Tangential exhaust compressor silencer

Abstract

A silencer body is composed of an annular base plate and a petal top cover, an upper bearing of an upper shaft of a rotor compressor crankshaft is sleeved with a center hole of the silencer body, and convex petals and concave petals in the petal top cover are arranged at intervals so that the inner cavity volume of the silencer body can be staggered in size in the circumferential direction; the exhaust holes are arranged to be independent single holes in the edge of the center hole, and each single hole is located between every two adjacent protruding petals according to the sound cavity mode of the silencer. Each single hole is a V-shaped opening with an opening facing the center of the petal-shaped top cover on the petal-shaped top cover, a guide plate is arranged on one side edge of each V-shaped opening in a protruding mode and faces the interior of the silencer, so that head-on airflow of the guide plates is discharged in the tangential direction of the crankshaft under the guidance of the guide plates, and the airflow is prevented from forming direct hedging on a rotating shaft system. Overall axial vibration of the compressor can be effectively improved, the problem of refrigerant direct blowing oil spitting deterioration is effectively solved, and the heat dissipation efficiency of the motor is improved.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically to a compressor muffler that exhausts air in a tangential direction. Background Technology

[0002] In industrial production, compressor noise is a significant issue. Excessive noise not only impacts the working environment but also threatens the health of workers. Currently, silencers for fixed-speed compressors primarily employ top-exhaust design. While this design achieves its exhaust function, it faces certain technical limitations due to the current trend towards lower overall compressor height. Specifically, during top-exhaust, high-pressure refrigerant can easily cause a direct impact on the rotor. This direct impact not only generates significant axial pulse excitation in the rotor shaft system but also further exacerbates the dynamic instability of rotor operation, thus adversely affecting the overall performance and reliability of the compressor.

[0003] The patent document with publication number CN222887085U discloses a "muffler for a rotor compressor", which includes multiple convex and concave lobes distributed on the muffler body. High-pressure pulse gas flowing out of the cylinder flows through the convex and concave lobes of the muffler in sequence. Due to the change in the volume of the inner cavity of the convex and concave lobes, the high-pressure pulse gas will generate propagation loss when it flows through, thereby reducing gas noise. At least one set of air outlets is provided on the convex lobes to change the direction of the high-pressure pulse gas before it flows out, so as to avoid direct collision between the gas and the rotor shaft system. The air outlets are located at the top of the convex lobes and have a side-flanged structure, which changes the vertical upward flow of the gas. The radial side discharge formed by the "side-flanged structure" of the air outlets will also lead to the deterioration of the flow field excitation. At the same time, the air outlets are located on one side of the side wall of the convex lobes, close to the bottom of the muffler, which makes it easy for oil to blow out, resulting in a deterioration of the compressor's oil discharge rate.

[0004] Patent document CN216788714U discloses a compressor and a compressor muffler. The muffler has an exhaust channel on its side wall parallel to the motor rotor, which communicates with the interior of the muffler. The muffler is equipped with a flow guiding device to limit the direction of gas discharge from the exhaust channel. The flow guiding device includes a flow guide shroud, which is fixed to the side wall of the muffler and protrudes outward to partially block the exhaust channel. This ensures that the direction of the discharged high-pressure gas is the same as the rotation direction of the motor rotor, preventing direct impact or friction between the high-pressure gas and the motor rotor, thus avoiding noise. Essentially, it is a radial side-discharge system. However, its structure, with the exhaust port located on the convex side wall, makes the exhaust port close to the bottom of the muffler, making it prone to oil blowing and leading to a deterioration in the compressor's oil discharge rate.

[0005] Patent document CN208634042U discloses a muffler and a compressor having the muffler. The muffler includes a muffler body and a flange. One end of the muffler body is provided with an exhaust hole. One end of the flange is arranged around the exhaust hole and is located on the hole wall surface of the exhaust hole. The other end of the flange extends outward in an arc shape towards the edge of the exhaust hole, which reduces the influence of burrs on the flange on the airflow and reduces exhaust noise. It is a central hole exhaust. However, it cannot effectively avoid the influence of the airflow force on the rotor. The exhaust channel arranged around the entire circle is not compatible with the acoustic cavity mode of the muffler. Summary of the Invention

[0006] The present invention aims to overcome the shortcomings of the prior art by providing a tangential exhaust compressor muffler, which effectively reduces the axial pulsation excitation experienced by the rotor shaft system and reduces compressor noise.

[0007] To achieve its objectives, the present invention employs the following technical solution: This invention relates to a tangential exhaust compressor muffler, comprising a circular annular base and a petal-shaped top cover, forming a muffler body with a central hole. The muffler body is fitted onto the upper bearing of the crankshaft of a rotor compressor via its central hole and is fixedly mounted on the upper bearing using bolt holes in the circular annular base. The petal-shaped top cover has convex and concave lobes spaced apart, creating an alternating pattern of large and small volumes within the muffler body along the circumferential direction. Its key feature is that the exhaust ports are configured as independent single holes located on the edge of the central hole, each single hole positioned between two adjacent convex lobes according to the muffler's acoustic cavity mode. Each single hole on the petal-shaped top cover is a "V"-shaped opening facing the center of the top cover. The first side of the "V"-shaped opening has a guide plate protruding towards the interior of the muffler, guiding the airflow towards the guide plate and discharging tangentially along the crankshaft, thus preventing direct impact of the airflow on the rotating shaft system.

[0008] The tangential exhaust compressor muffler of the present invention is also characterized in that: the exhaust hole is formed by marking a "V" shape at the location of the exhaust hole on the petal top cover, stamping according to the "V" shape, cutting the "V" shape on the second side, and bending it on the first side, forming a guide plate with a "V" shaped flange through cutting and bending.

[0009] The tangential exhaust compressor muffler of the present invention is also characterized in that the bending angle of the guide plate is less than 90°.

[0010] The characteristic of the compressor muffler with tangential exhaust in this invention is that: the sum of the areas of all individual holes in the exhaust port is denoted as the exhaust area S of the muffler; the exhaust area of ​​the bearing on the compressor pump body is denoted as the compressor exhaust area S0; then the value of the exhaust area S of the muffler satisfies: 0.5≤S / S0≤2.5.

[0011] The tangential exhaust compressor muffler of the present invention is also characterized in that: the height between the bottom surface and the top surface of the muffler body is recorded as the muffler body height H; the height between the lower edge of the guide plate and the bottom surface of the muffler body is recorded as the guide plate height H1; set: 2≤H≤30mm, H1≥1 / 2H.

[0012] Compared with existing technologies, the beneficial effects of this invention are reflected in: 1. This invention forms a guide plate at the "V"-shaped opening, allowing the airflow to be discharged tangentially along the crankshaft under the guidance of the guide plate, thereby achieving tangential exhaust from the exhaust port. This effectively improves the problem of direct impact force on the rotor caused by exhaust and significantly improves the overall axial vibration. 2. Compared with radial side-discharge, the silencer of this invention can effectively improve the secondary noise problem caused by direct impact on the main housing, reduce the secondary disturbance flow noise of the rotor to the high-pressure exhaust refrigerant, effectively improve the noise in the 500~3150Hz frequency band, and improve the overall noise by more than 3dB.

[0013] 3. The refrigerant discharged from the muffler of this invention is filtered through the motor windings, which effectively improves the problem of refrigerant deterioration caused by direct blowing and oil discharge.

[0014] 4. Due to the change in the direction of the discharged refrigerant flow, the heat dissipation efficiency and energy efficiency of the motor are improved in the silencer of this invention. Attached Figure Description

[0015] Figure 1 This is a schematic diagram showing the installation position of the present invention in a compressor; Figure 2 This is a schematic diagram of the silencer structure in this invention; Figure 3a and 3b This invention illustrates the sound pressure distribution within the acoustic cavity of the silencer under different modalities. The numbers in the diagram are: 1 upper crankshaft; 2 muffler; 201 concave petal; 202 circular base; 203 petal top cover; 204 center hole; 205 convex petal; 206 guide vane; 207 exhaust port; 3 upper bearing; 4 bolt hole. Detailed Implementation

[0016] See Figure 1 and Figure 2In this embodiment, the tangential exhaust compressor muffler consists of a circular annular base 202 and a petal-shaped top cover 203, forming a muffler body with a central hole 204. The muffler body is mounted on the upper bearing 3 of the upper shaft 1 of the rotor compressor crankshaft via its central hole 204, and is fixedly mounted on the upper bearing 3 using bolt holes 4 in the circular annular base 202. The petal-shaped top cover 203 is configured with alternating convex petals 205 and concave petals 201, so that the internal volume of the muffler body is staggered in a circumferential direction, with one large and one small petal. The key feature is the exhaust port. Configuration of 207: The exhaust port 207 consists of independent single holes located on the edge of the central hole 204. Each single hole is located between two adjacent convex petals 205 according to the acoustic cavity mode of the muffler. Each single hole is presented as a "V" shaped opening facing the center of the petal top cover 203. The first side of the "V" shaped opening has a guide plate 206 protruding towards the inside of the muffler, so that the airflow facing the guide plate 206 is discharged along the tangential direction of the crankshaft under the guidance of the guide plate 206, avoiding the airflow from directly impacting the rotating shaft system.

[0017] In practice, the corresponding technical measures also include: The exhaust port 207 is formed as follows: First, a "V" shape is marked at the location of the exhaust port on the petal top cover 203. Then, the "V" shape is stamped, and the "V" shape is cut on the second side and bent on the first side. The "V" shaped guide plate 206 is formed by cutting and bending. In order to ensure the formation of tangential flow, the bending angle of the guide plate 206 is set to be less than 90°. This exhaust method changes the vertical upward flow of gas, effectively improves the problem of direct impact force on the rotor caused by exhaust, and significantly improves the overall axial vibration.

[0018] Let the sum of the areas of all individual holes in exhaust port 207 be denoted as the muffler exhaust area S; let the exhaust area of ​​the bearing on the compressor pump body be denoted as the compressor exhaust area S0; then the value of the muffler exhaust area S should satisfy equation (1): 0.5≤S / S0≤2.5 (1).

[0019] If the exhaust area is too small, the airflow resistance will be high, which may lead to poor exhaust flow, but the reflection effect of mid-to-high frequency sound waves will be better. If the area is too large, sound waves can easily penetrate directly, the mid-to-high frequency silencing effect will decrease, and the orifice can easily excite airflow to regenerate noise. Therefore, the optimal exhaust area of ​​the muffler can be determined based on the S / S0 ratio.

[0020] The height between the bottom and top surfaces of the muffler body is denoted as the muffler body height H; the height between the lower edge of the guide vane and the bottom surface of the muffler body is denoted as the guide vane height H1, set as: 2≤H≤30mm, H1≥0.5H. The height of the muffler determines the frequency range of the acoustic cavity modes. The height must match the modal requirements of the target noise reduction frequency band, while ensuring sufficient airflow space to avoid back pressure or turbulent noise.

[0021] The present invention determines the acoustic cavity modal distribution by the muffler lobe shape, and determines the positional distribution of the exhaust port based on the acoustic cavity modal distribution.

[0022] Figure 3a The diagram illustrates the sound pressure distribution within the acoustic cavity of the silencer of this invention at a certain modal. At the natural frequency corresponding to this modality, the acoustic cavity exhibits a "petal-shaped" distribution, illustrating the propagation pattern of sound waves within the silencer. The silencer's exhaust port is generally located in the region of lower modal sound pressure, because a low sound pressure region indicates weaker sound wave vibration at that location. Placing the exhaust port here reduces the intensity of sound waves directly radiating from the exhaust port, thereby improving the noise reduction effect.

[0023] Figure 3b The diagram illustrates the sound pressure distribution within the acoustic cavity of the silencer of the present invention at different modal orders. Different modal orders correspond to different inherent vibration modes, and the vibration pattern of the sound wave within the cavity changes with the modal order. The location of the exhaust port is determined by combining the modal distribution of the target frequency band.

[0024] The high-pressure pulsating gas discharged from the cylinder passes through the valve passage and limiter, then passes through the convex and concave flaps of the muffler in sequence, and is discharged tangentially in the exhaust port. On the one hand, the change in the volume of the inner cavity of the convex and concave flaps causes the high-pressure pulsating gas to have a propagation loss, thereby reducing gas noise. On the other hand, the tangential exhaust changes the vertical upward flow of the gas, effectively avoiding direct collision between the gas and the rotor shaft system.

[0025] This invention can be widely applied to various types of compressor equipment, has strong installation adaptability, can improve the quietness of compressor operation, and improve the acoustic performance and service life of the equipment.

Claims

1. A tangential exhaust compressor muffler, comprising a muffler body with a central hole (204) consisting of an annular base (202) and a petal-shaped top cover (203), wherein the muffler body is fitted onto the upper bearing (3) of the upper shaft (1) of a rotor compressor via its central hole (204), and is fixedly mounted on the upper bearing (3) using bolt holes (4) in the annular base (202); wherein the petal-shaped top cover (203) is provided with convex petals (205) and concave petals (201) spaced apart, such that the internal volume of the muffler body is staggered in a circumferential direction; characterized in that: The exhaust port (207) is set as an independent single hole on the edge of the central hole (204). Each single hole is located between two adjacent convex petals (205) according to the acoustic cavity mode of the muffler. Each single hole is presented as a "V" shaped opening facing the center of the petal top cover (203). The first side of the "V" shaped opening has a guide plate (206) protruding towards the inside of the muffler, so that the airflow on the front of the guide plate (206) is discharged along the tangential direction of the crankshaft under the guidance of the guide plate (206), so as to avoid the airflow directly impacting the rotating shaft system.

2. The compressor muffler for tangential exhaust according to claim 1, characterized in that: The vent hole (207) is formed by marking a "V" shape at the location of the vent hole on the petal top cover (203), stamping according to the "V" shape, cutting the "V" shape on the second side, and bending it on the first side, forming a guide plate (206) with a "V" shaped flange through cutting and bending.

3. The compressor muffler for tangential exhaust according to claim 2, characterized in that: The bending angle of the guide plate (206) is less than 90°.

4. The compressor muffler for tangential exhaust according to claim 1, characterized in that: The sum of the areas of all individual holes in the exhaust port (207) is denoted as the exhaust area S of the muffler; the exhaust area of ​​the bearing on the compressor pump body is denoted as the exhaust area S0 of the compressor; then the value of the exhaust area S of the muffler satisfies: 0.5≤S / S0≤2.

5.

5. The compressor muffler for tangential exhaust according to claim 1, characterized in that: The height between the bottom and top surfaces of the muffler body is denoted as the muffler body height H; the height between the lower edge of the guide vane and the bottom surface of the muffler body is denoted as the guide vane height H1. Setting: 2≤H≤30mm, H1≥1 / 2H.

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