Heat pump circulation system and clothes treatment equipment

Abstract

The invention 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 invention 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] This application relates to the field of clothing processing devices, and in particular to a heat pump circulation system and clothing processing equipment. Background Technology

[0002] In related technologies, heat pump dryers utilize the condensation heat of the refrigerant to heat the clothes, causing the moisture in the clothes to turn into water vapor. This water vapor is then released through evaporation, achieving dryness without exhaust. To improve the drying speed of existing heat pump dryers, auxiliary heating (such as electric auxiliary heating) is typically activated during the fast drying mode to increase the temperature of the air flowing into the drum, thereby accelerating the evaporation of moisture from the clothes.

[0003] However, considering that clothes are easily damaged by high temperatures during the drying process, auxiliary heating cannot be increased indefinitely. Furthermore, the energy efficiency of electric auxiliary heating is far lower than that of a heat pump system, significantly increasing the dryer's energy consumption. To address the shortcomings of electric auxiliary heating, existing dryers use an alternative method to improve drying speed—by lowering the evaporator's evaporation temperature to enhance its dehumidification capacity. Because the condenser temperature in a heat pump dryer is high to ensure the temperature of the air flowing into the drum, a low evaporation temperature means lower pressure within the evaporator, while a high condensation temperature corresponds to higher pressure. The compressor needs to compress the low-pressure gas from the evaporator to the high-pressure state required by the condenser, leading to an increased compression ratio. This also increases the compressor's load, accelerates wear, and shortens its lifespan. This combination of low evaporation temperature and high condensation temperature in a heat pump system places higher demands on the compressor. Summary of the Invention

[0004] This application provides a heat pump cycle system and clothing processing equipment that can reduce the compressor load and compression ratio at low evaporation temperatures and high condensation temperatures.

[0005] In a first aspect, embodiments of this application provide a heat pump cycle system, the heat pump cycle system comprising:

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

[0007] A compression component, the compression component having a first compression section and a second compression section, the first compression section being connected to the first evaporator, and the second compression section being connected to the second evaporator;

[0008] A condenser assembly, wherein 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 component and the condenser assembly, and a second circuit consisting of the second evaporator, the second compression component and the condenser assembly.

[0009] In one embodiment, the first volume of the first compression section and the second volume of the second compression section are configured in a proportional manner, such that the flow rates through the first evaporator and the second evaporator are different.

[0010] In one embodiment, the compression component further includes 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. 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 section and the second compression section are independently configured. The compression section also has a first inner flow channel and a second inner flow channel. The exhaust section and the first intake section are both connected to the first compression section through the first inner flow channel, and the exhaust section and the second intake section are both connected to the second compression section through the second inner flow channel.

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

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

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

[0015] In one embodiment, the heat pump cycle system further includes a three-way connector, the first compression section having a total output port and a total input port, the second compression section having a total discharge port and a total injection port, the total input port of the first compression section being connected to the first evaporator, the total injection port of the second compression section being connected to the second evaporator, and the total output port of the first compression section, the total discharge port of the second evaporator, and the condenser inlet of the condenser assembly being connected to the three-way connector.

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

[0017] In one embodiment, the compression component further includes a cooling element for cooling the first compression section and the second compression section.

[0018] In one embodiment, the cooling element is a fan, and the number of cooling elements is configured to be two. The cooling element used to cool the first compression section is defined as a first heat sink, and the cooling element used to cool the second compression section 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 and the second compression section.

[0019] In one embodiment, the cooling element is a fan, and the number of cooling elements is one. The first compression section and the second compression section are both on the gas flow path of the cooling element, and the gas flow direction generated by the cooling element is from the one with greater power to the other with less power.

[0020] In one embodiment, the heat pump cycle system further includes a flow regulator disposed between the evaporator assembly and the condenser assembly, the flow regulator being used to regulate and control the flow rate of refrigerant from the condenser assembly to the evaporator assembly.

[0021] In one embodiment, the flow regulating element includes a main regulating valve with throttling and pressure reduction function, one end of which 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 regulator further includes a branch regulating valve having throttling and pressure reduction and flow regulation functions, the branch regulating valve being 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 connects the first evaporator to regulate the flow rate 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 connects the second evaporator.

[0024] Secondly, embodiments of this application provide a garment processing device, which includes:

[0025] The aforementioned heat pump cycle system;

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

[0027] Based on the above embodiments, the heat pump cycle system proposed in this application includes:

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

[0029] The compression component has a first compression section and a second compression section, the first compression section being connected to the first evaporator and the second compression section being connected to the second evaporator;

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

[0031] Compared to related technologies, the technical solution of this application, by configuring a first compression section and a second compression section with different volumes in the compression component, can adjust and control the refrigerant flow through the first and second evaporators. This, in conjunction with the first and second evaporators, effectively reduces the evaporation temperature of the evaporator assembly while maintaining a high condensing temperature. Furthermore, it can reduce the compression ratio of the compression component, thereby solving the problem of excessively high load and requirements caused by existing compressors under low evaporation temperature conditions. Attached Figure Description

[0032] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0033] Figure 1 This is a schematic diagram of the first arrangement of a heat pump cycle system according to an embodiment of the present invention;

[0034] Figure 2 This is a schematic diagram of the second arrangement of a heat pump cycle system according to an embodiment of the present invention;

[0035] Figure 3 This is a schematic diagram of the first structure of the compression component in one embodiment of the present invention;

[0036] Figure 4 This is a schematic diagram of the second structure of the compression component in one embodiment of the present invention;

[0037] Figure 5 This is a schematic diagram of the circulation loop of a clothing processing device according to an embodiment of the present invention.

[0038] Explanation of icon numbers:

[0039] 1-First evaporator, 2-Second evaporator, 3-Compression component, 31-First compression section, 32-Second compression section, 33-Exhaust section, 34-First intake section, 35-Second intake section, 36-Cylinder seat 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-Main exhaust flow channel, 384-Intermediate mixing cylinder, 4-Condenser assembly, 5-Drum assembly, 6-Drive 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 purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0041] To make the objectives, technical solutions, and advantages of this application clearer, the embodiments of this application will be described in further detail below with reference to the accompanying drawings.

[0042] Where the following description relates to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this 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 construed as indicating or implying relative importance. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances. Furthermore, in the description of this application, unless otherwise stated, "multiple" refers to two or more. "And / or" describes the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. The character " / " generally indicates that the preceding and following related 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 one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of this application. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0045] Please refer to the specific details. Figure 5 As shown, this application proposes a garment processing device for drying garments. This device utilizes heat energy to raise the temperature of flowing air, heating it into dry, hot air. As the dry, hot air flows over the damp garments, it carries away some of the moisture. After passing over the damp garments, the dry, hot air transforms into humid, hot air, which is then dehumidified and reheated before being recirculated back to the damp garments. This cycle is repeated until the damp garments are completely dried.

[0046] This solution employs a heat pump drying principle. The garment processing equipment includes a heat pump circulation system and a machine body. The machine body has a garment processing chamber. For example, the machine body contains a drum component 5 with an inner cavity for placing and drying clothes. This inner cavity is the garment processing chamber of the machine body. The drum component 5 rotates under the drive of a motor, allowing the clothes to tumble within the processing chamber. This ensures that each piece of damp clothing is thoroughly dried by hot, dry air and improves the drying efficiency. Alternatively, the machine body's inner drying chamber can also serve as the garment processing chamber, where each piece of damp clothing is hung for thorough drying by hot, dry air. The heat pump circulation system and the garment processing chamber form an airflow circulation path, allowing for continuous drying of damp clothing.

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

[0048] The heat exchange circuit is a heat exchange circuit in which the refrigerant circulates. The heat exchange circuit includes a first circuit consisting of a first evaporator 1, a first compression section 31, and a condenser assembly 4, and a second circuit consisting of a second evaporator 2, a first compression section 31, a second compression section 32, and a condenser assembly 4.

[0049] Optionally, the machine body is provided with an internal circulation drying duct. The first evaporator 1, the second evaporator 2, the condenser assembly 4, and the drum assembly 5 are arranged in sequence along the flow path of the internal circulation air in the internal circulation drying duct. Then, the clothes processing chamber, the internal circulation drying duct, and the first evaporator 1, the second evaporator 2, the condenser assembly 4, and the drum assembly 5 of the machine body will sequentially form an airflow circulation path.

[0050] In this airflow circulation path, the compression component 3 draws in low-pressure, low-temperature gaseous refrigerant and compresses it into high-pressure, high-temperature gaseous refrigerant through mechanical motion, providing power for the closed loop and delivering it to the condenser assembly 4. The high-temperature, high-pressure gaseous refrigerant liquefies at constant pressure in the condenser assembly 4, releasing heat and cooling into high-pressure subcooled liquid refrigerant. The large amount of heat released by the condenser assembly 4 is transferred to the flowing air, heating it into dry, hot air. The high-pressure subcooled liquid refrigerant is throttled by the flow regulator to become low-temperature, low-pressure mist refrigerant, which then evaporates in the first evaporator 1 and the second evaporator 2, absorbing heat from the flowing air to form low-temperature, low-pressure gaseous refrigerant, which is then delivered back to the compression component 3. Moisture in the humid air condenses into water droplets upon cooling and is discharged, thus transforming the humid air into dry, cold air. This dry, cold air is then reheated into dry, hot air as it flows through the condenser assembly 4, and the cycle continues in this manner.

[0051] To achieve the directionality and stability of the airflow within the machine's internal circulation drying tunnel, please refer to the specific instructions. Figure 5 As shown, the machine body also has a drive fan 6 inside. This drive fan 6 can be either a blower or an exhaust fan. The drive fan 6 is located on the internal circulation drying tunnel, that is, on the path of the gas circulation loop. Preferably, the second evaporator 2 and the condenser assembly 4 of the evaporator assembly are respectively located 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 sequentially through the condenser assembly 4, the drum component 5, and the second evaporator 2 and the first evaporator 1 of the evaporator assembly within the internal circulation drying tunnel.

[0052] With this configuration, since the first evaporator 1 and the second evaporator 2 are connected in parallel, the evaporation pressure of the first evaporator 1 and the second evaporator 2 can be adjusted independently, thereby setting or changing the evaporation temperature of the first evaporator 1 and the second evaporator 2. The first evaporator 1 and the second evaporator 2 work together to condense and remove moisture in the humid air, achieving dehumidification. Specifically, as the moisture in the humid air flows through the second evaporator 2, it exchanges heat with the evaporator 2, absorbing heat and lowering the temperature of the humid air. Some of the moisture then condenses into water droplets and is discharged, achieving initial dehumidification. Conversely, as the moisture in the humid air flows through the first evaporator 1, it exchanges heat with the evaporator 1, further lowering the temperature. The remaining moisture then condenses into water droplets and is discharged, achieving secondary dehumidification.

[0053] Understandably, the evaporation temperature of the first evaporator 1 can be lower than that of the second evaporator 2. Define the first evaporator 1 as a low-temperature evaporator and the second evaporator 2 as a high-temperature evaporator. In the gas circulation loop, the flowing air 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 exiting the clothing processing chamber and the evaporation temperature of the second evaporator 2. Simultaneously, the significant temperature difference between the humid air after passing through the second evaporator 2 and the evaporation temperature of the first evaporator 1 also guarantees good heat exchange efficiency for the first evaporator 1. This further ensures the dehumidification effect of the evaporator assembly, shortens the drying time, improves the drying efficiency, and saves energy for the clothing processing equipment.

[0054] Of course, the evaporation temperature of the first evaporator 1 can be higher than that of the second evaporator 2. Defining the first evaporator 1 as a high-temperature evaporator and the second evaporator 2 as a low-temperature evaporator, the flowing air sequentially passes through the low-temperature evaporator, the high-temperature evaporator, and the condenser assembly 4 in the gas circulation loop. This creates a significant temperature difference between the temperature of the humid air and the evaporation temperature of the second evaporator 2, thereby improving the heat exchange efficiency of the second evaporator 2 and absorbing heat from the humid air more efficiently, thus better removing moisture and maximizing the dehumidification effect. Since a temperature difference still exists between the temperature of the humid air after passing through the second evaporator 2 and the evaporation temperature of the first evaporator 1, the good dehumidification effect of the secondary dehumidification of the humid air can be effectively guaranteed.

[0055] An unexpected effect is that the temperature difference between the humid air flowing through the second evaporator 2 and the evaporation temperature of the first evaporator 1 is relatively small, resulting in less heat being absorbed by the humid air. Consequently, the temperature of the air flowing through the condenser assembly 4 increases, thereby raising the temperature of the air flowing into the garment processing chamber. This has a certain benefit on the drying time of the garments and improves the drying efficiency.

[0056] In summary, by cooperating with the first evaporator 1 and the second evaporator 2, the evaporation temperature of the evaporator assembly can be effectively reduced while maintaining a high condensation temperature, thereby maximizing the dehumidification effect of the evaporator assembly. To avoid the problems of high compression ratios and demanding requirements on the compression component 3 caused by the heat pump system with low evaporation and high condensation temperatures, the inventors have provided a preferred method, which can be found in conjunction with... Figures 1 to 4As shown, the compression component 3 has a first compression section 31 and a second compression section 32. The first compression section 31 is correspondingly arranged with the first evaporator 1, and the second compression section 32 is correspondingly arranged with the second evaporator 2. The first volume of the first compression section 31 and the second volume of the second compression section 32 are configured in a proportional manner, so that the flow rates through the first evaporator 1 and the second evaporator 2 are different, and the compression ratio of the compression component 3 is reduced.

[0057] With this configuration, the cooperation between the first compression unit 31 and the second compression unit 32 will achieve the following unexpected effect:

[0058] 1. Effectively reduces compression ratio and energy consumption: Compression component 3 divides the entire compression process into multiple stages. These multiple stages can be independent and parallel stages, or they can be multiple consecutive stages. For example, in a single-stage compression process, the refrigerant is directly compressed to its final pressure. Due to the large amount of heat generated during the compression of the refrigerant, a large amount of mechanical energy is converted into heat energy, but not into pressure energy. This leads to excessively high exhaust temperature, which can easily cause a decrease in the viscosity of the lubricating oil, exacerbating wear and increasing the risk of carbon buildup, thereby increasing energy consumption and equipment burden.

[0059] In this embodiment, the refrigerant is compressed in two stages through the first compression section 31 and the second compression section 32, with the compression ratio of each stage reduced by more than 50%, meaning that the compression ratio of each stage is relatively low. This not only avoids excessively high compression heat and exhaust temperature in each stage, but also helps to reduce throttling and overheating losses in the heat pump cycle system using this compression component 3, thus optimizing the overall performance and energy efficiency of the heat pump cycle system, and also reducing the energy consumption and burden of each compression cylinder and its compression component 3.

[0060] 2. Significant impact on the maintenance and lifespan of compression component 3: Because multi-stage compression can reduce the compression ratio of each compression, it is very beneficial to reduce the axial load on each stage bearing. This not only improves the lifespan of the bearings in compression component 3, but also the overall service life and reliability of compression component 3.

[0061] Furthermore, the first volume of the first compression section 31 and the second volume of the second compression section 32 are configured in a proportional manner so that the flow rates through the first evaporator 1 and the second evaporator 2 are 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 causes the discharge rate of the first compression section 31 and the discharge rate of the second compression section 32 to be different. This controls the flow rate 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 compression section 31 is larger than the second volume of the second compression section 32, resulting in a greater displacement of the first compression section 31 than the second compression section 32, then the flow rate of the first evaporator 1 is greater than the flow rate of the second evaporator 2. Thus, more refrigerant flows in the first evaporator 1, resulting in greater heat exchange with the humid air and faster absorption of heat from the humid air. This leads to more thorough heat exchange between the humid air and the first evaporator 1, making the first evaporator 1 a low-temperature evaporator. Conversely, if the first volume of the first compression section 31 is smaller than the second volume of the second compression section 32, resulting in a smaller displacement of the first compression section 31 than the second compression section 32, then the flow rate of the first evaporator 1 is less than the flow rate of the second evaporator 2. Thus, more refrigerant flows in the second evaporator 2, resulting in greater heat exchange with the humid air and faster absorption of heat from the humid air. This also ensures more thorough heat exchange between the humid air and the second evaporator 2, making the second evaporator 2 a low-temperature evaporator.

[0063] It should be further explained that the proportional configuration 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 effects: On the one hand, it can better control the compression ratio of the first compression section 31 to be close to the compression ratio of the second compression section 32, further saving power consumption during the compression process. Simultaneously, the refrigerant compressed by the first compression section 31 undergoes atomization treatment to achieve a better cooling effect. Therefore, the temperature at which the refrigerant supplied by the second evaporator 2 enters the second compression section 32 for compression will not be too high, thus significantly reducing the compression temperature before entering the second compression stage. Alternatively, 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. This effectively controls the compression temperature of the first compression stage to be close to the compression temperature of the second compression stage. In summary, the temperature during the compression process in the first compression section 31 will approach the temperature during the compression process in the second compression section 32, achieving a more isothermal compression process for each stage, thereby further improving compression efficiency and saving energy required for compression.

[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 to be 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 during the manufacturing and assembly of the compression component 3. The clearance volume not only reduces the effective volume of the compression cylinder, but the residual high-pressure refrigerant will also further reduce the effective volume of the compression cylinder. Since the compression ratio of the first compression section 31 and the compression ratio of the second compression section 32 are both very small, the residual refrigerant in the clearance volume can reach the suction pressure with a slight expansion. 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. It also allows the required first volume of the first compression section 31 and the second volume of the second compression section 32 to be reduced accordingly, further reducing compression power consumption.

[0065] Optionally, a cooling element is also provided between the first compression section 31 and the second compression section 32. This cooling element can be a single-stage cooling element or a multi-stage cooling element. In this way, not only can the exhaust temperature of each stage be further reduced, which helps to keep the gas at a lower temperature for the next stage of compression, but it also helps the compression component 3 to maintain isothermal compression. It will also help to reduce the compression ratio of each stage, thereby improving compression efficiency, volumetric efficiency and safety performance, and saving power consumption.

[0066] It should be noted that the cooling element is preferably a fan, and two cooling elements are configured. The cooling element used to cool the first compression section 31 is defined as the first heat sink, and the cooling element used to cool the second compression section 32 is defined as the 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, then the compression power of the first compression section 31 is greater than the compression power of the second compression section 32. In this case, the power of the first heat sink is greater than the power of the second heat sink, thereby better ensuring that the first compression section 31 with higher compression power can receive sufficient heat dissipation, and thus ensuring that the first compression section 31 maintains good working performance.

[0067] In addition, the aforementioned cooling element is a fan, and the number of cooling elements is configured as one. Both the first compression section 31 and the second compression section 32 are located on the gas flow path of the cooling element, and the gas flow direction generated by the cooling element is from the one with higher power to the other with lower power. For example, if the first volume of the first compression section 31 is larger than the second volume of the second compression section 32, then the compression power of the first compression section 31 is greater than the compression power of the second compression section 32. In this case, the cooling element is located on the side closer to the first compression section 31, so that the airflow generated by the cooling element will flow through the first compression section 31 and the second compression section 32 in sequence. This better ensures that the first compression section 31 with higher compression power can receive sufficient heat dissipation and also better ensures that the first compression section 31 maintains good working performance.

[0068] Preferably, please refer to the following for details. Figure 3 and Figure 4 As shown, the aforementioned compression component 3 further comprises a cylinder seat body 36, an exhaust section 33, a first intake section 34, and a second intake section 35. The exhaust section 33, the first intake section 34, and the second intake section 35 are all fixedly connected to the cylinder seat body 36. The first compression section 31 and the second compression section 32 are both molded and disposed inside the cylinder seat body 36. This fixed connection can be a detachable connection; for example, the exhaust section 33 can be an exhaust pipe connector with an exhaust through hole, and the exhaust pipe connector is threadedly connected to the cylinder seat body 36. This fixed connection can also be a welded connection or an integrally formed connection to ensure that the compression component 3 as a whole possesses good structural strength and good sealing performance.

[0069] For details, please refer to Figure 1 , Figure 2 and Figure 5 As shown, the first suction section 34 is connected to the first compression section 31, and the first evaporator 1 is connected to the first suction section 34, so that the refrigerant supplied from the first evaporator 1 can be transported to the first compression section 31 for compression. The exhaust section 33 and the second suction section 35 are both connected to the second compression section 32, and the second evaporator 2 is connected to the second suction section 35, so that the refrigerant supplied from 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 condenser inlet of the condenser assembly 4, so that the compressed refrigerant can be output from the exhaust section 33 to the condenser assembly 4. The first evaporator 1 and the second evaporator 2 are both connected to the condenser outlet of the condenser assembly 4, thereby realizing the purpose of refrigerant circulation and cyclic operation.

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

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

[0072] Thus, by independently configuring the first compression section 31 and the second compression section 32, it is not only convenient to form two compression cylinders with different volumes, which helps to improve the stability of refrigerant output and the ability to dynamically match the actual load, but also effectively ensures higher volumetric efficiency and lower compression ratio. Furthermore, the bearings experience less stress and have higher dynamic balance, resulting in high overall reliability of the compression component 3, a simple structure, and lower manufacturing cost.

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

[0074] This configuration allows the refrigerant to be buffered and stabilized within the intermediate mixing cylinder 384. Simultaneously, it reduces temperature and energy consumption. Understandably, cooling the refrigerant compressed by the first compression section 31 allows for more efficient further compression by the second compression section 32. This lowers the intake temperature of the second compression section 32 and slows down the deterioration of the lubricating oil at high temperatures, improving the lubrication of bearings and other moving parts, thus extending the service life of the compression component 3. This achieves a better near-isothermal compression effect, thereby improving the overall efficiency, compression efficiency, and volumetric efficiency of the compression component 3, reducing heat loss and internal leakage, and significantly reducing the load on the bearings in the compression component 3. This effectively increases the lifespan of the bearings in the compression component 3 and the overall service life of the compression component 3.

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

[0076] As a further preferred embodiment, the first compression unit 31 has a total output port and a total input port, and the second compression unit 32 has a total discharge port, a first injection end, and a second injection end. The total output port of the first compression unit 31 is connected to the first injection end of the second compression unit 32, and the total input port of the first compression unit 31 is connected to the first evaporator 1. The refrigerant supplied from the first evaporator 1 can be delivered to the first compression unit 31 for compression, and the refrigerant compressed by the first compression unit 31 will be delivered to the second compression unit 32. The second injection end of the second compression unit 32 is connected to the second evaporator 2, and the refrigerant compressed by the first compression unit 31, after mixing with the refrigerant supplied from the second evaporator 2, will be compressed together by the second compression unit 32. The total discharge port of the second compression unit 32 is connected to the condenser inlet of the condenser assembly 4.

[0077] In addition to the preferred embodiment described above, as a further preferred embodiment, the first compression unit 31 has a total output port, a first input port, and a second input port; the second compression unit 32 has a total discharge port, a first injection port, and a second injection port. The total output port of the first compression unit 31 is connected to the first injection port of the second compression unit 32. The first or second input port of the first compression unit 31 is connected to the first evaporator 1. This allows refrigerant supplied from the first evaporator 1 to be delivered to the first compression unit 31 for compression, and the compressed refrigerant is then delivered to the second compression unit 32. The second injection port of the second compression unit 32 is connected to the second evaporator 2, and the total discharge port of the second compression unit 32 is connected to the condenser inlet of the condenser assembly 4. In this way, the first compression unit 31 and the second compression unit 32 cooperate to achieve the purpose of two-stage compression of the refrigerant.

[0078] As a further preferred embodiment, the heat pump cycle system also includes a three-way connector. The first compression unit 31 has a total output port and a total input port, and the second compression unit 32 has a total discharge port and a total injection port. The total input port of the first compression unit 31 is connected to the first evaporator 1, so that the refrigerant supplied from the first evaporator 1 can be delivered to the first compression unit 31 for individual compression. The total injection port of the second compression unit 32 is connected to the second evaporator 2, so that the refrigerant supplied from the second evaporator 2 can be delivered to the second compression unit 32 for individual compression. The total output port of the first compression unit 31, the total discharge port of the second evaporator 2, and the condenser inlet of the condenser assembly 4 are all connected to the three-way connector.

[0079] With this configuration, the refrigerant supplied to the first evaporator 1 and the second evaporator 2 is individually compressed by the first compression unit 31 and the second compression unit 32, and then flows and converges to the three-way connector and is delivered to the condenser assembly 4.

[0080] In this embodiment, please refer to the specific details. Figure 1, Figure 2 and Figure 5 As shown, the heat pump cycle system also includes a flow regulator configured between the evaporator assembly and the condenser assembly 4. The flow regulator is preferably an expansion valve, which can also be called a throttling valve or a regulating valve. The flow regulator is used to regulate and control the flow rate of refrigerant from the condenser assembly 4 to the evaporator assembly, thereby ensuring that the heat pump cycle system operates under optimal conditions and achieves rapid cooling of the evaporator assembly and / or heating of the condenser assembly 4, as well as precise temperature control and energy saving.

[0081] It should also be noted that, under the throttling and pressure-reducing effect of the flow regulator, the medium-temperature, high-pressure / high-pressure subcooled liquid refrigerant can be transformed into a low-temperature, low-pressure mist-like refrigerant through the flow regulator, thereby reducing the refrigerant pressure. This allows the refrigerant to evaporate more easily and absorb heat in the evaporator assembly. Simultaneously, the flow regulator also has a stable superheat, meaning it can control the valve flow rate based on changes in superheat at the end of the evaporator assembly, preventing insufficient utilization of the evaporator assembly area and knocking phenomena, thus making the heat pump cycle system operate more stably.

[0082] As one of the preferred embodiments in this example, please refer to the following: Figure 1 As shown, the aforementioned flow regulating component includes a main regulating valve 71 with throttling and pressure reduction functions. 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. That is, the aforementioned evaporator assembly is connected to the condenser assembly 4 through a connecting pipe assembly, which includes a first connecting pipe 81 connecting the first evaporator 1, a second connecting pipe 82 connecting the second evaporator 2, and a main connecting pipe 83 connecting the condenser assembly 4.

[0083] Understandably, the first connecting pipe 81 and the second connecting pipe 82 can be integrally formed, or they can be connected by pipe fittings (such as threaded connections, crimp connections, etc.), with the main regulating valve 71 installed on the main connecting pipe 83. This arrangement allows the refrigerant flowing through both the first and second connecting pipes 81 to be throttled and regulated by the main regulating valve 71, facilitating system adjustments and ensuring more stable overall cooling capacity.

[0084] Optionally, please refer to the specific details. Figure 1As shown, the flow regulating component also includes a branch regulating valve 72 with throttling and pressure reduction and flow regulation functions. The branch regulating valve 72 is connected to at least one of the first evaporator 1 and the second evaporator 2, that is, the branch regulating valve 72 is disposed in at least one of the first connecting pipe 81 and the second connecting pipe 82. By utilizing the throttling and pressure reduction and flow regulation functions of the branch regulating valve 72, the pressure of the refrigerant flowing through the first connecting pipe 81 and / or the second connecting pipe 82 is made more stable, and more complete atomization is achieved. This better ensures more stable operation of the heat pump cycle system and improves the reliability of the heat pump cycle system.

[0085] As another preferred embodiment, please refer to the following for details. Figure 2 and Figure 5 As shown, the flow regulating component includes a first expansion valve 73 and a second expansion valve 74. The first expansion valve 73 opens the first evaporator 1 to regulate the flow rate of refrigerant flowing into the first evaporator 1, and changes the state of the refrigerant to low temperature and low pressure under its throttling effect. The second expansion valve 74 opens the second evaporator 2 to regulate the flow rate of refrigerant flowing into the second evaporator 2, and changes the state of the refrigerant to low temperature and low pressure under its throttling effect.

[0086] With this configuration, the first expansion valve 73 independently throttles and adjusts the refrigerant flowing through the first evaporator 1, and the second expansion valve 74 independently throttles and adjusts the refrigerant flowing through the second evaporator 2. Therefore, the flow rate adjustment range of the entire heat pump cycle system is wider, the adjustment flexibility is higher, and the adjustment operation is more convenient. Furthermore, the operating condition response of this heat pump cycle system is also faster.

[0087] In the above description, by using a first compression section 31 and a second compression section 32 with different volumes in the compression component 3, the problem of excessive load and requirements on the compression component 3 under conditions of high condensing temperature and low evaporating temperature can be avoided. However, since the temperature sensor in existing heat pump dryers is used to monitor the refrigerant temperature, this method usually overlooks the heat exchange efficiency of the evaporator assembly. This can easily lead to the air temperature after flowing through the evaporator assembly still being 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 overlooked by those skilled in the art, existing heat pump dryers basically all have the problem of deviation in cooling and dehumidification effect.

[0088] To address the aforementioned technical problems, the inventors have proposed a technical solution in which the machine body further includes a control circuit board, as well as an evaporation temperature sensor and a condensation temperature sensor disposed inside the fluid channel. The evaporation temperature sensor detects the temperature of the flowing air after passing through the evaporator assembly and generates an evaporation air temperature value. The condensation temperature sensor detects the temperature of the flowing air after passing through the condenser assembly 4 and generates a condensation temperature value. The first evaporator 1, the second evaporator 2, the evaporation temperature sensor, the condensation temperature sensor, the aforementioned compression component 3, and the aforementioned condenser assembly 4 are all electrically connected to the control circuit board. 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] With this configuration, the evaporator temperature sensor can promptly acquire the temperature information of the flowing air after passing through the evaporator assembly, generate an evaporator air temperature value, and transmit it to the control circuit board. This allows the control circuit board to monitor the temperature value and its changes of the flowing air after cooling by the evaporator assembly in real time, and compare this evaporator air temperature value with the set temperature value to determine whether to send a control command to the evaporator temperature sensor. At this point, the control circuit board can monitor the evaporator air temperature value most directly and accurately after heat exchange with the evaporator assembly, minimizing temperature monitoring errors / deviations. The control circuit board can also more accurately and in real-time monitor the changes in the flowing air throughout the entire drying process.

[0090] At the same time, in conjunction with the second evaporator 2 and the first evaporator 1, when the control circuit board determines that the evaporation air temperature exceeds the set temperature value, it will be able to adjust the air temperature to the set temperature value in a shorter time, thereby ensuring that the clothing processing equipment maintains a good cooling and dehumidification effect.

[0091] For example, if the evaporation air temperature is much higher than the upper limit of the set temperature, the evaporation temperature of the second evaporator 2 and the first evaporator 1 can be lowered simultaneously. This allows the flowing air to absorb more heat as it passes through the second evaporator 2 and the first evaporator 1, thus reducing the temperature of the flowing air more quickly and promptly, and adjusting the evaporation air temperature to the set temperature.

[0092] For example, if the evaporation air temperature is slightly lower than the lower limit of the set temperature, 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 it flows through the second evaporator 2 and the first evaporator 1 is reduced, thereby enabling the evaporation air temperature to be finely adjusted to the set temperature.

[0093] In addition, by using the control circuit board to monitor the evaporation air temperature and condensation temperature, the heat pump circulation system can be better maintained in a stable state of low evaporation temperature and high condensation temperature, and the clothes can be prevented from being damaged by excessively high temperature flowing into the roller component 5.

[0094] Simultaneously, the control circuit board can also preliminarily assess the operation of the compressor component 3 through the evaporator temperature and condenser temperature values. Specifically, the evaporator temperature value can reflect the intake state of the compressor component 3 to a certain extent, and the condenser temperature value can reflect the exhaust state of the compressor component 3 to a certain extent. Afterwards, by combining other parameters of the compressor component 3, such as pressure, current, and power, a comprehensive judgment can be made, enabling a more efficient and accurate assessment of the operation of the compressor component 3, ensuring the stable performance of the heat pump cycle system.

[0095] As a further preferred embodiment, the aforementioned evaporation temperature sensor includes a first detection element and a second detection element. The first detection element detects the temperature of the air flowing through the first evaporator 1 and generates a first temperature value. The second detection element detects the temperature of the air flowing through the second evaporator 2 and generates a second temperature value. This second temperature value is the evaporation air temperature value of the evaporation temperature sensor. Alternatively, it can be a temperature value calculated by combining the first and second temperature values. Furthermore, the control circuit board can adjust the evaporation temperature of the first evaporator 1 and the evaporation temperature of the second evaporator 2 based on the first and second temperature values.

[0096] This configuration not only allows for more precise monitoring of the evaporation temperatures of the first evaporator 1 and the second evaporator 2, but also enables better adjustment of the temperature combination between the first evaporator 1 and the second evaporator 2. This ensures that the overall evaporation temperature of the evaporator assembly remains within a more stable and optimal temperature range. In other words, it ensures that the temperature of the evaporating air 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. This, in turn, ensures that the clothing processing equipment has a good drying effect and drying quality, and also effectively saves energy consumption of the clothing processing equipment.

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

[0098] 1. By directly measuring the temperature of the airflow after passing through the first evaporator 1 and the second evaporator 2, the actual cooling effect of each evaporator 1 and the second evaporator 2 can be accurately reflected. This allows the heat pump cycle system to make timely adjustments based on this temperature value, ensuring that the output air temperature is always maintained within the set temperature value.

[0099] 2. The first detection element will be able to detect changes in the operating state of the first evaporator 1 more quickly, and the second detection element will also be able to detect changes in the operating state of the second evaporator 2 more quickly. When the cooling capacity of either the first evaporator 1 or the second evaporator 2 changes, such as due to changes in refrigerant flow or surface dust accumulation causing changes in cooling effect, the corresponding detection element in the evaporator 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 cycle system to make adjustments more quickly, improving the stability and response speed of the heat pump cycle system.

[0100] 3. Facilitates fault diagnosis. If the heat pump cycle system malfunctions, such as a blockage in either the first evaporator 1 or the second evaporator 2, or a refrigerant leak, the corresponding air outlet temperatures in the first evaporator 1 and the second evaporator 2 will change significantly. Repair personnel can quickly determine the approximate location and type of fault by reading the data from the corresponding sensors in the evaporator temperature sensors. For example, if the air outlet temperature of either the first evaporator 1 or the second evaporator 2 is consistently high, it may indicate a decrease in the corresponding cooling capacity of the first evaporator 1 or the second evaporator 2, requiring a check for insufficient refrigerant or blockage.

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

[0102] In the accompanying drawings of this embodiment, the same or similar reference numerals correspond to the same or similar components. In the description of this application, it should be understood that if terms such as "upper," "lower," "left," "right," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting this application. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

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

Claims

1. A heat pump cycle system, characterized in that, include: An evaporator assembly, comprising a first evaporator and a second evaporator connected in parallel; A compression component, the compression component having a first compression section and a second compression section, the first compression section being connected to the first evaporator, and the second compression section being connected to the second evaporator; A condenser assembly, wherein 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 component, the second compression component and the condenser assembly, and a second circuit consisting of the second evaporator, the second compression component and the condenser assembly.

2. The heat pump cycle system as described in claim 1, characterized in that, The first volume of the first compression section and the second volume of the second compression section are configured in a proportional manner, so that the flow rates through the first evaporator and the second evaporator are different.

3. The heat pump cycle system as described in claim 1 or 2, characterized in that, The compression component further includes an exhaust section, a first intake section, and a second intake 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, and the second evaporator is connected to the second intake section. The exhaust section of the compression component is connected to the condenser inlet of the condenser assembly, and the first evaporator and the second evaporator are both connected to the condenser outlet of the condenser assembly.

4. The heat pump cycle system as described in claim 3, characterized in that, The first compression section and the second compression section are independently configured. The compression section also has a first inner flow channel and a second inner flow channel. The exhaust section and the first intake section are both connected to the first compression section through the first inner flow channel. The exhaust section and the second intake section are both connected to the second compression section through the second inner flow channel.

5. The heat pump cycle system as described in claim 3, characterized in that, The compression component also has a primary flow channel, a secondary flow channel, a main exhaust flow channel, and an intermediate mixing cylinder. The first compression section is connected to the second compression section through the intermediate mixing cylinder. The first intake section is connected to the first compression section through the primary flow channel. The second intake section is connected to the intermediate mixing cylinder through the secondary flow channel. The exhaust section is connected to the second compression section through the main exhaust flow channel.

6. The heat pump cycle system as described in claim 1 or 2, characterized in that, The first compression unit and the second compression unit are both independently configured compressors. The first compression unit is used to compress and process the refrigerant flowing through the first evaporator separately, and the second compression unit is used to compress and process the refrigerant flowing through the second evaporator separately, or to compress and process the refrigerant flowing through the second evaporator mixed with the refrigerant compressed and output by the first compression unit.

7. The heat pump cycle system as described in claim 6, characterized in that, The first compression unit has a total output port and a total input port, and the second compression unit has a total discharge port, a first injection end and a second injection end. The total output port of the first compression unit is connected to the first injection end of the second compression unit, the total input port of the first compression unit is connected to the first evaporator, the second injection end of the second compression unit is connected to the second evaporator, and the total discharge port of the second compression unit is connected to the condenser inlet of the condenser assembly.

8. The heat pump cycle system as described in claim 6, characterized in that, It also includes a three-way connector. The first compression unit has a total output port and a total input port, and the second compression unit has a total discharge port and a total injection port. The total input port of the first compression unit is connected to the first evaporator, and the total injection port of the second compression unit is connected to the second evaporator. The total output port of the first compression unit, 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 cycle system as described in claim 6, characterized in that, The first compression unit has a total output port, a first input terminal and a second input terminal, and the second compression unit has a total discharge port, a first injection terminal and a second injection terminal. The total output port of the first compression unit is connected to the first injection terminal of the second compression unit. The first input terminal or the second input terminal of the first compression unit is connected to the first evaporator. The second injection terminal of the second compression unit is connected to the second evaporator. The total discharge port of the second compression unit is connected to the condenser inlet of the condenser assembly.

10. The heat pump cycle system as described in claim 2, characterized in that, The compression component also has a cooling element for cooling the first compression section and the second compression section.

11. The heat pump cycle system as described in claim 10, characterized in that, The cooling element is a fan, and the number of cooling elements is configured to be two. The cooling element used to cool the first compression section is defined as the first heat sink, and the cooling element used to cool the second compression section is defined as the 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 and the second compression section.

12. The heat pump cycle system as described in claim 10, characterized in that, The cooling element is a fan, and the number of cooling elements is one. The first compression section and the second compression section are both on the gas flow path of the cooling element, and the gas flow direction generated by the cooling element is from the one with greater power to the other with less power.

13. The heat pump cycle system as described in claim 1 or 2, characterized in that, It also includes a flow regulator disposed between the evaporator assembly and the condenser assembly, the flow regulator being used to regulate and control the flow rate of refrigerant from the condenser assembly to the evaporator assembly.

14. The heat pump cycle system as described in claim 13, characterized in that, The flow regulating component includes a main regulating valve with 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 cycle system as described in claim 14, characterized in that, The flow regulating component also includes a branch regulating valve with throttling and pressure reduction and flow regulation functions, wherein the branch regulating valve is connected to at least one of the first evaporator and the second evaporator.

16. The heat pump cycle system as described in claim 13, characterized in that, The flow regulating component includes a first expansion valve and a second expansion valve. The first expansion valve opens the first evaporator to regulate the flow rate 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 opens the second evaporator.

17. A garment processing device, characterized in that, include: The heat pump cycle system as described in any one of claims 1 to 16; The garment processing chamber and the heat pump circulation system form an airflow circulation path.

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