Independent suction multi-cylinder compressor, refrigeration system and clothes dryer

Abstract

The utility model belongs to clothes dryer technical field especially relates to a kind of independent suction multi-cylinder compressor, refrigerating system and clothes dryer, and the compressor includes shell, multiple independent suction cylinders and multiple distributors;Multiple the cylinder and multiple distributors are connected one by one in correspondence;Multiple the cylinder exhaust port is all communicated with the inner chamber of shell, and share an exhaust passage;At least two the cylinder volume is different, in the independent suction multi-cylinder compressor of the utility model, by setting multiple independent suction cylinders and differentiating design to its volume difference, the "flow demand difference" of refrigerating system is solidified as the structural difference of compressor "suction capacity", avoid the problem of "flow and demand dynamic mismatching" in traditional throttling regulation, and this transformation does not need additional control component, with Control process is simple, flow control is accurate, response is fast, reliability is strong, can have the advantages of drying effect and energy efficiency optimization.

Description

Technical Field

[0001] This utility model belongs to the field of dryer technology, and in particular relates to a multi-cylinder compressor with independent air intake, a refrigeration system and a dryer. Background Technology

[0002] During the operation of a dryer, to achieve circulating dehumidification, the evaporator cools and removes water from the humid air. As the humid air flows through the evaporator, the refrigerant absorbs heat and cools it. When the temperature drops below the air's dew point, the water vapor condenses into liquid water, thus achieving dehumidification. Generally, the lower the evaporator temperature, the lower the evaporator surface temperature, and the lower the temperature the humid air can be cooled to. Therefore, the maximum amount of water vapor (saturated humidity) that the circulating air can hold is smaller. Thus, a lower evaporation temperature allows the humid air to cool to a lower temperature, releasing more moisture and reducing residual humidity, thereby improving drying efficiency. However, on the other hand, when the evaporation temperature is too low, the saturated pressure of the refrigerant inside the evaporator decreases, leading to an increase in the refrigerant's suction volume. Therefore, when the evaporation temperature decreases, the mass of refrigerant circulating per unit time in the compressor decreases, and the heat absorbed by the evaporator (cooling capacity) decreases. Simultaneously, the compressor's compression ratio increases significantly, leading to a significant increase in power consumption per unit cooling capacity, resulting in a decrease in the dryer's drying capacity and energy efficiency. This leads to the core contradiction in traditional single-evaporator heat pump dryers: a single evaporator cannot simultaneously achieve both "low evaporation temperature (high dehumidification)" and "high cooling capacity and high energy efficiency".

[0003] To address this, those skilled in the art have proposed a refrigeration system with dual evaporators for clothes dryers. This system achieves two different evaporation temperatures through two evaporators connected in parallel or series. The higher evaporation temperature evaporator ensures cooling capacity and energy efficiency, while the lower evaporation temperature evaporator enhances dehumidification, thus improving drying performance while avoiding energy loss. Furthermore, existing technologies offer various methods to achieve dual evaporation temperatures. For example, adjusting the refrigerant flow rate and pressure drop into the two evaporators using two throttling elements of different specifications creates a pressure difference, ultimately achieving a temperature difference. Another example is connecting two evaporators in series in the same refrigerant circuit, controlling the refrigerant's "residence time" or "flow rate ratio" in the two evaporators to create different pressure losses, thus generating a temperature difference. Additionally, a single variable-capacity compressor, combined with a solenoid valve / check valve, dynamically switches the operating pressure of the two evaporators to achieve differentiated control of the evaporation temperature. However, these methods of achieving dual evaporation temperatures often suffer from problems such as large deviations in flow control, mismatch between compressor suction pressure and evaporator pressure, delayed response of the flow distribution system, easy imbalance, and frequent switching of components such as valves and compressors. This causes the refrigeration system to be mired in the quagmire of control complexity and face the dual dilemma of energy efficiency and cost.

[0004] In summary, providing a multi-cylinder compressor, refrigeration system, and dryer with independent air intake that features a simple control process, precise flow regulation, fast response, high reliability, and the ability to combine drying effect with energy efficiency optimization is one of the technical problems that urgently needs to be solved by those skilled in the art. Utility Model Content

[0005] The purpose of this invention is to address the aforementioned technical problems by providing a multi-cylinder compressor, refrigeration system, and dryer with independent air intake that features a simple, precise, fast-responding, and highly reliable control process, thereby achieving both drying effect and energy efficiency optimization while maintaining dual evaporation temperatures in the dryer.

[0006] In view of this, the present invention provides a multi-cylinder compressor with independent air intake. The compressor includes a housing, multiple independent air intake cylinders and multiple liquid distributors. The multiple cylinders and multiple liquid distributors are connected in a one-to-one correspondence. The exhaust ports of the multiple cylinders are all connected to the inner cavity of the housing to share a common exhaust channel. At least two of the cylinders have different volumes.

[0007] Furthermore, the compressor includes: Two independently intake cylinders, namely the first cylinder and the second cylinder; And two dispensers, namely the first dispenser and the second dispenser; The first cylinder is connected to the first distributor, and the second cylinder is connected to the second distributor.

[0008] Furthermore, the volumes of the first cylinder and the second cylinder are V1 and V2, respectively, and the volume ratio of the first cylinder and the second cylinder satisfies: 1 < V1 / V2.

[0009] Furthermore, the volume ratio of the first cylinder and the second cylinder satisfies: V1 / V2≤1.3.

[0010] Furthermore, the volumes of the first distributor and the second distributor are V3 and V4, respectively, and the volume ratio of the first distributor and the second distributor satisfies: 1 < V3 / V4.

[0011] Furthermore, the volume ratio of the first distributor and the second distributor satisfies: V3 / V4≤1.3.

[0012] Furthermore, the volume ratio V1 / V2 of the first cylinder and the second cylinder is equal to the volume ratio V3 / V4 of the first distributor and the second distributor.

[0013] This utility model also provides a refrigeration system, which includes: a condenser, a first evaporator, a second evaporator, a throttling device, and the aforementioned independent suction multi-cylinder compressor. The first evaporator and the second evaporator are connected in parallel at the air inlet of the independent suction multi-cylinder compressor, and the first evaporator is connected to a first liquid distributor, while the second evaporator and the second liquid distributor are connected.

[0014] This utility model also provides a clothes dryer, which is a heat pump clothes dryer, and the clothes dryer includes the above-mentioned refrigeration system.

[0015] Furthermore, in the dryer, the first evaporator is located in front of the second evaporator, and the circulating air in the dryer first passes through the first evaporator and then through the second evaporator.

[0016] The beneficial effects of this utility model are: 1. In the multi-cylinder compressor with independent air intake described in this utility model, by setting multiple independent air intake cylinders and designing their volumes differently, the "flow demand difference" of the refrigeration system is solidified into the "structural difference of air intake capacity" of the compressor, which avoids the problem of "dynamic mismatch between flow and demand" in traditional throttling regulation. Moreover, this conversion does not require additional control components, and has the advantages of simple control process, accurate flow regulation, fast response, high reliability, and can combine drying effect and energy efficiency optimization.

[0017] 2. In the multi-cylinder compressor described in this utility model, the design of connecting the exhaust ports of multiple cylinders to the inner cavity of the housing and sharing a single exhaust channel eliminates the need for separate exhaust pipes, valves, and other components for each cylinder. During the exhaust process, the shared exhaust channel directly collects the exhaust from each cylinder to the same intermediate cavity or high-pressure stage inlet, eliminating the need for additional pressure regulation. This results in a shorter airflow path, lower flow resistance, and lower friction loss, significantly reducing production and manufacturing costs while making the compressor more compact. Furthermore, it reduces exhaust pressure pulsation, minimizes pipeline vibration and noise, and improves the stability of system operation. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the structure of the independent intake multi-cylinder compressor described in this utility model; The markings in the diagram are as follows: 11. First cylinder; 12. Second cylinder; 21. First distributor; 22. Second distributor. Detailed Implementation

[0019] The technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application are within the scope of protection of this application.

[0020] In the description of this application, it should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. For ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0021] It should be noted that the terms "first," "second," etc., used in the specification and claims of this application are used to distinguish similar objects and not to describe a specific order or sequence. It should be understood that such use of data can be interchanged where appropriate so that embodiments of this application can be implemented in orders other than those illustrated or described herein, and the objects distinguished by "first," "second," etc., are generally of the same class and are not limited in number; for example, a first object can be one or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0022] It should be noted that, in this application, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes that element. Furthermore, it should be noted that the scope of the methods and apparatuses in the embodiments of this application is not limited to performing functions in the order shown or discussed, but may also include performing functions substantially simultaneously or in the reverse order, depending on the functions involved. For example, the described methods may be performed in a different order than described, and various steps may be added, omitted, or combined. Additionally, features described with reference to certain examples may be combined in other examples.

[0023] This utility model provides a multi-cylinder compressor with independent air intake, the compressor including a housing, multiple independent air intake cylinders and multiple liquid distributors; The cylinders and the distributors are connected in a one-to-one correspondence. The exhaust ports of the multiple cylinders are all connected to the inner cavity of the housing to share a single exhaust passage; At least two of the cylinders have different volumes.

[0024] In the multi-cylinder compressor with independent suction described in this utility model, by setting multiple independent suction cylinders and multiple liquid distributors, and connecting the multiple cylinders and multiple liquid distributors one by one, the independent operation of each cylinder is realized, avoiding mutual interference of pressure and flow in different circuits. On this basis, by setting multiple independent suction cylinders and designing their volumes differently, the "flow demand difference" of the refrigeration system can be solidified into the "structural difference of suction capacity" of the compressor. This can accurately match the differentiated flow demand of multiple evaporators, improve the system's compatibility, and avoid the problem of "dynamic mismatch between flow and demand" in traditional throttling regulation. Moreover, this conversion does not require additional control components, and has the advantages of simple control process, precise flow regulation, fast response, high reliability, and the ability to combine drying effect and energy efficiency optimization.

[0025] In multi-evaporator refrigeration systems, the difference in evaporation temperature among different evaporators is essentially due to the difference in refrigerant pressure within the evaporator. This difference in refrigerant pressure, in turn, is due to the difference in refrigerant flow rate. The difference in refrigerant flow rate requirement among different evaporators is essentially due to the different amounts of refrigerant vapor that need to be drawn away by the compressor per unit time. Cylinder volume, as a core physical parameter, directly determines the compressor's suction capacity. Generally, the larger the cylinder volume, the greater the displacement per suction stroke. Therefore, when the compressor speed is fixed, the total suction capacity (volume flow rate) per unit time is directly proportional to the volume. In this invention, the "difference in flow rate requirement" is solidified into a "structural difference in suction capacity" through the design of differentiated cylinder volumes, avoiding the problem of "dynamic mismatch between flow rate and demand" in traditional throttling regulation. Furthermore, this conversion does not require additional control components such as valves or sensors, offering the advantages of simplicity and ease of implementation.

[0026] Based on this, the cylinder volume directly determines the pressure maintenance capability and evaporation temperature of the corresponding evaporator by affecting the "vapor extraction rate". For example, a large-volume cylinder has a higher vacuum rate, which can quickly remove the refrigerant vapor generated in the evaporator, so that the "replenishment rate" and "removal rate" of vapor in the evaporator are balanced, naturally maintaining a higher pressure P1, and thus forming a high evaporation temperature; a small-volume cylinder has a lower vacuum rate, the vapor in the evaporator is removed more slowly, the vapor "accumulation" is less, forming a lower pressure P2, and thus forming a lower evaporation temperature.

[0027] In this invention, a gradient of pumping capacity for different cylinders is constructed by using a differentiated cylinder volume design. The differences in evaporation temperature, flow rate, and pressure of multiple evaporators are transformed into differences in the physical characteristics of the cylinder structure. Hardware calibration replaces complex software control, realizing a direct mapping from pressure difference to structural difference. While improving the control accuracy, system stability, and energy efficiency of multi-temperature zones, it simplifies the control logic and maintenance costs. It also has the advantages of precise flow control, fast response, and high reliability, making it particularly suitable for multi-scenario refrigeration equipment with high requirements for reliability and energy efficiency.

[0028] Furthermore, in the multi-cylinder compressor described in this utility model, the design of connecting the exhaust ports of multiple cylinders to the inner cavity of the housing and sharing a common exhaust channel eliminates the need to design exhaust pipes, valves, and other components separately for each cylinder. Only one set of connecting pipes is needed to complete the exhaust collection of all cylinders, reducing the number of parts, simplifying the assembly process, significantly reducing production and manufacturing costs, and making the compressor more compact.

[0029] More importantly, the cylinders of a multi-cylinder compressor are usually designed with a "phase difference," such as the staggered arrangement of the eccentric wheels in a rotary compressor. Therefore, there is a time difference in the exhaust process of a multi-cylinder compressor. In this structure, when multiple cylinders are designed to share a single exhaust channel, the exhaust from different cylinders will "overlap and buffer" in the pipeline, partially offsetting pressure fluctuations. For example, the exhaust peak value of the first cylinder 11 in this invention can be made to coincide with the exhaust valley value of the second cylinder 12, thereby reducing exhaust pressure pulsation, reducing pipeline vibration and noise, and improving the stability of system operation.

[0030] Furthermore, in this invention, multiple cylinders are connected in parallel with independent intake and common exhaust. During the exhaust process, the common exhaust channel can directly collect the exhaust from each cylinder to the same intermediate chamber or high-pressure stage inlet without additional pressure regulation. The airflow path is short, the flow resistance is low, and the friction loss is low.

[0031] As a preferred example of this utility model, the compressor includes: Two independent intake cylinders, namely cylinder 11 and cylinder 12; And two dispensers, namely the first dispenser 21 and the second dispenser 22; The first cylinder 11 is connected to the first distributor 21, and the second cylinder 12 is connected to the second distributor 22.

[0032] By setting up two cylinders 11 and 12 with different volumes and cooperating with corresponding distributors, the large-volume cylinder can be used to handle high-pressure refrigerant, which has the advantages of low compression ratio and low power consumption. The small-volume cylinder can be used to handle low-pressure refrigerant, which has the advantages of high compression ratio and enhanced dehumidification, but low flow rate and controllable total power consumption. This method, which allows the high-evaporation-temperature evaporator to ensure cooling capacity and energy efficiency, and the low-evaporation-temperature evaporator to enhance dehumidification, can improve the drying effect while avoiding energy loss.

[0033] Preferably, the volumes of the first cylinder 11 and the second cylinder 12 are V1 and V2, respectively, and the volume ratio of the first cylinder 11 and the second cylinder 12 satisfies: 1 < V1 / V2.

[0034] More preferably, the volume ratio of the first cylinder 11 and the second cylinder 12 satisfies: V1 / V2≤1.3.

[0035] This invention limits the volume ratio of the first cylinder 11 and the second cylinder 12 to within the range of 1 < V1 / V2 ≤ 1.3. This ensures that the first cylinder 11 has a stronger suction capacity than the second cylinder 12, and that the evaporator matched with the first cylinder 11 has a larger refrigerant circulation volume to maintain its efficient heat release capacity. It also avoids the problem of excessive pressure-flow difference leading to a high evaporation temperature evaporator, which reduces the heat exchange temperature difference with the environment and decreases cooling / heating efficiency, while an excessively low evaporation temperature evaporator will frost too quickly, negatively impacting dehumidification or heat exchange efficiency. Simultaneously, it avoids the problem of unbalanced loads on the cylinders, leading to uneven crankshaft stress, increased operating vibration, and noise. Furthermore, the present invention limits the volume ratio of the first cylinder 11 and the second cylinder 12 to the range of 1 < V1 / V2 ≤ 1.3, which means that the structural differences between the two cylinders are small. In use, only minor adjustments to the cylinder diameter and stroke are required, without the need for major changes to the overall layout of the compressor, thus reducing design complexity and manufacturing costs.

[0036] Preferably, the volumes of the first distributor 21 and the second distributor 22 are V3 and V4, respectively, and the volume ratio of the first distributor 21 and the second distributor 22 satisfies: 1 < V3 / V4.

[0037] More preferably, the volume ratio of the first distributor 21 and the second distributor 22 satisfies: V3 / V4≤1.3.

[0038] In this invention, the volume of the first distributor 21 is larger than that of the second distributor 22. This allows for flow-volume linkage with the large-volume first cylinder 11, matching the larger-volume first distributor 21 to buffer the gas-liquid two-phase flow and prevent refrigerant stagnation due to insufficient distributor capacity, thus affecting evaporation efficiency. Simultaneously, limiting the volume ratio V3 / V4 of the first distributor 21 and the second distributor 22 to ≤1.3 prevents imbalance in gas-liquid separation due to significant differences in distributor capacity.

[0039] More preferably, the volume ratio V1 / V2 of the first cylinder 11 and the second cylinder 12 and the volume ratio V3 / V4 of the first distributor 21 and the second distributor 22 are equal.

[0040] In this invention, setting the volume ratio of the distributor (V3 / V4) to the cylinder volume ratio (V1 / V2) equal ensures that the return gas from the high-flow-rate evaporator containing more gas-liquid mixture is fully separated by the large-capacity distributor, preventing liquid refrigerant from entering the cylinder. Conversely, the return gas from the low-flow-rate evaporator is efficiently processed by the small-capacity distributor, preventing gaseous refrigerant from stagnating. This matching ensures that the cylinder's suction state is unaffected by flow rate differences, further solidifying the transformation effect of converting structural differences into performance differences in this invention.

[0041] It should be noted that in this utility model, the relative positions of the first cylinder 11 and the second cylinder 12, as well as the first liquid dispenser 21 and the second liquid dispenser 22, are not particularly limited. The purpose of distinguishing them is only to more clearly illustrate this utility model.

[0042] As some examples of this utility model, the independently intake multi-cylinder compressor is a rotary compressor.

[0043] In addition, this utility model also provides a refrigeration system, which includes: a condenser, a first evaporator, a second evaporator, a throttling device, and the aforementioned independent suction multi-cylinder compressor. The first evaporator and the second evaporator are connected in parallel at the air inlet of the independent suction multi-cylinder compressor, and the first evaporator is connected to the first liquid distributor 21, and the second evaporator is connected to the second liquid distributor 22.

[0044] As some examples of this utility model, the structure of the refrigeration system is as follows: the first evaporator and the second evaporator are connected in parallel at the air inlet of the independently suction multi-cylinder compressor, the exhaust port of the independently suction multi-cylinder compressor is connected to one end of the condenser, and the other end of the condenser is connected to the first evaporator and the second evaporator respectively through a throttling device.

[0045] During the operation of the refrigeration system, the high-temperature, high-pressure gaseous refrigerant discharged from the exhaust port of the independently suction multi-cylinder compressor first enters the condenser. Through heat exchange with the heat exchange medium and the release of heat, the refrigerant gradually cools and condenses into a high-pressure saturated liquid refrigerant, which then flows out from the other end of the condenser. The high-pressure liquid refrigerant flowing out of the condenser is depressurized by a throttling device and converted into a low-pressure gas-liquid two-phase mixture. This mixture is then split into two streams and sent to the first evaporator and the second evaporator, respectively. The low-pressure gas-liquid two-phase refrigerant flowing into the first evaporator exchanges heat with the medium being cooled within the evaporator. After absorbing heat, the liquid refrigerant vaporizes into a low-pressure gaseous refrigerant, which then enters the first distributor 21. The first distributor 21 then centrifuges... Separation or gravity settling traps the liquid refrigerant, allowing only pure gaseous refrigerant to enter the first cylinder 11. The first cylinder 11 compresses the gaseous refrigerant, increasing its pressure and temperature to become high-pressure superheated gaseous refrigerant, which is then discharged from the compressor's exhaust port. Similarly, the low-pressure gas-liquid two-phase refrigerant flowing into the second evaporator exchanges heat with the cooled medium within the evaporator. After absorbing heat, the liquid refrigerant vaporizes into a low-pressure gaseous state and then enters the second distributor 22. Gas-liquid separation is completed in the second distributor 22, and the pure gaseous refrigerant enters the second cylinder 12. The second cylinder 12 compresses the gaseous refrigerant to produce high-pressure superheated gaseous refrigerant, which merges with the refrigerant discharged from the first cylinder 11 inside the compressor and enters the condenser together, completing this side cycle.

[0046] In multi-evaporator refrigeration systems, different evaporators have different evaporation temperatures, resulting in inherent differences in the required refrigerant flow rates. For example, high-evaporation-temperature evaporators require a larger flow rate to meet heat absorption demands due to their smaller heat exchange temperature difference, while low-evaporation-temperature evaporators require a smaller refrigerant flow rate due to their larger temperature difference. By employing the multi-cylinder compressor with independent suction as described in this invention, the larger-volume cylinder can be matched with the evaporator requiring a higher flow rate, ensuring sufficient refrigerant circulation through stronger suction capacity. Conversely, the smaller-volume cylinder can be matched with the evaporator requiring a lower flow rate, avoiding excessive refrigerant extraction due to excessive suction capacity. This precise "volume-flow rate" matching allows for refrigerant flow rate deviation control accuracy far superior to traditional throttling regulation, preventing cooling capacity loss due to flow rate mismatch.

[0047] Furthermore, the large-volume cylinder used in this invention has a higher suction rate, which can quickly remove the refrigerant vapor from the corresponding evaporator, maintain a higher saturation pressure, and generate a higher evaporation temperature; while the small-volume cylinder has a lower suction rate, which slows down the extraction speed of refrigerant vapor from the corresponding evaporator, naturally forming a lower saturation pressure and generating a lower evaporation temperature. This "vacuuming capacity gradient" formed by the volume difference can stably maintain the pressure difference between each evaporator without complex electronic control, thereby achieving precise separation of evaporation temperatures.

[0048] Furthermore, traditional technologies typically use a single-volume cylinder to handle refrigerants of varying flow rates. This approach can lead to decreased compression efficiency at low flow rates due to insufficient intake, while at high flow rates, it can cause a surge in power consumption due to excessively high compression ratios. The differentiated cylinder volume design in this invention allows for on-demand compression based on the pressure characteristics of the corresponding evaporator. Using a large-volume cylinder to handle high-pressure refrigerants offers advantages such as a low compression ratio and low power consumption, while using a small-volume cylinder to handle low-pressure refrigerants offers advantages such as a high compression ratio but low flow rate and controllable total power consumption. When multiple temperature zones operate simultaneously, the high-evaporation-temperature evaporator ensures cooling capacity and energy efficiency, while the low-evaporation-temperature evaporator enhances dehumidification. This improves drying performance while avoiding energy loss, resulting in more significant energy savings.

[0049] Meanwhile, each cylinder in this invention only needs to be adapted to the flow rate and pressure of the corresponding evaporator, without having to take into account the needs of other circuits, which can avoid interference to other circuits caused by load fluctuations of a certain evaporator.

[0050] In addition, this utility model also provides a clothes dryer, which is a heat pump clothes dryer, and the clothes dryer includes the above-mentioned refrigeration system.

[0051] In the dryer, the first evaporator is located in front of the second evaporator, and the circulating air in the dryer first passes through the first evaporator and then through the second evaporator.

[0052] In a heat pump dryer, the first evaporator is positioned before the second evaporator. The circulating air first passes through the first evaporator, where some of the water vapor condenses into water droplets and is discharged, initially reducing air humidity. Then, it passes through the second evaporator for further cooling and dehumidification, making the air even drier. This two-stage evaporator process effectively improves dehumidification efficiency, ensuring the air returning to the drying drum is drier and better removes moisture from the surface of clothes. Simultaneously, the two-stage evaporator allows for more thorough heat exchange between the circulating air and the refrigerant, enabling better heat circulation within the system and contributing to improved overall drying efficiency. Furthermore, the gradual cooling and dehumidification of the circulating air through the two-stage evaporator brings the refrigeration system closer to its ideal operating state, reducing energy consumption by the compressor under high load, lowering overall power consumption, and achieving energy savings.

[0053] It should be noted that, in addition to dryers, the independent suction multi-cylinder compressor and refrigeration system described in this utility model can also be used in other refrigeration systems or heat pump systems that require multi-temperature zone control and multi-evaporation conditions to work together, such as multi-temperature zone refrigerators / freezers, heat pump water heaters, and vehicle multi-temperature zone air conditioners, so as to enable multiple evaporators to work independently under different pressure and flow conditions.

[0054] The embodiments of this application have been described above with reference to the accompanying drawings. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. This application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. A multi-cylinder compressor with independent air intake, characterized in that, The compressor includes a housing, multiple independent intake cylinders, and multiple liquid distributors; The cylinders and the distributors are connected in a one-to-one correspondence. The exhaust ports of the multiple cylinders are all connected to the inner cavity of the housing and share a common exhaust passage; At least two of the cylinders have different volumes.

2. The multi-cylinder compressor with independent air intake according to claim 1, characterized in that, The compressor includes: Two independent intake cylinders, namely the first cylinder (11) and the second cylinder (12); And two dispensers, namely the first dispenser (21) and the second dispenser (22). The first cylinder (11) is connected to the first liquid dispenser (21), and the second cylinder (12) is connected to the second liquid dispenser (22).

3. The multi-cylinder compressor with independent air intake according to claim 2, characterized in that, The volumes of the first cylinder (11) and the second cylinder (12) are V1 and V2, respectively, and the volume ratio of the first cylinder (11) and the second cylinder (12) satisfies: 1 < V1 / V2.

4. The multi-cylinder compressor with independent air intake according to claim 3, characterized in that, The volume ratio of the first cylinder (11) and the second cylinder (12) satisfies: V1 / V2≤1.

3.

5. The multi-cylinder compressor with independent air intake according to claim 2, 3, or 4, characterized in that, The volumes of the first liquid dispenser (21) and the second liquid dispenser (22) are V3 and V4, respectively, and the volume ratio of the first liquid dispenser (21) and the second liquid dispenser (22) satisfies: 1 < V3 / V4.

6. The multi-cylinder compressor with independent air intake according to claim 5, characterized in that, The volume ratio of the first distributor (21) and the second distributor (22) satisfies: V3 / V4≤1.

3.

7. The multi-cylinder compressor with independent air intake according to claim 6, characterized in that, The volume ratio V1 / V2 of the first cylinder (11) and the second cylinder (12) is equal to the volume ratio V3 / V4 of the first distributor (21) and the second distributor (22).

8. A refrigeration system, characterized in that, The refrigeration system includes: a condenser, a first evaporator, a second evaporator, a throttling device, and an independent suction multi-cylinder compressor as described in any one of claims 1 to 7. The first evaporator and the second evaporator are connected in parallel at the air inlet of the independent suction multi-cylinder compressor, and the first evaporator is connected to the first liquid distributor (21), and the second evaporator is connected to the second liquid distributor (22).

9. A clothes dryer, wherein the clothes dryer is a heat pump clothes dryer, characterized in that, The dryer includes the refrigeration system described in claim 8.

10. The clothes dryer according to claim 9, characterized in that, In the dryer, the first evaporator is located in front of the second evaporator, and the circulating air in the dryer first passes through the first evaporator and then through the second evaporator.

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