Refrigerant composition and application thereof

Abstract

The invention provides a refrigerant composition and application thereof. The refrigerant composition provided by the invention comprises the following components in percentage by weight based on the total mass of the refrigerant composition: 52 to 62 percent of 1, 1, 1, 2-tetrafluoroethane, 32 to 40 percent of difluoromethane and 4 to 8 percent of carbon dioxide, and the refrigerant composition is a non-azeotropic composition. The refrigerant composition disclosed by the invention is suitable for small-air-volume heat dissipation (the heat dissipation air volume is smaller than 500m < 3 > / h) and high-environment-temperature (higher than 35 DEG C) scenes.

Description

Technical Field

[0001] The invention belongs to the technical field of refrigerants, and in particular relates to a refrigerant composition and application thereof. Background Art

[0002] For air-conditioning products with a small heat dissipation volume, the heat in the condenser cannot be discharged quickly due to the small heat dissipation volume, which will cause heat accumulation. At the same time, insufficient air volume will cause the heat exchange efficiency on the condenser surface to decrease, the heat dissipation efficiency of the condenser to decrease, and the condensation temperature to increase. The condenser cannot effectively condense the refrigerant from gas to liquid. In a high-temperature environment, the outside temperature is already very high, and the high-temperature environment makes it difficult for the condenser to transfer heat to the surrounding air, making it more difficult for the condenser to dissipate heat, and the condensation temperature to rise. The high outside temperature requires a higher condensation temperature to complete the heat discharge. Therefore, for air-conditioning products with a small heat dissipation volume or room air conditioners in a high-temperature environment, in order to ensure the cooling capacity, a higher condensation temperature is often required when the system is running. Under the restrictions of air volume or ambient temperature, a higher condensation temperature becomes a necessary condition for maintaining the flow of refrigerant and the operation of the system.

[0003] However, a higher condensing temperature means that the exhaust temperature and pressure of the compressor will increase. Appropriate system components (such as compressors and condensers) need to be designed to withstand higher temperatures and pressures to prevent the system from overheating or damage. While ensuring the reliability of the system, the selection of refrigerants is very critical. It is necessary to select refrigerants that are suitable for stable operation under high temperature and high pressure to ensure the long-term reliable operation of the system. From the perspective of refrigerants, R22's better thermodynamic properties and safety can meet the above requirements, but it has a destructive effect on the ozone layer (ODP>0). According to the requirements of the Montreal Protocol, R22 is facing reduction or elimination worldwide. The current mainstream R410A and R32 have problems with excessive system pressure and exhaust temperature when used in the above scenarios. Considering the reliability of equipment operation, a higher condensing temperature cannot be achieved, resulting in a decrease in refrigeration capacity. In addition, R32 is a flammable refrigerant and should not be used in some special occasions such as kitchens. Although R134a refrigerant can achieve a higher condensing temperature, its volumetric cooling capacity is small, and the system size needs to be increased.

[0004] Therefore, the choice of refrigerant is a key factor in refrigeration system design and performance optimization, and finding a new mixed refrigerant that meets performance requirements, environmental protection requirements and safety requirements has become an important challenge in the current refrigeration technology field. It is necessary to develop a new refrigerant that, when used in the above scenarios, has performance (volume cooling capacity, cooling EER) close to R22 or better, and an ODP (Ozone Depletion Potential) of 0. In addition, the system has a reasonable condensing pressure (<4MPa) and exhaust temperature (<110℃) when running. Summary of the invention

[0005] The present invention aims to solve at least one of the above-mentioned technical problems existing in the prior art. To this end, the present invention provides a refrigerant composition suitable for small air volume heat dissipation or high ambient temperature scenarios, the refrigerant composition can replace R22, has better energy efficiency than R32, and has an ODP (Ozone Depletion Potential) of 0.

[0006] The invention also provides a heat exchange system.

[0007] The invention also provides a device for refrigeration.

[0008] The invention also provides a device for heating.

[0009] A first aspect of the present invention provides a refrigerant composition, which comprises, based on the total mass of the refrigerant composition, 52wt%-62wt% of 1,1,1,2-tetrafluoroethane, 32wt%-40wt% of difluoromethane and 4wt%-8wt% of carbon dioxide, wherein the refrigerant composition is a non-azeotropic composition.

[0010] One of the technical solutions of the present invention regarding the refrigerant composition has at least the following beneficial effects:

[0011] The refrigerant composition of the present invention should have a safety level of A1 or A2L. The refrigerant composition is a non-azeotropic composition, which can boil or condense in a wide temperature range under constant pressure conditions, thereby generating temperature glide in the evaporator or condenser. Since the non-azeotropic mixed refrigerant has temperature glide during phase change, it can cooperate with the temperature gradient of the cooling medium to achieve better heat exchange. This feature combined with a multi-row countercurrent heat exchanger can reduce irreversible losses in the heat exchange process and improve system energy efficiency. The refrigerant composition of the present invention is suitable for small air volumes (heat dissipation air volume less than 500m 3 / h) heat dissipation or high ambient temperature (above 35°C), specifically:

[0012] The safety level of the refrigerant composition is A1 or A2L, which means it is a low-toxic, non-flammable or low-flammable refrigerant with low safety risks to humans and the environment, and is suitable for various application scenarios.

[0013] The refrigerant composition is a non-azeotropic composition, which means that its components can boil or condense separately under certain conditions without forming a fixed boiling point. This characteristic allows the refrigerant to produce temperature glide in the evaporator or condenser, helping to reduce irreversible losses in the heat exchange process.

[0014] The temperature glide characteristics of the refrigerant composition can be combined with a multi-row counter-flow heat exchanger to help reduce irreversible losses in the heat exchange process. This means that the system loses less energy during the energy conversion process, thereby improving the energy efficiency of the system.

[0015] The refrigerant composition also has a relatively high condensation temperature, which is above 52° C., for example, above 65° C. When the heat dissipation air volume of the condenser is small, due to the large temperature difference between the condenser and the ambient temperature, the small air volume can also achieve a good heat dissipation effect of the condenser and improve the refrigeration capacity; when used in a high temperature environment, the condenser and the ambient temperature still maintain a certain temperature difference, and high temperature refrigeration can be achieved.

[0016] The refrigerant composition of the present invention has a lower flammability than R32 (i.e., difluoromethane) because both R134a (i.e., 1,1,1,2-tetrafluoroethane) and R744 (i.e., CO2) are non-flammable.

[0017] Taking the above advantages into consideration, the refrigerant composition of the present invention can improve the energy efficiency of the system when used in scenarios with low air volume heat dissipation and high ambient temperature. By reducing energy loss, the system can achieve refrigeration more effectively, reduce energy consumption and reduce operating costs. The refrigerant composition of the present invention also has the advantages of low toxicity or low flammability.

[0018] According to some embodiments of the present invention, the mass percentage of 1,1,1,2-tetrafluoroethane can be, for example, 52wt%, 52.5wt%, 53wt%, 53.5wt%, 54wt%, 54.5wt%, 55wt%, 55.5wt%, 56wt%, 56.5wt%, 57wt%, 57.5wt%, 58wt%, 58.5wt%, 59wt%, 59.5wt%, 60wt%, 60.5wt%, 61wt%, 61.5wt%, 62wt%, any one of the values ​​or a range formed by any two of them.

[0019] According to some embodiments of the present invention, the mass percentage of difluoromethane can be, for example, 32wt%, 32.5wt%, 33wt%, 33.5wt%, 34wt%, 34.5wt%, 35wt%, 35.5wt%, 36wt%, 36.5wt%, 37wt%, 37.5wt%, 38wt%, 38.5wt%, 39wt%, 39.3wt%, 40wt%, any one of the values ​​or a range formed by any two of them.

[0020] According to some embodiments of the present invention, the mass percentage of carbon dioxide can be, for example, 2wt%, 2.5wt%, 3wt%, 3.5wt%, 4wt%, 4.5wt%, 5wt%, 5.5wt%, 6wt%, 6.5wt%, 7wt%, 7.5wt%, 8wt% or any value selected from the group consisting of any two of them.

[0021] According to some embodiments of the present invention, the refrigerant composition comprises: 58 wt%-62 wt% of 1,1,1,2-tetrafluoroethane, 32 wt%-36 wt% of difluoromethane and 4 wt%-7 wt% of carbon dioxide.

[0022] Selecting the above refrigerant composition can make the safety level of the refrigerant reach A1, further reduce the exhaust temperature and condensing pressure, and increase the relative volumetric cooling capacity and temperature glide, which is more suitable for scenarios with small air volume heat dissipation or high ambient temperature.

[0023] According to some embodiments of the present invention, under the operating conditions of an evaporating temperature of 13°C and a condensing temperature of 65°C, the exhaust temperature of the refrigerant composition is less than 107.5°C, the condensing pressure is less than 3.7 MPa, and the temperature glide under the condensing pressure is greater than 6.5°C.

[0024] The condensing temperature of the refrigerant composition refers to the average value of the dew point temperature and the bubble point temperature under the corresponding pressure (condensing pressure); the evaporation temperature of the refrigerant composition refers to the average value of the dew point temperature and the bubble point temperature under the corresponding pressure (evaporation pressure).

[0025] Lower exhaust temperature and condensing pressure usually means that the system operates in a more stable state. This can reduce the failure rate of the system and reduce the need for maintenance and repair in the long run.

[0026] In addition, under given working conditions, a higher temperature glide means that the refrigerant better matches the air temperature during the phase change heat exchange process, which helps to improve the energy efficiency of the system. Under the working condition of a condensing temperature of 65°C, the temperature glide of the refrigerant composition is 6.5 to 9.5°C. If the temperature glide is too low, the countercurrent heat exchange effect is not obvious.

[0027] A second aspect of the present invention provides a heat exchange system, comprising the refrigerant composition of the present invention, and:

[0028] a compressor for compressing the refrigerant composition;

[0029] a condenser connected to the compressor and used to condense the compressed refrigerant composition;

[0030] a throttling element connected to the condenser and used to reduce the pressure of the condensed refrigerant composition;

[0031] The evaporator has one end connected to the throttling element and the other end connected to the compressor, and is used for evaporating the low-pressure refrigerant composition.

[0032] One of the technical solutions of the present invention regarding the heat exchange system has at least the following beneficial effects:

[0033] Since the safety level of the refrigerant composition is A1, it has the characteristics of low toxicity and non-flammability, so the safety risk of the heat exchange system during operation is low, which is suitable for various application scenarios and ensures the safety of the system. Furthermore, the refrigerant composition is a non-azeotropic composition, which can boil or condense in a wide temperature range under constant pressure conditions, thereby generating temperature glide, which helps to improve the refrigeration efficiency of the system. This means that the heat exchange system can operate effectively in a wider temperature range and can still maintain a high refrigeration capacity at high ambient temperatures.

[0034] In summary, the heat exchange system containing the refrigerant composition of the present invention can improve the refrigeration capacity and energy efficiency while ensuring the safety of the system, thereby providing users with a more reliable and efficient heat exchange solution.

[0035] According to some embodiments of the present invention, the heat exchange system also includes a first heat exchange device, which uses a first medium to cool the condenser. The condenser includes a plurality of rows of first heat exchange tubes arranged and sequentially connected along the flow direction of the first medium. The refrigerant composition enters the condenser from the first heat exchange tube located downstream in the flow direction of the first medium, and flows out of the condenser from the first heat exchange tube located upstream in the flow direction of the first medium.

[0036] The temperature glide characteristics of the refrigerant composition combined with the multi-row countercurrent condenser reduce irreversible losses in the heat exchange process, thereby improving the energy efficiency of the system. By reducing energy losses, the system can achieve refrigeration more efficiently, reduce energy consumption and reduce operating costs. With the multi-row countercurrent condenser, heat can be dissipated more effectively. The countercurrent design makes the condenser more efficient in heat exchange, thereby achieving more effective heat dissipation.

[0037] The multi-row countercurrent condenser can use energy more efficiently and reduce the energy consumption of the system. This helps save energy and reduce carbon emissions, thereby reducing the operating costs of the system and reducing the adverse impact on the environment. The heat exchange system adopts a multi-row countercurrent condenser design, which can also improve the stability of the system. The countercurrent condenser can better cope with the changes in heat load under different working conditions and maintain the stable operation of the system.

[0038] The first medium may include at least one of air and water. The first heat exchange device may include a fan for driving air flow or a pump for driving water flow.

[0039] According to some embodiments of the present invention, the number of the first heat exchange tubes is at least 2 rows, preferably at least 3 rows, and more preferably 4 to 10 rows.

[0040] The number of rows of the first heat exchange tubes may be at least two, such as 2 rows, 3 rows, 4 rows, 5 rows, 6 rows, 7 rows, 8 rows, 9 rows, 10 rows, etc. The more rows there are, the better the condensation heat exchange effect is, and the temperature glide characteristics of the refrigerant composition can be better utilized in conjunction with the temperature gradient of the heat dissipation medium for heat exchange. To avoid excessive flow resistance of the first medium, the number of rows of the first heat exchange tubes is not more than 10 rows.

[0041] According to some embodiments of the present invention, the first medium includes air, and the air volume generated by the air flow is less than 500m 3 / h.

[0042] The first heat exchange device is a heat dissipation device with a small air volume. Since the condensation temperature of the refrigerant combination is relatively high, it has a temperature glide characteristic and cooperates with the countercurrent multi-row heat exchanger. It works under the condition of small heat dissipation air volume and can maintain a good heat dissipation effect even under the condition of small air volume. When the heat dissipation air volume of the condenser is small, the condenser needs to be set to multiple rows, which can be no less than 4 rows. The refrigerant and air are arranged in a countercurrent form to better form a ladder heat exchange.

[0043] The cooling air volume is small (<500m 3 / h) air-conditioning products, including but not limited to room air conditioners and mobile air conditioners that use ducts to exhaust heat, or room air conditioners in high temperature environments, such as T3 climate type (high temperature climate, maximum temperature 52°C) and higher temperatures specified in GB / T7725.

[0044] According to some embodiments of the present invention, the first heat exchange device further comprises an exhaust pipe, the exhaust pipe is used to exhaust the air, and the diameter of the exhaust pipe is ≤120 mm. Preferably, the diameter of the exhaust pipe is ≥50 mm and ≤120 mm.

[0045] It is understandable that the condenser of the heat exchange system needs small air volume to dissipate heat in some scenarios due to the limitation of the installation space, installation location or installation method of the heat exchange system. Small air volume heat dissipation usually has a small ventilation cross-sectional area and a small exhaust pipe cross-sectional size. The use of multi-row countercurrent condensers can improve the heat exchange efficiency while making more effective use of limited space, which makes the system more flexible in installation and layout and is suitable for places with limited space or requiring compact design. From the perspective of construction and air volume, the diameter of the exhaust pipe is preferably greater than or equal to 50 mm.

[0046] According to some embodiments of the present invention, the heat exchange system also includes a second heat exchange device, which uses a second medium to exchange heat with the evaporator, and the evaporator includes a plurality of rows of second heat exchange tubes arranged along the flow direction of the second medium and connected in sequence, and the refrigerant composition enters the evaporator from the second heat exchange tubes located downstream in the flow direction of the second medium, and flows out of the evaporator from the second heat exchange tubes located upstream in the flow direction of the second medium.

[0047] The temperature glide characteristics of the refrigerant composition during evaporation are combined with a multi-row countercurrent evaporator to reduce irreversible losses in the heat exchange process, thereby improving the energy efficiency of the system. By reducing energy losses, the system can more effectively increase cooling capacity, reduce energy consumption and reduce operating costs. With a multi-row countercurrent evaporator, heat exchange can be more efficient.

[0048] According to some embodiments of the present invention, the number of the second heat exchange tubes is at least 2 rows, preferably 2 to 10 rows.

[0049] The second medium may be at least one of air and water. The second heat exchange device may include a fan for driving air flow or a pump for driving water flow.

[0050] The number of rows of the second heat exchange tubes may be at least two, such as 2 rows, 3 rows, 4 rows, 5 rows, 6 rows, 7 rows, 8 rows, 9 rows, 10 rows, etc. To avoid excessive flow resistance of the second medium, the number of rows of the second heat exchange tubes is not greater than ten. Usually, the evaporator is used for heat exchange with indoor air for cooling, and the area of ​​the air outlet opposite to the evaporator is relatively large, and the number of rows of the second heat exchange tubes may be less than the number of rows of the first heat exchange tubes.

[0051] According to some embodiments of the present invention, the condenser is designed to operate under the condition that the ambient temperature is higher than 35°C.

[0052] The condenser using the refrigerant composition of the present invention and the countercurrent multi-row method can work effectively under the condition that the ambient temperature is higher than 35°C, ensuring that the system can still maintain high heat exchange efficiency in a high temperature environment and avoid poor heat exchange caused by excessively high ambient temperature. In a high temperature environment, the temperature of the refrigerant composition of the present invention remains higher than the ambient temperature, enhancing the stability of the system, ensuring that long-term operation is not affected by ambient temperature fluctuations, and reducing the failure rate.

[0053] The condenser is designed to work under the condition of high ambient temperature above 35℃. This design is suitable for places that need to work in high temperature environment, such as industrial equipment cooling, server room, kitchen equipment, etc., and can meet the heat dissipation requirements in various special environments. The condenser at high ambient temperature can efficiently exchange heat, improve the overall refrigeration efficiency, and ensure stable refrigeration effect in high temperature environment. In addition, the condenser can be designed to take into account the high temperature operating conditions, use more heat-resistant and efficient materials and technologies, enhance the reliability of the system, and be able to operate stably in harsh environments. Despite working in a high temperature environment, the condenser can maintain efficient heat dissipation performance, thereby reducing the load of the compressor, reducing the energy consumption of the system, and achieving energy saving effects. The heat exchange system that can be used in a high temperature environment can adapt to a variety of installation and use scenarios, and can operate effectively in both indoor and outdoor environments. Therefore, the heat exchange system designed to work under the condition of ambient temperature above 35℃ can achieve multiple beneficial effects such as efficient heat dissipation, improved stability, extended equipment life, wide applicability, improved refrigeration efficiency, enhanced reliability, significant energy saving effects, and flexible application.

[0054] According to some embodiments of the present invention, the heat exchange system is an integrated air conditioner, which includes a shell, and the compressor, the condenser, the throttling element and the evaporator are located in the shell and are interconnected by a refrigerant pipe.

[0055] The integrated air conditioner may include a main unit, which includes the core components of the air conditioner, including a compressor, a condenser, an evaporator, a throttling element, a first heat exchange device, and a second heat exchange device. The main unit also includes a shell, in which the compressor, the condenser, the evaporator, and the throttling element are all located.

[0056] The evaporator is usually used for indoor heat exchange in the refrigeration system to absorb indoor heat and evaporate the refrigerant therein. The evaporator is connected to the compressor through a refrigerant pipeline so that the refrigerant circulates indoors.

[0057] The compressor is the core component of the refrigeration system, responsible for compressing the low-pressure refrigerant gas from the evaporator into high-pressure gas, increasing its temperature and pressure. The high-pressure gas discharged from the compressor enters the condenser through the pipeline, and the high-temperature and high-pressure gas in the condenser is cooled into liquid refrigerant.

[0058] The compressor may be equipped with a gas-liquid separator, which is used to separate the refrigerant vapor and liquid refrigerant in the evaporator. The gaseous refrigerant in the gas-liquid separator enters the compressor through a pipeline, is sucked in by the compressor and compressed into high-pressure gas.

[0059] The condenser is used to dissipate heat and cool the high-temperature and high-pressure refrigerant gas into liquid refrigerant. The liquid refrigerant in the condenser enters the throttling element through the pipeline, and the throttling element reduces the pressure of the refrigerant.

[0060] The throttling element, such as an electronic expansion valve, is located between the condenser and the evaporator to control the flow and pressure of the refrigerant and adjust the operating state of the refrigeration system. The refrigerant after the throttling element enters the evaporator through the pipeline to complete the refrigeration cycle.

[0061] The first heat exchange device for cooling the condenser may include an exhaust fan, which is used to discharge the heat dissipated in the refrigeration system to the outside by using flowing air, i.e., wind, to maintain the refrigeration effect of the refrigeration system. The exhaust fan may be arranged close to the condenser, and discharge the heat in the condenser to the outside by blowing or sucking air, thereby achieving the heat dissipation of the refrigeration system.

[0062] The second heat exchange device for heat exchange with the evaporator may include an air supply fan, which is used to realize indoor air circulation and help to send heat into the refrigeration system during the refrigeration process. The air supply fan is arranged close to the evaporator and transfers the cold energy of the evaporator to the room by blowing or sucking air.

[0063] Through the cooperation and connection of these components, the refrigeration cycle process is realized and the refrigeration effect of the integrated air conditioner is achieved.

[0064] All-in-one air conditioners can also include:

[0065] The return air vent is used to draw in indoor air from the room. The return air vent is connected to the evaporator of the host through a pipe or air duct. The indoor air is drawn in through the return air vent and cooled by the evaporator.

[0066] The exhaust pipe is used to discharge the hot air or exhaust gas in the room to the outside. In some embodiments, the first heat exchange device may include an exhaust fan, and the exhaust fan discharges the hot air after the heat is dissipated by the condenser to the outside through the exhaust pipe. The hot air in the condenser is driven by the exhaust fan to flow and is discharged through the exhaust pipe to maintain the temperature balance inside the host.

[0067] The air outlet is used to pass the cold air processed by the evaporator into the room. In some embodiments, the cooled air is sent out by the air supply fan and delivered to the room through the air outlet. The area of ​​the air outlet can be larger than the cross-sectional area of ​​the exhaust pipe, so that the cold air can be effectively delivered to various areas of the room.

[0068] The air guide plate can be arranged at the air outlet, and the air guide plate can be moved, for example rotated, to control the direction and amount of air supply. The air guide plate allows the user to adjust the direction and amount of air supply to achieve comfortable air distribution.

[0069] According to some embodiments of the present invention, the workflow of the integrated air conditioner may be:

[0070] The return air inlet draws air from the room, and the inhaled air is cooled by the evaporator in the main unit, and the cooled air is sent into the room through the air outlet. The direction and amount of the cold air can be adjusted by the air guide plate. The condenser in the main unit discharges the hot air generated during the cooling process to the outside through the exhaust duct.

[0071] The integrated air conditioner is located indoors, and the condenser is connected to the outdoors through an exhaust pipe.

[0072] The exhaust pipe can be connected to the outside by opening a hole in the wall. Since the hole in the wall requires a small aperture, the exhaust air volume and the exhaust pipe diameter are limited. The refrigerant composition used in the present invention has a high condensing temperature, a large temperature difference with the first medium used for air conditioning heat dissipation, such as air, and a good heat exchange effect. It is suitable for small heat dissipation air volume scenes, and the present invention utilizes the temperature glide of the refrigerant composition, in conjunction with a countercurrent multi-row heat exchanger, it also improves the heat exchange efficiency in small heat dissipation air volume scenes.

[0073] According to some embodiments of the present invention, the integrated air conditioner is at least partially located above the indoor ceiling.

[0074] The integrated air conditioner can be installed through the ceiling, so as to be installed in the upper part of the indoor space, wherein the integrated air conditioner is at least partially located above the indoor ceiling, and there is a containing space between the ceiling and the top of the room, and the integrated air conditioner can be at least partially located in the space. Since the space is relatively closed, the ambient temperature where most of the body of the integrated air conditioner is located is higher than the indoor space temperature below the ceiling, and the heat exchange system using the refrigerant composition of the present invention is more adaptable to the application scenario with higher ambient temperature.

[0075] According to some embodiments of the present invention, the integrated air conditioner is a kitchen air conditioner, a bathroom air conditioner or a mobile air conditioner.

[0076] The integrated air conditioner using the refrigerant formulation of the present invention is particularly suitable for scenarios where the exhaust duct area is limited or the ambient temperature around the condenser is high, such as kitchens, bathrooms, etc., as well as mobile air conditioners with exhaust ducts for indoor or outdoor use.

[0077] A third aspect of the present invention provides a device for refrigeration, comprising:

[0078] A main body, wherein the main body is configured as an object to be cooled;

[0079] A container, wherein the container contains the refrigerant composition of the present invention;

[0080] The refrigerant composition is released from the container and evaporates in the vicinity of the body to cool the body.

[0081] A technical solution of the present invention regarding a device for refrigeration has at least the following beneficial effects:

[0082] The device for refrigeration adopts the refrigerant composition of the present invention, thereby at least having all the beneficial effects of the refrigerant composition of the present invention. Specifically, its non-azeotropic properties allow it to boil in a wide temperature range under constant pressure conditions, resulting in temperature glide, thereby improving the refrigeration efficiency in the evaporator. It can still maintain an excellent refrigeration effect at high ambient temperatures to ensure that the main body is effectively cooled. The safety level of the refrigerant composition is A1, which means that it is low in toxicity and non-flammable, reducing safety risks to the human body and the environment. The use of non-azeotropic compositions reduces energy losses and improves system energy efficiency, thereby reducing energy consumption and operating costs, meeting the requirements of energy conservation and environmental protection.

[0083] The device is suitable for small air volume heat dissipation (heat dissipation air volume less than 500m 3 / h) and high ambient temperature (above 35°C), it can be used in a variety of complex environments, such as electronic equipment cooling, industrial equipment heat dissipation, household air conditioning, etc., and has a wide range of applicability.

[0084] A fourth aspect of the present invention provides a device for heating, comprising:

[0085] A main body, wherein the main body is configured as an object to be heated;

[0086] A container, wherein the container contains the refrigerant composition of the present invention;

[0087] The refrigerant composition is released from the container and condenses adjacent the body to heat the body.

[0088] The present invention relates to a technical solution in a device for heating, which has at least the following beneficial effects:

[0089] The device for heating adopts the refrigerant composition of the present invention, thereby at least having all the beneficial effects of the refrigerant composition of the present invention. Specifically, the non-azeotropic properties of the refrigerant composition of the present invention enable condensation within a wide temperature range under constant pressure conditions, resulting in temperature glide, thereby improving the heating efficiency in the condenser. It can maintain excellent heating effects at low ambient temperatures to ensure that the main body is effectively heated. It can be used in a variety of complex environments, such as home heating, industrial equipment heating, heat pump systems, etc., and has a wide range of applicability. Since the heating system is efficient, energy-saving and has low maintenance costs, it can provide users with an economical and affordable heating solution, reducing long-term operation and maintenance costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0090] Figure 1 It is a temperature entropy diagram of the refrigerant composition and a schematic diagram of the wind temperature changes.

[0091] Figure 2 It is a schematic diagram of the air conditioning structure of the first embodiment of the heat exchange system of the present invention.

[0092] Figure 3 It is a schematic diagram of a refrigerant circulation system of a first embodiment of a heat exchange system of the present invention.

[0093] Figure 4 It is a flow diagram of a condenser of the first embodiment of the heat exchange system of the present invention.

[0094] Figure 5 It is a schematic diagram of the air conditioning installation structure of the second embodiment of the heat exchange system of the present invention.

[0095] Figure 6 It is a schematic structural diagram of the air conditioner in a second embodiment of the heat exchange system of the present invention when viewed from a certain top view after the shell is removed.

[0096] Figure 7 It is a horizontal cross-sectional bottom view of the second embodiment of the heat exchange system of the present invention.

[0097] Figure 8 It is a flow diagram of a condenser of the second embodiment of the heat exchange system of the present invention.

[0098] Reference numerals:

[0099] 100: host; 200: return air outlet; 300: exhaust duct; 400: supply air duct; 500: outlet;

[0100] 110: evaporator; 120: gas-liquid separator; 130: compressor; 140: condenser; 150: throttling element; 160: air supply fan; 170: exhaust fan;

[0101] 1000: kitchen air conditioner; 1001: housing; 1002: first fan; 1003: first heat exchanger;

[0102] 1004: second fan; 1005: second heat exchanger; 1006: compression device; 1009: refrigerant pipe;

[0103] 1014: a clearance groove; 1051: a first pipeline; 1052: a second pipeline;

[0104] 1101: first air inlet; 1103: second air inlet; 1104: second air outlet; 1110: first cavity; 1120: second cavity;

[0105] 2000: ceiling; 2100: keel; 2200: spliced ​​decorative panels. DETAILED DESCRIPTION

[0106] The following are specific embodiments of the present invention, and the technical solutions of the present invention are further described in conjunction with the embodiments, but the present invention is not limited to these embodiments.

[0107] The following will be combined with the embodiments to clearly and completely describe the concept of the present invention and the technical effects produced, so as to fully understand the purpose, characteristics and effects of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, other embodiments obtained by those skilled in the art without creative work are all within the scope of protection of the present invention.

[0108] In the description of the present invention, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0109] Unless otherwise specified, "room temperature" in the present invention means 25°C±5°C.

[0110] Unless otherwise specified, "about" in the present invention means that the allowable error is within ±1%.

[0111] If the specific conditions are not specified in the examples, the experiments were carried out under conventional conditions or conditions recommended by the manufacturer. If the manufacturers of the reagents or instruments are not specified, they are all conventional products that can be purchased from the market.

[0112] The relevant information of some refrigerants is shown in Table 1.

[0113] Table 1

[0114] Chemical formula Critical temperature / ℃ Critical pressure / MPa Security Level R134a <![CDATA[CH2FCF3]]> 101.1 4.06 A1 R32 <![CDATA[CH2F2]]> 78.11 5.78 A2L R744 <![CDATA[CO2]]> 30.98 7.38 A1 R22 <![CDATA[CHClF2]]> 96.14 4.99 A1

[0115] Examples 1 to 31

[0116] Examples 1 to 31 provide a refrigerant composition, which is a mixture of R134a, R32 and R744. The mass percentages of R134a:R32:R744 based on the total mass of the refrigerant composition are shown in Table 2.

[0117] Effect test

[0118] The mixed refrigerants of Examples 1 to 31, R22 and R32 were selected for theoretical cycle calculation.

[0119] The selected working conditions are: evaporation temperature 13°C, condensation temperature 65°C (for mixed refrigerants, the evaporation temperature and condensation temperature are defined by the average value of the dew point and bubble point under a certain pressure), superheat 2°C, subcooling 10°C, and compressor isentropic efficiency 0.7.

[0120] The refrigerant properties are obtained by calling REFPROP software. Compare the volumetric cooling capacity, refrigeration energy efficiency EER, condensing pressure, pressure ratio, temperature glide (under condensing pressure), exhaust temperature parameters. The relative values ​​in the calculation results are based on R22 as a reference.

[0121] The results are shown in Table 2.

[0122] Table 2

[0123]

[0124]

[0125] From the results in Table 2, it can be seen that although R32 has a significantly higher relative volumetric cooling capacity than R22, the condensing pressure and exhaust temperature are very high when the system is running, which is not conducive to equipment reliability, and the energy efficiency is reduced by about 7%.

[0126] For the refrigerant composition of the present invention, the relative volumetric refrigeration capacity of all embodiments exceeds R22 and is more than 115% of R22, and the relative energy efficiency is only slightly lower than R22, but the difference is within 4%. The condensing pressure is lower than R32 and slightly higher than R22, and the pressure ratio is basically the same as R22.

[0127] By comparing different embodiments, we can find that:

[0128] According to the test results of Examples 1, 6, 10 and 16, by keeping the R32 ratio unchanged and increasing the CO2 ratio (correspondingly reducing the R134a ratio), the refrigerant composition shows a trend of increasing relative volumetric refrigeration capacity, decreasing relative pressure ratio and increasing temperature glide.

[0129] According to the test results of Examples 10, 15, 21, 25, and 29, by keeping the CO2 ratio unchanged and increasing the R32 ratio (correspondingly reducing the R134a ratio), the refrigerant composition shows a trend of increasing volumetric refrigeration capacity and slightly decreasing relative pressure ratio, and the changes in various indicators are smaller than when CO2 replaces R134a.

[0130] According to the test results of Examples 7 to 10, by keeping the R134a ratio unchanged and increasing the R32 ratio (correspondingly reducing the CO2 ratio), the refrigerant composition shows a trend of decreasing condensing pressure and exhaust gas temperature.

[0131] The above test results indicate that changes in the amounts of different components in the refrigerant composition of the present invention will have varying degrees of influence on the relative volumetric refrigeration capacity, relative refrigeration energy efficiency, condensing pressure, relative pressure ratio, temperature glide, exhaust temperature, etc. of the heat exchange system.

[0132] To replace R22 without increasing the system pressure and exhaust temperature as much as R32, the refrigerant composition may be composed of 52 wt%-62 wt% of 1,1,1,2-tetrafluoroethane, 32 wt%-40 wt% of difluoromethane and 4 wt%-8 wt% of carbon dioxide.

[0133] In order to stably maintain the safety level of the refrigerant composition to A1 under the operating conditions of an evaporating temperature of 13°C and a condensing temperature of 65°C, the exhaust temperature is less than 105°C, the condensing pressure is less than 3.6MPa, the relative volumetric refrigeration capacity is above 115%, and the temperature glide is greater than 7°C, so as to better meet the reliability requirements of the system and the heat exchange requirements of a small exhaust volume and a high-temperature working environment, the refrigerant composition can be composed of 58wt%-62wt% of 1,1,1,2-tetrafluoroethane, 32wt%-36wt% of difluoromethane and 4wt%-7wt% of carbon dioxide.

[0134] It can be seen from the above test results that the refrigerant composition of the embodiment of the present invention has an obvious temperature glide phenomenon, and can be used in conjunction with a countercurrent multi-row heat exchanger to achieve a better heat exchange effect. Figure 1 As shown in the temperature-entropy diagram and the wind temperature change, during the condensation process, the temperature change of the refrigerant is not a parallel line. During the condensation process, the condensation temperature of the refrigerant gradually decreases, and the wind passing through the condenser usually gradually heats up along the direction of air flow. When the refrigerant composition of the present invention is combined with a countercurrent multi-row condenser, a large temperature difference between the refrigerant temperature and the air temperature can be maintained both upstream and downstream in the air flow direction, thereby achieving a better heat exchange effect.

[0135] In some examples, the condenser can be cooled by water in addition to air cooling. For example, the condensed water on the surface of the evaporator can be gathered under the condenser, and then the water can be sprayed onto the heat exchange tubes of the condenser and the exhaust air flowing through the condenser through a water wheel or a water distributor, resulting in a decrease in the air temperature. Figure 1 As shown in the figure, the air temperature will change in a tortuous way. But in general, along the flow direction of the air through the condenser, the air temperature shows an overall upward trend.

[0136] The refrigerant composition of the present invention is suitable for scenes with unfavorable heat dissipation conditions, with ODP=0, a volumetric refrigeration capacity better than R22, and a comparable energy efficiency.

[0137] In addition, using R1234ze(E) or R152a or R1270 to replace the R134a component can also reduce the GWP value of the refrigerant composition, but will increase the flammability of the mixed refrigerant. Therefore, the present invention does not use R1234ze(E) or R152a or R1270.

[0138] Heat exchange system first embodiment

[0139] This embodiment provides a heat exchange system, which is an integrated air conditioner.

[0140] The integrated air conditioner is embedded in the space between the indoor ceiling and the roof. The hot air is discharged to the outside through the exhaust duct through the exhaust holes on the wall. Due to the small diameter of the exhaust holes and the exhaust duct (no more than 120mm), the exhaust air volume is small (<500m 3 / h), when the air conditioner is placed in the kitchen, the ambient temperature in the ceiling may be high (higher than 35°C). Therefore, in order to ensure a certain cooling capacity output, the refrigerant composition of the present invention needs to be used.

[0141] like Figures 2 to 4 As shown, the integrated air conditioner is provided with a main unit 100, a return air port 200 is provided near the main unit 100, and the main unit 100 is connected with an exhaust duct 300 and an air supply duct 400, and the diameter of the exhaust duct 300 is ≤120 mm.

[0142] The host 100 includes core components of the air conditioner, including a compressor 130 , a condenser 140 , an evaporator 110 , an expansion valve 150 , an exhaust fan 170 and an air supply fan 160 .

[0143] The return air vent 200 is used to introduce indoor air from below the ceiling. The return air vent 200 may be connected to the evaporator 110 through a pipe or an air duct, and the return air vent 200 may also be arranged near the air inlet side of the evaporator 110. Indoor air is sucked in through the return air vent 200 and cooled by the evaporator 110.

[0144] The exhaust duct 300 is used to discharge indoor hot air or exhaust gas to the outside. In some embodiments, the exhaust fan 170 discharges the hot air after the heat is dissipated by the condenser 140 to the outside through the exhaust duct 300. The hot air of the condenser 140 is driven by the exhaust fan 170 and discharged through the exhaust duct 300. In some examples, part of the air flowing into the ceiling through the return air port 200 is used for heat dissipation of the condenser 140 and is discharged to the outside through the exhaust duct 300.

[0145] The air supply duct 400 is used to pass the treated cold air into the room. In some embodiments, the air cooled by the evaporator 110 is driven by the air supply fan 160 and transported to the room through the air supply duct 400. The air supply duct 400 is connected to the air outlet 500, and the air outlet 500 faces the room. An air guide plate may be provided at the air outlet 500, and the air guide plate can be moved, such as rotated, to control the direction and amount of air supply. In some embodiments, the end of the air supply duct 400 is connected to the air outlet 500, and the air outlet 500 is set on the wall or ceiling in the room. The air guide plate allows the user to adjust the direction and amount of air supply to achieve comfortable air distribution.

[0146] In some examples, the workflow of the integrated air conditioner may be:

[0147] The return air vent 200 draws in air from the room, and the drawn in air is cooled by the evaporator 110 in the main unit 100, and the cooled air is delivered to the room through the air supply pipe 400. The cold air enters the room through the air outlet 500. The condenser 140 in the main unit 100 discharges the hot air generated during the cooling process to the outside through the exhaust pipe 300.

[0148] In some examples, the integrated air conditioner performs condensation heat dissipation in a high ambient temperature. The integrated air conditioner can be specifically a kitchen refrigeration system, and the refrigeration system is composed of an evaporator 110, a gas-liquid separator 120, a compressor 130, a condenser 140, and an expansion valve 150. The expansion valve 150 serves as a throttling element. In particular, in order to better achieve countercurrent heat dissipation, the condenser 140 needs to be arranged in multiple rows (for example, not less than 4 rows), and the refrigerant and the air are arranged in a countercurrent form to form a stepped heat exchange. At this time, the temperature glide during the condensation of the mixed refrigerant can make the refrigerant and air temperatures better match, reduce irreversible losses in the heat exchange process, and improve the energy efficiency of the system. The outer diameter of the condenser copper tube can be selected from 5-7mm, specifically 7mm.

[0149] The condenser can work under the condition of ambient temperature higher than 35℃.

[0150] In some examples, the integrated air conditioner is a kitchen refrigeration system, which includes an evaporator 110, a gas-liquid separator 120, a compressor 130, a condenser 140, and an expansion valve 150 interconnected by a refrigerant pipe.

[0151] In kitchen refrigeration system:

[0152] The evaporator 110 is a refrigeration part of the refrigeration system, which is used to absorb indoor heat and use it for refrigerant evaporation. The evaporator 110 is connected to the gas-liquid separator 120 through a refrigerant pipeline.

[0153] The gas-liquid separator 120 is used to separate the refrigerant vapor and liquid refrigerant in the evaporator 110. The gaseous refrigerant in the gas-liquid separator 120 enters the compressor 130 through a pipeline, is sucked in by the compressor and compressed into high-pressure gas, and the liquid refrigerant can enter the condenser 140 or the expansion valve 150 or return to the evaporator 110.

[0154] The compressor 130 is the core component of the refrigeration system, which is responsible for compressing the low-pressure refrigerant gas into high-pressure gas, increasing its temperature and pressure. The high-pressure gas discharged from the compressor 130 enters the condenser 140 through a pipeline, and the high-temperature and high-pressure gas in the condenser 140 is cooled into liquid refrigerant.

[0155] The condenser 140 is used to cool the high-temperature and high-pressure refrigerant gas into liquid refrigerant by heat dissipation. The liquid refrigerant in the condenser 140 enters the expansion valve 150 through a pipeline. The expansion valve 150 can be, for example, an electronic expansion valve, which controls the flow rate of the refrigerant and adjusts its pressure.

[0156] It should be noted that the reference Figure 4 As shown, the condenser can be designed to be divided into multiple rows, and water wheels can be set between adjacent rows of heat exchangers to spray water. The evaporation of water droplets can cool the air that has been heat exchanged by the previous group of condensers, increase the heat transfer temperature difference of the next group of condensers, thereby further enhancing the heat dissipation capacity of the condenser and thus improving the refrigeration capacity of the system.

[0157] Figure 4 The diagram shows a 4-row condenser and refrigerant flow arrangement, where the 4-row condenser is divided into 2 groups (2+2), and a water wheel is provided between the two groups to atomize the condensed water. The refrigerant in the condenser 140 can be designed to include multiple parallel branches, each branch being countercurrent to the air flow direction.

[0158] The expansion valve 150 is located between the condenser 140 and the evaporator 110 and is used to reduce the pressure of the refrigerant. The expansion valve 150 may be, for example, an electronic expansion valve and may be used to adjust the operating state of the refrigeration system. The refrigerant throttled by the expansion valve 150 enters the evaporator 110 through a pipeline to complete the refrigeration cycle.

[0159] Heat exchange system second embodiment

[0160] like Figures 5 to 8 As shown, this embodiment provides a kitchen air conditioner 1000 using the refrigerant composition of the present invention. The kitchen air conditioner 1000 can be suspended and installed on a ceiling 2000, and the ceiling 2000 includes a keel 2100 as a supporting structure and a spliced ​​decorative plate 2200 installed on the keel 2100.

[0161] The kitchen air conditioner 1000 includes a housing 1001, a first fan 1002, a second fan 1004, a first heat exchanger 1003, a second heat exchanger 1005, a compression device 1006, an electric control box 2a and a throttling element. The first fan 1002, the second fan 1004, the first heat exchanger 1003, the second heat exchanger 1005, the compression device 1006 and the throttling element are located in the housing 1001 to form an integral or one-piece structure. The first fan 1002 can be used to supply air to the room, the second fan 1004 can be used to exhaust air to the outside, the first heat exchanger 1003 is used as an evaporator in cooling, the second heat exchanger 1005 is used as a condenser in cooling, and the compression device 1006 can be a compressor.

[0162] The top of the housing 1001 is recessed downward to form a clearance groove 1014. The clearance groove 1014 can be set as a straight groove. The clearance groove 1014 extends from one side of the housing 1001 to the other side of the housing 1001, and the clearance groove 1014 passes through the housing 1001 in the horizontal direction. The depth of the clearance groove 1014 can be 80% to 95% of the size of the housing 1001 in the vertical direction. The clearance groove 1014 can be used for the keel 2100 to pass through. When installing the kitchen air conditioner 1000, it is only necessary to align the opening of the clearance groove 1014 with the keel 2100 below the ceiling 2000, and then raise the height of the kitchen air conditioner 1000 so that the keel 2100 enters the clearance groove 1014 until the keel 2100 is located at the bottom of the clearance groove 1014. Finally, the kitchen air conditioner 1000 is fixed, for example, by fixing the kitchen air conditioner 1000 through a ceiling to complete the installation. During the installation of the kitchen air conditioner 1000, it is not necessary to remove the installed keel. The kitchen air conditioner 1000 is at least partially located above the ceiling 2000, and the chassis of the kitchen air conditioner 1000 can be located below the ceiling 2000 and covered with a panel. After the kitchen air conditioner 1000 has been in cooling operation for a certain period of time, the temperature above the ceiling 2000 is higher than the temperature of the indoor space below the ceiling 2000, and can reach more than 35°C.

[0163] The housing 1001 is provided with a first cavity 1110 and a second cavity 1120. The first cavity 1110 and the second cavity 1120 are separated by a clearance slot 1014. The housing 1001 is provided with a first air inlet 1101, a first air outlet (not shown in the figure), a second air inlet 1103 and a second air outlet 1104. The first air inlet 1101 is provided on the side wall of the first cavity 1110. The first air inlet 1101 is connected to the indoor space, for example, through a return air outlet spaced apart from the housing 1001, and is used to transport air into the first cavity 1110. The first air outlet is provided on the bottom wall of the first cavity 1110. The first air outlet is used to output the air input into the first cavity 1110 from the first air inlet 1101 to the first cavity 1110. The second air inlet 1103 is provided on the side wall of the second cavity 1120. The second air inlet 1103 is connected to the indoor space, for example, through the return air outlet, and is used to transport air into the second cavity 1120. The second air outlet 1104 is provided on the side wall of the second cavity 1120. The second air outlet 1104 is used to output the air input into the second cavity 1120 from the second air inlet 1103. The second air outlet 1104 can be connected to the outdoor space, for example, the second air outlet 1104 can discharge the second cavity 1120 to the outside through the exhaust pipe through the exhaust hole provided on the wall, and the diameter of the exhaust pipe is ≤120mm.

[0164] The first fan 1002 is connected to the housing 1001. The first fan 1002 is disposed in the first cavity 1110. The first fan 1002 is configured to drive the air in the first cavity 1110 to flow from the first air inlet 1101 of the first cavity 1110 to the first air outlet of the first cavity 1110, so as to realize air circulation between the indoor space and the first cavity 1110.

[0165] The first heat exchanger 1003 is disposed in the first cavity 1110. The air in the first cavity 1110 flows through the first heat exchanger 1003 when flowing from the first air inlet 1101 to the first air outlet, and the first heat exchanger 1003 can exchange heat with the air.

[0166] The second fan 1004 may be disposed in the second cavity 1120. The second fan 1004 is configured to drive the air in the second cavity 1120 to flow from the second air inlet 1103 of the second cavity 1120 to the second air outlet 1104 of the second cavity 1120, so as to inhale the air in the indoor space into the second cavity 1120 and then transport the air from the second cavity 1120 to the outdoor space.

[0167] The second heat exchanger 1005 is disposed in the second cavity 1120. The second heat exchanger 1005 may be disposed close to the second air inlet 1103. The air in the second cavity 1120 flows through the second heat exchanger 1005 when flowing from the second air inlet 1103 to the second air outlet 1104, and the second heat exchanger 1005 can exchange heat with the air.

[0168] The compression device 1006 may be arranged in the housing 1001. The compression device 1006 may be arranged in the first cavity 1110 or in the second cavity 1120. In this embodiment, the compression device 1006 is arranged in the second cavity 1120. The compression device 1006, the second heat exchanger 1005, the throttling element and the first heat exchanger 1003 are connected in sequence through the refrigerant pipe 1009 to form a refrigeration circuit. The refrigerant composition of the present invention may be pre-filled in the refrigeration circuit. The compression device 1006 can drive the refrigerant to circulate between the first heat exchanger 1003 and the second heat exchanger 1005. A throttling element is also arranged between the first heat exchanger 1003 and the second heat exchanger 1005. In the cooling mode of the kitchen air conditioner 1000, the refrigerant evaporates when flowing through the first heat exchanger 1003 and absorbs the heat of the air flowing through the first cavity 1110. The refrigerant releases heat to the air flowing through the second cavity and condenses when flowing through the second heat exchanger 1005. In this way, the temperature of the air flowing through the first cavity decreases, and the air transported from the first air outlet of the first cavity to the indoor room is cold air. Correspondingly, the temperature of the air flowing through the second cavity increases, and the air transported from the second cavity to the outdoor room is hot air.

[0169] Among them, the second heat exchanger 1005 can be a straight heat exchanger with a compact structure. The second heat exchanger 1005 includes multiple rows of first heat exchange tubes, and the number of rows of first heat exchange tubes is at least 4 rows, for example, 6 rows. Multiple rows of first heat exchange tubes are arranged in sequence along the air flow direction in the second cavity 1120 and connected in series in sequence, for example, the ends of adjacent rows of first heat exchange tubes are connected by U-shaped tubes. The refrigerant composition of the present invention enters the second heat exchanger 1005 from the first heat exchange tube located downstream in the air flow direction, and leaves the second heat exchanger 1005 from the first heat exchange tube located upstream in the air flow direction, realizing countercurrent heat exchange on the condenser side.

[0170] The first heat exchanger 1003 is constructed as a U-shaped heat exchanger, which has a large contact area with the air and high heat exchange efficiency. The first fan 1002 is arranged in the internal cavity enclosed by the first heat exchanger 1003, and the U-shaped heat exchanger can be arranged around the first fan 1002, with a compact layout. The first heat exchanger 1003 includes at least 2 rows of U-shaped second heat exchange tubes, and at least 2 rows of second heat exchange tubes are arranged in sequence and connected in series along the air flow direction of the first chamber 1100, for example, the ends of the second heat exchange tubes in adjacent rows are connected by U-shaped tubes. The number of rows of the second heat exchange tubes can be 2 rows, for example. The refrigerant composition of the present invention enters the first heat exchanger 1003 from the second heat exchange tube located downstream in the air flow direction, and leaves the first heat exchanger 1003 from the second heat exchange tube located upstream in the air flow direction, realizing countercurrent heat exchange on the evaporator side.

[0171] In this embodiment, the electric control box 2a includes a control board 27a and a cooling pipe 24a. The cooling pipe 24a is used for heat dissipation of the control board 27a. The cooling pipe 24a introduces refrigerant from the second heat exchanger 1005, and the refrigerant flows back to the second heat exchanger 1005 after passing through the cooling pipe 24a. The cooling pipe 24a can introduce refrigerant from the main flow path or the branch flow path of the second heat exchanger 1005. After passing through the cooling pipe 24a, the refrigerant flows back to the second heat exchanger 1005 before the subcooling section of the second heat exchanger 1005, and then flows to the subcooling section.

[0172] When the kitchen air conditioner 1000 is working, the control board 27a will generate heat and transfer the heat to the cooling pipe 24a. When the kitchen air conditioner 1000 is in cooling mode, the compression device 1006 compresses the refrigerant and then outputs the high-temperature and high-pressure refrigerant to the second heat exchanger 1005. When the refrigerant flows through the second heat exchanger 1005, it transfers the heat to the air flowing through the second cavity. The refrigerant is cooled to a low-temperature refrigerant. The refrigerant is transported from the second heat exchanger 1005 to the cooling pipe 24a. When the refrigerant flows through the cooling pipe 24a, it absorbs the heat of the control board 27a, thereby bringing the heat emitted by the control board 27a out of the electrical control box 2a. The refrigerant then re-enters the second heat exchanger 1005 for countercurrent heat exchange with the air, so that the cooling effect is not attenuated.

[0173] The second heat exchanger 1005 may be provided with a plurality of parallel pipelines, each of which exchanges heat in a countercurrent direction with the air flow direction. Due to some objective reasons (such as different heat exchange efficiencies between heat exchange tubes at different positions and heat dissipation media such as air, etc.), it is difficult to achieve the same heat exchange effect between the plurality of pipelines, resulting in different temperatures of the refrigerants output by the plurality of pipelines. The temperature of the refrigerant output by the pipeline with better heat exchange effect is lower, and the temperature of the refrigerant output by the pipeline with poor heat exchange effect is higher. If the temperature difference of the refrigerants output by the plurality of heat exchange flow paths is large, the condensation effect of the condenser will also be reduced, the cooling capacity will be reduced, and the power of the compressor will be increased.

[0174] In some examples, the second heat exchanger 1005 includes a first pipeline 1051 and a second pipeline 1052 connected in parallel. Since the first pipeline 1051 is in contact with more cooling water sprinkled by the water wheel, the heat exchange efficiency of the first pipeline 1051 is higher than that of the second pipeline 1052. The cooling pipe 24a is connected in series to the first pipeline 1051, that is, the refrigerant of the first pipeline 1051 is introduced into the cooling pipe 24a for electronically controlled heat dissipation, and then returned to the first pipeline 1051 or the second heat exchanger 1005, so that the temperature of the refrigerant output from the two pipelines is closer, so that the temperature difference of the refrigerant when it converges is reduced, which can improve the condensation efficiency of the second heat exchanger 1005 and the cooling capacity of the air conditioner, and reduce the power of the compressor. After the refrigerant returns to the second heat exchanger 1005 through the cooling pipe 24a, the refrigerant composition therein continues to dissipate heat in countercurrent with the air, or after the refrigerant returns to the second heat exchanger 1005 through the cooling pipe 24a, it merges with the second pipeline 1052 and continues to dissipate heat in countercurrent with the air, resulting in a good heat dissipation effect.

[0175] In other embodiments of the present invention, the refrigerant composition of the present invention is also suitable for heat pump hot water scenarios. In this case, the condenser adopts water cooling (shell heat exchanger, plate heat exchanger, etc.), and the water and refrigerant are arranged in countercurrent, which can achieve a higher water outlet temperature.

[0176] The present invention has been described in detail above in conjunction with the embodiments, but the present invention is not limited to the above embodiments, and various changes can be made within the knowledge scope of ordinary technicians in the relevant technical field without departing from the purpose of the present invention.

Claims

1. A refrigerant composition, characterized in that: The refrigerant composition comprises, based on the total weight of the refrigerant composition, 52 wt%-62 wt% of 1,1,1,2-tetrafluoroethane, 32 wt%-40 wt% of difluoromethane and 4 wt%-8 wt% of carbon dioxide. The refrigerant composition is a non-azeotropic composition.

2. The refrigerant composition according to claim 1, characterized in that The refrigerant composition comprises: 58 wt % to 62 wt % of 1,1,1,2-tetrafluoroethane, 32 wt % to 36 wt % of difluoromethane and 4 wt % to 7 wt % of carbon dioxide.

3. The refrigerant composition according to claim 1 or 2, characterized in that Under the operating conditions of an evaporation temperature of 13°C and a condensation temperature of 65°C, the exhaust temperature of the refrigerant composition is less than 107.5°C, the condensation pressure is less than 3.7 MPa, and the temperature glide at the condensation pressure is greater than 6.5°C.

4. A heat exchange system, characterized in that: A refrigerant composition comprising the refrigerant composition according to any one of claims 1 to 3, and: a compressor for compressing the refrigerant composition; a condenser connected to the compressor and used to condense the compressed refrigerant composition; a throttling element connected to the condenser and used to reduce the pressure of the condensed refrigerant composition; The evaporator has one end connected to the throttling element and the other end connected to the compressor, and is used for evaporating the low-pressure refrigerant composition.

5. The heat exchange system according to claim 4, characterized in that: The heat exchange system also includes a first heat exchange device, which uses a first medium to cool the condenser. The condenser includes a plurality of rows of first heat exchange tubes arranged along a flow direction of the first medium and connected in sequence. The refrigerant composition enters the condenser from the first heat exchange tubes located downstream in the flow direction of the first medium, and flows out of the condenser from the first heat exchange tubes located upstream in the flow direction of the first medium.

6. The heat exchange system according to claim 5, characterized in that: The first heat exchange tubes are arranged in at least 3 rows, and preferably in 4 to 10 rows.

7. The heat exchange system according to claim 5, characterized in that: The first medium includes air, and the air volume generated by the air flow is less than 500m 3 / h.

8. The heat exchange system according to claim 7, characterized in that: The first heat exchange device further includes an exhaust pipe, and the exhaust pipe is used to exhaust the air. The diameter of the exhaust pipe is ≤120 mm, and preferably the diameter of the exhaust pipe is ≥50 mm and ≤120 mm.

9. The heat exchange system according to claim 4, characterized in that: The heat exchange system also includes a second heat exchange device, which uses a second medium to exchange heat with the evaporator. The evaporator includes a plurality of rows of second heat exchange tubes arranged along the flow direction of the second medium and connected in sequence. The refrigerant composition enters the evaporator from the second heat exchange tubes located downstream in the flow direction of the second medium, and flows out of the evaporator from the second heat exchange tubes located upstream in the flow direction of the second medium.

10. The heat exchange system according to claim 9, characterized in that: The number of the second heat exchange tubes is 2 to 10.

11. The heat exchange system according to claim 5, characterized in that: The condenser is suitable for working under the condition that the ambient temperature is higher than 35°C.

12. The heat exchange system according to any one of claims 4 to 11, characterized in that: The heat exchange system is an integrated air conditioner, which includes a shell, and the compressor, the condenser, the throttling element and the evaporator are located in the shell and are interconnected by a refrigerant pipeline.

13. The heat exchange system according to claim 12, characterized in that: The integrated air conditioner is located indoors, and the condenser is connected to the outdoors through an exhaust pipe.

14. The heat exchange system according to claim 12, characterized in that: The integrated air conditioner is installed in a suspended ceiling, and at least a part of the integrated air conditioner is located above the indoor ceiling.

15. The heat exchange system according to claim 12, characterized in that: The integrated air conditioner is a kitchen air conditioner, a bathroom air conditioner or a mobile air conditioner.

16. A device for refrigeration, characterized in that: include: A main body, wherein the main body is configured as an object to be cooled; A container, comprising a refrigerant composition according to any one of claims 1 to 3; The refrigerant composition is released from the container and evaporates in the vicinity of the body to cool the body.

17. A device for heating, characterized in that: include: A main body, wherein the main body is configured as an object to be heated; A container, comprising a refrigerant composition according to any one of claims 1 to 3; The refrigerant composition is released from the container and condenses adjacent the body to heat the body.

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