CN108800384B - Air conditioning system and air conditioner - Google Patents
Air conditioning system and air conditioner Download PDFInfo
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- CN108800384B CN108800384B CN201810686827.0A CN201810686827A CN108800384B CN 108800384 B CN108800384 B CN 108800384B CN 201810686827 A CN201810686827 A CN 201810686827A CN 108800384 B CN108800384 B CN 108800384B
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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
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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Abstract
The invention discloses an air conditioning system and an air conditioner, wherein the air conditioning system comprises: the system comprises a refrigerant pipeline, and a compressor, a first heat exchanger, a balance tank, a first throttling device, a flash evaporator and a second heat exchanger which are sequentially and circularly connected by the refrigerant pipeline; refrigerant in the refrigerant pipeline enters the balance tank through the first heat exchanger after being compressed by the compressor, at least part of the refrigerant in the balance tank enters the flash evaporator through the first throttling device, the refrigerant separates gaseous refrigerant and liquid refrigerant from the flash evaporator, the separated gaseous refrigerant enters the compressor through the air supplement outlet and the air supplement inlet, and the separated liquid refrigerant enters the compressor through the second heat exchanger. According to the technical scheme, the air conditioning system is additionally provided with the flash evaporator to improve the working energy efficiency of the compressor, and meanwhile, the balance tank is additionally arranged to solve the problem of low heat exchange efficiency caused by excessive liquid refrigerants in the first heat exchanger, so that the heating energy efficiency of the air conditioning system is improved.
Description
Technical Field
The invention relates to the technical field of air conditioning, in particular to an air conditioning system and an air conditioner with the same.
Background
As an energy-saving and environment-friendly heating technology, the heat pump air conditioner is more and more widely applied. However, in the case of the low environmental temperature in winter in the north, the heat exchange capacity of the outdoor unit is reduced, the return air volume of the normal return air port of the compressor is reduced, and the power of the compressor is reduced in the process of heating by using the heat pump air conditioner. The pressure difference of suction and exhaust of the compressor is increased, so that the circulation flow of a refrigerant in an air conditioning system is reduced, the heat provided by a heat pump air conditioner phase chamber is reduced, and the heating energy efficiency is reduced.
Disclosure of Invention
The invention mainly aims to provide an air conditioning system, aiming at improving the heating energy efficiency of the air conditioning system.
In order to achieve the above object, the present invention provides an air conditioning system, comprising: the system comprises a refrigerant pipeline, and a compressor, a first heat exchanger, a balance tank, a first throttling device, a flash evaporator and a second heat exchanger which are sequentially and circularly connected by the refrigerant pipeline;
the flash evaporator is provided with an air supply outlet, the compressor is provided with an air supply inlet, and the air supply outlet is communicated with the air supply inlet;
refrigerant in the refrigerant pipeline enters the balance tank through the first heat exchanger after being compressed by the compressor, at least part of the refrigerant in the balance tank enters the flash evaporator through the first throttling device, the refrigerant separates gaseous refrigerant and liquid refrigerant from the flash evaporator, the separated gaseous refrigerant enters the compressor through the air supplement outlet and the air supplement inlet, and the separated liquid refrigerant enters the compressor through the second heat exchanger.
Optionally, the calculation formula of the volume V of the balancing tank 40 is as follows: v is (1.5-1.7) × (m2-m 1)/rho;
m1 is the mass of the balance tank to be tested when the tank is empty; m2 is the total mass of the balance tank to be tested after the refrigerant is stored in the balance tank in the working process of the air conditioning system; and rho is the density of the saturated liquid refrigerant in the working process of the air-conditioning system.
Optionally, the volume of the balance tank is 30-40% of the total volume of the refrigerant in the system.
Optionally, the air conditioning system further comprises an air supply pipeline and an enthalpy increasing switch, the air supply pipeline is communicated with the air supply outlet and the air supply inlet, and the enthalpy increasing switch is installed on the air supply pipeline.
Optionally, the air conditioning system includes a plurality of flash evaporators, the plurality of flash evaporators are sequentially connected to the refrigerant pipeline between the first throttling device and the second heat exchanger, and the air make-up outlet of each flash evaporator is communicated with the air make-up inlet of the compressor.
Optionally, the first heat exchanger is a condenser and the second heat exchanger is an evaporator.
Optionally, the air conditioning system further includes a second throttling device, and the second structural device is installed in the refrigerant pipeline and located between the flash evaporator and the second heat exchanger.
Optionally, the first throttling device is an electronic expansion valve or a capillary tube;
and/or the second throttling device is an electronic expansion valve or a capillary tube.
Optionally, the compressor is a rotary compressor.
The invention further provides an air conditioner which comprises the air conditioning system.
In the heating circulation system of the technical scheme of the invention, the refrigerant in the refrigerant pipeline is compressed by the compressor to form a high-temperature high-pressure gaseous refrigerant, then the refrigerant is subjected to heat release by the first heat exchanger to form a high-temperature high-pressure liquid refrigerant, so that the indoor temperature is increased, and the high-temperature high-pressure liquid refrigerant passes through the first throttling device to form a medium-temperature medium-pressure gas-liquid mixed refrigerant. The flash evaporator positioned at the downstream of the first throttling device can reduce the pressure of the refrigerant and realize gas-liquid separation, the separated liquid refrigerant enters the compressor through the second heat exchanger, the compressor sucks the refrigerant vapor in the evaporator and the gaseous refrigerant separated by the flash evaporator, and the gaseous refrigerant separated by the flash evaporator plays a role in supplementing air to the compressor and is mixed and compressed with the low-pressure gas sucked by the compressor, so that the enthalpy increasing effect is realized, and the heating capacity at low temperature is improved.
Furthermore, because the external environment temperature is low, the pressure difference between the high-pressure side and the low-pressure side is large, and excessive refrigerants can be retained in the condenser.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic structural diagram of an embodiment of an air conditioning system according to the present invention;
fig. 2 is a pressure-enthalpy diagram during operation of the air conditioning system of fig. 1.
The reference numbers illustrate:
| reference numerals | Name (R) | Reference numerals | Name (R) |
| 100 | |
51 | First throttling means |
| 10 | Compressor with a compressor housing having a plurality of |
52 | Second throttling means |
| 11 | |
60 | Flash |
| 20 | |
70 | |
| 31 | |
71 | Enthalpy-increasing |
| 32 | |
80 | Four- |
| 40 | Balance tank |
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that all the directional indicators (such as up, down, left, right, front, and rear … …) in the embodiment of the present invention are only used to explain the relative position relationship between the components, the movement situation, etc. in a specific posture (as shown in the drawing), and if the specific posture is changed, the directional indicator is changed accordingly.
In addition, the descriptions related to "first", "second", etc. in the present invention are for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
Referring to fig. 1 and 2, an air conditioning system 100 is provided. The air conditioning system 100 is mainly a heating system of a heat pump air conditioner. The heating process of the heat pump air conditioner is the reverse process of refrigeration, and the flow direction of the refrigerant in the refrigerant pipeline 20 is changed through the four-way valve, so that the conversion between refrigeration and heating is realized.
In the heat pump air conditioner in the prior art, heat the operation in-process under the condition that ambient temperature is too low, inverter compressor 10 needs high frequency operation, the refrigerant flow of system promotes by a wide margin, nevertheless because outdoor ambient temperature is low, low pressure side pressure is very low, the high pressure side still keeps higher pressure, under this operating condition, a large amount of liquid refrigerant of system gathers in the high pressure side, it is too much to lead to liquid refrigerant in the condenser, the heat transfer area of condenser has been reduced, cause condensing pressure to increase, heat the efficiency and reduce.
The technical scheme of the invention provides an air conditioning system 100 applied to a heat pump air conditioner, wherein the air conditioning system 100 comprises: the system comprises a refrigerant pipeline 20, and a compressor 10, a first heat exchanger 31, a balance tank 40, a first throttling device 51, a flash evaporator 60 and a second heat exchanger 32 which are sequentially and circularly connected by the refrigerant pipeline 20; the circulating connection is that the refrigerant sequentially flows through the compressor 10, the first heat exchanger 31, the balance tank 40, the first throttling device 51, the flash evaporator 60 and the second heat exchanger 32 in the refrigerant pipeline 20, and the refrigerant after heat exchange by the second heat exchanger 32 further enters the compressor 10 for circulating compression under the guidance of the refrigerant pipeline 20.
The flash evaporator 60 is provided with an air supply outlet, the compressor 10 is provided with an air supply inlet 11, and the air supply outlet is communicated with the air supply inlet 11;
the refrigerant in the refrigerant pipeline 20 is compressed by the compressor 10 and then enters the balancing tank 40 through the first heat exchanger 31, at least part of the refrigerant in the balancing tank 40 enters the flash evaporator 60 through the first throttling device 51, the refrigerant separates a gaseous refrigerant and a liquid refrigerant in the flash evaporator 60, the separated gaseous refrigerant enters the compressor 10 through the air supplement outlet and the air supplement inlet 11, and the separated liquid refrigerant enters the compressor 10 through the second heat exchanger 32.
In the air conditioning system 100 of the present invention, the first heat exchanger 31 is a condenser, and the second heat exchanger 32 is an evaporator.
In the heating cycle system of the technical scheme of the invention, the refrigerant in the refrigerant pipeline 20 is compressed by the compressor 10 to form a high-temperature high-pressure gaseous refrigerant, then the refrigerant is released by the condenser to form a high-temperature high-pressure liquid refrigerant, the condenser is positioned indoors to raise the indoor temperature, and the high-temperature high-pressure liquid refrigerant passes through the first throttling device 51 to form a medium-temperature medium-pressure gas-liquid mixed refrigerant.
The flash evaporator 60 located at the downstream of the first throttling device 51 can reduce the pressure of the refrigerant and realize gas-liquid separation, the separated liquid refrigerant enters the compressor 10 after passing through the evaporator, the compressor 10 sucks the refrigerant vapor in the evaporator and the gaseous refrigerant separated by the flash evaporator 60, and the gaseous refrigerant separated by the flash evaporator 60 has the effect of supplementing air to the compressor 10 and is mixed and compressed with the low-pressure gas sucked by the compressor 10, so that the enthalpy increasing effect is realized, and the heating capacity at low temperature is improved.
Further, because the external environment temperature is low, the pressure difference between the high-pressure side and the low-pressure side is large, and excessive refrigerants can be retained in the condenser, the technical scheme of the invention is that the balance tank 40 is additionally arranged on the refrigerant pipeline 20, when the liquid refrigerants on the high-pressure side are excessive, the excessive liquid refrigerants can be automatically stored in the balance tank 40, and part of the refrigerants are subjected to a pressure reduction process through the first throttling device 51, so that the problem of low heat exchange efficiency caused by excessive liquid refrigerants in the first heat exchanger 31 is solved, and the heating energy efficiency of the air-conditioning system 100 is improved.
In the embodiment of the invention, the calculation formula of the volume V of the balancing tank 40 is as follows: v is (1.5-1.7) × (m2-m 1)/rho;
m1 is the mass of the balance tank to be tested when the tank is empty; m2 is the total mass of the balance tank to be tested after the refrigerant is stored in the balance tank in the working process of the air conditioning system; rho is the density of the saturated liquid refrigerant in the working process of the air conditioning system. The units of m1 and m2 are kg, and the unit of rho is kg/m 3.
The above example is a selection of the volume of the equalization tank 40. In the process, the balance tank to be tested is firstly used as the balance tank 40 to be connected to the refrigerant pipeline 20, namely, only the balance tank to be tested is installed between the first heat exchanger 31 and the first throttling device 51, understandably, in order to accurately obtain an experimental result, the volume of the balance tank to be tested is selected to be slightly larger, and the volume of the refrigerant to be predicted to be stored in the balance tank to be tested in the working process of the air conditioning system can be at least stored. The balance tank to be tested comprises a tank body and a tank neck communicated with the tank body and a refrigerant pipeline 20, wherein an on-off switch is arranged on the tank neck. The on-off switch may be used to control whether the balancing tank 40 is operated and to facilitate testing of the balancing tank 40.
The mass of the balance tank to be tested when the tank is empty is m1, when the outdoor temperature is 7 ℃, the indoor temperature is controlled to be 20 ℃, the balance tank to be tested is not installed to perform a performance matching experiment, and the performance of the system is adjusted to reach the best state. And then installing a balance tank to be tested with an on-off switch between the first heat exchanger 31 and the first throttling device 51 for performance matching experiment, controlling the indoor temperature to be 20 ℃ under the working condition when the outdoor temperature is-20 ℃, turning on the on-off switch, adjusting the system performance to be in the best state, then turning off the on-off switch, taking down the balance tank to be tested, and weighing to obtain the total mass of the balance tank to be tested to be m 2. (m2-m1) is the amount of cold medium in the equalization tank to be tested, and ρ is the density of the saturated liquid refrigerant at-20 ℃.
After the test, the balancing tank 40 with the volume V is selected to be installed between the first heat exchanger 31 and the first throttling device 51, so that the heating energy efficiency of the air conditioning system 100 can be improved.
Specifically, the coefficient range of 1.5 to 1.7 is a result obtained through multiple tests, and in the test process, the air conditioning system can be placed in a severe environment with obvious changes, so that a reliable test value range can be obtained. In practical application, the coefficient of the selected volume of the balancing tank 40 needs to be greater than 1.5 to ensure that the balancing tank 40 can meet the use requirement when the air conditioning system is in a severe operating environment, and it can be understood that the coefficient can also be greater than 1.7 to ensure that the balancing tank can be used more reliably. According to the limitation of the installation space and the actual operation requirement of the air conditioning system, a certain error range is selected and reserved for the volume of the balance tank, and the optimal volume range of the balance tank 40 can be obtained by controlling the coefficient within the range of 1.5-1.7.
The coefficient of 1.5-1.7 in the above test can ensure that the volume of the selected balancing tank 40 is larger than the volume of the actual storage refrigerant, so as to improve the pressure balancing capability of the balancing tank 40 in the actual application process, and make the structure of the balancing tank 40 in the air conditioning system 100 compact, and not cause resource waste.
After testing, the volume of the balance tank 40 is 30-40% of the total volume of the refrigerant in the system. The total volume of the refrigerant is the total volume of the refrigerant injected into the refrigerant pipeline 20 and all components connected by the refrigerant pipeline 20 in the air conditioning system 100 during the production of the air conditioner.
It can be understood that, in order to prevent the configuration of the air conditioning system 100 during the installation process from being unreasonable due to the over-sized balance tanks 40, in an embodiment, the number of the balance tanks 40 is multiple, and the plurality of the balance tanks 40 are connected to the refrigerant pipeline 20 in sequence and in parallel. A plurality of small-sized balancing tanks 40 can be selected according to the practical application condition and are sequentially connected to the refrigerant pipeline 20 side by side, so that the air conditioning system 100 is more compactly installed in the air conditioner, the overall structure of the air conditioner is smaller, and the application range is wider.
Further, the air conditioning system further comprises an air supply pipeline 70 and an enthalpy increasing switch 71, the air supply pipeline 70 is communicated with the air supply outlet and the air supply inlet 11, and the enthalpy increasing switch 71 is installed on the air supply pipeline 70.
The enthalpy increasing switch 71 is an on-off valve for controlling whether to supplement air to the compressor 10, and when the working efficiency of the compressor 10 is high, the enthalpy increasing switch 71 can be selectively closed to stop the use of the flash evaporator 60.
The flash evaporator 60 is embodied as a flash tank, and since the boiling point of the fluid is related to the pressure, the fluid can be rapidly depressurized in the process of entering the flash tank, so that the fluid can be rapidly boiled and vaporized in the flash tank, and gas-liquid separation is performed. In order to further improve the working efficiency of the compressor 10 in the air conditioning system 100, a plurality of flash evaporators 60 are disposed in the air conditioning system 100, the plurality of flash evaporators 60 are sequentially connected to the refrigerant pipeline 20 between the first throttling device 51 and the second heat exchanger 32, and an air supply outlet of each flash evaporator 60 is communicated with the air supply inlet 11 of the compressor 10.
Specifically, when two flash evaporators 60 are provided in the system, the refrigerant passing through the first throttling device 51 enters one flash evaporator 60 to perform first-stage pressure reduction and first-stage gas-liquid separation, the refrigerant gas after part of the refrigerant is gasified in the process enters the compressor 10 through the gas supply outlet of the flash evaporator 60, the refrigerant liquid in the flash evaporator 60 in the process enters the next flash evaporator 60 through the refrigerant pipeline 20 to perform second-stage pressure reduction and second-stage gas-liquid separation, the refrigerant gas after part of the refrigerant is gasified in the process enters the compressor 10 through the gas supply outlet of the flash evaporator 60, and the refrigerant liquid in the flash evaporator 60 in the process enters the downstream second heat exchanger 32 through the refrigerant pipeline 20.
It is understood that in order to improve the efficiency of the compressor 10, a plurality of flash evaporators 60 may be provided in the above manner to optimize the installation structure of the air conditioning system 100, or only one flash evaporator 60 having a large volume may be provided to simplify the installation process.
When the air conditioning system 100 has a plurality of flash evaporators 60, the air supply outlet of each flash evaporator 60 is communicated with the air supply inlet 11 of the compressor 10 through an air supply pipeline, and specifically, a multi-way valve is installed at the air supply inlet 11 of the compressor 10 to communicate with the plurality of air supply pipelines. Preferably, each vapor replenishing pipeline is provided with an enthalpy increasing valve, and further, the opening degree of the enthalpy increasing valve can be adjusted according to the use condition, so that the flow and the pressure of the gas in the vapor replenishing process of the compressor 10 can be adjusted by each flash evaporator 60.
Further, the air conditioning system further includes a second throttling device 52, and the second throttling device 52 is installed in the refrigerant pipeline 20 and is located between the flash evaporator 60 and the second heat exchanger 32.
The second throttling device 52 can further decompress the refrigerant in the refrigerant pipeline 20, so that the refrigerant is more sufficiently liquefied, the temperature of the refrigerant entering the second heat exchanger 32 is low, and the refrigerant can exchange heat more sufficiently with the outside air, thereby improving the heating efficiency of the air conditioning system 100.
In the technical scheme of the invention, the first throttling device 51 is an electronic expansion valve or a capillary tube;
and/or the second throttling device 52 is an electronic expansion valve or a capillary tube. That is, the first throttling device 51 and the second throttling device 52 may be electronic expansion valves at the same time, may also be capillary tubes at the same time, and of course, may also be electronic expansion valves or capillary tubes respectively. The corresponding selection can be carried out according to the actual use condition.
The compressor 10 is an enhanced vapor injection compressor 10, specifically a rotor type compressor, and may also be a scroll compressor 10. The compressor 10 has two inlets and one outlet. An air inlet is communicated with the second heat exchanger 32, and the low-pressure gaseous refrigerant formed by the second heat exchanger 32 enters the compressor 10 through the refrigerant pipeline 20; the other inlet is the above-mentioned make-up gas inlet, and the gaseous high-pressure refrigerant separated by the flash evaporator 60 enters the compressor 10 through the make-up gas inlet. The compressor 10 compresses the low-pressure gas sucked from the evaporator and the higher-pressure gas introduced from the flash evaporator 60 together into a high-temperature and high-pressure gaseous refrigerant, and discharges the high-temperature and high-pressure gaseous refrigerant to the refrigerant pipeline 20 through the gas outlet, thereby improving the energy efficiency of the compressor 10.
The refrigerant pipeline 20 is provided with a four-way valve 80, and the four-way valve 80 connects an air inlet and an air outlet of the compressor 10 to the refrigerant pipeline. The air conditioning system is applied to a heat pump air conditioner which can perform refrigeration or heating, and the flow direction of a refrigerant in the refrigerant pipeline 20 is changed by adjusting the four-way valve 80 so as to realize the switching between refrigeration and heating.
The present invention further provides an air conditioner (not shown), the air conditioner includes an air conditioning system 100, the specific structure of the air conditioning system 100 refers to the above embodiments, and since the air conditioner employs all technical solutions of all the above embodiments, at least all beneficial effects brought by the technical solutions of the above embodiments are achieved, and details are not repeated herein. The air conditioner is a heat pump air conditioner.
The air conditioner is provided with the air conditioning system 100, so that the heating energy efficiency ratio of the air conditioner under the low temperature condition is improved, and the normal heating of the air conditioner under the outdoor temperature of-25 ℃ is ensured. When the outdoor temperature is not lower than-20 ℃, the heating capacity is not less than the nominal heating capacity.
When the outdoor temperature is-12 ℃, and the indoor temperature is adjusted to 20 ℃, the heating energy efficiency ratio of the air conditioner can reach more than 3.60; when the outdoor temperature is-20 ℃ and the indoor temperature is adjusted to 20 ℃, the heating energy efficiency ratio of the air conditioner can reach more than 2.00, and the air conditioner is more economical and energy-saving than a common heating mode.
Figure 2 shows a cyclic pressure-enthalpy diagram (p-h diagram) of the operation of the air conditioning system. The ordinate p represents the pressure and the abscissa h represents the specific enthalpy. The arch-shaped curve represents the states of all saturated liquid refrigerants and saturated gaseous refrigerants of the refrigerant, and the highest point on the curve is a critical point and is a boundary point of the saturated gaseous refrigerants and the saturated liquid refrigerants. The left curve is a saturated liquid refrigerant line, and the right curve is a saturated gaseous refrigerant line. The area in the arch-shaped line is a two-phase area, the area on the left of the saturated liquid refrigerant line is a supercooled liquid area, the area on the right of the saturated gaseous refrigerant line is a superheated vapor area, and the area above the critical point is a supercritical area. Wherein, B is a circulating pressure-enthalpy diagram without adding a flash evaporator and a balance tank, and A is the circulating pressure-enthalpy diagram with the flash evaporator and the balance tank.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention, and all modifications and equivalents of the present invention, which are made by the contents of the present specification and the accompanying drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (9)
1. An air conditioning system, characterized in that the air conditioning system comprises: the system comprises a refrigerant pipeline, and a compressor, a first heat exchanger, a balance tank, a first throttling device, a flash evaporator and a second heat exchanger which are sequentially and circularly connected by the refrigerant pipeline;
the flash evaporator is provided with an air supply outlet, the compressor is provided with an air supply inlet, and the air supply outlet is communicated with the air supply inlet;
refrigerant in a refrigerant pipeline enters the balance tank through the first heat exchanger after being compressed by the compressor, at least part of the refrigerant in the balance tank enters the flash evaporator through the first throttling device, the refrigerant separates gaseous refrigerant and liquid refrigerant from the flash evaporator, the separated gaseous refrigerant enters the compressor through the air supplement outlet and the air supplement inlet, and the separated liquid refrigerant enters the compressor through the second heat exchanger;
the calculation formula of the volume V of the balance tank is as follows: v is (1.5-1.7) × (m2-m 1)/rho;
m1 is the mass of the balance tank to be tested when the tank is empty; m2 is the total mass of the balance tank to be tested after the refrigerant is stored when the performance of the air conditioning system reaches the optimal state; and rho is the density of the saturated liquid refrigerant in the working process of the air-conditioning system.
2. The air conditioning system as claimed in claim 1, wherein the volume of the balancing tank is 30-40% of the total volume of refrigerant in the system.
3. The air conditioning system as claimed in claim 1 or 2, further comprising an air supplement line and an enthalpy increasing switch, wherein the air supplement line communicates the air supplement outlet and the air supplement inlet, and the enthalpy increasing switch is installed on the air supplement line.
4. The air conditioning system as claimed in claim 3, wherein the air conditioning system comprises a plurality of flash evaporators, the plurality of flash evaporators are sequentially connected to the refrigerant pipeline between the first throttling device and the second heat exchanger, and the air make-up outlet of each flash evaporator is communicated with the air make-up inlet of the compressor.
5. The air conditioning system of claim 1, wherein the first heat exchanger is a condenser and the second heat exchanger is an evaporator.
6. The air conditioning system as claimed in claim 1, further comprising a second throttling device installed in the refrigerant pipeline and located between the flash evaporator and the second heat exchanger.
7. The air conditioning system as claimed in claim 6, wherein the first throttling means is an electronic expansion valve or a capillary tube;
and/or the second throttling device is an electronic expansion valve or a capillary tube.
8. The air conditioning system of claim 1, wherein the compressor is a rotary compressor.
9. An air conditioner characterized in that it comprises an air conditioning system as claimed in any one of claims 1 to 8.
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| CN201810686827.0A CN108800384B (en) | 2018-06-27 | 2018-06-27 | Air conditioning system and air conditioner |
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| CN201810686827.0A CN108800384B (en) | 2018-06-27 | 2018-06-27 | Air conditioning system and air conditioner |
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| CN109442637A (en) * | 2018-11-19 | 2019-03-08 | 珠海格力节能环保制冷技术研究中心有限公司 | A kind of Gas-supplying enthalpy-increasing system and its control method |
| CN109631257B (en) * | 2018-12-14 | 2021-06-15 | 广东Tcl智能暖通设备有限公司 | Air conditioner and control method and control device thereof |
| CN110486967A (en) * | 2019-08-27 | 2019-11-22 | 珠海凌达压缩机有限公司 | A kind of air-conditioning system and its control method |
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