CN104596172A - Refrigeration air conditioning device - Google Patents

Abstract

The invention provides a refrigeration air conditioning device, wherein the inner volume of a refrigerant extension pipe can be accurately calculated by using operation data obtained during normal operation, and the calculation of the total quantity of a refrigerant within a refrigerant circuit and the detection of leakage of the refrigerant can be performed with high accuracy. Every time an operation state represented by operation data measured during normal operation satisfies operation data obtaining conditions, the operation data at the moment is obtained as operation data for initial learning; processing of calculating the quantity of the refrigerant except in the extension pipe and the density of the refrigerant in the extension pipe on the basis of the operation data for initial learning is performed; the inner volume of the extension pipe is calculated on the basis of a calculated result data group obtained by the processing; the basic quantity of the refrigerant is calculated on the basis of the calculated inner volume of the extension pipe and the operation data for initial learning. The total quantity of the refrigerant within the refrigerant circuit is calculated on the basis of the calculated inner volume of the extension pipe and the current operation data and then is compared with the basic quantity of the refrigerant to determine whether the refrigerant leaks or not.

Description

Refrigerating air-conditioning

The application is international application no is PCT/JP2010/001778, international filing date is on March 12nd, 2010, in the divisional application that on September 12nd, 2012 enters National Phase in China, application number is the application for a patent for invention " refrigerating air-conditioning " of 201080065367.1.

Technical field

The present invention relates to the high precision int of in the refrigerating air-conditioning formed by extending pipe arrangement via cold-producing medium and connect thermal source and outdoor unit and utilizing side and indoor unit, to calculate refrigerant loop inner refrigerant amount function.

Background technology

In the past, in the refrigerating air-conditioning of the divergence type formed by extending pipe arrangement via cold-producing medium and connect heat source machine and outdoor unit and utilizing side and indoor unit, there is following methods, that is: carry out cold-producing medium and extend pipe arrangement volume judgement operation (cold-producing medium extends two kinds of operations that in pipe arrangement, density is different under refrigeration), the cold-producing medium increase and decrease amount extended by cold-producing medium between two kinds of running statuses beyond pipe arrangement extends pipe arrangement variable density amount divided by cold-producing medium, calculate cold-producing medium and extend pipe arrangement volume, thus calculate refrigerant amount (for example, referring to patent document 1).

Look-ahead technique document

Patent document

Patent document 1: Japanese Unexamined Patent Publication 2007-163102 publication (summary)

Summary of the invention

Invent problem to be solved

But, pipe arrangement internal volume estimation method is extended for above-mentioned cold-producing medium, due to carry out be refrigerating air-conditioning arrange time cold-producing medium extend pipe arrangement internal volume calculate needed for cold-producing medium extend pipe arrangement internal volume and calculate and run operation special like this, so spend time, and cold-producing medium prolongation pipe arrangement internal volume calculating operation also difficulty is carried out to the refrigerating air-conditioning arranged.

The present invention makes in view of the above problems, and the service data that its object is to obtain when obtaining utilizing operation usually calculates the refrigerating air-conditioning that the internal volume of cold-producing medium prolongation pipe arrangement, the calculating can carrying out the cold-producing medium total amount in refrigerant loop accurately and refrigrant leakage detect exactly.

For solving the means of problem

Refrigerating air-conditioning involved in the present invention possesses: refrigerant loop, and this refrigerant loop extends pipe arrangement by cold-producing medium and connects as the outdoor unit of heat source unit and as the indoor unit utilizing side unit, measurement section, this measurement section measures the temperature and pressure of the major part of refrigerant loop as service data, calculation unit, the service data that this calculation unit has when obtaining service data obtains condition, when the running status represented by the service data measured by measurement section in usually running becomes the state meeting service data acquisition condition, obtain the service data that service data now learnt as the initial stage, repeatedly carry out such process, obtain the service data of study of multiple initial stage successively, the refrigerant amount extended beyond pipe arrangement and the process extending pipe arrangement density is calculated based on each service data, pipe arrangement internal volume is extended based on being calculated by this calculation result data group, the service data of the prolongation pipe arrangement internal volume calculated based on this and initial stage study calculates the benchmark refrigerant amount of the judgment standard as the refrigrant leakage from refrigerant loop, storage part, this storage part stores and extends pipe arrangement internal volume and benchmark refrigerant amount, and detection unit, this detection unit determines whether refrigrant leakage based on the prolongation pipe arrangement internal volume be stored in storage part and the service data that measured by measurement section in usually running.

The effect of invention

According to the present invention, even if for the equipment arranged, the service data obtained when usually running also can be utilized not run especially to calculate cold-producing medium prolongation pipe arrangement internal volume.In addition, pipe arrangement internal volume is extended owing to calculating based on the calculation result data group be made up of the refrigerant amount beyond multiple prolongation pipe arrangement and multiple prolongation pipe arrangement density, so, the impact that the measure error that can reduce measurement section is brought to the result of calculation extending pipe arrangement internal volume, can calculate accurately and extend pipe arrangement internal volume.Thus calculating and the refrigrant leakage that can carry out the cold-producing medium total amount in refrigerant loop accurately detect.

Accompanying drawing explanation

Fig. 1 is the refrigerant loop figure of the refrigerating air-conditioning 1 involved by an embodiment of the invention.

Fig. 2 is the figure that refrigerating air-conditioning control part 3 periphery of refrigerating air-conditioning 1 involved by an embodiment of the invention is formed.

P-h line chart when Fig. 3 is the refrigerating operaton of refrigerating air-conditioning 1 involved by an embodiment of the invention.

P-h line chart when Fig. 4 is the heating operation of refrigerating air-conditioning 1 involved by an embodiment of the invention.

Fig. 5 is the flow chart of the refrigrant leakage detection method of refrigerating air-conditioning 1 involved by an embodiment of the invention.

Fig. 6 is the flow chart of the initial stage study of refrigerating air-conditioning 1 involved by an embodiment of the invention.

Fig. 7 extends pipe arrangement density p for illustration of corresponding to _p, extend the refrigerant amount M of pipe arrangement _pwith the refrigerant amount M extended beyond pipe arrangement _{r_otherP}relative to the figure that the ratio of cold-producing medium total amount M changes.

Fig. 8 (a) is the refrigerant amount M with the prolongation pipe arrangement of Fig. 7 _pcorresponding line chart, (b) be with the prolongation pipe arrangement of Fig. 7 beyond refrigerant amount M _{r_otherP}corresponding line chart.

The cold-producing medium that Fig. 9 shows the refrigerating air-conditioning 1 represented involved by an embodiment of the invention extends pipe arrangement density p _pthe refrigerant amount M beyond pipe arrangement is extended with cold-producing medium _{r_otherP}between the figure of proximal line of relation.

Figure 10 is the figure of the overview of the refrigerant condition of the condenser 23 of the refrigerating air-conditioning 1 represented involved by an embodiment of the invention.

Figure 11 is the figure of the overview of the refrigerant condition of evaporimeter 42A, the 42B of the refrigerating air-conditioning 1 represented involved by an embodiment of the invention.

Detailed description of the invention

Below, be described based on the embodiment of accompanying drawing to refrigerating air-conditioning involved in the present invention.

The formation > of < equipment

Fig. 1 is the pie graph of the refrigerating air-conditioning 1 involved by an embodiment of the invention.Refrigerating air-conditioning 1 is that the freeze cycle by carrying out steam compression type is run and is used in the device of the cooling and warming of the indoor of high building etc.Refrigerating air-conditioning 1 mainly possesses: as the outdoor unit 2 of heat source unit, the multiple stage (in present embodiment being 2) that is connected in parallel with it as range site indoor unit 4A, 4B, liquid refrigerant extends pipe arrangement 6 and gas refrigerant extends pipe arrangement 7.It is connect outdoor unit 2 and indoor unit 4A, 4B and the pipe arrangement that passes through of cold-producing medium for liquid that liquid refrigerant extends pipe arrangement 6, forms by connecting liquid supervisor 6A, liquid tap 6a, 6b and distributor 51a.In addition, it is connect outdoor unit 2 and indoor unit 4A, 4B and pipe arrangement that supplied gas cold-producing medium passes through that gas refrigerant extends pipe arrangement 7, forms by connecting gas supervisor 7A, gas service pipe 7a, 7b and distributor 52a.

(indoor unit)

Indoor unit 4A, 4B are arranged on the ceiling of the indoor of high building etc. by burying or hang the mode such as to establish underground, or by the modes such as wall hanging wall disposed in the interior.Indoor unit 4A, 4B utilize liquid refrigerant prolongation pipe arrangement 6 to be connected with outdoor unit 2 with gas refrigerant prolongation pipe arrangement 7, form a part for refrigerant loop 10.

Then, the formation of indoor unit 4A, 4B is described.In addition, because indoor unit 4A, 4B are same formations, so be only described the formation of indoor unit 4A at this.The Reference numeral of the A of the formation of indoor unit 4B and each several part of replacing representation indoor unit 4A and to have marked the formation of the Reference numeral of B suitable.

Indoor unit 4A mainly has the indoor refrigerant loop 10a (being indoor refrigerant loop 10b in indoor unit 4B) of the part forming refrigerant loop 10.This indoor refrigerant loop 10a mainly has as the expansion valve 41A of expansion mechanism with as the indoor heat converter 42A utilizing side heat exchanger.

In the present embodiment, expansion valve 41A is adjustment of flow in order to carry out the cold-producing medium circulated in the refrigerant loop 10A of indoor etc. and the electric expansion valve be connected with the hydraulic fluid side of indoor heat converter 42A.

In the present embodiment, indoor heat converter 42A is the fin tube heat exchanger of the cross-fin formula be made up of heat-transfer pipe and multiple fin, is to play function when refrigerating operaton as the evaporimeter of cold-producing medium to play as the condenser of cold-producing medium the heat exchanger that function carrys out heating indoor air to cool room air, when heating operation.

In the present embodiment, indoor unit 4A have for room air is sucked in unit and after indoor heat converter 42A and cold-producing medium have carried out heat exchange supply air to indoor supply, as the indoor fan 43A of Air Blast fan.Indoor fan 43A is the fan of air quantity that can change the air supplied to indoor heat converter 42A, in the present embodiment, is the centrifugal fan that driven by DC fan motor or multiblade fan etc.

In addition, various sensor is provided with at indoor unit 4A.At the gas side of indoor heat converter 42A, 42B, be provided with gas side temperature sensor 33f, the 33i of the temperature (that is, corresponding with evaporating temperature Te when condensation temperature Tc during heating operation or refrigerating operaton refrigerant temperature) detecting cold-producing medium.In the hydraulic fluid side of indoor heat converter 42A, 42B, be provided with hydraulic fluid side temperature sensor 33e, the 33h of the temperature Teo detecting cold-producing medium.In the suction inlet side of the room air of indoor unit 4A, 4B, be provided with temperature (that is, the indoor temperature T detecting the room air flow in unit _r) indoor temperature transmitter 33g, 33j.In the present embodiment, each temperature sensor of above-mentioned 33e, 33f, 33g, 33h, 33i, 33j is made up of thermistor.

In addition, indoor unit 4A, 4B has indoor control part 32a, 32b of controlling the action of each several part forming indoor unit 4A, 4B.And, indoor control part 32a, 32b have the microcomputer of control that arranges in order to carry out indoor unit 4A, 4B or memory etc., can between the remote controller (not shown) for operating indoor unit 4A, 4B respectively, carry out the exchange of control signal etc. or between outdoor unit 2, carry out the exchange of control signal etc. via conveyer line.

(outdoor unit)

Outdoor unit 2 is arranged on the outdoor of high building etc., is responsible for 6A, liquid tap 6a, 6b and gas supervisor 7A, gas service pipe 7a, 7b and is connected with indoor unit 4A, 4B, form refrigerant loop 10 between indoor unit 4A, 4B by liquid.

Then, the formation of outdoor unit 2 is described.Outdoor unit 2 mainly has the outside refrigerant loop 10c of the part forming refrigerant loop 10.This outside refrigerant loop 10c mainly has compressor 21, cross valve 22, outdoor heat converter 23, accumulator 24, subcooler 26, hydraulic fluid side shutoff valve 28 and gas side shutoff valve 29.

Compressor 21 is the compressors that can change working capacity, in the present embodiment, is by utilizing the motor of convertor controls frequency F to carry out the positive displacement compressor driven.In the present embodiment, compressor 21 is only 1, but is not limited thereto, and the connection number of units etc. that also can correspond to indoor unit is connected in parallel the compressor of more than 2.

Cross valve 22 is the valves for switching flow of refrigerant direction.Cross valve 22 switches as shown by the solid line when refrigerating operaton, connects the discharge side of compressor 21 and the gas side of outdoor heat converter 23, and connects accumulator 24 and gas is responsible for 7A side.Thus, outdoor heat converter 23 plays function as the condenser of the cold-producing medium compressed by compressor 21, and in addition, indoor heat converter 42A, 42B play function as evaporimeter.Cross valve 22 switches as shown in the dotted line of cross valve when heating operation, and the discharge side and the gas that connect compressor 21 are responsible for 7A, and connect the gas side of accumulator 24 and outdoor heat converter 23.Thus, indoor heat converter 42A, 42B play function as the condenser of the cold-producing medium compressed by compressor 21, and in addition, outdoor heat converter 23 plays function as evaporimeter.

In the present embodiment, outdoor heat converter 23 is the fin tube heat exchangers of the cross-fin formula be made up of heat-transfer pipe and multiple fin.Outdoor heat converter 23 as described above, plays function when refrigerating operaton as the condenser of cold-producing medium, plays function when heating operation as the evaporimeter of cold-producing medium.The gas side of outdoor heat converter 23 is connected with cross valve 22, and hydraulic fluid side and liquid are responsible for 6A and are connected.

In the present embodiment, outdoor unit 2 have for outdoor air is sucked in unit and in outdoor heat converter 23, carried out heat exchange with cold-producing medium rear to outdoor discharge, as the outdoor fan 27 of Air Blast fan.This outdoor fan 27 is the fans of air quantity that can change the air supplied to outdoor heat converter 23, in the present embodiment, is the propeller type fan etc. that motor by being made up of DC fan motor carries out driving.

Accumulator 24 is the containers being connected between cross valve 22 and compressor 21, can being stored according to the variation etc. of the operating load of indoor unit 4A, 4B the residual refrigerant produced in refrigerant loop 10.

Subcooler 26 is heat exchangers of Double tube type, arranges in order to cool the cold-producing medium delivering to expansion valve 41A, 41B after condensation in outdoor heat converter 23.Subcooler 26 is connected between outdoor heat converter 23 and hydraulic fluid side shutoff valve 28 in the present embodiment.

In the present embodiment, the bypass circulation 71 as the cooling source of subcooler 26 is provided with.In addition, in the following description, the part eliminating bypass circulation 71 from refrigerant loop 10 is called main refrigerant circuit 10z.

Bypass circulation 71 is connected with main refrigerant circuit 10z, so that the suction side of a part from main refrigerant circuit 10z branch and to compressor 21 making heat exchanger 23 outdoor be sent to the cold-producing medium of expansion valve 41A, 41B returns.Specifically, bypass circulation 71 connects into, make heat exchanger 23 outdoor be sent to a part for the cold-producing medium of expansion valve 41A, 41B from the position branch between subcooler 26 and hydraulic fluid side shutoff valve 28, return via the bypass flow regulating valve 72 be made up of electric expansion valve and subcooler 26 suction side to compressor 21.Thus, the cold-producing medium of indoor expansion valve 41A, 41B delivered to by heat exchanger 23 outdoor, in subcooler 26, utilizes and cooled by the cold-producing medium flowing through bypass circulation 71 after bypass flow regulating valve 72 reduces pressure.That is, subcooler 26 is regulated by the aperture of bypass flow regulating valve 72 and carries out capability control.

Hydraulic fluid side shutoff valve 28 and gas side shutoff valve 29 are the valves being located at the connector be connected with the equipment of outside, pipe arrangement (being specifically that liquid is responsible for 6A and gas is responsible for 7A).

In addition, multiple pressure sensor and temperature sensor is provided with at outdoor unit 2.As pressure sensor, be provided with the suction pressure sensor 34a of suction pressure (low pressure refrigerant pressure) Ps detecting compressor 21 and detect discharge pressure (high-pressure refrigerant pressure) P of compressor 21 _ddischarge pressure sensor 34b.

Temperature sensor is made up of thermistor, as temperature sensor, be provided with inlet temperature sensor 33a, discharge temperature sensor 33b, heat exchange temperature sensor 33k, hydraulic fluid side temperature sensor 33l, liquid pipe temperature sensor 33d, bypass temperature sensor 33z and outdoor temperature sensor 33c.

Inlet temperature sensor 33a is located on the position between accumulator 24 and compressor 21, detects the inlet temperature Ts of compressor 21.Discharge temperature sensor 33b detects the discharge temperature T of compressor 21 _d.Heat exchange temperature sensor 33k detects the temperature of the cold-producing medium of circulation in outdoor heat converter 23.The hydraulic fluid side of hydraulic fluid side temperature sensor 33l heat exchanger 23 disposed in the outdoor, the refrigerant temperature of the hydraulic fluid side of sensing chamber's outer heat-exchanger 23.Liquid pipe temperature sensor 33d is arranged on the outlet of the main refrigerant circuit 10z side of subcooler 26, detects the temperature of cold-producing medium.Bypass temperature sensor 33z detects the temperature at the cold-producing medium of subcooler 26 outlet stream of bypass circulation 71.The suction inlet side of the outdoor air of outdoor temperature sensor 33c unit 2 disposed in the outdoor, detects the temperature of the outdoor air flowed in unit.

In addition, outdoor unit 2 has the outside control part 31 controlled the action of each key element forming outdoor unit 2.Further, outside control part 31 has the microcomputer of control, the memory that arrange in order to carry out outdoor unit 2 and controls the converter loop etc. of motor.Further, outside control part 31 is configured to the exchange carrying out control signal etc. between indoor control part 32a, 32b via conveyer line at indoor unit 4A, 4B.Outside control part 31 forms the control part 3 that the operation of carrying out refrigerating air-conditioning 1 entirety controls together with indoor control part 32a, 32b.

Fig. 2 is the controlling party block diagram of refrigerating air-conditioning 1.Control part 3 connects into the detection signal that can receive pressure sensor 34a, 34b, temperature sensor 33a ~ 33l, 33z, and, be connected with various equipment and valve various equipment (compressor 21, fan 27, fan 43A, 43B) and valve (cross valve 22, flow rate regulating valve (hydraulic fluid side shutoff valve 28, gas side shutoff valve 29, bypass flow regulating valve 72), expansion valve 41A, 41B) can be controlled based on these detection signals etc.

In addition, control part 3 possesses determination part 3a, calculation unit 3b, storage part 3c, detection unit 3d, drive division 3e, display part 3f, input part 3g and efferent 3h.Determination part 3a, being the position of the information measured from pressure sensor 34a, 34b and temperature sensor 33a ~ 33l, 33z, is the position forming measurement section together with pressure sensor 34a, 34b and temperature sensor 33a ~ 33l, 33z.Calculation unit 3b calculates cold-producing medium based on the information etc. measured by determination part 3a extend the internal volume of pipe arrangement or calculate the position of benchmark refrigerant amount of the judgment standard becoming refrigrant leakage from refrigerant loop 10.Storage part 3c stores the value that measured by determination part 3a or the value calculated by calculation unit 3b or stores internal volume data described later or initial stage charging quantity or the position stored from the information of outside.Detection unit 3d, be compare benchmark refrigerant amount that storage part 3c stores with by calculating the cold-producing medium total amount of the refrigerant loop 10 calculated to determine whether the position of refrigrant leakage.

Drive division 3e is the position of control of the key element that drives of the carrying out carrying out refrigerating air-conditioning 1 and compressor motor, valve, fan motor.Display part 3f, is this information of lower display such as situation about terminating in refrigerant charge or situation refrigrant leakage being detected and externally carries out notifying or being presented at the position of the exception produced in the operation of refrigerating air-conditioning 1.Input part 3g is the position of the input of the setting value of carrying out various control or the external information of change or input refrigerant charge amount etc.Efferent 3h is the position measured value measured by determination part 3a or the value calculated by calculation unit 3b externally exported.Efferent 3h can be for carrying out with external device (ED) the communication unit that communicates, and refrigerating air-conditioning 1 is configured to can to represent the refrigrant leakage of the testing result of refrigrant leakage with or without data by transmissions such as the administrative centers distally such as order wire.

The control part 3 of formation like this is switched by cross valve 22 and runs as the refrigerating operaton of operation usually and heating operation, and carries out the control of each equipment of outdoor unit 2 and indoor unit 4A, 4B according to the operating load of each indoor unit 4A, 4B.In addition, control part 3 carries out refrigrant leakage check processing described later.

(cold-producing medium prolongation pipe arrangement)

It is connect outdoor unit 2 with indoor unit 4A, 4B, for making the pipe arrangement needed for the refrigerant circulation in refrigerating air-conditioning 1 that cold-producing medium extends pipe arrangement.

It is have liquid refrigerant to extend the refrigerant piping that pipe arrangement 6 (liquid supervisor 6A, liquid tap 6a, 6b) and gas refrigerant extend pipe arrangement 7 (gas is responsible for 7A, gas service pipe 7a, 7b), construct at the scene when refrigerating air-conditioning 1 is arranged on the setting place of high building etc. that cold-producing medium extends pipe arrangement.The cold-producing medium of the caliber determined respectively with the combination of indoor unit 4A, 4B according to outdoor unit 2 is used to extend pipe arrangement.

Piping length is extended for cold-producing medium different because of the setting model at scene.For this reason, the internal volume extending pipe arrangement due to cold-producing medium is different because arranging scene, so cannot pre-enter when shipment.Thus, need to calculate to each scene the internal volume that cold-producing medium extends pipe arrangement.The details that cold-producing medium extends the computational methods of the internal volume of pipe arrangement will be described later.

In the present embodiment, in the connection of 1 outdoor unit 2 and 2 indoor units 4A, 4B, distributor 51a, 52a and cold-producing medium is used to extend pipe arrangement (liquid refrigerant extends pipe arrangement 6 and gas refrigerant extends pipe arrangement 7).Pipe arrangement 6 is extended for liquid refrigerant, is responsible for 6A by liquid and connects between outdoor unit 2 and distributor 51a, connect distributor 51a and each between indoor unit 4A, 4B by liquid tap 6a, 6b.Pipe arrangement 7 is extended for gas refrigerant, connects between indoor unit 4A, 4B and distributor 52a by gas service pipe 7a, 7b, be responsible for 7A by gas and connect between distributor 52a and outdoor unit 2.In the present embodiment, though distributor 51a, 52a employ T-tube, be not limited to this, also can use collector.In addition, when connecting multiple stage indoor unit, distributing with both can having used multiple T-tube, also can use collector.

As mentioned above, inside junction chamber, refrigerant loop 10a, 10b, outside refrigerant loop 10c and cold-producing medium extend pipe arrangement (liquid refrigerant extends pipe arrangement 6 and gas refrigerant extends pipe arrangement 7), form refrigerant loop 10.Refrigerating air-conditioning 1 has refrigerant loop 10 and bypass circulation 71.And, the refrigerating air-conditioning 1 of present embodiment utilizes the control part 3 be made up of indoor control part 32a, 32b and outside control part 31, run with switching refrigerating operaton and heating operation by cross valve 22, and, the control of each equipment of outdoor unit 2 and indoor unit 4A, 4B is carried out according to the operating load of each indoor unit 4A, 4B.

The action > of < refrigerating air-conditioning 1

Then, the action of each inscape during usual operation to the refrigerating air-conditioning 1 of present embodiment is described.

The refrigerating air-conditioning 1 of present embodiment carries out refrigerating operaton or heating operation as usually running, and carries out the control of the constitution equipment of outdoor unit 2 and indoor unit 4A, 4B according to the operating load of each indoor unit 4A, 4B.Below, be described by the order of refrigerating operaton, heating operation.

(refrigerating operaton)

P-h line chart when Fig. 3 is the refrigerating operaton of refrigerating air-conditioning 1 involved by an embodiment of the invention.Below, Fig. 3 and Fig. 1 is utilized to be described refrigerating operaton.

When refrigerating operaton, cross valve 22 becomes the state shown in the solid line of Fig. 1, that is, the discharge side of compressor 21 is connected with the gas side of outdoor heat converter 23 and the suction side of compressor 21 extends by gas side shutoff valve 29 and gas refrigerant the state that pipe arrangement 7 (gas is responsible for 7A, gas service pipe 7a, 7b) is connected with the gas side of indoor heat converter 42A, 42B.In addition, hydraulic fluid side shutoff valve 28, gas side shutoff valve 29 and bypass flow regulating valve 72 are all open mode.

Then, the flowing of the cold-producing medium of the main refrigerant circuit 10z in refrigerating operaton is described.

The flowing of the cold-producing medium in refrigerating operaton becomes the solid arrow of Fig. 1.The high-temperature high-pressure gas refrigerant (Fig. 3 point I) compressed by compressor 21 arrives outdoor heat converter 23 through cross valve 22, carries out condensation liquefaction (Fig. 3 point RO) by the air-supply effect of fan 27.Condensation temperature is now tried to achieve by heat exchange temperature sensor 33k, or tries to achieve by carrying out saturation temperature conversion to the pressure of discharge pressure sensor 34b.

The cold-producing medium having been carried out condensation liquefaction by outdoor heat converter 23 makes degree of subcooling become further greatly (Fig. 3 point HA) by subcooler 26.The degree of subcooling that subcooler 26 now exports is tried to achieve by deducting the temperature of the liquid pipe temperature sensor 33d of the outlet side being arranged on subcooler 26 from above-mentioned condensation temperature.

Afterwards, cold-producing medium is via hydraulic fluid side shutoff valve 28, extend in pipe arrangement 6 i.e. liquid supervisor 6A, liquid tap 6a, 6b at liquid refrigerant and make pressure drop (Fig. 3 point NI) by pipe wall friction, deliver to range site 4A, 4B, reduced pressure by expansion valve 41A, 41B, become the gas-liquid two-phase cold-producing medium (Fig. 3 point HO) of low pressure.Gas-liquid two-phase cold-producing medium is undertaken gasify (Fig. 3 point HI) by the air-supply effect of indoor fan 43A, 43B by evaporimeter and indoor heat converter 42A, 42B.

Evaporating temperature is now measured by hydraulic fluid side temperature sensor 33e, 33h, and the degree of superheat SH of the cold-producing medium of the outlet of each indoor heat converter 42A, 42B tries to achieve by deducting from the refrigerant temperature value detected by gas side temperature sensor 33f, 33i by the refrigerant temperature of hydraulic fluid side temperature sensor 33e, 33h detection.Each expansion valve 41A, 41B are subject to aperture and regulate, so that the degree of superheat SH of the cold-producing medium of the outlet of indoor heat converter 42A, 42B (that is, the gas side of indoor heat converter 42A, 42B) becomes degree of superheat desired value SHm.

The gas refrigerant (Fig. 3 point HI) that have passed through indoor heat converter 42A, 42B arrives gas refrigerant and extends pipe arrangement 7 i.e. gas service pipe 7a, 7b and gas supervisor 7A, makes pressure drop (Fig. 3 point TO) by the pipe wall friction of the pipe arrangement through these pipe arrangements.Further, cold-producing medium returns to compressor 21 through gas side shutoff valve 29 and accumulator 24.

Then, the flowing of the cold-producing medium in bypass circulation 71 is described.The entrance of bypass circulation 71 exports between hydraulic fluid side shutoff valve 28 at subcooler 26, make by a part of branch of the chilled high pressure liquid refrigerant of subcooler 26 (Fig. 3 point HA), after becoming low pressure two-phase system cryogen being reduced pressure by bypass flow regulating valve 72 (Fig. 3 point TI), flow into subcooler 26.In subcooler 26, the high pressure liquid refrigerant of the cold-producing medium and main refrigerant circuit 10z that have passed through the bypass flow regulating valve 72 of bypass circulation 71 carries out heat exchange, cools the high pressure liquid refrigerant circulated in main refrigerant circuit 10z.Thus, the cold-producing medium evaporation gasification of flowing in bypass circulation 71, returns (Fig. 3 point TO) to compressor 21.

Now, bypass flow regulating valve 72 is subject to aperture adjustment, so that the degree of superheat SHb of the cold-producing medium of the outlet of bypass circulation 71 side of subcooler 26 becomes degree of superheat desired value SHbm.In the present embodiment, the degree of superheat SHb of the cold-producing medium of the outlet of bypass circulation 71 side of subcooler 26, is detected by the saturation temperature scaled value of the suction pressure Ps deducting the compressor 21 detected by suction pressure sensor 34a from the refrigerant temperature detected by bypass temperature sensor 33z.In addition, though do not adopt in the present embodiment, but also can between bypass flow regulating valve 72 and subcooler 26 set temperature sensor, by deducting by the refrigerant temperature value of this temperature sensor measurement from the refrigerant temperature value measured by bypass temperature sensor 33z, be detected the degree of superheat SHb of the cold-producing medium of the outlet of the bypass circulation side of cooler 26.

In addition, in the present embodiment, bypass circulation 71 entrance is in subcooler 26 and exports between hydraulic fluid side shutoff valve 28, but also can between heat exchanger 23 disposed in the outdoor and subcooler 26.

(heating operation)

P-h line chart when Fig. 4 is the heating operation of refrigerating air-conditioning 1 involved by an embodiment of the invention.Below, Fig. 4 and Fig. 1 is utilized to be described heating operation.

When heating operation, cross valve 22 becomes the state shown in the dotted line of Fig. 1, that is, the discharge side of compressor 21 extends pipe arrangement 7 (gas is responsible for 7A, gas service pipe 7a, 7b) by gas side shutoff valve 29 and gas refrigerant and is connected with the gas side of indoor heat converter 42A, 42B and the state that is connected with the gas side of outdoor heat converter 23 of the suction side of compressor 21.In addition, hydraulic fluid side shutoff valve 28 and gas side shutoff valve 29 become open mode, and bypass flow regulating valve 72 becomes closed condition.

Then, the flowing of the cold-producing medium of the main refrigerant circuit 10z of heating operation is described.

The flowing heating the cold-producing medium under condition becomes the dotted arrows of Fig. 1.The high-temperature high-pressure refrigerant (Fig. 4 point I) compressed by compressor 21 is responsible for 7A, gas service pipe 7a, 7b through refrigerant gas prolongation pipe arrangement and gas, now make pressure drop (Fig. 4 point RO) by pipe wall friction, arrive indoor heat converter 42A, 42B.In indoor heat converter 42A, 42B, carry out condensation liquefaction (Fig. 4 point HA) by the air-supply effect of indoor fan 43A, 43B, reduced pressure by expansion valve 41A, 41B and become the gas-liquid two-phase cold-producing medium (Fig. 4 point NI) of low pressure.

Now, expansion valve 41A, 41B are subject to aperture adjustment, so that the degree of subcooling SC of the cold-producing medium of the outlet of indoor heat converter 42A, 42B is constant with degree of subcooling desired value SCm.In the present embodiment, the degree of subcooling SC of the cold-producing medium of the outlet of indoor heat converter 42A, 42B, by the discharge pressure P of compressor 21 will detected by discharge pressure sensor 34b _dbe converted into the saturation temperature value corresponding with condensation temperature Tc, deduct the refrigerant temperature value detected by hydraulic fluid side temperature sensor 33e, 33h from the saturation temperature value of this cold-producing medium, thus detect.

In addition, though do not adopt in the present embodiment, but the temperature sensor detected the temperature of the cold-producing medium flowed in each indoor heat converter 42A, 42B also can be set, by deducting the refrigerant temperature value corresponding with condensation temperature Tc detected by said temperature sensor from the refrigerant temperature value detected by hydraulic fluid side temperature sensor 33e, 33h, the degree of subcooling SC of the cold-producing medium of the outlet of sensing chamber's inside heat exchanger 42A, 42B thus.Afterwards, the gas-liquid two-phase cold-producing medium of low pressure liquid refrigerant extend in pipe arrangement 6 i.e. liquid supervisor 6A, liquid tap 6a, 6b make pressure drop by pipe wall friction after (Fig. 4 point HO), arrive outdoor heat converter 23 via hydraulic fluid side shutoff valve 28.In outdoor heat converter 23, evaporate gasification (Fig. 4 point HI) by the air-supply effect of outdoor fan 27, return to compressor 21 via cross valve 22, accumulator 24.

(refrigrant leakage detection method)

Then, the flow process of refrigrant leakage detection method is described.In addition, in the operation of refrigerating air-conditioning 1, implement refrigrant leakage all the time and detect.In addition, refrigerating air-conditioning 1 sends the refrigrant leakage of the testing result representing refrigrant leakage with or without data via order wire to administrative center (not shown) etc., is formed as the formation can carrying out remote monitoring.

In the present embodiment, calculating cold-producing medium total amount in the refrigerating air-conditioning 1 that is filled in and arranged, detect the method whether cold-producing medium leak and be described.

Below, Fig. 5 is utilized to be described refrigrant leakage detection method.At this, Fig. 5 is the flow chart of the flow process of the refrigrant leakage check processing represented in the refrigerating air-conditioning 1 of an embodiment of the invention.Refrigrant leakage is detected, does not carry out the specific run detected for refrigrant leakage, but carry out in common refrigerating operaton or heating operation, utilize these operating service datas to carry out refrigrant leakage detection.That is, control part 3 carries out usually running while carry out the process of the flow chart of Fig. 5.At this, so-called service data, refers to the data representing running status amount, is specifically each measured value obtained by each pressure sensor 34a, 34b, temperature sensor 33a ~ 33l, 33z.

First, for the machine acquisition of information of step S1, the internal volume of each inscape parts needed for control part 3 calculates from the storage part 3c refrigerant amount obtained among refrigerant loop 10.At this, obtain the internal volume that liquid refrigerant extends each inscape parts of the part beyond pipe arrangement 6 and gas refrigerant prolongation pipe arrangement 7.That is, the internal volume of each pipe arrangement in each pipe arrangement in indoor unit 4A, 4B and each equipment (compressor 21, outdoor heat converter 23 and subcooler 26) respective internal volume and outdoor unit 2 and each equipment (indoor heat converter 42A, 42B) is obtained.The cold-producing medium calculated in refrigerant loop 10 extends the internal volume data needed for refrigerant amount of the part beyond pipe arrangement, is stored in advance in the storage part 3c of control part 3.The storage of the storage part 3c to control part 3 of these internal volume data, both can input via input part 3g by arranging personnel, also can be configured to arrange outdoor unit 2 and indoor unit 4A, 4B go forward side by side Serial Communication setting time carried out communicating with the administrative center etc. of outside by control part 3 and automatically obtain.

Then, in step s 2, control part 3 collects current service data (data that each temperature sensor 33a ~ 33l, 33z and pressure sensor 34a, 34b obtain).In addition, the refrigrant leakage for present embodiment detects, due to only to make refrigerating air-conditioning 1 run required common data to judge that cold-producing medium has No leakage, so, do not need the time adding new sensor in order to carry out refrigrant leakage detection.

Then, in step s3, confirm whether the service data collected by step S2 is stable data, if stablize data then transfer to step S4.Such as, the rotating speed of compressor 21 has the aperture of variation or expansion valve 41A, 41B to have a variation when starting etc., the action of refrigerant circulation is unstable, thus, service data collected by step S2 can judge that current running status is unstable, in this case, do not implement refrigrant leakage to detect.

In step s 4 which, the stable data (service data) utilizing step S3 to obtain, the liquid refrigerant calculated among refrigerant loop 10 extends the density of the cold-producing medium of the part beyond pipe arrangement 6 and gas refrigerant prolongation pipe arrangement 7.Data required when the density of cold-producing medium is owing to being calculating refrigerant amount, so, undertaken asking calculation by step S4.The calculating of the density of each cold-producing medium of among refrigerant loop 10, beyond liquid refrigerant prolongation pipe arrangement 6 and gas refrigerant prolongation pipe arrangement 7 part and each inscape parts process, can be implemented by known method.That is, substantially can calculate according to pressure and temperature the density that cold-producing medium is any one single-phase portion in liquid or gas.Such as, from compressor 21 to outdoor heat converter 23, cold-producing medium is gaseous state, and the gas refrigerant density of this part can be calculated by the discharge pressure detected by discharge pressure sensor 34b and the discharge temperature detected by discharge temperature sensor 33b.

In addition, in the two-phase portion of heat exchanger etc., state vicissitudinous two-phase portion density, utilizes approximate expression to calculate two-phase density average according to equipment gateway quantity of state.These calculation needed for approximate expression etc. be pre-stored in storage part 3c, the service data that control part 3 utilizes step S3 to obtain and the data of the approximate expression be stored in advance in storage part 3c etc., calculate among refrigerant loop 10, that liquid refrigerant extends the part beyond pipe arrangement 6 and gas refrigerant prolongation pipe arrangement 7 each inscape parts refrigerant density separately.

Then, the presence or absence that initial stage study is implemented is confirmed in step s 5.So-called initial stage study, refers to that calculating liquid refrigerant extends the internal volume of pipe arrangement 6 and gas refrigerant and extend the internal volume of pipe arrangement 7 or calculate the process of the required benchmark refrigerant amount of presence or absence for detecting refrigrant leakage.The internal volume of each inscape of indoor unit or outdoor unit is determined by equipment various species and is known, relative to this, cold-producing medium extends pipe arrangement and makes according to on-the-spot setting model piping length different as described above, thus, the internal volume that cold-producing medium cannot be extended pipe arrangement is set in advance in storage part 3c as given data.In addition, this example is using the refrigerating air-conditioning 1 that arranged as object, and from this point, the internal volume that cold-producing medium extends pipe arrangement is also unknown.Thus for initial stage study, actual motion refrigerating air-conditioning after arranging, utilizes operating service data to calculate the internal volume that cold-producing medium extends pipe arrangement.The internal volume that the cold-producing medium once calculated in study in the early stage extends pipe arrangement (liquid refrigerant extends pipe arrangement 6 and gas refrigerant extends pipe arrangement 7) is used repeatedly when refrigrant leakage after this detects.For the initial stage, the details of study will be described later.In the judgement of step S5, if do not carry out initial stage study, then enter into step S6, if the initial stage of carrying out study, then enter into step S8.

In step s 6, confirm whether current running status meets initial stage study beginning condition.Initial stage study beginning condition, can be described as judging whether current running status is in the condition that accurately can calculate the state of cold-producing medium total amount, the following such condition of such as setting.That is, about the refrigerant amount of accumulator 24 inside, the cold-producing medium regarded as in accumulator 24 is all gas, utilizes Saturated vapor density to calculate.For this reason, when be detained in accumulator 24 have a remaining liq cold-producing medium time, if ignore liquid refrigerant to calculate refrigerant amount as gas refrigerant with whether being detained, understand and cannot calculate refrigerant amount accurately.Thus the value that the refrigerant amount as accumulator 24 calculates becomes the value comparing the little amount suitable with remaining liq refrigerant amount of actual value, this error count is calculated and is had an impact and cannot calculate the benchmark refrigerant amount M of step S35 described later exactly _rSTD.Thus, be detained in accumulator 24 like this have a state of remaining liq cold-producing medium time, do not implement initial stage study.That is, as initial stage study beginning condition, what specify is do not have cold-producing medium to be detained in accumulator 24.

As the judgement of whether being detained cold-producing medium in accumulator 24, based on current service data, be whether more than 0 to judge by the degree of superheat SH (degree of superheat of the entrance of compressor 21) of the cold-producing medium of the outlet of each indoor heat converter 42A, 42B.That is, when degree of superheat SH is more than 0, be judged as not having cold-producing medium to be detained in accumulator 24, when degree of superheat SH is less than 0, be judged as having cold-producing medium to be detained in accumulator 24.

As mentioned above, judge whether to meet initial stage study beginning condition, when running status meets initial stage condition for study, transfer to initial stage study process (S7), in ungratified situation, turn back to step S2 and proceed usual operation.For the initial stage, the details of study is described later.

In step s 8, calculating the refrigerant amount of each inscape of refrigerant loop 10, by adding up to these refrigerant amounts, calculating the cold-producing medium total amount M being filled in refrigerating air-conditioning 1 _r.After the determination part 3a by Fig. 2 obtains various sensor information, utilize these determination datas and be stored in various data in storage part 3c that (internal volume of each inscape parts, volumetric ratio α, liquid refrigerant extend the internal volume V of pipe arrangement 6 _pL, gas refrigerant extends the internal volume V of pipe arrangement 6 _pGdeng), calculate cold-producing medium total amount M by calculation unit 3b _r.In addition, the liquid refrigerant in storage part 3c extends the internal volume V of pipe arrangement 6 _pLthe internal volume V of pipe arrangement 7 is extended with gas refrigerant _pGcalculate by initial stage study and be stored.

Refrigerant amount is tried to achieve by refrigerant density being multiplied with internal volume.Thus the cold-producing medium about refrigerant loop 10 extends the refrigerant amount M of the part beyond pipe arrangement _{r_otherP}, can carry out asking calculation based on the density of the cold-producing medium through various piece and the internal volume data be stored in storage part 3c.In addition, the refrigerant amount M of pipe arrangement is extended _p(liquid refrigerant extends the additive quantity of the refrigerant amount of pipe arrangement 6 and the refrigerant amount of gas refrigerant prolongation pipe arrangement 7), utilizes the liquid refrigerant being learnt to obtain by the initial stage to extend the internal volume V of pipe arrangement 6 _pL, gas refrigerant extends the internal volume V of pipe arrangement 7 _pG, liquid refrigerant extends the refrigerant density ρ of pipe arrangement 6 _pLthe refrigerant density ρ of pipe arrangement 7 is extended with gas refrigerant _pGcalculate.About cold-producing medium total amount M _rthe details of computational methods be described later.

(step S9: the leak judgement of refrigerant amount)

In step s 9, benchmark refrigerant amount (initial stage charging quantity) M that initial stage study described later obtains is carried out _rSTDthe cold-producing medium total amount M calculated with step S8 _rcomparison, if M _rSTD=M _rthen be judged as without refrigrant leakage, if M _rSTD> M _rthen be judged as refrigrant leakage.When judging without refrigrant leakage, send the normal information of refrigerant amount by step S10.When having judged refrigrant leakage, sent the information having refrigrant leakage by step S11.The information of step S10 and step S11 sends, except such as except display part 3f carries out showing etc. carrying out, also by represent refrigerant amount leak with presence or absence of the refrigrant leakage of testing result send (information transmission) with or without data by the administrative center distally such as order wire.In addition, at this, at cold-producing medium total amount M _rbe not equal to initial stage charging quantity M _rSTDwhen, be judged as refrigrant leakage, but existed when refrigerant amount calculates because sensor error etc. causes cold-producing medium total amount M _rvalue change situation, thus, also can consider this point basis on determine decision threshold with presence or absence of refrigrant leakage.

Control part 3, after having carried out normal, abnormal information and having sent, shifts to returning (RETURN), the process again repeatedly from step S1.By the process repeatedly from above-mentioned steps S1 to step S11, in usually running, carry out refrigrant leakage detection all the time.

(step S7: the initial stage learns)

Fig. 6 is the flow chart of the initial stage study of refrigerating air-conditioning 1 involved by an embodiment of the invention.Below, Fig. 6 is utilized to be described initial stage study.For initial stage study, carry out internal volume calculating and benchmark refrigerant amount that cold-producing medium extends pipe arrangement _dthese two kinds of operations of calculating.Benchmark refrigerant amount M _rSTD, be become judge cold-producing medium when carrying out refrigrant leakage and detecting leakage with presence or absence of the datum quantity of benchmark.Easy leakage is become because cold-producing medium passed through along with the time, so, benchmark refrigerant amount M _rSTDcalculating have the necessity of as far as possible carrying out immediately after refrigerating air-conditioning 1 is arranged.In addition, refrigerating operaton is carried out at this.

First, in the step s 21, judge whether current running status obtains consistent with the service data preset.Current running status and service data obtain condition inconsistent during, turn back to the step S2 of Fig. 5, become obtain consistent running status with service data before all repeatedly carry out the process of step S2 ~ S7.In the present embodiment, be characterised in that, do not utilize special operational mode just can carry out the calculating of the internal volume of cold-producing medium prolongation pipe arrangement (liquid refrigerant extends pipe arrangement 6 and gas refrigerant extends pipe arrangement 7) according to the service data obtained in usually running, as the service data used when cold-producing medium extends the calculating of the internal volume of pipe arrangement, use the service data during running status of the service data acquisition condition meeting regulation.In addition, service data when initial stage charging quantity is known obtains condition both can to learn beginning condition identical with the initial stage of step S21, also can specify other condition.No matter which kind of is, service data obtains the running status that condition all specifies the calculating of the having stable behavior making refrigerant circulation, the internal volume that can carry out cold-producing medium prolongation pipe arrangement accurately.Specifically, the condition of following (A) ~ (C) is such as enumerated.

(A) as the variation of each running status such as running frequency, expansion valve opening, the rotation speed of the fan being installed on indoor and outdoor heat exchanger of the compressor of the key element equipment of refrigerating air-conditioning, be all in respectively in certain constant scope.This variation just specifying actuator is little.

(B) be installed on the value of discharge pressure sensor (high-pressure pressure sensor) 34b of refrigerating air-conditioning 1 for more than certain steady state value, and the value of suction pressure sensor (low-pressure sensor) 34a is below certain steady state value.

(C) refrigerant temperature (evaporating temperature) in indoor heat converter 42A, 42B of refrigerating air-conditioning 1 is within steady state value with the amplitude of fluctuation of the difference of indoor temperature, and the refrigerant temperature (condensation temperature) in outdoor heat converter 23 is within steady state value with the amplitude of fluctuation of the difference of the outdoor temperature measured by outdoor temperature sensor 33c.

Further, in step S22, when current running status becomes the running status meeting service data acquisition condition, service data now is automatically obtained maintenance (S22) as the service data that the initial stage learns.

Then, in step S23, S24, usual service data is utilized to calculate prolongation pipe arrangement density p _pthe refrigerant amount M beyond pipe arrangement is extended with cold-producing medium _{r_otherP}.According to a service data, calculate respectively and extend pipe arrangement density p _pthe refrigerant amount M beyond pipe arrangement is extended with cold-producing medium _{r_otherP}, each result of calculation is stored in storage part 3c.Extend pipe arrangement density p _pbe consider the pipe arrangement density of hydraulic fluid side and gas side both sides and the value calculated, calculated by ensuing (1) formula.

ρ _P＝ρ _PL+αρ _PG…(1)

At this, ρ _pLthat liquid refrigerant extends pipe arrangement average refrigerant density (extending pipe arrangement density hereinafter referred to as liquid refrigerant) [kg/m ³], try to achieve according to condensing pressure (obtaining by converting to the condensation temperature Tc obtained by heat exchange temperature sensor 33k) with by the outlet temperature of the subcooler 26 of liquid pipe temperature sensor 33d acquisition.

In addition, ρ _pG, be that gas refrigerant extends pipe arrangement average refrigerant density (extending pipe arrangement density hereinafter referred to as gas refrigerant) [kg/m ³], tried to achieve by the mean value of the refrigerant density of the suction side of compressor 21 and the outlet refrigerant density of indoor heat converter 42A, 42B.The refrigerant density of the suction side of compressor 21 is tried to achieve according to suction pressure Ps and inlet temperature Ts.In addition, the outlet refrigerant density of indoor heat converter 42A, 42B, tries to achieve according to the scaled value of evaporating temperature Te and the outlet temperature of evaporating pressure Pe and indoor heat converter 42A, 42B.

In addition, α, is that liquid refrigerant prolongation pipe arrangement 6 extends the volumetric ratio of pipe arrangement 7 with gas refrigerant, is pre-stored in the storage part 3c of control part 3.

Cold-producing medium extends the refrigerant amount M beyond pipe arrangement _{r_otherP}, be by condenser refrigerant amount M _rc, evaporator refrigeration dosage M _re, accumulator refrigerant amount M _rACC, oil dissolves refrigerant amount M _rOILall be added together the value obtained, the computational methods of each refrigerant amount are described later.

Then, whether the refrigerant amount confirming to be filled with at the initial stage being provided with refrigerating air-conditioning 1 is known (inputting) (S25).Such as when newly arranging the situation or the situation leaving the record of initial stage charging quantity at storage part 3c etc. of refrigerating air-conditioning 1, initial stage charging quantity is when being known, shift to step S26.In addition, such as do not stay in the refrigerating air-conditioning 1 arranged the situation of the record of initial stage charging quantity etc., initial stage charging quantity not clear, shift to step S30.

In step S26 ~ S29, flow process when being known to initial stage charging quantity is described.

(initial stage charging quantity is known situation)

Because liquid refrigerant extends the internal volume V of pipe arrangement 6 _pLnot clear, so, at internal volume V _pLfor determining the formula of cold-producing medium total amount Mr under the state of unknown number.Now, gas refrigerant extends the internal volume V of pipe arrangement 7 _pGliquid refrigerant is utilized to extend pipe arrangement internal volume V according to following (2) formula _pLcalculate.

V _PG＝αV _PL…(2)

At this, the liquid refrigerant density that the gas refrigerant density that gas refrigerant extends pipe arrangement 7 extends pipe arrangement 6 relative to liquid refrigerant is little of tens of/mono-times, compares the internal volume V that liquid refrigerant extends pipe arrangement 6 _pL, gas refrigerant extends the internal volume V of pipe arrangement 7 _pGgive the impact that total amount Mr brings of calculating cold-producing medium little.For this reason, be not calculate the internal volume V that gas refrigerant extends pipe arrangement 7 separately respectively _pGthe internal volume V of pipe arrangement 6 is extended with liquid refrigerant _pL, but only consider the difference in pipe arrangement footpath, the internal volume V of pipe arrangement 6 is extended according to liquid refrigerant _pLabove-mentioned (2) formula is utilized to calculate the internal volume V of gas refrigerant prolongation pipe arrangement 7 simply _pG.In addition, volumetric ratio α is stored in the storage part 3c of control part 3 in advance.

In step S26 and step S27, as mentioned above, the internal volume V of pipe arrangement 6 is extended at liquid refrigerant _pLfor under the state of unknown number, the service data of the initial stage study using step S22 to obtain is to determine cold-producing medium total amount M _rformula, utilize the cold-producing medium total amount M that this formula obtains _rwith known initial stage charging quantity M _rSTDequal situation, calculates the internal volume V that liquid refrigerant extends pipe arrangement 6 _pL.This cold-producing medium total amount M _rcalculating same with the computational methods of the cold-producing medium total amount in above-mentioned step S8.

M _r＝V _PL×ρ _PL+(α×V _PL)×ρ _PG+M _{r_otherP}

＝M _rSTD

According to above content, liquid refrigerant extends the internal volume V of pipe arrangement 6 _pLcalculate by following formula.

V _PL＝(M _rSTD－M _{r_otherP})/(ρ _PL+α×ρ _PG)

Wherein, ρ _pL: liquid refrigerant extends the refrigerant density of pipe arrangement 6, α: liquid refrigerant prolongation pipe arrangement 6 and gas refrigerant extend the volumetric ratio of pipe arrangement 7, ρ _pG: gas refrigerant extends the refrigerant density of pipe arrangement 7, M _{r_otherP}: the cold-producing medium of refrigerant loop 10 extends the refrigerant amount of the part beyond pipe arrangement.

In addition, at this cold-producing medium total amount M _rformula among, internal volume V _pLwith beyond volumetric ratio α be the known value that can calculate according to service data.

Then, in step S28, the liquid refrigerant of being tried to achieve by step S26 extends the internal volume V of pipe arrangement 6 _pLbe updated in above-mentioned (2) formula, calculate the internal volume V that gas refrigerant extends pipe arrangement 7 _pG.

Further, the liquid refrigerant calculated by above process is extended pipe arrangement internal volume V _pL, gas refrigerant extends pipe arrangement internal volume V _pG, benchmark refrigerant amount (being initial stage charging quantity when charging quantity is known in the early stage) M _rSTDbe recorded to the storage part 3c of memory etc., initial stage study (S29) when end initial stage charging quantity is known.

As described above, when charging quantity is known in the early stage, can calculate by once running the internal volume that cold-producing medium extends pipe arrangement.

(situation that initial stage charging quantity is not clear)

When charging quantity is known in the early stage, service data is one, the calculating that cold-producing medium extends pipe arrangement internal volume can be carried out, but when charging quantity is not clear in the early stage, if do not obtain the service data of multiple (more than 2), cold-producing medium cannot be calculated and extend pipe arrangement internal volume.Thus judge whether in step s 30 to obtain multiple service data, if do not obtain multiple service data, then the step S2 returning Fig. 5 proceeds usually to run until become and obtain consistent running status with service data.On the other hand, when judging in step s 30 to obtain multiple service data, approximate expression computing is entered.Thus, when entering into approximate expression computing, in storage part 3c, storing multiple cold-producing medium calculated respectively based on multiple service data and extending pipe arrangement density p _pthe refrigerant amount M beyond pipe arrangement is extended with cold-producing medium _{r_otherP}, in approximate expression computing, (multiple cold-producing medium extends pipe arrangement density p to utilize this calculation result data group _pthe refrigerant amount M beyond pipe arrangement is extended with multiple cold-producing medium _{r_other}), formulate and represent that cold-producing medium extends pipe arrangement density and extends the approximate expression of the relation between the refrigerant amount beyond pipe arrangement.

Approximate expression is the approximate expression needed in the internal volume calculating cold-producing medium prolongation pipe arrangement, is described below to the Computing Principle calculating cold-producing medium prolongation pipe arrangement internal volume according to approximate expression.

Fig. 7 extends pipe arrangement density p for illustration of corresponding to _p, extend the refrigerant amount M of pipe arrangement _pwith the refrigerant amount M extended beyond pipe arrangement _{r_otherP}relative to the figure that the ratio of cold-producing medium total amount M changes.In the figure 7, the part of shade is with to represent the refrigerant amount M extending pipe arrangement _p, the part not with shade represents the refrigerant amount M extended beyond pipe arrangement _{r_otherP}.Shown in Fig. 7, be M being filled to the cold-producing medium total amount M in refrigerant loop 10 _rtime, for prolongation pipe arrangement density p _plittle situation (ρ 1) and large situation (ρ 2), extend the refrigerant amount M of pipe arrangement _pwith the refrigerant amount M extended beyond pipe arrangement _{r_otherP}relative to cold-producing medium total amount M _rratio change.

At this, when the refrigerant condition in refrigerant loop 10 changes, extends pipe arrangement density p _pwhen changing to ρ 2 from ρ 1, extend the refrigerant amount M of pipe arrangement _pincrease Δ M, the opposing party, extend the refrigerant amount M beyond pipe arrangement _{r_otherP}reduce on the contrary and refrigerant amount M _pthe Δ M increased measures accordingly, and its variable quantity is identical.Extend the refrigerant amount M beyond pipe arrangement _{r_otherP}with prolongation pipe arrangement density p _powing to calculating according to service data as illustrated in step S23, S24 respectively, so, also can calculate Δ M.According to this point, below, pipe arrangement density p is being extended to utilization _pcold-producing medium variable quantity changing to ρ 2 from certain density p 1 is respectively at the refrigerant amount M extending pipe arrangement _pwith the refrigerant amount M extended beyond pipe arrangement _{r_otherP}in equal situation, calculate cold-producing medium and extend pipe arrangement internal volume V _porder be described.

Fig. 8 (a) is the refrigerant amount M with the prolongation pipe arrangement of Fig. 7 _pcorresponding line chart, illustrates and extends pipe arrangement density p _pwith the refrigerant amount M extending pipe arrangement _pbetween relation.Fig. 8 (b) be with the prolongation pipe arrangement of Fig. 7 beyond refrigerant amount M _{r_otherP}corresponding line chart, illustrates and extends pipe arrangement density p _pwith the refrigerant amount M extended beyond pipe arrangement _{r_otherP}between relation.

At this, because refrigerant amount calculates by internal volume and the amassing of density, so, M _p=V _p× ρ _psuch relation is set up.For this reason, the gradient V of Fig. 8 (a) _pwith current for asking the internal volume V of the prolongation pipe arrangement of calculation _pquite.But, due to V _pand M _pboth sides be all unknown number, so gradient V cannot be tried to achieve by Fig. 8 (a) _p.But, in prolongation pipe arrangement density p _pcold-producing medium variable quantity when changing to ρ 2 from ρ 1, owing to being Δ M too for the part extended beyond pipe arrangement, so the gradient of Fig. 8 (b) is equal with the gradient of Fig. 8 (a).Extend the refrigerant amount M beyond pipe arrangement _{r_otherP}with prolongation pipe arrangement density p _powing to calculating according to service data as illustrated in step S23, S24 respectively, so, also can calculate gradient-V _p.Thus, by the gradient of calculating chart 8 (b), ask and calculate its absolute value, refrigerant piping internal volume V can be tried to achieve thus _p.

At this, extend the refrigerant amount M of pipe arrangement _p, be liquid refrigerant is extended the amount that refrigerant amount that the refrigerant amount of pipe arrangement 6 and gas refrigerant extend pipe arrangement 7 is added together, calculated by ensuing (3) formula.

M _P＝(V _PL×ρ _PL)+(V _PG×ρ _PG)…(3)

Gas refrigerant extends the internal volume V of pipe arrangement 7 _pGutilize and use liquid refrigerant to extend pipe arrangement internal volume V according to above-mentioned (2) formula _pLcarry out the situation represented, if above-mentioned (2) formula be updated in (3) formula, then obtain ensuing (4) formula.

M _P＝(V _PL×ρ _PL)+(αV _PL×ρ _PG)…(4)

If (4) formula of arrangement, then obtain (5) formula.

M _P＝(ρ _PL+αρ _PG)·V _PL…(5)

ρ _pL+ α ρ _pGdue to prolongation pipe arrangement density p _pequal, so the absolute value of the gradient of Fig. 8 (b) and liquid refrigerant extend pipe arrangement internal volume V _pLquite.Thus, by asking the absolute value of the gradient of nomogram 8 (b), liquid refrigerant can be calculated and extend pipe arrangement internal volume V _pL, in addition, also can calculate gas refrigerant by (2) formula and extend pipe arrangement internal volume V _pG.

According to above content, the Computing Principle extending pipe arrangement internal volume becomes clear and definite, is described concrete calculating order.

(pipe arrangement density p is extended for the calculation result data group calculated based on each service data _p, extend refrigerant amount M beyond pipe arrangement _{r_otherP}), if to extend pipe arrangement density p _pfor transverse axis and to extend the refrigerant amount M beyond pipe arrangement _{r_otherP}for the XY coordinate of the longitudinal axis indicating each point of calculation result data group, then become as shown in Figure 9 ensuing.

Fig. 9 represents to extend pipe arrangement density p _pfor transverse axis and to extend the refrigerant amount M beyond pipe arrangement _{r_otherP}for the XY coordinate of the longitudinal axis denoting the figure of the state of multiple point.In addition, each point be indicated on XY coordinate obtains the service data of condition and the point that obtains based on meeting service data, is the data of the stable state of refrigerant loop 10.

Based on each sign point of Fig. 9, utilize least squares method to formulate linear approximate expression.The absolute value of the gradient of linear approximate expression becomes liquid refrigerant and extends pipe arrangement internal volume V _pL, when the example of Fig. 9, become 0.0206.Formulating method about linear approximate expression is described later.

According to above content, calculate liquid refrigerant by multiple service data and extend pipe arrangement internal volume V _pLmethod become clear and definite, turn back to the explanation of the flow chart of Fig. 6.

In step s 30, when judging to obtain multiple service data, reading from storage part 3c the calculation result data group calculated based on each service data and (extending pipe arrangement density p _p, extend refrigerant amount M beyond pipe arrangement _{r_otherP}).Further, calculation unit 3b carries out the calculating (S31) of approximate expression based on read calculation result data group.Further, judge whether to meet prolongation pipe arrangement internal volume determination condition (S32).When not meeting prolongation pipe arrangement internal volume determination condition, turning back to the step S2 of Fig. 5, when satisfied prolongation pipe arrangement internal volume determination condition, entering into the process of step S33.

At this, extend pipe arrangement internal volume determination condition as described below.

First condition: calculate the calculation result data group used as approximate expression, cold-producing medium extends pipe arrangement density p _pthe difference of maxima and minima be more than arbitrary value.

Second condition: the liquid refrigerant calculated extends pipe arrangement internal volume V _pLthere is higher limit, lower limit.

These data, when there are the data departing from data within the scope of this, are got rid of and again formulate approximate expression by Article 3 part: the data scope of application arranging certain arbitrary amplitude relative to the approximate expression formulated based on each data meeting first condition.

Liquid refrigerant when meeting these conditions is extended pipe arrangement internal volume to determine to extend pipe arrangement internal volume V as final liquid refrigerant _pLresult of calculation.

The reason of setting first condition there are following content: the cold-producing medium used when calculating approximate expression extends pipe arrangement density p _pvalue when being value close to each other, because little error will cause the gradient of approximate expression significantly to change.But, by first condition, add cold-producing medium prolongation pipe arrangement density p approximate expression being calculated and use as shown _pthe amplitude of value establish large condition, the amplitude of variation of gradient can be reduced, be difficult to be subject to the impact of measure error because sensor causes (equipment error, the error produced because of surrounding environment).Thus, the calculation result data group used when calculating approximate expression by step S31 does not meet first condition, cancelling this approximate expression, not carrying out liquid refrigerant and extending pipe arrangement internal volume V _pLdetermination.In addition, also first condition group can being entered in step S30, extending pipe arrangement density p when obtaining cold-producing medium _pthe difference of maxima and minima when being the calculation result data group of more than arbitrary value, enter into approximate expression computing.

In addition, the reason setting second condition there are following content: extend pipe arrangement internal volume V for liquid refrigerant _pLdetermine the upper lower limit value of internal volume in advance according to equipment, depart from this value sometimes.But, as shown in second condition, extend pipe arrangement internal volume V by making the liquid refrigerant calculated _pLwith upper lower limit value, can prevent the error count of refrigerant amount from calculating.

In addition, the reason of setting Article 3 part there are following content: when obtaining the large data of data error, make gradient become unstable because of the impact of these data.But, as shown in Article 3 part, by getting rid of the different large data of value difference according to the proximal line made based on each data meeting first condition, again trying to achieve proximal line, the impact of error can be reduced and obtain the high approximate expression of precision.

Only when meeting these first ~ Article 3 parts, determine that liquid refrigerant extends pipe arrangement internal volume V according to approximate expression _pL(S33).In addition, though preferably meet all conditions of first ~ Article 3 part, be not limited thereto.Further, calculate according to above-mentioned (2) formula the internal volume V that gas refrigerant extends pipe arrangement 7 _pG(S34).Further, the liquid refrigerant calculated by step S33 is utilized to extend pipe arrangement internal volume V _pLpipe arrangement internal volume V is extended with gas refrigerant _pGcalculate cold-producing medium total amount M _r.Cold-producing medium total amount M _rcomputational methods be described later.Then, the liquid refrigerant calculated by above-mentioned process is extended pipe arrangement internal volume V _pL, gas refrigerant extends pipe arrangement internal volume V _pG, benchmark refrigerant amount (being initial stage charging quantity when charging quantity is known in the early stage) M _rSTDbe recorded to the storage part 3c of memory etc., terminate initial stage study.

(formulating method (least squares method) of linear approximation formula)

Below, as the formulating method of the following linear approximate expression illustrated in the step S31 of Fig. 6.

[several 1]

f(X)＝aX+b ...........(6)

When measurement point is X, calculate the difference (Y-f (X)) of Y and function value f (X), if difference is square all little at all measurement points, then Y and f (X) is close value.Difference square total T become (7) formula of following formula.

[several 2]

T (total)=Σ (Yf (X)) ²... ... .. (7)

Ask coefficient that the T (total) of ensuing (8) formula is minimum function (a, b).If (6) formula be updated in (7) formula, then become following (8) formula.

[several 3]

T＝Σ(Y-aX-b) ²...........(8)

By the T of above-mentioned (8) formula, with coefficient, (when a, formula b) having carried out differential are 0, the T of (8) formula is minimum.

That is, ensuing (9) formula and (10) formula is obtained,

[several 4]

δT/δb＝0 ...........(9）

[several 5]

δT/δa＝0 ...........(10)

If untied and arrange, then form the binary simultaneous equations that following formula (11) is such.

[several 6]

$\left[\begin{array}{cc}\mathrm{\&Sigma;}{X}^0& \mathrm{\&Sigma;}{X}^1\\ \mathrm{\&Sigma;}{X}^1& \mathrm{\&Sigma;}{X}^2\end{array}\right]\left[\begin{array}{c}b\\ a\end{array}\right]=\left[\begin{array}{c}\mathrm{\&Sigma;}{X}^{0}Y\\ \mathrm{\&Sigma;}{X}^{1}Y\end{array}\right]...........\left(11\right)$

Binary simultaneous equations can be stated with following matrix (ranks) formula (12).

[several 7]

A×x＝b ...........(12)

As shown in (13) formula, untie this determinant, calculate ranks X, design factor a, b.This coefficient a becomes liquid refrigerant and extends pipe arrangement internal volume V _pL.

[several 8]

X=A ^(-1)× b A ^(-1)the ranks reciprocal of A ... ... .. (13)

(cold-producing medium total amount M _rcomputational methods)

The refrigerant amount computational methods of present embodiment are described for refrigerating operaton.In addition, also can adopt to use the same method for heating operation and calculate cold-producing medium total amount.

First, the cold-producing medium total amount M according to the running status amount of each inscape forming refrigerant loop 10 calculates the refrigerant amount of each inscape, calculation is present in refrigerant loop 10 is shown _rmethod.

Cold-producing medium total amount M _ras shown in ensuing (14) formula, try to achieve the refrigerant amount of each key element according to the running status of each key element, obtain as its summation.

[several 9]

M _r＝M _rc+M _re+M _rPL+M _rPG+M _rACC·M _rOIL...........(14)

At this, M _rc: condenser refrigerant amount, M _re: evaporator refrigeration dosage, M _rPL: liquid refrigerant extends pipe arrangement refrigerant amount, M _rPG: gas refrigerant extends pipe arrangement refrigerant amount, M _rACC: accumulator refrigerant amount, M _rOIL: oil dissolves refrigerant amount.

Below, the computational methods of each key element refrigerant amount are separately described successively.

(1) the refrigerant amount M of outdoor heat converter 23 (condenser) _rccalculating

Outdoor heat converter 23 plays function as condenser.Figure 10 is the figure of the overview of the refrigerant condition represented in condenser.At condenser inlet, the degree of superheat of the discharge side of compressor 21 is greater than 0 degree, and thus cold-producing medium becomes gas phase, and in addition, at condensator outlet, degree of subcooling is greater than 0 degree, and thus cold-producing medium becomes liquid phase.Within the condenser, temperature T _dthe cold-producing medium as gas phase state cooled by the outdoor air of temperature TA, become temperature Tcs _gsaturated vapor, changed and condensation by latent heat with two-phase state, become temperature T _cslsaturated solution, and then cooled and become temperature T _scoliquid phase.

Condenser refrigerant amount M _rc[kg] is represented by ensuing (15) formula.

[several 10]

M _rc＝V _c×ρ _c...........(15)

Condenser internal volume V _c[m ³] owing to being device specification, so be known.The average refrigerant density p of condenser _c[kg/m ³] represented by ensuing (16) formula.

[several 11]

ρ _c＝R _cg×ρ _cg+R _cs×ρ _cs+R _cl×ρ _cl...........(16)

At this, R _cg, R _cs, R _cl[-] represents the volume fraction of gas phase, two-phase, liquid phase respectively.Ρ _cg, ρ _cs, ρ _cl[kg/m ³] represent the average refrigerant density of gas phase, two-phase, liquid phase respectively.In order to calculate the average refrigerant density of condenser, need the volume fraction and the average refrigerant density that calculate each phase.

(1.1) calculating of the gas phase of condenser, two-phase, liquid phase average refrigerant density separately

The average refrigerant density p of (a) gas phase _cgcalculating

Gas phase average refrigerant density p _cgsuch as the Access-Point Density ρ of condenser _dwith the saturated gas density ρ in condenser _csgmean value, ask calculation by ensuing (17) formula.

[several 12]

${\mathrm{\&rho;}}_{\mathrm{cg}}=\frac{{\mathrm{\&rho;}}_d+{\mathrm{\&rho;}}_{\mathrm{csg}}}{2}...........\left(17\right)$

At this, condenser inlet density p _dcan according to condenser inlet temperature (with discharge temperature T _dquite) and pressure (with discharge pressure P _dquite) calculate.In addition, the saturated gas density ρ in condenser _csgcan according to condensing pressure (discharge pressure P _d) calculate.

The average refrigerant density p of (b) two-phase _cscalculating

The average refrigerant density p of two-phase _csrepresented by ensuing (18) formula.

[several 13]

${\mathrm{\&rho;}}_{\mathrm{cs}}={\&Integral;}_0^1[f_{\mathrm{cg}}\&times;{\mathrm{\&rho;}}_{\mathrm{csg}}+(1-f_{\mathrm{cg}})\&times;{\mathrm{\&rho;}}_{\mathrm{csf}}]\mathrm{dx}...........\left(18\right)$

At this, x is the mass dryness fraction [-] of cold-producing medium, f _cgfor the voidage [-] in condenser.F _cgrepresented by ensuing (19) formula.

[several 14]

$f_{\mathrm{cg}}=\frac{1}{1+(\frac{1}{x}-1)\frac{{\mathrm{\&rho;}}_{\mathrm{csg}}}{\mathrm{csl}}s})...........\left(19\right)$

At this, s is Slip Ratio [-].The calculation formula of Slip Ratio s is currently suggested great many of experiments formula, as mass flux Gm _r[kg/ (m ²s)], discharge pressure P _d, mass dryness fraction x function represented by ensuing (20) formula.

[several 15]

s＝f(G _m，r，P _d，x) ...........(20)

The average refrigerant density p of (c) liquid phase _clcalculating

Liquid phase average refrigerant density p _clsuch as the outlet density ρ of condenser _scowith the saturated liquid density ρ in condenser _cslmean value, ask calculation by ensuing (21) formula.

[several 16]

${\mathrm{\&rho;}}_{\mathrm{cl}}=\frac{{\mathrm{\&rho;}}_{\mathrm{sco}}+{\mathrm{\&rho;}}_{\mathrm{csl}}}{2}...........\left(21\right)$

At this, the outlet density ρ of condenser _scocan according to the condensator outlet temperature T obtained from hydraulic fluid side temperature sensor 203 _scowith pressure (with discharge pressure P _dquite) calculate.In addition, the saturated liquid density ρ in condenser _csltry to achieve by carrying out saturated conversion to the pressure of compressor outlet.

Mass flux Gm _rchange to some extent due to the running frequency according to compressor, so, by calculating Slip Ratio s with this method, calculation refrigerant amount M can be detected _rrelative to the change of the running frequency of compressor.

According to above content, calculate the average refrigerant density p of the gas phase needed for the average refrigerant density for calculating condenser, two-phase, liquid phase _cg, ρ _cs, ρ _cl[kg/m ³].

(1.2) calculating of the gas phase of condenser, two-phase, liquid phase volume fraction separately

Then, to the volume fraction (R of each phase of the gas phase of condenser, two-phase, liquid phase _cg: R _cs: R _cl) computational methods of [-] are described.Volume fraction represents due to the ratio by heat transfer area, so ensuing (22) formula is set up.

[several 17]

$R_{\mathrm{cg}}:R_{\mathrm{cs}}:R_{\mathrm{cl}}=\frac{A_{\mathrm{cg}}}{A_c}:\frac{A_{\mathrm{cs}}}{A_c}:\frac{A_{\mathrm{cl}}}{A_c}...........\left(22\right)$

At this, A _cg, A _cs, A _clthe heat transfer area [m of the gas phase in condenser, two-phase, liquid phase respectively ²], Ac is the heat transfer area [m of condenser ²].In addition, if the ratio enthalpy difference in the regional under gas phase, two-phase, liquid phase is set to Δ H [kJ/kg], the MTD carrying out the medium of heat exchange with cold-producing medium is set to Δ Tm [DEG C], then balances according to hot revenue and expenditure, in each phase, following (23) formula is set up.

[several 18]

G _r×ΔH＝AKΔT _m...........(23)

At this, G _rfor the mass flow [kg/h] of cold-producing medium, A is heat transfer area [m ²], K is heat transfer function [kW/ (m ²dEG C)].If be assumed to be constant by the heat flux flowed out in each phase, then the function K of conducting heat becomes constant, and volume fraction is proportional with the value by obtaining divided by temperature difference Δ T [DEG C] of cold-producing medium and outdoor air than enthalpy difference Δ H [kJ/kg].

But, according to wind speed profile, for each path, wind less than place, liquid phase is few, in the place that wind easily blows to, because heat transfer be promoted and make liquid phase become many, think that cold-producing medium is uneven.In addition, under liquid phase, the temperature difference between cold-producing medium and outdoor air is little, therefore thinks that heat flux diminishes compared with the state of gas phase, two-phase.So, when calculating the volume fraction of each phase, being multiplied by condenser liquid phase ratio correction coefficient β [-] for liquid phase portion, carrying out the correction for above-mentioned phenomenon.According to above content, derive ensuing (24) formula.

[several 19]

$R_{\mathrm{cg}}:R_{\mathrm{cs}}:R_{\mathrm{cl}}=\frac{\mathrm{\&Delta;}{H}_{\mathrm{cg}}}{\mathrm{\&Delta;}{T}_{\mathrm{cg}}}:\frac{\mathrm{\&Delta;}{H}_{\mathrm{cs}}}{\mathrm{\&Delta;}{T}_{\mathrm{cs}}}:\mathrm{\&beta;}\frac{\mathrm{\&Delta;}{H}_{\mathrm{cl}}}{\mathrm{\&Delta;}{T}_{\mathrm{cl}}}...........\left(24\right)$

At this, Δ H _cg, Δ H _cs, Δ Hcl is the ratio enthalpy difference [kJ/kg] of cold-producing medium of gas phase, two-phase, liquid phase respectively, Δ T _cg, Δ T _cs, Δ T _cltemperature difference [DEG C] that is each and outdoor air respectively.

At this, condenser liquid phase ratio correction coefficient β is the value of being tried to achieve by determination data, is the value changed to some extent according to specification of equipment, particularly condenser specifications.

Δ H _cgdeduct the specific enthalpy of saturated vapor by the specific enthalpy (suitable with the discharge specific enthalpy of compressor 21) from condenser inlet and try to achieve.Discharge specific enthalpy to pass through discharge pressure P _dand discharge temperature T _dcalculate and try to achieve, the specific enthalpy of the saturated vapor in condenser can according to condensing pressure (with discharge pressure P _dquite) calculate.

Δ H _cstry to achieve by deducting the specific enthalpy of the saturated solution in condenser from the specific enthalpy of the saturated vapor in condenser.The specific enthalpy of the saturated solution in condenser can according to condensing pressure (with discharge pressure P _dquite) calculate.

Δ H _clobtain by deducting the specific enthalpy of condensator outlet from the specific enthalpy of the saturated solution in condenser.The specific enthalpy of condensator outlet is passed through condensing pressure (with discharge pressure P _dquite) and condensator outlet temperature T _scocalculate and obtain.

For the temperature difference Δ T of gas phase and outdoor air _cg[DEG C], if such as hypothesis does not almost have the variations in temperature of outdoor air, then utilizes condenser inlet temperature (with discharge temperature T _dquite), the saturated vapor temperature T in condenser _csgthe inlet temperature T of [DEG C] and outdoor air _ca[DEG C], is represented by ensuing (25) formula as log-mean temperature difference.

[several 20]

$\mathrm{\&Delta;}{T}_{\mathrm{cg}}=\frac{(T_d-T_{\mathrm{ca}})-(T_{\mathrm{csg}}-T_{\mathrm{ca}})}{\ln \frac{(T_d-T_{\mathrm{ca}})}{(T_{\mathrm{csg}}-T_{\mathrm{ca}})}}...........\left(25\right)$

In addition, the saturated vapor temperature T in condenser _csgcan according to condensing pressure (with discharge pressure P _dquite) calculate.

The MTD Δ T of two-phase and outdoor air _csutilize the saturated vapor temperature T in condenser _csgand saturated solution temperature T _cslrepresent according to ensuing (26) formula.

[several 21]

$\mathrm{\&Delta;}{T}_{\mathrm{cs}}=\frac{T_{\mathrm{csg}}+T_{\mathrm{csl}}}{2}-T_{\mathrm{cs}}...........\left(26\right)$

Saturated solution temperature T in condenser _cslcan according to condensing pressure (with discharge pressure P _dquite) calculate.

The MTD Δ T of liquid phase and outdoor air _clutilize condensator outlet temperature T _sco, saturated solution temperature T in condenser _cslwith the outer temperature degree of suction, represented by ensuing (27) formula as log-mean temperature difference.

[several 22]

$\mathrm{\&Delta;}{T}_{\mathrm{cl}}=\frac{(T_{\mathrm{csl}}-T_{\mathrm{ca}})-(T_{\mathrm{sco}}-T_{\mathrm{ca}})}{\ln \frac{(T_{\mathrm{csl}}-T_{\mathrm{ca}})}{(T_{\mathrm{sco}}-T_{\mathrm{ca}})}}...........\left(27\right)$

According to above content, the volume fraction (R of each phase can be calculated _cg: R _cs: R _cl).

As mentioned above, average refrigerant density and the volume fraction of each phase can be calculated, condenser average refrigerant density p can be calculated _c.

(2) the refrigerant amount M of pipe arrangement is extended _rPL, M _rPGcalculating

Liquid refrigerant extends pipe arrangement refrigerant amount M _rPL[kg] and gas refrigerant extend pipe arrangement refrigerant amount M _rPG[kg] is represented by ensuing (28) formula, (29) formula respectively.

[several 23]

M _rPL＝V _PL×ρ _PL...........(28)

[several 24]

M _rPG＝V _PG×ρ _PG...........(29)

At this, ρ _pLsuch as by extending pipe arrangement inlet temperature (with condensator outlet temperature T to liquid refrigerant _scoquite) and liquid refrigerant extend pipe arrangement inlet pressure (with discharge pressure P _dquite) calculate and try to achieve.

In addition, ρ _pGsuch as calculate by extending pipe arrangement outlet pressure (suitable with suction pressure Ps) to gas refrigerant prolongation pipe arrangement outlet temperature (suitable with inlet temperature Ts) and liquid refrigerant and try to achieve.V _pLand V _pGthat liquid refrigerant extends pipe arrangement internal volume [m respectively ³] and gas refrigerant prolongation pipe arrangement internal volume [m ³], utilize the value obtained according to initial stage study.

(3) the refrigerant amount M of indoor heat converter 42A, 42B (evaporimeter) _recalculating

Indoor heat converter 42A, 42B play function as evaporimeter.Figure 11 is the figure of the overview of the refrigerant condition represented in evaporimeter.At evaporator inlet, cold-producing medium becomes two-phase, and at evaporator outlet, the degree of superheat of the suction side of compressor 21 is greater than 0 degree, and thus cold-producing medium becomes gas phase.At evaporator inlet, temperature T _eithe cold-producing medium as two-phase state of [DEG C], by the indoor suction air heat of temperature TA [DEG C], becomes temperature T _esgthe saturated vapor of [DEG C], and then the gas phase being become temperature Ts [DEG C] by heating.Evaporator refrigeration dosage M _re[kg] is represented by ensuing (30) formula.

[several 25]

M _re＝V _e×ρ _e...........(30)

At this, V _eevaporimeter internal volume [m ³], owing to being specification of equipment so be known.ρ _eevaporimeter average refrigerant density [kg/m ³], represented by ensuing (31) formula.

[several 26]

ρ _e＝R _eg×ρ _es+R _eg×ρ _eg...........(31)

At this, R _eg, R _esthe volume fraction [-] of gas phase, two-phase respectively, ρ _es, ρ _egrepresent the average refrigerant density [kg/m of gas phase, two-phase ³].In order to calculate the average refrigerant density of evaporimeter, need the volume fraction and the average refrigerant density that calculate each phase.

(3.1) gas phase of evaporimeter, the calculating of two-phase average refrigerant density separately

Two-phase average refrigerant density p in (a) evaporimeter _es[kg/m ³] calculating

Two-phase average refrigerant density p _esrepresented by ensuing (32) formula.

[several 27]

${\mathrm{\&rho;}}_{\mathrm{es}}={\&Integral;}_{\mathrm{xel}}^1[f_{\mathrm{eg}}\&times;{\mathrm{\&rho;}}_{\mathrm{esg}}+(1-f_{\mathrm{eg}})\&times;{\mathrm{\&rho;}}_{\mathrm{esl}}]\mathrm{dx}...........\left(32\right)$

At this, x is the mass dryness fraction [-] of cold-producing medium, f _egfor the voidage [-] in evaporimeter.F _egrepresented by ensuing (33) formula.

[several 28]

$f_{\mathrm{eg}}=\frac{1}{1+(\frac{1}{x}-1)\frac{{\mathrm{\&rho;}}_{\mathrm{esg}}}{{\mathrm{\&rho;}}_{\mathrm{esd}}}s}...........\left(33\right)$

At this, s is Slip Ratio [-].The calculation formula of Slip Ratio s is currently suggested great many of experiments formula, as mass flux GM _r[kg/ (m ²s)], the function of suction pressure Ps, mass dryness fraction x is represented by ensuing (34) formula.

[several 29]

s＝f(G _m，r，P _s，x) ...........(34)

Mass flux Gm _rchanging to some extent due to the running frequency according to compressor, so by calculating Slip Ratio s with this method, calculation refrigerant amount M can be detected _rrelative to the change of the running frequency of compressor.

Gas phase average refrigerant density p in (b) evaporimeter _eg[kg/m ³] calculating

Gas phase average refrigerant density p in evaporimeter _egsuch as the saturated gas density ρ in evaporimeter _esgwith the mean value of evaporator outlet density, tried to achieve by ensuing (35) formula.

[several 30]

${\mathrm{\&rho;}}_{\mathrm{eg}}=\frac{{\mathrm{\&rho;}}_{\mathrm{esg}}+{\mathrm{\&rho;}}_s}{2}...........\left(35\right)$

At this, the saturated gas density ρ in evaporimeter _esgcan calculate according to evaporating pressure (suitable with suction pressure Ps).Evaporator outlet density (suitable with suction density p s) can calculate according to evaporator outlet temperature (suitable with inlet temperature Ts) and pressure (suitable with suction pressure Ps).

According to above content, calculate the average refrigerant density p of the two-phase needed for the average refrigerant density for calculating evaporimeter, gas phase _es, ρ _eg[kg/m ³].

(3.2) two-phase of evaporimeter, the calculating of gas phase volume fraction separately

Then, the computational methods of the volume fraction of each phase are described.Volume fraction is represented by the ratio of heat transfer area, so ensuing (36) formula is set up.

[several 31]

$R_{\mathrm{es}}:R_{\mathrm{eg}}=\frac{A_{\mathrm{es}}}{A_e}:\frac{A_{\mathrm{eg}}}{A_e}...........\left(36\right)$

At this, A _es, A _egbe the heat transfer area of the two-phase in evaporimeter, gas phase respectively, Ae is the heat transfer area of evaporimeter.In addition, if the ratio enthalpy difference in the respective region of two-phase, gas phase is set to Δ H, the MTD carrying out the medium of heat exchange with cold-producing medium is set to Δ Tm, then according to hot revenue and expenditure balance, each mutually under, following (37) formula is set up.

[several 32]

G _r×ΔH＝AKΔT _m...........(37)

At this, G _rbe the mass flow [kg/h] of cold-producing medium, A is heat transfer area [m ²], K is heat transfer function [kW/ (m ²dEG C)].If the heat flux flowed out in each phase is assumed to be constant, the function K that then conducts heat becomes constant, volume fraction is proportional with the value by obtaining divided by temperature difference Δ T [DEG C] of cold-producing medium and outdoor air than enthalpy difference Δ H [kJ/kg], ensuing proportion expression (38) establishment.

[several 33]

$R_{\mathrm{es}}:R_{\mathrm{eg}}=\frac{\mathrm{\&Delta;}{H}_{\mathrm{es}}}{\mathrm{\&Delta;}{T}_{\mathrm{es}}}:\frac{\mathrm{\&Delta;}{H}_{\mathrm{eg}}}{\mathrm{\&Delta;}{T}_{\mathrm{eg}}}...........\left(38\right)$

Δ H _estry to achieve by deducting evaporator inlet specific enthalpy from the specific enthalpy of the saturated vapor in evaporimeter.The specific enthalpy of the saturated vapor in evaporimeter is by calculating to evaporating pressure (suitable with suction pressure) and obtain, and evaporator inlet specific enthalpy can according to condensator outlet temperature T _scocalculate.

Δ H _egdeduct the specific enthalpy of the saturated vapor in evaporimeter by the specific enthalpy (suitable with suction specific enthalpy) from evaporator outlet and try to achieve.The specific enthalpy of evaporator outlet is by calculating to outlet temperature (suitable with inlet temperature Ts) and pressure (suitable with suction pressure Ps) and obtain.

The MTD Δ T of the two-phase in evaporimeter and room air _es, such as, suppose the variations in temperature almost not having room air, then represented by ensuing (39) formula.

[several 34]

$\mathrm{\&Delta;}{T}_{\mathrm{es}}=T_{\mathrm{es}}=\frac{T_{\mathrm{esg}}+T_{\mathrm{ei}}}{2}...........\left(39\right)$

At this, the saturated vapor temperature T in evaporimeter _esgby calculating to evaporating pressure (suitable with suction pressure Ps) and obtain.Evaporator inlet temperature T _eican calculate according to evaporating pressure (suitable with suction pressure Ps).T _eafor indoor air temperature.

The MTD Δ T of gas phase and room air _egrepresented by ensuing (40) formula as log-mean temperature difference.

[several 35]

$\mathrm{\&Delta;}{T}_{\mathrm{eg}}=\frac{(T_{\mathrm{ea}}-T_{\mathrm{esg}})-(T_{\mathrm{es}}-T_{\mathrm{eg}})}{\ln \frac{(T_{\mathrm{ea}}-T_{\mathrm{esg}})}{(T_{\mathrm{es}}-T_{\mathrm{eg}})}}...........\left(40\right)$

At this, evaporator outlet temperature T _egobtained as inlet temperature Ts.

According to above content, the volume fraction (R of two-phase and gas phase can be calculated _es: R _eg).

As mentioned above, average refrigerant density and the volume fraction of each phase can be calculated, evaporimeter average refrigerant density p can be calculated _e.

(4) accumulator refrigerant amount M _rACCcalculating

In accumulator entrance and outlet, the degree of superheat due to the suction side of compressor 21 is greater than 0 degree, so cold-producing medium becomes gas phase.Accumulator refrigerant amount M _rACC[kg] is represented by ensuing (41) formula.

[several 36]

M _r，ACC＝V _ACC×ρ _ACC...........(41)

At this, V _aCCfor accumulator internal volume [m ³], owing to determining according to specification of equipment so be known value.ρ _aCCaccumulator average refrigerant density [kg/m ³], accumulator inlet temperature (suitable with inlet temperature Ts) and inlet pressure (suitable with suction pressure Ps) are calculated and tried to achieve.

(5) the refrigerant amount M in refrigerator oil is dissolved in _rOILcalculating

Be dissolved in the amount M of the cold-producing medium in refrigerator oil _rOIL[kg] is represented by ensuing (42) formula.

[several 37]

M _r，OIL＝V _OIL×ρ _OIL×φ _OIL...........(42)

At this, V _oILthe volume [m of the refrigerator oil be present in refrigerant loop ³], owing to being specification of equipment so be known.ρ _oILand φ _oILthe density [kg/m of refrigerator oil respectively ³] and cold-producing medium relative to the solubility [-] of oil.If most refrigerator oil is present in compressor and accumulator, then refrigerator oil density p _oILtreat with steady state value, in addition, cold-producing medium relative to the solubility φ [-] of oil as shown in ensuing (43) formula, by calculating to inlet temperature Ts and suction pressure Ps and try to achieve.

[several 38]

φ _OIL＝f(T _s，P _s) ...........(43)

According to above content, can calculate: (1) condenser refrigerant amount M _rc, (2) extend pipe arrangement refrigerant amount M _p(liquid refrigerant extends pipe arrangement refrigerant amount M _rPLpipe arrangement refrigerant amount M is extended with gas refrigerant _rPGadditive quantity), (3) evaporator refrigeration dosage M _re, (4) accumulator refrigerant amount M _rACC, and (5) oil dissolves refrigerant amount M _rOIL.By being all added together by these each refrigerant amounts, cold-producing medium total amount M can be tried to achieve _r.

If modification method implements the correction relevant with liquid phase portion, be then not limited to said method, revise position more, then more can calculate refrigerant amount accurately.

As described above, in the present embodiment, meet if become in usually running the running status that service data obtains condition, then automatically obtain the service data that service data now learnt as the initial stage successively.Further, calculate the refrigerant amount beyond prolongation pipe arrangement based on each service data respectively and extend pipe arrangement density, calculating based on this calculation result data group and extend pipe arrangement internal volume.Thus, the specific operation extending the internal volume of pipe arrangement for calculating cold-producing medium need not being carried out, usual operating service data just can be utilized to calculate the internal volume that cold-producing medium extends pipe arrangement.In addition, owing to usually running only by beginning, calculating and refrigrant leakage detection that cold-producing medium extends the internal volume of pipe arrangement just automatically can be carried out, so, without the need to implementing the time of specific run like that in the past.

In addition, refrigerating air-conditioning 1 is arranged, even if the internal volume of cold-producing medium prolongation pipe arrangement is failed to understand, also by carrying out initial stage study, and easily calculate the internal volume of cold-producing medium prolongation pipe arrangement and the refrigerant amount of cold-producing medium prolongation pipe arrangement based on service data when usually running.Therefore, when carry out cold-producing medium extend judge with presence or absence of the calculating of internal volume of pipe arrangement or refrigrant leakage time, the trouble that input cold-producing medium extends the information of pipe arrangement can be reduced with doing one's utmost.

In addition, when the initial stage of carrying out learns, judge whether to meet initial stage study beginning condition, that is, finally calculate the internal volume of cold-producing medium prolongation pipe arrangement based on service data during running status without the delay of remaining liq cold-producing medium accumulator 24 in.For this reason, cold-producing medium can be carried out exactly and extend the internal volume of pipe arrangement and the calculating of benchmark refrigerant amount.Thus, the refrigerant amount in cold-producing medium prolongation pipe arrangement can be calculated accurately, and then calculating and the refrigrant leakage detection of the cold-producing medium total amount in refrigerating air-conditioning can be carried out accurately.Its result, can detect refrigrant leakage ahead of time, also can prevent the damage of natural environment and refrigerating air-conditioning self.

In addition, when calculation result data quantity is few, there is the possibility bringing the impact of various error to the result of calculation extending pipe arrangement internal volume, but extend pipe arrangement internal volume, so be difficult to the impact being subject to error at this owing to calculating based on calculation result data group.

In addition, when calculating prolongation pipe arrangement internal volume according to calculation result data group, formulate based on calculation result data group and represent that cold-producing medium extends pipe arrangement density and extends the approximate expression of the relation between the refrigerant amount beyond pipe arrangement, the internal volume that the gradient of this approximate expression extends pipe arrangement as cold-producing medium is calculated.Thereby, it is possible to easily calculate the internal volume that cold-producing medium extends pipe arrangement.

In addition, cold-producing medium extends pipe arrangement has liquid refrigerant to extend pipe arrangement 6 and gas refrigerant prolongation pipe arrangement 7, in usually running, and the density change of both sides' pipe arrangement.Thus, need to calculate the prolongation pipe arrangement density p considering both sides' pipe arrangement variations in density _p.Pipe arrangement density p is extended in calculating _ptime, represent internal volume that gas refrigerant extends pipe arrangement 7 by using and the internal volume extending pipe arrangement 6 at liquid refrigerant be multiplied by volumetric ratio α and the equal relational expression (above-mentioned (2) formula) of the value that obtains, can be calculated by above-mentioned (1) formula.

In addition, cold-producing medium during satisfied prolongation pipe arrangement internal volume determination condition is extended the result of calculation that pipe arrangement internal volume determines to extend as final cold-producing medium pipe arrangement internal volume.Thus even if use the service data with various error obtained when usually running, the impact of error is also few, can calculate cold-producing medium accurately and extend pipe arrangement internal volume, can improve the reliability of result of calculation.

In addition, obtain as service data the condition that condition specifies above-mentioned (A) ~ (C), specify the running status of the having stable behavior of refrigerant circulation.Thus, the calculating that cold-producing medium extends the internal volume of pipe arrangement can be carried out accurately.

In addition, in the above-described embodiment, when judging the presence or absence of refrigrant leakage, step S9 is utilized, by benchmark refrigerant amount (initial stage charging quantity) M _rSTDwith cold-producing medium total amount M _rjudge, but also can adopt following method.Refrigrant leakage rate (the calculation cold-producing medium total amount ratio relative to suitable refrigerant amount) r [%] is utilized to judge.Refrigrant leakage rate r utilizes the initial stage to learn the initial stage charging quantity M of gained _rSTDwith the cold-producing medium total amount M that step S8 calculates _r, calculated by ensuing (44) formula.

[several 39]

$r=\frac{M_{\mathrm{rSTD}}-M_r}{M_{\mathrm{rSTD}}}\&times;100...........\left(44\right)$

Detection unit 3d compares the refrigrant leakage rate r calculated and the threshold value x [%] obtained by storage part 3c in advance, if r < is X, then be judged to be without refrigrant leakage, if X < is r, be then judged to be refrigrant leakage.Exist because sensor error etc. causes being worth situation about changing when the refrigerant amount of the method calculates, thus come up on the basis of these factors of consideration definite threshold.When without refrigrant leakage, send the normal information of refrigerant amount in step slo.When there being refrigrant leakage, send the information having refrigrant leakage in step s 11.

When transmission has the information of refrigrant leakage, by making the indication mechanisms such as display export refrigrant leakage rate r, operator is made easily to confirm the state of the refrigerant amount in refrigerant loop.

In addition, by display refrigrant leakage rate r, operator can grasp the state of device in more detail, can realize the raising of maintainability.

In addition, also can be connected to the network and form coolant amount judgment system by refrigerating air-conditioning.Specifically, connect as manage each constitution equipment of refrigerating air-conditioning and by telephone line, LAN circuit, the local control communicating to obtain the management devices of service data with outside such as wireless.Further, via network, the remote server of this local control with the Center For Information Management of the service data of reception refrigerating air-conditioning is connected.In addition, on remote server, connection is used for the storage device of the disk set of storage running quantity of state etc.Like this, coolant amount judgment system can be formed.Such as, consider following formation etc.: using local control as being used for the determination part of the running status amount obtaining refrigerating air-conditioning and being used for calculating the calculation unit of running status amount, using storage device as storage part, remote server is made to play function as comparing section, detection unit.In this case, just calculation refrigerant amount and refrigrant leakage rate are calculated the function compared according to current running status amount without the need to making refrigerating air-conditioning have.In addition, the system of remote monitoring can be carried out by so forming, when periodic maintenance, becoming and rushing towards scene to confirm operation with presence or absence of refrigrant leakage without the need to operator, thus making the reliability of equipment, operability is improved.

Above, based on accompanying drawing, embodiments of the present invention are illustrated, but concrete formation is not limited to these embodiments, can changes in the scope not departing from inventive concept.Such as, in the above-described embodiment, describe and apply the present invention to carry out the example in the refrigerating air-conditioning of cold and hot switching, but be not limited thereto, also or can heat in special refrigerating air-conditioning and apply the present invention in refrigeration.In addition, in the above-described embodiment, heat source unit and range site are respectively equipped with the refrigerating air-conditioning of as an example, but are not limited thereto, also can be respectively equipped with in the refrigerating air-conditioning of multiple stage at heat source unit and range site and apply the present invention.

In addition, in the present embodiment, be greater than 0 degree by the degree of superheat of the suction side making compressor 21 and in accumulator 24 gassy cold-producing medium, but, even if when being mixed into liquid refrigerant in accumulator 24, also sensor that the liquid level of accumulator 24 is detected can such as be added to carry out level detection, because the volume ratio of liquid and gas refrigerant is known, so the refrigerant amount being present in accumulator 24 can be calculated.

In addition, learnt by the above-mentioned initial stage, doing one's utmost to decrease while input cold-producing medium extends the time of the information such as the length of pipe arrangement, cold-producing medium can be calculated according to usual service data and extending pipe arrangement internal volume.Further, by refrigrant leakage being sent to administrative center etc. with or without data via order wire from efferent 3h, remote monitoring can be carried out all the time.Therefore, for unexpected refrigrant leakage, also can tackle immediately before generation equipment damage or ability reduction etc. are abnormal, the development of refrigrant leakage can be suppressed with doing one's utmost.Thus, the reliability of refrigerating air-conditioning 1 also improves, but also can prevent the ambient condition caused because cold-producing medium flows out from worsening with doing one's utmost, and then can prevent from continuing the such unfavorable condition of unreasonable operation because refrigrant leakage causes with few refrigerant amount, thus also can realize the long lifetime of refrigerating air-conditioning 1.

In addition, in the above description, situation with presence or absence of judgement refrigrant leakage to be illustrated, but when refrigerant charge etc., also can to apply the present invention in the whether too much judgement of refrigerant amount.

Description of reference numerals

1 refrigerating air-conditioning, 2 outdoor units, 3 control parts, 3a determination part, 3b calculation unit, 3c storage part, 3d detection unit, 3e drive division, 3f display part, 3g input part, 3h efferent, 4A, 4B indoor unit (range site), 6 liquid refrigerants extend pipe arrangement, 6A liquid is responsible for, 6a liquid tap, 7 gas refrigerants extend pipe arrangement, and 7A gas is responsible for, 7a gas service pipe, 10 refrigerant loops, 10a indoor refrigerant loop, 10b indoor refrigerant loop, 10c outside refrigerant loop, 10z main refrigerant circuit, 21 compressors, 22 cross valves, 23 outdoor heat converters, 24 accumulators, 26 subcoolers, 27 outdoor fans, 28 hydraulic fluid side shutoff valves, 29 gas side shutoff valves, 31 outside control parts, 32a indoor control part, 33a inlet temperature sensor, 33b discharge temperature sensor, 33c outdoor temperature sensor, 33d liquid pipe temperature sensor, 33e hydraulic fluid side temperature sensor, 33f gas side temperature sensor, 33g indoor temperature transmitter, 33h hydraulic fluid side temperature sensor, 33i gas side temperature sensor, 33j indoor temperature transmitter, 33k heat exchange temperature sensor, 33l hydraulic fluid side temperature sensor, 33z bypass temperature sensor, 34a suction pressure sensor, 34b discharge pressure sensor, 41A, 41B expansion valve, 42A, 42B indoor heat converter, 43A, 43B indoor fan, 51a distributor, 52a distributor, 71 bypass circulations, 72 bypass flow regulating valves.

Claims (11)

1. a refrigerating air-conditioning, is characterized in that, possesses:

Refrigerant loop, this refrigerant loop extends pipe arrangement by cold-producing medium and connects as the outdoor unit of heat source unit and as the indoor unit utilizing side unit;

Measurement section, this measurement section measures the temperature and pressure of the major part of above-mentioned refrigerant loop as service data;

Calculation unit, the service data that this calculation unit has when obtaining service data obtains condition, when the running status represented by the service data measured by above-mentioned measurement section in usually running becomes the state meeting above-mentioned service data acquisition condition, obtain the service data that service data now learnt as the initial stage, carry out calculating the refrigerant amount extended beyond pipe arrangement and the process extending pipe arrangement density based on the service data of this initial stage study, based on the calculation result data group calculated by this process, and the gas refrigerant forming above-mentioned cold-producing medium prolongation pipe arrangement extends the volumetric ratio of pipe arrangement and liquid refrigerant prolongation pipe arrangement, calculate the respective internal volume that above-mentioned gas cold-producing medium extends pipe arrangement and aforesaid liquid cold-producing medium prolongation pipe arrangement, the service data of the prolongation pipe arrangement internal volume calculated based on this and the study of above-mentioned initial stage calculates the benchmark refrigerant amount of the judgment standard as the refrigrant leakage from above-mentioned refrigerant loop,

Storage part, this storage part stores above-mentioned prolongation pipe arrangement internal volume and said reference refrigerant amount; And

Detection unit, this detection unit determines whether refrigrant leakage based on the above-mentioned prolongation pipe arrangement internal volume be stored in this storage part and the service data that measured by above-mentioned measurement section in usually running.

2. refrigerating air-conditioning as claimed in claim 1, it is characterized in that, above-mentioned calculation unit, formulate the approximate expression of the relation between the refrigerant amount representing and extend pipe arrangement density and extend beyond pipe arrangement based on above-mentioned calculation result data group, the absolute value of the gradient of this approximate expression is calculated as prolongation pipe arrangement internal volume.

3. refrigerating air-conditioning as claimed in claim 1 or 2, is characterized in that, above-mentioned prolongation pipe arrangement has liquid refrigerant and extends pipe arrangement and gas refrigerant prolongation pipe arrangement;

Above-mentioned calculation unit, afore mentioned rules coefficient in the relational expression of the value obtained representing the internal volume of gas refrigerant prolongation pipe arrangement to equal to be multiplied by predetermined coefficients on the internal volume that liquid refrigerant extends pipe arrangement, extend pipe arrangement density with the gas refrigerant calculated according to service data to be multiplied, the value that obtains of this being multiplied extends pipe arrangement density with the liquid refrigerant calculated according to service data and is added, and the value this addition obtained calculates as above-mentioned prolongation pipe arrangement density.

4. refrigerating air-conditioning as claimed in claim 1 or 2, it is characterized in that, above-mentioned calculation unit, by the difference by using cold-producing medium to extend the maxima and minima of pipe arrangement density for calculation result data group more than arbitrary value carries out the prolongation pipe arrangement internal volume that calculates, determine the result of calculation as final prolongation pipe arrangement internal volume.

5. refrigerating air-conditioning as claimed in claim 1 or 2, it is characterized in that, above-mentioned calculation unit, when the prolongation pipe arrangement internal volume calculated is in the scope of higher limit and the lower limit preset, this prolongation pipe arrangement internal volume is determined the result of calculation as final prolongation pipe arrangement internal volume.

6. refrigerating air-conditioning as claimed in claim 2, it is characterized in that, above-mentioned calculation unit, the data scope of application of any amplitude between the higher limit of the refrigerant amount extended beyond pipe arrangement and lower limit is set relative to the proximal line made, the data departing from this scope removed and carry out calculating again of proximal line, the absolute value of the gradient of the approximate expression after this being calculated again determines the result of calculation as final prolongation pipe arrangement internal volume.

7. refrigerating air-conditioning as claimed in claim 1 or 2, it is characterized in that possessing remote monitoring function, this remote monitoring function utilizes order wire that the information with or without refrigrant leakage is sent to administrative center.

8. refrigerating air-conditioning as claimed in claim 1 or 2, it is characterized in that, above-mentioned service data obtains condition and following condition is set to one of condition, that is: the variation of rotating speed running status separately as the running frequency of the compressor of the key element equipment of refrigerating air-conditioning, expansion valve opening and the fan that is installed on indoor and outdoor heat exchanger is all in certain constant range respectively.

9. refrigerating air-conditioning as claimed in claim 1 or 2, it is characterized in that, above-mentioned service data obtains condition and following condition is set to one of condition, that is: the value detecting the high-pressure pressure sensor of the high-pressure refrigerant pressure of refrigerant loop is that the value of the low-pressure sensor of more than certain steady state value and the low pressure refrigerant pressure detecting refrigerant loop is for below certain steady state value.

10. refrigerating air-conditioning as claimed in claim 1 or 2, it is characterized in that, above-mentioned service data obtains condition: the amplitude of fluctuation of the refrigerant temperature in the indoor heat converter in indoor unit and the difference of indoor temperature is within steady state value, and the amplitude of fluctuation of the difference of refrigerant temperature in outdoor heat converter in outdoor unit and outdoor temperature is within steady state value.

11. refrigerating air-conditionings as claimed in claim 1 or 2, is characterized in that possessing the efferent result of determination of above-mentioned detection unit externally sent.