Technical Field
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The present application relates to the field of compressors, in particular to a screw compressor.
Background Art
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A screw compressor comprises a pair of rotors. By means of the mutual meshing of rotor teeth of the pair of rotors, a change in an elementary volume formed by tooth-shaped spaces is caused to complete the processes of suction, compression and exhausting of gas. Since a screw compressor forms discontinuous inter-tooth volumes through the meshing of the rotors, suction and exhaust chambers are periodically in communication to working chambers, causing unstable flow of gas and pressure pulsations in processes of suction and exhausting, which in turn causes compressor vibration and noise.
Summary of the Invention
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At least one objective of the present application is to provide a screw compressor, comprising: a housing, a rotor assembly, an exhaust channel, and at least one noise reducer group. The housing is provided with a suction port and an exhaust port. The rotor assembly is accommodated in the housing and rotates along an axial direction, the rotor assembly is provided with a rotor inlet and a rotor outlet, and the rotor assembly is configured to compress gas sucked in from the rotor inlet and exhaust the gas from the rotor outlet, wherein the rotor inlet is in fluid communication with the suction port, and the rotor outlet is in fluid communication with the exhaust port. The exhaust channel is in fluid communication with the rotor outlet and the exhaust port, such that compressed gas exhausted from the rotor outlet passes through the exhaust channel to be exhausted from the exhaust port. The noise reducer group is arranged in the exhaust channel to eliminate noise in the exhaust channel, the noise reducer group comprises a front end plate, a rear end plate, and a plurality of partition plates, the front end plate and the rear end plate are opposite to each other along the axial direction of the rotor assembly and arranged at an interval, each partition plate is connected between the front end plate and the rear end plate to divide a space between the front end plate and the rear end plate into a plurality of noise reduction chambers, each noise reduction chamber is provided with a noise reducer inlet and a noise reducer outlet, each noise reducer inlet is independently in fluid communication with the rotor outlet, and each noise reducer outlet is independently in fluid communication with the exhaust port, wherein the noise reducer inlet is arranged on the front end plate, the noise reducer outlet is arranged on the rear end plate, and cross-sectional areas of the noise reducer inlet and the noise reducer outlet are less than cross-sectional areas of the noise reduction chambers.
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According to the above content, the plurality of noise reduction chambers in each noise reducer group are arranged side-by-side around the axial direction of the rotor assembly.
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According to the above content, the exhaust channel is defined by an accommodating cavity wall, and the front end plate and the rear end plate of the noise reducer group are connected to the accommodating cavity wall, wherein the accommodating cavity wall closes the noise reduction chambers around the axial direction of the rotor assembly.
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According to the above content, the noise reducer group comprises a sealing plate, the sealing plate is connected to the front end plate and the rear end plate, and the sealing plate closes the noise reduction chambers around the axial direction of the rotor assembly.
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According to the above content, the screw compressor further comprises a barrel portion, the barrel portion is connected between the front end plate and the rear end plate, the barrel portion defines a connection channel, the rotor outlet and the exhaust port are in fluid communication directly through the connection channel, the connection channel extends along the axial direction of the rotor assembly, and the plurality of noise reduction chambers are arranged outside the barrel portion around the connection channel.
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According to the above content, on an axial cross section, the exhaust port can cover the connection channel and the noise reducer outlet.
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According to the above content, the housing comprises an exhaust outer housing and an exhaust inner housing, the exhaust inner housing is arranged inside the exhaust outer housing, the exhaust channel is defined between the exhaust outer housing and the exhaust inner housing as well as inside the exhaust inner housing, and the exhaust channel comprises an annular channel around the exhaust inner housing, wherein an inner housing air outlet is provided on the exhaust inner housing, and the inner housing air outlet is in fluid communication with the noise reducer inlet of the noise reducer group through the annular channel.
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According to the above content, the front end plate and the rear end plate are arranged in parallel.
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According to the above content, the front end plate and the rear end plate are not arranged in parallel, such that at least a part of the plurality of noise reduction chambers have different lengths along the axial direction of the rotor assembly.
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According to the above content, the front end plate and the rear end plate are arranged perpendicular to the axial direction of the rotor assembly.
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According to the above content, at least a part of the noise reducer inlets in the noise reducer group are formed by an opening on the front end plate.
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According to the above content, the at least one noise reducer group comprises a plurality of noise reducer groups, the plurality of noise reducer groups are arranged along the axial direction of the rotor assembly, and the noise reducer inlets and the noise reducer outlets of adjacent noise reducer groups are arranged in an aligned manner.
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According to the above content, the noise reducer group is configured to set a noise reduction frequency and a noise reduction amount to eliminate noise in the exhaust channel by a number of the noise reduction chambers, lengths of the noise reduction chambers along the axial direction of the rotor assembly, a cross-sectional area ratio of the noise reducer inlets to the noise reduction chambers, and a cross-sectional area ratio of the noise reducer outlets to the noise reduction chambers.
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Other features, advantages, and embodiments of the present application may be set forth or become apparent by consideration of the following detailed description of the embodiments, drawings, and claims. In addition, it should be understood that the above summary and the following detailed description of the embodiments are all exemplary and intended to provide further explanation, rather than to limit the scope of the present application claimed. However, the detailed description of the embodiments and specific examples merely indicate preferred embodiments of the present application. Various changes and modifications within the spirit and scope of the present application will become apparent to those skilled in the art through the detailed description of the embodiments.
Brief Description of the Drawings
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- FIG. 1A is a three-dimensional structural diagram of a screw compressor according to one embodiment of the present application;
- FIG. 1B is a top view of the screw compressor shown in FIG. 1A;
- FIG. 2A is an exploded view of the screw compressor shown in FIG. 1A;
- FIG. 2B is a cross-sectional view of the screw compressor shown in FIG. 1B along a line A-A;
- FIG. 2C is a cross-sectional view of the screw compressor shown in FIG. 1B along a line B-B;
- FIG. 2D is a cross-sectional view of the screw compressor shown in FIG. 1B along a line C-C;
- FIG. 3A is a three-dimensional structural diagram of an exhaust housing in a screw compressor according to another embodiment of the present application;
- FIG. 3B is an exploded view of the exhaust housing shown in FIG. 3A;
- FIG. 3C is one cross-sectional view of the exhaust housing shown in FIG. 3A;
- FIG. 3D is another cross-sectional view of the exhaust housing shown in FIG. 3A;
- FIG. 4A is an exploded view of an exhaust housing in a screw compressor according to yet another embodiment of the present application;
- FIG. 4B is one cross-sectional view of the exhaust housing shown in FIG. 4A;
- FIG. 4C is another cross-sectional view of the exhaust housing shown in FIG. 4A;
- FIG. 5A is an exploded view of an exhaust housing in a screw compressor according to yet another embodiment of the present application;
- FIG. 5B is one cross-sectional view of the exhaust housing shown in FIG. 5A;
- FIG. 5C is another cross-sectional view of the exhaust housing shown in FIG. 5A;
- FIG. 6 is a cross-sectional view of an exhaust housing in a screw compressor according to yet another embodiment of the present application;
- FIG. 7A is a three-dimensional structural diagram of a noise reducer group in a screw compressor according to yet another embodiment of the present application;
- FIG. 7B is a top view of a noise reducer group shown in FIG. 7A;
- FIG. 8A is a three-dimensional structural diagram of an exhaust housing in a screw compressor according to yet another embodiment of the present application;
- FIG. 8B is an exploded view of the exhaust housing shown in FIG. 8A;
- FIG. 9A is a comparison diagram of noise reduction frequencies between one noise reduction chamber in FIG. 2A and a noise reduction chamber comprising an inlet pipeline and an outlet pipeline; and
- FIG. 9B is a comparison diagram of noise reduction frequencies between a plurality of noise reduction chambers in FIG. 2A and an overall noise reduction chamber not comprising partition plates.
Detailed Description of Embodiments
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Various detailed description of the embodiments of the present application will be described below with reference to the drawings, which constitute a part of this specification. It should be understood that while directional terms such as "front," "rear," "upper," "lower," "left," "right," "top," and "bottom" are used in the present application to describe various exemplary structural components and elements of the present application, these terms are used herein for convenience of description only and are determined based on the exemplary orientations shown in the drawings. Since the embodiments disclosed in the present application can be set in various directions, these directional terms are intended for illustrative purposes only and should not be construed as limiting.
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FIG. 1A and FIG. 1B show a structure of a screw compressor 100 according to one embodiment of the present application, and are used for illustrating an external structure of the screw compressor 100. FIG. 1A is a three-dimensional structural diagram of the screw compressor 100. FIG. 1B is a top view of FIG. 1A. As shown in FIG. 1A and FIG. 1B, the screw compressor 100 comprises a housing 101, and the housing 101 is approximately in a shape of a long cylinder and comprises a rotor housing 102 and an exhaust housing 104 that are connected in sequence in a length direction. The rotor housing 102 is provided with a suction port 105, and the rotor housing 102 is mainly used for accommodating a motor 212 and a rotor assembly 221 (see FIG. 2B) to rotate therein. The exhaust housing 104 is provided with an exhaust port 106, and the exhaust housing 104 is used for exhausting compressed gas from the exhaust port 106. Therefore, after entering the housing 101 through the suction port 105, the gas flows approximately along the length direction, and is exhausted out of the housing 101 from the exhaust port 106 after being compressed.
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FIG. 2A-FIG. 2D show an internal structure of the screw compressor 100 shown in FIG. 1A. FIG. 2A shows an exploded view of the screw compressor 100. FIG. 2B shows a cross-sectional view of the screw compressor 100 along a line A-A. FIG. 2C shows a cross-sectional view of the screw compressor 100 along a line B-B. FIG. 2D shows a cross-sectional view of the screw compressor 100 along a line C-C. As shown in FIG. 2A-FIG. 2D, in the present embodiment, the screw compressor 100 is a twin-screw compressor. The rotor assembly 221 comprises a pair of rotors arranged side-by-side in parallel. The pair of rotors comprise a male rotor and a female rotor. Those skilled in the art can understand that on the section position shown in FIG. 2B, only the male rotor is shown. The male rotor and the female rotor mesh with each other, and the male rotor is connected to the motor 212, such that the pair of rotors can be driven by the motor 212 to respectively rotate. The pair of rotors have axes parallel to each other, and the male rotor and the female rotor rotate around respective axes. In the present embodiment, an extension direction of the axis is an axial direction of the rotor assembly 221, a direction around the axial direction is a circumferential direction of the rotor assembly 221, and a direction perpendicular to the axial direction and the circumferential direction is a radial direction of the rotor assembly 221.
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The male rotor and the female rotor are respectively provided with a plurality of spiral teeth, and grooves are formed at intervals between adjacent teeth. The male rotor and the female rotor constitute a meshing structure through respective teeth and corresponding grooves, and jointly form a plurality of spaced compression cavities 225 with the rotor housing 102. The rotor assembly 221 is provided with a rotor inlet 222 and a rotor outlet 223. The rotor inlet 222 is located at a left end of the rotor assembly 221 and is in fluid communication with the suction port 105. The rotor outlet 223 is located at a right end of the rotor assembly 221 and is in fluid communication with the exhaust port 106. Each compression cavity 225 independently moves along the axial direction from the rotor inlet 222 to the rotor outlet 223. The gas is sucked into the compression cavity 225 from the rotor inlet 222, and as the rotor assembly 221 rotates, the compression cavity 225 gradually moves toward the rotor outlet 223. At the same time, the volume of the compression cavity 225 gradually decreases as the rotor assembly 221 rotates, and the gas in the compression cavity 225 is gradually compressed. The compressed gas is exhausted from the rotor outlet 223.
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The exhaust housing 104 is provided with an exhaust channel 217 therein. The exhaust port 106 is located in the middle of the exhaust housing 104. The rotor outlet 223 is in fluid communication with the exhaust port 106 through the exhaust channel 217, such that the compressed gas exhausted from the rotor outlet 223 is exhausted from the exhaust port 106 through the exhaust channel 217.
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When the screw compressor 100 is in operation, the pair of rotors of the rotor assembly 221 mesh with each other to form a discontinuous compression cavity 225, such that the compressed gas is intermittently exhausted from the rotor outlet 223, then flows through the exhaust channel 217 and then is exhausted from the exhaust port 106, thereby generating an exhaust pressure pulsation with higher acoustic energy, which results in vibration and noise of the screw compressor 100.
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In order to reduce the noise impact caused by the exhaust pressure pulsation, the screw compressor 100 further comprises at least one noise reducer group 240. The noise reducer group 240 is arranged in the exhaust channel 217 for eliminating the noise in the exhaust channel 217. In the present embodiment, the at least one noise reducer group 240 comprises one noise reducer group. Those skilled in the art can understand that according to the spatial dimension of the exhaust channel 217 and the spatial dimension of the noise reducer group 240, the at least one noise reducer group 240 may comprise more noise reducer groups. These noise reducer groups may be connected into the exhaust channel 217 in a manner of series connection or parallel connection.
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Specifically, each noise reducer group 240 comprises a front end plate 241, a rear end plate 242, and a plurality of partition plates 243. The front end plate 241 and the rear end plate 242 are arranged opposite to and spaced apart from each other along the axial direction of the rotor assembly 221, the partition plates 243 are connected between the front end plate 241 and the rear end plate 242 to divide a space between the front end plate 241 and the rear end plate 242 into a plurality of noise reduction chambers 248. In the present embodiment, the noise reducer group 240 further comprises a sealing plate 249 extending along the circumferential direction, and the sealing plate 249 is connected to outer edges of the front end plate 241 and the rear end plate 242, so as to enable the sealing plate 249 to close each noise reduction chamber 248 around the axial direction of the rotor assembly 221. That is, the sealing plate 249, the front end plate 241, and the rear end plate 242 jointly define a closed noise reduction space, and the partition plates 243 divide the closed noise reduction space into a plurality of noise reduction chambers 248. Moreover, in the present embodiment, the front end plate 241 and the rear end plate 242 are approximately arranged in parallel and perpendicular to the axial direction, and the partition plates 243 are connected between the front end plate 241 and the rear end plate 242 along the radial direction. In other embodiments, the front end plate and the rear end plate may not be arranged in parallel, for example, in the embodiment shown in FIG. 7A and FIG. 7B. Moreover, in other embodiments, the sealing plate may not be included, and the outer edges of the front end plate and the rear end plate are connected to an inner wall of the exhaust housing, such that the front end plate, the rear end plate, and the exhaust housing jointly define a closed noise reduction space. For example, the sealing plate is not included in the embodiments shown in FIG. 3A-FIG. 3D, FIG. 4A-FIG. 4C, FIG. 5A-FIG. 5C, FIG. 6 and FIG. 7A-FIG. 7B.
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Each noise reduction chamber 248 is provided with a noise reducer inlet 245 and a noise reducer outlet 246. The noise reducer inlet 245 is arranged on the front end plate 241, and the noise reducer outlet 246 is arranged in the rear end plate 242. The noise reducer inlet 245 of each noise reduction chamber 248 is independently in fluid communication with the rotor outlet 223, and the noise reducer outlet 246 of each noise reduction chamber 248 is independently in fluid communication with the exhaust port 106. Therefore, after entering the corresponding noise reduction chamber 248 through each noise reducer inlet 245, the compressed gas exhausted from the rotor outlet 223 is exhausted from the corresponding noise reducer outlet 246, and then is exhausted from the exhaust port 106. The cross-sectional areas of each noise reducer inlet 245 and each noise reducer outlet 246 are smaller than cross-sectional areas of the noise reduction chambers 248. Due to this change in cross-sectional area, the noise reducer group 240 can form an expansion noise reducer group. When the compressed gas enters the noise reduction chambers 248 through the noise reducer inlet 245 and then is exhausted from the noise reducer outlet 246, sound wave energy is consumed, and thus the noise reducer group 240 can reduce noise. The cross-sectional area here refers to the cross-sectional area on an axial cross section at the noise reducer inlet and the noise reducer outlet as shown in FIG. 2D.
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In the present embodiment, the exhaust housing 104 of the housing 101 comprises an exhaust outer housing 214 and an exhaust inner housing 213. The exhaust inner housing 213 is arranged inside the exhaust outer housing 214. An inner channel 219 in fluid communication with the rotor outlet 223 is defined inside the exhaust inner housing 213. The inner channel 219, the exhaust outer housing 214, and the exhaust inner housing 213 jointly form the exhaust channel 217. In the present embodiment, the noise reducer group 240 is arranged at an end of the exhaust inner housing 213 in the axial direction, the front end plate 241 of the noise reducer group 240 abuts against an end of the exhaust inner housing 213, and the sealing plate 249 of the noise reducer group 240 is connected to an inner wall of the exhaust outer housing 214 to fix the position of the noise reducer group 240 in the exhaust housing 104. As one example, the sealing plate 249 is welded together with the exhaust outer housing 214. The exhaust channel 217 comprises an annular channel 218 defined jointly by the exhaust inner housing 213, the exhaust outer housing 214, and the front end plate 241 of the noise reducer group 240. The annular channel 218 is arranged around the exhaust inner housing 213. Moreover, each noise reducer inlet 245 on the front end plate 241 is in fluid communication with the annular channel 218. The inner channel 219 forms an inner housing air outlet 215 on the exhaust inner housing 213, and the inner housing air outlet 215 is in fluid communication with the annular channel 218. Therefore, the compressed gas exhausted from the rotor outlet 223 is first exhausted from the inner housing air outlet 215 to the annular channel 218 through the inner channel 219 after entering the exhaust housing 104, then enters the noise reducer group 240 through the noise reducer inlet 245, is exhausted from the noise reducer outlet 246 after being subjected to noise reduction through the noise reducer group 240, and at least, is exhausted from the exhaust port 106.
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As one specific embodiment, in order to match the annular channel 218, the noise reducer group 240 further comprises an enclosure plate 247 arranged inside the sealing plate 249. The enclosure plate 247 and the sealing plate 249 are arranged opposite to and spaced apart from each other in the radial direction. The plurality of partition plates 243 are connected between the sealing plate 249 and the enclosure plate 247 in a radial shape to define and form a plurality of noise reduction chambers 248 arranged side-by-side around the axial direction, and hollow portions 244 are formed between these noise reduction chambers 248. On an axial cross section of the noise reducer group 240, the hollow portion 244 is approximately the same as the exhaust inner housing 213 in end dimension, and the noise reduction chambers 248 arranged side-by-side have dimensions that approximately match that of the annular channel 218, which will reduce the pressure loss of the compressed gas entering and exhausted from the noise reducer group 240 from the annular channel 218. As one more specific example, the hollow portion 244 extends from the middle to the bottom, that is, the noise reduction chambers 248 arranged side-by-side along the circumferential direction are not set as a complete circle. Each noise reducer inlet 245 and each noise reducer outlet 246 are correspondingly arranged at a lower corner of each noise reduction chamber 248, such as a corner formed by the partition plate 243 and the sealing plate 249, or a corner formed by the partition plate 243 and the enclosure plate 247. This arrangement facilitates liquid droplets such as lubricating oil entrained in the compressed gas to be exhausted from the noise reducer outlet 246 after entering the noise reduction chambers 248 along with the compressed gas.
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In the embodiment shown in FIG. 2C, the inner housing air outlet 215 comprises a pair of inner housing air outlets 215a and 215b. The inner channel 219 first extends approximately along the axial direction in the exhaust inner housing 213, and then extends along the radial direction to both sides of the exhaust inner housing 213 to form the inner housing air outlets 215a and 215b that are located on both sides of the exhaust inner housing 213. This arrangement enables the inner housing air outlets 215a and 215b to be also in fluid communication with the annular channel 218 from both sides even if the noise reducer group 240 abuts against a front end of the exhaust inner housing 213 in the axial direction.
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Thus, the screw compressor 100 can, after the compressed gas enters the exhaust channel 217, flow through the noise reducer group 240 to eliminate noise in the exhaust channel 217. By utilizing the reflection of sound waves at cross-sectional area changes of the noise reducer inlet 245, the noise reduction chamber 248, and the noise reducer outlet 246, the sound wave energy is reduced, thereby reducing noise.
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The noise reducer group 240 sets a noise reduction frequency and a noise reduction amount to eliminate the noise in the exhaust channel 217 by setting a number of the noise reduction chambers 248, lengths of the noise reduction chambers 248 in the axial direction, a cross-sectional area ratio of the noise reducer inlet 245 to the noise reduction chambers 248, and a cross-sectional area ratio of the noise reducer outlet 246 to the noise reduction chambers 248.
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Specifically, main noise reduction frequencies of the noise reduction chambers 248 are mainly determined by the lengths of the noise reduction chambers 248 in the axial direction. The shorter the length, the higher the main noise reduction frequency. In the present embodiment, since the front end plate 241 and the rear end plate 242 are arranged in parallel, main noise reduction frequencies of all noise reduction chambers 248 are approximately the same. In some other embodiments, the front end plate 241 and the rear end plate 242 may not be arranged in parallel, such that each noise reduction chamber 248 has a different main noise reduction frequency. Under the condition that the front end plate and the rear end plate are not parallel, an axial length of one noise reduction chamber is preliminary estimated generally through the axial center distance between the two end plates. An initial area ratio is then calculated based on projection areas of the noise reducer inlet and the noise reducer outlet on a cross section. A transmission loss curve is then simulated, and at last, final dimensional parameters of the noise reduction chambers are determined according to the desired main noise reduction frequency.
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The upper limit of the effective noise reduction frequency of the noise reduction chambers 248 is mainly determined by the number of noise reduction chambers 248. The greater the number of noise reduction chambers 248 within the same dimensional space, the higher the upper limit of the effective noise reduction frequency.
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The noise reduction amount of the noise reduction chambers 248 is mainly determined by the cross-sectional area ratio of the noise reducer inlet 245 to the noise reduction chambers 248 and the cross-sectional area ratio of the noise reducer outlet 246 to the noise reduction chambers 248 (i.e., an expansion ratio). The higher the expansion ratio, the greater the noise reduction amount.
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FIG. 3A-FIG. 3D show a structure of an exhaust housing 304 in a screw compressor according to another embodiment of the present application, wherein FIG. 3A is a three-dimensional structural diagram of the exhaust housing 304, FIG. 3B is an exploded view of FIG. 3A, FIG. 3C is a cross-sectional view of the exhaust housing 304 along a line D-D, and FIG. 3D is a cross-sectional view of the exhaust housing 304 along a line E-E. As shown in FIG. 3A-FIG. 3D, in the present embodiment, the exhaust housing 304 no longer comprises an exhaust inner housing, but an exhaust channel 317 extending along the axial direction is directly formed in the exhaust housing 304. The exhaust channel 317 is defined by an accommodating cavity wall 316 of the exhaust housing 304, such that the rotor outlet 223 and the exhaust port 306 are in fluid communication through the exhaust channel 317.
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The structure of the noise reducer group 340 is also different from the structure of the noise reducer group 240. Specifically, the noise reducer group 340 does not comprise a sealing plate, and the shapes of the front end plate 341 and the rear end plate 342 of the noise reducer group match the shape of an inner surface of the accommodating cavity wall 316, such that the front end plate 341 and the rear end plate 342 can be directly connected to the accommodating cavity wall 316, thereby forming a closed noise reduction space among the front end plate 341, the rear end plate 342, and the accommodating cavity wall 316. The partition plates 343 are connected between the front end plate 341 and the rear end plate 342 along the radial direction to divide the closed noise reduction space into a plurality of noise reduction chambers 348. Each noise reduction chamber 348 is provided with a noise reducer inlet 345 and a noise reducer outlet 346 that are correspondingly arranged on the front end plate 341 and the rear end plate 342. In the present embodiment, the cross section of the accommodating cavity wall 316 is square, and the front end plate 341 and the rear end plate 342 are also in shapes of square plates. The edges of the front end plate 441, the rear end plate 442, and the partition plates 443 are connected to the accommodating cavity wall 416, for example, by means of welding, interference fit assembling or integral casting.
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In the present embodiment, the noise reducer group 340 further comprises a barrel portion 352, and the barrel portion 352 is connected between the front end plate 341 and the rear end plate 342. The barrel portion 352 defines a connection channel 358 extending along the axial direction, and the connection channel 358 penetrates through the front end plate 341 and the rear end plate 342 to be in fluid communication with the rotor outlet 223 and the exhaust port 306 directly. In the present embodiment, the barrel portion 352 is connected between the front end plate 341 and the rear end plate 342, and the partition plates 343 are connected between the barrel portion 352 and the accommodating cavity wall 316 in a radial shape, such that the plurality of noise reduction chambers 348 are arranged side-by-side outside the barrel portion 352 around the connection channel 358. By arranging the barrel portion 352 and the connection channel 358, most of the compressed gas can be exhausted through the connection channel 358 without passing through the noise reducer group 340. Therefore, the noise reducer group 340 has fewer effects on the pressure loss of the compressed gas. In the present embodiment, the noise reducer inlets 345 and the noise reducer outlets 346 of the plurality of noise reduction chambers 348 are arranged on the front end plate 341 and the rear end plate 342 that are close to the barrel portion 352, and are evenly arranged along the circumferential direction around the barrel portion 352. On an axial cross section of the exhaust housing 304, the exhaust port 306 can cover the connection channel 358 and the noise reducer outlet 346, such that the compressed gas can be directly exhausted from the exhaust port 306 after flowing through the connection channel 358 or the noise reducer group 340. Thus, the pressure loss of the compressed gas can be further reduced. The cross-sectional areas of each noise reducer inlet 345 and each noise reducer outlet 346 are smaller than cross-sectional areas of the noise reduction chambers 348, such that when the compressed gas enters the noise reduction chambers 348 through the noise reducer inlets 345 and then is exhausted from the noise reducer outlets 346, the sound wave energy is consumed, and thus the noise reducer group 340 can reduce noise.
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FIG. 4A-FIG. 4C show a structure of an exhaust housing 404 in a screw compressor according to yet another embodiment of the present application, wherein FIG. 4A is an exploded view of the exhaust housing 404, FIG. 4B is a cross-sectional view of the exhaust housing 404 along a line F-F, and FIG. 4C is a cross-sectional view of the exhaust housing 404 along a line G-G. As shown in FIG. 4A-FIG. 4C, a difference between the exhaust housing 404 and the exhaust housing 304 is that the structure of the noise reducer group 440 is different from the structure of the noise reducer group 340. Specifically, the noise reducer group 440 further comprises a front end plate 441 and a rear end plate 442 that are approximately arranged in parallel, as well as a noise reducer inlet 445 and a noise reducer outlet 446 that are respectively arranged on the front end plate 441 and the rear end plate 442. The noise reducer inlet 445 and the noise reducer outlet 446 are arranged correspondingly to reduce the pressure loss of the compressed gas. However, in the present embodiment, the partition plates 443 of the noise reducer group 440 are no longer arranged in a radial shape, but are arranged in a "#" shape to define and form a square noise reduction chamber 448. Moreover, the noise reducer group 440 no longer comprises a barrel portion and a connection channel, such that all the compressed gas will pass through the noise reducer group 440 to reduce noise. The edges of the front end plate 441, the rear end plate 442, and the partition plates 443 are connected to the accommodating cavity wall 416, for example, by welding. The cross-sectional areas of each noise reducer inlet 445 and each noise reducer outlet 446 are smaller than cross-sectional areas of the noise reduction chambers 448, such that when the compressed gas enters the noise reduction chambers 448 through the noise reducer inlets 445 and then is exhausted from the noise reducer outlets 346, the sound wave energy is consumed, and thus the noise reducer group 440 can reduce noise.
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FIG. 5A-FIG. 5C show a structure of an exhaust housing 504 in a screw compressor according to yet another embodiment of the present application, wherein FIG. 5A is an exploded view of the exhaust housing 504, FIG. 5B is a cross-sectional view of the exhaust housing 504 at the D-D line position in FIG. 3B, and FIG. 5C is a cross-sectional view of the exhaust housing 504 at the E-E line position in FIG. 3B. As shown in FIG. 5A-FIG. 5C, a difference between the exhaust housing 504 and the exhaust housing 304 is that the structure of the noise reducer group 540 is different from the structure of the noise reducer group 340. Specifically, the noise reducer group 540 further comprises a front end plate 541 and a rear end plate 542 that are approximately arranged in parallel, as well as a noise reducer inlet 545 and a noise reducer outlet 546 that are respectively arranged on the front end plate 541 and the rear end plate 542. The noise reducer inlet 545 and the noise reducer outlet 546 are arranged correspondingly to reduce the pressure loss of the compressed gas. However, in the present embodiment, the barrel portion 552 no longer penetrates through the front end plate 541 and the rear end plate 542, but is connected between the front end plate 541 and the rear end plate 542 to form a cylindrical noise reduction chamber 558 in the barrel portion 552. The noise reduction chamber 558 is provided with a separate noise reducer inlet and a separate noise reducer outlet. Moreover, the partition plates 543 are connected between the barrel portion 552 and the accommodating cavity wall 516 in a radial shape, such that the plurality of noise reduction chambers 548 are arranged side-by-side outside the barrel portion 552 around the noise reduction chambers 558. The edges of the front end plate 541, the rear end plate 542, and the partition plates 543 are connected to the accommodating cavity wall 516, for example, by welding. The cross-sectional areas of each noise reducer inlet 545 and each noise reducer outlet 546 are smaller than cross-sectional areas of the noise reduction chambers 548 and the noise reduction chambers 558, such that when the compressed gas enters the noise reduction chambers 548 or the noise reduction chambers 558 through the noise reducer inlet 545 and then is exhausted from the noise reducer outlet 546, the sound wave energy is consumed, and thus the noise reducer group 540 can reduce noise.
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FIG. 6 shows a structure of an exhaust housing 604 in a screw compressor according to yet another embodiment of the present application, wherein FIG. 6 shows a cross-sectional view of the exhaust housing 604 at the E-E line position in FIG. 3B. As shown in FIG. 6, the structure of the exhaust housing 604 is approximately the same as the structure of the exhaust housing 404, and a difference is that in the present embodiment, two noise reducer groups 640a and 640b with the same structure are arranged in the exhaust housing 604. Both the structures of the noise reducer group 640a and the noise reducer group 640b are the same as the structure of the noise reducer group 440, and a difference is that the lengths of the noise reduction chambers in the axial direction are different. The front end plate 641a and the rear end plate 642a of the noise reducer group 640a are approximately arranged parallel to the front end plate 641b and the rear end plate 642b of the noise reducer group 640b, and the noise reducer inlet 645a and the noise reducer outlet 646a of the noise reducer group 640a are arranged corresponding to the noise reducer inlet 645b and the noise reducer outlet 646b of the noise reducer group 640b, so as to reduce the pressure loss of the compressed gas. Moreover, the cross-sectional areas of each noise reducer inlet and each noise reducer outlet are smaller than cross-sectional areas of the noise reduction chambers, such that the compressed gas exhausted from the rotor outlet 223 can flow through the noise reducer group 640a and the noise reducer group 640b in sequence, causing the sound wave energy to be consumed, and thus the noise reducer group 540 can reduce noise.
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FIG. 7A and FIG. 7B show a structure of a noise reducer group 740 in a screw compressor according to yet another embodiment of the present application. FIG. 7A is a three-dimensional structural diagram of a noise reducer group 740, and FIG. 7B is a top view of the noise reducer group 740. As shown in FIG. 7A and FIG. 7B, in the present embodiment, the noise reducer group 740 further comprises a front end plate 741 and a rear end plate 742, as well as a noise reducer inlet 745 and a noise reducer outlet 746 that are respectively arranged on the front end plate 741 and the rear end plate 742. The noise reducer inlet 745 and the noise reducer outlet 746 are arranged correspondingly to reduce the pressure loss of the compressed gas. However, in the present embodiment, the front end plate 741 and the rear end plate 742 are no longer arranged in parallel, but are arranged in the shape of a folded line. The partition plates 743 of the noise reducer group 740 are arranged in a "#" shape to define and form trapezoidal noise reduction chambers 748. The cross-sectional areas of each noise reducer inlet 745 and each noise reducer outlet 746 are smaller than cross-sectional areas of the noise reduction chambers 748, such that when the compressed gas enters the noise reduction chambers 748 through the noise reducer inlets 745 and then is exhausted from the noise reducer outlets 746, the sound wave energy is consumed, and thus the noise reducer group 740 can reduce noise.
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FIG. 8A-FIG. 8B show a specific structure of an exhaust housing 804 in a screw compressor according to yet another embodiment of the present application. FIG. 8A shows a three-dimensional structural view of an exhaust housing 804, and FIG. 8B shows an exploded view of FIG. 8A. As shown in FIG. 8A and FIG. 8B, the structure of the exhaust housing 804 is approximately the same as the structure of the exhaust housing 104, and differences are that the structure of the noise reducer group 840 is different from the structure of the noise reducer group 240, and the position of the exhaust port 806 is different from the position of the exhaust port 106. Specifically, the noise reducer group 840 comprises a front end plate 841, a rear end plate 842, a sealing plate 849, and an enclosure plate 847. The front end plate 841 and the rear end plate 842 are arranged opposite to and spaced apart from each other in the axial direction, and the enclosure plate 847 and the sealing plate 849 are arranged opposite to and spaced apart from each other in the radial direction. Moreover, the enclosure plate 847 and the sealing plate 849 are connected between the front end plate 841 and the rear end plate 842, the plurality of partition plates (not shown in the figures, see the partition plate 243 shown in FIG. 2D) form a plurality of noise reduction chambers, and hollow portions 844 are formed between these noise reduction chambers. The noise reduction principle of the noise reducer group 840 is the same as that of the noise reducer group 240, which will not be described again. Different from the noise reducer group 240, the rear end plate 842 no longer closes the hollow portion 844, but only closes each noise reduction chamber. That is, the hollow portion 844 is in fluid communication with the exhaust port 806 directly. Compared with the noise reducer group 240, this arrangement of the rear end plate 842 may on the one hand reduce the material usage of the rear end plate 842, and on the other hand reduce the possibility that the gas in the exhaust channel impacts the rear end plate 842, such that the rear end plate 842 generates vibration and noise.
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As further shown in FIG. 2D, after the liquid droplets such as lubricating oil entrained in the compressed gas enter the noise reduction chambers along with the compressed gas, a part of liquid can be exhausted from the noise reducer outlet along with an air flow, and the other part of the liquid accumulates at a corner at the bottom of each noise reduction chamber under the action of gravity, and is exhausted from the noise reducer outlet after accumulating to a certain amount. The liquid exhausted from the noise reducer outlet is exhausted from the exhaust port 806 together with an air flow formed by the compressed gas.
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In the present embodiment, the exhaust housing 804 further comprises an exhaust outer housing 814 and an exhaust inner housing 813. The exhaust port 806 is arranged at the bottom of an end surface of the exhaust outer housing 814. This arrangement can make it easier for liquid droplets such as lubricating oil entrained in the compressed gas to be exhausted from the exhaust housing 804 in a timely manner.
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FIG. 9A shows a comparison diagram of noise reduction performances between one noise reduction chamber 248 in the noise reducer group in FIG. 2A and the noise reduction chamber comprising the inlet pipeline and the outlet pipeline. FIG. 9B shows a comparison diagram of noise reduction performances between the plurality of noise reduction chambers 248 in FIG. 2A and the overall noise reduction chamber not comprising the partition plates, wherein the abscissa is a sound wave frequency, and the ordinate is a transmission loss of sound waves. Under the conditions that the dimension of the noise reduction chamber 248 is unchanged and the cross-sectional areas of the inlet and the outlet are the same, a curve 981 shows a noise reduction effect of the noise reduction chamber comprising an inlet pipeline and an outlet pipeline, and a curve 982 shows a noise reduction effect of a noise reduction chamber 248 comprising only a noise reducer inlet and a noise reducer outlet that are in the shape of an opening. A curve 983 shows a noise reduction effect of the overall noise reduction chamber not comprising the partition plates, and a curve 984 shows a noise reduction effect of the plurality of noise reduction chambers comprising the partition plates.
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As shown in FIG. 9A, the noise reduction amount of the noise reduction chamber 248 comprising only the noise reducer inlet and the noise reducer outlet at certain frequencies is smaller than that of a noise reducer comprising an inlet pipeline and an outlet pipe line, but a certain noise reduction effect is also still exerted. The noise reduction amount at frequencies above 1400 Hz is comparable to that of the noise reducer comprising the inlet pipeline and the outlet pipeline, while the noise reduction amount in certain frequency bands (900-1400 Hz) is even higher. Moreover, a noise reducer not comprising the inlet pipeline and the outlet pipeline can greatly reduce the pressure loss of the compressed gas in the process of flowing through the noise reducer group. By arranging a plurality of noise reduction chambers 248 arranged side-by-side, the noise reduction range can be increased and the noise reduction amount can be compensated.
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As shown in FIG. 9B, the upper limit of the effective noise reduction frequency of the plurality of noise reduction chambers comprising the partition plates may reach about 2750 Hz. However, the noise reduction effect of the overall noise reduction chamber not comprising the partition plates is unsatisfactory above about 1700 Hz. Therefore, within the same dimensional space, the greater the number of set noise reduction chambers, the higher the upper limit of the effective noise reduction frequency.
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In an existing screw compressor, the compressed gas flowing through the exhaust channel has an exhaust pressure pulsation with higher acoustic energy, which results in vibration and noise of the screw compressor. The exhaust channel is limited in dimension, and particularly, the length in the axial direction is limited. Arranging the noise reducer in the exhaust channel needs to meet dimensional requirements and avoids excessive pressure loss of the compressed gas by the noise reducer.
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In the screw compressor of the present application, the noise reducer group, which is formed by arranging side-by-side the noise reduction chambers of a plurality of expansion noise reducers, is arranged in the exhaust channel, which not only fully utilizes the space of the exhaust channel, but also increases the upper limit of plane waves, such that the upper limit of an effective noise reduction frequency is higher and thus more noise can be eliminated.
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Moreover, the noise reducer inlet and the noise reducer outlet of the noise reducer group of the present application are in the shape of an opening, and an inlet pipeline and an outlet pipeline are not included. Therefore, the noise reducer group does not cause excessive pressure loss of the compressed gas.
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In addition, by arranging noise reduction chambers with different axial lengths, the noise reducer group of the present application can also eliminate the noise in the exhaust channel within a wide-frequency range.
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While the present disclosure has been described with reference to the examples of embodiments outlined above, various alternative solutions, modifications, variations, improvements, and/or substantially equivalents, whether known or now or soon foreseeable, may be apparent to at least those of ordinary skill in the art. Accordingly, the examples of embodiments of the present disclosure set forth above are intended to be illustrative rather than restrictive. Various changes may be made without departing from the spirit or scope of the present disclosure. Accordingly, the present disclosure is intended to comprise all known or earlier developed alternative solutions, modifications, variations, improvements, and/or substantially equivalents. The technical effects and technical problems in this specification are illustrative rather than restrictive. It should be noted that the embodiments described in this specification may have other technical effects and solve other technical problems.