CN112268321A - Mixed working medium refrigerating system and dehumidifier - Google Patents
Mixed working medium refrigerating system and dehumidifier Download PDFInfo
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- CN112268321A CN112268321A CN202011153451.0A CN202011153451A CN112268321A CN 112268321 A CN112268321 A CN 112268321A CN 202011153451 A CN202011153451 A CN 202011153451A CN 112268321 A CN112268321 A CN 112268321A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/02—Ducting arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
- F24F2003/1446—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing
Abstract
The utility model relates to a mixed working medium refrigerating system and dehumidifier, wherein the first flow path that is rich in low boiling point component among the refrigerating system includes first evaporation branch road and first condensation branch road, and the second flow path that is rich in high boiling point component includes second evaporation branch road and second condensation branch road, and refrigerating system includes: a compression device; the gas-liquid separation device is communicated with the first air suction port through a gas refrigerant outlet; the first evaporator and the second evaporator are respectively arranged on the first evaporation branch and the second evaporation branch, a first outlet of the first evaporator is communicated with the refrigerant inlet, a second inlet of the second evaporator is communicated with the liquid refrigerant outlet, and a second outlet of the second evaporator is communicated with the second air suction port; and the first condenser and the second condenser are respectively arranged on the first condensing branch and the second condensing branch, a third inlet of the first condenser is communicated with the first exhaust port, a fourth inlet of the second condenser is communicated with the second exhaust port, and a third outlet of the first condenser and a fourth outlet of the second condenser are communicated with the first inlet of the first evaporator after being converged.
Description
Technical Field
The disclosure relates to the technical field of refrigeration equipment, in particular to a mixed working medium refrigeration system and a dehumidifier.
Background
The double-temperature circulation can reduce irreversible loss in the heat exchange process to improve the energy efficiency of the system, and can realize cascade utilization of energy to a certain extent, thereby being widely concerned. Especially, the dual-temperature circulating system constructed by the mixed working medium can reduce the irreversible loss in the heat exchange process and improve the system energy efficiency, but the heat transfer characteristic of the mixed working medium is considered, so that two problems exist: the low boiling point gas which is not easy to condense exists in the condensation process, so that the condensation heat transfer coefficient can be reduced; the dual-temperature completely depends on the temperature slip of the mixed working medium, but the larger the temperature slip is, the poorer the heat transfer performance is, and the effect improvement effect is not as expected. Therefore, the heat transfer performance of the mixed working medium needs to be improved.
Disclosure of Invention
The embodiment of the disclosure provides a mixed working medium refrigerating system and a dehumidifier, which can improve the overall heat exchange performance of the mixed working medium refrigerating system.
According to a first aspect of the present disclosure, a mixed working medium refrigeration system is provided, which has a first flow path and a second flow path for flowing mixed working medium, the mixed working medium in the first flow path is rich in low boiling point components, the mixed working medium in the second flow path is rich in high boiling point components, the first flow path includes a first evaporation branch and a first condensation branch, the second flow path includes a second evaporation branch and a second condensation branch, the mixed working medium refrigeration system includes:
a compression device having a first suction port and a first discharge port communicated with each other, and a second suction port and a second discharge port communicated with each other;
the gas-liquid separation device is provided with a refrigerant inlet, a gaseous refrigerant outlet and a liquid refrigerant outlet, and the gaseous refrigerant outlet is communicated with the first air suction port;
the first evaporator and the second evaporator are respectively arranged on the first evaporation branch and the second evaporation branch, a first outlet of the first evaporator is communicated with the refrigerant inlet, a second inlet of the second evaporator is communicated with the liquid refrigerant outlet, and a second outlet of the second evaporator is communicated with the second air suction port; and
the first condenser and the second condenser are respectively arranged on the first condensation branch and the second condensation branch, a third inlet of the first condenser is communicated with the first exhaust port, a fourth inlet of the second condenser is communicated with the second exhaust port, and a third outlet of the first condenser and a fourth outlet of the second condenser are communicated with the first inlet of the first evaporator after being converged.
In some embodiments, the mixed working medium refrigeration system further comprises a first air duct, and the second evaporator and the first evaporator are sequentially arranged in the first air duct along the air flow direction.
In some embodiments, the first condenser and the second condenser are disposed within the first air duct and are sequentially disposed downstream of the first evaporator in the direction of air flow.
In some embodiments, the mixed working medium refrigeration system further comprises a second air duct, the second air duct is independent from the first air duct, and at least one of the first condenser and the second condenser is arranged in the second air duct.
In some embodiments, a first condenser is disposed in the first air path downstream of the first evaporator, and a second condenser is disposed in the second air path; or the mixed working medium refrigerating system also comprises a third air channel, the third air channel is mutually independent with the first air channel and the second air channel, the first condenser is arranged in the second air channel, and the second condenser is arranged in the third air channel.
In some embodiments, the mixed refrigerant refrigeration system further includes a first throttling element disposed in the first evaporator branch between the first inlet and the junction of the third outlet and the fourth outlet.
In some embodiments, the mixed refrigerant refrigeration system further comprises: and the pressure regulating component is arranged at the position where the first condensation branch and the second condensation branch are close to the first evaporator and communicated with each other, and is configured to balance the pressure of the first condensation branch and the pressure of the second condensation branch.
In some embodiments, the mixed refrigerant refrigeration system further comprises: and a second throttling part configured to adjust a ratio of the gaseous refrigerant to the liquid refrigerant in the gas-liquid separation device.
In some embodiments, the second throttling element is disposed on the first evaporation branch and between the first outlet and the refrigerant inlet; and/or the second throttling component is arranged on a throttling branch which is connected with the first evaporation branch in parallel.
In some embodiments, the mixed working medium refrigeration system further comprises a heat recovery pipe, the heat recovery pipe is arranged in the lower region in the gas-liquid separation device and is connected in series in the second condensation branch.
In some embodiments, the mixed working medium refrigeration system further comprises a first heat regenerator arranged between the pipe section of the second condensation branch on the fourth outlet side and the pipe section of the second evaporation branch on the second outlet side; and/or the mixed working medium refrigerating system also comprises a second heat regenerator, a pipe section which is arranged on one side of the third outlet of the first condensation branch and a pipe section which is arranged between the gaseous refrigerant outlet and the first air suction port of the first evaporation branch.
In some embodiments, the compression device has a first compression chamber and a second compression chamber, the first compression chamber is provided with a first air suction port and a first air exhaust port, and the second compression chamber is provided with a second air suction port and a second air exhaust port; and/or the compression device comprises a first compressor having a first suction port and a first discharge port and a second compressor having a second suction port and a second discharge port.
According to a second aspect of the disclosure, a dehumidifier is provided, which includes the mixed working medium refrigeration system of the above embodiment.
In some embodiments, the mixed working medium refrigeration system further comprises a first air duct, and the second evaporator, the first condenser and the second condenser are sequentially arranged in the first air duct along the air flow direction.
The mixed working medium refrigerating system disclosed by the embodiment of the invention is based on the characteristics of component separation and temperature slippage of non-azeotropic mixed refrigerant in a phase equilibrium state, adopts the double-suction double-exhaust compression device to realize double-evaporation double-condensation temperature, carries out step cooling or heating on a heat exchange medium, can realize small temperature difference heat exchange of the refrigerant and the heat exchange medium, greatly reduces the irreversible loss in the heat exchange process, effectively improves the suction pressure, reduces the power consumption of the compression device and improves the system efficiency; and through the separation of different components, the evaporation temperature slippage of the mixed working medium is increased, and the effect improvement effect is enhanced.
Drawings
The accompanying drawings, which are included to provide a further understanding of the disclosure and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the disclosure and together with the description serve to explain the disclosure and not to limit the disclosure. In the drawings:
FIG. 1 is a system schematic of some embodiments of the disclosed mixed refrigerant refrigeration system;
FIG. 2 is a schematic diagram of the operation of the mixed refrigerant refrigeration system of FIG. 1;
FIG. 3 is a system schematic of further embodiments of the mixed refrigerant refrigeration system of the present disclosure;
FIG. 4 is a system schematic of some variations of FIG. 3;
FIG. 5 is a system schematic of further embodiments of the mixed refrigerant refrigeration system of the present disclosure;
FIG. 6 is a system schematic of still further embodiments of the mixed refrigerant refrigeration system of the present disclosure;
FIG. 7 is a system schematic of some variations of FIG. 6;
fig. 8 is a system schematic of further embodiments of the mixed refrigerant refrigeration system of the present disclosure.
Description of the reference numerals
1. A first evaporator; 1A, a first inlet; 1B, a first outlet; 2. a second evaporator; 2A, a second inlet; 2B, a second outlet; 3. a first condenser; 3A and a third inlet; 3B, a third outlet; 4. a second condenser; 4A, a fourth inlet; 4B, a fourth outlet; 5. a compression device; 51. a first air intake port; 52. a first exhaust port; 53. a second air suction port; 54. a second exhaust port; 56. an oil return assembly; 5A, a first compressor; 5B, a second compressor; 6. a gas-liquid separation device; 61. a refrigerant inlet; 62. a gaseous refrigerant outlet; 63. a liquid refrigerant outlet; 64. a heat recovery pipe; 7. a pressure regulating member; 8. a first throttling member; 9. a fan; 10. a first evaporation branch; 11. a second throttling member; 20. a second evaporation branch; 30. a first condensation branch; 40. a second condensation branch; 50. a first heat regenerator; 60. a second regenerator.
Detailed Description
The present disclosure is described in detail below. In the following paragraphs, different aspects of the embodiments are defined in more detail. Aspects so defined may be combined with any other aspect or aspects unless clearly indicated to the contrary. In particular, any feature considered to be preferred or advantageous may be combined with one or more other features considered to be preferred or advantageous.
The terms "first", "second", and the like in the present disclosure are merely for convenience of description to distinguish different constituent elements having the same name, and do not denote a sequential or primary-secondary relationship.
In addition, when an element is referred to as being "on" another element, it can be directly on the other element or be indirectly on the other element with one or more intervening elements interposed therebetween. In addition, when an element is referred to as being "connected to" another element, it may be directly connected to the other element or may be indirectly connected to the other element with one or more intervening elements interposed therebetween. Hereinafter, like reference numerals denote like elements.
The description of the relative orientations and positional relationships of the indications "upper," "lower," "top," "bottom," "front," "back," "inner" and "outer" and the like are used in this disclosure for convenience in describing the disclosure, and do not indicate or imply that the indicated devices must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the scope of the disclosure.
As shown in fig. 1 to 8, the present disclosure provides a mixed working medium refrigeration system, in which the mixed working medium is a non-azeotropic mixed working medium, the refrigeration system has a first flow path and a second flow path for the mixed working medium to flow, the mixed working medium in the first flow path is rich in low boiling point components, and the mixed working medium in the second flow path is rich in high boiling point components. The proportion of the working medium rich in the specific components in the mixed working medium is higher than that of the working medium rich in the other components, and the low-boiling-point component and the high-boiling-point component represent the relative high and low of boiling points. The first flow path comprises a first evaporation branch 10 and a first condensation branch 30 which are communicated, and the second flow path comprises a second evaporation branch 20 and a second condensation branch 40 which are communicated. The mixed working medium refrigerating system comprises: a compression device 5, a gas-liquid separation device 6, a first evaporator 1, a second evaporator 2, a first condenser 3, and a second condenser 4.
Wherein the compression device 5 has a first suction port 51 and a first discharge port 52 communicating with each other, and a second suction port 53 and a second discharge port 54 communicating with each other. Specifically, the compressing device 5 may be provided with a first compressing chamber and a second compressing chamber which are independent of each other, the first compressing chamber being provided with a first suction port 51 and a first discharge port 52, and the second compressing chamber being provided with a second suction port 53 and a second discharge port 54.
The gas-liquid separator 6 has a refrigerant inlet 61, a gaseous refrigerant outlet 62, and a liquid refrigerant outlet 63, and the gaseous refrigerant outlet 62 communicates with the first air intake port 51 through a pipe. The gas-liquid separation device 6 can be a conventional gas-liquid separator, and can also be filled with a filler, wherein the filler can be a paper film, metal, plastic, ceramic or the like; a plurality of baffle plates can be arranged in the separating device to improve the separating effect.
The first evaporator 1 and the second evaporator 2 are arranged in two stages and are respectively arranged on the first evaporation branch 10 and the second evaporation branch 20, a first outlet 1B of the first evaporator 1 is communicated with the refrigerant inlet 61, a second inlet 2A of the second evaporator 2 is communicated with the liquid refrigerant outlet 63, and a second outlet 2B of the second evaporator 2 is communicated with the second suction port 53. In order to improve the evaporation heat exchange effect, a fan 9 can be arranged on one side of the second evaporator 2.
The first condenser 3 and the second condenser 4 are respectively arranged on the first condensation branch 30 and the second condensation branch 40, the first condensation branch 30 and the second condensation branch 40 are arranged in parallel, a third inlet 3A of the first condenser 3 is communicated with the first exhaust port 52, a fourth inlet 4A of the second condenser 4 is communicated with the second exhaust port 54, and a third outlet 3B of the first condenser 3 and a fourth outlet 4B of the second condenser 4 are communicated with the first inlet 1A of the first evaporator 1 after being converged. As shown in fig. 1, the refrigeration system further includes a first throttling component 8, which is disposed on the first evaporation branch 10 and between the merging positions of the first inlet 1A and the third and fourth outlets 3B and 4B, for example, the first throttling component 8 adopts an expansion valve or a capillary tube, etc. to throttle and cool the refrigerant passing through the condenser.
The embodiment provides a cascade air suction and exhaust circulation scheme that the gaseous refrigerant after gas-liquid separation in the evaporation process directly enters the compression device 5 and the liquid refrigerant further evaporates and then enters the compression device 5 by utilizing the separation characteristic and the heat exchange characteristic of the mixed working medium components, and the scheme at least has one of the following beneficial effects:
1. based on the characteristics of component separation and temperature slippage of a non-azeotropic mixed refrigerant in a phase equilibrium state, a double-suction double-exhaust compression device is adopted to realize double-evaporation double-condensation temperature, and a heat exchange medium is subjected to step cooling or heating, so that small-temperature-difference heat exchange of the refrigerant and the heat exchange medium can be realized, the irreversible loss in the heat exchange process is greatly reduced, the suction pressure is effectively improved, the power consumption of the compression device is reduced, and the system efficiency is improved; and through the separation of different components, the evaporation temperature slippage of the mixed working medium is increased, and the effect improvement effect is enhanced.
From the thermodynamics angle, the most ideal refrigeration cycle is with the zero difference in temperature heat transfer between the heat source, and circulation efficiency is the highest like this, but actual heat transfer must have the difference in temperature just can go on, and the heat transfer difference in temperature is big more moreover, and irreversible loss is big more, so reduce the heat transfer difference in temperature and can effectively promote actual endless refrigeration coefficient.
2. Through separating the gas in the evaporimeter in advance, strengthened heat transfer coefficient, reduced the system pressure drop, improve the reposition of redundant personnel inequality, improve the evaporation performance, further promoted the system efficiency.
3. By adopting the double-exhaust compression device, high and low boiling point components in the condensation process are separated to form different condensation temperatures, non-condensable gas in the condensation process is reduced, and the condensation heat transfer performance is improved.
Therefore, the mixed working medium dual-temperature circulation refrigerating system has the advantages of obvious effect improvement effect, high heat exchange coefficient in the evaporation and condensation process, small pressure drop and capability of improving the overall heat exchange performance of the refrigerating system.
The operation of the refrigeration system of the present disclosure is described below in conjunction with fig. 1 and 2. The first high-temperature high-pressure mixed refrigerant which is rich in low-boiling components and is discharged from the first exhaust port 52 of the compression device 5 enters the first condenser 3 to be condensed and heat-exchanged to form saturated liquid or supercooled liquid (the temperature of the third inlet 3A of the first condenser 3 is higher than that of the third outlet 3B), the second high-temperature high-pressure mixed refrigerant which is rich in high-boiling components and is discharged from the second exhaust port 54 of the compression device 5 enters the second condenser 4 to be condensed and heat-exchanged to form saturated liquid or supercooled liquid after passing through the oil return assembly 56 (the temperature of the fourth inlet 4A of the second condenser 4 is higher than that of the fourth outlet 4B), and the refrigerant temperature of the second condenser 4 is integrally higher than that of the first condenser 3. Since the first discharge port 52 is discharged through the interior of the compression device 5, the lubricant oil can be returned to the oil pool, and the second discharge port 54 is not returned to the oil tank by the direct discharge cylinder, an additional oil return component 56 is required to return the lubricant oil in the refrigerant to the oil pool.
The refrigerant passing through the first condenser 3 and the second condenser 4 is converged by the pressure regulating part 7, subjected to pressure balance, throttled by the first throttling part 8, and then turned into a first low-temperature low-pressure two-phase refrigerant, and evaporated into a higher-dryness two-phase refrigerant (the temperature of the first outlet 1B of the first evaporator 1 is higher than that of the first inlet 1A) by the first evaporator 1, and then enters the gas-liquid separation device 6, and low-boiling-point components in the mixed refrigerant are easy to evaporate.
In the gas-liquid separation device 6, the mixed refrigerant is in a phase equilibrium state in which the refrigerant gas portion is rich in the low boiling point component and the liquid portion is rich in the high boiling point component. The refrigerant gas rich in the low boiling point component enters the first suction port 51 of the compression device 5 and is compressed, the compressed gas is discharged from the first discharge port 52, and the refrigerant liquid rich in the high boiling point component enters the second evaporator 2 through the liquid refrigerant outlet 63 of the gas-liquid separation device 6 and is evaporated into saturated or superheated gas (the temperature of the second outlet 2B of the second evaporator 2 is higher than that of the first inlet 2A), and the saturated or superheated gas is sucked by the second suction port 53 of the compression device 5 and is compressed to the second discharge port 54, so that the whole cycle is completed.
In a specific embodiment, taking a mixed working medium of R32 and R1234ze (E) (mass fraction R32: R1234ze (E) ═ 50:50) as an example, ideally, the two-phase refrigerant before entering the first evaporator 1 is R32: R1234ze (E) ═ 50:50, after passing through the first evaporator 1, the low boiling point component R32 is easily evaporated, and in the gas-liquid separation device 6, the refrigerant components are separated, wherein the gas refrigerant component at the top of the gas-liquid separation device 6 is rich in the refrigerant R32 which is easily evaporated (assuming that the inlet dryness of the gas-liquid separation device 6 is 0.6 and the gas-liquid is completely separated, the gas component is R32: R1234ze (E) ═ 60/40), and the liquid refrigerant component at the bottom of the gas-liquid separation device 6 is rich in the high boiling point component R1234ze (E) (the ratio is R32: R1234ze (E) ═ 35/65). Optionally, the dryness of the refrigerant at the inlet of the gas-liquid separation device 6 can be in the range of 0.3-0.9, and preferably in the range of 0.5-0.8.
Then, the gas refrigerant rich in the low boiling point component from the gas-liquid separation device 6 enters the compressor to be compressed and then enters the first condenser 3 to be condensed, the liquid refrigerant rich in the high boiling point component from the gas-liquid separation device 6 is evaporated by the second evaporator 2 and then is compressed to the second condenser 4 to be condensed, the saturated or supercooled liquid from the two condensers is mixed, and the refrigerant component is changed back to the original component (R32: R1234ze (E) ═ 50: 50).
Because the components of the refrigerant are changed, the refrigerant temperatures of the four heat exchangers are also changed, only the temperature change in a two-phase state is discussed here, the pressure loss of the heat exchangers is ignored, the temperature slippage of the refrigerant in the second condenser 4 is 10 ℃, the temperature slippage of the refrigerant in the first condenser 3 is 5.9 ℃, and the total temperature slippage of the condensers is 15.9 ℃ under specific pressure; the temperature glide of the refrigerant in the first evaporator 1 is 3.1 ℃, the temperature glide of the refrigerant in the second evaporator 2 is 10.9 ℃, and the total temperature glide of the evaporators is 14 ℃, which is the result of component separation; if the components are not separated, the mixed working medium of the original components has evaporator temperature slippage of 7.2 ℃ and condenser temperature slippage of 7.7 ℃ under the same pressure.
The temperature glide refers to the difference between the dew point temperature and the bubble point temperature when the refrigerant mixture with different boiling points undergoes phase change under a certain constant pressure. The temperature of the phase change of the refrigerant is gradually increased along the flowing direction of the refrigerant in the evaporator, and the difference of the phase change temperatures of the outlet and the inlet of the evaporator is the temperature slippage of the evaporator; in the condenser, the temperature of the refrigerant subjected to phase change is gradually reduced along the flowing direction of the refrigerant, and the difference of the phase change temperatures of the inlet and the outlet is condenser temperature slippage.
This embodiment is through setting up gas-liquid separation device 6 in the evaporimeter, the low boiling point component that will evaporate separates in advance, high boiling point component refrigerant further evaporates, pressure loss in the evaporation process has not only been reduced, the heat transfer coefficient has been improved, the system pressure drop has been reduced, and improve the evaporimeter reposition of redundant personnel inequality, the temperature difference that has increased high, low temperature evaporation temperature has promptly been improved to the temperature that has improved mixed working medium simultaneously and has slided, the step cooling and the little difference in temperature heat transfer of air side have been realized, reduce the irreversible loss among the heat transfer process, finally promote the system efficiency. Moreover, by adopting the double-suction double-exhaust compression device 5, high and low boiling point components in the condensation process are separated to form different condensation temperatures, non-condensable gas in the condensation process is reduced, and the condensation heat transfer performance is improved. In addition, the refrigerant used by the system circulation is non-azeotropic mixed refrigerant, the refrigerant can be matched according to the temperature difference of the heat exchange fluid inlet and outlet of the application occasion, and the temperature difference of the heat exchange fluid inlet and outlet is positively correlated with the temperature slippage of the refrigerant.
In some embodiments, as shown in fig. 1, the mixed working medium refrigeration system further includes a first air duct, and the second evaporator 2 and the first evaporator 1 are sequentially arranged in the first air duct along the air flow direction. For example, the second evaporator 2 and the first evaporator 1 are straight plate heat exchangers, and the airflow direction may be perpendicular to the windward side of the first evaporator 1 and the second evaporator 2.
This embodiment sets gradually second evaporator 2 and first evaporator 1 along the air current direction, is suitable for dehumidification system, and dehumidification system's characteristics need just to reduce the temperature below the dew point temperature of air, so the business turn over wind difference in temperature of evaporimeter and condenser is all great, and the temperature that the refrigerant matches slides and can realize refrigerant and the little difference in temperature heat transfer of air, reduces the irreversible loss among the heat transfer process, and then promotes the efficiency. Meanwhile, the low-boiling point components, namely non-condensable gas, are reduced in the second condenser 4, so that the condensation heat transfer performance is facilitated; the evaporated gas is reduced in the second evaporator 2, the pressure loss is reduced, and the evaporation heat transfer performance is improved. Therefore, the embodiment can improve the heat exchange performance of the dehumidification system and can improve the energy efficiency of the system.
In some embodiments, the first condenser 3 and the second condenser 4 are disposed in the first air duct and are sequentially disposed downstream of the first evaporator 1 in the air flow direction. For example, the first condenser 3 and the second condenser 4 may be straight plate heat exchangers, and the airflow direction may be perpendicular to the windward side of the first condenser 3 and the second condenser 4.
The embodiment can realize the functions of dehumidification and reheating after refrigeration of the dehumidification system, so that the air outlet of the dehumidification system is in a comfortable range, and the use performance of the system is improved. From the air flow direction, the air to be dehumidified is firstly cooled by the second evaporator 2 (dry cooling process), then is dehumidified by the first evaporator 1 to become low-temperature low-humidity air (dehumidification process), is heated for the first time by the first condenser 3 to become medium-temperature low-humidity air (reheating process), and finally is changed into high-temperature low-humidity air (reheating process) by the second condenser 4. From the temperature of the refrigerant, the temperature of the second evaporator 2 is higher than that of the first evaporator 1, the temperature of the second condenser 4 is higher than that of the first condenser 3, the temperature change trend of the second condenser is consistent with that of the air, and if the heat transfer temperature difference between the refrigerant and the air is identical or similar everywhere through the optimal matching of the refrigerant temperature slippage and the air inlet and outlet temperature difference, the irreversible loss in the heat transfer process can be greatly reduced, and the system energy efficiency is improved.
In some embodiments, the mixed working medium refrigeration system further comprises a second air duct, the second air duct is independent from the first air duct, and at least one of the first condenser 3 and the second condenser 4 is arranged in the second air duct. The embodiment can realize heating in the independent second air channel according to requirements, and therefore, the air conditioner can be suitable for different occasions.
In one configuration, a first condenser 3 is provided in the first air path downstream of the first evaporator 1, and a second condenser 4 is provided in the second air path. The embodiment can realize reheating after dehumidification in the first air channel, so that the air outlet of the dehumidification system is in a comfortable range, the service performance of the system is improved, and heating can be realized in the independent second air channel.
In another structure, the mixed working medium refrigerating system further comprises a third air duct, the third air duct is mutually independent of the first air duct and the second air duct, the first condenser 3 is arranged in the second air duct, and the second condenser 4 is arranged in the third air duct. According to the embodiment, dehumidification can be realized in the first air channel, heating of the second air channel and the third air channel can be realized respectively, and heat exchange requirements of users on different rooms can be met more flexibly through the multiple air channels.
In yet another configuration, both the first condenser 3 and the second condenser 4 are disposed within the second air duct. The embodiment can realize dehumidification in the first air channel and can also realize the heating requirement of the second air channel with larger heat exchange quantity.
On the basis of the above embodiment, as shown in fig. 1, the mixed working medium refrigeration system of the present disclosure further includes: and the pressure regulating part 7 is arranged at a position where the first condensation branch 30 and the second condensation branch 40 are close to and communicated with the first evaporator 1, and is configured to balance the pressure of the first condensation branch 30 and the pressure of the second condensation branch 40. For example, the pressure adjusting member 7 may be a capillary tube, an electronic expansion valve, or a connecting tube with different tube diameters, or in short, a member capable of adjusting the resistance characteristics.
In some embodiments, as shown in fig. 3 and 4, the mixed refrigerant refrigeration system further comprises: the second throttling means 11, such as a capillary tube or an electronic expansion valve, is configured to adjust the dryness of the refrigerant in the gas-liquid separation device 6, i.e., to adjust the ratio of the gaseous refrigerant to the liquid refrigerant.
In this embodiment, by providing the second throttling element 11, the refrigerant flow and the evaporation temperature in the first evaporator 1 can be changed, and further, the inlet dryness of the gas-liquid separation device 6 is changed, the gas-liquid ratio in the gas-liquid separation device 6 is different when the dryness is different, and the component ratio of low boiling point and high boiling point in the gas and liquid of the mixed working medium is also changed in a phase equilibrium state, so that the purpose of adjusting the component separation is achieved. The component separation can directly affect the air suction state of the compressor, the unit volume refrigerating capacity of the circulation and the load change of the system.
In some embodiments, as shown in fig. 3, the second throttling element 11 is disposed on the first evaporation branch 10 and between the first outlet 1B and the refrigerant inlet 61 of the gas-liquid separation device 6.
This embodiment can change the refrigerant flow rate and the evaporation temperature in the first evaporator 1 by adjusting the pressure of the first outlet 1B of the first evaporator 1 to change the inlet dryness of the gas-liquid separation device 6 to adjust the component separation effect, thereby adapting to the load change of the system.
In other embodiments, as shown in fig. 4, the second throttling part 11 is disposed on the throttling branch 12 connected in parallel with the first evaporation branch 10, one end of the throttling branch 12 is connected to the pipeline between the first throttling part 8 and the first inlet 1A, and the other end is connected to the pipeline between the first outlet 1B and the refrigerant inlet 61.
This embodiment can change the refrigerant flow rate and the evaporation temperature in the first evaporator 1 by adjusting the pressure difference between the first inlet 1A and the first outlet 1B of the first evaporator 1 to change the inlet dryness of the gas-liquid separation device 6 to adjust the component separation effect, thereby adapting to the load change of the system.
Alternatively, the second throttling part 11 in fig. 3 and 4 may be provided at the same time.
In some embodiments, as shown in fig. 5, the mixed refrigerant refrigeration system further includes a heat recovery pipe 64, and the heat recovery pipe 64 is disposed in a lower region of the gas-liquid separation device 6 and is connected in series in the second condensation branch 40. That is, the second condensation branch 40 is heat-exchanged with the gas-liquid separation device 6, and then joins the first condensation branch 30 to enter the first evaporator 1.
In this embodiment, the heat recovery pipe 64 is connected in series in the second condensation branch 40, so that the component separation effect can be improved, the heat of the refrigerant is utilized to evaporate more low-boiling-point components in the liquid in the gas-liquid separation device 6 into gas, and the better separation of the high-boiling-point components and the low-boiling-point components is realized, so as to optimize the heat exchange effect. Moreover, since the outlet temperature of the second condenser 4 is higher than that of the first condenser 3, the heat recovery pipe 64 is connected in series in the second condensation branch 40, so that a better effect of improving component separation can be obtained.
Alternatively, the heat recovery pipe 64 may be connected in series in the first condensing branch 30, and the above-mentioned effects can be obtained.
As shown in fig. 6, the mixed refrigerant refrigerating system further includes a first heat regenerator 50 disposed between the pipe section of the second condensing branch 40 located at the fourth outlet 4B side and the pipe section of the second evaporating branch 20 located at the second outlet 2B side.
In the embodiment, the second condensation branch 4 and the second evaporation branch 2 exchange heat, that is, the refrigerant gas coming out of the second evaporator 20 is used for cooling the high-pressure liquid at the outlet of the second condenser 4, so that the refrigerant liquid is subcooled and the gas is overheated, the specific enthalpy of the refrigerant at the outlet of the second condenser can be reduced, the dryness of the refrigerant in the first evaporator 1 is reduced, and the energy efficiency of the system is further improved.
As shown in fig. 7, the mixed refrigerant refrigeration system further includes a second regenerator 60, which is disposed between the pipe section of the first condensing branch 30 located at the third outlet 3B and the pipe section of the first evaporating branch 10 located between the gaseous refrigerant outlet 62 and the first air inlet 51.
In the embodiment, the first condensation branch 3 and the first evaporation branch 1 exchange heat, that is, the refrigerant gas coming out of the first evaporator 10 is used for cooling the high-pressure liquid at the outlet of the first condenser 3, so that the refrigerant liquid is subcooled and the gas is superheated, the specific enthalpy of the refrigerant at the outlet of the first condenser can be reduced, the dryness of the refrigerant in the first evaporator 1 is reduced, and the energy efficiency of the system is further improved.
In some embodiments, as shown in fig. 1 to 7, the compression device 5 has a first compression chamber and a second compression chamber which are independent, the first compression chamber is provided with a first suction port 51 and a first discharge port 52, and the second compression chamber is provided with a second suction port 53 and a second discharge port 54. According to the embodiment, the double-suction double-exhaust compressor is adopted, and high and low boiling point components in the condensation process are separated to form different condensation temperatures, so that non-condensable gas in the condensation process is reduced, and the condensation heat transfer performance is improved.
Further, the second exhaust port may be provided with an oil return component 56, since the first exhaust port is exhausted through the inside of the compressor, the lubricating oil can return to the oil sump, and the first exhaust port 101 is a straight cylinder, and oil cannot return, so an oil return device is required to return the lubricating oil in the refrigerant to the oil sump.
In some embodiments, as shown in FIG. 8, compression device 5 comprises a first compressor 5A and a second compressor 5B, the first compressor 5A having a first suction port 51 and a first discharge port 52, the second compressor 5B having a second suction port 53 and a second discharge port 54. According to the embodiment, two paths of air suction and exhaust are realized by adopting two independent compressors, high and low boiling point components in the condensation process are separated to form different condensation temperatures, non-condensable gas in the condensation process is reduced, and the condensation heat transfer performance is improved.
Secondly, the disclosure also provides a dehumidifier and the mixed working medium refrigerating system of the embodiment.
Because the dehumidifier needs to reduce the temperature below the dew point temperature of air, the temperature difference between the inlet air and the outlet air of the evaporator and the condenser is large, the temperature slippage of the dehumidifier refrigerant matched with the temperature difference of the air can realize the small temperature difference heat exchange between the refrigerant and the air, reduce the irreversible loss in the heat exchange process and further improve the energy efficiency. Meanwhile, the low-boiling point components, namely non-condensable gas, are reduced in the second condenser 4, so that the condensation heat transfer performance is improved; the evaporated gas is reduced in the second evaporator 2, the pressure loss is reduced, and the evaporation heat transfer performance is improved. Therefore, the embodiment can improve the heat exchange performance of the dehumidification system and can improve the energy efficiency of the system.
In some embodiments, the mixed working medium refrigeration system further comprises a first air duct, and the second evaporator 2, the first evaporator 1, the first condenser 3 and the second condenser 4 are sequentially arranged in the first air duct along the air flow direction. For example, the second evaporator 2, the first evaporator 1, the first condenser 3 and the second condenser 4 are all straight plate heat exchangers, and the airflow direction may be perpendicular to the windward side of the first evaporator 1, the second evaporator 2, the first condenser 3 and the second condenser 4.
The embodiment can realize the functions of dehumidification and reheating after refrigeration of the dehumidification system, so that the air outlet of the dehumidification system is in a comfortable range, and the use performance of the system is improved. From the air flow direction, the air to be dehumidified is firstly cooled by the second evaporator 2 (dry cooling process), then is dehumidified by the first evaporator 1 to become low-temperature low-humidity air (dehumidification process), is heated for the first time by the first condenser 3 to become medium-temperature low-humidity air (reheating process), and finally is changed into high-temperature low-humidity air (reheating process) by the second condenser 4. Moreover, from the temperature of the refrigerant, the temperature of the second evaporator 2 is higher than that of the first evaporator 1, the temperature of the second condenser 4 is higher than that of the first condenser 3, the temperature change trend of the second condenser is consistent with that of the air, and if the heat transfer temperature difference between the refrigerant and the air is identical or similar everywhere through the optimal matching of the temperature slippage of the refrigerant and the air inlet and outlet temperature difference, the irreversible loss in the heat transfer process can be greatly reduced, and the energy efficiency of the system is improved.
The mixed working medium refrigerating system and the dehumidifier provided by the disclosure are introduced in detail above. The principles and embodiments of the present disclosure are explained herein using specific examples, which are set forth only to help understand the method and its core ideas of the present disclosure. It should be noted that, for those skilled in the art, it is possible to make several improvements and modifications to the present disclosure without departing from the principle of the present disclosure, and such improvements and modifications also fall within the scope of the claims of the present disclosure.
Claims (14)
1. The mixed working medium refrigerating system is characterized by comprising a first flow path and a second flow path, wherein the mixed working medium flows through the first flow path, the mixed working medium in the first flow path is rich in low-boiling-point components, the mixed working medium in the second flow path is rich in high-boiling-point components, the first flow path comprises a first evaporation branch (10) and a first condensation branch (30), the second flow path comprises a second evaporation branch (20) and a second condensation branch (40), and the mixed working medium refrigerating system comprises:
a compression device (5) having a first intake port (51) and a first exhaust port (52) communicating with each other, and a second intake port (53) and a second exhaust port (54) communicating with each other;
a gas-liquid separation device (6) having a refrigerant inlet (61), a gaseous refrigerant outlet (62), and a liquid refrigerant outlet (63), the gaseous refrigerant outlet (62) communicating with the first air intake (51);
the first evaporator (1) and the second evaporator (2) are respectively arranged on the first evaporation branch (10) and the second evaporation branch (20), a first outlet (1B) of the first evaporator (1) is communicated with the refrigerant inlet (61), a second inlet (2A) of the second evaporator (2) is communicated with the liquid refrigerant outlet (63), and a second outlet (2B) of the second evaporator (2) is communicated with the second air suction port (53); and
first condenser (3) and second condenser (4) are established respectively first condensation branch road (30) with on second condensation branch road (40), third import (3A) of first condenser (3) with first gas vent (52) intercommunication, fourth import (4A) of second condenser (4) with second gas vent (54) intercommunication, third export (3B) of first condenser (3) with fourth export (4B) of second condenser (4) join the back with first import (1A) intercommunication of first evaporimeter (1).
2. The mixed working medium refrigerating system according to claim 1, further comprising a first air duct, wherein the second evaporator (2) and the first evaporator (1) are sequentially arranged in the first air duct along an air flow direction.
3. A mixed working medium refrigerating system according to claim 2, wherein the first condenser (3) and the second condenser (4) are arranged in the first air duct and are arranged downstream of the first evaporator (1) in the air flow direction in sequence.
4. A mixed working medium refrigerating system according to claim 2, further comprising a second air duct, said second air duct being independent from said first air duct, at least one of said first condenser (3) and said second condenser (4) being provided in said second air duct.
5. The mixed refrigerant refrigeration system as set forth in claim 4,
the first condenser (3) is arranged in the first air channel and located at the downstream of the first evaporator (1), and the second condenser (4) is arranged in the second air channel; or
The mixed working medium refrigerating system further comprises a third air channel, the third air channel is independent from the first air channel and the second air channel, the first condenser (3) is arranged in the second air channel, and the second condenser (4) is arranged in the third air channel.
6. A mixed working medium refrigerating system according to any one of claims 1 to 5, further comprising a first throttling member (8) provided on the first evaporation branch (10) and located between the merging positions of the first inlet (1A) and the third outlet (3B) and the fourth outlet (4B).
7. The mixed working medium refrigerating system according to any one of claims 1 to 5, further comprising: and the pressure regulating part (7) is arranged at a position where the first condensation branch (30) and the second condensation branch (40) are close to the first evaporator (1) and communicated with each other, and is configured to balance the pressure of the first condensation branch (30) and the pressure of the second condensation branch (40).
8. The mixed working medium refrigerating system according to any one of claims 1 to 5, further comprising: a second throttling member (11) configured to adjust a ratio of the gaseous refrigerant to the liquid refrigerant in the gas-liquid separation device (6).
9. The mixed refrigerant refrigeration system as set forth in claim 8,
the second throttling part (11) is arranged on the first evaporation branch (10) and is positioned between the first outlet (1B) and the refrigerant inlet (61); and/or
The second throttling part (11) is arranged on a throttling branch (12) which is connected with the first evaporation branch (10) in parallel.
10. A mixed working medium refrigerating system according to any one of claims 1 to 5, further comprising a heat recovery pipe (64), wherein the heat recovery pipe (64) is arranged in the lower region of the gas-liquid separation device (6) and is connected in series in the second condensation branch (40).
11. The mixed working medium refrigerating system according to any one of claims 1 to 5,
the mixed working medium refrigerating system also comprises a first heat regenerator (50) which is arranged between the pipe section of the second condensation branch (40) on one side of the fourth outlet (4B) and the pipe section of the second evaporation branch (20) on one side of the second outlet (2B); and/or
The mixed working medium refrigerating system further comprises a second heat regenerator (60), and a pipe section arranged on one side of the third outlet (3B) of the first condensing branch (30) and a pipe section arranged between the gaseous refrigerant outlet (62) and the first air suction port (51) of the first evaporating branch (10) are arranged.
12. The mixed working medium refrigerating system according to any one of claims 1 to 5,
the compression device (5) is provided with a first compression cavity and a second compression cavity which are independent, the first compression cavity is provided with the first air suction port (51) and the first exhaust port (52), and the second compression cavity is provided with the second air suction port (53) and the second exhaust port (54); and/or
The compression device (5) includes a first compressor (5A) and a second compressor (5B), the first compressor (5A) having the first suction port (51) and the first discharge port (52), the second compressor (5B) having the second suction port (53) and the second discharge port (54).
13. A dehumidifier, characterized by further comprising a mixed working medium refrigeration system as claimed in any one of claims 1 to 12.
14. The dehumidifier of claim 13, wherein the mixed refrigerant refrigeration system further comprises a first air duct, and the second evaporator (2), the first evaporator (1), the first condenser (3) and the second condenser (4) are sequentially arranged in the first air duct along an air flow direction.
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