Compressor and air conditioner

Abstract

The utility model relates to a kind of compressor and air conditioner in air conditioning technical field, compressor includes: cylinder;Flange, flange is opened with the flange exhaust hole of cylinder intercommunication, for discharging gas in cylinder;Silencer, silencer has the cavity of flange exhaust hole intercommunication, silencer is opened with the silencer exhaust hole of cavity intercommunication, for discharging gas in cavity;Wherein, the opening area of silencer exhaust hole and the displacement of cylinder, flange exhaust hole opening area are positively correlated, and the volume of the cavity of silencer is negatively correlated, to keep the opening area of silencer exhaust hole on silencer not relatively larger, so that the compressed gas discharged by flange exhaust hole on flange cannot obtain the resistance silencing effect of due noise reduction, simultaneously make the opening area of silencer exhaust hole on silencer not relatively smaller, so that the resistance of compressed gas discharged from silencer is increased.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and in particular to a compressor and an air conditioner. Background Technology

[0002] In the field of air conditioning technology, hydrocarbon refrigerants, such as R290 air conditioning refrigerant, also known as propane, are a new type of natural refrigerant with extremely high environmental protection characteristics. R290 has an ozone depletion potential of 0 and a global warming potential (GWP) of only 3, which means that it has no destructive effect on the ozone layer and has a minimal impact on the greenhouse effect of the Earth's atmosphere.

[0003] When refrigerant flows in a pipe, its velocity is determined by the mass flow rate, the pipe cross-sectional area, and the refrigerant density. The mass flow rate formula is: v = m / (ρ*A), where m represents the mass flow rate (kg / s), ρ is the density (kg / m³), A is the pipe cross-sectional area (m²), and v is the gas velocity (m / s). At 25℃, because R290 refrigerant has a lower density than R32, its flow rate is faster. Furthermore, since the volumetric cooling capacity of R290 refrigerant is approximately 87% that of R32, and the R290 charge is 0.4 to 0.65 times that of R32 models, to achieve the same cooling capacity, the discharge volume of a rolling rotor compressor using R290 refrigerant needs to be more than 70% larger than that using R32. However, currently, the ratio of the total area of ​​the compressor's muffler exhaust port to the exhaust ports of the upper and lower flanges is too small, resulting in a significant exhaust pressure drop and a reduction in the overall energy efficiency of the compressor. Utility Model Content

[0004] The technical problem to be solved by this utility model is to overcome the technical problem that the ratio of the total area of ​​the exhaust port of the compressor muffler to the exhaust port of the upper and lower flanges is too small, resulting in a significant exhaust pressure drop and a reduction in the overall energy efficiency of the compressor. To this end, a compressor and an air conditioner are provided.

[0005] This utility model aims to provide a compressor, comprising:

[0006] cylinder;

[0007] A flange is sealed and assembled on the cylinder, and the flange has a flange vent hole communicating with the cylinder for discharging gas from the cylinder.

[0008] A silencer is located on the exhaust side of the flange exhaust port. The silencer has a cavity communicating with the flange exhaust port. The silencer has an exhaust port communicating with the cavity for discharging gas from the cavity.

[0009] The opening area of ​​the muffler exhaust port is positively correlated with the opening area of ​​the flange exhaust port, the opening area of ​​the muffler exhaust port is negatively correlated with the volume of the cavity, and the opening area of ​​the muffler exhaust port is positively correlated with the displacement of the cylinder.

[0010] In some embodiments, the cylinder includes a first cylinder and a second cylinder;

[0011] The flange includes a first flange and a second flange;

[0012] The first flange corresponds to the first cylinder. The flange exhaust port includes a first exhaust port on the first flange that communicates with the first cylinder for discharging gas from the first cylinder, and a muffler exhaust port on the second flange that communicates with the second cylinder for discharging gas from the second cylinder.

[0013] The muffler includes a first muffler and a second muffler;

[0014] The first muffler is located on the exhaust side of the first exhaust port. The first muffler has a first cavity communicating with the flange exhaust port, and a muffler exhaust port communicating with the first cavity is provided on the first muffler. The second muffler is located on the exhaust side of the muffler exhaust port. The second muffler has a second cavity communicating with the muffler exhaust port. The second cavity is communicating with the first cavity. The muffler exhaust port is used to discharge the gas in the first cavity and the second cavity.

[0015] The opening area of ​​the muffler exhaust port is positively correlated with the total opening area of ​​the flange exhaust port and the muffler exhaust port, the opening area of ​​the muffler exhaust port is negatively correlated with the total volume of the first cavity and the second cavity, and the opening area of ​​the muffler exhaust port is positively correlated with the total displacement of the first cylinder and the second cylinder.

[0016] In some embodiments, when both the flange vent and the muffler vent are circular holes:

[0017] The radius of the muffler exhaust port is d, which satisfies:

[0018] d 2 =K×(πR) 2 )×V0 / (V1×π);

[0019] Wherein, V0 is the displacement of the cylinder, V1 is the volume of the cavity, R is the radius of the flange exhaust port, and K is a preset coefficient.

[0020] In some embodiments, the flange vent hole is provided in multiple locations and / or the muffler vent hole is provided in multiple locations.

[0021] In some embodiments, both the flange vent and the muffler vent are circular holes. Multiple flange vents are provided, and multiple muffler vents are also provided.

[0022] The radii of the plurality of muffler exhaust ports are d1, d2, d3, ..., respectively, satisfying:

[0023]

[0024] Wherein, V0 is the displacement of the cylinder, V1 is the volume of the cavity, R1, R2, and R3 are the radii of the plurality of flange exhaust holes, and K is a preset coefficient.

[0025] In some embodiments, when the first exhaust port, the second exhaust port, and the muffler exhaust port are all circular holes:

[0026] The radius d1 of the muffler exhaust port satisfies:

[0027] (d1) 2 =K×[π(R1)] 2 +π(R2) 2 ]×V0 / (V1×π);

[0028] Wherein, V0 is the displacement of the cylinder, V1 is the volume of the cavity (302), R1 is the radius of the first exhaust port, R2 is the radius of the second exhaust port, and K is a preset coefficient.

[0029] In some embodiments, the preset coefficient K is 2.5 to 4.5.

[0030] In some embodiments, the muffler includes an end wall and a side wall surrounding the periphery of the end wall, the end wall and the side wall forming the cavity, and the muffler exhaust port is located on the end wall.

[0031] In some embodiments, the compressor is a rotary compressor.

[0032] In some embodiments, an air conditioner is provided, comprising:

[0033] The aforementioned compressor.

[0034] The solution provided by this utility model has the following advantages compared with the prior art:

[0035] By designing the muffler exhaust port opening area in the compressor to be positively correlated with the cylinder displacement and the flange exhaust port opening area, and negatively correlated with the muffler cavity volume, the design ensures that the muffler exhaust port opening area and the flange exhaust port opening area are neither too large nor too small, but within a suitable range. This prevents the muffler exhaust port opening area from being too large, which would result in insufficient resistance to muffler discharge and thus inadequate noise reduction. Conversely, it prevents the muffler exhaust port opening area from being too small, which would increase the resistance to compressed gas discharge from the muffler, increase the vibration of the gas within the muffler, and prevent discharge, thus increasing noise. The design of the muffler exhaust port opening area effectively reduces cylinder aerodynamic noise, keeping the noise level within a low range. Attached Figure Description

[0036] The accompanying drawings, as part of this utility model, are used to provide a further understanding of the present utility model. The illustrative embodiments and descriptions of the present utility model are used to explain the present utility model, but do not constitute an undue limitation of the present utility model. Obviously, the drawings described below are merely some embodiments; those skilled in the art can obtain other drawings based on these drawings without creative effort. In the drawings:

[0037] Figure 1 This is a main sectional view of the compressor shown in an embodiment of the present invention;

[0038] Figure 2 This is a partial main sectional view of the compressor shown in an embodiment of the present invention;

[0039] Figure 3 This is a main sectional view of the muffler shown in an embodiment of the present invention;

[0040] Figure 4 This is a top sectional view of the muffler shown in an embodiment of the present invention;

[0041] Figure 5 This is a top view of the cylinder shown in an embodiment of the present invention;

[0042] Figure 6 This is a front view of the cylinder shown in an embodiment of the present invention;

[0043] Figure 7 This is a diagram showing the energy efficiency relationship of the compressor under different values ​​of k, as illustrated in this embodiment of the invention.

[0044] Figure 8This is a diagram showing the noise relationship of the compressor under different values ​​of k, as illustrated in this embodiment of the invention.

[0045] In the diagram: 101-First cylinder, 102-Second cylinder, 2-Flange, 201-Flange exhaust port, 2011-First exhaust port, 2012-Second exhaust port, 202-First flange, 203-Second flange, 3-Muffler, 301-Muffler exhaust port, 302-Cavity, 3031-End wall, 3032-Side wall, 304-First muffler, 305-Second muffler, 4-Baffle.

[0046] It should be noted that these accompanying drawings and textual descriptions are not intended to limit the scope of the present invention in any way, but rather to illustrate the concept of the present invention to those skilled in the art by referring to specific embodiments. Detailed Implementation

[0047] In the description of this utility model, it should be noted that the terms "inner" and "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings. They are only for the convenience of describing this utility model 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. Therefore, they should not be construed as limitations on this utility model.

[0048] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," "contact," and "communication" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0049] When refrigerant flows in a pipe, its velocity is determined by the mass flow rate, the pipe cross-sectional area, and the refrigerant density. The mass flow rate formula is: v = m / (ρ*A), where m represents the mass flow rate (kg / s), ρ is the density (kg / m³), A is the pipe cross-sectional area (m²), and v is the gas velocity (m / s). At 25℃, because R290 refrigerant has a lower density than R32, its flow rate is faster. Furthermore, since the volumetric cooling capacity of R290 refrigerant is approximately 87% that of R32, and the R290 charge is 0.4 to 0.65 times that of R32 models, to achieve the same cooling capacity, the discharge volume of a rolling rotor compressor using R290 refrigerant needs to be more than 70% larger than that using R32. However, currently, the ratio of the total area of ​​the compressor's muffler exhaust port to the exhaust ports of the upper and lower flanges is too small, resulting in a significant exhaust pressure drop and a reduction in the overall energy efficiency of the compressor.

[0050] Based on this, the following embodiments are proposed:

[0051] Example 1

[0052] like Figure 1 , 2 As shown, this embodiment provides a compressor, including:

[0053] cylinder;

[0054] Flange 2 is sealed and assembled on the cylinder. Flange 2 has a flange vent hole 201 that communicates with the cylinder to discharge gas from the cylinder.

[0055] The silencer 3 is located on the exhaust side of the flange exhaust port 201. The silencer 3 has a cavity 302 that communicates with the flange exhaust port 201. The silencer 3 has a silencer exhaust port 301 that communicates with the cavity 302 for discharging the gas in the cavity 302.

[0056] The opening area of ​​the muffler exhaust port 301 is positively correlated with the opening area of ​​the flange exhaust port 201, the opening area of ​​the muffler exhaust port 301 is negatively correlated with the volume of the cavity 302, and the opening area of ​​the muffler exhaust port 301 is positively correlated with the displacement of the cylinder.

[0057] Hydrocarbon refrigerants, such as R290, possess excellent thermophysical properties and have a negligible environmental impact, making them one of the most promising alternative refrigerants. However, with increasing concern about environmental issues such as air pollution, ozone layer depletion, and global warming, and given that R32 and R410A currently have global warming potentials (GWPs) as high as 675 and 2088 respectively, they also face the challenge of being phased out. Therefore, natural refrigerants such as R290, CO2, NH3, and R1270 will eventually replace short-term hydrofluorocarbons and chlorofluorocarbons. R290, also known as propane, is a new type of natural refrigerant with extremely high environmental protection characteristics. R290 has an ozone depletion potential of 0 and a GWP of only 3, meaning it has no destructive effect on the ozone layer and a minimal impact on the greenhouse effect of the Earth's atmosphere. Because R290 refrigerant has a lower density than R32 refrigerant and a faster refrigerant flow rate, the displacement of a compressor using R290 refrigerant is more than 70% larger than that using R32 refrigerant, and the refrigerant discharge speed is faster. In this embodiment, the compressor proposed is designed to take into account the characteristics of hydrocarbon refrigerants, such as R290 refrigerant. The opening area of ​​the muffler exhaust port 301 on the muffler 3 is positively correlated with the cylinder displacement and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the cavity 302 of the muffler 3. This ensures that the opening area of ​​the muffler exhaust port 301 on the muffler 3 is not relatively small, which would increase the resistance of the compressed gas in the cylinder to be discharged from the muffler 3, resulting in greater gas power consumption and lower cylinder volumetric efficiency. The compressor proposed in this embodiment keeps the cylinder volumetric efficiency in a high range, which can effectively reduce the aerodynamic noise of the cylinder in the compressor, thereby effectively improving the energy efficiency ratio of the compressor.

[0058] The opening area of ​​the muffler exhaust port 301 on the muffler 3 is positively correlated with the cylinder displacement and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the cavity 302 of the muffler 3. Therefore, the larger the volume of the cavity 302 of the muffler 3, the larger the buffer space for the refrigerant discharged from the flange exhaust port 201 on the flange 2; conversely, the smaller the volume of the cavity 302 of the muffler 3, the smaller the buffer space for the refrigerant discharged from the flange exhaust port 201 on the flange 2. By designing the opening area of ​​the muffler exhaust port 301 on the muffler 3 to be negatively correlated with the volume of the cavity 302 of the muffler 3, the opening area of ​​the muffler exhaust port 301 on the muffler 3 is better matched with the volume of the cavity 302 of the muffler 3. When the volume of the cavity 302 of the muffler 3 is small, the opening area of ​​the muffler exhaust port 301 on the muffler 3 is designed to be larger so that the refrigerant can be discharged as soon as possible, so as to avoid increasing the flow resistance and power.

[0059] By designing the opening area of ​​the muffler exhaust port 301 on the muffler 3 to be positively correlated with the cylinder displacement and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the muffler 3 cavity 302, a more reasonable opening area of ​​the muffler exhaust port 301 on the muffler 3 can be designed based on the cylinder displacement, the opening area of ​​the flange exhaust port 201, and the volume of the muffler 3 cavity 302. This effectively improves compressor noise and increases compressor power, while reducing research costs in designing the R290 compressor pump body structure. It also solves the problem of noise and significant compressor discharge pressure drop in existing R290 refrigerant compressors due to the small ratio of the muffler exhaust port area.

[0060] In this embodiment, a compressor for low-density hydrocarbon refrigerant is provided, wherein the flange 2 includes a flange exhaust port 201 for discharging gas inside the cylinder, and a silencer 3 is also provided downstream of the airflow of the flange 2, the silencer 3 including a silencer exhaust port 301 for discharging gas inside its cavity 302.

[0061] Preferably, the shape of the flange vent 201 can be circular, "D" shaped, crescent-shaped, or waist-shaped; the silencer vent 301 can be circular, "D" shaped, crescent-shaped, or waist-shaped.

[0062] Preferably, one flange vent 201 or multiple flange vent 201 are provided; one silencer vent 301 or multiple silencer vent 301 are provided.

[0063] When multiple flange vent holes 201 and multiple muffler vent holes 301 are provided, the opening area of ​​the muffler vent hole 301 on the muffler 3 refers to the total opening area of ​​the multiple muffler vent holes 301, and the opening area of ​​the flange vent hole 201 refers to the total opening area of ​​the multiple flange vent holes 201.

[0064] In this embodiment, the compressor's muffler exhaust port 301 on the muffler 3 has an opening area that is positively correlated with the cylinder displacement and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the muffler 3's cavity 302. This ensures that the opening area of ​​the muffler exhaust port 301 on the muffler 3 and the opening area of ​​the flange exhaust port 201 on the flange 2 are neither too large nor too small, but within a suitable range. This prevents the opening area of ​​the muffler exhaust port 301 on the muffler 3 from being relatively too large. The large size of the exhaust port 301 on the flange 2 results in the compressed gas being discharged without the necessary resistance to reduce noise, thus failing to achieve the desired noise reduction. When the opening area of ​​the exhaust port 301 on the muffler is relatively large, it will significantly reduce the impedance of the muffler structure, making it difficult for the muffler 3 and the flange 2 to achieve a noise reduction effect through changes in cross-sectional area. In other words, the opening area of ​​the exhaust port 301 on the muffler 3 is too large, which is equivalent to directly discharging compressed gas, making it impossible to further reduce noise at the exhaust port 301.

[0065] In this embodiment, the opening area of ​​the muffler exhaust port 301 on the muffler 3 is positively correlated with the displacement of the cylinder and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the cavity 302 of the muffler 3. This design ensures that the opening area of ​​the muffler exhaust port 301 on the muffler 3 is not relatively small, which would increase the resistance of compressed gas from the muffler 3, increase the vibration of gas in the muffler 3, prevent it from being discharged, and lead to increased noise. The design of the opening area of ​​the muffler exhaust port 301 on the muffler 3 can effectively reduce the aerodynamic noise of the cylinder, keeping the noise level within a low range.

[0066] Optionally, such as Figure 1 , 2 As shown, in one implementation of this embodiment,

[0067] The cylinder includes a first cylinder 101 and a second cylinder 102;

[0068] The flange 2 includes a first flange 202 and a second flange 203;

[0069] The first flange 202 corresponds to the first cylinder 101. The flange exhaust port 201 includes a first exhaust port 2011 opened on the first flange 202 and communicating with the first cylinder 101 for discharging gas in the first cylinder 101, and a second exhaust port 2012 opened on the second flange 102 and communicating with the second cylinder 102 for discharging gas in the second cylinder 102.

[0070] The muffler 3 includes a first muffler 304 and a second muffler 305;

[0071] The first muffler 304 is located on the exhaust side of the first exhaust port 2011. The first muffler 304 has a first cavity communicating with the first exhaust port 2011, and a muffler exhaust port 301 communicating with the first cavity is provided on the first muffler 304. The second muffler 305 is located on the exhaust side of the second exhaust port 2012. The second muffler 305 has a second cavity communicating with the second exhaust port 2012. The second cavity is communicating with the first cavity. The muffler exhaust port 301 is used to discharge the gas in the first cavity and the second cavity.

[0072] The opening area of ​​the muffler exhaust port 301 is positively correlated with the total opening area of ​​the first exhaust port 2011 and the second exhaust port 2012, the opening area of ​​the muffler exhaust port 301 is negatively correlated with the total volume of the first cavity and the second cavity, and the opening area of ​​the muffler exhaust port 301 is positively correlated with the total displacement of the first cylinder 101 and the second cylinder 102.

[0073] In this embodiment, preferably, the compressor is a rotary compressor. The compressor provided in this embodiment is a dual-cylinder rotary compressor. During operation, the compressor gas generated by the first cylinder 101 is discharged from the first exhaust port 2011 on the first flange 202 into the first cavity of the first silencer 304, and then discharged from the silencer exhaust port 301 on the first silencer 304. The compressor gas generated by the second cylinder 102 is discharged from the second exhaust port 2012 on the second flange 203 into the second cavity of the second silencer 305. The second cavity is connected to the first cavity through a compressor internal through-hole. The gas in the second cavity enters the first cavity and is discharged from the silencer exhaust port 301 on the first silencer 304.

[0074] In the compressor proposed in this embodiment, the opening area of ​​the muffler exhaust port 301 is positively correlated with the total exhaust volume of the first cylinder 101 and the second cylinder 102, and the total opening area of ​​the first exhaust port 2011 and the second exhaust port 2012, and negatively correlated with the total volume of the first cavity and the second cavity. This ensures that the opening area of ​​the muffler exhaust port 301 is neither too large nor too small, but falls within a suitable range, thus maintaining the opening area of ​​the muffler exhaust port 301 from being relatively... The large size of the exhaust port 301 of the muffler results in the compressed gas discharged from the first exhaust port 2011 and the second exhaust port 2012 not receiving the necessary resistance to reduce noise, thus failing to reduce noise as required. When the opening area of ​​the muffler exhaust port 301 is relatively large, it will significantly reduce the impedance of the muffler structure, making it difficult for the first muffler to achieve a noise reduction effect through changes in cross-sectional area with the first flange 202 and the second flange 203. In other words, the opening area of ​​the muffler exhaust port 301 on the first muffler is too large, which is equivalent to directly discharging compressed gas, making it impossible to further reduce noise at the muffler exhaust port 301.

[0075] In the compressor proposed in this embodiment, the opening area of ​​the muffler exhaust port 301 is positively correlated with the total exhaust volume of the first cylinder 101 and the second cylinder 102, and the total opening area of ​​the first exhaust port 2011 and the second exhaust port 2012, and negatively correlated with the total volume of the first cavity and the second cavity. This design ensures that the opening area of ​​the muffler exhaust port 301 is not relatively small, which would increase the resistance of the compressed gas from the first muffler, increase the oscillation effect of the gas in the first muffler and prevent it from being discharged, and lead to increased noise. The design of the opening area of ​​the muffler exhaust port 301 on the first muffler can effectively reduce the aerodynamic noise of the first cylinder 101 and the second cylinder 102, so that the noise is within a low range.

[0076] Optionally, such as Figure 1-4 As shown, in one implementation of this embodiment,

[0077] When both the flange vent 201 and the muffler vent 301 are circular holes:

[0078] The radius of the muffler exhaust port 301 is d, in mm, and satisfies:

[0079] d 2 =K×(πR) 2 )×V0 / (V1×π);

[0080] Where V0 is the displacement of the cylinder, in mm. 3 V1 is the volume of the cavity 302, in mm. 3R is the radius of the flange vent hole 201 in mm, and K is a preset coefficient with no unit.

[0081] In this embodiment, the cylinder displacement V0 = [π(r1)]. 2 -π(r2) 2 ]×H, such as Figure 5 , 6 As shown, r1 is the inner diameter of the cylinder, r2 is the outer diameter of the cylinder roller, and H is the height of the cylinder.

[0082] Furthermore, in this embodiment:

[0083] When the first exhaust port 2011, the second exhaust port 2012, and the muffler exhaust port 301 are all circular holes:

[0084] The radius of the muffler exhaust port 301 is d1, in mm, and satisfies:

[0085] (d1) 2 =K×[π(R1)] 2 +π(R2) 2 ]×V0 / (V1×π);

[0086] Where V0 is the displacement of the cylinder, in mm. 3 V1 is the volume of the cavity 302, in mm. 3 R1 is the radius of the first exhaust hole 2011 in mm, R2 is the radius of the second exhaust hole 2012 in mm, and K is a preset coefficient with no unit.

[0087] Preferably, K is between 2.5 and 4.5.

[0088] In this embodiment, when both the flange vent 201 and the muffler vent 301 are circular holes, according to d 2 =K×(πR2)×V0 / (V1×π), which can be used to directly calculate the radius of the muffler exhaust port 301 given the cylinder displacement, the volume of the cavity 302, and the radius of the flange exhaust port 201.

[0089] The radius of the muffler exhaust port 301 calculated according to this formula ensures that the opening area of ​​the muffler exhaust port 301 and the opening area of ​​the flange exhaust port 201 on the flange 2 are neither too large nor too small, but within a suitable range. This prevents the opening area of ​​the muffler exhaust port 301 on the muffler 3 from being relatively large, which would prevent the compressed gas discharged from the flange exhaust port 201 on the flange 2 from receiving the necessary resistance and noise reduction. If the opening area of ​​the muffler exhaust port 301 is relatively large, it will significantly reduce the impedance of the muffler structure, making it difficult for the muffler 3 and the flange 2 to achieve a noise reduction effect through changes in cross-sectional area. In other words, if the opening area of ​​the muffler exhaust port 301 on the muffler 3 is too large, it is equivalent to directly discharging compressed gas, and further noise reduction cannot be achieved through the muffler exhaust port 301.

[0090] Meanwhile, the radius of the muffler exhaust port 301 calculated according to this formula ensures that the opening area of ​​the muffler exhaust port 301 is positively correlated with the displacement of the cylinder and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the cavity 302 of the muffler 3. This also ensures that the opening area of ​​the muffler exhaust port 301 on the muffler 3 is not relatively small, which would increase the resistance of compressed gas from the muffler 3, increase the oscillation effect of gas in the muffler 3 and prevent it from being discharged, thus increasing the noise. The design of the opening area of ​​the muffler exhaust port 301 on the muffler 3 can effectively reduce the aerodynamic noise of the cylinder, keeping the noise level within a low range.

[0091] In this embodiment, the compressor's energy efficiency (COP) and noise (dB) are tested, such as... Figure 7 , 8 As shown, when K is between 2.5 and 4.5, the compressor has a high energy efficiency and a low noise level, achieving a better working condition.

[0092]

[0093]

[0094] Optionally, such as Figure 1-4 As shown, in one implementation of this embodiment,

[0095] The flange vent 201 is provided with multiple vents and / or the muffler vent 301 is provided with multiple vents.

[0096] Both the flange vent 201 and the muffler vent 301 are circular holes. Multiple flange vents 201 and multiple muffler vents 301 are provided.

[0097] The radii of the plurality of muffler exhaust holes 301 are d1, d2, d3..., respectively, in mm, and satisfy the following:

[0098]

[0099] Where V0 is the displacement of the cylinder, in mm. 3 V1 is the volume of the cavity 302, in mm. 3 R1, R2, and R3 are the radii of the plurality of flange vent holes 201, in mm, and K is a preset coefficient with no unit.

[0100] In this embodiment, when all three flange vent holes 201 and muffler vent holes 301 are circular holes, and multiple flange vent holes 201 and multiple muffler vent holes 301 are provided, according to...

[0101] Given the cylinder displacement, the volume of the cavity 302, and the radii of the multiple flange exhaust holes 201, the radii of the multiple muffler exhaust holes 301 can be directly calculated using the above formula. By reasonably allocating the multiple muffler exhaust holes 301, the radii of the multiple muffler exhaust holes 301 can satisfy the above formula.

[0102] The opening areas of the multiple muffler exhaust ports 301 and the multiple flange exhaust ports 201 are kept within a suitable range, neither too large nor too small. This ensures that the opening areas of the multiple muffler exhaust ports 301 are not too large, which would prevent the compressed gas discharged from the multiple flange exhaust ports 201 from receiving the necessary resistance and noise reduction. If the opening areas of the multiple muffler exhaust ports 301 are too large, it would significantly reduce the impedance of the muffler structure, making it difficult for the muffler 3 and flange 2 to achieve a noise reduction effect through changes in cross-sectional area. In other words, if the opening areas of the multiple muffler exhaust ports 301 are too large, it is equivalent to directly discharging compressed gas, making further noise reduction impossible through the multiple muffler exhaust ports 301.

[0103] Meanwhile, the radii of the multiple muffler exhaust holes 301 calculated according to this formula ensure that the opening area of ​​the multiple muffler exhaust holes 301 is positively correlated with the displacement of the cylinder and the opening area of ​​the multiple flange exhaust holes 201, and negatively correlated with the volume of the cavity 302 of the muffler 3. This also ensures that the opening area of ​​the multiple muffler exhaust holes 301 is not relatively small, which would increase the resistance of compressed gas from the muffler 3, increase the vibration of gas in the muffler 3 and prevent it from being discharged, thus increasing the noise. The design of the opening area of ​​the multiple muffler exhaust holes 301 can effectively reduce the aerodynamic noise of the cylinder, keeping the noise level within a low range.

[0104] Optionally, such as Figure 3 , 4 As shown, in one implementation of this embodiment,

[0105] The muffler 3 includes an end wall 3031 and a side wall 3032 surrounding the end wall 3031. The end wall 3031 and the side wall 3032 enclose the cavity 302, and the muffler exhaust port 301 is located on the end wall 3031.

[0106] In this embodiment, the silencer 3 has a compact structure and high space utilization. It forms a cavity 302 by enclosing the end wall 3031 and the peripheral side wall 3032. The whole is a closed cavity structure, which can realize the silencer function in a limited space. It is suitable for the compact installation environment inside the compressor and reduces the occupation of the overall volume of the equipment.

[0107] The muffler 3 has a reasonable airflow path, which improves the muffler efficiency. The muffler exhaust port 301 is set on the end wall 3031. When the airflow enters the cavity 302, the cavity 302 enclosed by the end wall 3031 and the side wall 3032 can effectively buffer and reflect the airflow. The volume of the cavity 302 is used to expand the airflow diffusion space, reduce airflow pulsation and turbulence noise, and enhance the muffler effect.

[0108] The silencer 3 has strong structural stability. The enclosure design of the end wall 3031 and the side wall 3032 makes the shell of the silencer 3 a rigid whole, which can withstand the vibration and pressure impact during the operation of the compressor, reduce the attenuation of the silencing performance caused by structural deformation, and improve the reliability of long-term use.

[0109] The silencer 3 is easy to integrate and assemble. The integrated housing simplifies the connection between the silencer 3 and other compressor components, reducing the complexity of the manufacturing process.

[0110] Example 2

[0111] In this embodiment, an air conditioner is provided, including:

[0112] The compressor in Example 1.

[0113] The air conditioner proposed in this embodiment includes the compressor in Embodiment 1. The opening area of ​​the muffler exhaust port 301 on the muffler 3 is positively correlated with the displacement of the cylinder and the opening area of ​​the flange exhaust port 201, and negatively correlated with the volume of the cavity 302 of the muffler 3. This ensures that the opening area of ​​the muffler exhaust port 301 on the muffler 3 and the opening area of ​​the flange exhaust port 201 on the flange 2 are neither too large nor too small, but within a suitable range, thereby maintaining the opening area of ​​the muffler exhaust port 301 on the muffler 3. As for the relatively large opening area of ​​the muffler exhaust port 301, which causes the compressed gas discharged from the flange 2 exhaust port 201 to not receive the necessary resistance and thus not reduce the noise as required, the relatively large opening area of ​​the muffler exhaust port 301 will significantly reduce the impedance of the muffler structure. This makes it difficult for the muffler 3 and the flange 2 to achieve a noise reduction effect through changes in cross-sectional area. In other words, the opening area of ​​the muffler exhaust port 301 on the muffler 3 is too large, which is equivalent to directly discharging the compressed gas, and it is impossible to further reduce the noise at the muffler exhaust port 301.

[0114] In this embodiment, the compressor's muffler exhaust port 301 opening area is positively correlated with the cylinder displacement and the flange exhaust port 201 opening area, and negatively correlated with the volume of the muffler 3 cavity 302. This design ensures that the opening area of ​​the muffler exhaust port 301 is not too small, which would increase the resistance to compressed gas discharge from the muffler 3, increase the oscillation of gas within the muffler 3, and prevent discharge, thus increasing noise. The design of the muffler exhaust port 301 opening area effectively reduces cylinder aerodynamic noise, keeping the noise level within a low range.

[0115] Since the air conditioner includes the compressor in Embodiment 1, it has all the beneficial effects of the compressor in Embodiment 1.

[0116] In summary, the ingenious design of the compressor lies in:

[0117] By designing the muffler exhaust port opening area in the compressor to be positively correlated with the cylinder displacement and the flange exhaust port opening area, and negatively correlated with the muffler cavity volume, the design ensures that the muffler exhaust port opening area and the flange exhaust port opening area are neither too large nor too small, but within a suitable range. This prevents the muffler exhaust port opening area from being too large, which would result in insufficient resistance to muffler discharge and thus inadequate noise reduction. Conversely, it prevents the muffler exhaust port opening area from being too small, which would increase the resistance to compressed gas discharge from the muffler, increase the vibration of the gas within the muffler, and prevent discharge, thus increasing noise. The design of the muffler exhaust port opening area effectively reduces cylinder aerodynamic noise, keeping the noise level within a low range.

[0118] It can be further understood that in this disclosure, "many" refers to two or more, and other quantifiers are similar. "And / or" describes the relationship between related objects, indicating that three relationships can exist; for example, A and / or B can represent: A alone, A and B simultaneously, and B alone. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. The singular forms "a," "the," and "the" are also intended to include the plural forms unless the context clearly indicates otherwise.

[0119] It is further understood that the terms "first," "second," etc., are used to describe various types of information, but this information should not be limited to these terms. These terms are only used to distinguish information of the same type from one another, and do not indicate a specific order or degree of importance. In fact, the expressions "first," "second," etc., are completely interchangeable. For example, without departing from the scope of this disclosure, first information can also be referred to as second information, and similarly, second information can also be referred to as first information.

[0120] It is further understood that although operations are described in a specific order in the accompanying drawings in the embodiments of this disclosure, this should not be construed as requiring these operations to be performed in the specific order or serial order shown, or requiring all of the shown operations to be performed to obtain the desired result. In certain environments, multitasking and parallel processing may be advantageous.

[0121] Other embodiments of this disclosure will readily occur to those skilled in the art upon consideration of the specification and practice of the utility models disclosed herein. This application is intended to cover any variations, uses, or adaptations of this disclosure that follow the general principles of this disclosure and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of this disclosure are indicated by the claims of this application.

[0122] It should be understood that this disclosure is not limited to the precise structures described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this disclosure is limited only by the appended claims.

Claims

1. A compressor, characterized in that, include: cylinder; Flange (2), the flange (2) is sealed and assembled on the cylinder, and the flange (2) has a flange exhaust hole (201) communicating with the cylinder (1) for discharging the gas in the cylinder (1); A silencer (3) is located on the exhaust side of the flange exhaust port (201). The silencer (3) has a cavity (302) communicating with the flange exhaust port (201). The silencer (3) has a silencer exhaust port (301) communicating with the cavity (302) for discharging the gas in the cavity (302). The opening area of ​​the muffler exhaust port (301) is positively correlated with the opening area of ​​the flange exhaust port (201), the opening area of ​​the muffler exhaust port (301) is negatively correlated with the volume of the cavity (302), and the opening area of ​​the muffler exhaust port (301) is positively correlated with the displacement of the cylinder (1).

2. The compressor according to claim 1, characterized in that, The cylinder includes a first cylinder (101) and a second cylinder (102); The flange (2) includes a first flange (202) and a second flange (203); The first flange (202) corresponds to the first cylinder (101). The flange exhaust port (201) includes a first exhaust port (2011) opened on the first flange (202) and communicating with the first cylinder (101) for discharging gas in the first cylinder (101), and a second exhaust port (2012) opened on the second flange (203) and communicating with the second cylinder (102) for discharging gas in the second cylinder (102). The muffler (3) includes a first muffler (304) and a second muffler (305); The first muffler (304) is located on the exhaust side of the first exhaust port (2011). The first muffler (304) has a first cavity communicating with the first exhaust port (2011). The first muffler (304) has a muffler exhaust port (301) communicating with the first cavity. The second muffler (305) is located on the exhaust side of the second exhaust port (2012). The second muffler (305) has a second cavity communicating with the second exhaust port (2012). The second cavity is communicating with the first cavity. The muffler exhaust port (301) is used to discharge the gas in the first cavity and the second cavity. The opening area of ​​the muffler exhaust port (301) is positively correlated with the total opening area of ​​the first exhaust port (2011) and the second exhaust port (2012), the opening area of ​​the muffler exhaust port (301) is negatively correlated with the total volume of the first cavity and the second cavity, and the opening area of ​​the muffler exhaust port (301) is positively correlated with the total displacement of the first cylinder (101) and the second cylinder (102).

3. The compressor according to claim 1, characterized in that, When both the flange vent (201) and the muffler vent (301) are circular holes: The radius of the muffler exhaust port (301) is d, which satisfies: d 2 =K×(πR 2 )×V0 / (V1×π); Wherein, V0 is the displacement of the cylinder, V1 is the volume of the cavity (302), R is the radius of the flange exhaust hole (201), and K is a preset coefficient.

4. The compressor according to claim 1, characterized in that, The flange vent (201) is provided in multiple locations and / or the muffler vent (301) is provided in multiple locations.

5. The compressor according to claim 4, characterized in that, Both the flange vent (201) and the muffler vent (301) are circular holes. Multiple flange vents (201) and multiple muffler vents (301) are provided. The radii of the plurality of muffler exhaust ports (301) are d1, d2, d3, ..., respectively, satisfying: Wherein, V0 is the displacement of the cylinder, V1 is the volume of the cavity (302), R1, R2, and R3 are the radii of the plurality of flange exhaust holes (201) respectively, and K is a preset coefficient.

6. The compressor according to claim 2, characterized in that, When the first exhaust port (2011), the second exhaust port (2012), and the muffler exhaust port (301) are all circular holes: The radius of the muffler exhaust port (301) is d1, which satisfies: (d1) 2 =K×[π(R1) 2 +π(R2) 2 ]×V0 / (V1×π); Wherein, V0 is the displacement of the cylinder, V1 is the volume of the cavity (302), R1 is the radius of the first exhaust port (2011), R2 is the radius of the second exhaust port (2012), and K is a preset coefficient.

7. The compressor according to any one of claims 3, 5, and 6, characterized in that, The preset coefficient K is between 2.5 and 4.

5.

8. The compressor according to claim 1, characterized in that, The muffler (3) includes an end wall (3031) and a side wall (3032) surrounding the end wall (3031). The end wall (3031) and the side wall (3032) enclose the cavity (302). The muffler exhaust port (301) is located on the end wall (3031).

9. An air conditioner, characterized in that, include: The compressor as described in any one of claims 1-8.

10. The air conditioner according to claim 9, characterized in that, The refrigerant used in the air conditioner is a hydrocarbon refrigerant.

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