CN102997527B - Gas-liquid heat exchange type refrigeration device - Google Patents
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- CN102997527B CN102997527B CN201110281313.5A CN201110281313A CN102997527B CN 102997527 B CN102997527 B CN 102997527B CN 201110281313 A CN201110281313 A CN 201110281313A CN 102997527 B CN102997527 B CN 102997527B
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- 239000007788 liquid Substances 0.000 title claims abstract description 115
- 238000005057 refrigeration Methods 0.000 title claims abstract description 20
- 239000003507 refrigerant Substances 0.000 claims abstract description 157
- 238000004804 winding Methods 0.000 claims abstract description 26
- 238000004781 supercooling Methods 0.000 claims description 12
- 239000000203 mixture Substances 0.000 claims description 8
- 230000005494 condensation Effects 0.000 claims description 6
- 238000009833 condensation Methods 0.000 claims description 6
- 230000006866 deterioration Effects 0.000 abstract description 8
- 230000000630 rising effect Effects 0.000 abstract description 6
- 238000000034 method Methods 0.000 description 21
- 230000008569 process Effects 0.000 description 18
- 230000008859 change Effects 0.000 description 14
- 238000001704 evaporation Methods 0.000 description 14
- 239000002826 coolant Substances 0.000 description 12
- 230000008020 evaporation Effects 0.000 description 11
- 238000010586 diagram Methods 0.000 description 8
- 238000001816 cooling Methods 0.000 description 4
- 230000006837 decompression Effects 0.000 description 4
- 238000009835 boiling Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000005514 two-phase flow Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 230000007115 recruitment Effects 0.000 description 1
- 238000004544 sputter deposition Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Abstract
A kind of gas-liquid heat exchange type refrigeration device, it can suppress the variation of the refrigerating capacity caused with the variation of the winding number of compressor, and suppresses the rising of the temperature that spues at compressor outlet place, and can prevent refrigerator oil from deterioration occurring.This gas-liquid heat exchange type refrigeration device is by refrigerant pipeline L1 ~ L5, by compressor 1, condenser 2, heat exchange control valve 3, gas-liquid heat exchanger 4, expansion valve 5 and evaporimeter 6, be connected in series, form closed circuit refrigerant circulation circuit and form, wherein: between the compressor 1 and condenser 2 of refrigerant circulation circuit, setting spues temperature sensor 7, and between heat exchange control valve 3 and gas-liquid heat exchanger 4, pressure sensor 8 is set, and be provided with controller (control device) 10, the refrigerant temperature of described controller 10 based on the exit of the compressor 1 detected by the temperature sensor 7 that spues and the refrigerant pressure in the exit of the heat exchange control valve 3 detected by pressure sensor 8, control the aperture of heat exchange control valve 3.
Description
Technical field
The present invention relates to a kind of gas-liquid heat exchange type refrigeration device, it, by refrigerant by condenser condenses and the refrigerant by evaporator evaporation, in gas-liquid heat exchanger, carries out heat exchange mutually, make the respectively supercooling and overheated of each refrigerant, improve refrigerating capacity thus.
Background technology
In general, refrigerating plant, by refrigerant pipeline, compressor, condenser, expansion valve and evaporator series are connected and form closed circuit refrigerant circulation circuit, the gaseous coolant of the high pressure by compressor compresses, heat release and liquefying within the condenser, become the liquid refrigerants of high pressure, by expansion valve make this liquid refrigerants expand (isenthalpic expansion) and decompression after, in evaporimeter, low-pressure liquid refrigerant evaporation after boiling point is declined, wait according to from freezer inside the evaporation latent heat captured required for evaporation, cool the places such as freezer inside.
As the raising refrigerating capacity of this kind of refrigerating plant or the method for coefficient of refrigerating performance (COP), there will be a known such method, described method arranges gas-liquid heat exchanger between the evaporimeter and expansion valve of refrigerant circulation circuit, and make the refrigerant after by condenser condenses with by the refrigerant after evaporator evaporation, in gas-liquid heat exchanger, carry out heat exchange mutually, and make the respectively supercooling and overheated of each refrigerant.
In addition, in patent document 1, for the refrigerating air-conditioning being equiped with gas-liquid heat exchanger, propose as lower device, described device is between the condenser and gas-liquid heat exchanger of refrigerant circulation circuit and between gas-liquid heat exchanger and evaporimeter, expansion valve is set respectively, and the aperture of expansion valve is controlled based on the refrigerant temperature of condensator outlet and the refrigerant temperature of suction port of compressor, the desired value being remained on regulation by the mass dryness fraction of the refrigerant by evaporator outlet place realizes high efficiency running, and eliminate and result from evaporimeter and become dry and the unfavorable condition of the condensed water sputtering that causes etc.
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2009-162388 publication
Invent problem to be solved
But, if under the environment that the winding number of the compressor as van cooler can change significantly, the situation of the refrigerating air-conditioning running that patent document 1 is proposed, then the heat exchange performance of gas-liquid heat exchanger also can change with the winding number variation of compressor significantly.Such as, if the winding number of compressor reduces, refrigerant circulation reduces, cause that because the heat exchange amount in gas-liquid heat exchanger is not enough cooling occurs bad, on the contrary, if the winding number increase of compressor, refrigerant circulation increases, the temperature that spues too much causing the refrigerant at compressor outlet place due to heat exchange amount rises, and the problem of refrigerator oil deterioration etc. occurs.
The present invention completes in view of the above problems, its object is to provide a kind of gas-liquid heat exchange type refrigeration device, it can suppress the variation of the refrigerating capacity caused with the variation of the winding number of compressor, and suppress the rising of the temperature that spues at compressor outlet place, and can prevent refrigerator oil from deterioration occurring.
Summary of the invention
The technological means of dealing with problems
To achieve these goals, the invention of technical scheme 1, it is a kind of gas-liquid heat exchange type refrigeration device, by refrigerant pipeline, to major general's compressor, condenser, heat exchange control valve, gas-liquid heat exchanger, expansion valve and evaporimeter, be connected in series, and form closed circuit refrigerant circulation circuit, by exchange the refrigerant that reduced pressure of control valve by aforementioned hot after condensation in aforementioned condenser and by forgoing evaporators in vaporized refrigerant, in aforementioned gas-liquid heat exchanger, carry out heat exchange and make the supercooling or overheated respectively of each refrigerant, it is characterized in that: between the aforementioned compressor and aforementioned condenser of aforementioned refrigerant circulation circuit, setting spues temperature sensor, and exchange between control valve and aforementioned gas-liquid heat exchanger in aforementioned hot, pressure sensor is set, and be provided with control device, the refrigerant pressure that described control device exports with the heat exchange control valve to be detected by aforementioned pressure sensor based on the refrigerant temperature of the compressor outlet detected by the aforementioned temperature sensor that spues, control the aperture that aforementioned hot exchanges control valve, and control exchange control valve through aforementioned hot and flow through the flow velocity of the refrigerant of aforementioned gas-liquid heat exchanger.
The invention of technical scheme 2, be based on the invention described in technical scheme 1, it is characterized in that: foregoing control device, if the winding number of aforementioned compressor reduces, reduce the aperture that aforementioned hot exchanges control valve, if the winding number of aforementioned compressor increases, then increase the aperture that aforementioned hot exchanges control valve.
The invention of technical scheme 3, based on the invention described in technical scheme 1, it is characterized in that: foregoing control device, if the refrigerant temperature of the compressor outlet detected by the aforementioned temperature sensor that spues exceedes setting value, till the aperture then aforementioned hot being exchanged control valve is contracted to and refrigerant can be made to maintain the value of gas-liquid mixture phase, described refrigerant is the refrigerant that have passed aforementioned gas-liquid heat exchanger after being reduced pressure by this heat exchange control valve.
The effect of invention
Invention according to technical scheme 1 and technical scheme 2, owing to reducing the aperture of heat exchange control valve when the rotation number of compressor reduces, so the flow velocity flowing through the refrigerant of gas-liquid heat exchanger rises, heat exchange amount increases, and according to the increase of this heat exchange amount, can compensate because winding number reduces the minimizing of the heat exchange amount in gas-liquid heat exchanger causing the minimizing of refrigerant circulation to cause, and the cooling that causes because of heat exchange amount deficiency can be suppressed bad.
In addition, owing to increasing the aperture of heat exchange control valve when the rotation number of compressor increases, so the flow velocity flowing through the refrigerant of gas-liquid heat exchanger declines, heat exchange amount reduces, and according to the minimizing of this heat exchange amount, can compensate because winding number increases the increase of the heat exchange amount in gas-liquid heat exchanger causing the increase of refrigerant circulation to cause, the rising of the temperature that spues of the refrigerant in the exit of the compressor too much caused because of heat exchange amount can be suppressed.
Invention according to technical scheme 3, due to when the refrigerant temperature of compressor outlet exceedes setting value, reduce the aperture of heat exchange control valve 3 significantly, till making maintaining the value of gas-liquid mixture phase by the refrigerant that have passed gas-liquid heat exchanger after the decompression of heat exchange control valve, therefore the heat exchange amount of two refrigerants in gas-liquid heat exchanger can be diminished by the temperature difference between the refrigerant of gas-liquid heat exchanger and the gaseous coolant carrying out flash-pot with the form of gas-liquid two-phase flow, so can be suppressed to lower.Therefore, the degree of superheat of the refrigerant at suction port of compressor place can be suppressed to lower, and can suppress the rising of the temperature that spues of the refrigerant at compressor outlet place, and can prevent the deterioration of refrigerator oil.
Accompanying drawing explanation
Fig. 1 is the refrigerant loop diagram of gas-liquid heat exchange type refrigeration device of the present invention.
Fig. 2 represents in gas-liquid heat exchange type refrigeration device of the present invention, the mollier diagram of the state change of the refrigerant when variation of corresponding compressor winding number controls the aperture of heat exchange control valve.
Fig. 3 represents the flow velocity of condensate liquid refrigerant in gas-liquid heat exchanger and the graph of a relation of heat transfer property.
Fig. 4 represents in gas-liquid heat exchange type refrigeration device of the present invention, when the temperature that spues of the refrigerant at compressor outlet place exceedes setting value, and the mollier diagram of the state change of refrigerant when controlling the aperture of heat exchange control valve.
Critical piece symbol description
1 compressor
2 condensers
3 heat exchange control valves
4 gas-liquid heat exchangers
5 expansion valves
6 evaporimeters
7 spue temperature sensor
8 pressure sensors
9 evaporating temperature sensor
10 controllers (control device)
L1 ~ L5 refrigerant pipeline
Detailed description of the invention
Below, with reference to accompanying drawing, embodiment of the present invention is described.
Fig. 1 is the refrigerant loop diagram of gas-liquid heat exchange type refrigeration device of the present invention, in illustrated gas-liquid heat exchange type refrigeration device, compressor 1, condenser 2, heat exchange control valve 3, gas-liquid heat exchanger 4, expansion valve 5 and evaporimeter 6, be connected in series by refrigerant pipeline L1, L2, L3, L4, L5, and formed closed circuit refrigerant circulation circuit.Herein, heat exchange control valve 3, is arranged on refrigerant pipeline L2, and described refrigerant pipeline L2 is in order to connect condenser 2 and gas-liquid heat exchanger 4; Expansion valve 5, is arranged on refrigerant pipeline L3, and described refrigerant pipeline L3 is in order to connect gas-liquid heat exchanger 4 and evaporimeter 6.In addition, heat exchange control valve 3, formed to the electronic control valve controlling aperture by stepless mode.
In addition, in gas-liquid heat exchange type refrigeration device of the present invention, the temperature sensor 7 that spues is arranged on to connect compressor 1 with on the refrigerant pipeline L1 of condenser 2, pressure sensor 8 is arranged on the refrigerant pipeline L2 between heat exchange control valve 3 and gas-liquid heat exchanger 4, evaporating temperature sensor 9 is arranged on to connect evaporimeter 6 with on the refrigerant pipeline L4 of gas-liquid heat exchanger 4, these temperature sensor 7 that spues, pressure sensor 8 and evaporating temperature sensor 9, be electrically connected on control device and controller 10.And then the heat exchange control valve 3 be made up of electronic control valve, is electrically connected to controller 10, as described later, heat exchange control valve 3 controls its aperture according to the control signal carrying out self-controller 10.
Then, the mollier diagram (P-i line chart) shown in Fig. 2 is used to come the Action Specification of gas-liquid heat exchange type refrigeration device of the present invention as follows.
If compressor 1 is driven by revolution according to drive source and not shown engine, be then positioned at the state (pressure P shown in a of Fig. 2
1, enthalpy i
1) gaseous coolant compressed by compressor 1, become the state (pressure P shown in the b of Fig. 2
2, enthalpy i
2) the gaseous coolant (compression travel) of HTHP, this gaseous coolant is imported in condenser 2 by refrigerant pipeline L1.In addition, the compression power W (being converted into heat) of compressor 1 is now with (i
2-i
1) represent.
In condenser 2, the gaseous coolant of HTHP, by condensation heat Q
2be discarded in air, be changing into the state (phase change) at c place and liquefy (condensation stroke) by the state of the b of Fig. 2, become the state (pressure P shown in the c of Fig. 2
2, enthalpy i
3) high-pressure liquid refrigerant.In addition, thermal discharge (condensation heat) Q now
2with (i
2-i
3) represent.
Then, as described above, the high-pressure liquid refrigerant liquefied in condenser 2, in fig. 2, such as, carries out state change through the path (condition) that represents with B.That is, the high-pressure liquid refrigerant liquefied in condenser 2, arrives heat exchange control valve 3 by refrigerant pipeline L2, by this heat exchange control valve 3, is depressurized to pressure P
3till carry out adiabatic expansion (isenthalpic expansion) (expansion stroke), become the state (pressure P shown in the d of Fig. 2
3, enthalpy i
3), the refrigerant of its part can gasify.
As described above, the refrigerant that a part has gasified, can be imported in gas-liquid heat exchanger 4 by refrigerant pipeline L2, in this gas-liquid heat exchanger 4, as described later, evaporation in the evaporimeter 6 and gaseous coolant that gasified is imported into through refrigerant pipeline L4, so from refrigerant pipeline L2 toward the refrigerant (refrigerant that a part has gasified) that gas-liquid heat exchanger 4 imports, can with to evaporate in evaporimeter 6 and the gaseous coolant of low temperature that imports from refrigerant pipeline L4 carries out heat exchange and by supercooling, become the state (pressure P shown in the e of Fig. 2
3, enthalpy i
4) liquid refrigerants.In addition, supercooling heat Δ Q now
2with (i
3-i
4) represent.
Then, as described above, by the refrigerant after supercooling in gas-liquid heat exchanger 4, carried out adiabatic expansion (isenthalpic expansion) (expansion stroke) according to again reducing pressure by expansion valve 5, state is changing into the state (pressure P shown in the f of Fig. 2
1, enthalpy i
4), so the refrigerant of its part can gasify, and reduce boiling point because of decompression.So, be depressurized by expansion valve 5 and boiling point reduce after refrigerant, be directed into evaporimeter 6 from refrigerant pipeline L3, in the process flowing through this evaporimeter 6, this refrigerant can capture heat of evaporation Q from surrounding
1and evaporate, be changing into the state (pressure P shown in g from the state shown in f
1, enthalpy i
5) and gasify (evaporation stroke).Heat of evaporation Q now
1with (i
5-i
4) represent, but as described above, be inflated the refrigerant before valve 5 decompression, in gas-liquid heat exchanger 4, only can by supercooling Δ Q
2(=i
3-i
4), so heat of evaporation only can increase the heat Δ Q of this supercooling amount
2so refrigerating capacity also only can improve its recruitment Δ Q
2.
Afterwards, vaporized low-pressure gaseous refrigerant in evaporimeter 6, as described above, flowing through in the process of gas-liquid heat exchanger 4 from refrigerant pipeline L4, be used for the high pressure refrigerant supercooling making to be fed to from refrigerant pipeline L2 gas-liquid heat exchanger 4, so the temperature of described low-pressure gaseous refrigerant rises, be inhaled into the stage in compressor 1, changing from the state shown in the g of Fig. 2 the state (pressure P become shown in a
1, enthalpy i
1), and only by the heat Δ Q shown in this figure overheated
1.Then, this overheated gaseous coolant, by compressor 1 second compression again, after, refrigerant carries out state change similar to the above repeatedly.
And, in gas-liquid heat exchange type refrigeration device of the present invention, freeze cycle described above is carried out repeatedly, absorbing heat according to the evaporation with low temperature liquid refrigerant in evaporimeter 6 carries out required freezing, the temperature of the gaseous coolant spued from compressor 1 is detected by the temperature sensor 7 that spues, detected by pressure sensor 8 by the pressure of the refrigerant reduced pressure by heat exchange control valve 3 after condenser 2 condensation, these detected values can be sent to controller 10.So controller 10, based on refrigerant temperature and the refrigerant pressure in the exit of the heat exchange control valve 3 detected by pressure sensor 8 in the exit of the compressor 1 detected by the temperature sensor 7 that spues, controls the aperture of heat exchange control valve 3.
Specifically, if the winding number of compressor 1 reduces, then reduce the aperture of heat exchange control valve 3, on the contrary, if the winding number of compressor 1 increases, then increase the aperture of heat exchange control valve 3.In addition, the refrigerant temperature in the exit of the compressor 1 detected by the temperature sensor 7 that spues, if exceed setting value, then aforementioned hot is exchanged the aperture of control valve 3, be contracted to till refrigerant can be made to maintain the value of gas-liquid mixture phase, described refrigerant is the refrigerant (with reference to Fig. 4) that have passed gas-liquid heat exchanger 4 after utilizing this heat exchange control valve 3 to reduce pressure.
When gas-liquid heat exchange type refrigeration device of the present invention being arranged on such as van cooler, the rotation number of the compressor 1 driven by engine, can change according to the travel condition of van cooler.
Such as, if the rotation number of compressor 1 reduces, the internal circulating load of the refrigerant in freeze cycle loop can reduce, therefore refrigerating capacity declines, in the case, as described above, because controller 10 reduces the aperture of heat exchange control valve 3, so the flow velocity flowing through the refrigerant of gas-liquid heat exchanger 4 rises, heat exchange amount increases, and according to the increase of this heat exchange amount, can compensate because winding number reduces the minimizing of the heat exchange amount in gas-liquid heat exchanger 4 causing the minimizing of refrigerant circulation to cause, the cooling that causes because of heat exchange amount deficiency can be suppressed bad.
Herein, the high-pressure liquid refrigerant liquefied in condenser 2, state change when flowing toward expansion valve 5 from heat exchange control valve 3 through gas-liquid heat exchanger 4, such as, represent with B, C, D process of Fig. 2.When operating with the state shown in B process, by heat exchange control valve 3, the pressure of described high-pressure liquid refrigerant is from P
2be depressurized into P
3if the winding number of compressor 1 reduces, then according to the reduction degree of this winding number, make the aperture of heat exchange control valve 3 reduce, as shown in C, D process of Fig. 2, by the pressure of described high-pressure liquid refrigerant to P
3', P
3" (P
3>P
3' >P
3"), as diagram, increase heat exchange amount, so the aforementioned cooling caused because heat exchange amount is not enough can be suppressed bad because the flow velocity flowing through the refrigerant of gas-liquid heat exchanger 4 improves.
Fig. 3 represents the flow velocity (m/s) of the refrigerant in gas-liquid heat exchanger 4 and the relation of heat transfer property KA (W/K), and scheme known thus, heat transfer property (heat exchange amount) KA can increase along with the increase of refrigerant flow rate.
Herein, A process in fig. 2, represent and do not use heat exchange control valve 3 and make refrigerant in gas-liquid heat exchanger 4 after supercooling, the process (condition) of situation about being expanded by expansion valve 5, the situation of state change is made as benchmark using making refrigerant through this process A, according to simulation obtain make refrigerant through each process B, C, D and do state change time refrigerant flow rate, heat exchange amount in gas-liquid heat exchanger 4 and performance boost rate, obtain the result shown in table 1.
[table 1]
As shown in Table 1, when the winding number of compressor 1 reduces, if reduce the aperture of heat exchange control valve 3, then the flow velocity of refrigerant increases, and heat-shift in gas-liquid heat exchanger 4 increases, result, performance boost and can improve refrigerating capacity.
On the contrary, if increase the winding number of compressor 1, refrigerant circulation increases, rise owing to too much causing the temperature that spues of the refrigerant in the exit at compressor 1 because of the heat-shift in gas-liquid heat exchanger 4, thus there is the problem of refrigerator oil deterioration etc., therefore, as described above, controller 10 controls in the mode making the aperture of heat exchange control valve 3 and increase.
Such as, when operating under with the state shown in the D process of Fig. 2, by heat exchange control valve 3, the pressure of described high-pressure liquid refrigerant is from P
2be depressurized into P
3", if the winding number of compressor 1 increases, then according to the increase degree of this winding number, the aperture of heat exchange control valve 3 is increased, as shown in C, B process of Fig. 2, by the pressure of described high-pressure liquid refrigerant to P
3', P
3(P
3" <P
3' <P
3) words, as diagram, heat exchange amount is reduced because the flow velocity flowing through the refrigerant in gas-liquid heat exchanger 4 reduces, so the temperature that spues of the refrigerant in the exit at compressor 1 that can suppress too much due to heat exchange amount and cause rises, thus the deterioration of refrigerator oil can be prevented.
As shown in Table 1, when the winding number of compressor 1 increases, if increase the aperture of heat exchange control valve 3, then the flow velocity of refrigerant reduces, and the heat-shift in gas-liquid heat exchanger 4 reduces, result, hydraulic performance decline and reduce refrigerating capacity.
And, in gas-liquid heat exchange type refrigeration device of the present invention, the refrigerant temperature in the exit of the compressor 1 detected by the temperature sensor 7 that spues, if exceed setting value, then as described above, controller 10, by the aperture of heat exchange control valve 3, is contracted to till refrigerant can be made to maintain the value of gas-liquid mixture phase, and described refrigerant is the refrigerant that have passed gas-liquid heat exchanger 4 after being reduced pressure by this heat exchange control valve 3.
Such as, the high-pressure liquid refrigerant liquefied in condenser 2, state change when flowing toward expansion valve 5 from heat exchange control valve 3 through gas-liquid heat exchanger 4, such as represent with B, C, D process of Fig. 4, if by the aperture reducing heat exchange control valve 3, by the high-pressure liquid refrigerant liquefied in condenser 2, from pressure P
2be decompressed to P significantly
3', P
3", then by have passed the refrigerant of gas-liquid heat exchanger 4 after being reduced pressure by heat exchange control valve 3, gas-liquid mixture phase can be maintained.That is, when operating with the state shown in B process, by heat exchange control valve 3 by the pressure of described high-pressure liquid refrigerant from P
2be decompressed to P
3if the winding number of compressor 1 reduces, then according to the reduction degree of this winding number, make the aperture of heat exchange control valve 3 reduce, as shown in C, D process of Fig. 2, by the pressure of described high-pressure liquid refrigerant to P
3', P
3" (P
3" <P
3' <P
3), have passed the refrigerant of gas-liquid heat exchanger 4 after being reduced pressure by heat exchange control valve 3, maintain gas-liquid mixture phase.
As described above, the refrigerant of gas-liquid heat exchanger 4 is have passed after being reduced pressure by heat exchange control valve 3, if maintain gas-liquid mixture phase, then with the form of gas-liquid two-phase flow by the refrigerant of gas-liquid heat exchanger 4 and via refrigerant pipeline L4, the temperature difference be imported between the gaseous coolant gas-liquid heat exchanger 4 diminishes from evaporimeter 6, the heat exchange amount of two refrigerants in gas-liquid heat exchanger 4 can be suppressed lower.Therefore, the degree of superheat of the refrigerant of the porch at compressor 1 can be suppressed lower, suppress the rising of the temperature that spues of the refrigerant in the exit at compressor 1, thus the deterioration of refrigerator oil can be prevented.
Herein, A process in the diagram, represent and do not use heat exchange control valve and make refrigerant in gas-liquid heat exchanger 4 after supercooling, the process of situation about being expanded by expansion valve 5, the situation of state change is made as benchmark using making refrigerant through this process A, according to simulation obtain make refrigerant through each process B, C, D and do state change time refrigerant flow rate, heat exchange amount in gas-liquid heat exchanger 4 and performance boost rate, and obtain the result shown in table 2.
[table 2]
As shown in Table 2, when the refrigerant temperature in the exit of the compressor 1 detected by the temperature sensor 7 that spues has exceeded setting value, if reduce the aperture of heat exchange control valve 3 significantly, the flow velocity of refrigerant can increase, on the other hand, now with the form of gas-liquid two-phase flow by the refrigerant of gas-liquid heat exchanger 4 and via refrigerant pipeline L4, the temperature difference be imported between the gaseous coolant gas-liquid heat exchanger 4 can diminish from evaporimeter 6, result, can suppress the heat exchange amount of two refrigerants in gas-liquid heat exchanger 4 lower, refrigerating capacity reduces.
Above, according to the present invention, following effect can be obtained.That is, not only can suppress the variation of the refrigerating capacity caused with the variation of the winding number of compressor 1, and the rising of the temperature that spues in the exit of compressor 1 can be suppressed, thus can prevent refrigerator oil from deterioration occurring.
Claims (3)
1. a gas-liquid heat exchange type refrigeration device, by refrigerant pipeline, to major general's compressor, condenser, heat exchange control valve, gas-liquid heat exchanger, expansion valve and evaporimeter, be connected in series, and form closed circuit refrigerant circulation circuit, by exchange the refrigerant that reduced pressure of control valve by aforementioned hot after condensation in aforementioned condenser and by forgoing evaporators in vaporized refrigerant, in aforementioned gas-liquid heat exchanger, carry out heat exchange and make the supercooling or overheated respectively of each refrigerant, it is characterized in that:
Between the aforementioned compressor and aforementioned condenser of aforementioned refrigerant circulation circuit, setting spues temperature sensor, and exchange between control valve and aforementioned gas-liquid heat exchanger in aforementioned hot, pressure sensor is set, and be provided with control device, the refrigerant pressure that described control device exports with the heat exchange control valve to be detected by aforementioned pressure sensor based on the refrigerant temperature of the compressor outlet detected by the aforementioned temperature sensor that spues, control the aperture that aforementioned hot exchanges control valve, and control exchange control valve through aforementioned hot and flow through the flow velocity of the refrigerant of aforementioned gas-liquid heat exchanger.
2. gas-liquid heat exchange type refrigeration device as claimed in claim 1, is characterized in that:
Foregoing control device, if the winding number of aforementioned compressor reduces, reduces the aperture that aforementioned hot exchanges control valve, if the winding number of aforementioned compressor increases, then increases the aperture that aforementioned hot exchanges control valve.
3. gas-liquid heat exchange type refrigeration device as claimed in claim 1, is characterized in that:
Foregoing control device, if the refrigerant temperature of the compressor outlet detected by the aforementioned temperature sensor that spues exceedes setting value, till the aperture then aforementioned hot being exchanged control valve is contracted to and refrigerant can be made to maintain the value of gas-liquid mixture phase, described refrigerant is the refrigerant that have passed aforementioned gas-liquid heat exchanger after being reduced pressure by this heat exchange control valve.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110281313.5A CN102997527B (en) | 2011-09-09 | 2011-09-09 | Gas-liquid heat exchange type refrigeration device |
| HK13106527.4A HK1178965A1 (en) | 2011-09-09 | 2013-06-04 | Gas-liquid heat exchanging-type refrigerating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110281313.5A CN102997527B (en) | 2011-09-09 | 2011-09-09 | Gas-liquid heat exchange type refrigeration device |
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| Publication Number | Publication Date |
|---|---|
| CN102997527A CN102997527A (en) | 2013-03-27 |
| CN102997527B true CN102997527B (en) | 2016-03-23 |
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|---|---|---|---|
| CN201110281313.5A Expired - Fee Related CN102997527B (en) | 2011-09-09 | 2011-09-09 | Gas-liquid heat exchange type refrigeration device |
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| HK (1) | HK1178965A1 (en) |
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| TWI709723B (en) * | 2014-02-03 | 2020-11-11 | 日商東普雷股份有限公司 | Refrigeration device and operation method of refrigeration device |
| CN106766482A (en) * | 2016-12-20 | 2017-05-31 | 中山阿瑞德电器设备有限公司 | A kind of reach in freezer |
| CN106766296A (en) * | 2016-12-20 | 2017-05-31 | 中山阿瑞德电器设备有限公司 | A kind of heat exchange cooling system |
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| JP2002130856A (en) * | 2000-10-23 | 2002-05-09 | Matsushita Seiko Co Ltd | Refrigerating cycle device and control method thereof |
| JP2002130849A (en) * | 2000-10-30 | 2002-05-09 | Calsonic Kansei Corp | Cooling cycle and its control method |
| JP2005351537A (en) * | 2004-06-10 | 2005-12-22 | Matsushita Electric Ind Co Ltd | Refrigerating cycle system and its control method |
| JP2007101069A (en) * | 2005-10-05 | 2007-04-19 | Mitsubishi Electric Corp | Air conditioner |
| CN200982764Y (en) * | 2006-12-09 | 2007-11-28 | 奇瑞汽车有限公司 | Automobile air conditioner |
| JP2009092258A (en) * | 2007-10-04 | 2009-04-30 | Panasonic Corp | Refrigerating cycle device |
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| HK1178965A1 (en) | 2013-09-19 |
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