CN1324280C - Refrigeration circulation and control method thereof - Google Patents
Refrigeration circulation and control method thereof Download PDFInfo
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- CN1324280C CN1324280C CNB021531498A CN02153149A CN1324280C CN 1324280 C CN1324280 C CN 1324280C CN B021531498 A CNB021531498 A CN B021531498A CN 02153149 A CN02153149 A CN 02153149A CN 1324280 C CN1324280 C CN 1324280C
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Abstract
The present invention relates to freezing circulation and a controlling method thereof. The freezing circulation of the present invention comprises a compressor, a condenser, an expanding and decompressing device, an evaporator and a flow dividing device, wherein the compressor compresses coolant into high temperature and high pressure gas coolant, and the condenser condenses the gas coolant exhausted from the compressor into a middle temperature and high pressure liquid coolant. The expanding and decompressing device decompresses the liquid coolant passing through the condenser into low temperature and low pressure liquid coolant, and the evaporator evaporates the liquid coolant passing through the expanding and decompressing device into low temperature and low pressure gas coolant. When the pressure at the high pressure side rises overly, the coolant at the high pressure side flows to the low pressure side. The controlling method of the freezing circulation comprises a pressure sensing stage that the piping pressure of coolant at the outlet side of the compressor is sensed, the stage that a controlling signal is generated when the sensed pressure is more than a set value, and the stage that flow is divided according to the signal, so the too high pressure at the high pressure side can be prevented. The compressor is protected to enhance freezing efficiency.
Description
Technical field
The present invention relates to a kind of freezing cycle device.
Background technology
General freeze cycle is, working fluid moves to the heat of low-temp. portion during by compressor, condenser, expansion valve and evaporimeter high-temperature portion and carries out refrigeration or heat; Described freeze cycle is applicable to air conditioner, refrigerator etc.
As shown in Figure 1, the freeze cycle of prior art includes following structure: compressor 2, condenser 4, expansion valve 6 and evaporimeter 8.
As shown in Figure 2, when the air conditioner that is made of described freeze cycle carried out work with refrigeration mode, the temperature of outside was high more, makes the discharge pressure of compressor 2 and temperature high more.
For example, under standard conditions (35/24 ℃), the discharge temperature of compressor 2 and pressure are respectively 80 ℃ and 20kgf/cm^2; Under overload condition (54/24 ℃), the discharge temperature of compressor 2 and pressure are respectively 108 ℃ and 30kgf/cm^2; When the outside temperature was high especially, the discharge temperature of compressor 2 and pressure can be higher.
That is to say, when if freeze cycle is carried out under overload condition, because refrigerant can not carry out heat exchange with outdoor air during by condenser 4 fully, through condenser 4, expansion valve 6 and evaporimeter 8 backs to the refrigerant of described compressor 2 side inflows than the relative higher temperature and pressure of standard conditions, the refrigerant that flows into has broken away from temperature and the pressure limit that ensures compressor 2 reliabilities when compressing in compressor 2, brought influence for the reliability of compressor 2.
So, in the prior art in order to ensure the reliability of compressor 2, the high reciprocating movement compressor of pressure property in using perhaps is provided with pressure-regulating valve door (INTERNAL PRESSURE RELIEF VALVE) between the high-voltage section of compressor 2 inside and low voltage section.
Below, simple declaration is carried out in the work that is arranged on the pressure-regulating valve door 10 on the reciprocating movement compressor.As shown in Figure 2, in being formed on the inner discharge chambe C of cylinder block 14 (CYLINDER BLOCK), suck refrigerant by suction line 3, make eccentric shaft carry out the off-centre rotation, make the connecting rod (CONNECTING ROD) 16 that converts eccentric revolving force to the straight line back and forth movement carry out rectilinear motion, make the piston (PISTON) 18 that links with connecting rod 16 that refrigerant in the discharge chambe C is compressed into HTHP, the refrigerant that is compressed into HTHP is discharged to the outside of compressor 2 by discharge pipe 9.
At this moment, if flow into the temperature of refrigerant of compressor 2 sides and the reliable operation condition that pressure has broken away from compressor 2, make the anti-locking mechanism of excess load carry out work, before the circulation of freeze cycle temporarily stops, make pressure-regulating valve door 10 carry out work and discharge gas coolant, temporarily reduce on the compressor 2 producing excess load from high side to low side.
But there is following shortcoming in the freeze cycle with prior art of described structure.
That is to say, in the temperature of outdoor air when higher, though utilize the pressure-regulating valve door that is arranged on the compressor can make freeze cycle carry out work, can temporarily prevent the excess load that produces on the compressor, but, because the pressure-regulating valve door from the gas coolant of high-voltage section to low voltage section discharge HTHP, rises the pressure and temperature of low voltage section, cause the pressure and the temperature of the refrigerant of circulating frozen circulation to rise totally, so certainly lead to the problem that reduces refrigerating efficiency.
Summary of the invention
In order to overcome the described shortcoming that prior art exists, the invention provides a kind of freezing cycle device, when the temperature of outdoor air is high, the refrigerant of freeze cycle is circulated by the shunting approach, thereby the excessive pressure that prevents refrigerant rises, not only can improve the reliability of compressor, but also can improve refrigerating efficiency.
The technical solution adopted for the present invention to solve the technical problems is:
A kind of freezing cycle device is characterized in that, it comprises compressor, condenser, the 1st decompressor, evaporimeter, the 2nd decompressor, valve and pressure switch; Described compressor is compressed into refrigerant the gas coolant of HTHP; Described condenser will carry out heat exchange from gas coolant and the outdoor air that compressor is discharged, the liquid coolant of warm high pressure in being condensed into; Described the 1st decompressor will reduce pressure into the liquid coolant of low-temp low-pressure by the liquid coolant behind the condenser; Described evaporimeter will carry out heat exchange by liquid coolant behind described the 1st decompressor and room air, flash to the gas coolant of low-temp low-pressure; Described the 2nd decompressor is communicated with the outlet side of compressor and the entrance side of evaporimeter; Described valve is arranged on described the 2nd decompressor, is used to open and close described the 2nd decompressor, and on high-tension side refrigerant is flowed to low-pressure side; Described pressure switch is arranged on the outlet side of compressor, according to sensed pressure from the outlet coolant piping of compressor, opens and closes described valve.
The present invention solves its technical problem also can adopt following technical scheme:
A kind of freezing cycle device is characterized in that, it comprises compressor, condenser, the 1st decompressor, evaporimeter, the 2nd decompressor, valve and pressure switch; Described compressor is compressed into refrigerant the gas coolant of HTHP; Described condenser will carry out heat exchange, the liquid coolant of warm high pressure in being condensed into from gas coolant and the outdoor air that described compressor is discharged; Described the 1st decompressor is divided into, the bottom, and the flow resistance ratio according to setting makes the liquid coolant that reduces pressure into low-temp low-pressure by the liquid coolant behind the described condenser successively; Described evaporimeter will carry out heat exchange by liquid coolant behind described the 1st decompressor and room air, flash to the gas coolant of low-temp low-pressure; Described the 2nd decompressor is communicated with the outlet side of described compressor and the entrance side of the 1st decompressor bottom; Described valve is arranged on described the 2nd decompressor, is used to open and close described the 2nd decompressor, and on high-tension side refrigerant is flowed to low-pressure side; Described pressure switch is arranged on the outlet side of described compressor, according to sensed pressure from the outlet coolant piping of compressor, opens and closes described valve.
The present invention solves its technical problem still can adopt following technical scheme:
A kind of freezing cycle device is characterized in that, it comprises compressor, condenser, the 1st decompressor, evaporimeter, the 2nd decompressor, valve and pressure switch; Described compressor is compressed into refrigerant the gas coolant of HTHP; Described condenser will carry out heat exchange, the liquid coolant of warm high pressure in being condensed into from gas coolant and the outdoor air that described compressor is discharged; Described the 1st decompressor will reduce pressure into the liquid coolant of low-temp low-pressure by the liquid coolant behind the described condenser; Described evaporimeter will carry out heat exchange by liquid coolant behind described the 1st decompressor and room air, flash to the gas coolant of low-temp low-pressure; Described the 2nd decompressor links the outlet side of described condenser and the entrance side of compressor; Described valve is arranged on described the 2nd decompressor, is used to open and close described the 2nd decompressor, and on high-tension side refrigerant is flowed to low-pressure side; Described pressure switch is arranged on the outlet side of compressor, according to sensed pressure from the outlet coolant piping of compressor, opens and closes described valve.
Aforesaid freezing cycle device, wherein valve is a magnetic valve, according to the pressure signal of pressure switch, the cold medium flux that flows by described the 2nd decompressor is regulated in the switching of described the 2nd decompressor of described valve regulated.
Freezing cycle device provided by the invention can bring following effect:
In freezing cycle device of the present invention, when freeze cycle is carried out work with refrigeration mode, under the high situation of the temperature of outdoor air, because the refrigerant of freeze cycle is circulated by the shunting approach, so can prevent the excessive pressure of refrigerant rises, not only can improve the reliability of compressor, but also can improve refrigerating efficiency.
Description of drawings
The present invention is further described below in conjunction with drawings and Examples.
Fig. 1 is the structure chart of the freeze cycle of prior art.
Fig. 2 is the sectional drawing that prior art includes the reciprocating movement compressor of pressure-regulating valve door.
Fig. 3 be in the freeze cycle of prior art according to outside the pressure of discharge coolant piping of gas condition compressor and the coordinate diagram (GRAPH) of temperature.
Fig. 4 is the structure chart of the 1st embodiment freezing cycle device of the present invention.
Fig. 5 is the structure chart of the 2nd embodiment freezing cycle device of the present invention.
Fig. 6 is the structure chart of the 3rd embodiment freezing cycle device of the present invention.
Fig. 7 is the suction pressure of compressor when being useful in the shunting of freezing cycle device of the present invention and the coordinate diagram of temperature and discharge pressure and temperature.
Fig. 8 is the programme diagram of the control method of freeze cycle of the present invention.
The number in the figure explanation:
52: compressor 54: condenser
62,72, decompressor 64,74 in 82: the 1, and 84: valve (VALVE)
66,76,86: pressure switch (SWITCH)
The specific embodiment
Down to shown in Figure 6, in freezing cycle device of the present invention, refrigerant is compressed into the refrigerant of HTHP at compressor 52 as Fig. 4; The gas coolant of the HTHP of discharging from compressor 52 carries out being condensed after the heat exchange with outdoor air by indoor pressure fan (not having in the drawing to point out) forced air supply during by condenser 54; By the liquid coolant of the middle temperature high pressure behind the condenser 54, undergoing phase transition when being depressurized during through the 1st decompressor 56; By the liquid coolant of the low-temp low-pressure behind described the 1st decompressor 56, carry out heat exchange with room air when the evaporimeter 58 by indoor pressure fan (not having in the drawing to point out) forced air supply after, flow into again in the compressor 52; Keep circulating frozen refrigerant the pressure higher pressure part (below be called the high-pressure side) and keep between the comparison low-pressure section (below be called low-pressure side) and be provided with part flow arrangement, when on high-tension side excessive pressure rises, make the part of high-pressure side refrigerant flow to low-pressure side.
As shown in Figure 4, the part flow arrangement of the 1st embodiment of the present invention includes following structure: the 2nd decompressor 62, valve 64 and pressure switch 66.Described the 2nd decompressor 62 links the outlet side of compressor 52 and the entrance side of evaporimeter 58; Valve 64 is arranged on the 2nd decompressor 62, is used to open and close the 2nd decompressor 62, makes on high-tension side refrigerant flow to low-pressure side; Pressure switch 66 is arranged on the outlet side of compressor 52, and according to sensed pressure on the outlet coolant piping of compressor 52, pressure switch 66 opens and closes valve 64.
Described valve 64 is magnetic valve (SOLENOID VALVE); Pressure switch 66 sensed pressure are when setting value P0 is above, and valve 64 obtains signal from pressure switch 66, regulates the switching of the 2nd decompressor 62, regulate the cold medium flux that flows by the 2nd decompressor 62.
So refrigerant is kept refrigerant the compressor 52 of comparison high-pressure state in freeze cycle outlet side flows into to the entrance side of the evaporimeter 58 of keeping the low-pressure state, can reduce on high-tension side pressure widely.
In above-mentioned the 1st embodiment, if the outlet side pressure of compressor 52 reaches setting value P0 when above, the part of refrigerant flows along the shunting approach to compressor 52 side inflows after passing through compressor the 52, the 2nd decompressor 62 and evaporimeter 58 again.
As shown in Figure 5, in the 2nd embodiment of the present invention, expansion valve 56 will be divided into top 56a and bottom 56b according to the 1st decompressor of setting respectively 56 that the flow resistance ratio of the liquid coolant of warm high pressure reduces pressure from condenser 54 inflows.The part flow arrangement of the 2nd embodiment includes following structure: the 2nd decompressor 72, valve 74 and pressure switch 76.
Described the 2nd decompressor 72 links the outlet side of compressor 52 and the entrance side of the 1st decompressor bottom 56b; Valve 74 is arranged on the 2nd decompressor 72, is used to open and close the 2nd decompressor 72, makes on high-tension side refrigerant flow to low-pressure side; Pressure switch 76 is arranged on the outlet side of compressor 52, and according to sensed pressure from the outlet coolant piping of compressor 52, pressure switch 76 opens and closes valve 74.
Described valve 74 is magnetic valve (SOLENOID VALVE) equally; Pressure switch 76 sensed pressure are when setting value P0 is above, and valve 74 obtains signal from pressure switch 76, regulates the switching of the 2nd decompressor 72, regulate the cold medium flux that flows by the 2nd decompressor 72.
Particularly, if the flow resistance of the 1st decompressor top 56a is compared the flow resistance hour of the 1st decompressor bottom 56b, the refrigerant of compressor 52 outlets is flowed into to the inlet of the 1st decompressor bottom 56b, though can not reduce on high-tension side pressure widely, but because the pressure that flows into to evaporimeter 58 is low, so can reduce the temperature of carrying out the room air of heat exchange with evaporimeter 58 widely.
On the contrary, if the flow resistance of described the 1st decompressor top 56a is compared the flow resistance of the 1st decompressor bottom 56b when big, the refrigerant of compressor 52 outlets is flowed into to the inlet of the 1st decompressor bottom 56b, though can reduce on high-tension side pressure widely, but owing to the pressure height that flows into to evaporimeter 58, so can not reduce the temperature of carrying out the room air of heat exchange with evaporimeter 58 widely.
In above-mentioned the 2nd embodiment, if the outlet side pressure of compressor 52 reaches setting value P0 when above, refrigerant flows along the shunting approach to compressor 52 side inflows after passing through compressor the 52, the 2nd decompressor the 72, the 1st decompressor bottom 56b and evaporimeter 58 again.
As shown in Figure 6, the part flow arrangement of the 3rd embodiment of the present invention includes following structure: the 2nd decompressor 82, valve 84 and pressure switch 86.Described the 2nd decompressor 82 links the outlet side of condenser 54 and the entrance side of compressor 52; Valve 84 is arranged on the 2nd decompressor 82, is used to open and close the 2nd decompressor 82, makes on high-tension side refrigerant flow to low-pressure side; Pressure switch 86 is arranged on the outlet side of compressor 52, and according to sensed pressure from the outlet coolant piping of compressor 52, pressure switch 86 opens and closes valve 84.
Described valve 84 is magnetic valve (SOLENOID VALVE) equally; Pressure switch 86 sensed pressure are when setting value P0 is above, and valve 84 obtains signal from pressure switch 86, regulates the switching of the 2nd decompressor 82, regulate the cold medium flux that flows by the 2nd decompressor 82.
So, in the 3rd embodiment, though can not reduce on high-tension side pressure widely, but because refrigerant is flow in the compressor 52 without evaporimeter 58, the evaporation of the refrigerant by part shunting can prevent the overheated of compressor 52, so can guarantee the reliably working of compressor 52.
In above-mentioned the 3rd embodiment, if the outlet side pressure of compressor 52 reaches setting value P0 when above, refrigerant flows along the shunting approach to compressor 52 side inflows after passing through compressor 52, condenser 54 and the 2nd decompressor 82 again.
Described the 1st decompressor 56 and the 2nd decompressor 62,72,82 can be formed by various ways such as expansion valve and the 2nd decompressors.
Below, the work of freeze cycle of the present invention with described structure is elaborated.
When carrying out work under the temperature overload condition (more than the condition of work of the freeze cycle of setting) of outdoor air, because refrigerant can not carry out heat exchange fully at condenser 54, the circulating frozen circulation time is to the refrigerant of compressor 52 side inflows comparison high-temperature high-pressure state, and the refrigerant that flow into compressor 52 sides is compressed the back and discharges.
If by 66,76,86 sensed pressure of the pressure switch on the outlet side that is arranged on compressor 52 at setting value P0 when above, pressure switch 66,76,86 to being arranged on the 2nd decompressor 62, valve 64,74 on 72,82,84 output signals are according to valve 64,74,84 switching degree, adjusting is flowing in the cold medium flux of the 2nd decompressor 62,72,82.
So the shunting approach of refrigerant from high side to low side along each embodiment circulates.
As shown in Figure 7,, the suction pressure of compressor 52 and temperature are risen, can make compressor 52 discharge pressures and temperature be reduced to pressure and the temperature that to guarantee the compressor operate as normal if be suitable for the shunting of freeze cycle.
So, if pressure switch 66,76, the pressure P of compressor 52 outlet sides of 86 perception are reduced to setting value P0 when following, can close from pressure switch 66,76,86 obtain the valve 64,74 of signal, 84, blocking shunting approach carries out normal freeze cycle work, makes refrigerant recycle compressor 52, condenser the 54, the 1st decompressor 56 and evaporimeter 58.
Below with reference to Fig. 8, the control method of freeze cycle of the present invention with said structure is elaborated.
As shown in Figure 8, at first,, apply power supply, keep the OFF state of closing of regulating the valve 64,74,84 that opens and closes the 2nd decompressor 62,72,82 to compressor 52 in the 1st stage.(with reference to S1, S2)
In addition, in the 2nd stage, in pressure switch 66,76, the discharge lateral pressure P of 86 perception compressors 52.(with reference to S3)
In the 3rd stage, if sensed pressure P was than the pressure P that has configured 0 hour in the 2nd stage, then again in pressure switch 66,76, the discharge lateral pressure of 86 perception compressors 52; If when sensed pressure P was bigger than the pressure P that configured 0 in the 2nd stage, then in pressure switch 66,76,86 produced control signals.(with reference to S4, S5)
In described the 4th stage, by the control signal that in described the 3rd stage, produces with valve 64,74,84 convert open (ON) state to, by described the 2nd decompressor 62,72,82, refrigerant is flowed along the shunting approach, the high-pressure side refrigerant is moved to low-pressure side.(with reference to S6)
In the 5th stage, again will be in pressure switch 66,76,86) sensed pressure P compares with the pressure P 0 that has configured, if sensed pressure P than the pressure P 0 that has configured greatly the time, then keeps valve 64,74,84 open states are (with reference to S7, S8)
But if sensed pressure P was than the pressure P that has configured 0 hour in the 5th stage, then with valve 64,74,84 convert closed condition to, interdict the 2nd decompressor 62,72,82, and refrigerant is circulated along the approach of general freeze cycle.(with reference to S9)
Claims (4)
1, a kind of freezing cycle device is characterized in that, it comprises compressor, condenser, the 1st decompressor, evaporimeter, the 2nd decompressor, valve and pressure switch;
Described compressor is compressed into refrigerant the gas coolant of HTHP;
Described condenser will carry out heat exchange from gas coolant and the outdoor air that compressor is discharged, the liquid coolant of warm high pressure in being condensed into;
Described the 1st decompressor will reduce pressure into the liquid coolant of low-temp low-pressure by the liquid coolant behind the condenser;
Described evaporimeter will carry out heat exchange by liquid coolant behind described the 1st decompressor and room air, flash to the gas coolant of low-temp low-pressure;
Described the 2nd decompressor is communicated with the outlet side of compressor and the entrance side of evaporimeter;
Described valve is arranged on described the 2nd decompressor, is used to open and close described the 2nd decompressor, and on high-tension side refrigerant is flowed to low-pressure side;
Described pressure switch is arranged on the outlet side of compressor, according to sensed pressure from the outlet coolant piping of compressor, opens and closes described valve.
2, a kind of freezing cycle device is characterized in that, it comprises compressor, condenser, the 1st decompressor, evaporimeter, the 2nd decompressor, valve and pressure switch;
Described compressor is compressed into refrigerant the gas coolant of HTHP;
Described condenser will carry out heat exchange, the liquid coolant of warm high pressure in being condensed into from gas coolant and the outdoor air that described compressor is discharged;
Described the 1st decompressor is divided into, the bottom, and the flow resistance ratio according to setting makes the liquid coolant that reduces pressure into low-temp low-pressure by the liquid coolant behind the described condenser successively;
Described evaporimeter will carry out heat exchange by liquid coolant behind described the 1st decompressor and room air, flash to the gas coolant of low-temp low-pressure;
Described the 2nd decompressor is communicated with the outlet side of described compressor and the entrance side of the 1st decompressor bottom;
Described valve is arranged on described the 2nd decompressor, is used to open and close described the 2nd decompressor, and on high-tension side refrigerant is flowed to low-pressure side;
Described pressure switch is arranged on the outlet side of described compressor, according to sensed pressure from the outlet coolant piping of compressor, opens and closes described valve.
3, a kind of freezing cycle device is characterized in that, it comprises compressor, condenser, the 1st decompressor, evaporimeter, the 2nd decompressor, valve and pressure switch;
Described compressor is compressed into refrigerant the gas coolant of HTHP;
Described condenser will carry out heat exchange, the liquid coolant of warm high pressure in being condensed into from gas coolant and the outdoor air that described compressor is discharged;
Described the 1st decompressor will reduce pressure into the liquid coolant of low-temp low-pressure by the liquid coolant behind the described condenser;
Described evaporimeter will carry out heat exchange by liquid coolant behind described the 1st decompressor and room air, flash to the gas coolant of low-temp low-pressure;
Described the 2nd decompressor links the outlet side of described condenser and the entrance side of compressor;
Described valve is arranged on described the 2nd decompressor, is used to open and close described the 2nd decompressor, and on high-tension side refrigerant is flowed to low-pressure side;
Described pressure switch is arranged on the outlet side of compressor, according to sensed pressure from the outlet coolant piping of compressor, opens and closes described valve.
4, according to claim 1 or 3 described freezing cycle devices, it is characterized in that described valve is a magnetic valve, according to the pressure signal of pressure switch, the cold medium flux that flows by described the 2nd decompressor is regulated in the switching of described the 2nd decompressor of described valve regulated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB021531498A CN1324280C (en) | 2002-11-26 | 2002-11-26 | Refrigeration circulation and control method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB021531498A CN1324280C (en) | 2002-11-26 | 2002-11-26 | Refrigeration circulation and control method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1502957A CN1502957A (en) | 2004-06-09 |
| CN1324280C true CN1324280C (en) | 2007-07-04 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB021531498A Expired - Fee Related CN1324280C (en) | 2002-11-26 | 2002-11-26 | Refrigeration circulation and control method thereof |
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| Country | Link |
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| CN (1) | CN1324280C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102215662A (en) * | 2011-05-09 | 2011-10-12 | 海尔集团公司 | Cooling device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04332356A (en) * | 1991-02-05 | 1992-11-19 | Daikin Ind Ltd | Air conditioner |
| CN1353291A (en) * | 2000-11-03 | 2002-06-12 | Lg电子株式会社 | Coolant distributor of heat pump refrigeration circulation |
-
2002
- 2002-11-26 CN CNB021531498A patent/CN1324280C/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04332356A (en) * | 1991-02-05 | 1992-11-19 | Daikin Ind Ltd | Air conditioner |
| CN1353291A (en) * | 2000-11-03 | 2002-06-12 | Lg电子株式会社 | Coolant distributor of heat pump refrigeration circulation |
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| Publication number | Publication date |
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| CN1502957A (en) | 2004-06-09 |
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Granted publication date: 20070704 |