CN210951938U - Water chilling unit - Google Patents
Water chilling unit Download PDFInfo
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- CN210951938U CN210951938U CN201920945476.0U CN201920945476U CN210951938U CN 210951938 U CN210951938 U CN 210951938U CN 201920945476 U CN201920945476 U CN 201920945476U CN 210951938 U CN210951938 U CN 210951938U
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Abstract
The utility model discloses a water chilling unit, include: the compressor comprises a first-stage compression cavity and a second-stage compression cavity which are communicated, and the compressor is provided with an air suction port, a low-pressure air supplement port, a medium-pressure air supplement port and an air exhaust port; the condenser is provided with a condensation inlet and a condensation outlet; a heat exchanger having a heat absorption passage and a heat release passage; the evaporator is provided with an evaporation inlet and an evaporation outlet, and the evaporation outlet is connected with the air suction port; the gas-liquid separation device is provided with a liquid inlet, a first outlet and a second outlet, the first outlet is connected with the medium-pressure air supplementing port, the second outlet is connected with the inlet of the heat releasing channel, one of the outlets of the heat releasing channel is connected with the evaporation inlet, and the other outlet is connected with the inlet of the heat absorbing channel. The utility model discloses a cooling water set refrigerant has carried out exothermal through exothermic channel before getting into the evaporimeter, can increase the super-cooled rate of refrigerant before getting into the evaporimeter, improves unit mass refrigerant refrigerating output, reduces the flash gas of refrigerant before getting into the evaporimeter, according to the pressure and the temperature of refrigerant.
Description
Technical Field
The utility model belongs to heat pump system, specifically speaking relates to a cooling water set.
Background
Two-stage compression refrigeration cycles have found wide application in some refrigeration compressors. The existing heat pump system adopts a mode of middle air supplement, specifically, liquid from a condenser is subjected to gas-liquid separation, and the separated gas directly enters a high-pressure cavity of a compressor as middle air supplement; the separated liquid enters an evaporator to be evaporated, cold energy is absorbed, and low-pressure steam from the evaporator enters a low-pressure cavity of the compressor. Because the gaseous refrigerant from the air outlet of the evaporator is usually in a slight liquid-carrying state, the power consumption can be increased during the liquid compression of the compressor, particularly in a centrifugal refrigeration compressor, the blades of the impeller are easy to break through by the liquid compression, the key parts of the compressor are directly damaged, the operation reliability of the compressor is reduced, and the service life of the compressor is shortened.
In addition, the supercooling degree of refrigerant liquid at the outlet of the gas-liquid separation device of the conventional heat pump system is very low, so that liquid at the front part of the throttling device is vaporized, and the technical problems that the unit refrigerating capacity is reduced and the expansion valve cannot normally work exist.
Disclosure of Invention
The utility model discloses contain the liquid from evaporimeter gas outlet exhaust refrigerant among the prior art, increase the consumption, damage the technical problem of compressor easily, provide a cooling water set, can solve above-mentioned problem.
In order to realize the purpose of the utility model, the utility model adopts the following technical scheme to realize:
a chiller, comprising: the compressor comprises a primary compression cavity and a secondary compression cavity which are communicated, and the compressor is provided with an air suction port, a low-pressure air supplement port, a medium-pressure air supplement port and an air exhaust port which are respectively communicated with the primary compression cavity and the secondary compression cavity;
a condenser having a condensation inlet and a condensation outlet, the condensation inlet being connected to the exhaust port;
a heat exchanger having a heat absorption passage and a heat release passage;
an evaporator having an evaporation inlet and an evaporation outlet, the evaporation outlet being connected to the suction port;
the gas-liquid separation device is provided with a liquid inlet, a first outlet and a second outlet, the liquid inlet is connected with the condensation outlet, the first outlet is connected with the medium-pressure air supplementing port, the second outlet is connected with the inlet of the heat release channel, one path of the outlet of the heat release channel is connected with the evaporation inlet, the other path of the outlet of the heat release channel is connected with the inlet of the heat absorption channel through a throttling element, and the outlet of the heat absorption channel is connected with the low-pressure air supplementing port.
Further, a first-stage throttling device is arranged between the condenser and the gas-liquid separation device;
and a secondary throttling device is arranged between the gas-liquid separation device and the evaporator.
Further, a first liquid level detection device is arranged in the condenser;
and a second liquid level detection device is arranged in the gas-liquid separation device.
Further, the air suction port is provided with an air suction temperature sensor and an air suction pressure sensor;
the exhaust port is provided with an exhaust temperature sensor and an exhaust pressure sensor;
the low-pressure air supplementing port is provided with a first air supplementing temperature sensor and a first air supplementing pressure sensor;
the medium-pressure air supplementing port is provided with a second air supplementing temperature sensor and a second air supplementing pressure sensor.
Furthermore, a flow regulating device is arranged between the first outlet and the medium-pressure air supplementing port.
Further, the compressor is a two-stage centrifugal compressor, a screw compressor set or a scroll compressor set.
Furthermore, a flow deflector is arranged at the inlet of the first-stage compression cavity and connected with a driving motor.
Further, the first-stage throttling device and/or the second-stage throttling device is an electronic expansion valve.
Further, the heat exchanger is an economizer.
Further, the gas-liquid separation device is a flash evaporator.
Compared with the prior art, the utility model discloses an advantage is with positive effect: the water chilling unit of the utility model adds the heat exchanger behind the gas-liquid separation device, so that the refrigerant coming out of the gas-liquid separation device enters the heat release channel of the heat exchanger, one path of the refrigerant flowing out of the heat release channel enters the heat absorption channel of the heat exchanger, absorbs the refrigerant in the heat release channel to vaporize and evaporate, becomes low-pressure gaseous refrigerant, is supplied with air for the primary compression cavity through the low-pressure air supply port, and the other path of the refrigerant enters the evaporator, the refrigerant absorbs heat in the evaporator and evaporates into gas state to enter the compressor, and because the refrigerant passes through the heat release channel to release heat before entering the evaporator, can increase the supercooling degree of the refrigerant before entering the evaporator, improve the refrigerating capacity of the refrigerant per unit mass, reduce flash evaporation gas of the refrigerant before entering the evaporator, according to the pressure and the temperature of the refrigerant, the opening of the throttling element is adjusted, so that the amount of the refrigerant entering the evaporator is adjusted, and the condition of air suction and liquid carrying of the compressor is improved.
Other features and advantages of the present invention will become more apparent from the following detailed description of the invention when read in conjunction with the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
Fig. 1 is a schematic diagram of an embodiment of a water chiller according to the present invention;
fig. 2 is a p-h diagram of the chiller of fig. 1.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings and embodiments.
It should be noted that, in the description of the present invention, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In a first embodiment, the present embodiment provides a water chilling unit, as shown in fig. 1, including a compressor 11, a condenser 12, a heat exchanger 13, a gas-liquid separation device 14, and an evaporator 15, where the compressor 11 includes a first-stage compression cavity and a second-stage compression cavity, the first-stage compression cavity is communicated with the second-stage compression cavity, the first-stage compression cavity is further communicated with a suction port 112 and a low-pressure air supplement port 115, the second-stage compression cavity is further communicated with a medium-pressure air supplement port 114 and an exhaust port 113, the condenser 12 has a condensation inlet 121 and a condensation outlet 122, and the condensation inlet 121 is connected with an exhaust port 113 of the second-; the evaporator 15 has an evaporation inlet 151 and an evaporation outlet 152, and the heat exchanger 13 has a heat absorption passage 131 and a heat release passage 132; the gas-liquid separating device 14 has a liquid inlet 141, a first outlet 142 and a second outlet 143, the liquid inlet 141 is connected to the condensation outlet 122, and the second outletOne outlet 142 is connected with the medium pressure air supplement port 114, the inlet of the heat release channel 132 of the second outlet 143 is connected, one path of the refrigerant flowing out of the heat release channel is connected with the evaporation inlet 151, the other path of the refrigerant is connected with the inlet of the heat absorption channel 131 through the throttling element 18, the outlet of the heat absorption channel 131 is connected with the low pressure air supplement port 115, and the evaporation outlet 152 is connected with the air suction port 112. The working principle of the water chilling unit is as follows: the low pressure vapor generated in the evaporator 15 is first sucked into the first stage compression chamber by the compressor 11, the first stage compression chamber compresses the vapor to an intermediate pressure, and the vapor enters the second stage compression chamber and is further compressed to a condensing pressurepk and then into the condenser 12 to be condensed into a liquid. The refrigerant from the condenser 12 enters a gas-liquid separator 14 to be separated into gas and liquid. The separated medium-pressure gas is used as intermediate air supplement and enters a medium-pressure air supplement port, and is merged with the exhaust gas from the primary compression cavity and enters a secondary compression cavity; the liquid refrigerant separated by the gas-liquid separation device 14 enters a heat release channel of the heat exchanger, one path of the refrigerant flowing out of the heat release channel enters a heat absorption channel of the heat exchanger, the refrigerant in the heat release channel is absorbed, vaporized and evaporated, the refrigerant is changed into low-pressure gaseous refrigerant, the low-pressure gaseous refrigerant is supplied to a primary compression cavity through a low-pressure gas supply port, the superheat degree of the refrigerant entering the compressor can be adjusted by adjusting the pressure and the temperature of the partial refrigerant, and the condition that the liquid is taken in the air sucked by the compressor. The other path of refrigerant enters the evaporator, absorbs heat in the evaporator and evaporates into gaseous state to enter a first-stage compression cavity of the compressor, and the refrigerant passes through the heat release channel to release heat before entering the evaporator, so that the supercooling degree of the refrigerant before entering the evaporator can be increased, the refrigerating capacity of the refrigerant per unit mass can be improved, the flash evaporation gas of the refrigerant before entering the evaporator can be reduced, the opening degree of the throttling element can be adjusted according to the pressure and the temperature of the refrigerant, the refrigerant entering the evaporator can be further adjusted, and the liquid-carrying condition of the compressor during air suction can be improved. Compared with the traditional scheme for preventing the compressor from compressing with liquid, the scheme has the advantages that the system pipeline layout structure is simple, and the cost is reduced.
Because the liquid separated by the gas-liquid separation device 14 enters the heat release channel 132 of the heat exchanger 13 to release heat and further reduce the temperature of the liquid, the supercooling degree of the evaporator is increased after the liquid enters the evaporator, the refrigerating capacity of the refrigerant per unit mass is improved, a small part of the refrigerant coming out of the heat release channel 132 needs to enter the heat absorption channel 131 of the heat release channel to absorb the heat of the refrigerant in the heat release channel 132, and the small part of the refrigerant needs to be further throttled and depressurized to be vaporized before entering the heat absorption channel 131, therefore, the throttling element 18 is arranged at the front end of the heat absorption channel 131 to throttle and depressurize the refrigerant entering the heat absorption channel 131, and the low-pressure gaseous refrigerant flowing out of the heat absorption channel 131 enters the low-pressure air supplement port 115 to supplement the refrigerant for the primary compression cavity.
A primary throttling device 16 is arranged between the condenser 12 and the gas-liquid separation device 14 and plays a role in throttling and depressurizing the refrigerant. The high pressure liquid refrigerant from the condenser 12 is throttled by the first stage throttling device 16, the pressure of the refrigerant is reduced to the intermediate pressure pm, and the refrigerant is throttled by the first stage throttling device 16, so that the pressure of the refrigerant can be preliminarily reduced, the gas-liquid separation of the later stage and the amount of the refrigerant entering the later stage are facilitated, at this time, the refrigerant comprises the liquid refrigerant and the gaseous refrigerant which is not fully liquefied in the condenser 12, and part of the liquid refrigerant is vaporized when the refrigerant passes through the first stage throttling device 16, the mixed refrigerant enters the gas-liquid separation device 14 to be subjected to the gas-liquid separation, and the separated gaseous refrigerant is still in the intermediate pressure state due to the pressure, so that the separated gaseous refrigerant directly enters the second stage compression cavity through the gas supplementing port 114 to be compressed, and the part of the refrigerant is not compressed in the first stage compression cavity and directly enters the second stage compression cavity as the intermediate gas supplementing, and the unit refrigerating capacity is improved, so that the efficiency of the unit is improved by about 7 percent.
As a preferred embodiment, the primary throttling device 16 may be implemented in the form of an electronic expansion valve, an orifice plate, or a combination of an electronic expansion valve and an orifice plate. The temperature and pressure of the refrigerant entering the gas-liquid separation device 14 are adjusted by adjusting the opening of the primary throttling device 16.
In order to adjust and control the refrigerant amount entering the evaporator 15 to adapt to the change of the refrigeration load and prevent the liquid impact phenomenon of the compressor, a secondary throttling device 17 is arranged between the heat exchanger 13 and the evaporator 15. The liquid refrigerant separated by the gas-liquid separation device 14 is supercooled after passing through the heat release channel 132 of the heat exchanger 13, and then one path of the liquid refrigerant is throttled to the evaporation pressure p0 by the secondary throttling device 17 and enters the evaporator 15 to be evaporated to prepare cold.
The heat release channel 132 of the heat exchanger can increase the supercooling degree of the refrigerant before entering the secondary throttling device 17, improve the refrigerating capacity of the refrigerant in unit mass and reduce the existence of flash evaporation gas before the secondary throttling device 17.
In order to adjust the pressure of the refrigerant, the second-stage throttling device 17 in this embodiment may also be implemented in the form of an electronic expansion valve, an orifice plate, or a combination of an electronic expansion valve and an orifice plate. The temperature and pressure of the refrigerant entering the evaporator 15 are adjusted by adjusting the opening of the secondary throttling device 17.
The heat exchanger 13 in this embodiment may be implemented by an economizer, for example, a plate-type heat exchange economizer, which is simple to implement and is suitable for being butted with products on the market.
The gas-liquid separation device in this embodiment may be implemented by a flash evaporator.
The condenser 12 is provided with a first liquid level detection device 123 for detecting the liquid level of the liquid refrigerant in the condenser 12; the liquid level of the liquid refrigerant in the condenser 12 is detected to adjust the opening degree of the primary throttling device 16, for example, when the liquid level of the condenser 12 is lower than a third set value, the opening degree of the primary throttling device 16 is decreased, and when the liquid level of the condenser 12 is higher than a fourth set value, the opening degree of the primary throttling device 16 is increased, wherein the third set value is greater than 0, and the fourth set value is greater than the third set value.
The gas-liquid separator 14 is provided with a second liquid level detection device 144 for detecting the liquid level of the liquid refrigerant in the gas-liquid separator 14. The detection of the liquid level of the liquid refrigerant in the gas-liquid separator 14 is used to adjust the opening degree of the secondary throttle device 17, for example, when the liquid level of the gas-liquid separator 14 is lower than a first set value, the opening degree of the secondary throttle device 17 is decreased, and when the liquid level of the gas-liquid separator 14 is higher than a second set value, the opening degree of the secondary throttle device 17 is increased, wherein the first set value is greater than 0, and the second set value is greater than the first set value.
The suction port 112 is provided with a suction temperature sensor 21 and a suction pressure sensor 22; the air suction protection device is used for detecting air suction pressure and air suction temperature, is used for air suction protection of the compressor, and is used for deloading when the air suction pressure is lower than an early warning set value and emergently stopping when the air suction pressure is lower than a protection set value.
The discharge port 113 is provided with a discharge temperature sensor 23 and a discharge pressure sensor 24 for detecting discharge pressure and discharge temperature, for discharge protection of the compressor, for set load shedding when the discharge pressure and temperature are higher than the pre-warning set value, and for emergency shutdown when the suction pressure is higher than the protection value.
In addition, the value detected by the sensor can be used for carrying out superheat degree protection on the compressor, calculating the exhaust superheat degree, reducing the load of the unit when the exhaust superheat degree is lower than an exhaust early warning set value, stopping the unit when the exhaust superheat degree is lower than an exhaust protection set value, and enabling the exhaust superheat degree to be a saturation temperature difference value corresponding to the exhaust temperature and the exhaust pressure.
The low-pressure air supplement port 115 is also provided with a first air supplement temperature sensor 25 and a first air supplement pressure sensor 26; which are respectively used for detecting the temperature and the pressure of the low-pressure air supplement and for adjusting the opening degree of the throttling element 18 so as to adapt to the refrigeration of the system and the balance of the load.
The medium-pressure air supplement port 114 is provided with a second air supplement temperature sensor 27 and a second air supplement pressure sensor 28. Which are respectively used for detecting the temperature and the pressure of the high-pressure air supply and are used for adjusting the opening degree of the primary throttling device 16.
A flow rate adjusting device 28 is provided between the first outlet 142 of the gas-liquid separation device 14 and the intermediate-pressure air replenishing port 114, and is configured to control the amount of air replenished to the secondary compression chamber, and by calculating the degree of superheat of air sucked by the intermediate-pressure air replenishing port 114, when the degree of superheat of air sucked by the intermediate-pressure air replenishing port is less than 0, the degree of opening of the primary throttle device is decreased, and the degree of opening of the secondary throttle device is increased, and the degree of opening of the flow rate adjusting device is decreased or closed.
The compressor in this embodiment is a two-stage centrifugal compressor, the inlet of the first-stage compression cavity is provided with a baffle 116, the baffle 116 is connected to a driving motor (not shown in the figure), and the driving motor drives the baffle 116 to move to adjust the opening of the air suction port 112, so that the driving motor can be used for assisting the adjustment of the second-stage throttling device and controlling the amount of refrigerant entering the compressor.
The compressor of this embodiment utilizes variable speed as the primary capacity control means and is assisted as needed by the inlet guide vanes 116. The refrigerant enters a first-stage compression cavity of the compressor through a suction port in the form of low-pressure and low-temperature superheated steam. By adjusting the opening of the guide vanes 116, it can then assist the compressor control at part load conditions. The two impellers 29, 30 are mounted on a common shaft 31. The gaseous refrigerant increases the velocity energy of the refrigerant by the first-stage impeller 29, increases the velocity energy to the refrigerant again by the second-stage impeller 30, converts the velocity energy into the final discharge pressure, and is discharged through the discharge port 113. From the secondary impeller 30, the refrigerant enters the condenser 12 as high pressure superheated vapor. The first-stage impeller 19 is provided with a low-pressure air supplement port 115 facing the inlet side, and a medium-pressure air supplement port 114 is provided between the first-stage compression chamber and the second-stage compression chamber.
The compressor 11 of the present embodiment may be implemented by using other compressors having two-stage compression functions, such as a screw compressor unit or a scroll compressor unit.
As shown in fig. 2, which is a p-h diagram (pressure-enthalpy diagram) of the water chilling unit of the present embodiment, 1 '-2' represents a compression process of a primary compression chamber, 2 '-10-3 represents a process in which exhaust gas 2' and intermediate make-up gas 10 of the primary compression chamber are mixed in a 3-point state, 3-4 represents a compression process in a secondary compression chamber, 4-6 represents cooling in a condenser 12, condensation and supercooling, 6-7, which represents a throttling process through the primary throttling device 16, after which the refrigerant is subjected to gas-liquid separation, the refrigerant at the point 7 is separated into saturated gas at the point 10, the separated liquid is supercooled to the point 8 ' through the heat exchanger 13, 8 ' -9 ' represents a throttling process through the secondary throttling device 17, and 9 ' -1 ' represents a superheating process after being mixed with superheated gas in the heat release channel 132 after being subjected to evaporative cooling in the evaporator 15.
The above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described in the foregoing embodiments, or that equivalents may be substituted for elements thereof; such modifications and substitutions do not depart from the spirit and scope of the present invention, which is claimed.
Claims (10)
1. A chiller, comprising:
the compressor comprises a primary compression cavity and a secondary compression cavity which are communicated, and the compressor is provided with an air suction port, a low-pressure air supplement port, a medium-pressure air supplement port and an air exhaust port which are respectively communicated with the primary compression cavity and the secondary compression cavity;
a condenser having a condensation inlet and a condensation outlet, the condensation inlet being connected to the exhaust port;
a heat exchanger having a heat absorption passage and a heat release passage;
an evaporator having an evaporation inlet and an evaporation outlet, the evaporation outlet being connected to the suction port;
the gas-liquid separation device is provided with a liquid inlet, a first outlet and a second outlet, the liquid inlet is connected with the condensation outlet, the first outlet is connected with the medium-pressure air supplementing port, the second outlet is connected with the inlet of the heat release channel, one path of the outlet of the heat release channel is connected with the evaporation inlet, the other path of the outlet of the heat release channel is connected with the inlet of the heat absorption channel through a throttling element, and the outlet of the heat absorption channel is connected with the low-pressure air supplementing port.
2. The water chilling unit according to claim 1, wherein a primary throttling device is arranged between the condenser and the gas-liquid separation device;
and a secondary throttling device is arranged between the gas-liquid separation device and the evaporator.
3. The chiller according to claim 2 wherein a first liquid level detection device is provided in said condenser;
and a second liquid level detection device is arranged in the gas-liquid separation device.
4. The water chilling unit according to claim 3, wherein the suction port is provided with a suction temperature sensor and a suction pressure sensor;
the exhaust port is provided with an exhaust temperature sensor and an exhaust pressure sensor;
the low-pressure air supplementing port is provided with a first air supplementing temperature sensor and a first air supplementing pressure sensor;
the medium-pressure air supplementing port is provided with a second air supplementing temperature sensor and a second air supplementing pressure sensor.
5. The water chilling unit according to any one of claims 1-4, wherein a flow regulating device is provided between the first outlet and the medium pressure air supplement port.
6. The chiller according to any of claims 1-4, wherein the compressor is a two-stage centrifugal compressor, a screw compressor, or a scroll compressor.
7. The water chilling unit according to any one of claims 1-4, wherein a guide vane is arranged at an inlet of the primary compression chamber, and the guide vane is connected with a driving motor.
8. The chiller according to any of claims 2-4 wherein the primary throttling device and/or the secondary throttling device is an electronic expansion valve.
9. The chiller according to any of claims 1-4 wherein said heat exchanger is an economizer.
10. The water chilling unit according to any one of claims 1-4, wherein the gas-liquid separation device is a flash evaporator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920945476.0U CN210951938U (en) | 2019-06-22 | 2019-06-22 | Water chilling unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920945476.0U CN210951938U (en) | 2019-06-22 | 2019-06-22 | Water chilling unit |
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| CN210951938U true CN210951938U (en) | 2020-07-07 |
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| CN201920945476.0U Active CN210951938U (en) | 2019-06-22 | 2019-06-22 | Water chilling unit |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020259131A1 (en) * | 2019-06-22 | 2020-12-30 | 青岛海尔空调电子有限公司 | Water cooling unit and control method |
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2019
- 2019-06-22 CN CN201920945476.0U patent/CN210951938U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020259131A1 (en) * | 2019-06-22 | 2020-12-30 | 青岛海尔空调电子有限公司 | Water cooling unit and control method |
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