Laundry treating apparatus

Abstract

The clothes treatment equipment comprises a heat pump circulating system and a driving fan, the heat pump circulating system comprises a first evaporator, a second evaporator, a compression part and a condenser assembly, and the first evaporator, the second evaporator, the compression part and the condenser assembly form a heat exchange loop; the driving fan is used for driving the drying airflow to flow through the first evaporator and the second evaporator in the fluid channel, and after the heat pump circulation system operates for a preset duration, the temperature of the drying airflow passing through the first evaporator is smaller than that of the drying airflow passing through the second evaporator; therefore, the purpose of accurately monitoring the actual temperature of the drying airflow in real time can be achieved, the efficient cooling and dehumidification effects are achieved, and the drying effect and drying quality of the clothes processing equipment are guaranteed.

Description

Technical Field

[0001] This application relates to the field of clothing processing devices, and in particular to a clothing processing device. Background Technology

[0002] Heat pump dryers work by using the heat of condensation 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 airless drying. In related technologies, the heat pump cycle system of a heat pump dryer includes an evaporator and a compressor. As air flows through the evaporator, the refrigerant absorbs heat during evaporation, causing the air temperature to drop. The moisture in the air condenses into water droplets and is expelled by the dryer, thus achieving the purpose of cooling and dehumidifying.

[0003] In current heat pump dryers, temperature sensors are typically used to detect the temperature of the evaporator's outer surface or the temperature of the refrigerant inside the evaporator. When the evaporator temperature drops below -1°C, the compressor stops working and the defrost indicator light illuminates. The compressor only restarts when the evaporator temperature rises above 2°C and defrosting time exceeds 10 minutes. In other words, the temperature sensor in current heat pump dryers monitors the refrigerant temperature to ensure the evaporator operates within its optimal temperature range, thereby ensuring the stable and efficient operation of the entire heat pump cycle system.

[0004] However, since there is still a large temperature difference between the refrigerant monitored by the temperature sensor and the air flowing through the evaporator, and the temperature sensor located near the drum inlet can only monitor the temperature of the air flowing into the drum in real time, it cannot accurately monitor the actual temperature of the air flowing through the evaporator. This will affect the cooling and dehumidification effect of the air, and thus affect the drying effect and drying quality of existing heat pump dryers. Utility Model Content

[0005] This application provides a garment processing device that can monitor the actual temperature of the drying airflow in real time and accurately, thereby achieving efficient cooling and dehumidification.

[0006] This application provides a garment processing device, which includes:

[0007] A heat pump cycle system, comprising a first evaporator, a second evaporator, a compression component, and a condenser assembly, wherein the first evaporator, the second evaporator, the compression component, and the condenser assembly form a heat exchange loop;

[0008] A drive fan is used to drive the drying airflow through the first evaporator and the second evaporator in the fluid channel;

[0009] The temperature of the drying airflow after passing through the first evaporator is less than the temperature of the drying airflow after passing through the second evaporator after the heat pump circulation system operates for a preset time length.

[0010] In an embodiment, the clothes treatment apparatus includes a first temperature detection member for detecting the temperature of the drying airflow after passing through the first evaporator and generating a first air temperature value, and a second temperature detection member for detecting the temperature of the drying airflow after passing through the second evaporator and generating a second air temperature value.

[0011] In an embodiment, the first temperature detection member is installed near one side of an air outlet of the first evaporator, and / or the second temperature detection member is installed near one side of an air outlet of the second evaporator.

[0012] In an embodiment, the temperature range of the first air temperature value is controlled to be 10℃ to 35℃.

[0013] In an embodiment, the temperature difference between the second air temperature value and the first air temperature value is greater than 5℃, and the second air temperature value is greater than 0℃.

[0014] In an embodiment, the evaporation temperature of the first evaporator is greater than the evaporation temperature of the second evaporator.

[0015] In an embodiment, the compression member has a first compression portion, a second compression portion, an exhaust portion, a first suction portion, and a second suction portion, the first suction portion communicates with the first compression portion, the exhaust portion and the second suction portion both communicate with the second compression portion, the first evaporator is connected to the first suction portion, the second evaporator is connected to the second suction portion, the exhaust portion of the compression member communicates with a condensing inlet of the condenser assembly, and the first evaporator and the second evaporator both communicate with a condensing outlet of the condenser assembly.

[0016] In an embodiment, the first compression portion and the second compression portion are independently configured, the compression member further has a first internal flow channel and a second internal flow channel, the exhaust portion and the first suction portion both communicate with the first compression portion through the first internal flow channel, and the exhaust portion and the second suction portion both communicate with the second compression portion through the second internal flow channel.

[0017] In an embodiment, the compression member further has a first-level flow channel, a second-level flow channel, a total exhaust flow channel, and an intermediate mixing cylinder, the first compression portion communicates with the second compression portion through the intermediate mixing cylinder, the first suction portion communicates with the first compression portion through the first-level flow channel, the second suction portion communicates with the intermediate mixing cylinder through the second-level flow channel, and the exhaust portion communicates with the second compression portion through the total exhaust flow channel.

[0018] In an embodiment, the heat pump circulation system further comprises a refrigerant flow adjusting member for adjusting the flow of refrigerant flowing to the evaporator assembly.

[0019] Based on the above-mentioned embodiments, the laundry treatment apparatus provided by the embodiments of the present application comprises a heat pump circulation system and a driving fan, the heat pump circulation system comprises a first evaporator, a second evaporator, a compression component and a condenser assembly, the first evaporator, the second evaporator, the compression component and the condenser assembly form a heat exchange loop, and the driving fan is used to drive the drying airflow to flow through the first evaporator and the second evaporator in the fluid channel, wherein the temperature of the drying airflow after passing through the first evaporator is lower than the temperature of the drying airflow after passing through the second evaporator after the heat pump circulation system operates for a preset time length.

[0020] Compared with the related art, the technical solution of the present application can realize the purpose of monitoring the actual temperature of the drying airflow in real time and accurately, and achieve the effect of efficient cooling and dehumidification, thereby ensuring the drying effect and drying quality of the laundry treatment apparatus, after the heat pump circulation system operates for a preset time length. BRIEF DESCRIPTION OF DRAWINGS

[0021] In order to more clearly illustrate the technical solutions in the embodiments of the present application or the prior art, the drawings needed to be used in the embodiments or prior art description will be briefly introduced as follows. Obviously, the drawings in the following description are only some embodiments of the present application, and other drawings can be obtained by those skilled in the art without creative labor based on the structures shown in the drawings.

[0022] Figure 1 First arrangement principle diagram of the heat pump circulation system of an embodiment of the present application;

[0023] Figure 2 Second arrangement principle diagram of the heat pump circulation system of an embodiment of the present application;

[0024] Figure 3 First structure schematic view of the compression component in an embodiment of the present application;

[0025] Figure 4 Second structure schematic view of the compression component in an embodiment of the present application;

[0026] Figure 5 Heat exchange loop schematic view of the laundry treatment apparatus of an embodiment of the present application;

[0027] Figure 6The utility model discloses a first evaporator and second evaporator dehumidification rate broken line chart of one embodiment.

[0028] Explanation of reference numerals:

[0029] 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 - roller component, 6 - driving fan, 71 - total regulating valve, 72 - branch regulating valve, 73 - first expansion valve, 74 - second expansion valve, 81 - first connecting pipe, 82 - second connecting pipe, 83 - total connecting pipe.

[0030] The implementation, functional features and advantages of the present application will be further described with reference to the embodiments and the accompanying drawings. DETAILED DESCRIPTION

[0031] To make the purpose, technical scheme and advantages of the present application more clear, the following will further describe the embodiments of the present application with reference to the accompanying drawings.

[0032] The following description relates to the drawings, unless otherwise indicated, the same numerals in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all the embodiments consistent with the present application. Instead, they are only examples of devices and methods consistent with some aspects of the present application as detailed in the appended claims.

[0033] In the description of the present application, it is understood that the terms "first", "second" and the like are only for the purpose of description, and cannot be understood as indicating or implying relative importance. For ordinary skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances. In addition, in the description of the present application, unless otherwise specified, "multiple" means two or more. "And / or", the association between the associated objects, means that there may be three kinds of relationship, for example, A and / or B, can represent: A exists alone, A and B exist simultaneously, B exists alone, these three cases. The character " / " generally represents that the associated objects before and after are a kind of "or" relationship.

[0034] 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 in the description herein is for describing particular embodiments only and is not intended to be limiting of the application. The use herein of the terms "and / or" includes a set of one or more associated listed items.

[0035] Specifically, according to Figure 5 As shown in the drawings, the present application proposes a laundry treatment device for drying laundry, i.e. using heat energy to increase the temperature of flowing air, heating the flowing air into dry hot air, and the dry hot air carries away part of the moisture on the wet laundry in the process of flowing through the wet laundry, and then the dry hot air is changed into wet hot air after flowing through the wet laundry, and the wet hot air is dehumidified and secondarily heated to be recycled to the wet laundry. Such circulation is repeated until the wet laundry is dried.

[0036] In this scheme, the heat pump drying principle is adopted, i.e. the laundry treatment device comprises a heat pump circulation system and a machine body, and the machine body is provided with a laundry treatment cavity, for example, the inside of the machine body has a drum component 5, and the drum component 5 is provided with a drum inner cavity for placing and drying laundry, and the drum inner cavity is the laundry treatment cavity of the machine body. The drum component 5 can rotate under the drive of the drive motor, so that the laundry can tumble in the laundry treatment cavity, not only ensuring that each piece of wet laundry can be fully dried by the dry hot air (hereinafter referred to as drying air flow), but also improving the drying efficiency of the wet laundry. For another example, the care inner drying cavity of the machine body is the laundry treatment cavity of the machine body, and each piece of wet laundry is hung in the laundry treatment cavity to be fully dried by the drying air flow. The heat pump circulation system and the laundry treatment cavity form an air flow circulation passage, so that the wet laundry can be continuously dried.

[0037] In this embodiment, specifically, as shown in Figure 1 , Figure 2 and Figure 5 , the heat pump circulation system comprises an evaporator assembly, a compression component 3, a refrigerant flow regulating member, and a condenser assembly 4, wherein the evaporator assembly comprises a first evaporator 1 and a second evaporator 2 connected in parallel, and 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 refrigerant flow regulating member, 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 refrigerant flow regulating member of the heat pump circulation system are all installed and fixed in the inside of the machine body.

[0038] The heat exchange circuit is a circulating flow heat exchange circuit of refrigerant, and the heat exchange circuit comprises a first evaporator 1, a first compression part 31, a first circuit composed of the condenser assembly 4, and a second circuit composed of a second evaporator 2, the first compression part 31, a second compression part 32, and the condenser assembly 4.

[0039] Optionally, the inside of the machine body is provided with an internal circulation drying channel, and the first evaporator 1, the second evaporator 2, the condenser assembly 4, and the drum component 5 are arranged in sequence along the flow path of the drying air flow in the internal circulation drying channel. Then, the clothes treatment cavity, the internal circulation drying channel, and the first evaporator 1, the second evaporator 2, the condenser assembly 4, and the drum component 5 of the machine body of the heat pump circulation system will form the air flow circulation passage in sequence.

[0040] In the air flow circulation passage in this circulation, the compression component 3 sucks in the low-pressure and low-temperature gaseous refrigerant (refrigerant), and through mechanical movement, the gaseous refrigerant is compressed into high-pressure and high-temperature gaseous refrigerant, which provides power for the closed circulation and is delivered to the condenser assembly 4. When the high-temperature and high-pressure gaseous refrigerant passes through the condenser assembly 4, it is liquefied at a constant pressure and releases heat, and is cooled into high-pressure supercooled liquid refrigerant. Then, a large amount of heat released by the condenser assembly 4 will be transferred to the drying air flow. The high-pressure supercooled liquid refrigerant is throttled into low-temperature and low-pressure mist refrigerant through the refrigerant flow regulating piece, and then evaporates and absorbs heat in the first evaporator 1 and the second evaporator 2 to form low-temperature and low-pressure gaseous refrigerant, and is delivered to the compression component 3 again. The moisture in the drying air flow condenses into water droplets and is discharged when the drying air flow encounters the condenser assembly 4. Then, the drying air flow is converted into dry cold air by refrigeration, and the dry cold air is heated into the drying air flow again when it flows through the condenser assembly 4, and the cycle is repeated.

[0041] To realize the directionality and stability of the flow of the drying air flow in the internal circulation drying channel of the machine body, please refer to the specific implementation of the machine body in the following description. Figure 5 As shown in the figure, the inside of the machine body also has a driving fan 6. The driving fan 6 here can be selected as a blower fan, and can also be selected as an exhaust fan. The driving fan 6 is arranged on the internal circulation drying channel, that is, the driving fan 6 is arranged on the path of the air flow circulation passage. Preferably, the second evaporator 2 of the evaporator assembly and the condenser assembly 4 are respectively arranged on the two opposite sides of the first evaporator 1 of the evaporator assembly. Under the guidance of the internal circulation drying channel, the driving fan 6 can drive the drying air flow to flow through the first evaporator 1 and the second evaporator 2 in the fluid passage. Specifically, the driving fan 6 drives the drying air flow 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 sequence in the internal circulation drying channel.

[0042] Wherein, after the heat pump circulation system runs for a preset time length, the temperature of the drying airflow after passing through the first evaporator 1 is less than the temperature of the drying airflow after passing through the second evaporator 2. Since the first evaporator 1 and the second evaporator 2 are arranged in parallel, the evaporation pressure of the first evaporator 1 and the evaporation pressure of the second evaporator 2 can be adjusted separately, so as to independently set or change the evaporation temperature of the first evaporator 1 and the evaporation temperature of the second evaporator 2. The first evaporator 1 and the second evaporator 2 cooperate with each other to condense and remove the moisture in the drying airflow into small water droplets, so as to achieve the purpose of dehumidifying the drying airflow. Specifically, in the process of passing through the second evaporator 2, the moisture in the drying airflow exchanges heat with the second evaporator 2, that is, the second evaporator 2 absorbs the heat in the drying airflow and further reduces the temperature of the drying airflow, so that part of the moisture in the drying airflow condenses into water droplets and is discharged, achieving the purpose of preliminary dehumidification of the drying airflow. In the process of passing through the first evaporator 1, the moisture in the drying airflow exchanges heat with the first evaporator 1, that is, the first evaporator 1 absorbs the heat in the drying airflow and further reduces the temperature of the drying airflow, so that the remaining part of the moisture in the drying airflow condenses into water droplets and is discharged, thereby achieving the purpose of secondary dehumidification of the drying airflow. It should be noted that the evaporation temperature refers to the temperature (value) of the refrigerant when it boils and vaporizes in the first evaporator 1 and the second evaporator 2.

[0043] Understandably, the evaporation temperature of the first evaporator 1 can be less than the evaporation temperature 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, then in the path of the airflow circulation passage, the drying airflow flows through the high-temperature evaporator, the low-temperature evaporator and the condenser assembly 4 in turn. In this way, since there is a temperature difference between the temperature of the drying airflow flowing out of the clothes treatment cavity and the evaporation temperature of the second evaporator 2, the heat exchange capacity / efficiency of the high-temperature evaporator is maximized. At the same time, the temperature of the drying airflow after passing through the second evaporator 2 and the evaporation temperature of the first evaporator 1 maintain a large temperature difference, which can also ensure the good heat exchange efficiency of the first evaporator 1, thereby better ensuring the dehumidification effect of the evaporator assembly, which is conducive to shortening the drying time of the clothes, improving the drying efficiency of the clothes, and saving the energy consumption of the clothes treatment device.

[0044] Of course, the evaporation temperature of the first evaporator 1 can also be greater than the evaporation temperature 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, then in the path of the air flow circulation channel, the drying air flow flows through the low-temperature evaporator, the high-temperature evaporator and the condenser assembly 4 in turn. In this way, a larger temperature difference is formed between the temperature of the drying air flow and the evaporation temperature of the second evaporator 2, thereby facilitating the improvement of the heat exchange efficiency of the second evaporator 2 and more efficiently absorbing the heat in the drying air flow and better removing the moisture in the drying air flow, so that the second evaporator 2 achieves the maximum dehumidification effect. Since there is still a temperature difference between the temperature of the drying air flow after flowing through the second evaporator 2 and the evaporation temperature of the first evaporator 1, the good dehumidification effect of the secondary dehumidification of the drying air flow can be effectively ensured.

[0045] The unexpected effect is that the temperature difference between the drying air flow after flowing through the second evaporator 2 and the evaporation temperature of the first evaporator 1 is relatively small, so that the drying air flow absorbs relatively less heat, and the temperature of the drying air flow flowing through the condenser assembly 4 is raised, thereby being able to raise the temperature of the drying air flow flowing into the clothes treatment cavity, which has certain benefits for the drying time of the clothes, and improves the drying efficiency of the clothes.

[0046] As can be seen from the above, through the cooperation of the first evaporator 1 and the second evaporator 2, the evaporation temperature of the evaporator assembly can be effectively reduced under the condition of high condensation temperature, thereby maximizing the dehumidification effect of the evaporator assembly. In order to avoid the problem of high compression ratio and high requirement of the compression component 3 of the heat pump system with low evaporation temperature and high condensation temperature, the present application provides a preferred mode, please refer to Figures 1 to 4 The above-mentioned compression component 3 has a first compression part 31 and a second compression part 32, the first compression part 31 is correspondingly arranged with the first evaporator 1, and the second compression part 32 is correspondingly arranged with the second evaporator 2, the first operating parameter of the first compression part 31 is different from the second operating parameter of the second compression part 32, so that the flow through the first evaporator 1 and the second evaporator 2 is different, wherein the type of the first operating parameter and the second operating parameter is different.

[0047] In this way, by changing or setting the first operating parameter and the second operating parameter which are not the same, the flow of the refrigerant (refrigerant) flowing through the first evaporator 1 and the second evaporator 2 can be adjusted, so that the pressure of the refrigerant (refrigerant) entering the first evaporator 1 and the second evaporator 2 is not the same, which promotes the heat absorbed by the first evaporator 1 and the second evaporator 2 to be different, thereby facilitating the evaporator assembly to absorb the heat of the wet drying air flow in the best state.

[0048] For example, by configuring different first operating parameters and second operating parameters, so that the refrigerant flow through the first evaporator 1 is larger than the refrigerant flow through the second evaporator 2, and the evaporation pressure of the first evaporator 1 is higher than the evaporation pressure of the second evaporator 2, the temperature difference between the evaporation temperature of the first evaporator 1 and the temperature of the drying air flow increases, thereby facilitating the speed of absorbing the heat of the drying air flow.

[0049] In addition, by changing or setting different first operating parameters and second operating parameters, the refrigerant flow through the first evaporator 1 and the second evaporator 2 can be more reasonably controlled, so that the first evaporator 1 and the second evaporator 2 work in a suitable working condition, thereby avoiding the case that the first evaporator 1 and the second evaporator 2 have abnormal pressure due to excessive or insufficient refrigerant flow, and to some extent, the compression ratio is improved, thereby avoiding the problem that the heat pump system with low evaporation temperature and high condensation temperature causes high compression ratio and high requirements on the compression component 3, and also ensures that the two evaporators with different temperatures are in the best state to stably absorb the heat of the drying air flow.

[0050] Preferably, the first operating parameters include a first volume, the second operating parameters include a second volume, and the first volume of the first compression part 31 and the second volume of the second compression part 32 are proportionally configured to make the flow through the first evaporator 1 and the second evaporator 2 different, and to reduce the compression ratio of the compression component 3.

[0051] In this way, by the cooperation of the first compression part 31 and the second compression part 32, the following unexpected effects can be achieved:

[0052] 1. Effectively reduce the compression ratio and energy consumption: The compression component 3 divides the entire compression process into multiple stages, which can be multiple independent and parallel stages, or multiple consecutive stages. For example, in the process of single-stage compression, the refrigerant (refrigerant) as a whole will be directly compressed to the final pressure. Since a large amount of refrigerant is compressed as a whole, a large amount of compression heat will be generated, a large amount of mechanical energy will be converted into heat energy, but cannot be converted into pressure energy, which will cause the exhaust temperature to be too high, and the exhaust temperature that is too high will easily cause the viscosity of the lubricating oil to decrease, aggravate the wear and risk of carbon deposition, thereby increasing the energy consumption and equipment burden.

[0053] In the present embodiment, the refrigerant is compressed in two stages by the first compression part 31 and the second compression part 32, and the compression ratio of each stage is reduced by more than 50%, i.e. the compression ratio of each stage is relatively low. This not only avoids the compression heat and exhaust temperature of each stage being too high, but also facilitates reducing the throttling and superheating loss of the heat pump cycle system using the compression component 3, i.e. optimizing the overall performance and energy efficiency of the heat pump cycle system, and reducing the energy consumption and burden of each compression cylinder and the compression component 3.

[0054] 2. Maintenance and life of the compression part 3 are significantly affected: since the multi-stage compression can reduce the compression ratio of each compression, it is very beneficial to reduce the axial load of each stage bearing. This not only improves the life of the bearing in the compression part 3, but also improves the overall service life and reliability of the compression part 3.

[0055] In addition, the first volume of the first compression part 31 and the second volume of the second compression part 32 are proportionally configured to make the flow rates through the first evaporator 1 and the second evaporator 2 different, that is, the first volume of the first compression part 31 and the second volume of the second compression part 32 are not the same, which causes the displacement of the first compression part 31 and the displacement of the second compression part 32 to be different, and then the flow rates through the first evaporator 1 and the second evaporator 2 are controlled to be different, so as to control the evaporation temperature of the first evaporator 1 and the evaporation temperature of the second evaporator 2.

[0056] For example, the first volume of the first compression part 31 is greater than the second volume of the second compression part 32, so that the displacement of the first compression part 31 is greater than the displacement of the second compression part 32, and then the flow rate of the first evaporator 1 is greater than the flow rate of the second evaporator 2. In this way, more refrigerant flows in the first evaporator 1, and the amount of heat exchange with the drying air flow is more, which accelerates the absorption of heat of the drying air flow, and then the heat exchange between the drying air flow and the first evaporator 1 is more sufficient. At this time, the first evaporator 1 is a low-temperature evaporator, that is, the evaporation temperature of the first evaporator 1 is less than the evaporation temperature of the second evaporator 2, and the compression power of the first compression part 31 is greater than the compression power of the second compression part 32.

[0057] On the contrary, the first volume of the first compression part 31 is less than the second volume of the second compression part 32, so that the displacement of the first compression part 31 is less than the displacement of the second compression part 32, and then the flow rate of the first evaporator 1 is less than the flow rate of the second evaporator 2. In this way, more refrigerant flows in the second evaporator 2, and the amount of heat exchange with the drying air flow is more, which accelerates the absorption of heat of the drying air flow, and ensures that the heat exchange between the drying air flow and the second evaporator 2 is more sufficient. At this time, the second evaporator 2 is a low-temperature evaporator, that is, the evaporation temperature of the first evaporator 1 is greater than the evaporation temperature of the second evaporator 2, and the compression power of the first compression part 31 is less than the compression power of the second compression part 32.

[0058] It should be noted that the first volume of the first compression part 31 and the second volume of the second compression part 32 are proportionally arranged, which has the unexpected effect that, on the one hand, the compression ratio of the first compression part 31 can be better controlled to approach the compression ratio of the second compression part 32, and the power consumption in the compression process is further saved. At the same time, the refrigerant compressed by the first compression part 31 is mist-processed to achieve a good cooling effect, and the temperature of the refrigerant mixed with the refrigerant supplied by the second evaporator 2 and then entering the second compression part 32 for compression will not be too high, that is, the compression temperature before entering the two-stage compression stage is greatly reduced. Alternatively, the first compression part 31 independently compresses the refrigerant supplied by the first evaporator 1, and the second compression part 32 independently compresses the refrigerant supplied by the second evaporator 2, so that the compression temperature in the first-stage compression stage is well controlled to approach the compression temperature in the second-stage compression stage. As described above, the temperature in the compression process in the first compression part 31 will approach the temperature in the compression process in the second compression part 32, so that the compression process of each stage approaches isothermal compression, thereby further improving the compression efficiency and saving the energy required for compression.

[0059] On the other hand, the compression ratio of the first compression part 31 and the compression ratio of the second compression part 32 can be further controlled at a lower level, that is, the compression ratio of each stage of the compression part 3 can be controlled at a lower level for easier control. This not only further improves the overall volumetric efficiency / volumetric utilization, but it is not difficult to understand that there will be a clearance volume in the process of producing and assembling and operating the compression part 3, and the clearance volume not only reduces the effective volume of the compression cylinder, but also the residual high-pressure refrigerant further reduces the effective volume of the compression cylinder. The compression ratio of the first compression part 31 and the compression ratio of the second compression part 32 are small, so that the refrigerant remaining in the clearance volume can slightly expand to reach the suction pressure. In other words, the residual high-pressure refrigerant effectively avoids reducing the effective volume of the compression cylinder, thereby improving the volumetric efficiency / volumetric utilization of the compression part 3, and also allowing the first volume of the first compression part 31 and the second volume of the second compression part 32 to be correspondingly reduced, further reducing the compression power consumption.

[0060] Optionally, a cooling element is arranged between the first compression part 31 and the second compression part 32. The cooling element can be a single-stage cooling element or a multi-stage cooling element. In this way, the exhaust temperature of each stage can be further reduced, which helps to keep the gas at a lower temperature for the next stage of compression, and is conducive to the compression part 3 to approach isothermal compression, and will also be conducive to reducing the compression ratio of each stage, thereby improving the compression efficiency, volumetric efficiency and safety performance, and saving power consumption.

[0061] It should be noted that the cooling element is preferably a fan, and the number of cooling elements is configured to be two, the cooling element for cooling the first compression part 31 is defined as the first heat dissipation member, and the cooling element for cooling the second compression part 32 is defined as the second heat dissipation member. The power ratio between the first heat dissipation member and the second heat dissipation member is the same as the volume ratio between the first compression part 31 and the second compression part 32. For example, the first volume of the first compression part 31 is greater than the second volume of the second compression part 32, and the compression power of the first compression part 31 is greater than the compression power of the second compression part 32. At this time, the power of the first heat dissipation member is greater than the power of the second heat dissipation member, so that the first compression part 31 with large compression power can be better cooled, and the working performance of the first compression part 31 can be better guaranteed.

[0062] In addition, the cooling element is a fan, and the number of cooling elements is configured to be one. The first compression part 31 and the second compression part 32 are both on the gas flow path of the cooling element, and the direction of the gas flow generated by the cooling element is from the one with large power to the other with small power. For example, the first volume of the first compression part 31 is greater than the second volume of the second compression part 32, and the compression power of the first compression part 31 is greater than the compression power of the second compression part 32. At this time, the cooling element is arranged on the side close to the first compression part 31, and the flow generated by the cooling element will flow through the first compression part 31 and the second compression part 32 in turn. Therefore, the first compression part 31 with large compression power can be better cooled, and the working performance of the first compression part 31 can be better guaranteed.

[0063] Preferably, as shown in Figure 3 and Figure 4 The compression part 3 also has a cylinder base body 36, an exhaust part 33, a first suction part 34, and a second suction part 35. The exhaust part 33, the first suction part 34, and the second suction part 35 are fixedly connected to the cylinder base body 36, and the first compression part 31 and the second compression part 32 are both formed and arranged in the interior of the cylinder base body 36. The fixed connection here can be detachable connection, for example, the exhaust part 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, and can also be integrally formed, so as to guarantee that the compression part 3 has good structural strength and good sealing performance.

[0064] Specifically, as shown in Figure 1 , Figure 2 and Figure 5As shown, the first suction part 34 is communicated with the first compression part 31, the first evaporator 1 is connected with the first suction part 34, so that the refrigerant provided from the first evaporator 1 can be transported into the first compression part 31 for compression, the exhaust part 33 and the second suction part 35 are both communicated with the second compression part 32, the second evaporator 2 is connected with the second suction part 35, so that the refrigerant provided from the second evaporator 2 can be transported into the second compression part 32 for compression. Optionally, the exhaust part 33 of the compression component 3 is communicated with the condensing inlet of the condenser assembly 4, then the refrigerant after compression processing can be output from the exhaust part 33 to the condenser assembly 4, the first evaporator 1 and the second evaporator 2 are both communicated with the condensing outlet of the condenser assembly 4, so as to realize the purpose of circulating transportation and circulating work of the refrigerant.

[0065] As a preferred mode of the embodiment, please refer to the following Figure 4 As shown, the first compression part 31 and the second compression part 32 are independently configured, and the compression component 3 further has a first inner flow channel 371 and a second inner flow channel 372. The first inner flow channel 371 includes a first inflow channel 3711 formed between the first suction part 34 and the first compression part 31, and a first outflow channel 3712 formed between the exhaust part 33 and the first compression part 31. One end of the first inflow channel 3711 is communicated with the first suction port / first suction pipe of the first suction part 34, and the other end of the first inflow channel 3711 is communicated with the first compression part 31. Therefore, the refrigerant will flow into the first compression part 31 under the guidance of the first inflow channel 3711. One end of the first outflow channel 3712 is communicated with the first compression part 31, and the other end of the first outflow channel 3712 is communicated with the exhaust hole of the exhaust part 33. Therefore, the compressed refrigerant will flow to the exhaust part 33 and be output from the exhaust part 33 under the guidance of the first outflow channel 3712. In this way, the exhaust part 33 and the first suction part 34 are both communicated with the first compression part 31 through the first inner flow channel 371.

[0066] Optionally, as shown in the following Figure 4 The second inner flow channel 372 includes a second inflow channel 3721 formed between the second suction part 35 and the second compression part 32, and a second outflow channel 3722 formed between the exhaust part 33 and the second compression part 32. One end of the second inflow channel 3721 is communicated with the second suction port / second suction pipe of the second suction part 35, and the other end of the second inflow channel 3721 is communicated with the second compression part 32. Therefore, the refrigerant will flow into the second compression part 32 under the guidance of the second inflow channel 3721. One end of the second outflow channel 3722 is communicated with the second compression part 32, and the other end of the second outflow channel 3722 is communicated with the exhaust hole of the exhaust part 33. Therefore, the compressed refrigerant will flow to the exhaust part 33 and be output from the exhaust part 33 under the guidance of the second outflow channel 3722. In this way, the exhaust part 33 and the second suction part 35 are both communicated with the second compression part 32 through the second inner flow channel 372.

[0067] Therefore, by configuring the first compression part 31 and the second compression part 32 independently, the two compression cylinders with different volumes can be conveniently formed, thereby facilitating the improvement of the stability of the refrigerant output and the ability to dynamically match the actual load. Meanwhile, higher volumetric efficiency and lower compression ratio can be effectively ensured, the bearing stress is smaller, the dynamic balance is higher, the reliability of the compression part 3 as a whole is high, and the structure is simple, and the manufacturing cost is smaller.

[0068] It should be noted that, assuming that the evaporation temperature of the first evaporator 1 is higher than that of the second evaporator 2, the first evaporator 1 corresponds to a high-temperature evaporator, and the second evaporator 2 corresponds to a low-temperature evaporator. And define the gas flow of the first compression part 31 as the first gas flow, the gas flow of the second compression part 32 as the second gas flow, and the sum of the gas flows of the first compression part 31 and the second compression part 32 as the total gas flow. Further, the first gas flow is equal to the total gas flow minus the second gas flow, and it can be understood that the first operating parameter further includes the first gas flow, and the second operating parameter further includes the second gas flow. The ratio between the second gas flow and the total gas flow is 0.357~0.375.

[0069] Preferably, the second gas flow is 30~50 kg / H, and the total gas flow is 80~140 kg / H. Then the ratio between the second gas flow and the total gas flow = (30~50 kg / H) / (80~140 kg / H), that is, the minimum ratio value between the second gas flow and the total gas flow is equal to 30 / 80=0.375, and the maximum ratio value between the second gas flow and the total gas flow is equal to 50 / 140≈0.357. For example, if the second gas flow is 30 kg / H, the first gas flow is 80~140 kg / H-30 kg / H=50~110 kg / H. If the second gas flow is 50 kg / H, the first gas flow is 80~140 kg / H-50 kg / H=30~90 kg / H. In summary, the first gas flow corresponding to the high-temperature evaporator is 30~90 kg / H.

[0070] In this way, the second gas flow of the second compression part 32 corresponding to the low-temperature evaporator is low (such as 30~50 kg / H), which is suitable for the operation of the second evaporator 2 at a lower evaporation temperature. By reducing the gas flow, the load of the second compression part 32 is reduced, and the efficiency is prevented from being reduced due to the reduction of the gas flow coefficient. At the same time, the first gas flow of the first compression part 31 corresponding to the high-temperature evaporator is high, which is suitable for the operation of the second evaporator 2 at a higher evaporation temperature. The higher gas flow helps to maintain a higher refrigeration efficiency under high evaporation temperature conditions, better meets the refrigeration demand, and thereby optimizes the overall efficiency of the heat pump circulation system.

[0071] In addition, when the ratio between the second gas delivery amount and the total gas delivery amount is within the range of 0.357-0.375, the stable operation of the compression component 3 can be maintained, the pressure balance inside the compression component 3 can be well controlled, pressure fluctuation and mechanical vibration can be avoided, and the overall operation stability of the compression component 3 can be ensured.

[0072] As another preferred mode of the present embodiment, specifically, as shown in Figure 3 The compression component 3 further has a first-stage flow channel 381, a second-stage 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. The first suction part 34 is connected to the first compression part 31 through the first-stage flow channel 381, i.e., one end of the first-stage 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 first-stage flow channel 381 is connected to the first compression part 31. The refrigerant flows into the first compression part 31 under the guidance of the first-stage flow channel 381. The second suction part 35 is connected to the intermediate mixing cylinder 384 through the second-stage flow channel 382, i.e., one end of the second-stage flow channel 382 is connected to the second suction port / second suction pipe of the second suction part 35, and the other end of the second-stage flow channel 382 is connected to the intermediate mixing cylinder 384. The refrigerant flows into the intermediate mixing cylinder 384 under the guidance of the second-stage flow channel 382, mixes with the refrigerant compressed by the first compression part 31, and flows into the second compression part 32. 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 flows into the exhaust part 33 under the guidance of the total exhaust flow channel 383 and is output from the exhaust part 33.

[0073] In this way, the refrigerant is buffered and pressure-stabilized in the intermediate mixing cylinder 384, and the temperature of the refrigerant is reduced and the energy consumption is reduced. It can be understood that the refrigerant compressed by the first compression part 31 is cooled so that the second compression part 32 can further compress efficiently, the suction temperature of the second compression part 32 is reduced, the deterioration speed of the lubricating oil at high temperature is slowed down, the lubrication of the bearings and other moving parts is improved, and the service life of the compression component 3 is prolonged. Thus, the effect of approaching isothermal compression can be better achieved, and the overall efficiency, compression energy efficiency, and volumetric efficiency of the compression component 3 are improved, the heat loss and internal leakage are reduced, and the load on the bearings in the compression component 3 is greatly reduced, thereby effectively prolonging the service life of the bearings in the compression component 3 and the service life of the compression component 3.

[0074] It should be noted that the gas delivery amount of the first compression part 31 is assumed to be a first-stage gas delivery amount, and the gas delivery amount of the second compression part 32 is assumed to be a second-stage gas delivery amount. It can be understood that the first operating parameter further includes the first-stage gas delivery amount, and the second operating parameter further includes the second-stage gas delivery amount. The ratio between the first-stage gas delivery amount and the second-stage gas delivery amount is within the range of 0.357-0.375.

[0075] Preferably, the first gas delivery amount is 30-50 kg / H, and the second gas delivery amount is 80-140 kg / H, so the ratio between the first gas delivery amount and the second gas delivery amount = (30-50 kg / H) / (80-140 kg / H), that is, the minimum value of the ratio between the first gas delivery amount and the second gas delivery amount is equal to 30 / 80=0.375, and the maximum value of the ratio between the first gas delivery amount and the second gas delivery amount is equal to 50 / 140≈0.357. Such a setting has unexpected technical effects, including the following:

[0076] 1. Achieving the purpose of efficient energy utilization and improvement: The first compression part 31 performs first-stage compression on the refrigerant supplied by the first evaporator 1 and recovers heat. For example, assuming that the first evaporator 1 is a low-temperature evaporator, the first evaporator 1 absorbs heat from the drying air flow, and the setting of the first gas delivery amount of 30-50 kg / H will ensure that the refrigerant absorbs heat at an appropriate flow rate, avoiding the refrigerant being taken away before fully absorbing heat due to excessive refrigerant flow, or the refrigerant flow being too small to make the heat exchange efficiency of the first evaporator 1 low. At the same time, after completing the first-stage compression, the refrigerant will be mixed with the refrigerant supplied by the second evaporator 2 in the intermediate mixing cylinder 384 for second-stage compression, and the setting of the second gas delivery amount of 80-140 kg / H will also effectively improve the temperature and pressure of the refrigerant, so that it can release high enough heat in the condenser assembly 4 for heating and other purposes.

[0077] 2. Achieving flexible adjustment of the gas delivery amount of the compression part to adapt to load changes. For example, when the heat load is low, the first-stage compression can operate at a gas delivery amount of about 30 kg / H, and the second-stage compression can also correspondingly reduce the gas delivery amount, such as operating at a gas delivery amount of about 80 kg / H, so that the heat pump circulation system can also operate efficiently in a partial load state, avoiding energy waste. When the heat load is high, the heat pump circulation system can increase the gas delivery amount to meet the demand, and the first gas delivery amount can be adjusted to about 50 kg / H, and the second gas delivery amount can be correspondingly adjusted to about 140 kg / H.

[0078] In addition, the ratio between the first gas delivery amount and the second gas delivery amount is in the range of 0.357-0.375, which can also maintain the stable operation of the compression part 3, so that the pressure balance inside the compression part 3 can be well controlled to avoid pressure fluctuations and mechanical vibrations, and the overall operation stability of the compression part 3 can also be ensured.

[0079] As another preferred mode of the embodiment, the first compression unit 31 and the second compression unit 32 are independently provided compressors, the first compression unit 31 is used to compress the refrigerant flowing through the first evaporator 1, and the second compression unit 32 is used to compress the refrigerant flowing through the second evaporator 2 or the refrigerant mixed with the refrigerant compressed and output by the first compression unit 31.

[0080] As a further preferred mode, the first compression unit 31 has a total output port and a total input port, 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, so that the refrigerant provided by 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 is delivered to the second compression unit 32, the second injection end of the second compression unit 32 is connected to the second evaporator 2, so that the refrigerant compressed by the first compression unit 31 is mixed with the refrigerant provided by the second evaporator 2 and then compressed by the second compression unit 32, and the total discharge port of the second compression unit 32 is connected to the condensing inlet of the condenser assembly 4.

[0081] In addition to the above preferred mode, as a further preferred mode, the first compression unit 31 has a total output port, a first input end and a second input end, 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 first input end or the second input end of the first compression unit 31 is connected to the first evaporator 1, so that the refrigerant provided by 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 is 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 total discharge port of the second compression unit 32 is connected to the condensing inlet of the condenser assembly 4. In this way, the two-stage compression of the refrigerant is achieved by the cooperation of the first compression unit 31 and the second compression unit 32.

[0082] As a further preferred mode, the heat pump circulation system further comprises a three-way connector, the first compression unit 31 has a total output port and a total input port, 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 provided by the first evaporator 1 can be delivered to the first compression unit 31 for separate compression, the total injection port of the second compression unit 32 is connected to the second evaporator 2, so that the refrigerant provided by the second evaporator 2 can be delivered to the second compression unit 32 for separate compression, and the total output port of the first compression unit 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.

[0083] In this way, the refrigerant provided to the first evaporator 1 and the second evaporator 2 is compressed separately by 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.

[0084] It should be noted that the pressure at the end of the compression part 3 connected to the first evaporator 1 is the suction pressure, and the suction pressure is in the range of 0.4-1.2 Mpa. In this way, when the suction pressure is in the range of 0.4-1.2 Mpa, not only can the compression ratio of the compression part 3 be controlled in a suitable range, but also the heat pump circulation system can adapt to such changes through corresponding control measures (such as adjustment of the refrigerant flow adjusting part), so that the flow and state of the refrigerant remain relatively stable.

[0085] If the suction pressure is less than 0.4 Mpa, the suction pressure is too low, which will cause the compression ratio of the compression part 3 to be too large, and the high compression ratio will cause the exhaust temperature of the compression part 3 to be too high, which not only reduces the efficiency of the compression part 3, but also damages the seal and lubricating oil of the compression part 3, affecting the service life of the compression part 3. At the same time, the low suction pressure will also cause the heat pump circulation system to malfunction, such as serious frosting of the evaporator assembly, insufficient refrigerant flow, etc. If the suction pressure is greater than 1.2 Mpa, the suction pressure is too high, which will cause the system pressure of the heat pump circulation system to be too high, causing pipe rupture, safety valve jump and other safety problems.

[0086] Further, the pressure at the end of the compression part 3 connected to the condenser assembly 4 is the exhaust pressure, and the exhaust pressure is in the range of 1.0-4.2 Mpa. It can be understood that the exhaust pressure is one of the resistance indexes that the compression part 3 needs to overcome when working. By controlling the range of the exhaust pressure to be 1.0-4.2 Mpa, the power consumption of the compression part 3 is avoided to be too large, that is, the risk of the mechanical load of the compression part 3 being too large due to the high exhaust pressure is avoided, thereby avoiding the wear and fatigue of the internal parts of the compression part 3, ensuring the service life of the compression part 3 and ensuring the safe and stable operation of the heat pump circulation system.

[0087] If the exhaust pressure is greater than 4.2 Mpa, the exhaust pressure is too high, which will cause the compression ratio of the compression component 3 to be too large, and the irreversible loss of the refrigerant leakage loss, heat loss, etc. inside the compression component 3 will increase. At the same time, it will also make the condensation temperature of the refrigerant too high, which will cause the heat dissipation load of the condenser assembly 4 to increase. In addition, it will also make the pressure of the heat pump circulating system too high, which will easily cause the pipes and other components in the heat pump circulating system to fail due to the inability to withstand high pressure, such as pipe rupture, explosion, etc. If the exhaust pressure is less than 1.0 Mpa, the exhaust pressure is too low, which will cause the refrigerant circulation to be not smooth, and the heat pump circulating system will not be able to operate normally, such as the evaporator assembly being severely frosted, the refrigerant flow being insufficient, etc.

[0088] In this embodiment, as shown in Figure 1 , Figure 2 and Figure 5 , the heat pump circulating system further comprises a refrigerant flow regulating member arranged between the evaporator assembly and the condenser assembly 4. The refrigerant flow regulating member is preferably an expansion valve, which can also be referred to as a throttling valve or a regulating valve. The refrigerant flow regulating member is used to regulate and control the flow of refrigerant flowing from the condenser assembly 4 to the evaporator assembly, thereby ensuring that the heat pump circulating system operates under optimal conditions, and achieving the purposes of rapid refrigeration of the evaporator assembly and / or heating of the condenser assembly 4, precise temperature control and energy saving.

[0089] It should be noted that under the throttling and pressure reducing effect of the refrigerant flow regulating member, the medium temperature high pressure / high pressure subcooled liquid refrigerant can also become low temperature low pressure mist refrigerant through the refrigerant flow regulating member, thereby achieving the purpose of reducing the pressure of the refrigerant, so that the refrigerant can evaporate more easily in the evaporator assembly and absorb heat. At the same time, the refrigerant flow regulating member also has a stable superheat degree, i.e. the refrigerant flow regulating member can control the valve flow through the change of the superheat degree at the end of the evaporator assembly, preventing the occurrence of insufficient area utilization of the evaporator assembly and knocking cylinder phenomenon, making the heat pump circulating system run more stably.

[0090] As one of the preferred modes of this embodiment, as shown in Figure 1 , the above-mentioned refrigerant flow regulating member comprises a total regulating valve 71 having a throttling and pressure reducing function, one end of the total regulating valve 71 being communicated with the condenser assembly 4, and the first evaporator 1 and the second evaporator 2 being communicated with the other end of the total regulating valve 71. That is, the above-mentioned evaporator assembly is communicated with the condenser assembly 4 through a connecting pipe assembly, which comprises a first connecting pipe 81 connecting the first evaporator 1, a second connecting pipe 82 connecting the second evaporator 2, and a total connecting pipe 83 connecting the condenser assembly 4.

[0091] It can be understood that the first connecting pipe 81 and the second connecting pipe 82 can be integrally formed, and can also be connected by a pipe joint (such as threaded connection, clamping connection, etc.), and the total adjusting valve 71 is installed on the total connecting pipe 83. In this way, the refrigerant flowing through the first connecting pipe 81 and the second connecting pipe 82 can be throttled and adjusted by the total adjusting valve 71, the system working condition is easy to adjust, and the overall cooling capacity is more stable.

[0092] Optionally, according to Figure 1 It can be understood that the first connecting pipe 81 and the second connecting pipe 82 can be integrally formed, and can also be connected by a pipe joint (such as threaded connection, clamping connection, etc.), and the total adjusting valve 71 is installed on the total connecting pipe 83. In this way, the refrigerant flowing through the first connecting pipe 81 and the second connecting pipe 82 can be throttled and adjusted by the total adjusting valve 71, the system working condition is easy to adjust, and the overall cooling capacity is more stable.

[0093] As another preferred mode of the present embodiment, in combination with Figure 2 and Figure 5 It can be understood that the first connecting pipe 81 and the second connecting pipe 82 can be integrally formed, and can also be connected by a pipe joint (such as threaded connection, clamping connection, etc.), and the total adjusting valve 71 is installed on the total connecting pipe 83. In this way, the refrigerant flowing through the first connecting pipe 81 and the second connecting pipe 82 can be throttled and adjusted by the total adjusting valve 71, the system working condition is easy to adjust, and the overall cooling capacity is more stable.

[0094] In this way, the first expansion valve 73 throttles and adjusts the refrigerant flowing through the first evaporator 1, and the second expansion valve 74 throttles and adjusts the refrigerant flowing through the second evaporator 2, so that the flow regulation range of the entire heat pump circulation system is larger, the adjustment flexibility is higher, and the adjustment operation is more convenient. And the working condition of the heat pump circulation system is also faster.

[0095] In the above, by using the first compression part 31 and the second compression part 32 with different volumes in the compression part 3, the problem of excessive load required by the compression part 3 and the requirement of too high 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, the heat exchange efficiency of the evaporator assembly is usually missed, which easily leads to the phenomenon that the temperature of the drying air flow after flowing through the evaporator assembly is still much higher than the temperature of the refrigerant inside the evaporator assembly, resulting in heat exchange deviation. Since the heat exchange deviation caused by the evaporator assembly is a common technical problem easily ignored by those skilled in the art, the existing heat pump clothes dryer basically has the problem of deviation of cooling and dehumidifying effect.

[0096] To solve the above technical problems, the utility model also provides a technical scheme, the inside of the machine body further has a control circuit board, and an evaporation temperature sensing element and a condensation temperature sensing element arranged in the fluid channel, wherein the evaporation temperature sensing element is used to detect the temperature of the drying air flow after flowing through the evaporator assembly and generate an evaporation air temperature value, and the condensation temperature sensing element is used to detect the temperature of the drying air flow flowing through the condenser assembly 4 and generate a condensation air temperature value, the first evaporator 1, the second evaporator 2, the evaporation temperature sensing element, the condensation temperature sensing element, the compression part 3 and the condenser assembly 4 are 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 air temperature value.

[0097] In this way, the evaporation temperature sensing element can obtain the temperature information of the drying air flow after flowing through the evaporator assembly in time, generate the evaporation air temperature value and transmit it to the control circuit board, so that the control circuit board can monitor the temperature value and its change after the drying air flow is cooled by the evaporator assembly in real time and directly, and compare the evaporation air temperature value with the reference range value to determine whether to send a control instruction to the evaporator assembly. At this time, the control circuit board can most directly and accurately monitor the evaporation air temperature value after the drying air flow exchanges heat 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 drying air flow during the entire drying process.

[0098] At the same time, 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 reference range value, the temperature of the drying air flow can be adjusted to the reference range value in a shorter time, so as to ensure that the clothes treatment equipment has good cooling and dehumidifying effect.

[0099] For example, when the evaporative air temperature value is far beyond the upper limit temperature value of the reference range value, the evaporative temperature of the second evaporator 2 and the first evaporator 1 can be simultaneously lowered, so that the drying air flow can absorb more heat when flowing through the second evaporator 2 and the first evaporator 1, thereby rapidly reducing the temperature of the drying air flow, and timely and significantly adjusting the evaporative air temperature value to the reference range value.

[0100] For example, when the evaporative air temperature value is far beyond the upper limit temperature value of the reference range value, the evaporative temperature of the second evaporator 2 and the first evaporator 1 can be simultaneously lowered, so that the drying air flow can absorb more heat when flowing through the second evaporator 2 and the first evaporator 1, thereby rapidly reducing the temperature of the drying air flow, and timely and significantly adjusting the evaporative air temperature value to the reference range value.

[0101] In addition, monitoring the evaporative air temperature value and the condensing air temperature value by the control circuit board can not only better realize the stable operation of the heat pump circulation system at a low evaporative temperature and a high condensing temperature, but also avoid damage to clothes due to excessively high temperature flowing into the drum component 5.

[0102] At the same time, the control circuit board can also preliminarily evaluate the operation of the compression component 3 through the evaporative air temperature value and the condensing air temperature value. Specifically, the evaporative air temperature value can reflect the suction state of the compression component 3 to a certain extent, and the condensing air temperature value can reflect the exhaust state of the compression component 3 to a certain extent. Then, combined with other parameters of the compression component 3, such as pressure, current, power, etc., a comprehensive judgment can be made to more efficiently and accurately troubleshoot and judge the operation of the compression component 3, thereby ensuring the stable performance of the heat pump circulation system.

[0103] As a further preferred mode of the present embodiment, the evaporative temperature sensing member includes a first temperature detection member and a second temperature detection member, wherein the first temperature detection member is used to detect the temperature of the drying air flow after flowing through the first evaporator 1 and generate a first air temperature value, and the second temperature detection member is used to detect the temperature of the drying air flow after flowing through the second evaporator 2 and generate a second air temperature value. The first air temperature value is the evaporative air temperature value of the evaporative temperature sensing member, and of course, it can also be a temperature value calculated by the first air temperature value and the second air temperature value. Moreover, the control circuit board can adjust the evaporative temperature of the first evaporator 1 and the evaporative temperature of the second evaporator 2 according to the first air temperature value and the second air temperature value.

[0104] Therefore, the first evaporator 1 and the second evaporator 2 can be adjusted to maintain the temperature of the evaporator assembly within a more stable and better temperature range, that is, to ensure that the evaporated air temperature after the drying air flow passes through the evaporator assembly is stably within the reference range, thereby achieving the best cooling and dehumidifying effect, and further ensuring that the clothes treatment equipment has good drying effect and drying quality, and effectively saves the energy consumption of the clothes treatment equipment.

[0105] Preferably, the first temperature detection member is installed near the air outlet side of the first evaporator 1, and / or the second temperature detection member is installed near the air outlet side of the second evaporator 2. Therefore, the following unexpected effects can be achieved:

[0106] 1. The temperature of the drying air flow after flowing through the first evaporator 1 and the second evaporator 2 can be directly measured, which can accurately reflect the actual refrigeration effect of the first evaporator 1 and the second evaporator 2. This allows the heat pump circulation system to make timely adjustments based on the temperature value to ensure that the output drying air temperature is always within the reference range.

[0107] 2. The first temperature detection member can quickly sense changes in the working state of the first evaporator 1, and the second temperature detection member can quickly sense changes in the working state of the second evaporator 2. When the refrigeration capacity of either the first evaporator 1 or the second evaporator 2 changes, such as due to changes in refrigerant flow, surface dust, etc., the corresponding temperature detection member in the evaporated temperature sensor can quickly detect fluctuations in the temperature of the drying air flow and transmit signals to the control circuit board. This allows the heat pump circulation system to make adjustments more quickly, improving the stability and response speed of the heat pump circulation system.

[0108] 3. It is helpful for fault diagnosis. If the heat pump circulation system fails, such as one of the first evaporator 1 and the second evaporator 2 being blocked or refrigerant leaking, the temperature of the corresponding air outlet 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 member in the evaporated temperature sensor. For example, if the temperature of the air outlet 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.

[0109] As a preferred mode of the present embodiment, please refer to Figure 6As shown, the temperature range of the evaporated air temperature value is 5℃~40℃. Within this temperature range, the evaporator assembly can effectively condense the moisture in the drying air flow into water droplets for discharge, improving the drying efficiency. At the same time, it can also operate at a higher energy efficiency ratio, reducing the power demand of the clothes treatment equipment, reducing energy consumption, and achieving the purpose of saving electricity, thereby achieving a balance between efficiency and quality, and ensuring the safety, stability and reliability of the clothes treatment equipment during use. In addition, the appropriate temperature can also prevent the occurrence of phenomena such as scaling and corrosion inside the evaporator assembly, and maintain the good performance of the evaporator assembly.

[0110] When the evaporated air temperature value is less than 5℃, the evaporated air temperature value is too low, which will increase the power consumption of the compression component 3 and reduce the operating efficiency of the clothes treatment equipment. When the evaporated air temperature value is greater than 40℃, the ability of the evaporator assembly to extract heat will decrease, and the heat exchange efficiency will be greatly reduced.

[0111] Further, the first temperature detection member detects and generates a first air temperature value within a temperature range of 10℃~35℃, that is, the temperature of the drying air flow flowing through the first evaporator 1 is controlled within a range of less than 35℃, and the second evaporator 2 cooperates with the first evaporator 1, which can increase the dehumidification rate of the clothes treatment equipment and its heat pump circulation system by at least one time, and the drying time of a 3kg IEC European standard load (moisture content 60%) can be close to 45min. Therefore, the drying time of 45min can generally ensure that the wet clothes are fully dried. Within this time period, the heat pump circulation system can continuously absorb moisture from the wet clothes and discharge it to the external environment. Whether the clothes are made of cotton, hemp or synthetic fibers, the moisture in the wet clothes can be fully evaporated to achieve the desired drying degree. At the same time, the longer drying time helps to achieve uniform drying of the wet clothes. The drying air flow can circulate fully inside the clothes treatment equipment, so that each part of the wet clothes can be subjected to the same drying effect. This can avoid local wetness or uneven drying, and reduce the possibility of wrinkles on the clothes.

[0112] The unexpected effect is that compared with the existing single-cycle pure heat pump drying method, the drying time of a 3kg IEC European standard load (moisture content 60%) is close to 45min, which is a very short time, achieving the purpose of efficient drying, and the clothes fibers will not be damaged due to excessive heating. This is particularly important for some high-end fabrics or delicate clothes, which can prolong the service life of the clothes. At the same time, within this time period, the heat pump circulation system can operate in a relatively stable state, fully utilize energy, reduce energy waste and reduce costs.

[0113] It should be noted that the temperature difference between the second air temperature value and the first air temperature value is greater than 5℃, and the second air temperature value is greater than 0℃. In this way, the first evaporator 1 can be guaranteed to be normal and efficient heat exchange. For example, please refer to Figure 1 , Figure 2 and Figure 5 When the evaporation temperature of the first evaporator 1 is less than the evaporation temperature of the second evaporator 2, the temperature of the drying air flow flowing through the second evaporator 2 is preferably controlled to be less than 30℃, as shown in Figure 6 The temperature range of the first air temperature value detected and generated by the first temperature detection member is controlled to be between 5℃ and 25℃, which effectively ensures that the dehumidification rate of the clothes treatment equipment is increased by at least one time when the air volume is greater than 200m3 / h. When the evaporation temperature of the first evaporator 1 is greater than the evaporation temperature of the second evaporator 2, it not only ensures that the first evaporator 1 and the second evaporator 2 can be more accurately heat exchanged with the drying air flow, thereby improving the energy efficiency ratio of the entire heat pump circulation system, and realizing the effect of deep dehumidification, thereby effectively ensuring the stability and reliability of the clothes treatment equipment.

[0114] The above is the explanation and description of the clothes treatment equipment proposed in the embodiments of the present application, and since the clothes treatment equipment proposed in the embodiments of the present application adopts all the technical solutions of the above-mentioned embodiments, it at least has all the beneficial effects brought by the technical solutions of the above-mentioned embodiments, which will not be repeated here.

[0115] The same or similar reference numerals in the drawings of the embodiments correspond to the same or similar parts; in the description of the present application, it should be understood that if the orientations or positional relationships indicated by the terms "upper", "lower", "left", "right" and the like are based on the orientations or positional relationships shown in the drawings, they are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, therefore the terms describing the positional relationship in the drawings are only used for exemplary illustration, and cannot be understood as a limitation of the present application, for those skilled in the art, the specific meanings of the above-mentioned terms can be understood according to the specific circumstances.

[0116] The above is only a preferred embodiment of the present application, and does not limit the present application, any modification, equivalent replacement and improvement made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1.A laundry treating apparatus, characterized by, The laundry treatment apparatus comprises a heat pump circulation system, a driving fan, and a temperature detection member. The heat pump circulation system comprises a first evaporator, a second evaporator, a compression component, and a condenser assembly. The driving fan is configured to drive a drying air flow to pass through the first evaporator and the second evaporator in a fluid passage. The temperature of the drying air flow after passing through the first evaporator is lower than the temperature of the drying air flow after passing through the second evaporator. 2.The laundry treating apparatus of claim 1, wherein, The first temperature detection member is arranged on a side close to an air outlet of the first evaporator, and / or the second temperature detection member is arranged on a side close to an air outlet of the second evaporator. 3.The laundry treating apparatus of claim 2, wherein, The temperature range of the first air temperature value is controlled to be 10-35℃. 4.The laundry treating apparatus of claim 2 or 3, wherein, The temperature difference between the second air temperature value and the first air temperature value is greater than 5℃, and the second air temperature value is greater than 0℃. 5.The laundry treating apparatus of claim 2 or 3, wherein, The evaporation temperature of the first evaporator is higher than the evaporation temperature of the second evaporator. 6.The laundry treating apparatus of claim 1 or 2 or 3, wherein, The compression component comprises a first compression part, a second compression part, an exhaust part, a first suction part, and a second suction part. 7.The laundry treating apparatus of claim 1, wherein The first suction part is connected to the first compression part, the exhaust part and the second suction part are both connected to the second compression part. 8.The laundry treating apparatus of claim 7, wherein, The first evaporator is connected to the first suction part, and the second evaporator is connected to the second suction part. 9.The laundry treating apparatus of claim 7, wherein the first and second openings are formed in the first and second sides of the cabinet, respectively. The exhaust part of the compression component is connected to a condensing inlet of the condenser assembly. 10.The laundry treating apparatus of claim 1 or 2 or 3, wherein, The first evaporator and the second evaporator are both connected to a condensing outlet of the condenser assembly. The first compression part and the second compression part are independently configured. The compression component further comprises a first internal flow channel and a second internal flow channel. The exhaust part and the first suction part are both connected to the first compression part through the first internal flow channel. The compression component further comprises 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 suction part is connected to the first compression part through the primary flow channel. The second suction 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. The heat pump circulation system further comprises a refrigerant flow adjusting member. The refrigerant flow adjusting member is configured to adjust and control the flow of refrigerant to the evaporator assembly.

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