CN1502957A - Refrigeration circulation and control method thereof - Google Patents
Refrigeration circulation and control method thereof Download PDFInfo
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- CN1502957A CN1502957A CNA021531498A CN02153149A CN1502957A CN 1502957 A CN1502957 A CN 1502957A CN A021531498 A CNA021531498 A CN A021531498A CN 02153149 A CN02153149 A CN 02153149A CN 1502957 A CN1502957 A CN 1502957A
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Abstract
The present invention relates to a freezing-circulation process and its control method. Said invention includes comprssor, condenser, expansion decompression device, evaporator and splitter device. The compressor can compress the cooling medium into high-temp. high-pressure gas cooling medium, the condenser can condense the above-mentioned gas cooling medium into medium-temp. high-pressure liquid cooling medium, and the expansion decompressino device can decompress the above-mentioned liquid cooling medium into low-temp. low-pressure liquid cooling medium, the evaporator can evaporate the liquid cooling medium into low-temp. low-pressure gas cooling medium, and the splitter device can be used for making high-pressure side cooling medium flow toward low-pressure side when high-pressure side pressure is excessively raised.
Description
Technical field
The present invention relates to freeze cycle, also relate in particular to control method.
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).
Compressor (2) is used for compression refrigerant; HTHP Compressed Gas refrigerant and outdoor air that condenser (4) will form in compressor (2) carry out heat exchange condensed gas refrigerant; Expansion valve (6) is used for the liquid coolant of the warm high pressure compressed of condenser (4) is reduced pressure; Evaporimeter (8) will be by expansion valve (6) the refrigerant and the room air of low-temp low-pressure carry out heat exchange; During refrigeration, refrigerant is circulated in compressor (2), condenser (4), expansion valve (6) and evaporimeter (8) room air is cooled off, and when heating, refrigerant circulates with reverse order room air is warmed.
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 20f/c; Under overload condition (54/24 ℃), the discharge temperature of compressor (2) and pressure are respectively 108 ℃ and 30f/c; When the outside temperature was high especially, the discharge temperature and the pressure of compressor (2) 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) afterwards to the refrigerant of described compressor (2) side inflow than the relative higher temperature and pressure of standard conditions, the refrigerant that flows into has broken away from the temperature and the pressure limit of guarantee compressor (2) reliability 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 inner high-voltage section of compressor (2) 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, by suction line (3) to being formed on (CYLINDERBLOCK) suction refrigerant in the inner discharge chambe (C) of cylinder block (4), make eccentric shaft carry out the off-centre rotation, make the connecting rod (CONNECTING ROD) (6) that converts eccentric revolving force to the straight line back and forth movement carry out rectilinear motion, make the piston (PISTON) (8) that links with connecting rod (6) that the interior refrigerant of 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) side 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 compressor (2) and go up the generation excess load from high side to low side.
But the freeze cycle with prior art of described structure has following shortcoming.
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 freeze cycle with and control method, 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:
Refrigerating circulation system of the present invention comprises compressor, condenser, expansion valve, evaporimeter and part flow arrangement.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 expansion valve 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 the described expansion valve and room air, flash to the gas coolant of low-temp low-pressure; Described part flow arrangement when on high-tension side excessive pressure rises, makes the part of high-pressure side refrigerant flow to low-pressure side.
The invention provides that to include as the next stage be the control method of the freeze cycle of feature: when freeze cycle is carried out work, the pressure perception stage of the outlet side coolant piping pressure of the described compressor of perception; If sensed pressure is when setting value is above in described pressure perception stage, then produce the signal generation stage of control signal according to described situation; By the signal that in the described signal generation stage, produces, the open shunting stage that links the shunting approach of high-pressure side and low-pressure side.
The effect of invention
Freeze cycle provided by the invention with and control method can bring following effect.
Freeze cycle of the present invention with and control method in, 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 freeze cycle of the present invention.
Fig. 5 is the structure chart of the 2nd embodiment freeze cycle of the present invention.
Fig. 6 is the structure chart of the 3rd embodiment freeze cycle of the present invention.
Fig. 7 is the suction pressure of compressor when being useful in the shunting of freeze cycle 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 freeze cycle 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 through evaporimeter when (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 is when setting value (P0) is above, and valve (64) obtains signal from pressure switch (66), regulates the switching of the 2nd decompressor (62), regulates 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 of keeping the low-pressure state (58), 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 inflow again by behind compressor (52), the 2nd decompressor (62) and the evaporimeter (58).
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) inflow.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 is when setting value (P0) is above, and valve (74) obtains signal from pressure switch (76), regulates the switching of the 2nd decompressor (72), regulates the cold medium flux that flows by the 2nd decompressor (72).
Particularly, if the flow resistance on the 1st decompressor top (56A) is compared the flow resistance hour of the 1st decompressor bottom (56B), the inlet of refrigerant to the 1st decompressor bottom (56B) of compressor (52) outlet flowed into, 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 on described the 1st decompressor top (56A) is compared the flow resistance of the 1st decompressor bottom (56B) when big, the inlet of refrigerant to the 1st decompressor bottom (56B) of compressor (52) outlet flowed into, 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 inflow after passing through compressor (52), the 2nd decompressor (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 is when setting value (P0) is above, and valve (84) obtains signal from pressure switch (86), regulates the switching of the 2nd decompressor (82), regulates 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 inflow again by behind compressor (52), condenser (54) and the 2nd decompressor (82).
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 inflow comparison high-temperature high-pressure state, and the refrigerant that flow into compressor (52) side is compressed the back and discharges.
If by the pressure switch on the outlet side that is arranged on compressor (52) (66,76,86) sensed pressure in setting value (P0) when above, pressure switch (66,76,86) is to being arranged on the 2nd decompressor (62,72,82) valve (64,74 on, 84) output signal is 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 pressure 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 the pressure (P) of compressor (52) outlet side of pressure switch (66,76,86) perception is 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 (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 (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 the discharge lateral pressure (P) of pressure switch (66,76,86) perception compressors (52).(with reference to S3)
In the 3rd stage, if sensed pressure (P) is than the pressure that has configured (P0) hour in the 2nd stage, then again in the discharge lateral pressure of pressure switch (66,76,86) perception compressors (52); If when sensed pressure in the 2nd stage (P) is bigger than the pressure that has configured (P0), then produce control signal in pressure switch (66,76,86).(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 (P0) that configured, if when sensed pressure (P) is bigger than the pressure that has configured (P0), then keeps valve (64,74,84) open state is (with reference to S7, S8)
But, if sensed pressure (P) then converts valve (64,74,84) to closed condition than the pressure that has configured (P0) hour in the 5th stage, interdict the 2nd decompressor (62,72,82), refrigerant is circulated along the approach of general freeze cycle.(with reference to S9)
Claims (6)
1, a kind of freeze cycle 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 links 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 freeze cycle 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 links 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 freeze cycle 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 freeze cycle, it is characterized in that described valve is the pressure signal of magnetic valve according to 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.
5, a kind of control method of freeze cycle is characterized in that,
When freeze cycle is carried out work, the pressure perception stage of the outlet side coolant piping pressure of the described compressor of perception;
If sensed pressure is when setting value is above in described pressure perception stage, then produce the signal generation stage of control signal according to described situation;
By the signal that in the described signal generation stage, produces, the open shunting stage that links the shunting approach of high-pressure side and low-pressure side.
6, the control method of freeze cycle according to claim 5 is characterized in that, if sensed pressure is when setting value is following in described pressure perception stage, then interdicts the shunting blocking stage of described shunting approach.
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 true CN1502957A (en) | 2004-06-09 |
| CN1324280C 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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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102215662A (en) * | 2011-05-09 | 2011-10-12 | 海尔集团公司 | Cooling device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2765243B2 (en) * | 1991-02-05 | 1998-06-11 | ダイキン工業株式会社 | Air conditioner |
| CN1144989C (en) * | 2000-11-03 | 2004-04-07 | Lg电子株式会社 | Coolant distributor of heat pump refrigeration circulation |
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2002
- 2002-11-26 CN CNB021531498A patent/CN1324280C/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102215662A (en) * | 2011-05-09 | 2011-10-12 | 海尔集团公司 | Cooling device |
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| CN1324280C (en) | 2007-07-04 |
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Granted publication date: 20070704 |