A parallel compressor and its air conditioner

Abstract

This invention provides a parallel compressor and its air conditioner, comprising an upper cylinder assembly, a middle cylinder assembly, and a lower cylinder assembly sequentially arranged on a crankshaft; the upper cylinder assembly includes an upper cylinder, the middle cylinder assembly includes a middle cylinder and a middle cylinder vane corresponding to the middle cylinder, and the lower cylinder assembly includes a lower cylinder and a lower cylinder vane corresponding to the lower cylinder; the phase angle α between the upper cylinder and the middle cylinder vane is 135° to 170°, and the phase angle θ between the middle cylinder and the lower cylinder vane is -10° to 10°. This invention achieves dual temperature control of the system through a multi-cylinder parallel compressor structure; by setting the phase angles between the three cylinders, the compressor volumetric efficiency can be improved, effectively reducing compressor pulsation, reducing compressor vibration, and improving compressor volumetric efficiency, thereby enhancing energy efficiency.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a parallel compressor and its air conditioner. Background Technology

[0002] With the continuous increase in the growth rate of the VRF (Variable Refrigerant Layout) air conditioning market and the diversification of VRF product forms, most residential applications only require air conditioning in a few rooms. However, VRF systems are designed based on the maximum heat load of the entire house, resulting in most units operating at low loads. Low-load operation leads to low-frequency operation, causing a decline in compressor motor and volumetric efficiency, resulting in prolonged low-efficiency compressor operation and significant deviation from the optimal efficiency point, leading to substantial energy efficiency degradation. Therefore, without sacrificing efficiency during medium and high loads, significantly optimizing low-load operation efficiency and developing independent temperature and humidity control systems has become a widely recognized development direction in the industry.

[0003] The dual-evaporation-temperature compressor enables independent control of two evaporation temperatures, achieving separate cooling and dehumidification processes in air conditioning systems. This effectively improves the overall energy efficiency of the system and can also be used in refrigeration cycle systems requiring temperature and humidity control, household fresh air conditioning, and other applications requiring dual-temperature zones, showing broad application prospects. However, patents CN 210569333U, CN 115030900A, and CN212720358U primarily detail how to implement dual-temperature control within the system, lacking specific optimization solutions for the compressor. Summary of the Invention

[0004] In order to overcome the above-mentioned shortcomings of the prior art, the purpose of this invention is to provide a parallel compressor and its air conditioner to realize a dual-temperature-controlled three-cylinder compressor. By optimizing the structural design of the three cylinders, compressor pulsation can be effectively reduced, compressor vibration can be reduced, compressor volumetric efficiency can be improved, and energy efficiency can be enhanced.

[0005] The technical solution adopted by this invention to solve its technical problem is:

[0006] A parallel compressor includes an upper cylinder assembly, a middle cylinder assembly, and a lower cylinder assembly sequentially arranged on a crankshaft; the upper cylinder assembly includes an upper cylinder, the middle cylinder assembly includes a middle cylinder and a middle cylinder vane corresponding to the middle cylinder, and the lower cylinder assembly includes a lower cylinder and a lower cylinder vane corresponding to the lower cylinder; the phase angle α between the upper cylinder and the middle cylinder vane is 135° to 170°, and the phase angle θ between the middle cylinder and the lower cylinder vane is -10° to 10°.

[0007] As a further improvement of the present invention: the eccentric part of the upper cylinder is the same as the eccentric part of the middle cylinder; the phase angle between the eccentric part of the lower cylinder and the eccentric part of the middle cylinder is 180°.

[0008] As a further improvement of the present invention: the phase angle α between the upper cylinder and the middle cylinder sliding plate is 150° to 170°.

[0009] As a further improvement of the present invention: the phase angle α between the upper cylinder and the middle cylinder sliding plate is 165°.

[0010] As a further improvement of the present invention: the phase angle θ between the middle cylinder and the lower cylinder sliding plate is 0°.

[0011] As a further improvement of the present invention: the upper cylinder, the middle cylinder and the lower cylinder are each connected to an independent liquid distributor, and the independent liquid distributors are distributed along the circumference of the compressor housing.

[0012] As a further improvement of the present invention: the upper cylinder assembly further includes an upper cylinder muffler, an upper cylinder flange, an upper cylinder roller and an upper cylinder partition plate arranged sequentially along the crankshaft; the upper cylinder, upper cylinder slide and upper cylinder spring are arranged outside the upper cylinder roller.

[0013] As a further improvement of the present invention: the cylinder assembly further includes a cylinder partition and a cylinder roller arranged sequentially along the crankshaft; the cylinder, cylinder slide, and cylinder spring are arranged outside the cylinder roller.

[0014] As a further improvement of the present invention: the lower cylinder assembly further includes a lower cylinder partition, a lower cylinder roller, a lower cylinder flange and a lower cylinder muffler arranged sequentially along the crankshaft; the lower cylinder, lower cylinder slide and lower cylinder spring are arranged outside the lower cylinder roller.

[0015] An air conditioner, wherein a parallel compressor as described in any of the preceding claims is used.

[0016] Compared with the prior art, the beneficial effects of the present invention are:

[0017] This invention enables dual temperature control of the system through a multi-cylinder parallel compressor structure; by setting the phase angle between the three cylinders, the volumetric efficiency of the compressor can be improved, effectively reducing compressor pulsation, reducing compressor vibration, and improving compressor volumetric efficiency, thereby improving energy efficiency. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the pump body structure of the present invention.

[0019] Figure 2 This is a schematic diagram of the phase angle of the present invention.

[0020] Figure 3 This is a schematic diagram showing the front and rear centroid positions of the present invention.

[0021] Figure 4 This is the front view of the present invention.

[0022] Figure 5 This is a schematic diagram of the lower cylinder position according to the present invention.

[0023] Figure 6 This is a diagram showing the changes in the pressure test experiment of the present invention.

[0024] Figure 7 This is a table of experimental data for the vibration test of the dispenser of the present invention.

[0025] Figure 8 This is a table of experimental data for volumetric efficiency testing of the present invention.

[0026] Figure 9 This is the standard for the compressor operating condition test experimental data of the present invention.

[0027] Figure 10 This is a table of experimental data from the intermediate cooling test of the system of the present invention.

[0028] Figure 11 This is a schematic diagram of the pump body structure in the prior art.

[0029] Figure 12 This is a diagram of the existing technology.

[0030] Explanation of reference numerals in the attached figures:

[0031] 1-Crankshaft; 2-Upper cylinder assembly; 21-Upper cylinder; 22-Upper cylinder muffler; 23-Upper cylinder flange; 24-Upper cylinder roller; 25-Upper cylinder partition; 26-Upper cylinder vane; 27-Upper cylinder spring; 3-Intermediate cylinder assembly; 31-Intermediate cylinder; 32-Intermediate cylinder vane; 33-Intermediate cylinder partition; 34-Intermediate cylinder roller; 35-Intermediate cylinder spring; 4-Lower cylinder assembly; 41-Lower cylinder; 42-Lower cylinder vane; 43-Lower cylinder partition; 44-Lower cylinder roller; 45-Lower cylinder flange; 46-Lower cylinder muffler; 47-Lower cylinder spring; 5-Independent distributor; 6-Compressor; 100-Upper cylinder mechanism; 101 - Silencer; 102 - Upper flange; 103 - Upper cylinder structure; 104 - Upper roller; 105 - Upper vane; 106 - Upper spring; 107 - Upper partition; 200 - Middle cylinder mechanism; 201 - Middle partition; 202 - Middle cylinder structure; 203 - Middle roller; 204 - Middle vane; 205 - Middle spring; 300 - Lower cylinder mechanism; 301 - Lower partition; 302 - Lower cylinder structure; 303 - Lower roller; 304 - Lower vane; 305 - Variable displacement assembly; 306 - Lower flange; 307 - Lower flange cover; 400 - Crankshaft; 500 - Whole machine distributor; 600 - Existing compressor. Detailed Implementation

[0032] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below in conjunction with specific embodiments and corresponding drawings. Obviously, the described embodiments are only a part of the embodiments of this invention, and not all of them. Based on the embodiments of this invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this invention. The invention will now be further described in conjunction with the accompanying drawings, prior art, and embodiments:

[0033] Existing technology:

[0034] As a device for regulating environmental comfort, air conditioning systems have evolved beyond simple temperature control to offer more diverse functions, meeting people's ever-increasing demands for comfortable living environments. Currently, the main dehumidification method in air conditioning systems is cooling dehumidification. This method is suitable for high-temperature environments. However, in situations where the temperature is not high but the relative humidity is high, conventional household inverter air conditioners struggle to achieve both temperature control and dehumidification. Therefore, in cold and humid weather, conventional household inverter air conditioners cannot meet the comfort requirements for dehumidification through cooling dehumidification and are usually left idle.

[0035] The existing three-cylinder compressor is a one-cylinder variable displacement, two-stage enthalpy-increasing structure. Its structure is simply an addition of a variable displacement cylinder to the two-cylinder compressor with a two-stage enthalpy-increasing structure to achieve the functions of a two-cylinder or three-cylinder compressor (it cannot achieve the functions of a single cylinder). This results in high compressor costs and serious vibration problems. When operating at low temperature and low frequency, its low-load performance advantage is not significant, resulting in insufficient APF (intermediate cooling factor) and poor heating performance. In addition, when the compressor and air conditioning system are running, cooling and dehumidification are completed in one system, resulting in low heat exchange efficiency of the evaporator. As a result, the air conditioning system cannot meet the cooling, dehumidification and heating needs of areas north of the Yangtze River.

[0036] The existing three-cylinder engine structure is shown in the attached figure. Figure 11-12 As shown, it consists of an upper cylinder mechanism 100, a middle cylinder mechanism 200, and a lower cylinder mechanism 300. The upper cylinder mechanism 100 is composed of a crankshaft 400, a muffler 101, an upper flange 102, an upper cylinder structure 103, an upper roller 104, an upper sliding vane 105, an upper spring 106, and an upper partition 107. The middle cylinder mechanism 200 is composed of a crankshaft 400, a middle partition 201, a middle cylinder structure 202, a middle roller 203, a middle sliding vane 204, and a middle spring 205. The lower cylinder mechanism 300 is composed of a crankshaft 400, a lower partition 301, a lower cylinder structure 302, a lower roller 303, a lower sliding vane 304, a variable displacement assembly 305, a lower flange 306, and a lower flange cover plate 307.

[0037] In existing technology, the sliding vane follows the roller movement, isolating the intake and exhaust chambers. The lower cylinder mechanism 300 is a variable displacement cylinder; by controlling the pin of the variable displacement component, the sliding vane is disengaged from the roller, achieving variable volume. The middle cylinder structure 202 and the lower cylinder structure 302 share a distributor, while the upper cylinder structure 103 has an independent distributor 5. The upper and middle sliding vane slots are in the same position, i.e., the phase angle α between the upper cylinder structure 103 and the middle sliding vane 204 is 0°, and the phase angle θ between the middle cylinder structure 202 and the lower sliding vane 304 is 0°. The intake port angles of the upper cylinder structure 103, middle cylinder structure 202, and lower cylinder structure 402 are the same as the sliding vane angles of each cylinder, meaning the distributor outlet positions are on the same straight line. The entire machine has two distributors 500: the middle cylinder structure 202 and the lower cylinder structure 402 share the same distributor 500, while the upper cylinder structure 103 has an independent distributor. According to the existing compressor 600 layout, the compressor's center of gravity is biased towards the distributor 500 end, resulting in large vibrations. At the same time, none of the three-cylinder structures can independently intake air, resulting in poor system efficiency.

[0038] Example 1:

[0039] This embodiment provides the following: Figure 1-5 The parallel compressor 6 shown includes an upper cylinder assembly 2, an intermediate cylinder assembly 3, and a lower cylinder assembly 4 sequentially arranged on a crankshaft 1. The upper cylinder assembly 2 includes an upper cylinder 21, the intermediate cylinder assembly 3 includes an intermediate cylinder 31 and an intermediate cylinder vane 32 corresponding to the intermediate cylinder 31, and the lower cylinder assembly 4 includes a lower cylinder 41 and a lower cylinder vane 42 corresponding to the lower cylinder 41. The phase angle α between the upper cylinder 21 and the intermediate cylinder vane 32 is 135° to 170°, and the phase angle θ between the intermediate cylinder 31 and the lower cylinder vane 42 is -10° to 10°.

[0040] In this embodiment, in order to solve the problems caused by the three-cylinder structure in the prior art, the phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is set to 135° to 170°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is set to -10° to 10°. By adjusting the phase angle, the center of mass can be shifted inward, reducing compressor pulsation and vibration; improving volumetric efficiency and system energy efficiency.

[0041] Furthermore, after optimizing the phase angle, to avoid machining difficulties caused by the phase angle of crankshaft 1, the eccentric part of crankshaft 1 is set as shown in the attached figure. Figure 1 As shown, the eccentric portion of the upper cylinder 21 is the same as the eccentric portion of the middle cylinder 31; the phase angle between the eccentric portion of the lower cylinder 41 and the eccentric portion of the middle cylinder 31 is 180°. Based on the above configuration, structural optimization enables the center of gravity to shift inward, reducing the vibration of the dispenser at its 60Hz operating frequency.

[0042] Example 2:

[0043] This embodiment provides the following: Figure 1-5The parallel compressor 6 shown includes an upper cylinder assembly 2, an intermediate cylinder assembly 3, and a lower cylinder assembly 4 sequentially arranged on a crankshaft 1. The upper cylinder assembly 2 includes an upper cylinder 21, the intermediate cylinder assembly 3 includes an intermediate cylinder 31 and an intermediate cylinder vane 32 corresponding to the intermediate cylinder 31, and the lower cylinder assembly 4 includes a lower cylinder 41 and a lower cylinder vane 42 corresponding to the lower cylinder 41. The phase angle α between the upper cylinder 21 and the intermediate cylinder vane 32 is 150° to 170°, and the phase angle θ between the intermediate cylinder 31 and the lower cylinder vane 42 is -10° to 10°.

[0044] In this embodiment, based on Embodiment 1, the phase angles of the upper cylinder 21 and the middle cylinder vane 32 are further optimized. The phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is set to 150° to 170°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is set to -10° to 10°. This embodiment further optimizes the range of the phase angle α. By further optimizing the phase angle, the center of mass is further shifted inward, further reducing the pulsation of the compressor 6 and further reducing the vibration of the compressor 6; further improving volumetric efficiency and system energy efficiency. In addition, based on this, the crankshaft 1 is also set such that the eccentric part of the upper cylinder 21 is the same as the eccentric part of the middle cylinder 31; the phase angle between the eccentric part of the lower cylinder 41 and the eccentric part of the middle cylinder 31 is 180°. The scheme described in this embodiment can achieve an inward shift of the center of mass of more than 20%, and the vibration of the 60Hz operating frequency of the distributor can be reduced by more than 7%.

[0045] Example 3:

[0046] This embodiment provides the following: Figure 1-5 The parallel compressor 6 shown includes an upper cylinder assembly 2, an intermediate cylinder assembly 3, and a lower cylinder assembly 4 sequentially arranged on a crankshaft 1. The upper cylinder assembly 2 includes an upper cylinder 21, the intermediate cylinder assembly 3 includes an intermediate cylinder 31 and an intermediate cylinder vane 32 corresponding to the intermediate cylinder 31, and the lower cylinder assembly 4 includes a lower cylinder 41 and a lower cylinder vane 42 corresponding to the lower cylinder 41. The phase angle α between the upper cylinder 21 and the intermediate cylinder vane 32 is 165°, and the phase angle θ between the intermediate cylinder 31 and the lower cylinder vane 42 is 0°.

[0047] In this embodiment, based on Embodiment 1, the phase angles of the upper cylinder 21 and the middle cylinder vane 32 are further optimized. The phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is set to 165°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is set to 0°. This embodiment is based on Embodiment 2. When the phase angle α is set to 165°, the pressure fluctuation in the upper cylinder cavity is minimized, the volumetric efficiency of the compressor 6 increases, the energy efficiency of the compressor 6 is improved, and thus the system energy efficiency is improved. Similarly, by fixing the phase angle α to 165°, the inward displacement distance of the center of mass can be optimized, the pressure fluctuation in the upper cylinder cavity is minimized, the pulsation of the compressor 6 is further reduced, the vibration of the compressor 6 is reduced, and the volumetric efficiency and system energy efficiency are further improved. In addition, based on this, the crankshaft 1 is also set such that the eccentric part of the upper cylinder 21 is the same as the eccentric part of the middle cylinder 31; the phase angle between the eccentric part of the lower cylinder 41 and the eccentric part of the middle cylinder 31 is 180°. The solution described in this embodiment can achieve the optimal distance by shifting the center of gravity inward, and reduce the vibration of the dispenser at the 60Hz operating frequency to the best effect.

[0048] Example 4:

[0049] This embodiment provides the following: Figure 1-5 The parallel compressor shown includes an upper cylinder assembly 2, a middle cylinder assembly 3, and a lower cylinder assembly 4 sequentially arranged on a crankshaft 1. The upper cylinder assembly 2 includes an upper cylinder 21, the middle cylinder assembly 3 includes a middle cylinder 31 and a middle cylinder vane 32 corresponding to the middle cylinder 31, and the lower cylinder assembly 4 includes a lower cylinder 41 and a lower cylinder vane 42 corresponding to the lower cylinder 41. The phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is 165°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is 0°. In this embodiment, the phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is set to 165°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is set to 0°. Multiple experiments have shown that when the phase angle α is 165°, the pressure fluctuation in the upper cylinder cavity is minimal, the volumetric efficiency of the compressor 6 increases, the energy efficiency of the compressor 6 is improved, and thus the overall system energy efficiency is improved. Furthermore, based on this, the crankshaft 1 is also configured such that the eccentric portion of the upper cylinder 21 is the same as the eccentric portion of the middle cylinder 31; the phase angle between the eccentric portion of the lower cylinder 41 and the eccentric portion of the middle cylinder 31 is 180°. In this embodiment, the scheme can achieve optimal center of gravity shift to the inner distance, and the vibration of the distributor at its 60Hz operating frequency can be reduced to the best effect.

[0050] Furthermore, in this embodiment, based on Embodiment 3, in order to further reduce the pulsation of compressor 6 and improve the volumetric efficiency of operation, as shown in the attached... Figure 3-5As shown, the upper cylinder 21, the middle cylinder 31, and the lower cylinder 41 are all connected to independent distributors 5, which are distributed along the circumference of the compressor 6 housing. Thus, the compressor 6 has three independent distributors: one for the upper cylinder 21, one for the middle cylinder 31, and one for the lower cylinder 41. This allows each cylinder to have independent intake and exhaust, further reducing compressor pulsation and improving volumetric efficiency. Simultaneously, each independent distributor 5 is individually connected to the system, and its layout is distributed around the compressor 6 housing, as shown in the attached diagram. Figure 3 As shown, the center of mass of the traditional three cylinders is B, and the distance between them and the center of the compressor 6 is b. In this embodiment, the center of mass of the three cylinders is C, and the distance between them is c. It can be seen that the position of the three cylinders in this embodiment is closer to the center position, which can further reduce the vibration of the compressor 6.

[0051] Example 5:

[0052] This embodiment provides the following: Figure 1-5 A parallel compressor 6 is shown, comprising an upper cylinder assembly 2, an intermediate cylinder assembly 3, and a lower cylinder assembly 4 sequentially arranged on a crankshaft 1. The upper cylinder assembly 2 includes an upper cylinder 21, the intermediate cylinder assembly 3 includes an intermediate cylinder 31 and an intermediate cylinder vane 32 corresponding to the intermediate cylinder 31, and the lower cylinder assembly 4 includes a lower cylinder 41 and a lower cylinder vane 42 corresponding to the lower cylinder 41. The upper cylinder assembly 2 further includes an upper cylinder muffler 22, an upper cylinder flange 23, an upper cylinder roller 24, and an upper cylinder baffle 25 sequentially arranged along the crankshaft 1; the upper cylinder 21, the upper cylinder vane 26, and the upper cylinder spring 27 are disposed outside the upper cylinder roller 24. The intermediate cylinder assembly 3 further includes an intermediate cylinder baffle 33 and an intermediate cylinder roller 34 sequentially arranged along the crankshaft 1; the intermediate cylinder 31, the intermediate cylinder vane 32, and the intermediate cylinder spring 35 are disposed outside the intermediate cylinder roller 34. The lower cylinder assembly 4 further includes a lower cylinder partition 43, a lower cylinder roller 44, a lower cylinder flange 45, and a lower cylinder muffler 46 arranged sequentially along the crankshaft 1; the lower cylinder 41, a lower cylinder slide 42, and a lower cylinder spring 47 are arranged outside the lower cylinder roller 44.

[0053] In this embodiment, the phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is 165°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is 0°. At a phase angle of 165°, the pressure fluctuation in the upper cylinder cavity is minimal, increasing the volumetric efficiency of the compressor 6 and improving its energy efficiency, thereby enhancing the overall system energy efficiency. The entire unit has three distributors: the upper cylinder 21, the middle cylinder 31, and the lower cylinder 41 each have an independent distributor 5. The three cylinders have independent intake and exhaust, resulting in low pulsation and high volumetric efficiency in the compressor 6. Each distributor is individually connected to the system, and the distributor layout is distributed along the circumference of the casing, with the center of mass approaching the center position, minimizing compressor vibration.

[0054] As attached Figure 5 As shown, the position of the distributor connected to its lower cylinder can be as shown in the attached figure. Figure 5 The position in the middle has been adjusted.

[0055] Example 6:

[0056] This embodiment provides the following: Figure 1-5 The parallel compressor 6 shown includes an upper cylinder assembly 2, an intermediate cylinder assembly 3, and a lower cylinder assembly 4 sequentially arranged on a crankshaft 1. The upper cylinder assembly 2 includes an upper cylinder 21, the intermediate cylinder assembly 3 includes an intermediate cylinder 31 and an intermediate cylinder vane 32 corresponding to the intermediate cylinder 31, and the lower cylinder assembly 4 includes a lower cylinder 41 and a lower cylinder vane 42 corresponding to the lower cylinder 41. The phase angle α between the upper cylinder 21 and the intermediate cylinder vane 32 is 170°, and the phase angle θ between the intermediate cylinder 31 and the lower cylinder vane 42 is 0°.

[0057] In this embodiment, to address the problems caused by the existing three-cylinder structure, the phase angle α between the upper cylinder 21 and the middle cylinder vane 32 is set to 170°, and the phase angle θ between the middle cylinder 31 and the lower cylinder vane 42 is set to 0°. This phase angle allows the center of mass to shift inward, reducing compressor pulsation and vibration; increasing volumetric efficiency to 0.9 and the intermediate system pressure to 0.955. After optimizing the phase angle, to avoid machining difficulties caused by the phase angle, the eccentric portion of the crankshaft 1 is configured as shown in the attached figure. Figure 1 As shown, the eccentric portion of the upper cylinder 21 is the same as the eccentric portion of the middle cylinder 31; the phase angle between the eccentric portion of the lower cylinder 41 and the eccentric portion of the middle cylinder 31 is 180°. Based on the above configuration, structural optimization enables the center of gravity to shift inward, reducing the vibration of the dispenser at its 60Hz operating frequency.

[0058] Example 7:

[0059] This embodiment provides an air conditioner, wherein a parallel compressor 6 as described in any one of embodiments one to six above is used.

[0060] Experimental data:

[0061] Set the phase angle between the upper cylinder and the middle cylinder vanes to α, and set the phase angle between the middle cylinder and the lower cylinder vanes to θ.

[0062] 1. Pressure Test: The pressure fluctuation of the compressor cavity under different three-cylinder configurations (α, θ) is tested. Four sets of data are provided: configuration three-cylinder (135°, 0°); configuration three-cylinder (150°, 0°); configuration three-cylinder (165°, 0°); and configuration three-cylinder (180°, 0°). The pressure fluctuation data variation graphs are attached. Figure 6 As shown.

[0063] 2. Dispenser Vibration Test: The vibration changes of dispensers with different three cylinders (α, θ) were tested. Three sets of data were provided: Scheme 3 cylinder (135°, 0°); Scheme 3 cylinder (150°, 0°); and Scheme 3 cylinder (165°, 0°). A standard three-cylinder (0°, 0°) was provided as a control group. The measured vibration changes of the dispensers are shown in the attached figure. Figure 7 As shown.

[0064] 3. Volumetric Efficiency Test: The volumetric efficiency changes of different three-cylinder configurations (α, θ) are tested. Five sets of data are provided: Configuration 3 (140°, 0°); Configuration 3 (150°, 0°); Configuration 3 (160°, 0°); Configuration 3 (165°, 0°); and Configuration 3 (170°, 0°). A conventional three-cylinder configuration (0°, 0°) is provided as a control group. The volumetric efficiency changes are shown in the attached figure. Figure 8 As shown.

[0065] 4. Compressor Operating Condition Test: The operating conditions of a conventional three-cylinder compressor (180°, 0°) and a proposed three-cylinder compressor (165°, 0°) were tested for comparison. The results are attached. Figure 9 As shown.

[0066] 5. System Intermediate Cooling Test: The intermediate cooling conditions of the conventional three-cylinder (180°, 0°) and the proposed three-cylinder (165°, 0°) systems were tested for comparison. The results are attached. Figure 10 As shown.

[0067] 6. Conclusion:

[0068] Test 1 shows that as α increases, the pressure that the compressor can withstand also increases. Among them, the pressure fluctuation of cylinder 3 (165°, 0°) is the smallest.

[0069] Test 2 shows that the distributor vibration frequency of α under the conventional three-cylinder setting is 5.3. Compared with 5.3 as the baseline, it was found that the distributor vibration frequency of Scheme 3 was the lowest at (150°, 0°) at 4.92, which is 7.2% lower than the baseline. The second lowest was at (165°, 0°) at 4.95, which is 6.6% lower than the baseline. Finally, the distributor vibration frequency of Scheme 3 was 5 at (135°, 0°), which is 5.7% lower than the baseline.

[0070] Test 3 shows that the volumetric efficiency of the conventional three-cylinder (0°, 0°) is 0.88, and its system intermediate pressure is 0.91. In contrast, the proposed three-cylinder (α between 140° and 170°) shows that as the α angle increases, its volumetric efficiency also increases, and its ability to withstand system intermediate pressure also improves, reaching peak values ​​at both (160°, 0°) and (165°, 0°) angles.

[0071] Test 4 shows that compared with the conventional three-cylinder (180°, 0°), the cooling capacity of the proposed three-cylinder (165°, 0°) is increased by 32.1W, and the power consumption is reduced by 8.7W. Overall, the single-unit performance is improved from 6.278 to 6.37, an improvement of 1.4%.

[0072] Test 5 shows that compared with the conventional three-cylinder (180°, 0°), the cooling capacity of the proposed three-cylinder (165°, 0°) is increased by 82.6, and its power is increased by 2.3. Overall, the system energy efficiency is improved from 8.336 to 8.531, an improvement of 2.3%.

[0073] In summary, as α increases, the pressure fluctuations of the compressor tend to stabilize, with minimal fluctuations at 165°. Simultaneously, with increasing α, the distributor vibration frequency, volumetric efficiency, and intermediate system pressure all improve. Furthermore, when α reaches 165°, the performance of the compressor and intermediate system cooling conditions is improved by 1.4% and 2.3% respectively compared to a conventional three-cylinder compressor (180°, 0°). Therefore, adjusting α can effectively reduce compressor pulsation, decrease compressor vibration, improve compressor volumetric efficiency, and enhance energy efficiency.

[0074] The main functions of this invention are: to provide an optimized solution for a dual-temperature-controlled three-cylinder parallel compressor, by setting the phase angles of the upper, middle, and lower cylinders. This phase angle shifts the center of mass inward, reducing compressor pulsation and vibration, improving volumetric efficiency, and enhancing system energy efficiency. Furthermore, the entire compressor's distributor is divided into three independent distributors, ensuring each cylinder has independent intake and exhaust, resulting in minimal compressor pulsation and high volumetric efficiency. Each distributor is individually connected to the system, and its layout is arranged along the circumference of the casing, bringing the center of mass closer to the center and minimizing compressor vibration.

[0075] In the description of this invention, it should be noted that the terms "upper," "lower," etc., indicating orientation or positional relationships are based on the orientation or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. In the description of this invention, it should be noted that unless otherwise explicitly specified and limited, the term "connection" should be interpreted broadly. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a connection within two elements. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances. Furthermore, the technical features involved in the different embodiments of the invention described below can be combined with each other as long as they do not conflict with each other. Furthermore, the terms “comprising” and “having”, and any variations thereof, are intended to cover non-exclusive inclusion, such that a process, method, system, product, or apparatus that includes a series of steps or units is not necessarily limited to those steps or units that are explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to such process, method, product, or apparatus.

[0076] In summary, after reading this invention document, those skilled in the art can make various other corresponding modifications to the technical solutions and concepts based on this invention without creative mental effort, and all of these modifications fall within the scope of protection of this invention.

Claims

1. A parallel compressor, characterized in that, The compressor comprises an upper cylinder assembly, a middle cylinder assembly, and a lower cylinder assembly sequentially mounted on a crankshaft. The upper cylinder assembly includes an upper cylinder, the middle cylinder assembly includes a middle cylinder and a middle cylinder slide corresponding to the middle cylinder, and the lower cylinder assembly includes a lower cylinder and a lower cylinder slide corresponding to the lower cylinder. The phase angle α between the upper cylinder and the middle cylinder slide is 135°~170°, the phase angle θ between the middle cylinder and the lower cylinder slide is -10°~10°, the eccentric portion of the upper cylinder is the same as the eccentric portion of the middle cylinder, and the phase angle between the eccentric portion of the lower cylinder and the eccentric portion of the middle cylinder is 180°. Each of the upper cylinder, the middle cylinder, and the lower cylinder is connected to an independent distributor, which is distributed along the circumference of the compressor housing.

2. A parallel compressor according to claim 1, characterized in that, The phase angle α between the upper cylinder and the middle cylinder sliding plate is 150°~170°.

3. A parallel compressor according to claim 2, characterized in that, The phase angle α between the upper cylinder and the middle cylinder sliding plate is 165°.

4. A parallel compressor according to claim 1, characterized in that, The phase angle θ between the middle cylinder and the lower cylinder sliding plate is 0°.

5. A parallel compressor according to claim 1, characterized in that, The upper cylinder assembly also includes an upper cylinder muffler, an upper cylinder flange, an upper cylinder roller, and an upper cylinder partition plate arranged sequentially along the crankshaft; the upper cylinder, upper cylinder slide, and upper cylinder spring are arranged outside the upper cylinder roller.

6. A parallel compressor according to claim 1, characterized in that, The cylinder assembly further includes a cylinder partition and a cylinder roller arranged sequentially along the crankshaft; the cylinder, cylinder slide, and cylinder spring are arranged outside the cylinder roller.

7. A parallel compressor according to claim 1, characterized in that, The lower cylinder assembly also includes a lower cylinder partition, a lower cylinder roller, a lower cylinder flange, and a lower cylinder muffler arranged sequentially along the crankshaft; the lower cylinder, lower cylinder slide, and lower cylinder spring are arranged outside the lower cylinder roller.

8. An air conditioner, characterized in that, The application uses a parallel compressor as described in any one of claims 1-7.

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