Cylinder, compressor and air conditioner with resonance muffler

Abstract

The present application provides a cylinder, compressor and air conditioner with resonance silencer. The cylinder with resonance silencer includes a cylinder body, a sliding vane groove is provided on the inner wall of the cylinder body, a resonance cavity, an exhaust cutout and a connecting channel connecting the resonance cavity and the exhaust cutout are provided on one end surface of the cylinder body, the exhaust cutout has a flat bottom surface, and the bottom surface of the connecting channel is flush with the bottom surface of the exhaust cutout. The cylinder with resonance silencer of the present application can form a silencer cavity together with the exhaust cutout, thereby increasing the volume of the silencer cavity to improve the silencer effect; and can reduce the volume of the exhaust cutout, thereby reducing the clearance volume.

Description

Technical Field

[0001] The present application belongs to the technical field of compressors, and more specifically, relates to a cylinder, a compressor and an air conditioner with resonance silencer. Background Art

[0002] As compressor technology matures, it becomes increasingly difficult to improve the performance of air conditioner compressors. To provide a better user experience, the noise level of air conditioner compressors is becoming increasingly lower. While maintaining compression performance, a slight reduction in compressor noise often requires extensive experimentation. Similarly, while maintaining compression performance, a slight improvement in compression performance often requires significant improvements to the compressor structure. Figure 2 Currently, a resonance chamber 230 connected to the exhaust port 220 is generally provided on the cylinder body 210 of the cylinder 200. The resonance chamber 230 and the connecting channel 240 together form a silencer chamber for noise reduction. Since the compressed gas is discharged from the exhaust port 220, the space (i.e., the clearance volume) formed by the exhaust port 220 connecting the resonance chamber 230 will store some of the compressed gas, thereby reducing the performance of the compressor. To reduce the noise of the compressor, the resonance chamber needs to be larger, which will increase the clearance volume, reduce the performance of the compressor, and thus reduce the energy efficiency ratio of the air conditioner. Summary of the Invention

[0003] The purpose of the embodiments of the present application is to provide a cylinder, a compressor and an air conditioner with resonance silencer to solve the problem in the related art that it is difficult to strike a balance between the performance and silencer of the compressor.

[0004] To achieve the above-mentioned purpose, the technical solution adopted in the embodiment of the present application is: to provide a cylinder with resonance silencer, including a cylinder body, a sliding vane groove is provided on the inner wall of the cylinder body, and a resonance cavity, an exhaust cutout and a connecting channel connecting the resonance cavity and the exhaust cutout are provided on one end face of the cylinder body, the exhaust cutout has a flat bottom surface, and the bottom surface of the connecting channel is flush with the bottom surface of the exhaust cutout.

[0005] In an optional embodiment, along the radial direction of the cylinder body, the length of the communication channel is greater than the length of the exhaust cutout.

[0006] In an optional embodiment, along the circumference of the cylinder body, the width of the bottom surface of the exhaust cutout is greater than or equal to the width of the bottom surface of the communication channel.

[0007] In an optional embodiment, along the circumference of the cylinder body, the width of the top of the exhaust cutout is greater than the width of the top of the communication channel.

[0008] In an optional embodiment, the side wall surface of the exhaust cutout is a flat surface, a curved surface or an arc surface.

[0009] In an optional embodiment, the exhaust cutout has a rectangular or trapezoidal cross section perpendicular to the radial direction of the cylinder body.

[0010] In an optional embodiment, the edge of the sliding vane slot is chamfered.

[0011] In an optional embodiment, the minimum distance between the side wall surface of the exhaust cutout and the chamfer is in the range of 0.5-2 mm.

[0012] Another object of an embodiment of the present application is to provide a compressor, comprising a cylinder with resonance silencer as described in any of the above embodiments.

[0013] Another object of an embodiment of the present application is to provide an air conditioner, comprising the compressor described in the above embodiment.

[0014] The beneficial effect of the cylinder with resonance silencer provided by the embodiment of the present application is that: compared with the prior art, the cylinder with resonance silencer of the present application, by providing a flat surface on the bottom surface of the exhaust cutout and making the bottom surface of the exhaust cutout flush with the bottom surface of the connecting channel, can make the exhaust cutout, the connecting channel and the resonance cavity together constitute a silencer cavity, thereby increasing the volume of the silencer cavity to enhance the silencer effect; and can reduce the volume of the exhaust cutout, thereby reducing the clearance volume.

[0015] The beneficial effect of the compressor provided by the embodiment of the present application is that, compared with the prior art, the compressor of the present application uses the cylinder with resonance silencer of the above embodiment, which can not only improve the performance of the compressor, but also reduce the noise of the compressor operation.

[0016] The beneficial effect of the air conditioner provided by the embodiment of the present application is that, compared with the prior art, the air conditioner of the present application uses the compressor of the above embodiment, which can make the operation noise of the air conditioner lower and improve the energy efficiency ratio of the air conditioner. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the embodiments or exemplary technical descriptions. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0018] Figure 1 This is a schematic diagram of the structure of the cylinder in a traditional compressor;

[0019] Figure 2 A schematic structural diagram of a cylinder with resonance noise reduction provided in Example 1 of the present application;

[0020] Figure 3 for Figure 2 Enlarged view of part A;

[0021] Figure 4 A schematic top view of the cylinder with resonance noise reduction provided in Example 1 of the present application;

[0022] Figure 5 A schematic diagram of the partial structure of a cylinder with resonance silencer provided in Example 2 of the present application.

[0023] Among them, the main marks of the drawings in the figure are:

[0024] 100- Cylinder with resonance muffler;

[0025] 110 - cylinder block; 120 - exhaust cutout; 130 - resonance chamber; 140 - connecting channel; 150 - vane groove; 151 - chamfer. DETAILED DESCRIPTION

[0026] In order to make the technical problems, technical solutions and beneficial effects to be solved by this application more clearly understood, this application is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this application and are not intended to limit this application.

[0027] In the description of this application, it should be understood that the terms "top", "bottom", "inside", "outside", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, they cannot be understood as limitations on this application.

[0028] References to "one embodiment," "some embodiments," or "an embodiment" in this specification mean that a particular feature, structure, or characteristic described in conjunction with that embodiment is included in one or more embodiments of the present invention. Thus, phrases such as "in one embodiment," "in some embodiments," "in other embodiments," and "in other embodiments" appearing in various places in this specification do not necessarily refer to the same embodiment, but rather mean "one or more, but not all, embodiments," unless otherwise specifically emphasized. Furthermore, in one or more embodiments, particular features, structures, or characteristics may be combined in any suitable manner.

[0029] The English abbreviations used in this application correspond to the original Chinese and English texts and their explanations as follows:

[0030] COP, English: Coefficient Of Performance; Chinese: Refrigeration coefficient, also known as energy efficiency ratio, refers to the ratio of cooling capacity to compressor power.

[0031] SEER (seasonal energy efficiency ratio) is the standard for seasonal energy efficiency in cooling. The standard for SEER used in variable-frequency air conditioners is GB21455-2008.

[0032] See also Figures 2 to 4 The cylinder 100 with resonance noise reduction provided by the present application is now described. The cylinder 100 with resonance noise reduction includes a cylinder body 110, and a vane groove 150 is provided on the inner wall of the cylinder body 110 so that the vanes of the compressor can be slidably placed in the vane groove 150. The cylinder body 110 is provided with a resonance cavity 130, an exhaust cutout 120 and a connecting channel 140, and the resonance cavity 130, the exhaust cutout 120 and the connecting channel 140 are all arranged on one end surface of the cylinder body 110, the exhaust cutout 120 is located on the inner side of the cylinder body 110, and the exhaust cutout 120 extends to the inner wall surface of the cylinder body 110 so that the compressed air in the cylinder body 110 can enter the exhaust cutout 120. The two ends of the connecting channel 140 extend to the resonance cavity 130 and the exhaust cutout 120 respectively, so that the compressed gas is discharged through the exhaust cutout 120; and the connecting channel 140 and the resonance cavity 130 can be combined for noise reduction. The exhaust cutout 120 has a flat bottom surface, that is, the bottom surface of the exhaust cutout 120 is a plane, and the bottom surface of the connecting channel 140 is flush with the bottom surface of the exhaust cutout 120, so that the exhaust cutout 120 can also play a silencing role. In other words, the resonance cavity 130, the connecting channel 140 and the exhaust cutout 120 together constitute a silencing cavity. Compared with the method in which only the resonance cavity 130 and the connecting channel 140 are combined to form a silencing cavity, the volume of the silencing cavity on the cylinder body 110 of this embodiment is greatly increased, thereby better silencing and improving the silencing effect. In addition, the bottom surface of the exhaust cutout 120 is set to be a plane, and the bottom surface of the connecting channel 140 is made flush with the bottom surface of the exhaust cutout 120. In this way, along the axial direction of the cylinder body 110, the depth of the exhaust cutout 120 is equal to the depth of the connecting channel 140. This structure can make the volume of the exhaust cutout 120 smaller, thereby reducing the clearance volume formed by the resonance chamber 130, the connecting channel 140 and the exhaust cutout 120, thereby improving the performance of the compressor.

[0033] The cylinder 100 with resonance silencer provided in the present application is compared with the prior art. The cylinder 100 with resonance silencer provided in the present application provides a plane on the bottom surface of the exhaust cutout 120 and makes the bottom surface of the exhaust cutout 120 flush with the bottom surface of the connecting channel 140, so that the exhaust cutout 120, the connecting channel 140 and the resonance cavity 130 together constitute a silencer cavity, thereby increasing the volume of the silencer cavity to enhance the silencer effect; and can reduce the volume of the exhaust cutout 120, thereby reducing the clearance volume.

[0034] In one embodiment, see Figure 3 and Figure 4 The length of the communicating channel 140 along the radial direction of the cylinder body 110 is greater than the length of the exhaust cutout 120 along the radial direction of the cylinder body 110. That is, along the radial direction of the cylinder body 110, the length of the communicating channel 140 is greater than the length of the exhaust cutout 120. In this way, the resonance cavity 130 can be relatively far away from the inner wall surface of the cylinder body 110 to ensure the strength of the cylinder body 110.

[0035] In one embodiment, the cross section of the communication channel 140 is rectangular, that is, the cross section along a direction perpendicular to the communication channel 140 is rectangular, so as to facilitate processing and manufacturing, and also facilitate designing the size of the communication channel 140 .

[0036] In one embodiment, the width of the bottom surface of the exhaust cutout 120 is equal to the width of the bottom surface of the connecting channel 140, that is, along the circumferential direction of the cylinder body 110, the width of the bottom surface of the exhaust cutout 120 is equal to the width of the bottom surface of the connecting channel 140. This makes it easier to design the width of the bottom surface of the exhaust cutout 120 and reduce the volume of the exhaust cutout 120.

[0037] In one embodiment, the width of the bottom surface of the exhaust cutout 120 is greater than the width of the bottom surface of the connecting channel 140, that is, along the circumferential direction of the cylinder body 110, the width of the bottom surface of the exhaust cutout 120 is greater than the width of the bottom surface of the connecting channel 140. This makes it easier to design the width of the bottom surface of the exhaust cutout 120, reduce the volume of the exhaust cutout 120, and reduce the resistance of the exhaust cutout 120 when discharging compressed gas, thereby facilitating exhaust.

[0038] In one embodiment, along the circumferential direction of the cylinder body 110, the width of the top of the exhaust cutout 120 is greater than the width of the top of the connecting channel 140, that is, the width of the mouth of the exhaust cutout 120 close to the end face of the cylinder body 110 is greater than the width of the mouth of the connecting channel 140 close to the end face of the cylinder body 110, so as to reduce the resistance of the exhaust cutout 120 when discharging compressed gas and facilitate exhaust.

[0039] In one embodiment, the sidewalls of the exhaust cutout 120 are flat to facilitate fabrication and design and control of the volume of the exhaust cutout 120. Of course, the sidewalls of the exhaust cutout 120 can also be curved, allowing for direct fabrication with a drill. It is understood that the sidewalls of the exhaust cutout 120 can also be curved.

[0040] In one embodiment, the cross section of the exhaust cutout 120 is trapezoidal, that is, the cross section of the exhaust cutout 120 perpendicular to the radial direction of the cylinder body 110 is trapezoidal, to facilitate processing, and make the opening at the top of the exhaust cutout 120 larger to facilitate exhaust and reduce exhaust resistance.

[0041] In one embodiment, see Figure 5 The cross section of the exhaust cutout 120 is rectangular, that is, the cross section of the exhaust cutout 120 perpendicular to the radial direction of the cylinder body 110 is rectangular, which is convenient for processing and easy to design and control the volume of the exhaust cutout 120.

[0042] In one embodiment, see Figures 2 to 4 The edge of the slide slot 150 is provided with a chamfer 151 to facilitate processing and manufacturing, and to facilitate the installation of the slide in the slide slot 150, and to reduce wear during assembly, production and operation.

[0043] In one embodiment, the minimum distance D between the sidewall of the exhaust notch 120 and the edge chamfer 151 of the vane slot 150 is in the range of 0.5-2 mm to ensure the strength of the portion of the cylinder body 110 between the exhaust notch 120 and the vane slot 150. This also allows the compressor of the cylinder 100 with resonance noise reduction to have a higher compression ratio when in operation. When the minimum distance D between the sidewall of the exhaust notch 120 and the edge chamfer 151 of the vane slot 150 is less than 0.5 mm, the strength of the portion of the cylinder body 110 between the exhaust notch 120 and the vane slot 150 is weakened, affecting the quality and service life of the gas. When the minimum distance D between the sidewall of the exhaust notch 120 and the edge chamfer 151 of the vane slot 150 is greater than 2 mm, the compression ratio is low when compressing gas using the cylinder 100 with resonance noise reduction, thereby reducing the performance of the compressor.

[0044] The cylinder 100 with resonance muffler of the embodiment of the present application, when used in a compressor, can not only reduce noise but also improve compression performance. The cylinder 100 with resonance muffler of the embodiment of the present application can be used in rolling rotor compressors of types such as single-cylinder rolling rotor compressors, double-cylinder rolling rotor compressors, jet enthalpy increase rolling rotor compressors, independent compression rolling rotor compressors, variable capacity compression rolling rotor compressors, two-stage compression rolling rotor compressors, and three-stage compression rolling rotor compressors.

[0045] The present application also discloses a compressor comprising the cylinder 100 with resonance muffler as described in any of the above embodiments. The compressor, using the cylinder 100 with resonance muffler as described in the above embodiments, can improve the performance of the compressor and reduce the noise of the compressor operation.

[0046] In one embodiment, the compressor can be a single-cylinder rolling rotor compressor, a double-cylinder rolling rotor compressor, an injection reheat rolling rotor compressor, an independent compression rolling rotor compressor, a variable capacity compression rolling rotor compressor, a two-stage compression rolling rotor compressor, a three-stage compression rolling rotor compressor, etc.

[0047] The compressor of the embodiment of the present application can be used in equipment that requires a compressor, such as air conditioners and refrigerators.

[0048] The present application also discloses an air conditioner including the compressor described in the above embodiment. The air conditioner uses the compressor described in the above embodiment, which can reduce operating noise and improve the energy efficiency of the air conditioner.

[0049] Air conditioner performance is generally described using the energy efficiency ratio (COP), which is the ratio of the air conditioner's cooling capacity to the compressor power (i.e., COP). Due to the development and improvement of compressors, and improvements in compressor structure, improving the COP of air conditioners has become increasingly difficult. For example, for a 1.5-horsepower air conditioner, over the past decade, while maintaining the same compressor noise level, improvements in compressor structure have resulted in an improvement of less than 0.1 in COP. Especially in recent years, as compressor structures have become increasingly sophisticated, improvements in compressor structure have often resulted in an improvement in COP of less than 0.06.

[0050] Air conditioners using the compressors of the embodiments of this application not only reduce noise but also improve their energy efficiency. Compared to air conditioners using conventional cylinders (i.e., conventional air conditioners), air conditioners using the resonant muffler cylinder 100 of the embodiments of this application (i.e., the air conditioners of this embodiment) achieve a noise reduction of 0.5-1.2 dB and a significant improvement in the COP, particularly when the compressor is operating at medium and low frequencies, where the COP is increased by 0.01-0.035.

[0051] For example, a comparison experiment was conducted between a 1.5 HP air conditioner using a compressor according to an embodiment of the present application and a conventional 1.5 HP air conditioner. The air conditioner according to the present embodiment has a power of 1.5 HP, and its compressor uses the cylinder 100 with resonance muffler according to an embodiment of the present application, i.e., the 1.5 HP air conditioner according to the present embodiment. The conventional air conditioner has a power of 1.5 HP, and its compressor uses a conventional cylinder, i.e., the conventional 1.5 HP air conditioner.

[0052] Under the seer 30Hz operating condition, that is, under the seer operating condition, when the compressor speed is 30 revolutions per second and the frequency is low, the compressor power of the 1.5-hp air conditioner in this embodiment is reduced by 1.38W compared with the traditional 1.5-hp air conditioner, and the corresponding cooling capacity is only reduced by 3.33W, and the corresponding COP is improved by 0.0165.

[0053] Under the seer 60Hz operating condition, that is, under the seer operating condition, when the compressor speed is a medium frequency operation of 60 revolutions per second, the 1.5-horsepower air conditioner of this embodiment has a compressor power reduced by 1.55W compared with the traditional 1.5-horsepower air conditioner, while the corresponding cooling capacity increases by 20.97W, and the corresponding COP is improved by 0.0321; the noise is reduced by 1.1bd.

[0054] Under the seer 90Hz operating condition, that is, under the seer operating condition, when the compressor speed is 90 revolutions per second and the high frequency operation condition, the 1.5-hp air conditioner of this embodiment has a compressor power increased by 6.27W compared with the traditional 1.5-hp air conditioner, and the corresponding cooling capacity increased by 17.83W, and the corresponding COP increased by 0.0019; the noise was reduced by 0.52bd.

[0055] From the above, it can be seen that the air conditioner using the compressor of the cylinder 100 with resonance silencer of the present application not only has improved operating noise, but also has improved energy efficiency, especially the energy efficiency during medium and low frequency operation, which is greatly improved compared to traditional air conditioners.

[0056] The above description is merely an optional embodiment of the present application and is not intended to limit the present application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present application shall be included in the scope of protection of the present application.

Claims

1. A cylinder with resonance muffler, comprising a cylinder body, an inner wall of which is provided with a sliding vane groove, and an end surface of which is provided with a resonance cavity, an exhaust cutout, and a communication channel connecting the resonance cavity and the exhaust cutout, characterized in that: The exhaust cutout has a flat bottom surface, and the bottom surface of the communication channel is flush with the bottom surface of the exhaust cutout; along the axial direction of the cylinder body, the depth of the exhaust cutout is equal to the depth of the communication channel.

2. The cylinder with resonance muffler according to claim 1, characterized in that: In the radial direction of the cylinder body, the length of the communication channel is greater than the length of the exhaust cutout.

3. The cylinder with resonance muffler according to claim 1, characterized in that: Along the circumference of the cylinder body, the width of the bottom surface of the exhaust cutout is greater than or equal to the width of the bottom surface of the communication channel.

4. The cylinder with resonance muffler according to any one of claims 1 to 3, characterized in that: Along the circumference of the cylinder body, the width of the top of the exhaust cutout is greater than the width of the top of the communication channel.

5. The cylinder with resonance muffler according to claim 4, characterized in that: The side wall surface of the exhaust cutout is a flat surface or a curved surface.

6. The cylinder with resonance muffler according to claim 4, characterized in that: The exhaust cutout has a rectangular or trapezoidal cross section perpendicular to the radial direction of the cylinder body.

7. The cylinder with resonance muffler according to any one of claims 1 to 3, characterized in that: The edges of the sliding vane slots are chamfered.

8. The cylinder with resonance muffler according to claim 7, characterized in that: The minimum distance between the side wall surface of the exhaust cutout and the chamfer is in the range of 0.5-2 mm.

9. A compressor, characterized in that: The invention comprises a cylinder with resonance sound absorption as claimed in any one of claims 1 to 8.

10. An air conditioner, characterized in that: Comprising the compressor of claim 9.

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