Silencer for compressor and compressor

Abstract

The utility model relates to the technical field of compressors, and discloses a silencer for a compressor, the silencer comprises a shell and a filter part, the shell is provided with an inner cavity, and the shell is provided with an air inlet hole and an air outlet hole which are communicated with the inner cavity; the filter part is arranged in the inner cavity and corresponds to the air inlet, and exhaust airflow flows into the inner cavity through the air inlet and flows out of the air outlet after flowing through the filter part; wherein the filtering part comprises a diffusion layer and an energy dissipation layer, the diffusion layer comprises a first filter screen, the energy dissipation layer is filled with porous sound absorption particles, and the porous sound absorption particles can move within the range of the energy dissipation layer under the action of exhaust airflow so as to dissipate sound energy and airflow pulsation kinetic energy. The filtering piece is arranged to be of a multi-layer structure, the synergistic effect between the flow dispersing layer and the energy dispersing layer is improved, and the exhaust noise of the compressor can be reduced while the oil spitting rate is reduced. The utility model further discloses the compressor.

Description

Technical Field

[0001] This application relates to the field of compressor technology, specifically to a muffler and compressor for use in compressors. Background Technology

[0002] Currently, after the existing rolling rotor compressor completes compression, the exhaust gas carries the refrigerant and is discharged through the exhaust port, which reduces the amount of refrigeration oil in the compressor. This results in poor lubrication of the internal structure of the compressor during rotation and increases the power consumption of the compressor.

[0003] The related technology discloses a compressor and refrigeration equipment. The compressor includes a pump body assembly, a muffler, and an oil separator structure. The muffler has a discharge port. The oil separator structure includes an oil separator housing and a filter screen. The oil separator housing is connected to the muffler or the pump body assembly. The oil separator housing covers the outlet side of the discharge port and forms an inner cavity. The oil separator housing has an exhaust port communicating with the inner cavity and the compressor's outer casing. The filter screen is connected to the oil separator housing and covers the exhaust port. The filter screen filters the refrigeration oil, allowing only gaseous refrigerant to pass through, thereby effectively separating the refrigeration oil and gaseous refrigerant, reducing oil discharge, and improving the compressor's reliability.

[0004] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art:

[0005] In related technologies, although refrigeration oil and gaseous refrigerant can be effectively separated, the pulsation of the airflow when the exhaust gas passes through the filter screen will cause the filter screen to vibrate, thereby generating noise.

[0006] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Utility Model Content

[0007] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0008] This disclosure provides a muffler and compressor for a compressor, which reduces the compressor's exhaust noise while lowering the oil discharge rate.

[0009] According to a first aspect of the present invention, a muffler for a compressor is provided, comprising a housing and a filter element. The housing has an inner cavity and is provided with an air inlet and an air outlet communicating with the inner cavity. The filter element is disposed in the inner cavity and corresponds to the air inlet. Exhaust airflow flows into the inner cavity through the air inlet and flows out through the air outlet after passing through the filter element. The filter element includes a diffuser layer and an energy dissipation layer. The diffuser layer includes a first filter screen, and the energy dissipation layer is filled with porous sound-absorbing particles. The porous sound-absorbing particles can move under the action of the exhaust airflow to dissipate sound energy and airflow pulsation kinetic energy.

[0010] Optionally, the diffuser layer further includes a second filter screen, wherein the first and second filters screens are spaced apart along the direction from the air inlet to the air outlet, and the energy dissipation layer is disposed between the first and second filters screens, wherein porous sound-absorbing particles can move between the first and second filters screens to dissipate sound energy and airflow pulsation kinetic energy.

[0011] Optionally, the first and second filters adopt an elastic membrane structure.

[0012] Optionally, the first filter screen adopts a one-way filter screen structure to allow the exhaust airflow to flow unidirectionally from the air inlet to the air outlet; and / or, the second filter screen adopts a one-way filter screen structure to allow the exhaust airflow to flow unidirectionally from the air inlet to the air outlet.

[0013] Optionally, the porous sound-absorbing particles are made of polyvinyl alcohol-carbon black material; and / or, the porous sound-absorbing particles are made of hollow spherical foam material.

[0014] Optionally, the housing includes: a bottom wall located below the inner cavity, with an oil return channel at the radial end of the bottom wall along the inner cavity, the oil return channel communicating with the inner cavity, the middle part of the bottom wall protruding towards the inner cavity, and the end of the bottom wall inclined downward away from the inner cavity.

[0015] Optionally, the housing includes: a top wall with an air outlet; and a bottom wall with an air inlet; wherein an inner cavity is formed between the top wall and the bottom wall, the inner diameter of the inner cavity being larger than the diameter of the air inlet, and the inner diameter of the inner cavity being larger than the diameter of the air outlet.

[0016] Optionally, the diameter of the air inlet gradually increases along the direction of the air inlet toward the inner cavity; and / or, the filter extends radially along the inner cavity, and the size of the filter is adapted to the inner diameter of the inner cavity.

[0017] Optionally, the muffler for the compressor further includes a cooling pipe disposed in the inner cavity, the cooling pipe being connected to a low-temperature source outside the housing to reduce the temperature of the cooling pipe.

[0018] According to a second aspect of the present invention, a compressor is provided, comprising: a bearing assembly including a bearing having an exhaust port; and a muffler for the compressor as described in any of the above-disclosed embodiments, wherein the housing of the muffler is disposed on the end face of the bearing, and the air inlet of the muffler corresponds to the exhaust port of the bearing, so that the exhaust gas flow in the exhaust port flows out and enters the inner cavity through the air inlet of the muffler.

[0019] The muffler and compressor for compressors provided in this disclosure can achieve the following technical effects:

[0020] By setting the filter element to a multi-layer structure, the synergistic effect between the diffuser layer and the energy dissipation layer is improved, which can reduce the oil discharge rate while reducing the compressor's exhaust noise. When the exhaust airflow passes through the diffuser layer, the first filter screen can intercept the refrigerant oil droplets, separating the refrigerant oil droplets from the gaseous refrigerant in the exhaust airflow, allowing only the gaseous refrigerant to be discharged through the outlet, thus achieving oil-gas separation and reflux lubrication functions. This can reduce the compressor's oil discharge, thereby improving the lubrication effect within the compressor and reducing the compressor's power consumption. The porous structure of the porous sound-absorbing particles filled in the energy dissipation layer can effectively absorb the sound energy and airflow pulsation kinetic energy generated by the exhaust airflow movement. The first filter screen can also disperse the exhaust airflow, and the dispersed exhaust airflow can increase the contact area with the porous sound-absorbing particles, allowing the porous sound-absorbing particles to be more evenly distributed and move, thereby more effectively absorbing and dissipating sound energy and airflow pulsation kinetic energy. At the same time, the porous composite particles move under the impact of the exhaust airflow and continuously collide and dissipate sound energy and airflow pulsation kinetic energy, which can reduce the vibration caused by exhaust airflow pulsation. This can effectively reduce the exhaust noise of the compressor.

[0021] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0022] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0023] Figure 1 This is a schematic diagram of the structure of a compressor provided in an embodiment of this disclosure;

[0024] Figure 2 This is a schematic diagram of the assembly of a bearing assembly and a muffler provided in an embodiment of this disclosure;

[0025] Figure 3 This is a cross-sectional schematic diagram of a bearing assembly and a muffler assembled according to an embodiment of this disclosure;

[0026] Figure 4 This is a schematic diagram of the structure of a muffler provided in an embodiment of this disclosure;

[0027] Figure 5 This is a schematic diagram of the structure of a diffuser layer provided in an embodiment of this disclosure;

[0028] Figure 6 This is a partial schematic diagram of a filter element provided in an embodiment of this disclosure;

[0029] Figure 7 This is a partial schematic diagram of another filter element provided in an embodiment of this disclosure;

[0030] Figure 8 This is a cross-sectional schematic diagram of a cooling tube provided in an embodiment of this disclosure;

[0031] Figure 9 This is a cross-sectional schematic diagram of another cooling tube provided in an embodiment of this disclosure;

[0032] Figure 10 This is a schematic diagram of the structure of an internal cooling pipe provided in an embodiment of this disclosure;

[0033] Figure 11 This is a schematic diagram of the structure of a bearing assembly provided in an embodiment of this disclosure;

[0034] Figure 12 This is a schematic diagram of another bearing assembly provided in an embodiment of this disclosure;

[0035] Figure 13 This is a schematic diagram of another bearing assembly provided in an embodiment of this disclosure;

[0036] Figure 14 This is a cross-sectional schematic diagram of a bearing assembly provided in an embodiment of this disclosure;

[0037] Figure 15 This is a schematic diagram of the structure of a bearing provided in an embodiment of this disclosure;

[0038] Figure 16 This is a schematic diagram of the structure of another bearing provided in an embodiment of this disclosure;

[0039] Figure 17 This is a cross-sectional schematic diagram of a bearing provided in an embodiment of this disclosure;

[0040] Figure 18 yes Figure 17 An enlarged schematic diagram of part A shown.

[0041] Figure label:

[0042] 10: Compressor; 12: Silencer; 13: Casing; 14: Cooler;

[0043] 20: Bearing; 21: Exhaust port; 211: First exhaust hole; 212: Second exhaust hole; 213: First side exhaust channel; 214: Second side exhaust channel; 215: Side wall; 22: End face; 221: First end face; 222: Second end face; 223: Groove; 23: Heat transfer channel; 231: Heat transfer element;

[0044] 30: Exhaust component; 31: Exhaust valve; 311: First valve plate; 312: Second valve plate; 313: Connecting part; 32: Thermal drive element;

[0045] 40: Shell; 41: Inner cavity; 42: Air inlet; 43: Air outlet; 44: Bottom wall; 441: Oil return channel; 442: Middle section; 443: End; 45: Top wall;

[0046] 50: Filter element; 51: Diffuser layer; 511: First filter screen; 512: Second filter screen; 52: Energy dissipation layer; 521: Porous sound-absorbing particles;

[0047] 60: Cooling pipe; 601: Second end; 602: First end; 61: Internal cooling pipe; 611: Through hole; 62: External cooling pipe; 63: Cavity. Detailed Implementation

[0048] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0049] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0050] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0051] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0052] Unless otherwise stated, the term "multiple" means two or more.

[0053] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0054] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0055] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0056] Combination Figure 1-7 As shown, this disclosure provides a muffler 12 for a compressor 10, including a housing 40 and a filter element 50.

[0057] The housing 40 has an inner cavity 41 and an air inlet 42 and an air outlet 43 that communicate with the inner cavity 41. The filter element 50 is disposed in the inner cavity 41 and corresponds to the air inlet 42. The exhaust airflow flows into the inner cavity 41 through the air inlet 42 and flows out through the air outlet 43 after passing through the filter element 50. The filter element 50 includes a diffuser layer 51 and an energy dissipation layer 52. The diffuser layer 51 includes a first filter screen 511. The energy dissipation layer 52 is filled with porous sound-absorbing particles 521. The porous sound-absorbing particles 521 can move under the action of the exhaust airflow to dissipate sound energy and airflow pulsation kinetic energy.

[0058] The muffler 12 for compressor 10 provided in this embodiment of the present disclosure, by setting the filter element 50 to a multi-layer structure, enhances the synergistic effect between the diffuser layer 51 and the energy dissipation layer 52, thereby reducing the oil discharge rate and the exhaust noise of compressor 10. When the exhaust airflow passes through the diffuser layer 51, the first filter screen 511 can intercept the refrigerant oil droplets, separating the refrigerant oil droplets and gaseous refrigerant in the exhaust airflow, allowing only the gaseous refrigerant to be discharged through the outlet 43, thus achieving oil-gas separation and reflux lubrication functions. This reduces the oil discharge of compressor 10, thereby improving the lubrication effect within compressor 10 and reducing the power consumption of compressor 10. The porous structure of the porous sound-absorbing particles 521 filled in the energy dissipation layer 52 can effectively absorb the sound energy and airflow pulsation kinetic energy generated by the exhaust airflow movement. The first filter screen can also disperse the exhaust airflow, which increases the contact area with the porous sound-absorbing particles, allowing the porous sound-absorbing particles to be more evenly distributed and move, thereby more effectively absorbing and dissipating sound energy and airflow pulsation kinetic energy. Simultaneously, the porous composite particles move under the impact of the exhaust airflow, continuously colliding and dissipating sound energy and airflow pulsation kinetic energy, thus reducing the vibration caused by exhaust airflow pulsation. This effectively reduces the exhaust noise of the compressor 10. Furthermore, the porous sound-absorbing particles 521 collide with oil droplets in the exhaust airflow, altering the trajectory of the oil droplets, causing them to aggregate and form larger droplets, thereby separating the refrigerant oil from the exhaust airflow, further reducing the oil discharge of the compressor 10.

[0059] The energy dissipation layer 52 is filled with porous sound-absorbing particles 521, meaning it is filled with multiple porous sound-absorbing particles 521, rather than a single particle. The porous sound-absorbing particles 521 typically exist in the form of granules or small spheres, filling and moving within the energy dissipation layer 52. This allows the collective properties of the porous sound-absorbing particles 521 to be utilized, through their interaction and movement, to absorb and dissipate the acoustic energy and kinetic energy of the exhaust gas flow, achieving both noise reduction and oil droplet separation effects. This application does not limit the filling rate of the porous sound-absorbing particles 521 in the energy dissipation layer 52.

[0060] Optionally, combined Figure 4 and Figure 7 As shown, the diffuser layer 51 also includes a second filter 512. The first filter 511 and the second filter 512 are spaced apart along the direction from the air inlet 42 toward the air outlet 43. The energy dissipation layer 52 is disposed between the first filter 511 and the second filter 512. The porous sound-absorbing particles 521 can move between the first filter 511 and the second filter 512 to dissipate sound energy and airflow pulsation kinetic energy.

[0061] The first filter screen 511 and the second filter screen 512 are spaced apart along the direction from the air inlet 42 toward the air outlet 43, forming a filling space between them. Porous sound-absorbing particles 521 are filled between the first filter screen 511 and the second filter screen 512 to form an energy dissipation layer 52. The flow direction of the exhaust airflow in the muffler is as follows: Figure 4 As indicated by the middle arrow, the exhaust airflow sequentially flows through the first filter 511, the energy dissipation layer 52, and the second filter 512, achieving multi-level energy dissipation and filtration effects. First, the first filter 511 performs preliminary filtration of the exhaust airflow, intercepting larger refrigerant oil droplets and reducing their impact on subsequent structures. Then, the exhaust airflow enters the energy dissipation layer 52, where porous sound-absorbing particles 521 move, absorbing and dissipating the sound energy and airflow pulsation kinetic energy in the exhaust airflow through the porous structure and collision friction, effectively reducing exhaust noise and further separating oil droplets. Finally, the exhaust airflow passes through the second filter 512 for secondary filtration, ensuring only gaseous refrigerant is discharged smoothly. The porous sound-absorbing particles 521, moving between the first and second filters 511, more fully absorb and dissipate the sound energy and airflow pulsation kinetic energy in the exhaust airflow, resulting in more effective noise reduction. An energy dissipation layer 52 is disposed between the first filter screen 511 and the second filter screen 512 of the flow dissipation layer 51. The porous sound-absorbing particles 521 in the energy dissipation layer 52 can buffer the pulsation of the exhaust airflow, reduce the impact of the exhaust airflow on the first filter screen 511 and the second filter screen 512, and reduce the vibration amplitude of the filter screens. At the same time, the double-layer filter structure of the first filter screen 511 and the second filter screen 512 can increase the filtration area and improve the filtration effect, thereby effectively improving the separation efficiency of refrigeration oil and gaseous refrigerant.

[0062] Optionally, the first filter 511 and the second filter 512 adopt an elastic mesh structure.

[0063] Porous sound-absorbing particles 521 are filled between the first filter screen 511 and the second filter screen 512. When no external force is applied, the porous sound-absorbing particles 521 are in a static state; when the exhaust airflow passes through the energy dissipation layer 52, the porous sound-absorbing particles 521 are in a dynamic state. The elastic mesh structure of the first and second filter screens 511 and 512 provides stable support, ensuring that the porous sound-absorbing particles 521 are in close contact with the first and second filter screens 511 and 512 in the static state, forming a stable filter element 50 structure. Thus, when the exhaust airflow passes through the filter element 50, the exhaust airflow impacts and collides with the porous sound-absorbing particles 521, causing them to move and continuously collide. The movement of the porous sound-absorbing particles 521 can drive the contacting first and second filter screens 511 and 512 to undergo elastic deformation. Figure 7The diagram shows a partial view of the filter element. Under the influence of the exhaust airflow, the porous sound-absorbing particles between the first filter screen 511 and the second filter screen 512 can move and align in a row. This alignment helps form a continuous sound-absorbing barrier, enhancing sound wave reflection and scattering, thereby improving the noise reduction effect. The elastic deformation of the first filter screen 511 and the second filter screen 512 allows the porous sound-absorbing particles 521 to move as the airflow passes through. This elastic deformation can convert the vibrations caused by the pulsation of the exhaust airflow into elastic potential energy, achieving energy dissipation and effectively reducing noise. The elastic membrane structure can filter large oil droplets in the exhaust airflow, achieving oil-gas separation and reflux lubrication functions.

[0064] Optionally, the first filter 511 adopts a one-way filter structure so that the exhaust airflow flows unidirectionally from the air inlet 42 toward the air outlet 43.

[0065] In this way, the first filter 511 can intercept and filter the refrigeration oil while also preventing the backflow of gaseous refrigerant.

[0066] Optionally, the second filter 512 adopts a one-way filter structure so that the exhaust airflow flows unidirectionally from the air inlet 42 toward the air outlet 43.

[0067] In this way, the second filter 512 can not only intercept and filter the refrigeration oil, but also prevent the backflow of gaseous refrigerant.

[0068] Optionally, the porous sound-absorbing particles 521 are made of polyvinyl alcohol-carbon black material.

[0069] Polyvinyl alcohol-carbon black materials possess excellent sound absorption properties and stability. The porous structure of polyvinyl alcohol-carbon black materials can effectively absorb and dissipate sound wave energy in exhaust gas flow, thereby reducing noise.

[0070] Optionally, the porous sound-absorbing particles 521 are made of hollow spherical foam material.

[0071] The lightweight structure and high energy absorption characteristics of hollow spherical foam material can effectively dissipate energy in the exhaust airflow, enhancing noise reduction. Simultaneously, the hollow spherical foam material also possesses good elasticity, which can buffer airflow pulsations, reducing the vibration of the first filter 511 and the second filter 512, thereby reducing noise. It is understandable that the porous sound-absorbing particles 521 can also be a composite material composed of polyvinyl alcohol-carbon black and hollow spherical foam.

[0072] Optionally, combined Figure 4As shown, the housing 40 includes a bottom wall 44 located below the inner cavity 41. The bottom wall 44 has an oil return channel 441 at its radial end 443 along the inner cavity 41, which connects to the inner cavity 41. The middle part 442 of the bottom wall 44 protrudes towards the inner cavity 41, and the end 443 of the bottom wall 44 slopes downward away from the inner cavity 41.

[0073] After the exhaust gas flows through the filter element 50, the first and second filter screens can filter the oil droplets in the exhaust gas. At the same time, the disordered collision between porous composite particles can also achieve oil-gas separation. The separated exhaust gas continues to move along the axial direction of the inner cavity 41 toward the outlet 43, while the oil droplets drip down under the action of gravity and collect at the bottom of the housing 40. The bottom of the housing 40 is provided with a bottom wall 44, which is located below the inner cavity 41. An oil return channel 441 is provided in the bottom wall 44, which connects to the inner cavity 41, so that the refrigerant oil collected at the bottom of the inner cavity 41 can flow out through the oil return channel 441 and return smoothly to the compressor 10 for lubrication. The oil return channel 441 is located at the radial end 443 of the bottom wall 44 along the inner cavity 41. The middle part 442 of the bottom wall 44 protrudes towards the inner cavity 41, while the end 443 of the bottom wall 44 slopes downward away from the inner cavity 41. This guides the dripping oil droplets towards the oil return channel 441 at the end 443 to collect and flow, achieving efficient return of the refrigeration oil and preventing oil droplet retention. The number of oil return channels 441 can be one or more, and this application does not limit the number of oil return channels 441.

[0074] Optionally, combined Figure 4 As shown, the air inlet 42 is located in the middle part 442 of the bottom wall 44, and the bottom wall 44 on both sides of the air inlet 42 is inclined downward away from the inner cavity 41.

[0075] An air inlet 42 is located in the middle 442 of the bottom wall 44, through which exhaust airflow flows into the inner cavity 41. The air pressure of the exhaust airflow prevents dripping oil droplets from falling into the air inlet 42, thus avoiding backflow. At the same time, after dripping under the influence of gravity, the oil droplets are guided by the inclined bottom wall 44 to flow from both sides of the air inlet 42 toward the end 443 of the bottom wall 44, achieving oil droplet aggregation and backflow.

[0076] Optionally, combined Figure 4 As shown, the housing 40 includes a top wall 45 and a bottom wall 44, with an air outlet 43 formed on the top wall 45 and an air inlet 42 formed on the bottom wall 44. The inner cavity 41 is constructed between the top wall 45 and the bottom wall 44, and the inner diameter of the inner cavity 41 is larger than the diameter of the air inlet 42 and the inner diameter of the inner cavity 41 is larger than the diameter of the air outlet 43.

[0077] The top wall 45 of the housing 40 is provided with an air outlet 43, and the bottom wall 44 is provided with an air inlet 42. The inner cavity 41 is constructed between the top wall 45 and the bottom wall 44, and the inner diameter of the inner cavity 41 is larger than the diameter of the air inlet 42 and the diameter of the air outlet 43. This creates an expansion-type silencing structure between the air inlet 42, the inner cavity 41, and the air outlet 43 of the housing 40, which can reduce exhaust pressure pulsation. After the exhaust airflow enters the inner cavity 41 through the air inlet 42, the cross-sectional area of ​​the inner cavity 41 suddenly expands, causing the exhaust airflow velocity to decrease, which can effectively reduce noise. Subsequently, the exhaust airflow flows into the smaller inner diameter air outlet 43, at which point the airflow velocity moderately increases, ensuring exhaust efficiency while maintaining a low noise level.

[0078] Optionally, the inner cavity 41 includes a first cavity segment and a second cavity segment that are connected to each other. The first cavity segment is connected to the air inlet 42, and the second cavity segment is connected to the air outlet 43. The inner diameter of the first cavity segment is larger than the inner diameter of the second cavity segment, the inner diameter of the second cavity segment is larger than the diameter of the air outlet 43, and the inner diameter of the first cavity segment is larger than the diameter of the air inlet 42.

[0079] This causes the exhaust airflow to gradually slow down in the inner cavity 41, which can effectively enhance the noise reduction effect.

[0080] Optionally, combined Figure 4 As shown, the diameter of the air inlet 42 gradually increases along the direction from the air inlet 42 toward the inner cavity 41.

[0081] The diameter of the air intake 42 gradually increases along the direction from the air intake 42 towards the inner cavity 41, which gradually reduces the flow resistance and flow velocity of the exhaust airflow in the air intake 42. This reduces airflow pulsation and improves the noise reduction effect.

[0082] Optionally, combined Figure 4 As shown, the filter element 50 extends radially along the inner cavity 41, and the size of the filter element 50 is adapted to the inner diameter of the inner cavity 41.

[0083] The filter element 50 extends radially along the inner cavity 41 and its dimensions are adapted to the inner diameter of the inner cavity 41, enabling the filter element 50 to fit tightly against the wall of the inner cavity 41, preventing the exhaust airflow from being discharged directly through the gap without filtration, thereby improving the filtration effect. For example, the inner cavity 41 of the muffler 12 has a circular cross-section in the radial direction, and the filter element 50 is also circular and extends radially along the inner cavity 41.

[0084] Optionally, combined Figure 4 As shown, the muffler 12 for the compressor 10 also includes a cooling pipe 60, which is located between the filter element 50 and the outlet port 43. The cooling pipe 60 is connected to a low temperature source outside the housing 40 to reduce the temperature of the cooling pipe. After the exhaust gas comes into contact with the cooling pipe 60, it flows out through the outlet port 43.

[0085] The direction of exhaust airflow in the muffler is as follows Figure 4 As indicated by the arrow, the exhaust gas flows into the inner cavity 41 through the air inlet 42 of the muffler 12. After being filtered by the filter element 50 to remove refrigerant droplets and reduce airflow pulsation, the exhaust gas flows through the cooling pipe 60 for further noise reduction. By installing the cooling pipe 60 in the inner cavity 41 of the housing 40, a low-temperature source is used to cool the cooling pipe 60, creating a low-temperature region around it. The high-temperature exhaust gas flows into the inner cavity 41 through the air inlet 42. As it flows through the low-temperature region around the cooling pipe 60, a temperature gradient is generated around the cooling pipe 60 due to the temperature difference, forming a variable-temperature region. The different propagation speeds of sound waves in different temperature regions cause the noise waves of the exhaust gas to be refracted and scattered in the variable-temperature region, resulting in sound wave absorption and thus noise reduction. At the same time, the cooling pipe 60 has a simple structure, which simplifies the flow path of the exhaust gas in the inner cavity 41 and reduces the flow resistance of the refrigerant exhaust gas, thereby reducing the energy loss of the refrigerant while reducing exhaust noise.

[0086] Optionally, the cryogenic source is a cryogenic fluid source.

[0087] Cryogenic gas sources can introduce cryogenic gas into the condenser pipes through a simple piping and valve system. Cryogenic gases are lightweight, experience low flow resistance, and generate minimal noise during flow. It's also possible that a cryogenic source could be a cryogenic liquid source.

[0088] Optionally, one end of the cooling pipe 60 is a closed end and the other end is an open end. The closed end is located in the inner cavity, and the open end is connected to a low-temperature source outside the shell 40.

[0089] One end of the cooling pipe is designed as a closed end, which prolongs the residence time of the cryogenic fluid inside the cooling pipe, allowing the cryogenic fluid to fully dissipate its cooling capacity and create a low-temperature zone around the cooling pipe. This enables the exhaust gas to undergo more uniform heat exchange as it flows through the cooling pipe, further improving the noise reduction effect.

[0090] The compressor includes a cooler 14, which is connected to an external cryogenic gas source. The open end of the induced cooling pipe 60 is connected to the cooler 14, allowing the cooler 14 to introduce cryogenic gas into the induced cooling pipe 60. Under the impact and compression of the newly introduced cryogenic gas, the heat-exchanged gas is discharged from the induced cooling pipe, and the newly introduced cryogenic gas continues to cool the induced cooling pipe. Alternatively, both ends of the induced cooling pipe 60 can be open; one open end is connected to a cryogenic source outside the casing to introduce cryogenic fluid into the induced cooling pipe, and the other open end is connected to the outside of the casing to discharge the heat-exchanged gas.

[0091] Optionally, combined Figure 8-10As shown, the cooling pipe 60 includes an inner cooling pipe 61 and an outer cooling pipe 62. The inner cooling pipe 61 is connected to a low-temperature source outside the housing 40, and the pipe wall of the inner cooling pipe 61 is provided with a through hole 611. The outer cooling pipe 62 is sleeved on the outside of the inner cooling pipe 61, and a cavity 63 is formed between the outer cooling pipe 62 and the inner cooling pipe 61. The low-temperature fluid of the inner cooling pipe 61 can flow into the cavity 63 through the through hole 611.

[0092] The cryogenic fluid first enters the inner cooling pipe 61 from the first end 602, and then enters the cavity 63 between the inner cooling pipe 61 and the outer cooling pipe 62 through the through hole 611 opened in the pipe wall of the inner cooling pipe 61, forming a cryogenic zone in the cavity 63. The flow direction of the cryogenic fluid between the through hole and the cavity is as follows: Figure 9 and Figure 10 As indicated by the middle arrow, the cryogenic fluid circulates between the internal cooling pipe 61 and the cavity 63, increasing the contact time and contact area between the cryogenic fluid and the exhaust gas flow through the external cooling pipe 62. This enhances the heat exchange efficiency between the cryogenic fluid and the high-temperature exhaust gas flow, making the temperature gradient in the variable temperature region more pronounced, improving the sound wave absorption effect, and thus more effectively reducing the noise of the exhaust gas flow.

[0093] Optionally, the first end 602 of the cooling tube is connected to a low-temperature source outside the shell, and the low-temperature fluid of the low-temperature source flows from the first end 602 of the cooling tube to the second end 601 of the cooling tube. There are multiple through holes 611, and the number of through holes 611 gradually increases along the direction from the first end 602 to the second end 601.

[0094] During the flow of the cryogenic fluid through the internal cooling pipe 61, the flow velocity gradually decreases. By gradually increasing the number of through holes 611 from the first end 602 towards the second end 601, the change in the flow velocity of the cryogenic fluid can be effectively compensated. This allows the cryogenic fluid to be more evenly distributed throughout the cavity 63, forming a more uniform cryogenic region and avoiding excessively high or low local concentrations of cryogenic fluid. The cryogenic fluid in the cavity 63 indirectly contacts the exhaust gas flow in the internal cavity 41 through the external cooling pipe 62. The gradual increase in the number of through holes 611 from the first end 602 towards the second end 601 allows for more sufficient indirect contact between the cryogenic fluid and the exhaust gas flow, thereby improving the noise reduction effect.

[0095] Optionally, the first end 602 of the cooling tube is connected to a low-temperature source outside the shell, and the low-temperature fluid of the low-temperature source flows from the first end 602 of the cooling tube to the second end 601 of the cooling tube. There are multiple through holes 611, and the density of the through holes 611 gradually increases along the direction from the first end 602 to the second end 601.

[0096] During the flow of the cryogenic fluid in the internal cooling pipe 61, the flow velocity gradually decreases. By gradually increasing the density of the through-holes 611 along the direction from the first end 602 to the second end 601, the change in the flow velocity of the cryogenic fluid can be effectively compensated. This gradual increase in density along the direction from the first end 602 to the second end 601 allows for a more uniform distribution of the cryogenic fluid within the cavity 63, preventing excessively high or low local concentrations of the cryogenic fluid, thereby improving the overall cooling effect of the cooling pipe 60. This also allows for more thorough indirect contact between the cryogenic fluid and the exhaust gas flow, thus improving noise reduction.

[0097] Optionally, combined Figure 4 As shown, there are multiple cooling tubes 60, which are evenly distributed along the circumference of the inner cavity 41.

[0098] Multiple cooling pipes 60 are evenly distributed circumferentially along the inner cavity 41, creating multiple low-temperature regions along the circumference of the inner cavity 41. As the exhaust gas flows through the multiple cooling pipes 60, a temperature gradient is generated around them, forming multiple variable-temperature regions. This enhances the absorption of sound waves, thereby effectively improving noise reduction. The even distribution of the multiple cooling pipes 60 along the circumference of the inner cavity 41 also ensures that the exhaust gas flows evenly through the inner cavity 41, reducing local disturbances and eddies, lowering flow resistance, and thus optimizing the flow path of the exhaust gas. It can be understood that the multiple cooling pipes 60 can also be symmetrically or randomly distributed along the circumference of the inner cavity 41; the arrangement of multiple cooling pipes 60 in either case improves the noise reduction effect.

[0099] Optionally, combined Figure 4 As shown, the air inlet 42 and the air outlet 43 are located at opposite ends of the inner cavity 41 along the axial direction, and the cooling pipe 60 extends radially along the inner cavity 41.

[0100] The exhaust gas flows from the inlet 42 towards the outlet 43. The extension direction of the cooling pipe 60 intersects with the flow direction of the exhaust gas, allowing the exhaust gas to contact the cooling pipe 60 more evenly during its flow. This increases the heat exchange area between the exhaust gas and the cooling pipe 60, thereby improving the heat exchange efficiency between the exhaust gas and the cryogenic fluid. The radially extending cooling pipe 60 can form a more uniform cryogenic region in the inner cavity 41, allowing the exhaust gas to exchange heat more fully with the cryogenic region as it flows through, optimizing the temperature gradient distribution and enhancing the noise reduction effect.

[0101] Combination Figure 1As shown, this embodiment of the present disclosure provides a compressor 10, including a bearing assembly 11 and a muffler 12 for the compressor 10 as described in any of the above-disclosed embodiments. The bearing assembly 11 includes a bearing 20, which has an exhaust port 21. The housing 40 of the muffler 12 is disposed on the end face 22 of the bearing 20, and the air inlet 42 of the muffler 12 corresponds to the exhaust port 21 of the bearing 20, so that the exhaust gas flow in the exhaust port 21 flows out and enters the inner cavity 41 through the air inlet 42 of the muffler 12.

[0102] The air inlet 42 of the muffler 12 corresponds to the exhaust port 21 of the bearing 20, meaning that the air inlet 42 of the muffler 12 and the exhaust port 21 of the bearing 20 are connected. The air inlet 42 of the muffler 12 and the exhaust port 21 of the bearing 20 can be directly connected adjacently, or they can be indirectly connected at intervals.

[0103] The compressor 10 provided in this embodiment includes the muffler 12 for the compressor 10 as described in any of the above-described embodiments, and therefore possesses all the beneficial effects of the muffler 12 for the compressor 10 as described in any of the above-described embodiments. The housing 40 of the muffler 12 is disposed on the end face 22 of the bearing 20, and the air inlet 42 of the muffler 12 corresponds to the exhaust port 21 of the bearing 20, so that the exhaust airflow, after flowing out from the exhaust port 21, can enter the inner cavity 41 of the muffler 12 through the air inlet 42. By using a filter 50 disposed in the inner cavity 41 to perform silencing and oil-gas separation treatment on the exhaust airflow, the exhaust noise can be reduced while lowering the oil discharge rate.

[0104] Optionally, the end face 22 of the bearing 20 is provided with a fixing hole, and the housing 40 of the muffler 12 is installed in the fixing hole by a fastener.

[0105] The housing 40 of the muffler 12 is mounted in the fixing hole on the end face 22 of the bearing 20 by a fastener. This enhances the structural strength and installation stability of the muffler 12, ensuring it remains in a stable position during compressor 10 operation and preventing displacement or loosening due to vibration. Multiple fixing holes can be evenly distributed on the end face 22, distributing the installation force evenly and reducing localized stress concentration, thereby improving the installation stability of the muffler 12.

[0106] Optionally, combined Figure 1As shown, the compressor 10 includes a housing 13 and a cooler 14. The housing 13 has a receiving space, in which the bearing 20 assembly 11 and the silencer 12 are both located. The cooler 14 passes through the housing 13 and has an inlet channel and an outlet channel. One end of the inlet channel is connected to a low-temperature source, and the other end is connected to a cooling pipe 60 to introduce low-temperature fluid into the cooling pipe 60. One end of the outlet channel is connected to the cooling pipe 60, and the other end is connected to the outside of the housing so that the gas after heat exchange in the cooling pipe 60 is discharged through the outlet channel.

[0107] Low-temperature fluid is introduced into the induced cooling tube 60 through the air inlet channel of the cooler 14, and the heat-exchanged gas is discharged through the air outlet channel of the cooler, which can provide continuous cooling for the induced cooling tube. This enables efficient cooling of the induced cooling tube 60.

[0108] Optionally, combined Figure 11-14 As shown, the compressor 10 also includes an exhaust component 30, which includes an exhaust valve 31 and a thermal drive element 32. The exhaust valve 31 is movably mounted on the bearing 20 and is correspondingly arranged with the exhaust port 21. The thermal drive element 32 is drivenly connected to the exhaust valve 31 to drive the exhaust valve 31 to open and close the exhaust port 21. The thermal drive element 32 is heat-transferringly connected to the exhaust port 21 so that the exhaust gas flow in the exhaust port 21 heats the thermal drive element 32 through heat transfer. When the thermal drive element 32 reaches the deformation temperature, it deforms to drive the exhaust valve 31 to open the exhaust port 21. When the thermal drive element 32 is below the deformation temperature, it cools down and resets to drive the exhaust valve 31 to close the exhaust port 21.

[0109] The compressor 10 includes a cylinder with a compression chamber capable of compressing refrigerant gas. When the compressor 10 is running, the refrigerant gas in the compression chamber is periodically compressed. The temperature of the refrigerant gas rises after compression. High-temperature exhaust gas flows into the exhaust port 21 of the bearing 20 and heats the thermal drive element 32 through heat transfer. The thermal drive element 32 deforms after being heated to its deformation temperature, generating a driving force to open the exhaust valve 31, allowing the exhaust gas to exit from the exhaust port 21. After exhausting, the pressure of the refrigerant gas in the compression chamber decreases, and its temperature also drops. The thermal drive element 32 resets because its temperature is below its deformation temperature, thereby closing the exhaust valve 31. The entire exhaust process is performed periodically with the compression action of the compression chamber, and the exhaust gas is discharged intermittently. When the compressor 10 is not running, the exhaust valve 31 remains closed, and the thermal drive element 32 is in the reset state.

[0110] The heat transfer connection between the heat-driven element 32 and the exhaust port 21 allows the heat from the exhaust airflow to be effectively transferred to the heat-driven element 32, providing energy for its deformation and thus driving the exhaust valve 31 to automatically open and close the exhaust port 21. The deformation of the heat-driven element 32 also limits the movement of the exhaust valve 31 within its deformation range, eliminating the need for a lift limiter in the traditional compressor 10 and preventing mechanical impacts to the exhaust valve 31, thereby reducing noise. This also reduces the number of mechanical parts and simplifies the structure of the bearing assembly 11. Furthermore, the deformation driving force of the heat-driven element 32 is based on temperature changes rather than airflow pressure, and the deformation of the heat-driven element 32 is gradual, making the movement of the exhaust valve 31 more stable. This avoids or reduces impact noise during the movement of the exhaust valve 31, thereby extending its service life.

[0111] The compressor 10's bearing 20 includes a main bearing and a secondary bearing. The bearing 20 involved in this application can be either a main bearing or a secondary bearing.

[0112] Optionally, combined Figure 11-14 As shown, the exhaust valve 31 is located on the axial end face 22 of the bearing 20. The thermal drive element 32 deforms in a direction parallel to the end face 22 to drive the exhaust valve 31 to move in a direction parallel to the end face 22.

[0113] The exhaust valve 31 is located on the axial end face 22 of the bearing 20, and the thermal drive element 32 drives the exhaust valve 31 to move in a direction parallel to the end face 22 when opening and closing the exhaust port 21, which can effectively prevent the exhaust valve 31 from colliding with the bearing 20 when closing the exhaust port 21. At the same time, the movement of the exhaust valve 31 in a direction parallel to the end face 22 can also reduce the axial space occupied by the bearing 20, thereby optimizing the space utilization of the shaft assembly.

[0114] Optionally, combined Figure 15-18As shown, the exhaust port 21 is located on the first end face 221 of the bearing 20 along the axial direction. The second end face 222 of the bearing 20 along the axial direction is provided with a first exhaust hole 211 and a second exhaust hole 212. Both the first exhaust hole 211 and the second exhaust hole 212 are connected to the exhaust port 21. The exhaust gas flows into the exhaust port 21 and is discharged through the first exhaust hole 211 and the second exhaust hole 212 respectively. The exhaust valve 31 includes a first valve plate 311 and a second valve plate 312. The first valve plate 311 covers the first exhaust hole 211, and the second valve plate 312 covers the first exhaust hole 211. A plate 312 is placed over the second exhaust port 212; one end of the heat drive element 32 is connected to the first valve plate 311, and the other end of the heat drive element 32 is connected to the second valve plate 312. When the deformation temperature is reached, the heat drive element 32 simultaneously drives the first valve plate 311 and the second valve plate 312 to open the first exhaust port 211 and the second exhaust port 212. When the deformation temperature is lower than the deformation temperature, the heat drive element 32 simultaneously drives the first valve plate 311 and the second valve plate 312 to close the first exhaust port 211 and the second exhaust port 212.

[0115] The exhaust port 21 is located on the first end face 221 of the bearing 20 along the axial direction. The first exhaust hole 211 and the second exhaust hole 212 are opened on the second end face 222 of the bearing 20. The first exhaust hole 211 and the second exhaust hole 212 are connected to the exhaust port 21, so that the first exhaust hole 211 and the second exhaust hole 212 form a U-shaped or similar U-shaped exhaust hole along the axial direction of the shaft.

[0116] After entering the exhaust port 21, the exhaust airflow flows into the first exhaust hole 211 and the second exhaust hole 212 respectively, dividing the exhaust process into two paths. This optimizes the exhaust path, effectively reduces exhaust resistance, and thus improves exhaust efficiency. The exhaust valve 31 includes a first valve plate 311 and a second valve plate 312, which respectively cover the first exhaust hole 211 and the second exhaust hole 212. Both the first exhaust hole 211 and the second exhaust hole 212 are connected to the exhaust port 21. Thus, by driving the first valve plate 311 and the second valve plate 312 to open or close the first exhaust hole 211 and the second exhaust hole 212, the exhaust valve 31 can control the opening and closing of the exhaust port 21. One end of the thermal drive element 32 is connected to the first valve plate 311, and the other end is connected to the second valve plate 312. When the thermal drive element 32 reaches its deformation temperature, it can simultaneously drive the first valve plate 311 and the second valve plate 312 to move, thereby synchronously opening the first exhaust hole 211 and the second exhaust hole 212. When the thermal drive element 32 is below its deformation temperature, it can simultaneously drive the first valve plate 311 and the second valve plate 312 to move, thereby synchronously closing the first exhaust port 211 and the second exhaust port 212. The synchronous movement of the first valve plate 311 and the second valve plate 312 can improve the uniformity and stability of the exhaust process, thereby enhancing the operational stability of the compressor 10.

[0117] Optionally, combined Figure 16 As shown, the first exhaust port 211 and the second exhaust port 212 are symmetrically arranged with respect to the exhaust port 21.

[0118] The first exhaust port 211 and the second exhaust port 212 are symmetrically arranged relative to the exhaust port 21, so that when the exhaust airflow flows from the exhaust port 21 toward the first exhaust port 211 and the second exhaust port 212, the resistance and flow area of ​​the exhaust airflow in all directions remain consistent, thereby achieving a uniform distribution of exhaust airflow and optimizing the exhaust process.

[0119] Optionally, combined Figure 11-13 As shown, one end of the first valve plate 311 and one end of the second valve plate 312 are connected to form a connecting portion 313, and the first valve plate 311 and the second valve plate 312 are respectively inclined to both sides of the connecting portion 313. The thermal drive element 32 is disposed between the first valve plate 311 and the second valve plate 312. The connecting portion 313 is fixedly connected to the bearing 20. When the deformation temperature is reached, the thermal drive element 32 drives the first valve plate 311 and the second valve plate 312 to move in opposite directions. When the deformation temperature is lower than the deformation temperature, the thermal drive element 32 drives the first valve plate 311 and the second valve plate 312 to move back to their original positions.

[0120] One end of the first valve plate 311 and one end of the second valve plate 312 are connected to form a connecting part 313. The first valve plate 311 and the second valve plate 312 are inclined to both sides of the connecting part 313, so that the exhaust valve 31 as a whole forms a V-shaped or similar V-shaped structure. The thermal drive element 32 is disposed between the first valve plate 311 and the second valve plate 312 and can drive the first valve plate 311 and the second valve plate 312 to move. The connecting part 313 is fixedly connected to the bearing 20, providing a stable support point for the exhaust valve 31, making the structure of the exhaust valve 31 more stable and preventing displacement. The thermal drive element 32 deforms and expands due to temperature changes, which can drive the first valve plate 311 and the second valve plate 312 to move in opposite directions along the plane of the end face 22, opening the first exhaust port 211 and the second exhaust port 212, or drive the first valve plate 311 and the second valve plate 312 to move back towards each other along the plane of the end face 22, closing the first exhaust port 211 and the second exhaust port 212, thereby realizing intermittent exhaust control.

[0121] The first valve plate 311 is matched in shape and size with the first exhaust port 211, enabling it to effectively close or open the first exhaust port 211. The second valve plate 312 is matched in shape and size with the second exhaust port 212, enabling it to effectively close or open the second exhaust port 212. This improves the sealing performance and control precision of the exhaust valve 31, thereby enhancing the efficiency and stability of the exhaust process.

[0122] Optionally, the bearing 20 is provided with a fixing hole, and the connecting part 313 corresponds to the fixing hole and is fixed to the bearing 20 by a fastening screw.

[0123] The exhaust valve 31 is fixed to the bearing 20 by means of fastening screws and fixing holes. The fixing method is simple and easy to install and maintain.

[0124] Optionally, combined Figure 16 and Figure 18 As shown, the bearing 20 is also provided with a first exhaust channel 213 and a second exhaust channel 214. The first exhaust channel 213 is connected between the exhaust port 21 and the first exhaust hole 211, and the second exhaust channel 214 is connected between the exhaust port 21 and the second exhaust hole 212. The exhaust port 21, the first exhaust hole 211 and the second exhaust hole 212 are all opened along the axial direction of the bearing 20, and the first exhaust channel 213 and the second exhaust channel 214 are opened along the tangential direction of the bearing 20.

[0125] The tangential direction of bearing 20 refers to the direction perpendicular to the radial direction of bearing 20. After the compressor 10 completes compression, the exhaust gas flows into the exhaust port 21 located on the first end face 221 of bearing 20, then splits into the first side exhaust passage 213 and the second side exhaust passage 214, and is subsequently discharged through the first exhaust hole 211 and the second exhaust hole 212, respectively. The flow direction of the exhaust gas is as follows: Figure 18 As indicated by the middle arrow. The exhaust port 21, the first exhaust hole 211 and the second exhaust hole 212 are all opened along the axial direction of the bearing 20, and the first side exhaust channel 213 and the second side exhaust channel 214 are opened along the tangential direction of the bearing 20, so that the flow direction of the exhaust airflow passes through the axial direction, the tangential direction and the axial direction in sequence. Through the multiple changes in the flow direction, the sound wave reflection and absorption can be increased, thereby effectively reducing exhaust noise.

[0126] Optionally, combined Figure 16 As shown, the first exhaust channel 213 and the second exhaust channel 214 are symmetrically arranged with respect to the exhaust port 21. The first exhaust port 211 corresponds to the first exhaust channel 213, and the second exhaust port 212 corresponds to the second exhaust channel 214.

[0127] This ensures that the flow characteristics of the exhaust airflow are consistent on both sides of the symmetry, which can balance the exhaust pressure, reduce the asymmetry of the airflow, and thus improve the uniformity of the exhaust airflow distribution.

[0128] Optionally, the flow cross-sectional area of ​​the exhaust port 21 is smaller than the sum of the flow cross-sectional areas of the first side exhaust channel 213 and the second side exhaust channel 214.

[0129] The flow cross-sectional area refers to the cross-sectional area perpendicular to the direction of exhaust gas flow. The exhaust gas flows simultaneously from the exhaust port 21 into the first exhaust channel 213 and the second exhaust channel 214. Due to the increased flow cross-sectional area, the airflow resistance decreases. This reduces pressure pulsation and effectively lowers injection noise.

[0130] Optionally, the sum of the flow cross-sectional areas of the first exhaust passage 213 and the second exhaust passage 214 is less than the sum of the flow cross-sectional areas of the first exhaust hole 211 and the second exhaust hole 212.

[0131] The exhaust gas flows into the first exhaust hole 211 and the second exhaust hole 212 from the first exhaust channel 213 and the second exhaust channel 214 respectively. Due to the increase in the flow cross-sectional area, the pressure pulsation can be reduced and the injection noise can be effectively reduced.

[0132] The cross-sectional area of ​​the exhaust port 21 is smaller than the sum of the cross-sectional areas of the first exhaust channel 213 and the second exhaust channel 214, and the sum of the cross-sectional areas of the first exhaust channel 213 and the second exhaust channel 214 is smaller than the sum of the cross-sectional areas of the first exhaust hole 211 and the second exhaust hole 212. This allows the cross-sectional area of ​​the exhaust airflow to gradually increase during the exhaust process, resulting in a more stable change in exhaust pressure, effectively reducing pressure pulsation and improving the stability of the exhaust process.

[0133] Optionally, the thermal drive element 32 is made of shape memory alloy.

[0134] Shape memory alloys possess a unique shape memory effect and superelasticity, enabling them to undergo reversible shape changes in response to temperature variations. Furthermore, shape memory alloys exhibit a faster temperature response and a wider deformation range. The phase transition temperature of a shape memory alloy is equivalent to the deformation temperature of a thermal drive element. Applying shape memory alloys to the thermal drive element 32 allows for precise control of the opening and closing of the exhaust valve 31 under the influence of heat from the exhaust gas flow, improving the stability and accuracy of the exhaust valve 31's movement. Simultaneously, shape memory alloys have a long fatigue life, maintaining good performance during frequent temperature changes and deformations, thus extending the service life of the thermal drive element 32.

[0135] The exhaust gas temperature of an air conditioner compressor is affected by the compressor model, refrigerant type, and operating conditions. Based on common refrigerants and operating conditions, the exhaust gas temperature range of a compressor is typically between 70℃ and 110℃. Shape memory alloys, once above their phase transition temperature, will return to their preset shape, expanding or contracting according to their original shape and phase transition type. Shape memory alloys can be made of nickel-titanium alloys. By adjusting the nickel-titanium ratio or adding a third element (such as copper or iron), the phase transition temperature can be increased to 70–100℃. Nickel-titanium alloys have high fatigue life and strong corrosion resistance, making them suitable for long-term cyclic use. Copper-based shape memory alloys, such as copper-zinc-aluminum alloys, can also be used. By adjusting different component ratios, the phase transition temperature can cover 70–120℃. Furthermore, copper-zinc-aluminum alloys are less expensive and easier to process.

[0136] It is understandable that the thermal drive element 32 can also adopt a bimetallic strip structure.

[0137] A bimetallic strip is made of two metals with different coefficients of thermal expansion laminated together. When the temperature changes, the bimetallic strip will bend and deform, and this deformation can be used to drive the opening and closing of the exhaust valve.

[0138] Optionally, the thermal drive element 32 is spring-shaped, and the direction of thermal deformation of the thermal drive element 32 is consistent with the direction of elastic deformation.

[0139] The thermal drive element 32 is configured as a spring. When the thermal drive element 32 deforms due to heat, the direction of thermal deformation is consistent with the direction of elastic deformation, enabling the exhaust valve to move simultaneously using both thermal and elastic deformation forces. Based on the thermal deformation and cooling-down reset capabilities of the thermal drive element 32 itself, combined with the elastic deformation force of the spring, the driving force and deformation range of the thermal drive element 32 can be effectively increased. This allows the thermal drive element 32 to more accurately and stably control the movement range of the exhaust valve. Simultaneously, the spring-like structure provides stable elastic force and excellent deformation recovery capability. Under the stable contraction action of the spring, the movement of the thermal drive element 32 is smoother, thereby reducing impact and vibration during movement and lowering noise. Furthermore, the spring-like structure has good flexibility and fatigue resistance, enabling it to adapt to frequent deformation and reset processes, ensuring the long-term stable operation of the thermal drive element 32. The thermal drive element 32 can adopt a spiral, folded, or other forms of spring-like structure.

[0140] Optionally, a lubricating layer is provided on the side of the thermal drive element 32 near the bearing 20.

[0141] The lubrication layer reduces friction between the thermal drive element 32 and the bearing 20, thereby reducing wear on both elements and improving the durability of the thermal drive element 32 while reducing frictional noise. Simultaneously, during the movement of the thermal drive element 32, the lubrication layer reduces frictional resistance, improves the stability of the thermal drive element 32 during deformation, and also reduces heat and energy loss caused by friction.

[0142] Optionally, combined Figure 3 , Figure 14 and Figure 18 As shown, the bearing 20 is also provided with a heat transfer channel 23, which is connected between the side wall 215 of the exhaust port 21 and the heat drive element 32, so that the heat of the exhaust gas flow in the exhaust port 21 can be transferred to the heat drive element 32 through the heat transfer channel 23.

[0143] The heat transfer channel 23 connects the side wall 215 of the exhaust port 21 and the heat drive element 32, allowing the heat of the exhaust gas flow in the exhaust port 21 to be quickly transferred to the heat drive element 32 through the heat transfer channel 23. This improves the thermal response speed of the heat drive element 32.

[0144] Optionally, combined Figure 3 and Figure 14 As shown, the bearing assembly 11 for the compressor 10 also includes a heat transfer element 231, which is disposed in the heat transfer channel 23. One end of the heat transfer element 231 is in contact with the exhaust gas flow in the exhaust port 21, and the other end of the heat transfer element 231 is in contact with the heat drive element 32.

[0145] A heat transfer element 231 is provided in the heat transfer channel 23, which can efficiently transfer the heat of the exhaust gas flow to the heat-driven element 32, while preventing the exhaust gas flow from flowing out of the heat transfer channel 23. This not only improves the speed and efficiency of heat transfer, but also concentrates the exhaust direction, facilitating subsequent exhaust noise reduction. The heat transfer element 231 can be made of a high thermal conductivity material, such as metal. This application does not limit the shape of the heat transfer channel 23.

[0146] Optionally, combined Figure 3 and Figure 14 As shown, the radial dimension of the heat transfer element 231 is adapted to the radial dimension of the heat transfer channel 23.

[0147] This improves the sealing effect of the heat transfer element 231, causing the heat transfer element 231 to block the heat transfer channel 23 and effectively prevent the exhaust gas from flowing out of the heat transfer channel 23.

[0148] For example, when the compressor 10 finishes compression and is about to discharge, the temperature of the compression chamber rises, and the exhaust gas flows into the exhaust port 21, transferring the high heat to the heat transfer element 231 installed in the heat transfer channel 23. The heat transfer element 231 transfers the heat to the heat drive element 32. The heat drive element 32 deforms due to heat, generating a deformation force F to both sides. The deformation force F acts simultaneously on the first valve plate 311 and the second valve plate 312 of the V-shaped exhaust valve 31, causing the first valve plate 311 and the second valve plate 312 to move in opposite directions around the connecting part 313. The included angle between the first valve plate 311 and the second valve plate 312 gradually increases, opening the first exhaust port 211 and the second exhaust port 212 respectively, allowing the exhaust gas to flow out. When the discharge ends, the temperature of the compression chamber decreases, the temperature of the exhaust gas transferred to the heat drive element 32 decreases, and the heat drive element 32 contracts, driving the first valve plate 311 and the second valve plate 312 to move in opposite directions around the connecting part 313. When the thermal drive element 32 is fully retracted and reset to its original position, the first valve plate 311 and the second valve plate 312 completely block and close the first exhaust port 211 and the second exhaust port 212.

[0149] Optionally, combined Figure 11-15 As shown, the bearing 20 has a groove 223 on its second end face 222 along the axial direction. The first exhaust hole 211 and the second exhaust hole 212 are opened in the groove 223, and the exhaust valve 31 is accommodated in the groove 223.

[0150] The first vent 211 and the second vent 212 are opened in the groove 223, and the vent valve 31 is correspondingly accommodated in the groove 223. This optimizes space utilization and makes the structure of the entire bearing assembly 11 more compact.

[0151] For example, the compressor 10 also includes a motor, crankshaft, rollers, and cylinder, all of which are housed within the housing. The housing includes a top cover with an exhaust port. The motor is driven by the crankshaft, which is driven by the rollers. The cylinder has a cylinder cavity 41, and the rollers are located within the cylinder cavity 41. When the compressor 10 is running, the motor drives the crankshaft and rollers to perform circular motion. The rollers periodically compress the refrigerant gas within the cylinder cavity 41, forming an exhaust gas flow. The exhaust gas flow flows into the exhaust port 21 of the bearing 20 and is discharged through the first exhaust port 211 and the second exhaust port 212. Intermittent exhaust can be achieved by controlling the opening and closing of the first exhaust port 211 and the second exhaust port 212 through the exhaust valve 31. After the exhaust airflow exits the first exhaust port 211 and the second exhaust port 212, it enters the inner cavity 41 of the muffler 12 through the air inlet 42, and then exits into the housing space through the air outlet 43 of the muffler 12, finally exiting the compressor 10 through the exhaust port on the top cover of the compressor 10. By setting a heat-driven element 32 in the bearing 20 to drive the exhaust valve 31 to open and close the first exhaust port 211 and the second exhaust port 212, and by setting a filter element 50 and a cooling pipe 60 in the muffler 12, multiple noise reduction effects can be achieved, thereby effectively reducing the exhaust noise of the compressor 10.

[0152] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A muffler for a compressor, characterized by, The silencer comprises: a shell configured with an inner cavity, and the shell is provided with an air inlet hole and an air outlet hole communicating with the inner cavity; a filter provided in the inner cavity, and the filter corresponds to the air inlet hole, the exhaust gas flow flows into the inner cavity through the air inlet hole and flows out of the air outlet hole after flowing through the filter; wherein the filter comprises a flow-diffusing layer and an energy-diffusing layer, the flow-diffusing layer comprises a first filter screen, and the energy-diffusing layer is filled with porous sound-absorbing particles which can move under the action of the exhaust gas flow to dissipate sound energy and gas flow pulsation kinetic energy.

2. The sound suppressor for a compressor according to claim 1, characterized by, The flow-diffusing layer further comprises: a second filter screen, the first filter screen and the second filter screen are arranged in a spaced manner along the direction of the air inlet hole towards the air outlet hole, the energy-diffusing layer is arranged between the first filter screen and the second filter screen, and the porous sound-absorbing particles can move between the first filter screen and the second filter screen to dissipate sound energy and gas flow pulsation kinetic energy.

3. The silencer for the compressor according to claim 2, wherein the first filter screen and the second filter screen adopt an elastic mesh film structure.

4. The silencer for the compressor according to claim 2, wherein the first filter screen adopts a one-way filter screen structure to enable the exhaust gas flow to flow in one direction along the direction of the air inlet hole towards the air outlet hole; and / or the second filter screen adopts a one-way filter screen structure to enable the exhaust gas flow to flow in one direction along the direction of the air inlet hole towards the air outlet hole.

5. The silencer for the compressor according to claim 1, wherein the porous sound-absorbing particles adopt a polyvinyl alcohol-carbon black material; and / or the porous sound-absorbing particles adopt a hollow spherical foam material.

6. The sound damper for a compressor according to any one of claims 1 to 5, characterized in that, The shell comprises: a bottom wall located below the inner cavity, the end of the bottom wall along the radial direction of the inner cavity is provided with an oil return channel, the oil return channel communicates with the inner cavity, the middle part of the bottom wall is raised towards the inner cavity, and the end part of the bottom wall is inclined downward away from the inner cavity.

7. The sound damper for a compressor according to any one of claims 1 to 5, characterized in that The shell comprises: a top wall, the air outlet hole is formed in the top wall; a bottom wall, the air inlet hole is formed in the bottom wall; wherein the inner cavity is configured between the top wall and the bottom wall, the inner diameter of the inner cavity is greater than the hole diameter of the air inlet hole, and the inner diameter of the inner cavity is greater than the hole diameter of the air outlet hole.

8. The silencer for the compressor according to any one of claims 1 to 5, wherein the hole diameter of the air inlet hole gradually increases along the direction of the air inlet hole towards the inner cavity; and / or the filter extends along the radial direction of the inner cavity, and the size of the filter is matched with the inner diameter of the inner cavity.

9. The sound damper for a compressor according to any one of claims 1 to 5, characterized in that, Further comprising: a cold lead pipe provided between the filter and the air outlet hole, the cold lead pipe communicates with a low-temperature source outside the shell to reduce the temperature of the cold lead pipe.

10. A compressor characterized by, The silencer comprises: a bearing assembly comprising a bearing, the bearing is provided with an exhaust port; The silencer for the compressor according to any one of claims 1 to 9, the shell of the silencer is arranged on the end surface of the bearing, and the air inlet hole of the silencer corresponds to the exhaust port of the bearing, so that the exhaust gas flow in the exhaust port flows out and then enters the inner cavity through the air inlet hole of the silencer.

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