CN210197770U - Refrigerating and heating system - Google Patents
Refrigerating and heating system Download PDFInfo
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- CN210197770U CN210197770U CN201921073575.0U CN201921073575U CN210197770U CN 210197770 U CN210197770 U CN 210197770U CN 201921073575 U CN201921073575 U CN 201921073575U CN 210197770 U CN210197770 U CN 210197770U
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- 238000010438 heat treatment Methods 0.000 title claims abstract description 74
- 239000007788 liquid Substances 0.000 claims abstract description 43
- 238000005057 refrigeration Methods 0.000 claims abstract description 25
- 230000001502 supplementing effect Effects 0.000 claims abstract description 8
- 238000001816 cooling Methods 0.000 claims description 18
- 239000013589 supplement Substances 0.000 claims description 16
- 230000008878 coupling Effects 0.000 abstract description 6
- 238000010168 coupling process Methods 0.000 abstract description 6
- 238000005859 coupling reaction Methods 0.000 abstract description 6
- 238000000034 method Methods 0.000 abstract description 3
- 239000003507 refrigerant Substances 0.000 description 57
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000006073 displacement reaction Methods 0.000 description 7
- 238000004378 air conditioning Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000005265 energy consumption Methods 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 241001391944 Commicarpus scandens Species 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
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Abstract
The utility model discloses a refrigeration and heating system and a control method thereof, which belong to the technical field of refrigeration and heating, and comprise a compressor, a four-way reversing structure, an outer heat exchanger, an inner heat exchanger and an intercooler, wherein the compressor is provided with an exhaust port, an air inlet and an air supplementing port, the exhaust port and the air inlet are both connected with the four-way reversing structure, the four-way reversing structure is respectively connected with the outer heat exchanger and the inner heat exchanger through a first pipeline and a second pipeline, a third pipeline is connected between the outer heat exchanger and the inner heat exchanger, and a first throttle valve is arranged on the third pipeline; the intercooler has inlet, liquid outlet and gas outlet, and the inlet passes through fourth tube coupling in interior heat exchanger, and the liquid outlet passes through the third tube coupling in outer heat exchanger, and the gas outlet passes through fifth tube coupling in tonifying qi mouth, is provided with the second choke valve on the fourth pipeline. The utility model provides a refrigeration and heating system can promote heating ability and efficiency under the low temperature situation, and saves the electric quantity, has improved user experience.
Description
Technical Field
The utility model relates to a refrigeration and heating technical field especially relate to a refrigeration and heating system.
Background
At present, when a conventional air source heat pump air conditioning unit encounters a low-temperature condition in a heating state, the evaporation temperature of the whole air conditioning unit is reduced, namely the low-pressure is reduced, so that the compression ratio of a compressor in the unit exceeds a reliable range, the compressor is easy to break down and damage, the heating capacity is insufficient, and the normal heating requirement cannot be met. In order to ensure the reliability of the air conditioning unit, the problem of insufficient heating capacity in a low-temperature environment is solved by electric auxiliary heating when the reliability of the air conditioning unit is met at a lower temperature (the edge of the running range of the compressor), meanwhile, the damage of the compressor is avoided, but the structure of the heat pump air conditioning unit is undoubtedly increased by the electric auxiliary heating, the power consumption is increased, and the user experience is poor.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a refrigeration and system of heating to the realization is under the low temperature situation, and refrigeration and system of heating still can normally heat, saves the electric quantity, improves user experience.
As the conception, the utility model adopts the technical proposal that:
a refrigeration and heating system comprises a compressor, a four-way reversing structure, an outer heat exchanger and an inner heat exchanger, wherein the compressor is provided with an exhaust port, an air inlet and an air supplementing port, the exhaust port and the air inlet are connected to the four-way reversing structure, the four-way reversing structure is respectively connected to the outer heat exchanger and the inner heat exchanger through a first pipeline and a second pipeline, a third pipeline is connected between the outer heat exchanger and the inner heat exchanger, and a first throttle valve is arranged on the third pipeline;
refrigeration and heating system still includes intercooler, intercooler has inlet, liquid outlet and gas outlet, the inlet pass through the fourth tube coupling in interior heat exchanger, the liquid outlet pass through the third tube coupling in outer heat exchanger, the gas outlet pass through the fifth tube coupling in the tonifying qi mouth, be provided with the second choke valve on the fourth pipeline.
Furthermore, the four-way reversing structure is connected to the air inlet and the air supplementing port through a first branch pipeline and a second branch pipeline respectively, and a first control valve and a second control valve are arranged on the first branch pipeline and the second branch pipeline respectively.
Furthermore, the refrigerating and heating system further comprises three pressure detectors which are respectively arranged at the exhaust port, the air inlet and the air supplementing port of the compressor.
Further, the cooling and heating system further comprises a temperature detector disposed at the discharge port of the compressor.
Furthermore, the refrigerating and heating system further comprises a gas-liquid separator, and the gas-liquid separator is connected between the four-way reversing structure and the compressor.
Furthermore, a third control valve is arranged on the fifth pipeline, the third control valve is a one-way valve, and the one-way valve is communicated along the direction pointing to the air supplement port of the compressor.
Further, a liquid outlet of the intercooler is connected to the third pipeline through a sixth pipeline, a connection position of the sixth pipeline and the third pipeline is located between the first throttle valve and the inner heat exchanger, and a fourth control valve is arranged on the sixth pipeline.
Furthermore, a fifth control valve is arranged on the third pipeline and is positioned between the connection position of the sixth pipeline and the third pipeline and the connection position of the fourth pipeline and the third pipeline.
The utility model has the advantages that:
when the refrigerating and heating system is in heating operation, the refrigerant forms two parts in the intercooler through the control of the second throttle valve, wherein one part is the gas refrigerant which absorbs heat and evaporates, and enters the air supplement port of the compressor through the fifth pipeline; and the other part is further cooled supercooled refrigerant liquid which enters the outer heat exchanger through a third pipeline, compared with the common heat pump system, although the total amount of the liquid refrigerant entering the outer heat exchanger is reduced, the supercooling degree of the liquid refrigerant is increased, and the final heat exchange amount is not lost. And the gaseous refrigerant returning to the compressor from the air supplementing port is in the state of intermediate pressure and intermediate temperature (relative to the pressure and temperature of an exhaust port and an air inlet of the compressor), the exhaust temperature of the compressor can be reduced, the compression ratio is increased, the heating capacity and efficiency of the refrigeration and heating system under the low-temperature condition are improved, and compared with the prior art in which electric auxiliary heating is adopted, the electric quantity is saved, and the user experience is improved.
Drawings
Fig. 1 is a schematic view of a cooling and heating system according to an embodiment of the present invention;
fig. 2 is a schematic view of a cooling and heating system according to a second embodiment of the present invention;
in the figure:
11. a first pipeline; 12. a second pipeline; 13. a third pipeline; 131. a fifth control valve; 132. a first throttle valve; 14. a fourth pipeline; 141. a second throttle valve; 15. a fifth pipeline; 151. a third control valve; 161. a first branch line; 1611. a first control valve; 162. a second branch pipe; 1621. a second control valve; 17. a sixth pipeline; 171. a fourth control valve;
2. a compressor; 3. a four-way reversing structure; 4. an external heat exchanger; 5. an inner heat exchanger; 6. an intercooler; 7. a gas-liquid separator;
81. a first pressure detector; 82. a second pressure detector; 83. a third pressure detector;
9. a temperature detector.
Detailed Description
In order to make the technical problem solved by the present invention, the technical solution adopted by the present invention and the technical effect achieved by the present invention clearer, the technical solution of the present invention will be further explained by combining the drawings and by means of the specific implementation manner. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some but not all of the elements related to the present invention are shown in the drawings.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, detachably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present disclosure, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact between the first and second features, or may comprise contact between the first and second features not directly. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
In the description of the present embodiment, the terms "upper", "lower", "right", etc. are used in an orientation or positional relationship based on that shown in the drawings only for convenience of description and simplicity of operation, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used only for descriptive purposes and are not intended to have a special meaning.
As shown in fig. 1, the embodiment provides a cooling and heating system, which is mainly applied to the field of automobiles, and certainly can be applied to other fields requiring cooling and heating. The refrigerating and heating system comprises a compressor 2, a four-way reversing structure 3, an outer heat exchanger 4 and an inner heat exchanger 5. Wherein, compressor 2 has gas vent, air inlet and tonifying qi mouth, and the tonifying qi mouth is located between air inlet and the gas vent, and by the first section compression of air inlet to tonifying qi mouth refrigerant, by tonifying qi mouth to gas vent refrigerant through the second section compression, gas vent and air inlet all are connected in four-way switching-over structure 3. In this embodiment, the four-way reversing structure 3 is a four-way reversing valve, the four-way reversing valve is connected to the outer heat exchanger 4 through a first pipeline 11, the four-way reversing valve is connected to the inner heat exchanger 5 through a second pipeline 12, and a third pipeline 13 is connected between the inner heat exchanger 5 and the outer heat exchanger 4.
The refrigerating and heating system further comprises an intercooler 6, the intercooler 6 is provided with a liquid inlet, a liquid outlet and a gas outlet, the liquid inlet is connected to the inner heat exchanger 5 through a fourth pipeline 14, a second throttle valve 141 is arranged on the fourth pipeline 14, in this embodiment, the second throttle valve 141 is an electronic expansion valve, and in other embodiments, the second throttle valve 141 may also be a thermal expansion valve. The liquid outlet is connected to the third pipeline 13 through a sixth pipeline 17, the sixth pipeline 17 is provided with a fifth control valve 171, in this embodiment, the fifth control valve 171 is a one-way valve, and the one-way valve is communicated in a direction pointing to the third pipeline 13, but in other embodiments, the fifth control valve 171 may also be a two-way valve capable of opening and closing. The air outlet is connected to the air supplement port of the compressor 2 through a fifth pipeline 15, and the fifth pipeline 15 is provided with a third control valve 151, in this embodiment, the third control valve 151 is also a one-way valve, and the one-way valve is conducted in a direction pointing to the air supplement port, but in other embodiments, the third control valve 151 may also be a two-way valve capable of being opened and closed.
Specifically, in the present embodiment, the fourth pipeline 14 is also connected to the third pipeline 13, the position where the fourth pipeline 14 is connected to the third pipeline 13 is named as a first position, the position where the sixth pipeline 17 is connected to the third pipeline 13 is named as a second position, the third pipeline 13 is provided with the fifth control valve 131, the fifth control valve 131 is located between the first position and the second position, in the present embodiment, the fifth control valve 131 is an electromagnetic valve, but in other embodiments, the fifth control valve 131 may be a two-way valve that can be opened and closed. The third line 13 is provided with a first throttle 132 between the second position and the outer heat exchanger 4, in which embodiment the first throttle 132 is also an electronic expansion valve, although in other embodiments the first throttle 132 may also be a thermostatic expansion valve.
When the cooling and heating system is operated in a cooling mode, the second throttle 141 is in a closed state, and the fifth control valve 171 is set as a check valve, so that the refrigerant in the outer heat exchanger 4 is changed into a gas-liquid mixed saturated refrigerant through the first throttle 132, and then enters the inner heat exchanger 5 along the third pipeline 13 to exchange heat with the air in the vehicle, without passing through the intercooler 6, thereby avoiding the influence on the cooling and heating system.
When the cooling and heating system is operated in heating mode, the second throttle 141 can be in an open state or a closed state, when the second throttle 141 is in the open state, the fifth control valve 131 is closed, and the refrigerant passes through the intercooler 6, so that the compressor 2 is supplemented with air and enthalpy, and a good heating effect is still achieved in a low-temperature environment. Specifically, when the cooling and heating system is in heating operation and the outside temperature is relatively low, the refrigerant is controlled by the second throttle 141 to form two parts in the intercooler 6, wherein one part is the gas refrigerant that absorbs heat and evaporates, and enters the air supplement port of the compressor 2 through the fifth pipeline 15; the other part is the further cooled subcooled refrigerant liquid, which is fed into the outer heat exchanger 4 through the third line 13, compared to the conventional heat pump system, although the total amount of the liquid refrigerant fed into the outer heat exchanger 4 is reduced, the subcooling degree of the liquid refrigerant is increased, and thus the final heat exchange amount is not lost. And the gaseous refrigerant returning to the compressor 2 from the air supplementing port is in the state of intermediate pressure and intermediate temperature, so that the exhaust temperature of the compressor 2 can be reduced, the compression ratio is increased, and the heating capacity and efficiency of the refrigeration and heating system under the low-temperature condition are improved.
The refrigerating and heating system also comprises a gas-liquid separator 7, the gas-liquid separator 7 is connected between the four-way reversing structure 3 and the compressor 2, specifically, a gas outlet of the gas-liquid separator 7 is connected with a third branch pipeline, the third branch pipeline is connected with a first branch pipeline 161, the first branch pipeline 161 is connected with a gas inlet of the compressor 2, the third branch pipeline is also connected with a second branch pipeline 162, the second branch pipeline 162 is connected with a gas supplementing port of the compressor 2, and a first control valve 1611 is provided on the first branch line 161, a second control valve 1621 is provided on the second branch line 162, in this embodiment, the first control valve 1611 is a solenoid valve, the second control valve 1621 is a check valve, and the check valve is conducted in a direction toward the air supplement port, of course, in other embodiments, the first control valve 1611 and the second control valve 1621 may be other valves that can be opened and closed.
Through setting up first branch pipeline 161 and second branch pipeline 162, when first branch pipeline 161 communicates, can adapt to the higher displacement of compressor 2, satisfy higher refrigeration or heating load demand, when second branch pipeline 162 communicates, can adapt to the lower displacement of compressor 2, reduce the energy consumption of system, and then can make this refrigeration and heating system can be in the start-up operation stage, environmental load change stage, under the circumstances such as system operation itself is undulant, adjust the work load of self. For example, when the air conditioner is started to perform heating, if the external temperature is too low, the first control valve 1611 is opened at the moment, and the refrigerant is compressed by two sections from the air inlet to the air outlet, so that the air displacement of the compressor 2 is increased, and the requirement of a higher heating load is met; if the outside temperature is high, the workload of the compressor 2 is low, and at this time, the first control valve 1611 is closed, and the refrigerant passes through a section of compression from the air inlet to the air outlet, which does not affect the heating effect, but reduces the energy consumption of the compressor 2.
This refrigeration and heating system still includes pressure detector, and pressure detector is provided with threely, and three pressure detector sets up respectively in compressor 2's gas vent, air inlet and tonifying qi mouth, specifically, is provided with first pressure detector 81 on the pipeline between compressor 2's gas vent and the four-way reversing structure 3 for detect the pressure of compressor 2's gas vent. A second pressure detector 82 is arranged on a pipeline between the four-way reversing structure 3 and the gas-liquid separator 7 and is used for detecting the pressure of the gas inlet of the compressor 2. The end of the fifth pipe 15 connected to the supply port is provided with a third pressure detector 83 for detecting the pressure at the supply port of the compressor 2. In this embodiment, all three pressure detectors are pressure sensors, but in other embodiments, the pressure detectors may also be pressure detectors and the like.
When the refrigerating and heating system operates in heating, the opening of the second throttle valve 141 is adjusted to enable the pressure of the air supplement port of the compressor 2 to be equal to the preset pressure, and the preset pressure is set according to actual needs, so that the refrigerating and heating system is in the best working state, and the heating effect is improved. The preset pressure is slightly larger than the pressure in the position opposite to the air supplement port in the compressor 2, so that the gaseous refrigerant in the intercooler 6 can enter the compressor 2 from the air supplement port, and simultaneously, the gaseous refrigerant entering the compressor 2 from the air supplement port is in a state of intermediate pressure and intermediate temperature, the exhaust temperature of the compressor 2 is reduced, the compression ratio of the compressor 2 is increased, and the heating capacity of the refrigerating and heating system is improved.
The operation of the cooling and heating system will be described in detail below.
1. In heating operation
If the temperature outside the vehicle is higher than T1, the second throttle valve 141 is closed, the first throttle valve 132 is opened, the fifth control valve 131 is opened, the compressor 2 starts to operate, the high-temperature high-pressure gaseous refrigerant discharged from the exhaust port of the compressor 2 enters the inner heat exchanger 5 through the four-way reversing structure 3 and the second pipeline 12, the gaseous refrigerant in the inner heat exchanger 5 exchanges heat with the air in the vehicle, the temperature of the air in the vehicle rises, and the high-temperature high-pressure gaseous refrigerant is cooled into the medium-temperature high-pressure liquid refrigerant. The medium-temperature high-pressure liquid refrigerant discharged from the inner heat exchanger 5 enters the outer heat exchanger 4 through the first throttle valve 132, and in the outer heat exchanger 4, the liquid refrigerant absorbs heat and is evaporated into a gaseous refrigerant, and then the gaseous refrigerant passes through the four-way reversing structure 3 and the gas-liquid separator 7 and then returns to the air inlet of the compressor 2 through the first branch pipeline 161, or enters the compressor 2 through the second branch pipeline 162 from the air supplement port of the compressor 2.
If the temperature outside the vehicle is lower than T1, the second throttle valve 141 is opened, the first throttle valve 132 is opened, the fifth control valve 131 is closed, the high-temperature high-pressure gaseous refrigerant discharged from the exhaust port of the compressor 2 enters the inner heat exchanger 5 through the four-way reversing structure 3 and the second pipeline 12, the gaseous refrigerant in the inner heat exchanger 5 exchanges heat with the air inside the vehicle, the temperature of the air inside the vehicle is increased, and the high-temperature high-pressure gaseous refrigerant is cooled into the medium-temperature high-pressure liquid refrigerant. The intermediate-pressure and intermediate-temperature liquid refrigerant discharged from the inner heat exchanger 5 is adjusted to an intermediate-pressure state by the second throttle valve 141, and a part of the liquid refrigerant introduced into the intercooler 6 absorbs heat and evaporates, thereby generating intermediate-pressure and intermediate-temperature gaseous refrigerant, and subcooling the remaining liquid refrigerant. The liquid refrigerant in the intercooler 6 enters the outer heat exchanger 4 through the seventh pipeline 17 and the third pipeline 13 (and simultaneously passes through the first throttle valve 132 on the third pipeline 13) to exchange heat with the air outside the vehicle, the low-temperature and low-pressure liquid refrigerant absorbs heat and evaporates to form a gaseous refrigerant, and then the gaseous refrigerant passes through the first pipeline 11, the four-way reversing structure 3 and the gas-liquid separator 7 and then returns to the air inlet of the compressor 2 through the first branch pipeline 161, or returns to the air supplement port of the compressor 2 through the second branch pipeline 162. The gaseous refrigerant in the intercooler 6 enters the compressor 2 from the air supply port of the compressor 2 through the fifth pipeline 15, and is mixed with the gaseous refrigerant which enters the compressor 2 from the air inlet of the compressor 2 and is compressed in the first stage, and then the mixed gaseous refrigerant is compressed in the second stage and is discharged from the exhaust port, so that the circulation of the refrigerant in the heating state is formed.
In the process, before the compressor 2 is started, the temperature outside the vehicle is detected, if the temperature outside the vehicle (outside temperature) is less than or equal to t2, the first control valve 1611 is opened, and the first branch pipeline 161 is communicated so as to adapt to the high displacement after the compressor 2 is started and meet the requirement of higher heating load. If the outside temperature (outside temperature) > t2, the first control valve 1611 is closed, and the second control valve 1621 is a one-way valve, so that the second branch pipeline 162 is communicated at the moment to adapt to low displacement after the compressor 2 is started, and the energy consumption of the system is reduced. In addition, since the pressure at the air inlet of the compressor 2 is lower than the pressure at the air supplement port, when the first control valve 1611 is opened to communicate the first branch line 161, even if the second control valve 1621 is opened, the gaseous refrigerant will enter the compressor 2 through the air inlet due to the pressure difference, and thus the operation of the cooling and heating system will not be affected by the opening or closing of the second control valve 1621.
The specific values of T1 and T2 are set according to actual needs, and the values of T1 and T2 are the same or different.
2. During refrigeration operation
The second throttle valve 141 is closed, the first throttle valve 132 is opened, the fifth control valve 131 is opened, the high-temperature and high-pressure gaseous refrigerant discharged from the exhaust port of the compressor 2 enters the outer heat exchanger 4 through the four-way reversing structure 3 and the first pipeline 11 to exchange heat with the air outside the vehicle, the high-temperature and high-pressure gaseous refrigerant is cooled into medium-temperature and high-pressure liquid refrigerant, the medium-temperature and high-pressure liquid refrigerant flowing out of the outer heat exchanger 4 is cooled and depressurized into gas-liquid mixed saturated refrigerant through the first throttle valve 132, and then enters the inner heat exchanger 5 through the fifth control valve 131 to exchange heat with the air inside the vehicle, the temperature of the air inside the vehicle is reduced, and the refrigerant absorbs heat and evaporates into the gaseous refrigerant. The gaseous refrigerant flowing out of the inner heat exchanger 5 returns to the air inlet of the compressor 2 through the second pipeline 12, the four-way reversing structure 3 and the gas-liquid separator 7 by the first branch pipeline 161, or enters the compressor 2 through the air supplement port by the second branch pipeline 162, is compressed by the compressor 2 and then is discharged from the exhaust port, and the circulation of the refrigerant in the refrigeration state is formed.
In the process, before the compressor 2 is started, the temperature outside the vehicle is detected, if the temperature outside the vehicle (the external temperature) is not less than t1, the first control valve 1611 is opened, and the first branch pipeline 161 is communicated so as to adapt to the high displacement after the compressor 2 is started and meet the high refrigeration load requirement. If the outside temperature (outside temperature) < t1, the first control valve 1611 is closed, and the second control valve 1621 is a one-way valve, so that the second branch pipe 162 is communicated at this time, thereby adapting to the low displacement after the compressor 2 is started and reducing the energy consumption of the system. In addition, since the pressure at the air inlet of the compressor 2 is lower than the pressure at the air supplement port, when the first control valve 1611 is opened to communicate the first branch line 161, even if the second control valve 1621 is opened, the gaseous refrigerant will enter the compressor 2 through the air inlet due to the pressure difference, and thus the operation of the cooling and heating system will not be affected by the opening or closing of the second control valve 1621.
The specific value of t1 is set as required.
Example two
As shown in fig. 2, the cooling and heating system provided in this embodiment has basically the same structure as the cooling and heating system in the first embodiment, but the difference is that: the cooling and heating system provided by the embodiment further includes a temperature detector 9, and the temperature detector 9 is disposed at the exhaust port of the compressor 2 and is used for detecting the temperature of the exhaust port of the compressor 2. When the cooling and heating system is operated for heating, the opening of the second throttle valve 141 is adjusted according to the detection result of the temperature detector 9, and when the temperature of the exhaust port of the compressor 2 detected by the temperature detector 9 exceeds the preset temperature, the opening of the second throttle valve 141 is increased, so that the amount of the gaseous refrigerant entering the compressor 2 from the air supply port of the compressor 2 is increased, and the exhaust temperature of the compressor 2 is reduced.
The above embodiments have been described only the basic principles and features of the present invention, and the present invention is not limited by the above embodiments, and is not departing from the spirit and scope of the present invention. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (8)
1. A refrigeration and heating system is characterized by comprising a compressor (2), a four-way reversing structure (3), an outer heat exchanger (4) and an inner heat exchanger (5), wherein the compressor (2) is provided with an exhaust port, an air inlet and an air supplementing port, the exhaust port and the air inlet are connected to the four-way reversing structure (3), the four-way reversing structure (3) is respectively connected to the outer heat exchanger (4) and the inner heat exchanger (5) through a first pipeline (11) and a second pipeline (12), a third pipeline (13) is connected between the outer heat exchanger (4) and the inner heat exchanger (5), and a first throttle valve (132) is arranged on the third pipeline (13);
refrigeration and heating system still includes intercooler (6), intercooler (6) have inlet, liquid outlet and gas outlet, the inlet pass through fourth pipeline (14) connect in interior heat exchanger (5), the liquid outlet pass through third pipeline (13) connect in outer heat exchanger (4), the gas outlet pass through fifth pipeline (15) connect in the tonifying qi mouth, be provided with second choke valve (141) on fourth pipeline (14).
2. Refrigeration and heating system according to claim 1, wherein the four-way reversing structure (3) is connected to the air inlet and the air supplement port through a first branch pipe (161) and a second branch pipe (162), respectively, and a first control valve (1611) and a second control valve (1621) are disposed on the first branch pipe (161) and the second branch pipe (162), respectively.
3. The cooling and heating system according to claim 1, further comprising three pressure detectors provided at the discharge port, the intake port, and the supplementary air port of the compressor (2), respectively.
4. Refrigeration and heating system according to claim 1, further comprising a temperature detector (9), said temperature detector (9) being arranged at said discharge port of said compressor (2).
5. Refrigeration and heating system according to claim 1, characterized in that it further comprises a gas-liquid separator (7), said gas-liquid separator (7) being connected between said four-way reversing structure (3) and said compressor (2).
6. Refrigeration and heating system according to claim 1, characterized in that a third control valve (151) is arranged on the fifth pipeline (15), the third control valve (151) is a check valve, and the check valve is conducted in a direction towards the supplementary air port of the compressor (2).
7. Refrigeration and heating system according to claim 1, wherein the liquid outlet of the intercooler (6) is connected to the third pipeline (13) via a sixth pipeline (17), the connection position of the sixth pipeline (17) and the third pipeline (13) is located between the first throttle valve (132) and the inner heat exchanger (5), and a fourth control valve (171) is arranged on the sixth pipeline (17).
8. Refrigeration and heating system according to claim 7, characterized in that a fifth control valve (131) is arranged on the third line (13), said fifth control valve (131) being located between the connection of the sixth line (17) to the third line (13) and the connection of the fourth line (14) to the third line (13).
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| CN201921073575.0U CN210197770U (en) | 2019-07-10 | 2019-07-10 | Refrigerating and heating system |
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| CN201921073575.0U CN210197770U (en) | 2019-07-10 | 2019-07-10 | Refrigerating and heating system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110243102A (en) * | 2019-07-10 | 2019-09-17 | 上海加冷松芝汽车空调股份有限公司 | A kind of refrigeration and heating system and its control method |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110243102A (en) * | 2019-07-10 | 2019-09-17 | 上海加冷松芝汽车空调股份有限公司 | A kind of refrigeration and heating system and its control method |
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Effective date of registration: 20240519 Address after: No.17-29 Lianshang Road, Guannan Industrial Zone, Jimei District, Xiamen City, Fujian Province 361023 Patentee after: XIAMEN SONGZHI AUTOMOBILE AIR CONDITIONER Co.,Ltd. Country or region after: China Address before: 201108 Shanghai Huaning Minhang District Industrial Zone Xhenzhuang Road No. 4999 Patentee before: SONGZ AUTOMOBILE AIR CONDITIONING Co.,Ltd. Country or region before: China |