HK1178965B - Gas-liquid heat exchanging-type refrigerating device - Google Patents
Gas-liquid heat exchanging-type refrigerating device Download PDFInfo
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- HK1178965B HK1178965B HK13106527.4A HK13106527A HK1178965B HK 1178965 B HK1178965 B HK 1178965B HK 13106527 A HK13106527 A HK 13106527A HK 1178965 B HK1178965 B HK 1178965B
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- refrigerant
- heat exchange
- gas
- compressor
- liquid
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Abstract
The present invention provides a gas-liquid heat exchanging-type refrigerating device, which can suppress the variation of freezing capacity caused by the variation of rotational frequency of the compressor and suppress the increasing temperature resulting from the exhaust of the outlet of the compressor, thereby preventing the refrigerating machine oil from degradation. The gas-liquid heat exchanging-type refrigerating device is consisting essentially of a compressor 1, a condenser 2, a heat exchange valve 3, a gas-liquid heat exchanger 4, an expansion valve 5, and an evaporator 6 connecting in series via refrigerant pipelines L1~L5 and form a closed-loop refrigerant circulation circuit, wherein, in the closed-loop refrigerant circulation circuit, a temperature sensor 7 is disposed between the compressor 1 and the condenser 2, a pressure sensor 8 is disposed between the heat exchange valve 3 and the gas-liquid heat exchanger 4, and a controller (control means) 10 is disposed to control the aperture of the heat exchange valve 3 according to the refrigerant temperature at the outlet of the compressor 1 detected by the temperature sensor 7 and the refrigerant pressure at the outlet of the heat exchange valve 3 detected by the pressure sensor 8.
Description
Technical Field
The present invention relates to a gas-liquid heat exchange type refrigerating apparatus in which a refrigerant condensed by a condenser and a refrigerant evaporated by an evaporator are heat-exchanged with each other in a gas-liquid heat exchanger to supercool and overheat the respective refrigerants, thereby improving refrigerating capacity.
Background
Generally, a refrigeration apparatus is a closed refrigerant circulation circuit formed by connecting a compressor, a condenser, an expansion valve, and an evaporator in series by refrigerant pipes, wherein a high-pressure gaseous refrigerant compressed by the compressor is liquefied by heat release in the condenser to become a high-pressure liquid refrigerant, the liquid refrigerant is expanded (isenthalpic expansion) by the expansion valve to be decompressed, and then the low-pressure liquid refrigerant having a lowered boiling point is evaporated in the evaporator, whereby the interior of the refrigerator or the like is cooled by taking the latent heat of evaporation necessary for the evaporation from the interior of the refrigerator or the like.
As a method of improving the refrigerating capacity or coefficient of performance (COP) of such a refrigerating apparatus, there is known a method in which a liquid-gas heat exchanger is provided between an evaporator and an expansion valve in a refrigerant circulation circuit, and a refrigerant condensed by a condenser and a refrigerant evaporated by the evaporator are heat-exchanged with each other in the liquid-gas heat exchanger to supercool and superheat each refrigerant.
In addition, patent document 1 proposes a refrigerating and air-conditioning apparatus equipped with a gas-liquid heat exchanger, in which expansion valves are provided between a condenser and the gas-liquid heat exchanger and between the gas-liquid heat exchanger and an evaporator of a refrigerant circulation circuit, respectively, and an opening degree of the expansion valve is controlled based on a refrigerant temperature at an outlet of the condenser and a refrigerant temperature at an inlet of the compressor, thereby maintaining a dryness of the refrigerant at an outlet of the evaporator at a predetermined target value to realize a high-efficiency operation and eliminate a trouble such as scattering of condensed water due to drying of the evaporator.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 2009-162388
Problems to be solved by the invention
However, when the refrigerating and air-conditioning apparatus proposed in patent document 1 is operated in an environment where the number of revolutions of the compressor greatly varies, such as a refrigerator car, the heat exchange performance of the gas-liquid heat exchanger also greatly varies with the variation in the number of revolutions of the compressor. For example, when the number of revolutions of the compressor is decreased, the refrigerant circulation amount is decreased, and a cooling failure occurs due to an insufficient heat exchange amount in the gas-liquid heat exchanger, whereas when the number of revolutions of the compressor is increased, the refrigerant circulation amount is increased, and a discharge temperature of the refrigerant at the outlet of the compressor is increased due to an excessive heat exchange amount, and a problem such as deterioration of the refrigerating machine oil occurs.
The present invention has been made in view of the above problems, and an object of the present invention is to provide a gas-liquid heat exchange type refrigerating apparatus capable of suppressing a variation in refrigerating capacity caused by a variation in the number of revolutions of a compressor, suppressing an increase in discharge temperature at an outlet of the compressor, and preventing deterioration of refrigerating machine oil.
Disclosure of Invention
Means for solving the problems
In order to achieve the above object, the invention according to claim 1 provides a gas-liquid heat exchange type refrigeration apparatus in which at least a compressor, a condenser, a heat exchange control valve, a gas-liquid heat exchanger, an expansion valve, and an evaporator are connected in series by a refrigerant line to form a closed refrigerant circulation circuit, and a refrigerant condensed in the condenser and decompressed by the heat exchange control valve and a refrigerant evaporated in the evaporator are heat exchanged in the gas-liquid heat exchanger to supercool or superheat each refrigerant, characterized in that: a discharge temperature sensor is provided between the compressor and the condenser of the refrigerant circulation circuit, a pressure sensor is provided between the heat exchange control valve and the gas-liquid heat exchanger, and a control device is provided for controlling the opening degree of the heat exchange control valve and controlling the flow rate of the refrigerant passing through the heat exchange control valve and flowing through the gas-liquid heat exchanger based on the refrigerant temperature at the outlet of the compressor detected by the discharge temperature sensor and the refrigerant pressure at the outlet of the heat exchange control valve detected by the pressure sensor.
The invention of claim 2 is an invention described in claim 1, and is characterized in that: the controller reduces the opening degree of the heat exchange control valve when the number of revolutions of the compressor decreases, and increases the opening degree of the heat exchange control valve when the number of revolutions of the compressor increases.
The invention of claim 3 is an invention described in claim 1, and is characterized in that: the controller reduces the opening degree of the heat exchange control valve to a value at which the refrigerant, which has been decompressed by the heat exchange control valve and passed through the gas-liquid heat exchanger, is maintained in a gas-liquid mixed state when the temperature of the refrigerant at the outlet of the compressor detected by the discharge temperature sensor exceeds a set value.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the inventions described in claim 1 and claim 2, since the opening degree of the heat exchange control valve is reduced when the number of revolutions of the compressor is reduced, the flow rate of the refrigerant flowing through the gas-liquid heat exchanger is increased, and the amount of heat exchange is increased, and according to this increase in the amount of heat exchange, it is possible to compensate for the reduction in the amount of heat exchange in the gas-liquid heat exchanger due to the reduction in the refrigerant circulation amount caused by the reduction in the number of revolutions, and to suppress a cooling failure due to a shortage of the amount of heat exchange.
Further, since the opening degree of the heat exchange control valve is increased when the number of revolutions of the compressor is increased, the flow rate of the refrigerant flowing through the gas-liquid heat exchanger is decreased, and the amount of heat exchange is decreased.
According to the invention described in claim 3, when the temperature of the refrigerant at the outlet of the compressor exceeds the set value, the opening degree of the heat exchange control valve 3 is greatly reduced until the refrigerant that has been decompressed by the heat exchange control valve and has passed through the gas-liquid heat exchanger is maintained at a value at which the refrigerant is in a gas-liquid mixed state, and therefore the temperature difference between the refrigerant that has passed through the gas-liquid heat exchanger in the form of a gas-liquid two-phase flow and the gaseous refrigerant from the evaporator is reduced, and the amount of heat exchange between the two refrigerants in the gas-liquid heat exchanger is suppressed to be low. Therefore, the superheat of the refrigerant at the inlet of the compressor is suppressed to be low, and the rise of the discharge temperature of the refrigerant at the outlet of the compressor is suppressed, whereby the deterioration of the refrigerating machine oil can be prevented.
Drawings
Fig. 1 is a refrigerant circuit diagram of a gas-liquid heat exchange type refrigerating apparatus according to the present invention.
Fig. 2 is a mollier diagram showing a change in the state of the refrigerant when the opening degree of the heat exchange control valve is controlled in accordance with a change in the number of revolutions of the compressor in the gas-liquid heat exchange type refrigeration apparatus according to the present invention.
Fig. 3 is a graph showing a relationship between a flow rate of a condensate refrigerant and a heat transfer performance in the liquid-gas heat exchanger.
Fig. 4 is a mollier chart showing a change in the state of the refrigerant when the opening degree of the heat exchange control valve is controlled when the discharge temperature of the refrigerant at the outlet of the compressor exceeds a set value in the gas-liquid heat exchange type refrigeration apparatus according to the present invention.
Description of the main part symbols
1 compressor
2 condenser
3 Heat exchange control valve
4 gas-liquid heat exchanger
5 expansion valve
6 evaporator
7 spitting temperature sensor
8 pressure sensor
9 evaporation temperature sensor
10 controller (control device)
L1-L5 refrigerant pipeline
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Fig. 1 is a refrigerant circuit diagram of a gas-liquid heat exchange refrigeration system according to the present invention, in which a compressor 1, a condenser 2, a heat exchange control valve 3, a gas-liquid heat exchanger 4, an expansion valve 5, and an evaporator 6 are connected in series by refrigerant lines L1, L2, L3, L4, and L5 to form a closed refrigerant circulation circuit. Here, the heat exchange control valve 3 is provided on a refrigerant line L2 for connecting the condenser 2 and the liquid-gas heat exchanger 4 with each other through a refrigerant line L2; the expansion valve 5 is provided on a refrigerant line L3, and the refrigerant line L3 connects the liquid-gas heat exchanger 4 and the evaporator 6. The heat exchange control valve 3 is constituted by an electronic control valve whose opening degree is controlled in a stepless manner.
In the gas-liquid heat exchange type refrigeration apparatus according to the present invention, the discharge temperature sensor 7 is provided on the refrigerant line L1 connecting the compressor 1 and the condenser 2, the pressure sensor 8 is provided on the refrigerant line L2 between the heat exchange control valve 3 and the gas-liquid heat exchanger 4, the evaporation temperature sensor 9 is provided on the refrigerant line L4 connecting the evaporator 6 and the gas-liquid heat exchanger 4, and the discharge temperature sensor 7, the pressure sensor 8, and the evaporation temperature sensor 9 are electrically connected to the controller 10, which is a control device. Further, the heat exchange control valve 3, which is an electronic control valve, is electrically connected to the controller 10, and the opening degree of the heat exchange control valve 3 is controlled in accordance with a control signal from the controller 10, as described later.
Next, the operation of the gas-liquid heat exchange refrigerator of the present invention will be described below with reference to a mollier diagram (P-i diagram) shown in fig. 2.
When the compressor 1 is rotationally driven by an engine (not shown) as a driving source, the compressor is in a state (pressure P) shown in a of fig. 21Enthalpy i1) The gaseous refrigerant (b) is compressed by the compressor 1 to a state (pressure P) shown in fig. 22Enthalpy i2) The high-temperature high-pressure gaseous refrigerant (compression stroke) is introduced into the condenser 2 through the refrigerant line L1. At this time, the compression power W (converted into heat) of the compressor 1 is represented by (i)2-i1) To indicate.
In the condenser 2, the high-temperature and high-pressure gaseous refrigerant condenses the heat Q2The liquid is released into the atmosphere, changes from the state at b to the state at c in fig. 2 (phase change), liquefies (condensation stroke), and changes to the state shown at c in fig. 2 (pressure P)2Enthalpy i3) The high-pressure liquid refrigerant. Further, the heat generation amount (heat of condensation) Q at this time2To (i)2-i3) To indicate.
Then, as described above, the high-pressure liquid refrigerant liquefied in the condenser 2 changes its state through a path (condition) indicated by B in fig. 2, for example. That is, the high-pressure liquid refrigerant liquefied in the condenser 2 reaches the heat exchange control valve 3 through the refrigerant line L2, and is decompressed to the pressure P by the heat exchange control valve 33Adiabatic expansion (isenthalpic expansion) (expansion stroke) is performed until then, and the state (pressure P) shown at d in fig. 2 is obtained3Enthalpy i3) Part of the refrigerant is gasified.
As described above, a part of the vaporized refrigerant is introduced into the liquid-gas heat exchanger 4 through the refrigerant line L2, and the gaseous refrigerant vaporized and vaporized in the evaporator 6 passes through the liquid-gas heat exchanger 4 as described laterSince the refrigerant line L4 is introduced, the refrigerant (a part of the vaporized refrigerant) introduced from the refrigerant line L2 into the gas-liquid heat exchanger 4 is supercooled by heat exchange with the low-temperature gaseous refrigerant evaporated in the evaporator 6 and introduced from the refrigerant line L4, and is in a state shown at e in fig. 2 (pressure P)3Enthalpy i4) The liquid refrigerant of (2). In addition, the supercooling heat amount Δ Q at this time2To (i)3-i4) To indicate.
Then, as described above, the refrigerant supercooled in the liquid-gas heat exchanger 4 is decompressed again by the expansion valve 5 to be adiabatically expanded (isenthalpic expansion) (expansion stroke), and the state changes to the state shown at f in fig. 2 (pressure P)1Enthalpy i4) Then, part of the refrigerant is vaporized, and the boiling point is lowered by the pressure reduction. The refrigerant decompressed by the expansion valve 5 and having a lowered boiling point is introduced into the evaporator 6 from the refrigerant line L3, and while flowing through the evaporator 6, the refrigerant takes evaporation heat Q from the surroundings1And evaporates, changing from the state shown at f to the state shown at g (pressure P)1Enthalpy i5) And is vaporized (evaporation process). Heat of vaporization Q at this time1To (i)5-i4) However, as described above, the refrigerant before being decompressed by the expansion valve 5 is supercooled by Δ Q only in the liquid-gas heat exchanger 42(＝i3-i4) So that the heat of vaporization will only increase the amount of subcooling Δ Q2Then the freezing capacity will also be increased only by the increase Δ Q2。
Thereafter, the low-pressure gaseous refrigerant evaporated in the evaporator 6 is supercooled by the high-pressure refrigerant introduced from the refrigerant line L2 into the liquid-gas heat exchanger 4 while flowing through the liquid-gas heat exchanger 4 from the refrigerant line L4 as described above, and therefore the temperature of the low-pressure gaseous refrigerant rises and changes from the state shown at g in fig. 2 to the state shown at a (pressure P) at the stage of being sucked into the compressor 11Enthalpy i1) And is only overheated by the heat quantity Δ Q shown in the figure1. The superheated gaseous refrigerant is then cooled byThe compressor 1 compresses the refrigerant again, and thereafter, the refrigerant repeats the same state change as described above.
In the gas-liquid heat exchange type refrigeration apparatus of the present invention, the refrigeration cycle described above is repeated, and the required refrigeration is performed by absorbing heat in accordance with the evaporation of the low-temperature liquid refrigerant in the evaporator 6, the temperature of the gaseous refrigerant discharged from the compressor 1 is detected by the discharge temperature sensor 7, the pressure of the refrigerant decompressed by the heat exchange control valve 3 after being condensed by the condenser 2 is detected by the pressure sensor 8, and these detected values are transmitted to the controller 10. Then, the controller 10 controls the opening degree of the heat exchange control valve 3 based on the refrigerant temperature at the outlet of the compressor 1 detected by the discharge temperature sensor 7 and the refrigerant pressure at the outlet of the heat exchange control valve 3 detected by the pressure sensor 8.
Specifically, when the number of revolutions of the compressor 1 is decreased, the opening degree of the heat exchange control valve 3 is decreased, and conversely, when the number of revolutions of the compressor 1 is increased, the opening degree of the heat exchange control valve 3 is increased. When the temperature of the refrigerant at the outlet of the compressor 1 detected by the discharge temperature sensor 7 exceeds a set value, the opening degree of the heat exchange control valve 3 is reduced to a value at which the refrigerant that has been reduced in pressure by the heat exchange control valve 3 and has passed through the gas-liquid heat exchanger 4 is maintained in a gas-liquid mixed state (see fig. 4).
When the gas-liquid heat exchange type refrigeration apparatus of the present invention is mounted on, for example, a refrigeration vehicle, the number of revolutions of the compressor 1 driven by the engine varies depending on the traveling state of the refrigeration vehicle.
For example, if the number of revolutions of the compressor 1 is reduced, the circulation amount of the refrigerant in the refrigeration cycle decreases, and therefore the refrigeration capacity decreases, in this case, as described above, since the controller 10 reduces the opening degree of the heat exchange control valve 3, the flow rate of the refrigerant flowing through the gas-liquid heat exchanger 4 increases, and the heat exchange amount increases, and according to this increase in the heat exchange amount, the decrease in the heat exchange amount in the gas-liquid heat exchanger 4 due to the decrease in the circulation amount of the refrigerant due to the reduction in the number of revolutions can be compensated for, and a cooling failure due to a shortage of the heat exchange amount can be suppressed.
Here, a state change of the high-pressure liquid refrigerant liquefied in the condenser 2 when the refrigerant passes through the liquid-gas heat exchanger 4 from the heat exchange control valve 3 and flows to the expansion valve 5 is shown as, for example, B, C, D in fig. 2. When the operation is performed in the state shown in the B process, the pressure of the high-pressure liquid refrigerant is controlled from P by the heat exchange control valve 32Is decompressed into P3When the number of revolutions of the compressor 1 is decreased, the opening degree of the heat exchange control valve 3 is decreased according to the decrease degree of the number of revolutions, and the pressure of the high-pressure liquid refrigerant is reduced to P as shown in C, D of fig. 23’、P3”(P3>P3’>P3") the flow rate of the refrigerant flowing through the liquid-gas heat exchanger 4 is increased to increase the heat exchange amount as shown in the drawing, so that the cooling failure due to the shortage of the heat exchange amount can be suppressed.
Fig. 3 shows the relationship between the flow velocity (m/s) of the refrigerant and the heat transfer performance KA (W/K) in the liquid-gas heat exchanger 4, and it is understood from this figure that the heat transfer performance KA increases as the flow velocity of the refrigerant increases.
Here, the process a in fig. 2 shows a process (condition) in which the refrigerant is supercooled in the liquid-gas heat exchanger 4 without using the heat exchange control valve 3 and then expanded by the expansion valve 5, and the flow rate of the refrigerant, the amount of heat exchange in the liquid-gas heat exchanger 4, and the performance improvement rate when the state of the refrigerant is changed by passing through the process a are obtained from a simulation on the basis of the state of the refrigerant changed by passing through the processes B, C, D, and the results shown in table 1 are obtained.
[ Table 1]
As is clear from the results in table 1, when the number of revolutions of the compressor 1 is decreased, if the opening degree of the heat exchange control valve 3 is decreased, the flow rate of the refrigerant is increased, and the amount of heat exchanged in the gas-liquid heat exchanger 4 is increased, so that the performance is improved and the refrigerating capacity can be improved.
On the contrary, when the number of revolutions of the compressor 1 is increased, the refrigerant circulation amount is increased, and the discharge temperature of the refrigerant at the outlet of the compressor 1 is increased due to an excessive heat exchange amount in the gas-liquid heat exchanger 4, thereby causing a problem such as deterioration of the refrigerating machine oil, and therefore, the controller 10 performs control such that the opening degree of the heat exchange control valve 3 is increased as described above.
For example, when the operation is performed in the state shown in the D process of fig. 2, the pressure of the high-pressure liquid refrigerant is controlled from P by the heat exchange control valve 32Is decompressed into P3", if the number of revolutions of the compressor 1 increases, the opening degree of the heat exchange control valve 3 is increased according to the increase degree of the number of revolutions, and the pressure of the high-pressure liquid refrigerant is reduced to P as shown in C, B of fig. 23’、P3(P3”<P3’<P3) Since the flow rate of the refrigerant flowing through the liquid-gas heat exchanger 4 is decreased and the heat exchange amount is decreased as shown in the drawing, the rise in the discharge temperature of the refrigerant at the outlet of the compressor 1 due to the excessive heat exchange amount can be suppressed, and the deterioration of the refrigerating machine oil can be prevented.
As is clear from the results in table 1, when the number of revolutions of the compressor 1 increases, the flow rate of the refrigerant decreases and the amount of heat exchanged in the gas-liquid heat exchanger 4 decreases as the opening degree of the heat exchange control valve 3 increases, and as a result, the performance decreases and the refrigerating capacity decreases.
In the gas-liquid heat exchange type refrigeration apparatus of the present invention, when the temperature of the refrigerant at the outlet of the compressor 1 detected by the discharge temperature sensor 7 exceeds a set value, the controller 10 reduces the opening degree of the heat exchange control valve 3 to a value at which the refrigerant, which has been decompressed by the heat exchange control valve 3 and passed through the gas-liquid heat exchanger 4, is maintained in a gas-liquid mixed state, as described above.
For example, when the state of the high-pressure liquid refrigerant liquefied in the condenser 2 flows from the heat exchange control valve 3 to the expansion valve 5 through the gas-liquid heat exchanger 4 is changed, as shown by, for example, B, C, D in fig. 4, the opening degree of the heat exchange control valve 3 is reduced to reduce the pressure P of the high-pressure liquid refrigerant liquefied in the condenser 22Greatly reducing the pressure to P3’、P3"the refrigerant that has been decompressed by the heat exchange control valve 3 and has passed through the gas-liquid heat exchanger 4 can be maintained in a gas-liquid mixed state. That is, when the operation is performed in the state indicated by the B-process, the pressure of the high-pressure liquid refrigerant is controlled from P by the heat exchange control valve 32Reducing the pressure to P3When the number of revolutions of the compressor 1 is decreased, the opening degree of the heat exchange control valve 3 is decreased according to the decrease degree of the number of revolutions, and the pressure of the high-pressure liquid refrigerant is reduced to P as shown in C, D of fig. 23’、P3”(P3”<P3’<P3) Then, the refrigerant decompressed by the heat exchange control valve 3 and passed through the gas-liquid heat exchanger 4 is maintained in a gas-liquid mixed state.
As described above, if the refrigerant decompressed by the heat exchange control valve 3 and having passed through the gas-liquid heat exchanger 4 is maintained in the gas-liquid mixed state, the temperature difference between the refrigerant passing through the gas-liquid heat exchanger 4 in the form of a gas-liquid two-phase flow and the gaseous refrigerant introduced into the gas-liquid heat exchanger 4 from the evaporator 6 through the refrigerant line L4 is reduced, and the amount of heat exchange between the two refrigerants in the gas-liquid heat exchanger 4 can be suppressed to a low level. Therefore, the degree of superheat of the refrigerant at the inlet of the compressor 1 can be suppressed to a low level, and the rise in discharge temperature of the refrigerant at the outlet of the compressor 1 can be suppressed, whereby the deterioration of the refrigerating machine oil can be prevented.
Here, the process a in fig. 4 shows a process in which the refrigerant is supercooled in the liquid-gas heat exchanger 4 without using the heat exchange control valve and then expanded by the expansion valve 5, and the refrigerant flow rate, the amount of heat exchange in the liquid-gas heat exchanger 4, and the performance improvement rate when the state of the refrigerant is changed by passing through each process B, C, D are obtained from a simulation with reference to the case where the state of the refrigerant is changed by passing through this process a, and the results shown in table 2 are obtained.
[ Table 2]
As is clear from the results in table 2, when the refrigerant temperature at the outlet of the compressor 1 detected by the discharge temperature sensor 7 exceeds the set value, the flow rate of the refrigerant increases if the opening degree of the heat exchange control valve 3 is greatly reduced, while the temperature difference between the refrigerant passing through the gas-liquid heat exchanger 4 in the form of a gas-liquid two-phase flow and the gaseous refrigerant introduced into the gas-liquid heat exchanger 4 from the evaporator 6 through the refrigerant line L4 at this time is reduced, and as a result, the amount of heat exchange between the two refrigerants in the gas-liquid heat exchanger 4 is suppressed to a low level, and the refrigerating capacity is reduced.
As described above, according to the present invention, the following effects can be obtained. That is, not only can the variation of the refrigerating capacity caused by the variation of the number of revolutions of the compressor 1 be suppressed, but also the rise of the discharge temperature at the outlet of the compressor 1 can be suppressed, and the deterioration of the refrigerating machine oil can be prevented.
Claims (3)
1. A gas-liquid heat exchange type refrigerating apparatus, wherein at least a compressor, a condenser, a heat exchange control valve, a gas-liquid heat exchanger, an expansion valve and an evaporator are connected in series by a refrigerant line to constitute a closed refrigerant circulation circuit, and a refrigerant condensed in the condenser and decompressed by the heat exchange control valve and a refrigerant evaporated in the evaporator are heat exchanged in the gas-liquid heat exchanger to supercool or overheat the refrigerants, respectively, characterized in that:
a discharge temperature sensor is provided between the compressor and the condenser of the refrigerant circulation circuit, a pressure sensor is provided between the heat exchange control valve and the gas-liquid heat exchanger, and a control device is provided for controlling the opening degree of the heat exchange control valve and controlling the flow rate of the refrigerant passing through the heat exchange control valve and flowing through the gas-liquid heat exchanger based on the refrigerant temperature at the outlet of the compressor detected by the discharge temperature sensor and the refrigerant pressure at the outlet of the heat exchange control valve detected by the pressure sensor.
2. The gas-liquid heat exchange type refrigerating apparatus according to claim 1, wherein:
the controller reduces the opening degree of the heat exchange control valve when the number of revolutions of the compressor decreases, and increases the opening degree of the heat exchange control valve when the number of revolutions of the compressor increases.
3. The gas-liquid heat exchange type refrigerating apparatus according to claim 1, wherein:
the controller reduces the opening degree of the heat exchange control valve to a value at which the refrigerant, which has been decompressed by the heat exchange control valve and passed through the gas-liquid heat exchanger, is maintained in a gas-liquid mixed state when the temperature of the refrigerant at the outlet of the compressor detected by the discharge temperature sensor exceeds a set value.
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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| HK1178965A1 HK1178965A1 (en) | 2013-09-19 |
| HK1178965B true HK1178965B (en) | 2016-10-07 |
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