CN205261965U - But varactor doublestage compression system - Google Patents
But varactor doublestage compression system Download PDFInfo
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- CN205261965U CN205261965U CN201521127010.8U CN201521127010U CN205261965U CN 205261965 U CN205261965 U CN 205261965U CN 201521127010 U CN201521127010 U CN 201521127010U CN 205261965 U CN205261965 U CN 205261965U
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Abstract
The utility model provides a but varactor doublestage compression system, including compressor (1), wherein compressor (1) includes the low pressure jar and the high pressure cylinder of establishing ties, wherein the low pressure jar includes two at least parallelly connected cylinders, compression system still includes steerablely the control mechanism that at least one cylinder in two at least parallelly connected cylinders carries out full -load run and/or no -load running. The utility model discloses can realize the height and arbitrarily downgrade the discharge capacity than variable on a compressor, compare its efficiency of system that two compressors establish ties change less, can satisfy the refrigeration and the efficiency that heats requires, improves greatly the economic nature of system simultaneously, and the structure is simpler, the cost is lower, and does not have the equal oily uneven scheduling problem of two compressors, the operating temperature scope and the operating efficiency of system can also be improved in addition, doublestage compression system's reliability is improved to doublestage compression system's economic nature is greatly improved.
Description
Technical field
The utility model belongs to air-conditioning technical field, is specifically related to a kind of variable capacity Two-stage Compression system.
Background technology
Environment temperature is lower, larger to the demand of air-conditioning heating amount, but the heat pump of single stage compress can only at presentAccomplishing that minus 20 degrees (outdoor environment temperature) is above normal starts operation, and heating capacity seriously decays, systemThermal effect can not ensure, unit reliability also meets a severe test.
Compare single stage compress heat pump, with air injection enthalpy-increasing Two-stage Compression system, heating capacity is larger at low temperatures,Efficiency is higher. And Two-stage Compression system can reduce the pressure ratio of single-stage compressor, reduce delivery temperature, simultaneouslyGettering efficiency and compression efficiency be can improve, thereby heating capacity and heating efficiency promoted.
Existing double-stage compressor is because high pressure cylinder volume and low pressure (LP) cylinder volume are fixed, and its volumetric ratio is for fixingValue, thereby the height of compressor arbitrarily downgrades discharge capacity than fixing, and any discharge capacity exists than fixing compressorCertain specific operation only has an efficiency peak, and along with air-conditioning load variations, efficiency changes greatly, warpJi property is undesirable. On the other hand, under nominal cooling condition, the best height of Two-stage Compression system is arbitrarily downgradedCompression ratio is in 0.9 left and right, and under low-temperature heating operating mode, and the compression ratio that height is arbitrarily downgraded is in 0.6 left and right the best,And the efficiency requirement that a kind of Two-stage Compression system of fixing compression ratio cannot meet refrigeration simultaneously and heat.
Existing Two-stage Compression system, only can rely on the mode of two frequency-changeable compressor series connection to realize high-low pressureThe variation of level discharge capacity ratio, system complex, system cost is high, and oil return poor reliability.
Change greatly because Two-stage Compression system of the prior art exists efficiency, a kind of fix compression ratio cannotThe efficiency that simultaneously meets refrigeration and heat requires, the undesirable technical problem of economy, therefore the utility modelResearch and design goes out a kind of variable capacity Two-stage Compression system.
Utility model content
Therefore, the technical problems to be solved in the utility model is to overcome Two-stage Compression system of the prior artThere is efficiency changes greatly, a kind of fixing compression ratio cannot meet refrigeration simultaneously and heat efficiency requirement, warpThe defect that Ji property is undesirable, thus a kind of variable capacity Two-stage Compression system is provided.
The utility model provides a kind of variable capacity Two-stage Compression system, comprises compressor, wherein said compressorComprise low pressure (LP) cylinder and the high pressure cylinder of series connection, wherein said low pressure (LP) cylinder comprises at least two cylinders in parallel, described inVariable capacity Two-stage Compression system also comprises at least one cylinder at least two cylinders in parallel described in controlCarry out the controlling organization of full-load run and/or no-load running.
Preferably, described high pressure cylinder is one, is the 3rd cylinder, and wherein low pressure (LP) cylinder comprises two, is respectivelyThe first cylinder and the second cylinder.
Preferably, described the first cylinder can be realized no-load running or two kinds of operational modes of full-load run, and instituteState the second cylinder and described the 3rd cylinder full-load run always.
Preferably, in the time that the first cylinder is zero load, now in low pressure (LP) cylinder, only the second cylinder is being worked, refrigerant warpCross after the second cylinder compression and after middle jet mixing, enter described the 3rd cylinder and carry out second level compression.
Preferably, when the first cylinder is full load, now the first cylinder of low pressure (LP) cylinder and the second cylinder all carry outWork, refrigerant enters respectively the first cylinder and the second cylinder, compresses respectively through the first cylinder and the second cylinderAfter refrigerant and middle jet mixing, then enter the 3rd cylinder and carry out second level compression.
Preferably, described controlling organization comprises the pipeline structure and the setting that are connected with described low pressure (LP) cylinder air entryElectromagnetic valve structure on described pipeline structure.
Preferably, in the time that described low pressure (LP) cylinder comprises the first cylinder and the second cylinder, described pipeline structure comprise withThe first pipeline that the air entry of described the first cylinder is connected, and comprise and the air entry of described the second cylinderThe second pipeline being connected.
Preferably, described electromagnetic valve structure comprises the first magnetic valve and the setting that are arranged on described the first pipelineThe second magnetic valve on described the second pipeline.
The variable capacity Two-stage Compression system that the utility model provides has following beneficial effect:
1. variable capacity Two-stage Compression system of the present utility model can realize height and arbitrarily downgrade on a compressorDischarge capacity is than variable, and that its efficiency changes is less, can meet refrigeration and the efficiency that heats requires, raising greatly simultaneouslyThe economy of system;
2. variable capacity Two-stage Compression system of the present utility model, the system of two the compressor series connection that compare moreAdd simply, cost is lower, and does not have the problems such as two compressor oil equalization imbalances;
3. temperature range of operation and the operational efficiency of system can also be improved in addition, and Two-stage Compression can also be improvedThe reliability of system, thus the economy of Two-stage Compression system greatly improved.
Brief description of the drawings
Fig. 1 is the structural representation of variable capacity Two-stage Compression system of the present utility model;
Fig. 2 is refrigerating operaton scope and the transfiguration control chart of variable capacity Two-stage Compression system of the present utility model;
Fig. 3 is heating operation scope and the transfiguration control chart of variable capacity Two-stage Compression system of the present utility model.
In figure, Reference numeral is expressed as:
1-compressor, the air entry of the 101-the first cylinder, the air entry of the 102-the second cylinder, 2-theOne pipeline, the 3-the second pipeline, the 4-the first magnetic valve, the 5-the second magnetic valve, 6-gas-liquid separator,7-outdoor heat exchanger, 8-cross valve, 9-electric expansion valve, 1,10-flash vessel, 11-electronic expansionValve 2 (aeration valve), 12-compressor carries vapour liquid separator.
Detailed description of the invention
As shown in Figure 1, the utility model provides a kind of variable capacity Two-stage Compression system, comprises compressor,Wherein said compressor comprises low pressure (LP) cylinder and the high pressure cylinder of series connection, and wherein said low pressure (LP) cylinder comprises at least two alsoThe cylinder of connection, described variable capacity Two-stage Compression system also comprises described in control at least two cylinders in parallelAt least one cylinder carries out the controlling organization of full-load run or no-load running.
By above-mentioned structure can on a compressor, realize height arbitrarily downgrade discharge capacity can than (or volumetric ratio)Become, that its efficiency of system of two compressors series connection that compares changes is less, can meet refrigeration simultaneously and makeThe efficiency of heat requires, has greatly improved the economy of system; And structure is simpler, cost is lower, andThere is not the problems such as two compressor oil equalization imbalances; Can also improve in addition temperature range of operation and the fortune of systemLine efficiency, and can also improve the reliability of Two-stage Compression system, thus Two-stage Compression system greatly improvedEconomy.
Preferably, described high pressure cylinder is one, is the 3rd cylinder, and wherein low pressure (LP) cylinder comprises two, is respectivelyThe first cylinder and the second cylinder. This is a kind of structure and embodiment of cylinder of preferred compressor, canBy the first and second cylinders of being arranged in parallel according to regulating in different actual demand situations, then in conjunction with doingFor the 3rd cylinder of high pressure cylinder, arbitrarily downgrade discharge capacity than variable thereby realize height, efficiency changes little, meets refrigerationWith the efficiency demand heating, and effect and the object of raising economy.
Preferably, described the first cylinder can be realized no-load running or two kinds of operational modes of full-load run, and instituteState the second cylinder and described the 3rd cylinder full-load run always. This be one preferred embodiment, byThe full-load run always of two cylinders and the 3rd cylinder can effectively ensure normally carrying out of Two-stage Compression, more simultaneouslyIn conjunction with regulating the first cylinder to realize the means of no-load running or full-load run, thereby it is two to regulate this compressor to realizeConversion between cylinder-tri-cylinder pattern, realizes the variation of the discharge capacity ratio of just arbitrarily downgrading, and reaches system energy efficiency is becomeChange littlely, can meet refrigeration simultaneously, heat the object of efficiency demand.
Preferably, when the first cylinder is while being unloaded, now the second cylinder only in low pressure (LP) cylinder (being also low-pressure stage)In work, refrigerant enters described the 3rd cylinder and carries out the after mixing with centre is jet after the second cylinder compressionTwo-stage compression, now the height discharge capacity larger (discharge capacity is than the ratio of volume that is two cylinders) of arbitrarily downgrading, supposesNow discharge capacity is than being a; This kind of operational mode is applicable to the less situation of load; And claim this kind of operational mode to beTwin-tub pattern.
Preferably, when the first cylinder is full load, now the first cylinder of low pressure (LP) cylinder (being also low-pressure stage) andThe second cylinder all carries out work, and refrigerant (from vapour liquid separator 6) enters respectively the first cylinder and the second gasCylinder, refrigerant and middle jet mixing after the first cylinder and the second cylinder compress respectively, pass through low pressureRefrigerant and middle jet mixing after cylinder compression, then enter the 3rd cylinder (being high pressure cylinder) and carry out second level pressureContracting, the discharge capacity of now just arbitrarily downgrading is smaller, supposes that now discharge capacity is than being b; This kind of operational mode is applicable to bearCarry larger situation, and claim that this kind of operational mode is three cylinder patterns.
Preferably, described controlling organization comprises the pipeline structure and the setting that are connected with described low pressure (LP) cylinder air entryElectromagnetic valve structure on described pipeline structure. Realize cold-producing medium is led in low pressure (LP) cylinder by pipeline structureObject, can carry out regulating action to the cold-producing medium in pipeline according to actual needs by electromagnetic valve structure, fromAnd reach the object of switching between twin-tub-tri-cylinder pattern.
Preferably, in the time that described low pressure (LP) cylinder comprises the first cylinder and the second cylinder, described pipeline structure comprise withThe first pipeline 2 that the air entry 101 of described the first cylinder is connected, and comprise with described the second cylinderThe second pipeline 3 that air entry 102 is connected. By be connected with the air entry of described the first cylinder firstPipeline makes cold-producing medium can enter the air entry of the first cylinder, by with the air entry phase of described the second cylinderThe second pipeline being communicated with makes cold-producing medium can enter the air entry of the second cylinder, reaches connection cold-producing medium and entersObject in cylinder.
Preferably, described electromagnetic valve structure comprises the first magnetic valve 4 Hes that are arranged on described the first pipeline 2Be arranged at the second magnetic valve 5 on described the second pipeline 3. By being arranged at the first electromagnetism on above-mentioned pipelineValve and the second magnetic valve can effectively reach the object of the cold-producing medium in pipeline described in switching, play effectivelyControl action.
Regulate and can realize transfiguration twin-stage pressure by the opening and closing of the first magnetic valve 4 and the second magnetic valve 5The height of contracting machine is arbitrarily downgraded discharge capacity than changing.
The utility model has been created a kind of height of realizing and has been arbitrarily downgraded discharge capacity than the two-stage compression heat pump system changing,This system can realize the Two-stage Compression operation of high compression ratio, the less or indoor function at system loading on the one handPower demand has efficient operational efficiency when lower, on the other hand, also can realize the twin-stage of low compression ratio and pressContracting also has efficient operational efficiency in the time that system loading is large or indoor unit capability demand is higher. This practicalityThe novel temperature range of operation of not only widening unit refrigeration and heating, and than conventional two-stage compressionSystem, high-temperature refrigeration and low-temperature heating efficiency also have a distinct increment, and especially low-temperature heating capacity promotes significantly, makesUnit can have powerful heating capacity and heating efficiency in the environment temperature below-20 DEG C, fully protectsComfortableness and the economy of low-temperature heating operation are demonstrate,proved.
The utility model also provides a kind of variable capacity Two-stage Compression control method, and it uses aforesaid variable capacityTwo-stage Compression system is carried out the control and regulation of transfiguration Two-stage Compression by described controlling organization to it. By usingAforesaid variable capacity Two-stage Compression system can realize height and arbitrarily downgrade discharge capacity than (or volume on a compressorThan) variable, that its efficiency of system of two compressors series connection that compares changes is less, can meet system simultaneouslyThe efficiency that cold-peace heats requires, has greatly improved the economy of system; And structure is simpler, cost moreLow, and there is not the problems such as two compressor oil equalization imbalances; Can also improve in addition the running temperature model of systemEnclose and operational efficiency, and can also improve the reliability of Two-stage Compression system, thereby greatly improved Two-stage CompressionThe economy of system.
Preferably, in the time that described controlling organization comprises the first magnetic valve and the second magnetic valve, need to enter in systemWhen row twin-tub mode operation, the first magnetic valve 4 is opened, the second magnetic valve 5 cuts out, compressor firstCylinder no-load running, now compressibility enter twin-tub operational mode (native system adopt be by machinery sideFormula realizes the compressor that cylinder body switches, and mainly controls compressor internal part by refrigerant pressure and realizes oneCylinder fully loaded and unloaded. The effect of magnetic valve one and magnetic valve two is exactly to introduce pressure and relieving pressure, fromAnd control cylinder is fully loaded and unloaded. Refrigerant in magnetic valve one and magnetic valve two pipelines only opens or closes at valveHave in a flash mobilely, be thereafter inactive state, the refrigerant in magnetic valve 1 and 2 pipelines can't enter pressureContracting machine is compressed. Lower same). Realize the effect of the adjusting of twin-tub operational mode.
Preferably, in the time that described controlling organization comprises the first magnetic valve and the second magnetic valve, need to enter in systemWhen row three cylinder mode operation, the second magnetic valve 5 is opened, and the first magnetic valve 4 cuts out, compressor the first gasCylinder full-load run; Now compressibility enters three cylinder operational modes. Thereby realize the adjusting of twin-tub operational modeEffect.
Preferably, the unlatching of described the first magnetic valve 4 and/or the second magnetic valve 5 and/or close, according toThe situation of complete machine load and indoor and outdoor surroundings temperature and controlling. Thereby reach by according to complete machine loadAnd the situation of indoor and outdoor surroundings temperature controls first, second magnetic valve, realize according to actual conditionsControl the adjusting object that compressibility carries out twin-tub or three cylinder patterns.
As shown in Figure 2, preferably, in the time that cooling system moves, judge outdoor environment temperature and indoor setExecutable operations action after rate of load condensate: when outdoor environment temperature and relatively low (the now chamber of indoor set loadInterior machine ability need is less) time, open the first magnetic valve 4, close the second magnetic valve 5, now compressionMachine is with twin-tub mode operation; When outdoor environment temperature and relatively high (the now indoor function of indoor set loadPower demand is larger) time, open the first magnetic valve 4, close the second magnetic valve 5, now compressor is with threeCylinder mode operation. Here relatively high and relatively lowly judge according to following method:
Fig. 2 is unit refrigerating operaton scope and transfiguration control chart, outdoor when wherein abscissa is refrigerating operatonEnvironment temperature, ordinate is indoor set rate of load condensate.
Suppose that unit refrigerating operaton outdoor environment temperature and load range are as dotted line frame in Fig. 2, straight lineA-B-C-D (straight line A-B-C-D draws according to the operational efficiency of Two-stage Compression system) is by unit operation modelEnclose and be divided into C1 and two regions of C2. The outdoor environment temperature in C1 region is relatively low, indoor set loadRate is relatively low, means that indoor unit capability demand is less, now less to the demand of compressor power;The outdoor environment temperature in C2 region is relatively high, indoor set rate of load condensate is relatively high, means indoor functionPower demand is higher, now larger to the demand of compressor power. Therefore, when stable operation of unit, firstJudge outdoor environment temperature and indoor set rate of load condensate. When outdoor environment temperature and indoor set are loaded in C1, the first magnetic valve 4 is opened when in the region, and the second magnetic valve 5 cuts out, and now compressor is transported with twin-tub patternOK. When outdoor environment temperature and indoor set rate of load condensate are in C2 region or when straight line A-B-C-D is upper, theTwo magnetic valves 5 are opened, and the first magnetic valve 4 cuts out, and now compressor is with three cylinder mode operations.
As shown in Figure 3, preferably, in the time of system heating operation, judge outdoor environment temperature and indoor setExecutable operations action after rate of load condensate: when outdoor environment temperature is relatively high and indoor set rate of load condensate is relativeWhen lower (now indoor unit capability demand is less), open the first magnetic valve 4, close the second magnetic valve5, now compressor is with twin-tub mode operation; When outdoor environment temperature is relatively low and indoor set loadWhen rate is relatively high (now indoor unit capability demand is larger), open the second magnetic valve 5, close firstMagnetic valve 4, now compressor is with three cylinder mode operations. Under the relatively high and relatively low basis hereThe method of stating judges:
Fig. 3 is unit heating operation scope and transfiguration control chart, outdoor when wherein abscissa is refrigerating operatonEnvironment temperature, ordinate is indoor set rate of load condensate.
Suppose that unit heating operation outdoor environment temperature and load range are as dotted line frame in Fig. 3, straight lineE-F-G-H (straight line A-B-C-D draws according to the operational efficiency of Two-stage Compression system) is by unit operation modelEnclose and be divided into H1 and two regions of H2, the outdoor environment temperature in H1 region is relatively high, indoor set loadRate is relatively low, means that indoor unit capability demand is less, now less to the demand of compressor power;The outdoor environment temperature in H2 region is relatively low, indoor set rate of load condensate is relatively high, means indoor setAbility need is higher, now larger to the demand of compressor power. Therefore, when stable operation of unit, headFirst judge outdoor environment temperature and indoor set rate of load condensate. When outdoor environment temperature and indoor set rate of load condensate in, the first magnetic valve 4 is opened when in H1 the region, and the second magnetic valve 5 cuts out, and now compressor is with twin-tub mouldFormula operation. When outdoor environment temperature and indoor set rate of load condensate are in H2 region or when straight line E-F-G-H is upper,The second magnetic valve 5 is opened, and the first magnetic valve 4 cuts out, and now compressor is with three cylinder mode operations.
Introduce preferred embodiment of the present utility model below
The utility model adopts a kind of double-stage compressor that can transfiguration, and this compressor has three cylinders, itsIn a cylinder (the 3rd cylinder) be high pressure cylinder, two cylinders (the first cylinder and the second cylinder) are low pressureCylinder, the first cylinder and the second cylinder are parallel-connection structure, and low pressure (LP) cylinder (the first cylinder and the second cylinder) is with highCylinder pressure (the 3rd cylinder) is cascaded structure. The first cylinder can be realized no-load running and two kinds of fortune of full-load runRow mode, and the second cylinder and the 3rd cylinder always are full-load run.
A. in the time that the first cylinder is zero load, now only the second cylinder is in work for low-pressure stage, and refrigerant is through the second gasAfter cylinder compression with after middle jet mixing, enter the 3rd cylinder and carry out second level compression, the discharge capacity of now just arbitrarily downgradingLarger, suppose that now discharge capacity is than being a; This kind of operational mode is applicable to the less situation of load; And claim thisPlanting operational mode is twin-tub pattern;
B. when the first cylinder is full load, now the first cylinder of low-pressure stage and the second cylinder all carry out work,Refrigerant enters respectively the first cylinder and the second cylinder from vapour liquid separator, through refrigerant after low-pressure stage compression withMiddle jet mixing, the refrigerant after the first cylinder and the compression of the second cylinder mixes with jet, then entersEntering high pressure cylinder is that the 3rd cylinder carries out second level compression, and the discharge capacity of now just arbitrarily downgrading is smaller, supposes now rowAmount is than being b; This kind of operational mode is applicable to the situation that load is larger, and claims that this kind of operational mode is three cylinder mouldsFormula.
This system by regulate compressor mesolow level the first cylinder zero load and be fully loaded with to realize high-low pressureLevel discharge capacity ratio, and the fully loaded of the first cylinder in compressor need be controlled by system pressure with unloaded switchingSystem.
Fully loaded and the unloaded concrete control mode of switching of the first cylinder is as follows:
1, when unit operation, the first magnetic valve 4 is opened, and the second magnetic valve 5 cuts out, compressor firstCylinder no-load running; It is now twin-tub operational mode;
2, when unit operation, the second magnetic valve 5 is opened, and the first magnetic valve 4 cuts out, compressor firstCylinder full-load run; Be now three cylinder operational modes;
And the opening and closing control of the first magnetic valve 4 and the second magnetic valve 5, according to complete machine load andThe situation of indoor and outdoor surroundings temperature and determining. Its control mode is as follows.
Refrigerating operaton:
Fig. 2 is unit refrigerating operaton scope and transfiguration control chart, outdoor when wherein abscissa is refrigerating operatonEnvironment temperature, ordinate is indoor set rate of load condensate.
Suppose that unit refrigerating operaton outdoor environment temperature and load range are as dotted line frame in Fig. 2, straight lineUnit operation scope is divided into C1 and two regions of C2 by A-B-C-D. The outdoor environment temperature in C1 regionRelatively low, indoor set rate of load condensate is relatively low, means that indoor unit capability demand is less, now to pressThe demand of contracting mechanomotive force is less; The outdoor environment temperature in C2 region is relatively high, indoor set rate of load condensate is relativeHigher, mean that indoor unit capability demand is higher, now larger to the demand of compressor power. Therefore,When stable operation of unit, first judge outdoor environment temperature and indoor set rate of load condensate. Work as outdoor environment temperatureAnd indoor set loads in the time of C1 region, the first magnetic valve 4 is opened, and the second magnetic valve 5 cuts out, thisTime compressor with twin-tub mode operation. When outdoor environment temperature and indoor set rate of load condensate in C2 region orWhen straight line A-B-C-D is upper, the second magnetic valve 5 is opened, and the first magnetic valve 4 cuts out, now compressor withThree cylinder mode operations.
Heating operation:
Fig. 3 is unit heating operation scope and transfiguration control chart, outdoor when wherein abscissa is refrigerating operatonEnvironment temperature, ordinate is indoor set rate of load condensate.
Suppose that unit heating operation outdoor environment temperature and load range are as dotted line frame in Fig. 3, straight lineUnit operation scope is divided into H1 and two regions of H2, the outdoor environment temperature in H1 region by E-F-G-HRelatively high, indoor set rate of load condensate is relatively low, means that indoor unit capability demand is less, now to pressThe demand of contracting mechanomotive force is less; The outdoor environment temperature in H2 region is relatively low, indoor set rate of load condensate phaseTo higher, mean that indoor unit capability demand is higher, now larger to the demand of compressor power. Therefore,When stable operation of unit, first judge outdoor environment temperature and indoor set rate of load condensate. Work as outdoor environment temperatureAnd indoor set rate of load condensate is in the time of H1 region, the first magnetic valve 4 is opened, and the second magnetic valve 5 cuts out,Now compressor is with twin-tub mode operation. When outdoor environment temperature and indoor set rate of load condensate are in H2 regionOr straight line E-F-G-H is when upper, the second magnetic valve 5 is opened, and the first magnetic valve 4 cuts out, now compressorWith three cylinder mode operations.
Those skilled in the art will readily understand, under the prerequisite of not conflicting, above-mentioned each advantageous manner canFreely to combine, to superpose.
The foregoing is only preferred embodiment of the present utility model, not in order to limit the utility model,All any amendments of doing within spirit of the present utility model and principle, be equal to and replace and improvement etc., all shouldWithin being included in protection domain of the present utility model. The above is only preferred enforcement side of the present utility modelFormula, it should be pointed out that for those skilled in the art, is not departing from the utility model skillUnder the prerequisite of art principle, can also make some improvement and modification, these improve and modification also should be considered as this realityWith novel protection domain.
Claims (8)
1. a variable capacity Two-stage Compression system, comprises compressor (1), it is characterized in that: described compressionMachine (1) comprises low pressure (LP) cylinder and the high pressure cylinder of series connection, and wherein said low pressure (LP) cylinder comprises at least two gas in parallelCylinder, described variable capacity Two-stage Compression system also comprises described in control at least one at least two cylinders in parallelIndividual cylinder carries out the controlling organization of full-load run and/or no-load running.
2. variable capacity Two-stage Compression system according to claim 1, is characterized in that: described high pressureCylinder is one, is the 3rd cylinder, and wherein low pressure (LP) cylinder comprises two, is respectively the first cylinder and the second cylinder.
3. variable capacity Two-stage Compression system according to claim 2, is characterized in that: described firstCylinder can be realized no-load running or two kinds of operational modes of full-load run, and described the second cylinder and the described the 3rdCylinder is full-load run always.
4. variable capacity Two-stage Compression system according to claim 3, is characterized in that: when the first gasWhen cylinder is unloaded, now in low pressure (LP) cylinder only the second cylinder in work, refrigerant after the second cylinder compression with inBetween enter described the 3rd cylinder after jet mixing and carry out second level compression.
5. variable capacity Two-stage Compression system according to claim 3, is characterized in that: when the first gasCylinder is full load, and now the first cylinder of low pressure (LP) cylinder and the second cylinder all carry out work, and refrigerant enters respectivelyOne cylinder and the second cylinder, the refrigerant after the first cylinder and the second cylinder compress is respectively with middle jet mixedClose, then enter the 3rd cylinder and carry out second level compression.
6. according to the variable capacity Two-stage Compression system one of claim 1-5 Suo Shu, it is characterized in that: described inControlling organization comprises the pipeline structure being connected with described low pressure (LP) cylinder air entry and is arranged at described pipeline structureOn electromagnetic valve structure.
7. variable capacity Two-stage Compression system according to claim 6, is characterized in that: when described low pressureWhen cylinder comprises the first cylinder and the second cylinder, described pipeline structure comprises the air entry with described the first cylinder(101) the first pipeline (2) being connected, and comprise and the air entry (102) of described the second cylinderThe second pipeline (3) being connected.
8. variable capacity Two-stage Compression system according to claim 7, is characterized in that: described magnetic valveStructure comprises the first magnetic valve (4) being arranged on described the first pipeline (2) and is arranged at described the second pipeThe second magnetic valve (5) on road (3).
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105466060A (en) * | 2015-12-28 | 2016-04-06 | 珠海格力电器股份有限公司 | Variable-volume two-stage compression system and control method thereof |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105466060A (en) * | 2015-12-28 | 2016-04-06 | 珠海格力电器股份有限公司 | Variable-volume two-stage compression system and control method thereof |
| WO2017113938A1 (en) * | 2015-12-28 | 2017-07-06 | 珠海格力电器股份有限公司 | Positive-displacement compressor, two-stage compressor system, and control method thereof |
| US10247449B2 (en) | 2015-12-28 | 2019-04-02 | Gree Electric Appliances, Inc. Of Zhuhai | Variable-capacity compressor, two-stage compression system and control method thereof |
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