of lack of refrigerant.
Figure 10 is the figure of the air quantity and an example of the relation of temperature efficiency threshold value that represent heat source side fan.Such as Figure 10 institutes
Show, compared with the temperature efficiency threshold value T3 when air quantity of heat source side fan 27 is more, the air quantity of heat source side fan 27 will be declined
In the case of temperature efficiency threshold value T2 be set as small value so that the refrigerant amount that can also suppress temperature in use efficiency T is sentenced
Surely it is possible to that erroneous judgement can be turned into.
[exceptional condition 5 (certain time in compressor stopped process, after starting compressor)]
Exceptional condition 5 be compressor stopped process in, the certain time after starting compressor.Figure 11 is to illustrate to start compression
With the condensation temperature after starting compressor, external air temperature, the outlet temperature of the 1st subcooler and temperature efficiency before machine
The figure of relation.For example, it is contemplated that making the situation that compressor 21 is started after compressor 21 is stopped for a long time.Long-term in compressor 21 is stopped
During only, external air temperature, the 1st subcooler 22 outlet temperature, condensation temperature it is roughly equal.In this case, such as
Really all temperature are all equal, then temperature efficiency T=B/A=0/0.But, in fact, due to the deviation of sensor, for example, cold
Solidifying temperature is 25.0 DEG C, and external air temperature is 24.9 DEG C, and the outlet temperature of the 1st subcooler 22 is 24.8 DEG C, temperature efficiency T
=B/A=0.2/0.1=2.0.In addition, above-mentioned example is an example, in fact, in the long-term stopped process of compressor 21
In, due to deviation of sensor etc., temperature efficiency T can significantly change.When the starting compressor 21 at moment m1, temperature efficiency T
The value between 0.0~1.0 is stabilized in moment m2.In addition, the time untill playing moment m2 from moment m1 is, for example, 30 seconds~1
Minute or so.
As described above, the certain time after the starting compressor 21 from the stopped process of compressor 21, temperature efficiency T is
Unstable situation, for example, in the case where the stopping of compressor 21 is repeated in short time, operates, temperature efficiency T is low
Situation continues.Its result is, in the case that refrigerant is not leaked, and is judged using temperature efficiency T refrigerant
It can be lack of refrigerant to be also possible to.Therefore, the certain time after the starting compressor 21 from the stopped process of compressor 21,
Without the judgement of lack of refrigerant.
[determining amount of refrigerant action]
Figure 12 is the figure of an example of the determining amount of refrigerant action for illustrating the refrigerating plant described in Fig. 1.This implementation
The refrigerating plant 1 of mode carries out the judgement of refrigerant amount using the temperature efficiency T of the 1st subcooler 22.In addition, following explanation
Refrigerant amount judgement can also apply to set refrigerating plant 1 when refrigerant filling operation or carry out refrigerating plant 1
Maintenance when refrigerant filling operation.Alternatively, it is also possible to when receiving the instruction from remote-control device (not shown), perform system
Cryogen amount acts of determination.
In Figure 12 step ST1, the refrigerating plant 1 described in Fig. 1 carries out conventional operating control.In refrigerating plant 1
Under conventional operating control, heat source side control unit 31 for example obtains the pressure and temperature for the refrigerant loop 10 that sensor class is detected
The service datas such as degree, service firing data carry out the controlling values such as the desired values such as computing condensation temperature and evaporating temperature and deviation,
And carry out the control of actuator class.Hereinafter, the action to actuator class is illustrated.
For example, heat source side control unit 31 controls the operating frequency of compressor 21, so that the steaming of the kind of refrigeration cycle of refrigerating plant 1
Send out temperature consistent with target temperature (such as 0 DEG C).In addition, the evaporating temperature of kind of refrigeration cycle also can be by the way that suction pressure be sensed
The conversion pressure that device 34a is detected is obtained into saturation temperature.For example, heat source side control unit 31 compares mesh in current evaporating temperature
The operating frequency of compressor 21 is increased in the case that mark temperature is high, make in the case where current evaporating temperature is lower than desired value
The operating frequency of compressor 21 declines.
In addition, for example, the control heat source of heat source side control unit 31 side heat exchanger 23 blows the heat source side fan 27 of air
Rotating speed so that the condensation temperature of the kind of refrigeration cycle of refrigerating plant 1 and target temperature (such as 45 DEG C) are consistent.In addition, refrigeration dress
The condensation temperature for putting a kind of refrigeration cycle also can be by the conversion pressure that is detected discharge pressure sensor 34b into saturation temperature
Spend to obtain.For example, heat source side control unit 31 increases thermal source crosswind in the case where current condensation temperature is higher than target temperature
The rotating speed of fan 27, reduces the rotating speed of heat source side fan 27 in current condensation temperature than target temperature in the case of low.
In addition, for example, heat source side control unit 31 adjusts the 1st infusion circuit 71 using the signal obtained from sensor class
Injection rate adjusts the aperture of valve 72, or adjusts the aperture of the suction injection magnetic valve 75 of the 2nd infusion circuit 73.For example, hot
Source control unit 31 makes injection rate adjust valve 72 or suction injection in the case where the discharge temperature of current compressor 21 is high
It is open mode with magnetic valve 75, in the case where the discharge temperature of current compressor 21 is low, closes injection rate adjustment valve 72
Or suction injection magnetic valve 75.In addition, for example, heat source side control unit 31 is carried out to the profit that air is blowed using side component 4
The control of 43 rotating speed is fanned with crosswind.
In step ST2, heat source side control unit 31 is for example using the outlet temperature of heat source side heat exchanger 23, the 1st supercooling
But the temperature of the outlet of device 22, suction external air temperature sensor 33c are detected external air temperature and discharge pressure
Pressure that sensor 34b is detected etc., carries out the temperature efficiency T of the 1st subcooler 22 computing.
In step ST3, heat source side control unit 31 obtains the operating condition of refrigerating plant 1.In the operating shape of refrigerating plant 1
In the case that state meets above-mentioned " exceptional condition of determining amount of refrigerant ", step ST1 is returned to, in the operating shape of refrigerating plant 1
In the case that state does not meet above-mentioned " exceptional condition of determining amount of refrigerant ", step ST4 is entered.
In step ST4, heat source side control unit 31 judges that the operating of the refrigerating plant 1 carried out by step ST1 is controlled whether
It is stable.In the case where the operating control of refrigerating plant 1 is unstable, step ST1 is returned to, is controlled in the operating of refrigerating plant 1
In the case of stable, step ST5 is entered.
In step ST5, heat source side control unit 31 is by comparing determining amount of refrigerant parameter and determining amount of refrigerant parameter
A reference value, so as to carry out the whether appropriate judgement of refrigerant amount.Specifically, the temperature efficiency T of the 1st subcooler 22 is solved
With decision threshold Tm departure Δ T (=T-Tm), and judge departure Δ T whether as on the occasion of.It is positive in departure Δ T
In the case of, heat source side control unit 31 is judged as that refrigerant amount is not not enough, enters step ST6.It is negative feelings in departure Δ T
Under condition, heat source side control unit 31 is judged as short of refrigerant, enters step ST7.Now, for the 1st subcooler 22
For temperature efficiency T, compared with using instantaneous value, multiple temperature efficiency T different in time rolling average is preferably taken as.
By being taken as multiple temperature efficiency T different in time rolling average, also can with respect to kind of refrigeration cycle stabilization.This
Outside, decision threshold Tm can for example be pre-stored within the storage part 3c of heat source side control unit 31, by remote control or can also open
The input closed etc. is set, and can also be set according to the instruction from remote-control device (not shown).
In the case of the determining amount of refrigerant result in step ST5 is suitable for refrigerant amount, in step ST6, heat
Source control unit 31 carries out the output that refrigerant amount suitably looks like.In the case of refrigerant amount is suitable, for example, being disposed in
Either the display part such as liquid crystal display refrigerant amount (not shown) suitably looks like or closes refrigerant amount the LED of refrigerating plant 1
The signal of the suitable meaning is sent to remote-control device is (not shown).
In the case that the determining amount of refrigerant result in step ST5 is short of refrigerant, in step ST7, heat
Source control unit 31 carries out the output of the abnormal meaning of refrigerant amount.In the case of refrigerant amount exception, for example, being disposed in
The LED of refrigerating plant 1 either alarms of the abnormal meaning of the display part such as liquid crystal display refrigerant amount (not shown) or will refrigeration
The signal of the abnormal meaning of dosage is sent to remote-control device is (not shown).Further, since there is also in the abnormal feelings of refrigerant amount
The situation of emergent management is needed under condition, so can also be configured to, by telephone line etc., exception directly be reported to attendant
Generation.
In addition, in the above-described embodiment, temperature efficiency T computing is carried out in step ST2, in step ST3 and
The judgement of the judgement of progress refrigerant amount is made whether in step ST4, but it is also possible to held after step ST3 and step ST4
Row step ST2.By whether carry out after the judgement for the judgement for carrying out refrigerant amount temperature efficiency T computing, energy
Enough reduction heat source side control unit 31 carries out the treating capacity of computing.
As described above, in the present embodiment, the refrigerant loop 10 in refrigerating plant 1 is carried out using temperature efficiency T
The judgement of the amount of the refrigerant of middle flowing, so in the case of assuming that refrigerant there occurs leakage, can also examine in advance
Measure the leakage of refrigerant.
Moreover, in the present embodiment, obtaining the operating condition of refrigerating plant 1, meeting in the operating condition of refrigerating plant 1
In the case of " exceptional condition of determining amount of refrigerant ", without the determining amount of refrigerant using temperature efficiency T, so can press down
The possibility of the erroneous judgement of refrigerant amount processed.Its result is that in the present embodiment, it is suitable amount, institute that can make refrigerant amount
So that the cost of refrigerant can be reduced.Moreover, in the present embodiment, because refrigerant amount is suitable amount, so even in
Assuming that in the case that refrigerant there occurs leakage, can also reduce the amount that refrigerant is released to air.Moreover, in present embodiment
In, because refrigerant amount is suitable amount, so even in assuming that expansion valve etc. remarkable action and produce the feelings of liquid backflow
Under condition, the liquid capacity of returns to compressor 21 can be also reduced.Therefore, the reliability of the refrigerating plant 1 of present embodiment is improved.
In addition, in the operating control of described above, the control of specific condensation temperature, evaporating temperature is not carried out, but
Can be for example to make condensation temperature, evaporating temperature are controlled as constant mode.In addition, for example, it is also possible to by compressor
The rotating speed of 21 operating frequency and the heat source side fan 27 of heat source side component 2 is set to steady state value, and without condensation temperature and steaming
Send out the control of temperature.In addition, for example, it is also possible to so that any one party in condensation temperature and evaporating temperature turns into the side of desired value
Formula is controlled.By being certain condition, the degree of subcooling of the 1st subcooler 22 by the operating condition control of refrigerating plant 1
Variation, the variation of the operation state quantity changed according to degree of subcooling diminish, the determination of threshold value becomes easy, it is easy to freezed
The judgement of underdosage.
In addition, passing through the system initial applied to the setting of refrigerating plant 1 of the determining amount of refrigerant action by present embodiment
Cryogen filling operation, or be applied to and while safeguarding once to discharge refrigerant and refrigerant when being again filled with is filled and made
Industry, so as to realize that the time shortening of refrigerant filling operation, the load of operator mitigate.
[variation 1]
Figure 13 is Fig. 1 variation 1.As shown in figure 13, compared with the refrigerating plant 1 described in Fig. 1, the system of variation 1
Device for cooling 1A heat source side component 2A also has the 2nd subcooler 26 in the downstream of the 1st subcooler 22.In addition, the 2nd supercooling
" subcooler " of the device 26 equivalent to the present invention.2nd subcooler 26 is for example configured to include double pipe or template heat exchange
Device etc., in making the refrigerant of the high pressure flowed in heat source side refrigerant loop 10b and being flowed in the 1st infusion circuit 71A
Between the refrigerant pressed carry out heat exchange.Valve 72 is adjusted using injection rate by a part for the refrigerant after the 2nd subcooler 26
And be inflated, the refrigerant as intermediate pressure, and with carrying out heat exchange by the refrigerant of the 2nd subcooler 26.Its result is,
In variation 2, flowed into from receiver 25 and using the 2nd subcooler 26 carry out heat exchange high pressure refrigerant further by
Supercooling.In addition, adjusting the refrigerant that valve 72 flowed into and carried out using the 2nd subcooler 26 intermediate pressure of heat exchange from injection rate
As the high refrigerant of aridity, the suction side of compressor 21 is injected into reduce the discharge temperature of compressor 21.For
For refrigerant acts of determination in variation 1, by using the temperature efficiency of the 1st subcooler 22, the 2nd subcooler 26
Temperature efficiency or the temperature efficiency of the 1st subcooler 22 and the 2nd subcooler 26 carry out refrigerant acts of determination i.e.
Can.In addition, in variation 1, or following structure：The 1st subcooler 22 is omitted, makes the system flowed out from receiver 25
Cryogen is flowed into the 2nd subcooler 26.
The present invention is not limited to above-mentioned embodiment, and various changes can be carried out within the scope of the invention.That is, may be used
Improved with the structure suitably to above-mentioned embodiment, alternatively, it is also possible to replace above-mentioned embodiment with other structures
At least partially.Moreover, for for configuring the structure important document being not particularly limited to it, being not limited to disclose in embodiments
Configuration, can be only fitted to can reach the position of its function.
Description of reference numerals
1：Refrigerating plant；1A：Refrigerating plant；2：Heat source side component；2A：Heat source side component；3：Control unit；3a：Acquisition unit；
3b：Operational part；3c：Storage part；3d：Drive division；3e：Input unit；3f：Output section；4：Utilize side component；5：Supercooling heat exchange
Device；6：Liquid refrigerant extends pipe arrangement；7：Gas refrigerant extends pipe arrangement；10：Refrigerant loop；10a：Returned using side refrigerant
Road；10b：Heat source side refrigerant loop；21：Compressor；22：1st subcooler；23：Heat source side heat exchanger；24：Reservoir；
25：Receiver；26：2nd subcooler；27：Heat source side fan；28：Hydraulic fluid side stop valve；29：Gas side stop valve；31：Heat
Source control unit；32：Utilize side control unit；33a：Inlet temperature sensor；33b：Discharge temperature sensor；33c：Suction is outside
Air temperature sensor；33d：Subcooler high side outlet temperature sensor；33e：Inlet temperature sensor is handed over using side heat；
33f：Outlet temperature sensor is handed over using side heat；33g：Inhaled air temperature sensor；34a：Suction pressure sensor；34b：Row
Go out pressure sensor；41：Utilize side expansion valve；42：Utilize side heat exchanger；43：Fanned using crosswind；71：1st infusion circuit；
71A：1st infusion circuit；72：Injection rate adjusts valve；73：2nd infusion circuit；74：Capillary；75：Suck injection magnetic valve；
T：Temperature efficiency；T1：Temperature efficiency threshold value；T2：Temperature efficiency threshold value；T3：Temperature efficiency threshold value.
Claims (9)
1. a kind of refrigerating plant, the refrigerating plant has refrigerant loop, the refrigerant loop connects heat source side group by pipe arrangement
Part and at least one are formed using side component, and refrigerant is circulated wherein, and the heat source side component has compressor, conduct
The heat source side heat exchanger and subcooler of condenser function, utilization side component, which has, utilizes side expansion valve and work
For the utilization side heat exchanger of evaporator function, wherein,
The refrigerating plant possesses determining amount of refrigerant portions, and the determining amount of refrigerant portions are imitated using the temperature of the subcooler
Rate judges to be filled in the refrigerant amount of the refrigerant loop, and the temperature efficiency of the subcooler is by the subcooler
Exit the degree of subcooling of refrigerant divided by the maximum temperature difference of the subcooler obtained from be worth,
The determining amount of refrigerant portions obtain the operating condition of the refrigerating plant, may be into being determined with for the refrigerant amount
In the case of for erroneous judgement, without the judgement of the refrigerant amount.
2. refrigerating plant according to claim 1, wherein,
Being determined with for the refrigerant amount may be to play the profit from the heat source side heat exchanger as the situation of erroneous judgement
Tailed off temporarily with the high-pressure side refrigerant untill the entrance of side expansion valve, play the pressure from the outlet of utilization side expansion valve
Low side refrigerant untill the Attractive side of contracting machine becomes many situations temporarily.
3. refrigerating plant according to claim 2, wherein,
The refrigerating plant is also equipped with using crosswind fan, and the utilization crosswind is fanned to utilization side heat exchanger and blows air,
High-pressure side refrigerant untill playing the entrance of utilization side expansion valve from the heat source side heat exchanger tails off temporarily,
Low side refrigerant untill playing the Attractive side of the compressor from the outlet of utilization side expansion valve becomes many feelings temporarily
Condition is the situation that the air output for blowing the utilization crosswind fan declines temporarily.
4. refrigerating plant according to claim 2, wherein,
High-pressure side refrigerant untill playing the entrance of utilization side expansion valve from the heat source side heat exchanger tails off temporarily,
Low side refrigerant untill playing the Attractive side of the compressor from the outlet of utilization side expansion valve becomes many feelings temporarily
Condition is the situation for making the refrigerating plant cool.
5. refrigerating plant according to claim 2, wherein,
The refrigerating plant is also equipped with：
A part for the refrigerant cooled down by the heat source side heat exchanger is injected into described by infusion circuit, the infusion circuit
Compressor；And
Open and close valve, the open and close valve is disposed in the infusion circuit,
High-pressure side refrigerant untill playing the entrance of utilization side expansion valve from the heat source side heat exchanger tails off temporarily,
Low side refrigerant untill playing the Attractive side of the compressor from the outlet of utilization side expansion valve becomes many feelings temporarily
Condition is the situation for making the open and close valve be open mode.
6. refrigerating plant according to claim 1, wherein,
The refrigerating plant is also equipped with heat source side fan, and the heat source side fan blows air to the heat source side heat exchanger,
Being determined with for the refrigerant amount may be that the air output for blowing the heat source side fan faces as the situation of erroneous judgement
When situation about declining.
7. refrigerating plant according to claim 1, wherein,
Being determined with for the refrigerant amount may turn into the stopped process that situation about judging by accident is the compressor and described
Certain time after compressor start.
8. refrigerating plant according to claim 1, wherein,
The determining amount of refrigerant portions are stored with temperature efficiency threshold value, and the temperature efficiency threshold value is used to judge the refrigerant amount
Deficiency, the temperature efficiency threshold value is changed according to the operating condition of the refrigerating plant.
9. refrigerating plant according to claim 8, wherein,
The refrigerating plant is also equipped with heat source side fan, and the heat source side fan blows air to the heat source side heat exchanger,
The temperature efficiency threshold value is changed according to the air output that the heat source side fan is blowed.
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| PCT/JP2015/055476 WO2016135904A1 (en) | 2015-02-25 | 2015-02-25 | Refrigeration apparatus |
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| CN112005062A (en) * | 2018-04-23 | 2020-11-27 | 三菱电机株式会社 | Refrigeration cycle device and refrigeration device |
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| CN114761743A (en) | 2019-12-04 | 2022-07-15 | 三菱电机株式会社 | Outdoor unit and refrigeration loop device |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN107110586B (en) | 2020-01-24 |
| JP6449979B2 (en) | 2019-01-09 |
| WO2016135904A1 (en) | 2016-09-01 |
| JPWO2016135904A1 (en) | 2017-09-07 |
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