Compressor and air conditioner
By optimizing the assembly structure of the compressor housing, cylinder, motor, and crankshaft, the problems of vibration, noise, and high power consumption under propane refrigerant were solved, achieving stable motor assembly, reduced noise, and improved energy efficiency.
Patent Information
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- GUANGDONG MEIZHI PRECISION MFG
- Filing Date
- 2025-12-19
- Publication Date
- 2026-07-23
AI Technical Summary
In existing technologies, replacing R32 refrigerant with propane refrigerant results in increased compressor vibration and noise, higher power consumption, and decreased performance.
By optimizing the fit structure of the compressor housing, cylinder, motor, and crankshaft, ensuring ø2≥ø1, 0.6≥ø3/ø1≥0.5, and 40≥ø3/ø4≥30, an interference fit is achieved between the motor and the housing. The ratio of the cylinder's inner diameter to the housing's inner diameter is between 0.5 and 0.6, and the ratio of the crankshaft's inner diameter to the motor's inner diameter is between 30 and 40, thereby enhancing structural rigidity and reducing friction.
It effectively reduces compressor operating noise and vibration, improves energy efficiency and performance, ensures stable motor assembly, and reduces refrigerant leakage.
Smart Images
Figure CN2025143766_23072026_PF_FP_ABST
Abstract
Description
Compressors and air conditioners
[0001] This application claims priority to Chinese Patent Application No. 202510065536.X, filed on January 15, 2025, entitled "Compressor and Air Conditioner", the entire contents of which are incorporated herein by reference. Technical Field
[0002] This application relates to the field of compressor technology, and more specifically, to a compressor and an air conditioner. Background Technology
[0003] In related technologies, air conditioner compressors use R32 refrigerant as the refrigerant. The type of refrigerant is related to the fitting dimensions of the compressor's casing, cylinder, motor, and crankshaft. Replacing the refrigerant with propane results in increased compressor vibration and noise, higher power consumption, and significantly reduced compressor performance. Technical solutions
[0004] This application aims to address at least one of the technical problems existing in the prior art or related technologies.
[0005] Therefore, the first aspect of this application proposes a compressor.
[0006] The second aspect of this application proposes an air conditioner.
[0007] In view of the above, the first aspect of this application provides a compressor, comprising: a housing; a cylinder disposed within the housing; a motor disposed within the housing, the motor being spaced apart on one side of the cylinder; a crankshaft disposed within the housing, and the crankshaft passing through the motor and the cylinder; the maximum inner diameter of the housing is ø1, the outer diameter of the motor is ø2, the inner diameter of the cylinder is ø3, and the outer diameter of the portion of the crankshaft located within the motor is ø4; wherein, ø2≥ø1, 0.6≥ø3 / ø1≥0.5, 40≥ø3 / ø4≥30.
[0008] The compressor provided in this application includes a housing, a cylinder, a motor, and a crankshaft.
[0009] The cylinder, motor, and crankshaft are all housed within the housing. The motor is spaced apart on one side of the cylinder, and the crankshaft passes through both the motor and the cylinder. The housing serves as the mounting carrier for the cylinder, motor, and crankshaft, and is responsible for mounting and securing them.
[0010] The compressor in this application uses propane as the refrigerant, and the fit structure of the housing, cylinder, motor, and crankshaft is defined based on the propane refrigerant. The maximum inner diameter of the housing is denoted as ø1, the outer diameter of the motor as ø2, the inner diameter of the cylinder as ø3, and the outer diameter of the portion of the crankshaft located inside the motor as ø4. The relationships between ø1, ø2, ø3, and ø4 are defined to satisfy ø2 ≥ ø1, 0.6 ≥ ø3 / ø1 ≥ 0.5, and 40 ≥ ø3 / ø4 ≥ 30.
[0011] The motor is located inside the housing. The outer diameter ø2 of the motor is greater than or equal to the maximum value of the inner diameter ø1 of the housing. That is, the motor and the housing are interference-fitted, which allows the motor to be stably assembled inside the housing and prevents the motor from shifting relative to the housing.
[0012] The cylinder is located inside the housing. The ratio of the cylinder's inner diameter ø3 to the maximum inner diameter of the housing ø1 is greater than or equal to 0.5 and less than or equal to 0.6. This design balances the cylinder's structural rigidity with the compressor's energy efficiency and operating noise. With a fixed cylinder cavity volume, a larger inner diameter ø3 allows for a corresponding reduction in the cylinder's axial height. This helps reduce refrigerant leakage, improves compressor energy efficiency, and lowers compressor operating noise.
[0013] Therefore, when ø3 / ø1 < 0.5, the axial height of the cylinder is relatively high, which increases refrigerant leakage, thereby reducing the compressor's energy efficiency and increasing its operating noise. When ø3 / ø1 > 0.6, the cylinder wall thickness is relatively thin, resulting in insufficient structural strength and rigidity. The cylinder is prone to deformation during operation, which reduces the compressor's energy efficiency and affects its performance.
[0014] The crankshaft passes through the motor. The outer diameter of the portion of the crankshaft located inside the motor is denoted as ø4. That is, the outer diameter of the portion of the crankshaft surrounding the motor is ø4. The inner diameter ø3 of the cylinder and the outer diameter ø4 of the crankshaft located inside the motor satisfy the following condition: 40 ≥ ø3 / ø4 ≥ 30. This configuration ensures that the crankshaft effectively drives the piston movement of the cylinder while reducing friction between the crankshaft and motor bearings, thus guaranteeing the compressor's performance.
[0015] If ø3 / ø4 < 30, then the outer diameter of the crankshaft portion inside the motor is too large. This will increase the friction between the crankshaft and the motor bearings, reducing performance.
[0016] If ø3 / ø4 > 40, then the crankshaft's structural rigidity is insufficient. When the compressor is working, this will increase the rotor deflection of the motor and increase electromagnetic noise.
[0017] Therefore, it can be seen that, based on the use of propane refrigerant in the compressor, by reasonably setting the matching structure of the housing, cylinder, motor and crankshaft, the stability and reliability of the assembly of the housing, cylinder, motor and crankshaft can be guaranteed, while also improving the energy efficiency of the compressor, reducing the operating noise of the compressor, and improving the performance of the compressor.
[0018] The compressor described above according to this application may also have the following additional technical features:
[0019] In some embodiments, optionally, ø1, ø2, ø3 and ø4 satisfy: ø1+0.1mm>ø2≥ø1, 0.54≥ø3 / ø1≥0.51, 37.2≥ø3 / ø4≥34.5.
[0020] In this embodiment, the matching structure of ø1, ø2, ø3 and ø4 is further defined such that ø1, ø2, ø3 and ø4 satisfy: ø1+0.1mm>ø2≥ø1, 0.54≥ø3 / ø1≥0.51, 37.2≥ø3 / ø4≥34.5.
[0021] This setup, based on the use of propane refrigerant in the compressor, ensures the stability and reliability of the housing, cylinder, motor, and crankshaft assembly by rationally configuring the matching structure of the housing, cylinder, motor, and crankshaft. At the same time, it helps to improve the energy efficiency of the compressor, reduce the operating noise of the compressor, and improve the performance of the compressor.
[0022] If ø2≥ø1+0.1mm, then the interference fit between the motor and the housing is too large, which will increase the vibration and noise of the compressor during operation.
[0023] If ø2 < ø1, the gap between the motor and the housing is too large, and the motor is prone to displacement relative to the housing, which cannot guarantee the assembly position of the motor and affects the normal operation of the compressor.
[0024] For example, ø2=ø1+0.02mm, ø2=ø1+0.04mm, ø2=ø1+0.05mm, ø2=ø1+0.06mm and ø2=ø1+0.08mm, etc., will not be listed here one by one.
[0025] If ø3 / ø1 < 0.51, then the axial height of the cylinder is relatively high, which will increase the refrigerant leakage, thereby reducing the compressor's energy efficiency and increasing the compressor's operating noise.
[0026] If ø3 / ø1 > 0.54, then the cylinder wall thickness is too thin, the cylinder structure strength and rigidity are insufficient, the cylinder is prone to deformation during operation, which will reduce the energy efficiency of the compressor and affect the performance of the compressor.
[0027] If ø3 / ø4 < 34.5, then the outer diameter of the crankshaft portion inside the motor is too large. This will increase the friction between the crankshaft and the motor bearings, reducing performance.
[0028] If ø3 / ø4 > 37.2, then the crankshaft's structural stiffness is insufficient. When the compressor is working, this will increase the rotor deflection of the motor and increase electromagnetic noise.
[0029] In some embodiments, the axial height of the cylinder may optionally be H, where H < ø3.
[0030] In this embodiment, the structure of the cylinder is defined.
[0031] The axial height of the cylinder is H, and the inner diameter of the cylinder is ø3. H and ø3 satisfy H < ø3. This setting takes into account both the structural rigidity of the cylinder and the leakage of the cylinder, which is beneficial to improving the energy efficiency of the compressor and reducing the operating noise of the compressor.
[0032] If H≥ø3, then the axial height of the cylinder is too large, which will increase the refrigerant leakage, reduce the compressor's energy efficiency, and increase the compressor's operating noise.
[0033] In some embodiments, H and ø3 may optionally satisfy: 0.78 ≥ H / ø3 ≥ 0.512.
[0034] In this embodiment, the relationship between H and ø3 is defined such that 0.78 ≥ H / ø3 ≥ 0.512.
[0035] If H / ø3 < 0.512, the cylinder wall thickness is relatively thin, which will reduce the structural rigidity and strength of the cylinder. When the compressor is working, the deformation of the cylinder will increase, which will reduce the energy efficiency of the compressor and affect its performance.
[0036] If H / ø3 > 0.78, then the axial height of the cylinder is too large, which will increase the leakage, reduce the energy efficiency of the compressor, and increase the operating noise of the compressor.
[0037] Examples include H / ø3=0.55, H / ø3=0.58, H / ø3=0.6, H / ø3=0.62, H / ø3=0.65, H / ø3=0.7, and H / ø3=0.75, etc., which will not be listed here one by one.
[0038] In some embodiments, the cylinder is optionally provided with a slide groove, a mounting hole, a slide, and an elastic element. The slide is slidably disposed in the slide groove, the elastic element is disposed in the mounting hole, and one end of the elastic element abuts against the slide. The cylinder is cross-sectioned along a direction perpendicular to the axis of the motor. In the cross-section, the length of the end of the elastic element that abuts against the slide in the first direction is ø5. Wherein, 0.3≥ø5 / ø3≥0.2.
[0039] In this embodiment, the structure of the cylinder is defined.
[0040] The cylinder is equipped with a sliding vane groove, mounting hole, sliding vane, and elastic element.
[0041] The slider is slidably disposed in the slider groove.
[0042] The elastic element is located in the mounting hole, and one end of the elastic element abuts against the slider.
[0043] A cross-section of the cylinder is taken along a direction perpendicular to the axis of the motor. In the cross-section, the length of the end of the elastic element that abuts against the slide plate in the first direction is ø5.
[0044] The relationship between ø5 and ø3 is defined to satisfy 0.3≥ø5 / ø3≥0.2. This setting can ensure the energy efficiency and operating noise of the compressor.
[0045] If ø5 / ø3 < 0.2, the vane is prone to tilting, resulting in uneven gap between the vane and the vane groove. This not only fails to ensure effective sliding of the vane but also increases refrigerant leakage, reduces compressor energy efficiency, and increases compressor operating noise.
[0046] If ø5 / ø3 > 0.3, it will increase the volume of the mounting hole that mates with the elastic element, reduce the structural rigidity and strength of the cylinder, increase the deformation of the cylinder when the compressor is working, reduce the energy efficiency of the compressor, and affect the performance of the compressor.
[0047] In some embodiments, optionally, ø3 and ø5 satisfy: 0.27≥ø5 / ø3≥0.21.
[0048] In this embodiment, the relationship between ø3 and ø5 is further defined to satisfy 0.27≥ø5 / ø3≥0.21, which can guarantee the energy efficiency and operating noise of the compressor.
[0049] In some embodiments, the elastic element may optionally include at least one spring, one end of which abuts against the slide.
[0050] In this embodiment, the elastic element includes a spring, one end of which abuts against the slider.
[0051] Alternatively, the elastic element may include multiple springs, with one end of any one of the springs abutting against the slider. This arrangement increases the contact area and contact angle between the elastic element and the slider, ensuring the balance of the force acting on the slider, guaranteeing the slider's running trajectory, and preventing slider deviation.
[0052] In some embodiments, optionally, when the elastic element includes multiple springs, the number of mounting holes is multiple, with each spring disposed in one mounting hole; the cylinder is cross-sectioned along a direction perpendicular to the motor axis, and in the cross-section, the sum of the lengths of the ends of the multiple springs that abut against the slide plate in a first direction is ø5.
[0053] In this embodiment, the structure of the elastic element is further defined.
[0054] When the elastic element includes multiple springs, there are multiple mounting holes, with each spring having one mounting hole. That is, the number of springs matches the number of mounting holes, with each spring corresponding to one mounting hole.
[0055] A cross-section of the cylinder is taken along a direction perpendicular to the motor's axis. In this cross-section, the length of the end of the elastic element that abuts against the slide in a first direction is the sum of the lengths of the ends of the multiple springs that abut against the slide in the first direction. That is, when a cross-section of the cylinder is taken along a direction perpendicular to the motor's axis, the sum of the lengths of the ends of the multiple springs that abut against the slide in the first direction is ø5.
[0056] In some embodiments, optionally, when the elastic element includes a plurality of springs, the slide is provided with a plurality of abutments, the plurality of abutments being arranged axially spaced along the crankshaft, and each spring abutting against one abutment.
[0057] In this embodiment, the mating structure of the slider and the elastic element is further defined.
[0058] When the elastic element includes multiple springs, the slide has multiple abutment portions.
[0059] Multiple abutments are arranged at intervals along the axial direction of the crankshaft, with each spring abutting against one abutment.
[0060] The compressor in this application uses propane as the refrigerant. Propane refrigerant has a relatively low cooling capacity per unit volume; therefore, the cylinder volume needs to be increased. This, in turn, increases the axial height of the cylinder, necessitating a corresponding increase in the size of the vane slot and vane. By rationally designing the cooperation structure of multiple springs and vanes, the vane is provided with multiple abutment parts. These abutment parts are spaced apart along the crankshaft axial direction, with each spring engaging one abutment part. This increases the contact area and contact angle between the elastic element and the vane, ensuring the balance of force acting on the vane. This helps maintain the vane's running trajectory, prevents vane deviation, and reduces refrigerant leakage. This provides reliable structural support for improving compressor energy efficiency and reducing compressor operating noise.
[0061] The second aspect of this application proposes an air conditioner comprising: a compressor as described in the first aspect.
[0062] The air conditioner provided in this application includes a compressor as described in the first aspect, and therefore has all the beneficial effects of the aforementioned compressor, which will not be described in detail here.
[0063] Additional aspects and advantages of this application will become apparent in the following description or may be learned by practice of this application. Attached Figure Description
[0064] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:
[0065] Figure 1 shows a schematic diagram of the first part of the compressor according to an embodiment of this application;
[0066] Figure 2 shows a schematic diagram of the second part of the compressor according to an embodiment of this application;
[0067] Figure 3 shows a partial structural schematic diagram of a cylinder according to an embodiment of this application;
[0068] Figure 4 is a magnified view of part A of the cylinder shown in Figure 3.
[0069] The correspondence between the reference numerals and component names in Figures 1 to 4 is as follows:
[0070] 10 Compressor, 100 Housing, 200 Cylinder, 210 Sliding vane groove, 212 Abutment part, 220 Mounting hole, 230 Sliding vane, 240 Elastic element, 242 Spring, 300 Motor, 400 Crankshaft. Embodiments of the present invention
[0071] To better understand the above-mentioned objectives, features, and advantages of this application, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.
[0072] Many specific details are set forth in the following description in order to provide a full understanding of this application. However, this application may also be implemented in other ways different from those described herein. Therefore, the scope of protection of this application is not limited to the specific embodiments disclosed below.
[0073] The compressor 10 and air conditioner of some embodiments of this application are described below with reference to Figures 1 to 4.
[0074] As shown in Figures 1, 2 and 3, a compressor 10 according to some embodiments of this application includes a housing 100, a cylinder 200, a motor 300 and a crankshaft 400.
[0075] The cylinder 200 is located inside the housing 100.
[0076] The motor 300 is located inside the housing 100.
[0077] Motor 300 is spaced apart on one side of cylinder 200.
[0078] The crankshaft 400 is located inside the housing 100 and is connected to the motor 300 and the cylinder 200.
[0079] The maximum inner diameter of housing 100 is ø1.
[0080] The outer diameter of motor 300 is ø2.
[0081] The inner diameter of cylinder 200 is ø3.
[0082] The outer diameter of the portion of crankshaft 400 located inside motor 300 is ø4.
[0083] Among them, ø2≥ø1, 0.6≥ø3 / ø1≥0.5, 40≥ø3 / ø4≥30.
[0084] The compressor 10 provided in this application includes a housing 100, a cylinder 200, a motor 300, and a crankshaft 400.
[0085] The cylinder 200, motor 300, and crankshaft 400 are all housed within the housing 100. The motor 300 is spaced apart on one side of the cylinder 200, and the crankshaft 400 passes through both the motor 300 and the cylinder 200. The housing 100 serves as the mounting carrier for the cylinder 200, motor 300, and crankshaft 400, and has the function of mounting and fixing the cylinder 200, motor 300, and crankshaft 400.
[0086] The compressor 10 of this application uses propane as the refrigerant, and the mating structure of the housing 100, cylinder 200, motor 300, and crankshaft 400 is defined based on the propane refrigerant. The maximum inner diameter of the housing 100 is denoted as ø1, the outer diameter of the motor 300 as ø2, the inner diameter of the cylinder 200 as ø3, and the outer diameter of the portion of the crankshaft 400 located within the motor 300 as ø4. The relationships between ø1, ø2, ø3, and ø4 are defined to satisfy ø2≥ø1, 0.6≥ø3 / ø1≥0.5, and 40≥ø3 / ø4≥30.
[0087] The motor 300 is located inside the housing 100. The outer diameter ø2 of the motor 300 is greater than or equal to the maximum value ø1 of the inner diameter of the housing 100. That is, the motor 300 and the housing 100 are interference fit, so that the motor 300 can be stably assembled inside the housing 100 and the situation of the motor 300 shifting relative to the housing 100 is avoided.
[0088] Cylinder 200 is located inside housing 100. The ratio of the inner diameter ø3 of cylinder 200 to the maximum inner diameter ø1 of housing 100 is greater than or equal to 0.5 and less than or equal to 0.6. This design balances the structural rigidity of cylinder 200 with the energy efficiency and operating noise of compressor 10. Since the internal volume of cylinder 200 is constant, a larger inner diameter ø3 allows for a corresponding reduction in the axial height of cylinder 200. This helps reduce refrigerant leakage, improves the energy efficiency of compressor 10, and lowers the operating noise of compressor 10.
[0089] Therefore, when ø3 / ø1 < 0.5, the axial height of cylinder 200 is relatively high, which will increase refrigerant leakage, thereby reducing the energy efficiency of compressor 10 and increasing the operating noise of compressor 10. When ø3 / ø1 > 0.6, the wall thickness of cylinder 200 is relatively thin, and the structural strength and rigidity of cylinder 200 are insufficient. Cylinder 200 is prone to deformation during operation, which will reduce the energy efficiency of compressor 10 and affect the performance of compressor 10.
[0090] The crankshaft 400 is connected to the motor 300. The outer diameter of the portion of the crankshaft 400 located within the motor 300 is denoted as ø4. That is, the outer diameter of the portion of the crankshaft 400 surrounded by the motor 300 is ø4. The inner diameter ø3 of the cylinder 200 and the outer diameter ø4 of the portion of the crankshaft 400 located within the motor 300 satisfy the following condition: 40 ≥ ø3 / ø4 ≥ 30. This arrangement ensures that the crankshaft 400 effectively drives the piston movement of the cylinder 200 while reducing the friction between the bearings of the crankshaft 400 and the motor 300, thus guaranteeing the performance of the compressor 10.
[0091] If ø3 / ø4 < 30, then the outer diameter of the portion of crankshaft 400 located inside motor 300 is too large. This will increase the friction between the bearings of crankshaft 400 and motor 300, reducing performance.
[0092] If ø3 / ø4 > 40, then the structural rigidity of crankshaft 400 is insufficient. When compressor 10 is working, it will cause an increase in the deflection of the rotor of motor 300, which will increase electromagnetic noise.
[0093] Therefore, based on the use of propane refrigerant in compressor 10, by reasonably setting the matching structure of housing 100, cylinder 200, motor 300 and crankshaft 400, the stability and reliability of the assembly of housing 100, cylinder 200, motor 300 and crankshaft 400 can be guaranteed, while improving the energy efficiency of compressor 10, reducing the operating noise of compressor 10, and improving the performance of compressor 10.
[0094] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features: ø1, ø2, ø3 and ø4 satisfy: ø1+0.1mm>ø2≥ø1, 0.54≥ø3 / ø1≥0.51, 37.2≥ø3 / ø4≥34.5.
[0095] In this embodiment, the matching structure of ø1, ø2, ø3 and ø4 is further defined such that ø1, ø2, ø3 and ø4 satisfy: ø1+0.1mm>ø2≥ø1, 0.54≥ø3 / ø1≥0.51, 37.2≥ø3 / ø4≥34.5.
[0096] This configuration, based on the use of propane refrigerant in compressor 10, ensures the stability and reliability of the assembly of housing 100, cylinder 200, motor 300 and crankshaft 400 by reasonably setting the cooperative structure of housing 100, cylinder 200, motor 300 and crankshaft 400, while also improving the energy efficiency of compressor 10, reducing the operating noise of compressor 10 and improving the performance of compressor 10.
[0097] If ø2≥ø1+0.1mm, then the interference fit between the motor 300 and the housing 100 is large, which will increase the vibration and noise of the compressor 10 during operation.
[0098] If ø2 < ø1, then the gap between the motor 300 and the housing 100 is large, and the motor 300 is prone to displacement relative to the housing 100, which cannot guarantee the assembly position of the motor 300 and affects the normal operation of the compressor 10.
[0099] For example, ø2=ø1+0.02mm, ø2=ø1+0.04mm, ø2=ø1+0.05mm, ø2=ø1+0.06mm and ø2=ø1+0.08mm, etc., will not be listed here one by one.
[0100] If ø3 / ø1 < 0.51, then the axial height of cylinder 200 is relatively high, which will increase the refrigerant leakage, thereby reducing the energy efficiency of compressor 10 and increasing the operating noise of compressor 10.
[0101] If ø3 / ø1 > 0.54, then the wall thickness of cylinder 200 is too thin, the structural strength and rigidity of cylinder 200 are insufficient, cylinder 200 is prone to deformation during operation, which will reduce the energy efficiency of compressor 10 and affect the performance of compressor 10.
[0102] Examples include ø3 / ø1=0.515, ø3 / ø1=0.52, ø3 / ø1=0.525, ø3 / ø1=0.53 and ø3 / ø1=0.535, etc., which will not be listed here one by one.
[0103] If ø3 / ø4 < 34.5, then the outer diameter of the portion of crankshaft 400 located inside motor 300 is too large. This will increase the friction between the bearings of crankshaft 400 and motor 300, reducing performance.
[0104] If ø3 / ø4 > 37.2, then the structural rigidity of crankshaft 400 is insufficient. When compressor 10 is working, it will cause an increase in the deflection of the rotor of motor 300, which will increase electromagnetic noise.
[0105] Examples include ø3 / ø4=35, ø3 / ø4=35.5, ø3 / ø4=36, ø3 / ø4=36.5, and ø3 / ø4=37, etc., which will not be listed here one by one.
[0106] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features. As shown in FIG2, the axial height of the cylinder 200 is H, wherein H < ø3.
[0107] In this embodiment, the structure of cylinder 200 is defined.
[0108] The axial height of cylinder 200 is H, and the inner diameter of cylinder 200 is ø3. H and ø3 satisfy H < ø3. This setting takes into account both the structural rigidity of cylinder 200 and the leakage of cylinder 200, which is beneficial to improving the energy efficiency of compressor 10 and reducing the operating noise of compressor 10.
[0109] If H≥ø3, then the axial height of cylinder 200 is too large, which will increase the refrigerant leakage, reduce the energy efficiency of compressor 10, and increase the operating noise of compressor 10.
[0110] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features, where H and ø3 satisfy: 0.78≥H / ø3≥0.512.
[0111] In this embodiment, the relationship between H and ø3 is defined such that 0.78 ≥ H / ø3 ≥ 0.512.
[0112] If H / ø3 < 0.512, the wall thickness of cylinder 200 is relatively thin, which will reduce the structural rigidity and strength of cylinder 200. When compressor 10 is working, the deformation of cylinder 200 will increase, which will reduce the energy efficiency of compressor 10 and affect the performance of compressor 10.
[0113] If H / ø3 > 0.78, the axial height of cylinder 200 is too large, which will increase leakage, reduce the energy efficiency of compressor 10, and increase the operating noise of compressor 10.
[0114] Examples include H / ø3=0.55, H / ø3=0.58, H / ø3=0.6, H / ø3=0.62, H / ø3=0.65, H / ø3=0.7, and H / ø3=0.75, etc., which will not be listed here one by one.
[0115] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features, as shown in Figures 3 and 4: the cylinder 200 is provided with a vane groove 210, a mounting hole 220, a vane 230 and an elastic element 240.
[0116] The slider 230 is slidably disposed in the slider groove 210.
[0117] The elastic element 240 is provided in the mounting hole 220, and one end of the elastic element 240 abuts against the slide 230.
[0118] A cross-section of the cylinder 200 is taken along the direction perpendicular to the axis of the motor 300. In the cross-section, the length of the end of the elastic element 240 that abuts against the slide plate 230 in the first direction is ø5.
[0119] Among them, 0.3≥ø5 / ø3≥0.2.
[0120] In this embodiment, the structure of cylinder 200 is defined.
[0121] The cylinder 200 is provided with a sliding plate groove 210, a mounting hole 220, a sliding plate 230 and an elastic element 240.
[0122] The slider 230 is slidably disposed in the slider groove 210.
[0123] The elastic element 240 is provided in the mounting hole 220, and one end of the elastic element 240 abuts against the slide 230.
[0124] A cross-section of the cylinder 200 is taken along the direction perpendicular to the axis of the motor 300. In the cross-section, the length of the end of the elastic element 240 that abuts against the slide plate 230 in the first direction is ø5.
[0125] The relationship between ø5 and ø3 is defined such that 0.3≥ø5 / ø3≥0.2. This setting ensures the energy efficiency and operating noise of compressor 10.
[0126] If ø5 / ø3 < 0.2, then the vane 230 is prone to tilting, which makes the gap between the vane 230 and the vane groove 210 uneven. This not only fails to ensure the effective sliding of the vane 230, but also increases the amount of refrigerant leakage, which will reduce the energy efficiency of the compressor 10 and increase the operating noise of the compressor 10.
[0127] If ø5 / ø3>0.3, the volume of the mounting hole 220 that mates with the elastic element 240 will increase, which will reduce the structural rigidity and strength of the cylinder 200. When the compressor 10 is working, the deformation of the cylinder 200 will increase, which will reduce the energy efficiency of the compressor 10 and affect the performance of the compressor 10.
[0128] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features, where ø3 and ø5 satisfy: 0.27≥ø5 / ø3≥0.21.
[0129] In this embodiment, the relationship between ø3 and ø5 is further defined to satisfy 0.27≥ø5 / ø3≥0.21, which can ensure the energy efficiency and operating noise of compressor 10.
[0130] Examples include ø5 / ø3=0.22, ø5 / ø3=0.23, ø5 / ø3=0.24, ø5 / ø3=0.25, and ø5 / ø3=0.26, etc., which will not be listed here one by one.
[0131] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features: the elastic element 240 includes at least one spring 242, and one end of each spring 242 abuts against the slide plate 230.
[0132] In this embodiment, the elastic element 240 includes a spring 242, one end of which abuts against the slider 230.
[0133] Alternatively, the elastic element 240 may include a plurality of springs 242, one end of any one of the springs 242 abutting against the slider 230. This arrangement can increase the contact area and contact angle between the elastic element 240 and the slider 230, ensure the balance of the force acting on the slider 230, ensure the running trajectory of the slider 230, and prevent the slider 230 from deviating.
[0134] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features: when the elastic element 240 includes a plurality of springs 242, the number of mounting holes 220 is a plurality.
[0135] Each spring 242 is provided with a mounting hole 220.
[0136] A cross-section of the cylinder 200 is taken along the axis perpendicular to the motor 300. In the cross-section, the sum of the lengths of the ends of the multiple springs 242 that abut against the slide plate 230 in the first direction is ø5.
[0137] In this embodiment, the structure of the elastic member 240 is further defined.
[0138] When the elastic element 240 includes multiple springs 242, there are multiple mounting holes 220, with each spring 242 located in one mounting hole 220. That is, the number of springs 242 matches the number of mounting holes 220, with each spring 242 corresponding to one mounting hole 220.
[0139] A cross-section of the cylinder 200 is taken along the axis perpendicular to the motor 300. In this cross-section, the length of the end of the elastic element 240 that abuts against the slide 230 in the first direction is the sum of the lengths of the ends of the multiple springs 242 that abut against the slide 230 in the first direction. That is, a cross-section of the cylinder 200 is taken along the axis perpendicular to the motor 300. In this cross-section, the sum of the lengths of the ends of the multiple springs 242 that abut against the slide 230 in the first direction is ø5.
[0140] For example, when the elastic element 240 includes a spring 242, the slide 230 is provided with two protrusions, and the spring 242 abuts against the two protrusions.
[0141] For example, when the elastic element 240 includes N springs 242, the slide 230 is provided with N×2 protrusions, and each spring 242 abuts against two protrusions. Here, N is a positive integer greater than 1.
[0142] For example, when the elastic element 240 includes N springs 242, the slide 230 is provided with N×3 protrusions, and each spring 242 abuts against three protrusions. Here, N is a positive integer greater than 1.
[0143] This embodiment provides a compressor 10. In addition to the technical features of the above embodiments, this embodiment further includes the following technical features. As shown in Figures 3 and 4, when the elastic element 240 includes a plurality of springs 242, the slide 230 is provided with a plurality of abutment portions 212. The plurality of abutment portions 212 are arranged at intervals along the axial direction of the crankshaft 400, and each spring 242 abuts against one abutment portion 212.
[0144] In this embodiment, the mating structure of the slider 230 and the elastic member 240 is further defined.
[0145] When the elastic element 240 includes multiple springs 242, the slide 230 is provided with multiple abutment portions 212.
[0146] Multiple abutment portions 212 are arranged at intervals along the axial direction of the crankshaft 400, and each spring 242 abuts against one abutment portion 212.
[0147] The compressor 10 of this application uses propane as the refrigerant. Propane refrigerant has a low cooling capacity per unit volume, therefore, the volume of the cylinder 200 needs to be increased. This will correspondingly increase the axial height of the cylinder 200, and consequently, the dimensions of the vane groove 210 and the vane 230 need to be increased accordingly. By rationally arranging the cooperation structure between multiple springs 242 and the vane 230, the vane 230 is provided with multiple abutment portions 212. These abutment portions 212 are arranged axially at intervals along the crankshaft 400, and each spring 242 cooperates with one abutment portion 212. This increases the contact area and contact angle between the elastic element 240 and the vane 230, ensuring the balance of the force acting on the vane 230. This helps to ensure the running trajectory of the vane 230, prevents the vane 230 from deviating, and reduces refrigerant leakage. This provides reliable structural support for improving the energy efficiency of the compressor 10 and reducing its operating noise.
[0148] An air conditioner according to some embodiments of this application includes: a compressor 10 as described in any of the above embodiments.
[0149] An air conditioner provided in this application includes a compressor 10.
[0150] The compressor 10 includes a housing 100, a cylinder 200, a motor 300, and a crankshaft 400.
[0151] The cylinder 200, motor 300, and crankshaft 400 are all housed within the housing 100. The motor 300 is spaced apart on one side of the cylinder 200, and the crankshaft 400 passes through both the motor 300 and the cylinder 200. The housing 100 serves as the mounting carrier for the cylinder 200, motor 300, and crankshaft 400, and has the function of mounting and fixing the cylinder 200, motor 300, and crankshaft 400.
[0152] The compressor 10 of this application uses propane as the refrigerant, and the mating structure of the housing 100, cylinder 200, motor 300, and crankshaft 400 is defined based on the propane refrigerant. The maximum inner diameter of the housing 100 is denoted as ø1, the outer diameter of the motor 300 as ø2, the inner diameter of the cylinder 200 as ø3, and the outer diameter of the portion of the crankshaft 400 located within the motor 300 as ø4. The relationships between ø1, ø2, ø3, and ø4 are defined to satisfy ø2≥ø1, 0.6≥ø3 / ø1≥0.5, and 40≥ø3 / ø4≥30.
[0153] The motor 300 is located inside the housing 100. The outer diameter ø2 of the motor 300 is greater than or equal to the maximum value ø1 of the inner diameter of the housing 100. That is, the motor 300 and the housing 100 are interference fit, so that the motor 300 can be stably assembled inside the housing 100 and the situation of the motor 300 shifting relative to the housing 100 is avoided.
[0154] Cylinder 200 is located inside housing 100. The ratio of the inner diameter ø3 of cylinder 200 to the maximum inner diameter ø1 of housing 100 is greater than or equal to 0.5 and less than or equal to 0.6. This design balances the structural rigidity of cylinder 200 with the energy efficiency and operating noise of compressor 10. Since the internal volume of cylinder 200 is constant, a larger inner diameter ø3 allows for a corresponding reduction in the axial height of cylinder 200. This helps reduce refrigerant leakage, improves the energy efficiency of compressor 10, and lowers the operating noise of compressor 10.
[0155] Therefore, when ø3 / ø1 < 0.5, the axial height of cylinder 200 is relatively high, which will increase refrigerant leakage, thereby reducing the energy efficiency of compressor 10 and increasing the operating noise of compressor 10. When ø3 / ø1 > 0.6, the wall thickness of cylinder 200 is relatively thin, and the structural strength and rigidity of cylinder 200 are insufficient. Cylinder 200 is prone to deformation during operation, which will reduce the energy efficiency of compressor 10 and affect the performance of compressor 10.
[0156] The crankshaft 400 is connected to the motor 300. The outer diameter of the portion of the crankshaft 400 located within the motor 300 is denoted as ø4. That is, the outer diameter of the portion of the crankshaft 400 surrounded by the motor 300 is ø4. The inner diameter ø3 of the cylinder 200 and the outer diameter ø4 of the portion of the crankshaft 400 located within the motor 300 satisfy the following condition: 40 ≥ ø3 / ø4 ≥ 30. This arrangement ensures that the crankshaft 400 effectively drives the piston movement of the cylinder 200 while reducing the friction between the bearings of the crankshaft 400 and the motor 300, thus guaranteeing the performance of the compressor 10.
[0157] If ø3 / ø4 < 30, then the outer diameter of the portion of crankshaft 400 located inside motor 300 is too large. This will increase the friction between the bearings of crankshaft 400 and motor 300, reducing performance.
[0158] If ø3 / ø4 > 40, then the structural rigidity of crankshaft 400 is insufficient. When compressor 10 is working, it will cause an increase in the deflection of the rotor of motor 300, which will increase electromagnetic noise.
[0159] Therefore, based on the use of propane refrigerant in compressor 10, by reasonably setting the matching structure of housing 100, cylinder 200, motor 300 and crankshaft 400, the stability and reliability of the assembly of housing 100, cylinder 200, motor 300 and crankshaft 400 can be guaranteed, while improving the energy efficiency of compressor 10, reducing the operating noise of compressor 10, and improving the performance of compressor 10.
[0160] Exemplarily, the compressor 10 includes a housing 100, a motor 300, and a compression pump body driven by the motor 300 through a rotor and a crankshaft 400 fixed inside the rotor. The compression pump body includes a cylinder 200, which has a vane groove 210 and a vane 230 sliding in the vane groove 210. The cylinder 200 also has a mounting hole 220 and an elastic element 240 within the mounting hole 220. The elastic element 240 is used to push the vane 230 to move, and the length of the end of the elastic element 240 that contacts the vane 230 in a first direction is ø5. The cylinder 200 also includes a piston that is sleeved outside the eccentric portion of the crankshaft 400 and rotates with the crankshaft 400 around the center of the cylinder 200 to supply gas to the compressor 10. The maximum inner diameter of the housing 100 is ø1, the outer diameter of the motor 300 is ø2, the inner diameter of the cylinder 200 is ø3, and the outer diameter of the portion of the crankshaft 400 located inside the motor 300 is ø4. Among them, ø1+0.1mm>ø2≥ø1, and 0.54≥ø3 / ø1≥0.51, and 37.2≥ø3 / ø4≥34.5.
[0161] The axial height of cylinder 200 is H, where 0.78≥H / ø3≥0.512.
[0162] This application rationally sets up the matching structure of the housing 100, cylinder 200, motor 300 and crankshaft 400, so that the compressor 10 has the advantages of high reliability and low vibration and noise.
[0163] A cross-section of the cylinder 200 is taken along the axis perpendicular to the motor 300. In this cross-section, the length of the end of the elastic element 240 that abuts against the slide plate 230 in a first direction is ø5. The elastic element 240 includes at least one spring 242. When there are multiple springs 242, a cross-section of the cylinder 200 is taken along the axis perpendicular to the motor 300. In this cross-section, the sum of the lengths of the ends of the multiple springs 242 that abut against the slide plate 230 in a first direction is ø5. ø3 and ø5 satisfy: 0.27 ≥ ø5 / ø3 ≥ 0.21. This configuration gives the compressor 10 the advantages of high energy efficiency and low noise.
[0164] In this application, the term "multiple" refers to two or more unless otherwise expressly defined. The terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; "linking" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.
[0165] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. The above descriptions are merely preferred embodiments of this application and are not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.
Claims
1. A compressor, wherein, include: case; A cylinder is disposed within the housing; An electric motor is housed within the housing, and the electric motor is spaced apart on one side of the cylinder; A crankshaft is disposed within the housing, and the crankshaft passes through the motor and the cylinder; The maximum inner diameter of the housing is ø1, the outer diameter of the motor is ø2, the inner diameter of the cylinder is ø3, and the outer diameter of the portion of the crankshaft located inside the motor is ø4. Among them, ø2≥ø1, 0.6≥ø3 / ø1≥0.5, 40≥ø3 / ø4≥30.
2. The compressor according to claim 1, wherein, ø1, ø2, ø3 and ø4 satisfy: ø1+0.1mm>ø2≥ø1, 0.54≥ø3 / ø1≥0.51, 37.2≥ø3 / ø4≥34.
5.
3. The compressor according to claim 1 or 2, wherein, The axial height of the cylinder is H, where H < ø3.
4. The compressor according to claim 3, wherein, H and ø3 satisfy: 0.78≥H / ø3≥0.
512.
5. The compressor according to any one of claims 1 to 4, wherein, The cylinder is provided with a sliding plate groove, a mounting hole, a sliding plate and an elastic element. The sliding plate is slidably disposed in the sliding plate groove, the elastic element is disposed in the mounting hole, and one end of the elastic element abuts against the sliding plate. A cross-section of the cylinder is taken along a direction perpendicular to the axis of the motor. In the cross-section, the length of the end of the elastic element that abuts against the slide plate in the first direction is ø5. Among them, 0.3≥ø5 / ø3≥0.
2.
6. The compressor according to claim 5, wherein, ø3 and ø5 satisfy: 0.27≥ø5 / ø3≥0.
21.
7. The compressor according to claim 5 or 6, wherein, The elastic element includes at least one spring, one end of each spring abutting against the slide.
8. The compressor according to claim 7, wherein, When the elastic element includes multiple springs, the number of mounting holes is multiple, and each spring is provided in one mounting hole; A cross-section is taken of the cylinder along a direction perpendicular to the axis of the motor. In the cross-section, the sum of the lengths of the ends of the plurality of springs that abut against the slide plate in the first direction is ø5.
9. The compressor according to claim 7, wherein, When the elastic element includes a plurality of springs, the slide is provided with a plurality of abutment portions, the plurality of abutment portions being arranged at intervals along the axial direction of the crankshaft, and each spring abutting against one of the abutment portions.
10. An air conditioner, wherein, include: The compressor as described in any one of claims 1 to 9.