Heat pump circulation system and clothes treatment equipment

Abstract

The utility model discloses a heat pump circulating system. The heat pump circulating system comprises an evaporator assembly, wherein the evaporator assembly comprises a first evaporator and a second evaporator which are connected in parallel; the compression component is provided with a first compression part and a second compression part, the first compression part is communicated with the first evaporator, and the second compression part is communicated with the second evaporator; the condenser assembly, the evaporator assembly, the compression part and the condenser assembly form a heat exchange loop, and the heat exchange loop comprises a first loop composed of the first evaporator, the first compression part and the condenser assembly and a second loop composed of the second evaporator, the second compression part and the condenser assembly. The utility model further discloses clothes processing equipment applying the heat pump circulating system. According to the technical scheme, the load and the compression ratio of the compressor can be reduced at the low evaporation temperature and the high condensation temperature.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of clothes treatment devices, and particularly relates to a heat pump circulation system and a clothes treatment device. BACKGROUND

[0002] In the related art, a heat pump clothes dryer uses the condensation heat of refrigerant to heat clothes, and water in the clothes is changed into water vapor, and then the water vapor is condensed by using the evaporation condensation principle, so that no exhaust air drying is realized. In order to improve the drying speed of the existing heat pump clothes dryer, when the heat pump clothes dryer is operated in a fast drying mode, an auxiliary heater (for example, an electric auxiliary heater) of the heat pump clothes dryer is started to increase the temperature of the air flowing into the drum, so as to increase the evaporation speed of the water on the clothes.

[0003] However, considering that the clothes are easily damaged by high temperature in the drying process, the auxiliary heater cannot be increased unlimitedly. Moreover, the energy utilization rate of the electric auxiliary heater is much lower than that of the heat pump system, which greatly increases the energy consumption of the clothes dryer. In view of the defects of the electric auxiliary heater, the existing clothes dryer uses another method to replace the electric auxiliary heater method to improve the drying speed, that is, by reducing the evaporation temperature of the evaporator to enhance the dehumidification capacity of the evaporator. Since the condensation temperature of the condenser in the heat pump clothes dryer is high to ensure the temperature of the air flowing into the drum, the low evaporation temperature means that the pressure in the evaporator is low, and the high condensation temperature corresponds to the high pressure in the condenser. The compressor needs to compress the low-pressure gas from the evaporator to the high-pressure state required by the condenser, which leads to an increase in the compression ratio, and also leads to an increase in the load of the compressor, an increase in the wear of the compressor and a shortening of the service life of the compressor. The heat pump system with low evaporation temperature and high condensation temperature will have high requirements for the compressor. CONTENT OF THE UTILITY MODEL

[0004] Embodiments of the present application provide a heat pump circulation system and a clothes treatment device, which can reduce the load and compression ratio of the compressor under low evaporation temperature and high condensation temperature.

[0005] In a first aspect, the embodiments of the present application provide a heat pump circulation system, which comprises:

[0006] an evaporator assembly, the evaporator assembly comprising a first evaporator and a second evaporator connected in parallel;

[0007] a compression component, the compression component having a first compression part and a second compression part, the first compression part being connected in communication with the first evaporator, and the second compression part being connected in communication with the second evaporator;

[0008] A condenser assembly, the evaporator assembly, the compression component and the condenser assembly form a heat exchange circuit, and the heat exchange circuit includes a first circuit consisting of the first evaporator, the first compression part and the condenser assembly, and a second circuit consisting of the second evaporator, the second compression part and the condenser assembly.

[0009] In one embodiment, the first volume of the first compression part and the second volume of the second compression part are configured in proportion, so that the flow rates flowing through the first evaporator and the second evaporator are different.

[0010] In one embodiment, the compression component further has an exhaust section, a first intake section and a second intake section, the exhaust section and the second intake section are both connected to the second compression section, the first intake section is connected to the first compression section, the exhaust section and the second intake section are both connected to the second compression section, the first evaporator is connected to the first intake section, the second evaporator is connected to the second intake section, the exhaust section of the compression component is connected to the condensation inlet of the condenser assembly, and the first evaporator and the second evaporator are both connected to the condensation outlet of the condenser assembly.

[0011] In one embodiment, the first compression part and the second compression part are configured independently, and the compression component further has a first internal flow channel and a second internal flow channel. The exhaust part and the first intake part are both connected to the first compression part through the first internal flow channel, and the exhaust part and the second intake part are both connected to the second compression part through the second internal flow channel.

[0012] In one embodiment, the compression component further has a primary flow channel, a secondary flow channel, a total exhaust flow channel and an intermediate mixing cylinder. The first compression part is connected to the second compression part through the intermediate mixing cylinder. The first intake part is connected to the first compression part through the primary flow channel. The second intake part is connected to the intermediate mixing cylinder through the secondary flow channel. The exhaust part is connected to the second compression part through the total exhaust flow channel.

[0013] In one embodiment, the first compression part and the second compression part are both independently arranged compressors, the first compression part is used to independently compress and process the refrigerant flowing through the first evaporator, and the second compression part is used to independently compress and process the refrigerant flowing through the second evaporator, or compress and process the refrigerant flowing through the second evaporator and mixed with the refrigerant compressed and output by the first compression part.

[0014] In one embodiment, the first compression section has a total output port and a total input port, the second compression section has a total discharge port, a first injection end and a second injection end, the total output port of the first compression section is connected to the first injection end of the second compression section, the total input port of the first compression section is connected to the first evaporator, the second injection end of the second compression section is connected to the second evaporator, and the total discharge port of the second compression section is connected to the condensation inlet of the condenser assembly.

[0015] In one embodiment, the heat pump circulation system also includes a three-way connector, the first compression part has a total output port and a total input port, the second compression part has a total discharge port and a total injection port, the total input port of the first compression part is connected to the first evaporator, the total injection port of the second compression part is connected to the second evaporator, the total output port of the first compression part, the total discharge port of the second evaporator, and the condensation inlet of the condenser assembly are all connected to the three-way connector.

[0016] In one embodiment, the first compression section has a total output port, a first input end, and a second input end; the second compression section has a total discharge port, a first injection end, and a second injection end; the total output port of the first compression section is connected to the first injection end of the second compression section; the first input end or the second input end of the first compression section is connected to the first evaporator; the second injection end of the second compression section is connected to the second evaporator; and the total discharge port of the second compression section is connected to the condensation inlet of the condenser assembly.

[0017] In one embodiment, the compression component further comprises a cooling element, and the cooling element is used to cool the first compression part and the second compression part.

[0018] In one embodiment, the cooling element is a fan, and the number of the cooling elements is configured to be two, the cooling element used to cool the first compression part is defined as a first heat sink, and the cooling element used to cool the second compression part is defined as a second heat sink, and the power ratio between the first heat sink and the second heat sink is the same as the volume ratio between the first compression part and the second compression part.

[0019] In one embodiment, the cooling element is a fan, and the number of the cooling elements is configured to be one, the first compression part and the second compression part are both on the gas flow path of the cooling element, and the gas flow direction generated by the cooling element is from the first compression part with higher power to the other one with lower power.

[0020] In one embodiment, the heat pump circulation system further includes a flow regulating member disposed between the evaporator assembly and the condenser assembly, wherein the flow regulating member is used to regulate and control the flow of the refrigerant flowing from the condenser assembly to the evaporator assembly.

[0021] In one embodiment, the flow regulating component includes a main regulating valve with a throttling and pressure reduction function, one end of the main regulating valve is connected to the condenser assembly, and the first evaporator and the second evaporator are both connected to the other end of the main regulating valve.

[0022] In one embodiment, the flow regulating member further includes a branch regulating valve having functions of throttling, reducing pressure and regulating flow, and the branch regulating valve is connected to at least one of the first evaporator and the second evaporator.

[0023] In one embodiment, the flow regulating component includes a first expansion valve and a second expansion valve. The first expansion valve is connected to the first evaporator to regulate the flow of refrigerant flowing into the first evaporator, and changes the state of the refrigerant to low temperature and low pressure under its throttling effect. The second expansion valve is connected to the second evaporator.

[0024] In a second aspect, an embodiment of the present application provides a clothes processing device, the clothes processing device comprising:

[0025] The heat pump circulation system mentioned above;

[0026] The heat pump circulation system and the clothes processing chamber form an air circulation path.

[0027] Based on the above embodiments, the heat pump circulation system proposed in the embodiments of the present application includes:

[0028] an evaporator assembly, the evaporator assembly comprising a first evaporator and a second evaporator connected in parallel;

[0029] a compression component, the compression component having a first compression part and a second compression part, the first compression part being connected to the first evaporator, and the second compression part being connected to the second evaporator;

[0030] The condenser assembly, the evaporator assembly, the compression component and the condenser assembly form a heat exchange circuit, and the heat exchange circuit includes a first circuit consisting of a first evaporator, a first compression part and a condenser assembly, and a second circuit consisting of a second evaporator, a second compression part and a condenser assembly.

[0031] Compared to related technologies, the technical solution of this application adjusts and controls the refrigerant flow through the first and second evaporators by configuring the compression element with first and second compression elements of different volumes. This, in conjunction with the first and second evaporators, effectively lowers the evaporation temperature of the evaporator assembly while maintaining a high condensing temperature. Furthermore, it reduces the compression ratio of the compression element, thereby resolving the problem of existing compressors experiencing excessive load and requirements under low evaporation temperature conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying any creative work.

[0033] Figure 1 This is a first layout principle diagram of a heat pump circulation system according to an embodiment of the present invention;

[0034] Figure 2 This is a second layout principle diagram of the heat pump circulation system according to one embodiment of the present utility model;

[0035] Figure 3 This is a first structural diagram of a compression component in one embodiment of the present utility model;

[0036] Figure 4 This is a second structural diagram of the compression component in one embodiment of the present utility model;

[0037] Figure 5 Schematic diagram of a circulation circuit of a clothes processing device according to an embodiment of the present invention.

[0038] Description of Figure Numbers:

[0039] 1-first evaporator, 2-second evaporator, 3-compression component, 31-first compression part, 32-second compression part, 33-exhaust part, 34-first suction part, 35-second suction part, 36-cylinder base body, 371-first inner flow channel, 3711-first inlet flow channel, 3712-first outlet flow channel, 372-second inner flow channel, 3721-second inlet flow channel, 3722-second outlet flow channel, 381-primary flow channel, 382-secondary flow channel, 383-total exhaust flow channel, 384-intermediate mixing cylinder, 4-condenser assembly, 5-drum component, 6-driving fan, 71-main regulating valve, 72-branch regulating valve, 73-first expansion valve, 74-second expansion valve, 81-first connecting pipe, 82-second connecting pipe, 83-main connecting pipe.

[0040] The realization of the objectives, functional features and advantages of this application will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0041] In order to make the purpose, technical solutions and advantages of this application clearer, the following part will further describe the embodiments of this application in detail with reference to the accompanying drawings.

[0042] When the following description refers to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present application. Instead, they are merely examples of devices and methods consistent with some aspects of the present application, as detailed in the appended claims.

[0043] In the description of this application, it should be understood that the terms "first", "second", etc. are used for descriptive purposes only and should not be understood as indicating or implying relative importance. For those of ordinary skill in the art, the specific meanings of the above terms in this application can be understood according to specific circumstances. In addition, in the description of this application, unless otherwise specified, "multiple" refers to two or more. "And / or" describes the association relationship of associated objects, indicating that three relationships may exist. For example, A and / or B can represent: A exists alone, A and B exist at the same time, and B exists alone. The character " / " generally indicates that the previous and subsequent associated objects are in an "or" relationship.

[0044] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which this application belongs. The terms used in this specification are for the purpose of describing specific embodiments only and are not intended to limit this application. The term "and / or" as used herein includes any and all combinations of one or more of the relevant listed items.

[0045] Please refer to the specific Figure 5 As shown, the present application provides a clothing treatment device for drying clothes. The device utilizes heat energy to increase the temperature of flowing air, heating the flowing air into dry hot air. The dry hot air carries away some of the moisture from the wet clothes as it flows through the wet clothes. The dry hot air then flows through the wet clothes and is converted into humid hot air. The humid hot air is dehumidified and heated again before being circulated back to the wet clothes. This cycle repeats until the wet clothes are dried.

[0046] Among them, this solution adopts the heat pump drying principle, that is, the clothing processing equipment includes a heat pump circulation system and a machine body, and a clothing processing chamber is provided on the machine body. For example, the interior of the machine body has a drum component 5, and the drum component 5 is provided with a drum cavity for placing and drying clothes. The drum cavity is the clothing processing chamber of the machine body. The drum component 5 can be driven by a drive motor to rotate, so that the clothes can tumble in the clothing processing chamber, which not only ensures that each piece of wet clothing can be fully dried by dry hot air, but also improves the drying efficiency of wet clothes. For another example, the nursing inner drying chamber of the machine body is the clothing processing chamber of the machine body, and each piece of wet clothing is hung in the clothing processing chamber to be fully dried by dry hot air. The heat pump circulation system and the clothing processing chamber form an air circulation path, so that wet clothes can be continuously dried.

[0047] In this embodiment, please refer to Figure 1 、 Figure 2 and Figure 5 As shown, the above-mentioned heat pump circulation system includes an evaporator assembly, a compression component 3, a flow regulating component and a condenser assembly 4, wherein the evaporator assembly includes a first evaporator 1 and a second evaporator 2 in parallel, the first evaporator 1 and the second evaporator 2 are connected in parallel to the compression component 3, the evaporator assembly, the compression component 3, the flow regulating component and the condenser assembly 4 form a circulating heat exchange circuit, and the first evaporator 1, the second evaporator 2, the compression component 3, the condenser assembly 4 and the flow regulating component of the heat pump circulation system are all installed and fixed inside the machine body.

[0048] Among them, the heat exchange circuit is a heat exchange circuit for the circulation flow of refrigerant, and the heat exchange circuit includes a first circuit composed of a first evaporator 1, a first compression part 31, and a condenser assembly 4, and a second circuit composed of a second evaporator 2, a first compression part 31, a second compression part 32 and a condenser assembly 4.

[0049] Optionally, an internal circulation drying tunnel is provided inside the machine body, and the first evaporator 1, the second evaporator 2, the condenser assembly 4, and the drum part 5 are arranged in sequence along the flow path of the internal circulation air in the internal circulation drying tunnel. Then, the clothing processing chamber, the internal circulation drying tunnel, and the first evaporator 1, the second evaporator 2, the condenser assembly 4, and the drum part 5 of the machine body of the heat pump circulation system will form an airflow circulation path in sequence.

[0050] In the air flow circulation path of this cycle, the compression component 3 absorbs the low-pressure and low-temperature gaseous refrigerant (refrigerant), and then compresses it into a high-pressure and high-temperature gaseous refrigerant through mechanical movement, providing power for the closed cycle and transporting it to the condenser assembly 4. The high-temperature and high-pressure gaseous refrigerant is liquefied at a constant pressure when passing through the condenser assembly 4, releasing heat, and is cooled to a high-pressure supercooled liquid refrigerant. The large amount of heat released by the condenser assembly 4 will be transferred to the flowing air, thereby heating the flowing air into dry hot air. The high-pressure supercooled liquid refrigerant is throttled by the flow regulating member to become a low-temperature and low-pressure mist refrigerant, and then evaporates and absorbs heat from the flowing air in the first evaporator 1 and the second evaporator 2 to form a low-temperature and low-pressure gaseous refrigerant, which is then transported to the compression component 3 again. The moisture in the humid hot air condenses into water droplets when it is cooled and is discharged. The humid hot air will be cooled and converted into dry cold air. The dry cold air will be heated again to dry hot air when it flows through the condenser assembly 4, and the cycle works like this.

[0051] In order to achieve the directionality and stability of the flow of air in the internal circulation drying tunnel of the machine body, please refer to Figure 5 As shown, the machine body also has a drive fan 6 inside. Here, the drive fan 6 can be a blower or an exhaust fan. The drive fan 6 is arranged on the internal circulation drying tunnel, that is, the drive fan 6 is arranged on the path of the gas circulation loop. Preferably, the second evaporator 2 and the condenser assembly 4 of the evaporator assembly are respectively arranged on opposite sides of the first evaporator 1 of the evaporator assembly. Under the guidance of the internal circulation drying tunnel, the drive fan 6 drives air to flow through the condenser assembly 4, the drum component 5, and the second evaporator 2 and the first evaporator 1 of the evaporator assembly in the internal circulation drying tunnel.

[0052] With this configuration, since the first and second evaporators 1 and 2 are arranged in parallel, the evaporation pressures of the first and second evaporators 1 and 2 can be adjusted independently, thereby setting or changing the evaporation temperatures of the first and second evaporators 1 and 2. The first and second evaporators 1 and 2 work together to condense and remove moisture from the hot and humid air into small droplets, thereby achieving dehumidification of the hot and humid air. Specifically, the moisture in the hot and humid air exchanges heat with the second evaporator 2 as it flows through the second evaporator 2. This means that the second evaporator 2 absorbs heat from the hot and humid air, thereby lowering its temperature. As a result, some of the moisture in the hot and humid air condenses into droplets and is discharged, achieving initial dehumidification of the hot and humid air. Furthermore, as the moisture in the hot and humid air exchanges heat with the first evaporator 1 as it flows through the first evaporator 1, further lowering its temperature by absorbing heat from the hot and humid air. The remaining moisture in the hot and humid air condenses into droplets and is discharged, achieving secondary dehumidification of the hot and humid air.

[0053] It is understood that the evaporation temperature of the first evaporator 1 can be lower than that of the second evaporator 2. Defining the first evaporator 1 as a low-temperature evaporator and the second evaporator 2 as a high-temperature evaporator, the flowing air in the gas circulation loop sequentially passes through the high-temperature evaporator, the low-temperature evaporator, and the condenser assembly 4. This ensures that the heat exchange capacity / efficiency of the high-temperature evaporator is maximized due to the temperature difference between the flowing air flowing out of the laundry processing chamber and the evaporation temperature of the second evaporator 2. Furthermore, maintaining a significant temperature difference between the temperature of the hot and humid air after passing through the second evaporator 2 and the evaporation temperature of the first evaporator 1 also ensures relatively good heat exchange efficiency of the first evaporator 1, thereby better ensuring the dehumidification effect of the evaporator assembly, which helps shorten the drying time, improve the drying efficiency, and save energy consumption of the laundry processing device.

[0054] Of course, the evaporation temperature of the first evaporator 1 can also be higher than that of the second evaporator 2. Define the first evaporator 1 as a high-temperature evaporator and the second evaporator 2 as a low-temperature evaporator. In this case, along the path of the gas circulation loop, the flowing air sequentially passes through the low-temperature evaporator, the high-temperature evaporator, and the condenser assembly 4. This creates a significant temperature difference between the temperature of the hot and humid air and the evaporation temperature of the second evaporator 2, thereby improving the heat exchange efficiency of the second evaporator 2, more efficiently absorbing heat from the hot and humid air, and better removing moisture from the hot and humid air, thereby achieving the maximum dehumidification effect of the second evaporator 2. Because there is still a temperature difference between the temperature of the hot and humid air after passing through the second evaporator 2 and the evaporation temperature of the first evaporator 1, a good secondary dehumidification effect of the hot and humid air can be effectively ensured.

[0055] The unexpected effect is that the temperature difference between the temperature of the humid hot air after flowing through the second evaporator 2 and the evaporation temperature of the first evaporator 1 is relatively small, so that the humid hot air absorbs relatively less heat, and the temperature of the air flowing through the condenser assembly 4 increases, thereby increasing the temperature of the air flowing into the clothing processing chamber, which has certain benefits for the drying time of the clothes and improves the drying efficiency of the clothes.

[0056] From the above, it can be seen that the cooperation between the first evaporator 1 and the second evaporator 2 can effectively maintain a high condensing temperature while lowering the evaporation temperature of the evaporator assembly, thereby maximizing the dehumidification effect of the evaporator assembly. In order to avoid the problem of high compression ratio and high requirements on the compression component 3 caused by the heat pump system with low evaporation temperature and high condensing temperature, the utility model provides a preferred method. Please refer to the following for details. Figures 1 to 4As shown, the above-mentioned compression component 3 has a first compression part 31 and a second compression part 32. The first compression part 31 is arranged corresponding to the first evaporator 1, and the second compression part 32 is arranged corresponding to the second evaporator 2. The first volume of the first compression part 31 and the second volume of the second compression part 32 are proportionally configured, so that the flow rates flowing through the first evaporator 1 and the second evaporator 2 are different, and the compression ratio of the compression component 3 is reduced.

[0057] Such arrangement, through the cooperation between the first compression part 31 and the second compression part 32, will have the following unexpected effects:

[0058] 1. Effectively reduce the compression ratio and energy consumption: The compression component 3 divides the entire compression process into multiple stages. The multiple stages here can be multiple independent and parallel stages, or multiple consecutive stages. For example, in the single-stage compression process, the refrigerant (refrigerant) will be directly compressed to the final pressure. Since a large amount of refrigerant will generate a large amount of compression heat during the compression process, a large amount of mechanical energy will be converted into thermal energy, but not into pressure energy. This will cause the exhaust temperature to be too high. Excessively high exhaust temperature can easily lead to a decrease in the viscosity of the lubricating oil, exacerbating the risk of wear and carbon deposition, thereby increasing energy consumption and equipment burden.

[0059] In this embodiment, the refrigerant is compressed in two stages using the first and second compression sections 31, 32. The compression ratio of each stage is reduced by more than 50%, resulting in a relatively low compression ratio in each stage. This not only prevents excessive heat of compression and exhaust temperature in each stage, but also helps reduce throttling and overheating losses in the heat pump cycle system employing this compression element 3. This optimizes the overall performance and energy efficiency of the heat pump cycle system and reduces the energy consumption and burden of each compression cylinder and its compression element 3.

[0060] 2. Significant impact on the maintenance and life of compression unit 3: Multi-stage compression can reduce the compression ratio of each compression, which is very helpful in reducing the axial load on each stage bearing. This not only increases the life of the bearings in compression unit 3, but also the service life and reliability of compression unit 3 as a whole.

[0061] In addition, the first volume of the first compression section 31 and the second volume of the second compression section 32 are configured in proportion to make the flow rates flowing through the first evaporator 1 and the second evaporator 2 different, that is, the first volume of the first compression section 31 and the second volume of the second compression section 32 are different, which makes the displacement of the first compression section 31 and the displacement of the second compression section 32 different, thereby controlling the flow rates flowing through the first evaporator 1 and the second evaporator 2 to be different, thereby controlling the evaporation temperature of the first evaporator 1 and the evaporation temperature of the second evaporator 2.

[0062] For example, if the first volume of the first compressor 31 is larger than the second volume of the second compressor 32, resulting in a larger displacement of the first compressor 31 than the second compressor 32, the flow rate of the first evaporator 1 will be larger than the flow rate of the second evaporator 2. In this way, more refrigerant flows through the first evaporator 1, exchanging more heat with the hot and humid air, accelerating the absorption of heat from the hot and humid air, and ensuring more complete heat exchange between the hot and humid air and the first evaporator 1. In this case, the first evaporator 1 is a low-temperature evaporator. Conversely, if the first volume of the first compressor 31 is smaller than the second volume of the second compressor 32, resulting in a smaller displacement of the first compressor 31 than the second compressor 32, the flow rate of the first evaporator 1 will be smaller than the flow rate of the second evaporator 2. In this way, more refrigerant flows through the second evaporator 2, exchanging more heat with the hot and humid air, accelerating the absorption of heat from the hot and humid air, and ensuring more complete heat exchange between the hot and humid air and the second evaporator 2. In this case, the second evaporator 2 is a low-temperature evaporator.

[0063] It should be noted that the proportional arrangement of the first volume of the first compression section 31 and the second volume of the second compression section 32 also has the following unexpected benefits: Firstly, it can better control the compression ratio of the first compression section 31 to be approximately equal to that of the second compression section 32, further reducing power and energy consumption during the compression process. Furthermore, the refrigerant compressed by the first compression section 31 is atomized, achieving a relatively good cooling effect. This allows the refrigerant to enter the second compression section 32 at a temperature that is not too high after mixing with the refrigerant supplied by the second evaporator 2. This significantly reduces the compression temperature before entering the secondary compression stage. Alternatively, if the first compression section 31 independently compresses the refrigerant supplied by the first evaporator 1, and the second compression section 32 independently compresses the refrigerant supplied by the second evaporator 2, the compression temperature during the first compression stage can be effectively controlled to be approximately equal to the compression temperature during the second compression stage. In summary, the temperature during the compression process within the first compression section 31 will approach the temperature during the compression process within the second compression section 32, achieving a more isothermal compression process at each stage, thereby further improving compression efficiency and saving compression energy.

[0064] On the other hand, it is also possible to further control the compression ratio of the first compression section 31 and the compression ratio of the second compression section 32 to be at a lower level, that is, to make it easier to control the compression ratio of each stage of the compression component 3, the compression ratio can be controlled at a lower level. This not only further improves the overall volumetric efficiency / volume utilization rate, but it is also easy to understand that there must be a clearance volume in the process of manufacturing and assembling the compression component 3, and the clearance volume not only reduces the effective volume of the compression cylinder, but the residual high-pressure refrigerant will further reduce the effective volume of the compression cylinder. The compression ratio of the first compression section 31 and the compression ratio of the second compression section 32 are both very small, which can make the refrigerant remaining in the clearance volume slightly expand to reach the suction pressure. In other words, it effectively avoids the residual high-pressure refrigerant from reducing the effective volume of the compression cylinder, thereby improving the volumetric efficiency / volume utilization rate of the compression component 3, and also makes the first volume of the first compression section 31 and the second volume of the second compression section 32 required to be used also can be reduced accordingly, further reducing the compression power consumption.

[0065] Optionally, a cooling element is provided between the first compression section 31 and the second compression section 32. The cooling element may be a single-stage cooling element or a multi-stage cooling element. This not only further reduces the exhaust temperature at each stage, helping to maintain a lower temperature for the next stage of compression, but also helps the compression component 3 maintain isothermal compression. This also helps reduce the compression ratio of each stage, thereby improving compression efficiency, volumetric efficiency, safety performance, and saving power.

[0066] It should be noted that the above-mentioned cooling element is preferably a fan, and the number of cooling elements is configured to be two. The cooling element used to cool the first compression section 31 is defined as a first heat sink, and the cooling element used to cool the second compression section 32 is defined as a second heat sink. The power ratio between the first heat sink and the second heat sink is the same as the volume ratio between the first compression section 31 and the second compression section 32. For example, if the first volume of the first compression section 31 is greater than the second volume of the second compression section 32, the compression power of the first compression section 31 is greater than the compression power of the second compression section 32. At this time, the power of the configured first heat sink is greater than the power of the second heat sink, thereby better ensuring that the first compression section 31 with a large compression power can obtain sufficient heat dissipation, thereby ensuring that the first compression section 31 maintains good working performance.

[0067] In addition, the cooling element is a fan, and the number of cooling elements is configured as one, the first compression section 31 and the second compression section 32 are both on the gas flow path of the cooling element, and the gas flow direction generated by the cooling element is from the first compression section 31 and the second compression section 32 with greater power to the other with less power. For example, if the first volume of the first compression section 31 is greater than the second volume of the second compression section 32, the compression power of the first compression section 31 is greater than the compression power of the second compression section 32. At this time, the cooling element is arranged on a side close to the first compression section 31, and the flow airflow generated by the cooling element will flow through the first compression section 31 and the second compression section 32 in sequence, which better ensures that the first compression section 31 with greater compression power can obtain sufficient heat dissipation, and also better ensures that the first compression section 31 maintains good working performance.

[0068] Preferably, please combine Figure 3 and Figure 4 As shown, the compression component 3 further comprises a cylinder base body 36, an exhaust portion 33, a first air intake portion 34, and a second air intake portion 35. The exhaust portion 33, the first air intake portion 34, and the second air intake portion 35 are all fixedly connected to the cylinder base body 36, and the first compression portion 31 and the second compression portion 32 are both molded and disposed within the cylinder base body 36. The fixed connection here can be a detachable connection. For example, the exhaust portion 33 is an exhaust pipe joint provided with an exhaust through hole, and the exhaust pipe joint is threadedly connected to the cylinder base body 36. The fixed connection here can also be a welded connection or can be integrally molded to ensure that the compression component 3 as a whole has good structural strength and good sealing performance.

[0069] Please refer to the following for details: Figure 1 、 Figure 2 and Figure 5 As shown, the first air intake section 34 is connected to the first compression section 31, and the first evaporator 1 is connected to the first air intake section 34, so that the refrigerant provided by the first evaporator 1 can be transported to the first compression section 31 for compression. The exhaust section 33 and the second air intake section 35 are both connected to the second compression section 32, and the second evaporator 2 is connected to the second air intake section 35, so that the refrigerant provided by the second evaporator 2 can be transported to the second compression section 32 for compression. Optionally, the exhaust section 33 of the compression component 3 is connected to the condensation inlet of the condenser assembly 4, so that the compressed refrigerant can be output from the exhaust section 33 to the condenser assembly 4, and the first evaporator 1 and the second evaporator 2 are both connected to the condensation outlet of the condenser assembly 4, thereby achieving the purpose of refrigerant circulation and circulation.

[0070] As a preferred method of this embodiment, please refer to Figure 4As shown, the first compression part 31 and the second compression part 32 are configured independently, and the compression component 3 further has a first inner flow channel 371 and a second inner flow channel 372, wherein the first inner flow channel 371 includes a first inlet flow channel 3711 formed between the first air intake part 34 and the first compression part 31, and a first outlet flow channel 3712 formed between the exhaust part 33 and the first compression part 31, one end of the first inlet flow channel 3711 is connected to the first air intake port / first air intake pipe of the first air intake part 34, and the first inlet flow channel 3711 is connected to the first air intake port / first air intake pipe of the first air intake part 34. The other end is connected to the first compression part 31, and the refrigerant will flow into the first compression part 31 under the guidance of the first inlet channel 3711. One end of the first outlet channel 3712 is connected to the first compression part 31, and the other end of the first outlet channel 3712 is connected to the exhaust hole of the exhaust part 33. The compressed refrigerant will flow to the exhaust part 33 under the guidance of the first outlet channel 3712 and be output from the exhaust part 33. In this way, the exhaust part 33 and the first intake part 34 are both connected to the first compression part 31 through the first inner channel 371.

[0071] Alternatively, as Figure 4 As shown, the second inner flow channel 372 includes a second inlet flow channel 3721 formed between the second intake section 35 and the second compression section 32, and a second outlet flow channel 3722 formed between the exhaust section 33 and the second compression section 32. One end of the second inlet flow channel 3721 is connected to the second intake port / second intake pipe of the second intake section 35, and the other end of the second inlet flow channel 3721 is connected to the second compression section 32. The refrigerant will flow into the second compression section 32 under the guidance of the second inlet flow channel 3721, one end of the second outlet flow channel 3722 is connected to the second compression section 32, and the other end of the second outlet flow channel 3722 is connected to the exhaust through hole of the exhaust section 33. The compressed refrigerant will flow to the exhaust section 33 under the guidance of the second outlet flow channel 3722 and be output from the exhaust section 33. In this way, the exhaust section 33 and the second intake section 35 are both connected to the second compression section 32 through the second inner flow channel 372.

[0072] Thus, the independently configured first and second compression sections 31, 32 facilitate the formation of two compression cylinders with different capacities, thereby improving the smoothness of refrigerant output and the ability to dynamically match the actual load. Furthermore, this effectively ensures higher volumetric efficiency and a lower compression ratio, while also reducing bearing stress and improving dynamic balance. This results in high overall reliability of the compression element 3, a simple structure, and reduced manufacturing costs.

[0073] As another preferred method of this embodiment, please refer to Figure 3As shown, the compression component 3 also has a primary flow channel 381, a secondary flow channel 382, ​​a total exhaust flow channel 383 and an intermediate mixing cylinder 384. The first compression part 31 is connected to the second compression part 32 through the intermediate mixing cylinder 384, and the first suction part 34 is connected to the first compression part 31 through the primary flow channel 381. That is, one end of the primary flow channel 381 is connected to the first suction port / first suction pipe of the first suction part 34, and the other end of the primary flow channel 381 is connected to the first compression part 31. Then, the refrigerant will flow into the first compression part 31 under the guidance of the primary flow channel 381, and the second suction part 35 will flow into the first compression part 31 through the secondary flow channel. 382 is connected to the intermediate mixing cylinder 384, that is, one end of the secondary flow channel 382 is connected to the second intake port / second intake pipe of the second intake part 35, and the other end of the secondary flow channel 382 is connected to the intermediate mixing cylinder 384. The refrigerant will flow into the intermediate mixing cylinder 384 under the guidance of the secondary flow channel 382, ​​mix with the refrigerant compressed by the first compression part 31, and flow to the second compression part 32 together. The exhaust part 33 is connected to the second compression part 32 through the total exhaust flow channel 383. In this way, the compressed refrigerant will flow to the exhaust part 33 under the guidance of the total exhaust flow channel 383 and be output from the exhaust part 33.

[0074] With this arrangement, the refrigerant is buffered and pressure-stabilized in the intermediate mixing cylinder 384, while also lowering the temperature and reducing energy consumption. It is understandable that the refrigerant compressed by the first compression section 31 is cooled so that the second compression section 32 can be further compressed efficiently, thereby reducing the suction temperature of the second compression section 32 and slowing down the deterioration rate of the lubricating oil at high temperatures, improving the lubrication condition of the bearings and other moving parts, and helping to extend the service life of the compression section 3. This can better achieve the effect of approaching isothermal compression, thereby improving the overall efficiency, compression energy efficiency, and volumetric efficiency of the compression section 3, reducing heat loss and internal leakage, and greatly reducing the load on the bearings in the compression section 3, thereby effectively extending the service life of the bearings in the compression section 3 and the service life of the compression section 3.

[0075] As another preferred embodiment of the present invention, the first compression section 31 and the second compression section 32 are both independently arranged compressors. The first compression section 31 is used to independently compress and process the refrigerant flowing through the first evaporator 1, and the second compression section 32 is used to independently compress and process the refrigerant flowing through the second evaporator 2, or to compress and process the refrigerant flowing through the second evaporator 2 and mixed with the refrigerant compressed and output by the first compression section 31.

[0076] As one of the further preferred manners, the first compression part 31 has a total output port and a total input port, the second compression part 32 has a total discharge port, a first injection end and a second injection end, the total output port of the first compression part 31 is connected to the first injection end of the second compression part 32, and the total input port of the first compression part 31 is connected to the first evaporator 1, so that the refrigerant provided by the first evaporator 1 can be delivered into the first compression part 31 for compression, and the refrigerant compressed by the first compression part 31 is delivered into the second compression part 32, the second injection end of the second compression part 32 is connected to the second evaporator 2, so that the refrigerant compressed by the first compression part 31 is mixed with the refrigerant provided by the second evaporator 2, and then compressed by the second compression part 32, and the total discharge port of the second compression part 32 is connected to the condensing inlet of the condenser assembly 4.

[0077] In addition to the above preferred manners, as one of the further preferred manners, the first compression part 31 has a total output port, a first input end and a second input end, the second compression part 32 has a total discharge port, a first injection end and a second injection end, the total output port of the first compression part 31 is connected to the first injection end of the second compression part 32, and the first input end or the second input end of the first compression part 31 is connected to the first evaporator 1, so that the refrigerant provided by the first evaporator 1 can be delivered into the first compression part 31 for compression, and the refrigerant compressed by the first compression part 31 is delivered into the second compression part 32, the second injection end of the second compression part 32 is connected to the second evaporator 2, and the total discharge port of the second compression part 32 is connected to the condensing inlet of the condenser assembly 4. In this way, the two-stage compression of the refrigerant is realized by the cooperation of the first compression part 31 and the second compression part 32.

[0078] As one of the further preferred manners, the heat pump circulation system further comprises a three-way connector, the first compression part 31 has a total output port and a total input port, the second compression part 32 has a total discharge port and a total injection port, the total input port of the first compression part 31 is connected to the first evaporator 1, so that the refrigerant provided by the first evaporator 1 can be delivered into the first compression part 31 for single compression, the total injection port of the second compression part 32 is connected to the second evaporator 2, so that the refrigerant provided by the second evaporator 2 can be delivered into the second compression part 32 for single compression, and the total output port of the first compression part 31, the total discharge port of the second evaporator 2 and the condensing inlet of the condenser assembly 4 are all connected to the three-way connector.

[0079] In this way, the refrigerant provided by the first evaporator 1 and the second evaporator 2 is compressed separately by the cooperation of the first compression part 31 and the second compression part 32, and then flows into the three-way connector and is delivered to the condenser assembly 4.

[0080] In the present embodiment, the specific connection relationship between the first compression part 31, the second compression part 32, the first evaporator 1, the second evaporator 2 and the condenser assembly 4 can be determined according to the actual needs. Figure 1、 Figure 2 and Figure 5 As shown, the heat pump circulation system also includes a flow regulating member arranged between the evaporator assembly and the condenser assembly 4. The flow regulating member is preferably an expansion valve, which can also be called a throttle valve or a regulating valve. The flow regulating member is used to regulate and control the flow of the refrigerant flowing from the condenser assembly 4 to the evaporator assembly, thereby ensuring that the heat pump circulation system operates under optimal working conditions, and realizes rapid cooling of the evaporator assembly and / or heating of the condenser assembly 4, and precise temperature control and energy saving.

[0081] It should also be noted that the throttling and pressure-reducing action of the flow regulator allows medium-temperature, high-pressure / high-pressure, subcooled liquid refrigerant to pass through the regulator and become low-temperature, low-pressure mist refrigerant, thereby reducing the refrigerant pressure and allowing the refrigerant to evaporate and absorb heat more easily in the evaporator assembly. Furthermore, the flow regulator provides a stable superheat level, meaning it can control the valve flow rate based on changes in the superheat level at the end of the evaporator assembly, preventing underutilization of the evaporator assembly area and cylinder knocking, thereby ensuring more stable operation of the heat pump circulation system.

[0082] As one of the preferred methods of this embodiment, please refer to Figure 1 As shown, the flow regulating component includes a main regulating valve 71 with a throttling and pressure-reducing function. One end of the main regulating valve 71 is connected to the condenser assembly 4, and the first evaporator 1 and the second evaporator 2 are both connected to the other end of the main regulating valve 71. In other words, the evaporator assembly is connected to the condenser assembly 4 via a connecting pipe assembly, which includes a first connecting pipe 81 connected to the first evaporator 1, a second connecting pipe 82 connected to the second evaporator 2, and a main connecting pipe 83 connected to the condenser assembly 4.

[0083] It is understood that the first connecting pipe 81 and the second connecting pipe 82 can be integrally formed or connected by a pipe connector (such as a threaded connection, a press connection, etc.), and the main regulating valve 71 is installed on the main connecting pipe 83. This arrangement allows the refrigerant flowing through the first connecting pipe 81 and the second connecting pipe 82 to be throttled and regulated by the main regulating valve 71, making it easier to adjust the system operating conditions and more stable in overall cooling capacity.

[0084] Optionally, please refer to Figure 1As shown, the flow regulating member further comprises a branch regulating valve 72 having throttling pressure reduction and flow regulating functions, the branch regulating valve 72 being connected to at least one of the first evaporator 1 and the second evaporator 2, i.e. the branch regulating valve 72 being arranged in at least one of the first connecting pipe 81 and the second connecting pipe 82. That is, by means of the throttling pressure reduction and flow regulating functions of the branch regulating valve 72, the refrigerant pressure flowing through the first connecting pipe 81 and / or the second connecting pipe 82 is more stable, and more sufficient atomization is performed, so that the operation of the heat pump circulation system can be more stable, and the reliability of the heat pump circulation system is improved.

[0085] As another preferred mode of the present embodiment, please refer to Figure 2 and Figure 5 As shown, the flow regulating member comprises a first expansion valve 73 and a second expansion valve 74, the first expansion valve 73 being connected to the first evaporator 1 to regulate the flow of refrigerant into the first evaporator 1, and the state of the refrigerant is changed to low temperature and low pressure under the throttling action of the first expansion valve 73, and the second expansion valve 74 being connected to the second evaporator 2 to regulate the flow of refrigerant into the second evaporator 2, and the state of the refrigerant is changed to low temperature and low pressure under the throttling action of the second expansion valve 74.

[0086] In this way, the first expansion valve 73 throttles and adjusts the refrigerant flowing through the first evaporator 1 alone, and the second expansion valve 74 throttles and adjusts the refrigerant flowing through the second evaporator 2 alone, so that the flow regulating range of the entire heat pump circulation system is larger, the adjustment flexibility is higher, and the adjustment operation is more convenient. Moreover, the working condition of the heat pump circulation system is reflected more quickly.

[0087] In the above, by configuring the first compression part 31 and the second compression part 32 with different volumes in the compression component 3, the problem of excessively high load and requirement of the compression component 3 in the case of high condensation temperature and low evaporation temperature can be avoided. However, since the temperature sensor in the existing heat pump clothes dryer is used to monitor the temperature of the refrigerant, such a way usually misses the heat exchange efficiency of the evaporator assembly, which easily leads to the phenomenon that the air temperature after flowing through the evaporator assembly is still much higher than the refrigerant temperature inside the evaporator assembly, resulting in heat exchange deviation. Since the heat exchange deviation caused by the evaporator assembly is a technical problem that is generally easily ignored by those skilled in the art, therefore, the existing heat pump clothes dryer basically has the problem of deviation of cooling and dehumidifying effect.

[0088] In view of the above technical problems, the utility model discloses a technical scheme, the inside of the machine body still has control circuit board, and the inside of the fluid channel is provided with evaporation temperature sensing element and condensation temperature sensing element, wherein the evaporation temperature sensing element is used to detect the temperature of the flowing air after flowing through the evaporator assembly and generate an evaporation air temperature value, the condensation temperature sensing element is used to detect the temperature of the flowing air after flowing through the condenser assembly 4 and generate a condensation temperature value, the first evaporator 1, the second evaporator 2, the evaporation temperature sensing element, the condensation temperature sensing element, the above-mentioned compression component 3 and the above-mentioned condenser assembly 4 are all electrically connected to the control circuit board, and the control circuit board can adjust the evaporation temperature of the first evaporator 1 and / or the evaporation temperature of the second evaporator 2 according to the evaporation air temperature value and the condensation temperature value.

[0089] In this way, the evaporation temperature sensing element can obtain the temperature information of the flowing air after flowing through the evaporator assembly in time, generate an evaporation air temperature value and then transmit it to the control circuit board, so that the control circuit board can monitor the temperature value and its change after the flowing air is cooled by the evaporator assembly in real time and directly, and compare the evaporation air temperature value with the set temperature value to determine whether to send a control instruction to the evaporation temperature sensing element. At this time, the control circuit board can most directly and accurately monitor the evaporation air temperature value of the flowing air after heat exchange with the evaporator assembly, and the error / deviation of temperature monitoring is eliminated to the greatest extent. The control circuit board can also more accurately and in real time monitor the change of the flowing air during the entire drying process.

[0090] Meanwhile, in cooperation with the second evaporator 2 and the first evaporator 1, when the control circuit board determines that the evaporation air temperature value exceeds the set temperature value, the temperature of the air can be adjusted to the set temperature value in a shorter time, thereby ensuring that the clothes treatment equipment maintains good cooling and dehumidifying effect.

[0091] For example, the evaporation air temperature value is much greater than the upper limit temperature value of the set temperature value, so the evaporation temperature of the second evaporator 2 and the first evaporator 1 can be lowered at the same time, so that the flowing air can absorb more heat when flowing through the second evaporator 2 and the first evaporator 1, thereby reducing the temperature of the flowing air more quickly, so that the evaporation air temperature value can be adjusted to the set temperature value in time and significantly.

[0092] For example, the evaporation air temperature value is slightly less than the lower limit temperature value of the set temperature value, so the evaporation temperature of one of the second evaporator 2 and the first evaporator 1 can be increased, so that the heat absorbed by the flowing air when flowing through one of the second evaporator 2 and the first evaporator 1 is reduced, thereby adjusting the evaporation air temperature value to the set temperature value.

[0093] In addition, using the control circuit board to monitor the evaporation air temperature value and the condensation temperature value can not only better realize the operation of the heat pump circulation system stably maintaining a low evaporation temperature and a high condensation temperature, but also avoid the temperature of the air flowing into the drum component 5 being too high and damaging the clothes.

[0094] The control circuit board also uses the evaporating air temperature and condensing temperature values ​​to preliminarily assess the operating status of the compression unit 3. Specifically, the evaporating air temperature value reflects the intake state of the compression unit 3 to a certain extent, while the condensing temperature value reflects the exhaust state of the compression unit 3 to a certain extent. A comprehensive assessment based on other parameters of the compression unit 3, such as pressure, current, and power, enables a more efficient and accurate diagnosis of the operation of the compression unit 3, ensuring the stable performance of the heat pump circulation system.

[0095] As a further preferred embodiment of this embodiment, the above-mentioned evaporative temperature sensor includes a first detection member and a second detection member, wherein the first detection member is used to detect the temperature of the air flowing through the first evaporator 1 and generate a first temperature value, and the second detection member is used to detect the temperature of the air flowing through the second evaporator 2 and generate a second temperature value. The second temperature value is the evaporation wind temperature value of the evaporative temperature sensor. Of course, it can also be a temperature value calculated by combining the first temperature value and the second temperature value. In addition, the control circuit board can adjust the evaporation temperature of the first evaporator 1 and the evaporation temperature of the second evaporator 2 according to the first temperature value and the second temperature value.

[0096] Such a setting can not only more accurately monitor the evaporation temperature of the first evaporator 1 and the evaporation temperature of the second evaporator 2, but also better adjust the matching between the evaporation temperature of the first evaporator 1 and the second evaporator 2, so as to more effectively ensure that the evaporation temperature of the evaporator assembly as a whole is maintained within a more stable and better temperature range, that is, to ensure that the evaporation wind temperature value generated after the detected air flows through the evaporator assembly is stably within the set temperature value, thereby achieving the best cooling and dehumidification effect, thereby ensuring that the clothing processing equipment has good drying effect and drying quality, and effectively saving the energy consumption of the clothing processing equipment.

[0097] Preferably, the first detection element is installed on the side close to the air outlet of the first evaporator 1, and / or the second detection element is installed on the side close to the air outlet of the second evaporator 2. Such an arrangement will have the following unexpected effects:

[0098] 1. The temperature of the air flowing through the first evaporator 1 and the second evaporator 2 will be more directly measured, which can very accurately reflect the actual cooling effect of the first evaporator 1 and the second evaporator 2. This allows the heat pump circulation system to make timely adjustments based on this temperature value, ensuring that the output air temperature always remains within the set temperature value.

[0099] 2. The first detection element will be able to more quickly sense changes in the operating status of the first evaporator 1, and the second detection element will also be able to more quickly sense changes in the operating status of the second evaporator 2. When the cooling capacity of either evaporator 1 or evaporator 2 changes, such as due to changes in refrigerant flow or surface dust accumulation, the corresponding detection element in the evaporating temperature sensor will be able to quickly detect the temperature fluctuation and transmit the signal to the control circuit board. This allows the heat pump circulation system to make adjustments more quickly, improving its stability and response speed.

[0100] 3. It helps in fault diagnosis. If the heat pump circulation system fails, such as one of the first evaporator 1 and the second evaporator 2 is blocked, the refrigerant leaks, etc., the corresponding air outlet temperature of the first evaporator 1 and the second evaporator 2 will change significantly. Maintenance personnel can quickly determine the approximate location and type of the fault by reading the data of the corresponding detection element in the evaporation temperature sensor. For example, if the air outlet temperature of one of the first evaporator 1 and the second evaporator 2 is always high, it may mean that the corresponding refrigeration capacity of the first evaporator 1 and the second evaporator 2 has decreased, and it is necessary to check whether the refrigerant is insufficient or blocked.

[0101] The above is an explanation of the heat pump circulation system proposed in the embodiment of the present application. Since the clothing processing device proposed in the embodiment of the present application adopts all the technical solutions of all the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, which will not be repeated here one by one.

[0102] The same or similar numbers in the drawings of this embodiment correspond to the same or similar parts; in the description of this application, it should be understood that if the terms "up", "down", "left", "right", etc. indicate directions or positional relationships, they are based on the directions or positional relationships shown in the drawings. This is only for the convenience of describing this application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes and cannot be understood as limiting this application. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0103] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principles of the present application should be included in the scope of protection of the present application.

Claims

1. A heat pump circulation system, characterized in that: include: an evaporator assembly, the evaporator assembly comprising a first evaporator and a second evaporator connected in parallel; a compression component, the compression component comprising a first compression portion and a second compression portion, the first compression portion being connected to the first evaporator, and the second compression portion being connected to the second evaporator; A condenser assembly, the evaporator assembly, the compression component and the condenser assembly form a heat exchange circuit, and the heat exchange circuit includes a first circuit consisting of the first evaporator, the first compression part, the second compression part and the condenser assembly, and a second circuit consisting of the second evaporator, the second compression part and the condenser assembly.

2. The heat pump circulation system according to claim 1, characterized in that: The first volume of the first compression part and the second volume of the second compression part are arranged in proportion, so that the flow rates flowing through the first evaporator and the second evaporator are different.

3. The heat pump circulation system according to claim 1 or 2, characterized in that: The compression component also has an exhaust part, a first intake part and a second intake part. The first intake part is connected to the first compression part, and the exhaust part and the second intake part are both connected to the second compression part. The first evaporator is connected to the first intake part, and the second evaporator is connected to the second intake part. The exhaust part of the compression component is connected to the condensation inlet of the condenser assembly, and the first evaporator and the second evaporator are both connected to the condensation outlet of the condenser assembly.

4. The heat pump circulation system according to claim 3, characterized in that: The first compression part and the second compression part are configured independently, and the compression component also has a first internal flow channel and a second internal flow channel. The exhaust part and the first intake part are both connected to the first compression part through the first internal flow channel, and the exhaust part and the second intake part are both connected to the second compression part through the second internal flow channel.

5. The heat pump circulation system according to claim 3, characterized in that: The compression component also has a primary flow channel, a secondary flow channel, a total exhaust flow channel and an intermediate mixing cylinder. The first compression part is connected to the second compression part through the intermediate mixing cylinder. The first intake part is connected to the first compression part through the primary flow channel, the second intake part is connected to the intermediate mixing cylinder through the secondary flow channel, and the exhaust part is connected to the second compression part through the total exhaust flow channel.

6. The heat pump circulation system according to claim 1 or 2, characterized in that: The first compression part and the second compression part are both independently arranged compressors. The first compression part is used to independently compress and process the refrigerant flowing through the first evaporator, and the second compression part is used to independently compress and process the refrigerant flowing through the second evaporator, or compress and process the refrigerant flowing through the second evaporator and mixed with the refrigerant compressed and output by the first compression part.

7. The heat pump circulation system according to claim 6, characterized in that: The first compression section has a total output port and a total input port, the second compression section has a total discharge port, a first injection end and a second injection end, the total output port of the first compression section is connected to the first injection end of the second compression section, the total input port of the first compression section is connected to the first evaporator, the second injection end of the second compression section is connected to the second evaporator, and the total discharge port of the second compression section is connected to the condensation inlet of the condenser assembly.

8. The heat pump circulation system according to claim 6, characterized in that: It also includes a three-way connector, the first compression part has a total output port and a total input port, the second compression part has a total discharge port and a total injection port, the total input port of the first compression part is connected to the first evaporator, the total injection port of the second compression part is connected to the second evaporator, the total output port of the first compression part, the total discharge port of the second evaporator, and the condensation inlet of the condenser assembly are all connected to the three-way connector.

9. The heat pump circulation system according to claim 6, characterized in that: The first compression section has a total output port, a first input end and a second input end, and the second compression section has a total discharge port, a first injection end and a second injection end. The total output port of the first compression section is connected to the first injection end of the second compression section, the first input end or the second input end of the first compression section is connected to the first evaporator, the second injection end of the second compression section is connected to the second evaporator, and the total discharge port of the second compression section is connected to the condensation inlet of the condenser assembly.

10. The heat pump circulation system according to claim 2, wherein: The compression component further includes a cooling element for cooling the first compression portion and the second compression portion.

11. The heat pump circulation system according to claim 10, characterized in that: The cooling element is a fan, and the number of the cooling elements is configured to be two. The cooling element used to cool the first compression part is defined as a first heat sink, and the cooling element used to cool the second compression part is defined as a second heat sink. The power ratio between the first heat sink and the second heat sink is the same as the volume ratio between the first compression part and the second compression part.

12. The heat pump circulation system according to claim 10, wherein: The cooling element is a fan, and the number of the cooling elements is configured to be one. The first compression part and the second compression part are both on the gas flow path of the cooling element, and the gas flow direction generated by the cooling element is from the first compression part with greater power to the other compression part with less power.

13. The heat pump circulation system according to claim 1 or 2, characterized in that: It also includes a flow regulating member disposed between the evaporator assembly and the condenser assembly, and the flow regulating member is used to regulate and control the flow of the refrigerant flowing from the condenser assembly to the evaporator assembly.

14. The heat pump circulation system according to claim 13, wherein: The flow regulating component includes a main regulating valve with a throttling and pressure reduction function. One end of the main regulating valve is connected to the condenser assembly, and the first evaporator and the second evaporator are both connected to the other end of the main regulating valve.

15. The heat pump circulation system according to claim 14, wherein: The flow regulating member further includes a branch regulating valve having functions of throttling, reducing pressure and regulating flow, and the branch regulating valve is connected to at least one of the first evaporator and the second evaporator.

16. The heat pump circulation system according to claim 13, wherein: The flow regulating component includes a first expansion valve and a second expansion valve. The first expansion valve is connected to the first evaporator to regulate the flow of refrigerant flowing into the first evaporator, and changes the state of the refrigerant to low temperature and low pressure under its throttling effect. The second expansion valve is connected to the second evaporator.

17. A clothes processing device, characterized in that: include: The heat pump circulation system according to any one of claims 1 to 16; The heat pump circulation system and the clothes processing chamber form an air circulation path.

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