CN1898505A

CN1898505A - Refrigerator

Info

Publication number: CN1898505A
Application number: CNA2004800387606A
Authority: CN
Inventors: 天明稔; 吉冈功博; 林秀竹
Original assignee: Toshiba Corp; Toshiba Consumer Marketing Corp; Toshiba Home Appliances Corp
Current assignee: Toshiba Corp; Toshiba Consumer Marketing Corp; Toshiba Lifestyle Products and Services Corp
Priority date: 2003-12-24
Filing date: 2004-11-30
Publication date: 2007-01-17
Anticipated expiration: 2024-11-30
Also published as: TWI257472B; WO2005061970A1; CN100417876C; JP2005188783A; TW200526912A; US20070144190A1; KR20060132869A

Abstract

The object of the invention is to provided a refrigerator where a variable-performance freezing cycle that has coolers for freezing and cold storage and is formed as a two-stage compression-type is controlled by freezing space temperature information, so that a freezing space and a cold storage space are each appropriately controlled at its storage temperature. A refrigerator where a freezing cycle is formed by an inverter-driven variable-performance compressor (9) where a compression element is constituted of a low stage side compression section (9a) and a high stage side compression section (9b), by a switching valve (11) for controlling a flow rate together with a refrigerant flow path provided on the exit side of a condenser (10) receiving a discharge gas from the compressor, and by cooler (4) for freezing and a cooler (5) for cold storage that are respectively connected through pressure reducing devices (12, 13) to the switching valve, wherein the rotating speed of the compressor is determined by a freezing space temperature (Fa) and a target value (Fr) for the freezing space temperature.

Description

Refrigerator

Technical field

The present invention relates to a kind of refrigerator that uses twin-stage compression ability changeable type compressor, especially relate to the refrigerator of determining compressor rotary speed according to the storage space temperature.

Background technology

In recent years, be equiped with the variable compressor of ability on the refrigerator mostly,, can obtain and the corresponding cooling performance of loading, and can reduce consumption electric power by changing its refrigerating capacity by VFC.

Generally have the reefer space and the temperature that are cooled to about-18～-20 ℃ as the domestic refrigerator of comparatively popularizing to remain on+about 1～+ 5 ℃ refrigeration and vegetables shelf space, in the structure of utilizing a cooler that the both sides space is cooled off, utilize air damper etc. that cold airflow is controlled to the distribution of freezing and refrigerating space, drive accordingly with integral body load or stop compressor, and utilize VFC further to control the rotating speed of compressor, thereby both sides' storage space is remained on set point of temperature.

In addition, have respectively in the structure of cooler at freezing and refrigerating space, control the distribution that refrigerant flow direction is configured in the cooler in described each cooling space by switching refrigerant flow path, control compressor according to loads such as the temperature of cooling space integral body and temperature differences.

On the other hand, employed compressor is the so-called single stage compress formula compressor that has a compression unit in compressor housing on the refrigerator of selling on the market now, but in recent years, as shown in figure 13, a kind of thought of twin-stage compression fridge-freezer is disclosed, in closed container, be provided with and have motor, low-pressure stage side pressure the contract double-stage compressor 39 of key element 39b of key element 39a and hiigh pressure stage side pressure that contracts, contract and press with expansion gear 43 in the middle of being connected with on the outlet side of the condenser 40 on the efferent duct 46 of key element 39a being connected side pressure from hiigh pressure stage, low-pressure stage side pressure the contract suction side of key element 39b of the outlet side of key element 39a and hiigh pressure stage side pressure of contracting is communicated with suction line 47 with middle the pressure, this centre press with suction line 47 with described in the middle of be connected with middle pressure evaporimeter 35 between pressing with expansion gear 43, and contracting the suction side 45 of key element with the low-pressure stage side pressure of expansion gear 42 and double-stage compressor between, the low pressure that is connected with condenser 40 outlet sides is connected with low pressure with evaporimeter 34, low-pressure stage side pressure the contract suction side of key element 39b of the outlet side of key element 39a and hiigh pressure stage side pressure of contracting is communicated with in closed container 39, thereby can improve the temperature control precision in the case, and realize the homogenising of each several part temperature in the case, and high efficiency, economize electrification (for example with reference to patent documentation 1).

Patent documentation 1: the Japan Patent spy opens the 2001-74325 communique

Summary of the invention

Invent technical problem to be solved

In the kind of refrigeration cycle of above-mentioned patent documentation 1 record, improve cycle efficieny with evaporimeter 34 by making to be higher than as freezing low pressure with the evaporating temperature of evaporimeter 35 with pressure in the middle of the cooler with cooler as refrigeration.But, because the freezing suction line with cooler 34 in the twin-stage compression cycle directly is connected on the low-pressure stage side compression unit 39a of compressor, refrigeration is connected the middle splenium of compressor 39 with the suction line 47 of cooler 35, therefore, the refrigerating capacity of reefer space is not vulnerable to flow to the influence of refrigeration with the cold-producing medium of cooler 35, load in the total of utilizing freezing side load and refrigeration side load and to control in the existing method of compressor 39 rotating speeds, for example in the cooling degree of reefer space fully and during the refrigerating space sub-cooled, the rotating speed of compressor is descended, and the result produces the not enough problem of reefer space cooling.

In view of the above problems, thus the object of the present invention is to provide and a kind ofly can control the refrigerator that reefer space and refrigerating space suitably is controlled at storage temperature separately with the variable kind of refrigeration cycle of ability of cooler and employing twin-stage compression to having freezing usefulness and refrigeration according to the reefer space temperature information.

The technical scheme that is used for the technical solution problem

In order to solve the problems of the technologies described above, refrigerator of the present invention, by compressor, transfer valve, freezing with cooler and refrigeration form kind of refrigeration cycle with cooler, described compressor compression key element is made of low-pressure stage side compression unit and hiigh pressure stage side compression unit, because of the variable compressor of frequency conversion drive ability, described transfer valve is controlled flow with refrigerant flow path, and this refrigerant flow path is arranged on the condensator outlet side of reception from the output gas of described compressor, described freezing with cooler and refrigeration be connected with described transfer valve by decompressor respectively with cooler, it is characterized in that, determine the rotating speed of described compressor according to reefer space temperature and desired value thereof.

In addition, the refrigerator of the invention of technical scheme 2, by compressor, transfer valve, freezing with cooler and refrigeration form kind of refrigeration cycle with cooler, described compressor compression key element is made of low-pressure stage side compression unit and hiigh pressure stage side compression unit, because of the variable compressor of frequency conversion drive ability, described transfer valve is controlled flow with refrigerant flow path, and this refrigerant flow path is arranged on the condensator outlet side of reception from the output gas of described compressor, described freezing with cooler and refrigeration be connected with described transfer valve by decompressor respectively with cooler, it is characterized in that, according to reefer space temperature and desired value thereof, refrigerating space temperature and desired value thereof are determined the rotating speed of compressor, when determining rotating speed, compare the temperature information feedback quantity that strengthens the reefer space side with refrigerating space.

The invention effect

Adopt this structure, can make freezing usefulness and refrigeration become the evaporating temperature corresponding with the cooling of each storage space with the cooler both sides, can improve the efficient of kind of refrigeration cycle, the stream that leads to each cooler switches and cold-producing medium current control such as flow, and, by simultaneously reefer space and refrigerating space being cooled off, can suppress the temperature change in each space, suitably control each space temperature.

The specific embodiment

With reference to the accompanying drawings the present invention's one example is described.Refrigerator body 1 among Fig. 2 shown in the longitudinal sectional view forms storage space in the inside of heat insulating box, storage space is divided into the reefer space 2 with refrigerating chamber and ice-making compartment by partition wall and has refrigerating chamber and a plurality of storerooms such as the refrigerating space of vegetable compartment 3.

Each storeroom is freezingly cooled off with cooler 5 and circulating

cold air fan

6,7 and remains on the design temperature of regulation respectively with cooler 4 and refrigeration by what be configured in reefer space and refrigerating space respectively, and each

cooler

4,5 is cooled off by the 9 the supply system cryogens of the compressor in the Machine Room 8 that is arranged on the body lower backside.

Fig. 1 represents the kind of refrigeration cycle of the refrigerator of the invention described above, and the transfer valve 11 of described compressor 9, condenser 10, refrigerant flow path and the described freezing usefulness that is connected in parallel and refrigeration are connected into ring-type with cooler 4,5.Described condenser 10 forms tabular, be provided in the outer bottom space of refrigerator body 1 in 8 the place aheads, described Machine Room, cold-producing medium by condenser 10 liquefaction is supplied with cooler 5 with cooler 4 or refrigeration to freezing via the

capillary

12,13 as decompressor respectively by transfer valve 11, make cooler low temperatureization by evaporation, utilize circulation that cooling

fan

6,7 causes with the air themperature that is cooled in the storeroom stipulate, the cold-producing medium of evaporation gasification returns compressor 9 once more by liquid reservoir 14.

The concrete structure of compressor 9 as shown in Figure 3, be the reciprocating type double-stage compressor that the compression key element is made of low-pressure stage side compression unit 9a and hiigh pressure stage side compression unit 9b, utilize the eccentric shaft 9f of eccentric rotation that connecting rod 9g is moved back and forth along with the rotation of the rotating shaft 9e that is accommodated in the motor drive mechanism 9d in the closed shell 9c.

Front end at connecting rod 9g is fixed with piston 9i with ball-joint 9h embedding, reciprocating motion by the piston 9i in the cylinder body 9j, make described low-pressure stage side compression unit 9a and hiigh pressure stage side compression unit 9b alternately cold-producing medium be sucked, compress and output, owing to adopt ball-joint 9h at above-mentioned compression unit, thereby volumetric efficiency improves, and can suppress the expansion in profile space of the double-stage compressor 9 of needs two

compression unit

9a, 9b.

The suction inlet 9k of low-pressure stage side compression unit 9a is connected with the end of suction line 15, this suction line 15 utilizes liquid reservoir 14 freezingly to be connected with cooler 4 with described, the delivery outlet 9m of the refrigerant gas after the output compression is opened in the housing 9c, and the delivery outlet 9n of hiigh pressure stage side compression unit 9b is connected with the efferent duct 16 that leads to condenser 10.

Described liquid reservoir 14 pairs of gases, liquid separate, and the liquid refrigerants of all evaporations of failing in cooler 4 are stored, only gaseous refrigerant is sent, thereby prevent that the cylinder body 9j that flows into compressor 9 because of liquid refrigerant from producing fault, in the present embodiment, 14 of liquid reservoirs are arranged on freezing back segment with cooler 4.

Connect to be imported into the form that becomes the middle spatial portion of pressing in the closed shell 9c from the suction line 17 of described refrigeration with cooler 5.Thus, owing to do not flow directly in the cylinder body of compressor with the cold-producing medium that cooler 5 sucks,, get final product with small-sized liquid reservoir as being provided with then so there is no need specially liquid reservoir to be set at the back segment that refrigerates with cooler 5 from refrigeration.And, the refrigerant gas that sucks with the suction line 17 of cooler side from refrigeration and being inhaled into together from the refrigerant gas that the delivery outlet 9m of described low-pressure stage side compression unit 9a exports in the suction inlet 9p of hiigh pressure stage side compression unit 9b of connection, and be compressed.

Described compressor 9 utilizes VFC and ability is variable, can for example in 30～70Hz scope, determine speed according to poor, the rate of temperature change of the detected temperatures of freezing and refrigerating space and goal-setting temperature etc., and utilize the control device that constitutes by microcomputer etc. to turn round.

Transfer valve 11 is arranged on the outlet side of reception from the condenser 10 of the output gas of compressor 9, be used to switch the refrigerant flow path that leads to

cooler

4,5 sides and control flow, as shown in Figure 4, transfer valve 11 is a kind of triple valves, in clack box 18, be provided with valve seat 19, be formed with on this valve seat 19 and lead to freezing valve port A 19a and the valve port B 19b that leads to refrigeration side cooler 5 sides, valve body 20 is configured in the top of valve seat 19 with cooler 4 sides.

Valve body 20 is formed with groove A 20a and the groove B 20b that cross section, two places is V word shape on the lower surface of the heavy wall stage portion 20d that is configured as regulation ora terminalis shape, this groove A 20a and groove B 20b are corresponding on rotational trajectory with described valve port A 19a and valve port B 19b respectively, and with circular-arc extension specific length, and both are apart from the mobile radius difference of the rotation at rotating shaft 20c center, the upper surface of valve seat 19 is close to valve body 20 is overlapped, by the not shown stepper motor that is arranged on top with the capable driving rotation of 0～85 pulse step.

Pulse enable signal valve body 20 rotations that this transfer valve 11 utilizes the kind of refrigeration cycle control signal to produce, when overlapping up and down at the groove A 20a in the radius of turn of the above valve body of the predetermined pulse position outside and valve port A 19a when being communicated with, enter in the groove A 20a of V word shape from the open ora terminalis of the described heavy wall stage portion 20d of groove A 20a from flowing into the cold-producing medium that valve port 21 flows in the clack boxes 18, and flow out and import freezingly with the capillary 12 from the valve port A 19a that is communicated with groove A, gasify with evaporation in the cooler 4 freezing.

On the other hand, similarly, when the groove B 20b of radius of turn inboard and valve port B 19b were communicated with, the cold-producing medium that flows among the groove B 20b flowed into refrigeration with the capillary 13 from the valve port B 19b that is communicated with, and in refrigeration with evaporation in the cooler 15.

The V word shape flute profile of refrigeration side groove B 20b becomes sectional area and enlarges gradually to the open end of heavy wall stage portion 20d from the rotation front end, because the rotation of valve body 20 is communicated with valve port B 19b with the form of flow-through opening area from the minimum to the maximum, can fine control the switching and the Flow-rate adjustment of stream, can linear efficiently change refrigerant flow so utilize pulse to be rotated control.

The open control of the valve that triple valve 20 is carried out can be selected following various pattern: lead to and freezingly be with the opening degree of valve 19a, the 19b of cooler 5 that standard-sized sheet or full cut-off and freezing side valve opening dwindle and the valve opening that refrigerates the side standard-sized sheet or refrigerate side dwindles and freezing side standard-sized sheet etc. with cooler 4 and refrigeration, but in the present embodiment, freezingly be connected in parallel with cooler 5 with cooler 4 and refrigeration, cooling control has the freezing and refrigeration side to cool off simultaneously with freezing side only to cool off these two kinds.

The cold-producing medium that flows out from freezing side valve mouth A 19a flow through for reach with reefer space 2 the evaporating temperature that adapts of chilling temperature set capillary 12 time be depressurized, about-25 ℃, evaporate in freezing with cooler 4, similarly, the cold-producing medium that flows out from refrigeration side valve mouth B 19b flow through for reach with refrigerating space 3 the refrigeration set of approximate about-5 ℃ the evaporating temperature of chilling temperature be transported to capillary 13 and refrigerate with evaporating in the cooler 5.

Freezing usefulness in the described kind of refrigeration cycle and refrigeration make freezing with cooler 4 with refrigerate and to have temperature difference with the cold-producing medium evaporating temperature in the cooler 5 with capillary 12,13, therefore, strengthen the throttling of freezing side capillary 12, the result is as previously mentioned, cold-producing medium to freezing, when the refrigeration both sides are flowed, must be easy to the little refrigeration side flow of resistance, exist be difficult for the tendency to freezing side flow, extreme occasion cold-producing medium can occur not to the situation of freezing side flow.

In order to improve above-mentioned situation, respectively cooling freezing and refrigerating

space

2,3 is controlled with cold-producing medium stream at described transfer valve 11, and in order to prevent that the one-sided of so-called cold-producing medium from flowing, carry out throttling slightly with the refrigerant flow of refrigeration side that cold-producing medium is easy to flow into and append control.

And, if the groove A 20a of freezing side and valve port A 19a are communicated with and standard-sized sheet, then can be subjected to refrigerating the cold-producing medium stream mode influence of side hardly, the freezing refrigerating capacity stipulated of obtaining basically with cooler 4, for the refrigerating capacity of refrigeration side, also can utilize the groove B 20b of described transfer valve 11 and valve port 19b connected state from close to the range opened, and the rotation speed change of compressor 9 carry out trickle control.

Can make refrigeration exist temperature difference ground to improve by above-mentioned cold-producing medium current control with the evaporating temperature and the freezing side of cooler 5, the refrigeration room temperature can be cooled to 1～2 ℃, thereby but if strengthen refrigeration makes the heat exchange amount increasing that refrigerating space is cooled off with the heat transfer surface area of cooler 5 words, also can further improve evaporating temperature, the temperature difference of the chilling temperature of refrigerating space 3 and chiller temperature is littler at this moment, reduce the effect that to play and prevent the space inner drying, keeps the high humility in the case with the frost amount on the cooler 5 attached to refrigeration.

In general domestic refrigerator, the required refrigerating capacity of the cooling of reefer space and refrigerating space is identical basically, so, can cool off each cooling space efficiently by making refrigeration identical or bigger slightly with the freezing cooler 4 of using than it with the heat transfer surface area of cooler 5.

Action to kind of refrigeration cycle describes below.Connect power supply rear drive compressor 9, be compressed and the refrigerant gas that becomes high-temperature high-pressure state outputs to the condenser 10 from carrier pipe 16, arrive transfer valve 11 then.As previously mentioned, transfer valve 11 can carry out various patterns and set, but when above-mentioned power connection, because freezing, refrigerating

space

2,3 all is in uncooled state, so both valve port A 19a, B 19b are full-gear, cold-producing medium flows into freezing usefulness and refrigeration with in the capillary 12,13 and be depressurized, and flow into respectively freezing with cooler 4 and refrigerate and evaporate with each evaporating temperature with cooler 5, thereby each cooler is cooled to set point of temperature.

Flow into liquid reservoir 14 from freezing cold-producing medium with cooler 4, when just in case in cooler during the residual liquid refrigerant that evaporation fully arranged not, then be stored in liquid reservoir 14 inside, have only gaseous refrigerant to be inhaled into the low-pressure stage side compression unit 9a of compressor 9 from suction line 15.In the closed shell 9c that cold-producing medium in refrigerating with cooler 5 after the evaporation is pressed be imported into as described compressor 9 via suction line 17 in the middle of.

Compress the back the low-pressure stage side compression unit 9a and output to the refrigerant gas in the closed shell 9c and converge from freezing being drawn into from the refrigerant gas of refrigeration with the middle splenium of cooler 5 inflow closed shell 9c from delivery outlet 9m with cooler 4, be drawn into from suction inlet 9p the hiigh pressure stage side compression unit 9b then and compressed, output to the efferent duct 16 and directed toward condenser 10 from delivery outlet 9n again, thereby form kind of refrigeration cycle.

Therefore, adopt above-mentioned kind of refrigeration cycle, be provided with freezing and

refrigeration cooler

4,5, and both have capillary 12 respectively in order to reach the evaporating temperature of fitting mutually with reefer space 2 and refrigerating space 3 design temperature separately, 13, make the refrigerant gas after refrigeration is evaporated with cooler 5 directly be drawn into middle splenium in the compressor housing 9c with the middle pressure condition higher than freezing lateral pressure, thereby can make refrigeration with the evaporating temperature of cooler 5 with respect to freezing with the state raising of cooler 4 to adapt with indoor chilling temperature, and, because the compressor input diminishes, so cycle efficieny improves, and can reduce power consumption.

In addition, make refrigeration with the rising of the evaporating temperature of cooler 5 to reduce the temperature difference with refrigerating space, thereby reduce attached to the frost amount on the cooler 5, can prevent the refrigerating space inner drying, keep the high humility in the case, keep food fresh for a long time, and, cold-producing medium can flow into freezing usefulness simultaneously and refrigeration is cooled off with cooler 4,5 both sides, so compare with the existing alternately type of cooling, can suppress each indoor temperature change.

Shown in Figure 5 as the part mark prosign identical with Fig. 1, kind of refrigeration cycle also can described relatively compressor 9, the transfer valve 11 of condenser 10, refrigerant flow path is connected in series with cooler 5 with cooler 4 and refrigeration freezing, the shunt valve 22 that carries out bypass from 11 pairs of refrigerations of transfer valve with capillary 13 and refrigeration with cooler 5 is connected to freezingly with on the cooler 4 by gas-liquid separator 23 from freezing with capillary 12, and the top of described gas-liquid separator 23 is connected by the spatial portion that becomes the centre splenium in the closed shell 9c of suction line 24 and compressor 9.

Like this, cold-producing medium flows to refrigeration cooler 5 and freezing with cooler 4 simultaneously or optionally by the transfer valve of controlling as hereinbefore 11, be separated into gaseous refrigerant and liquid refrigerant with the cold-producing medium of cooler 5 at gas-liquid separator 23 from shunt valve 22 or refrigeration, liquid refrigerant is to freezing cooler 4 side flow of using, gaseous refrigerant returns the middle splenium of compressor 9 by refrigeration side suction line 24, and liquid refrigerant freezing with cooler 4 once more with low-temperature evaporation, and turn back to the low-pressure stage side of compressor 9, thereby the identical cycle efficieny that improves with previous embodiment plays and can will be cooled to the action effect of set point of temperature in each storeroom.

It is certain value and when making compressor 9 with the regulation rotation speed operation with cooler 4 and refrigeration with the condensation temperature of the evaporating temperature of cooler 5 even condenser 10 that Fig. 6 is illustrated in freezing, the refrigerating capacity of freezing side and refrigeration side, the longitudinal axis represents to refrigerate the refrigerating capacity of side, and transverse axis is represented the refrigerating capacity of freezing side.Among the figure, the expression of a point utilizes transfer valve to make cold-producing medium only flow into situation about refrigerating in the side cooler 5, b point expression only flows into the situation in the freezing side cooler 4, and c point is illustrated in the situation that cold-producing medium under the state that valve opening 19a, 19b be in standard-sized sheet flows into freezing usefulness and

refrigeration usefulness cooler

4,5 both sides.

In this chart, the quality of the cold-producing medium from the freezing low-pressure stage side compression unit 9a that directly is drawn into compressor 9 with cooler 4 or volume are discharged the volume decision by the cylinder body of low-pressure stage side compression unit, corresponding refrigeration power is 69W when only flowing into freezing side, is 64W and flow into freezing, refrigeration at the same time during side, not too can be subjected to turning back to the influence of the cold-producing medium the middle splenium of compressor 9 with cooler 5, show as certain substantially from refrigeration.

Relative therewith, the refrigeration side be drawn into the corresponding refrigeration power of refrigerant amount the compressor 9 from refrigeration with cooler 5, when only flowing into the refrigeration side is 155W, significantly be reduced to about 75W during side and flow into freezing, refrigeration at the same time, the refrigerating capacity of refrigeration side according to have the freezing cold-producing medium that sucks with cooler 4 of having no way of, promptly according to be only from refrigeration with the cold-producing medium of cooler 5 or become and from the amount of converging of freezing cold-producing medium with cooler 4 suctions and significantly variation.

In addition, because the indoor temperature of refrigerating space is+3～5 ℃ generally speaking, and the reefer space temperature is-18～-20 ℃, so it is big with the temperature difference of outdoor temperature, thereby the required refrigerating capacity of the cooling of the reefer space value more required than refrigerating space is big, thus, when the refrigerating capacity of freezing side is bigger than the refrigerating capacity of refrigeration side, when the duty ratio refrigeration side of setting freezing side is big, as schematically illustrate the shown in Figure 7 of Fig. 6, in cooling operation, use the big zone of the refrigerating capacity of freezing side, i.e. hatched example areas part among the figure.

Therefore, as previously mentioned, the refrigerating capacity of freezing side is not vulnerable to from refrigerating the influence of the cold-producing medium that returns with cooler 5, thereby the cooling of reefer space control is got final product by the rotating speed control of compressor 9, when cooling was not enough, then as shown by arrows, the rotating speed that improves compressor 9 was to increase refrigerating capacity, when excess coolant, thereby then by reducing its rotating speed or making it stop suitably to keep chilling temperature.The rotating speed of the then obstructed overcompression machine 9 of refrigeration side is controlled, thereby but carries out the chilling temperature that open and close controlling is regulated refrigerant flow control refrigeration side by the valve opening to transfer valve 11.

An embodiment who compressor rotary speed of the present invention is controlled with reference to the controlling party block diagram of Fig. 8 describes.Will by the detected reefer space of temperature sensor for example the indoor temperature Fa of refrigerating chamber 4 and the desired value Fr of regulation compare, its deviation is input to the PID controller 25 of the frequency that is used for determining compressor.

And,, increase the cooling that ormal weight promotes reefer space 2, the control of turning round in order to reach set point of temperature by the rotating speed that makes compressor 9 if the temperature of reefer space 2 than desired value Fr height, then increases the PID calculated value according to deviation.In addition, if the temperature of reefer space 2 is lower than desired value Fr, rotating speed is reduced or stops operating, to reduce refrigeration power.

Other embodiment to compressor rotary speed control of the present invention describe below.In the above-described embodiments, control the rotating speed of compressor 9, but according to refrigerator operating condition difference, relative reefer space 2 is also arranged and the occasion of the refrigerating capacity deficiency of refrigerating space 3 according to the temperature information of reefer space 2.

Therefore, if the temperature information of refrigerating space 3 is also imported with the temperature information of reefer space 2, make the words that turn round in the hatched example areas of compressor 9 in Fig. 7, then increase refrigerating capacity, thereby the refrigerating capacity of refrigerating space 3 can increase also with reefer space 2 by the rotating speed that improves compressor 9.

But, be cooled to desired value when following at reefer space 2, the rotating speed increase of compressor 9 can cause reefer space 2 is carried out unnecessary cooling, cause electric power to waste, therefore, in the block diagram of Fig. 9, with reefer space temperature Fa and desired value Fr thereof, refrigerating space temperature Ra and desired value Rr thereof are input in the PID controller 25 together, but when determining the rotating speed of compressor 9, import after the deviation data value of the temperature inside the box Fa of reefer space side and target temperature Fr for example be multiply by 2 times etc., thereby compare the feedback quantity of the temperature information data that strengthen reefer space 2 sides with refrigerating space 3.

Thus, the rotating speed of compressor 9 is according to the deviate bigger than reality, is the feedback temperature information of reefer space 2 sides, with freezing side is that benchmark is determined, but when reefer space 2 is in the abundant state of cooling, under the situation that does not improve compressor 9 rotating speeds, utilize transfer valve 11 controls to flow to the cold-producing medium stream of refrigeration with cooler 5, thereby the refrigerating capacity to the refrigeration side increases and decreases, and is controlled to be suitable temperature can not causing will refrigerating side under the supercooled situation of freezing side.

In the above-described embodiments, the situation that the temperature information of refrigerating space 3 is taken in to determine the rotating speed of compressor 9 is illustrated, but when the temperature of refrigerating space 3 is lower than desired value Rr just in case outside air temperature reduces, existence reduces the rotating speed of compressor 9 according to its feedback signal, the problem that the result causes the refrigerating capacity of reefer space 2 sides to descend.

Figure 10 is that reply is this just in case the block diagram of situation, only add temperature at refrigerating space 3 and feed back the function F x of this temperature information when higher than desired value Rr, hour import this value in the difference of refrigerating space temperature Ra and desired value Rr, but when negative value, then zero-signal is input in the PID controller 25.

By this kind control, even when the little and actual temperature Ra of the load of refrigerating space 3 is lower than goal-setting value Rr, reefer space 2 also can utilize the refrigeration power corresponding with its temperature information to keep desired value Fr, can prevent to cause the temperature of reefer space 2 than desired value Fr height because of refrigeration power descends.

Below another other embodiment are described.Figure 11 represents with certain certain rotating speed drive compression machine 9 and when refrigeration is changed with the temperature of cooler 5, and freezing usefulness and refrigeration are with the refrigerating capacity QF1 that circulates, the variation of QR1.

At this moment, refrigeration can make its refrigerating capacity QR1 descend with cooler 5 by reducing its surface temperature as can be known, by improving its surface temperature refrigerating capacity is risen, and, freezing side refrigerating capacity QF1 makes chiller temperature necessarily for example be-23.5 ℃, even the refrigerating capacity change of refrigeration side can not be subjected to big influence yet.

And, with cooler 5,, rotating speed is descended for refrigeration if change the rotating speed of refrigeration with fan 7, then refrigeration reduces with the heat exchange amount in the cooler 5, the surface temperature of cooler 5 reduces, and the result is that the refrigerating capacity QR1 of kind of refrigeration cycle also descends, on the contrary, if improve the rotating speed of fan 7, then heat exchange amount increases, thereby the surface temperature of cooler 5 rises, and the refrigerating capacity QR1 of circulation increases.

Promptly, cooling control for refrigerating space 3, can control space temperature with the rotating speed of fan 7 by increase and decrease refrigeration, when refrigerating space temperature Ra is higher than its desired value Rr, can improve the rotating speed that refrigerates with fan 7 cools off, when sub-cooled is following to desired value Rr, can weakens refrigeration power by reducing rotation speed of the fan, thereby be controlled to the suitable temperature of regulation.

When Figure 12 represents to make freezing temperature with cooler 4 to change, freezing usefulness and the refrigeration refrigerating capacity QF2 of circulation, the variation of QR2, freezing temperature with cooler 4 is reduced, thereby reduce by the freezing circulating mass of refrigerant that is drawn into the low-pressure stage side of compressor 9 with cooler 4, the refrigerating capacity QF2 of freezing side circulation reduces.In addition, the refrigerant amount that is transported to hiigh pressure stage side compression unit owing to the low-pressure stage side from compressor 9 also reduces, so because relation of the discharge volume of hiigh pressure stage side compression unit, splenium in the middle of returning with cooler 5 from refrigeration and the refrigerant amount that is inhaled into hiigh pressure stage side compression unit increases, thereby the refrigerating capacity QR2 increase of refrigeration side circulation.

Thus, in the temperature of refrigerating space 3 when high and cooling is not enough than desired value Rr or when the refrigeration power of reefer space 2 is excessive, by reducing the rotating speed of freezing side cooling fan 6, reduce freezing with the heat exchange amount in the cooler 4, the surface temperature of cooler 4 is descended, thereby the circulation ability QR2 that can make the refrigeration side increases or the circulation ability QF2 of freezing side is reduced, and cooling space separately can be controlled at suitable temperature.

Like this, since cold-producing medium to freezing flow into cooler 4 in, also flow into cooler 5 to refrigeration, can improve evaporating temperature, thereby can cool off reefer space 2 and refrigerating space 3 high cycle efficieny ground, even at the temperature load that drops at any time in each storage space, also can utilize the cold-producing medium current control transfer valve 11 that is made of triple valve to carry out reliable refrigerant amount distributes, thereby but the temperature change of freezing-inhibiting space and refrigerating space is suitably controlled each space temperature.

In the kind of refrigeration cycle of above explanation, can control to make cold-producing medium stream flow to freezing simultaneously and refrigerate and use

cooler

4,5 both sides, thereby compare with the existing control that in two coolers, alternately flows into cold-producing medium, cold-producing medium can the secund cooler, and the required refrigerant amount of kind of refrigeration cycle can excessively not increase.Therefore, even when combustible refrigerants such as employing hydrocarbon class cold-producing medium, owing to can reduce the cold-producing medium loading, security improves.

The situation of pressing in the middle of in the foregoing description to double-stage compressor 9 with the pressure in the compressor housing 9c serving as is illustrated, but be not limited thereto, though do not illustrate especially, but also can make from freezing suction line with cooler as the low pressure housing to be communicated with the compression case intracorporeal space, will be from refrigerating on the connecting portion of suction inlet that suction line with cooler is connected the delivery outlet of low-pressure stage side compression unit and hiigh pressure stage side compression unit.Similarly, as High Pressure Shell, also can will be connected from freezing suction line on the low-pressure stage side compression unit suction inlet with cooler, to be connected with the suction line of cooler on the connecting portion of suction inlet of the delivery outlet of low-pressure stage side compression unit and hiigh pressure stage side compression unit from refrigeration, will in High Pressure Shell, export from the output gas of hiigh pressure stage side compression unit to the efferent duct that leads to condenser.

Utilizability on the industry:

The present invention can be applicable to and utilizes two-stage compression refrigeration circulation formation to improve on the refrigerator of cycle efficieny.

Description of drawings

Fig. 1 is the refrigeration cyclic graph of the refrigerator of expression the present invention one example.

Fig. 2 is the summary longitudinal sectional view of refrigerator with kind of refrigeration cycle of Fig. 1.

Fig. 3 is the longitudinal sectional view of the double-stage compressor in the detailed presentation graphs 1.

Fig. 4 is the vertical view of the major part of the triple valve in the detailed presentation graphs 1.

Fig. 5 is the structure chart of other embodiment of expression kind of refrigeration cycle.

Fig. 6 is a graph of a relation freezing and refrigeration side refrigerating capacity and cold-producing medium.

Fig. 7 is the schematic diagram of Fig. 6.

Fig. 8 is the block diagram of compressor rotary speed control.

Fig. 9 is the rotating speed controlling party block diagram that has added in the control of Fig. 8 after the refrigerated storage temperature information.

Figure 10 has made rotating speed controlling party block diagram after the further improvement to the control of Fig. 9.

Figure 11 is the key diagram that is illustrated in the variation of freezing and refrigeration side refrigerating capacity when refrigeration of the present invention is changed with chiller temperature.

Figure 12 is illustrated in the key diagram that makes the freezing variation of freezing and refrigeration side refrigerating capacity when changing with chiller temperature of the present invention.

Figure 13 is the refrigeration cyclic graph of current refrigerator.

(component symbol explanation)

1 refrigerator body, 2 reefer spaces, 3 refrigerating spaces

4 is freezing with cooler 5

refrigeration cooler

6,7 cooling fans

8 Machine Rooms, 9 double-stage compressor 9a low-pressure stage compression units

9b hiigh pressure stage compression unit 9c housing 10 condensers

11 transfer valves 12 are freezing with capillary 13 refrigeration capillaries

14 liquid reservoirs, 15 freezing side suction line 16 efferent ducts

17,24 refrigeration side suction lines, 18 clack boxes, 19 valve seats

The freezing side valve mouth of 19a A 19b refrigeration side valve mouth B 20 valve bodies

The freezing side groove of 20a A 20b refrigeration side groove B 20c rotating shaft

20d heavy wall stage portion 21 flows into valve port 22 shunt valves

23 gas-liquid separators, 25 PID controllers

Claims

1, a kind of refrigerator, by compressor, transfer valve, freezing with cooler and refrigeration form kind of refrigeration cycle with cooler, described compressor compression key element is made of low-pressure stage side compression unit and hiigh pressure stage side compression unit, because of the variable compressor of frequency conversion drive ability, described transfer valve is controlled flow with refrigerant flow path, and this refrigerant flow path is arranged on the condensator outlet side of reception from the output gas of described compressor, described freezing with cooler and refrigeration be connected with described transfer valve by decompressor respectively with cooler, it is characterized in that, determine the rotating speed of described compressor according to reefer space temperature and desired value thereof.

2, a kind of refrigerator, by compressor, transfer valve, freezing with cooler and refrigeration form kind of refrigeration cycle with cooler, described compressor compression key element is made of low-pressure stage side compression unit and hiigh pressure stage side compression unit, because of the variable compressor of frequency conversion drive ability, described transfer valve is controlled flow with refrigerant flow path, and this refrigerant flow path is arranged on the condensator outlet side of reception from the output gas of described compressor, described freezing with cooler and refrigeration be connected with described transfer valve by decompressor respectively with cooler, it is characterized in that, according to reefer space temperature and desired value thereof, refrigerating space temperature and desired value thereof are determined the rotating speed of compressor, when determining rotating speed, compare the temperature information feedback quantity that strengthens the reefer space side with refrigerating space.

3, refrigerator as claimed in claim 2 is characterized in that, only when the refrigerating space temperature is higher than its desired value, its temperature information is used for determining compressor rotary speed.

4, as each described refrigerator in the claim 1 to 3, it is characterized in that, when the refrigerating space temperature is higher than its desired value, strengthen refrigeration side speed of cooling fan.

5, as each described refrigerator in the claim 1 to 4, it is characterized in that, when the refrigerating space temperature is higher than its desired value, reduce freezing side speed of cooling fan.