Screw compressor

Abstract

The present application discloses a screw compressor, comprising: a housing, a rotor group, an exhaust passage and at least one muffler group. The muffler group is arranged in the exhaust passage to eliminate the noise in the exhaust passage, and the muffler group comprises a front end plate, a rear end plate and several partition plates, each of the partition plates divides the space between the front end plate and the rear end plate into several muffler chambers, each of the muffler chambers has a muffler inlet and a muffler outlet, each of the muffler inlets is independently connected to the rotor outlet fluid, and each of the muffler outlets is independently connected to the exhaust port fluid. In the screw compressor of the present application, the muffler group formed by arranging the muffler chambers of multiple expansion mufflers side by side is arranged in the exhaust passage, which not only makes full use of the space of the exhaust passage, but also increases the upper limit of the plane wave, so that the upper limit of the effective muffler frequency is higher, and more noise can be eliminated.

Description

Technical Field

[0001] The present application relates to the field of compressors, and in particular to a screw compressor. Background Art

[0002] The screw compressor includes a pair of rotors, which use the meshing of the rotor teeth to change the volume of the unit composed of the tooth-shaped space to complete the gas suction, compression and discharge process. Since the screw compressor forms a discontinuous inter-tooth volume through the meshing of the rotors, the suction and exhaust chambers are periodically connected to the working chamber, which causes unstable gas flow, causing pressure pulsation during the suction and exhaust process, and then causing compressor vibration and noise. Summary of the invention

[0003] At least one object of the present application is to provide a screw compressor, comprising: a housing, a rotor group, an exhaust passage, and at least one muffler group. The housing has an air intake port and an exhaust port. The rotor group is accommodated in the housing and rotates axially, and the rotor group has a rotor inlet and a rotor outlet. The rotor group is configured to compress the gas sucked from the rotor inlet and discharge it from the rotor outlet, wherein the rotor inlet is fluidically connected to the air intake port, and the rotor outlet is fluidically connected to the exhaust port. The exhaust passage fluidly connects the rotor outlet and the exhaust port, so that the compressed gas discharged from the rotor outlet is discharged from the exhaust port through the exhaust passage. The muffler group is arranged in the exhaust passage to eliminate the noise in the exhaust passage, and the muffler group includes a front end plate, a rear end plate and a plurality of partition plates, the front end plate and the rear end plate are arranged opposite to each other and spaced apart along the axial direction of the rotor group, each of the partition plates is connected between the front end plate and the rear end plate to divide the space between the front end plate and the rear end plate into a plurality of muffler chambers, each of the muffler chambers has a muffler inlet and a muffler outlet, each of the muffler inlets is independently connected to the rotor outlet fluid, and each of the muffler outlets is independently connected to the exhaust port fluid. The muffler inlet is arranged on the front end plate, the muffler outlet is arranged on the rear end plate, and the cross-sectional areas of the muffler inlet and the muffler outlet are smaller than the cross-sectional area of ​​the muffler chamber.

[0004] According to the above content, the several muffler chambers in each muffler group are arranged side by side around the axial direction of the rotor group.

[0005] According to the above, the exhaust passage is defined by a cavity wall, and the front plate and the rear plate of the muffler group are connected to the cavity wall, wherein the cavity wall closes the muffler cavity around the axial direction of the rotor group.

[0006] According to the above, the muffler group includes a sealing plate, which is connected to the front end plate and the rear end plate, and the sealing plate closes the muffler chamber around the axial direction of the rotor group.

[0007] According to the above content, the screw compressor also includes a barrel, which is connected between the front end plate and the rear end plate, and the barrel defines a connecting channel, which directly fluidically connects the rotor outlet and the exhaust port, and the connecting channel extends axially along the rotor group, wherein the plurality of muffler chambers are arranged around the connecting channel on the outside of the barrel.

[0008] According to the above, in the axial section, the exhaust port can cover the connecting passage and the muffler outlet.

[0009] According to the above content, the housing includes an exhaust outer housing and an exhaust inner housing, the exhaust inner housing is arranged inside the exhaust outer housing, the exhaust outer housing and the exhaust inner housing and the exhaust inner housing together define the exhaust passage, and the exhaust passage includes an annular passage surrounding the exhaust inner housing. The exhaust inner housing is provided with an inner housing air outlet, and the inner housing air outlet and the muffler inlet of the muffler group are fluidically connected through the annular passage.

[0010] According to the above content, the front end plate and the rear end plate are arranged in parallel.

[0011] According to the above content, the front end plate and the rear end plate are not arranged in parallel, so that at least a part of the plurality of muffler chambers have different lengths along the axial direction of the rotor group.

[0012] According to the above content, the front end plate and the rear end plate are arranged perpendicular to the axial direction of the rotor group.

[0013] According to the above, at least a part of the muffler inlets in the muffler group is formed by the openings on the front end plate.

[0014] According to the above, the at least one muffler group includes a plurality of muffler groups, the plurality of muffler groups are arranged along the axial direction of the rotor group, and the muffler inlets and muffler outlets of adjacent muffler groups are aligned.

[0015] According to the above content, the muffler group is configured to set the muffler frequency and muffler amount for eliminating the noise in the exhaust channel by the number of muffler chambers, the axial length of the muffler chambers along the rotor group, the cross-sectional area ratio of the muffler inlet to the muffler chamber, and the cross-sectional area ratio of the muffler outlet to the muffler chamber.

[0016] By considering the following specific embodiments, drawings and claims, other features, advantages and embodiments of the present application can be set forth or become apparent. In addition, it should be understood that the above-mentioned summary of the invention and the following specific embodiments are exemplary and are intended to provide further explanations without limiting the scope of the present application for protection. However, the specific embodiments and specific examples only indicate preferred embodiments of the present application. For those skilled in the art, various changes and modifications within the spirit and scope of the present application will become apparent through the specific embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1A is a three-dimensional structural diagram of a screw compressor according to an embodiment of the present application;

[0018] Figure 1B for Figure 1A A top view of the screw compressor shown;

[0019] Figure 2A for Figure 1A An exploded view of the screw compressor shown;

[0020] Figure 2B for Figure 1B The cross-sectional view of the screw compressor along line AA is shown;

[0021] Figure 2C for Figure 1B The cross-sectional view of the screw compressor along line BB is shown;

[0022] Figure 2D for Figure 1B The cross-sectional view of the screw compressor along the CC line is shown;

[0023] Figure 3A for Figure 1A A three-dimensional structural diagram of another embodiment of the exhaust housing;

[0024] Figure 3B for Figure 3A An exploded view of the exhaust housing is shown;

[0025] Figure 3C for Figure 3A A cross-sectional view of the exhaust housing is shown;

[0026] Figure 3D for Figure 3A Another cross-sectional view of the exhaust housing is shown;

[0027] Figure 4A for Figure 1A An exploded view of yet another embodiment of the exhaust housing;

[0028] Figure 4B for Figure 4A A cross-sectional view of the exhaust housing is shown;

[0029] Figure 4C for Figure 4A Another cross-sectional view of the exhaust housing is shown;

[0030] Figure 5A for Figure 1A An exploded view of yet another embodiment of the exhaust housing;

[0031] Figure 5B for Figure 5A A cross-sectional view of the exhaust housing is shown;

[0032] Figure 5C for Figure 5A Another cross-sectional view of the exhaust housing is shown;

[0033] Figure 6 for Figure 1A A cross-sectional view of yet another embodiment of an exhaust housing;

[0034] Fig. 7A for Figure 1A A three-dimensional structural diagram of another embodiment of the muffler group;

[0035] Figure 7B for Fig. 7A A top view of the muffler assembly is shown;

[0036] Fig. 8A for Figure 1A A three-dimensional structural diagram of another embodiment of the exhaust housing;

[0037] Figure 8B for Fig. 8A An exploded view of the exhaust housing shown;

[0038] Fig. 9A for Figure 2A A comparison diagram of the muffler frequency of a muffler cavity in the embodiment and a muffler cavity including an inlet pipe and an outlet pipe;

[0039] Fig. 9B for Figure 2A A comparison chart of the muffler frequencies of multiple muffler chambers and the overall muffler chamber without partition plates. DETAILED DESCRIPTION

[0040] Various specific embodiments of the present application will be described below with reference to the accompanying drawings that form a part of this specification. It should be understood that although terms indicating directions, such as "front", "rear", "upper", "lower", "left", "right", "top", "bottom", etc., are used in this application to describe various example structural parts and elements of the present application, these terms are used here only for the purpose of convenience of description and are determined based on the example orientations shown in the accompanying drawings. Since the embodiments disclosed in the present application can be set in different directions, these terms indicating directions are only for illustration and should not be regarded as limitations.

[0041] Figure 1A and Figure 1B The structure of a screw compressor 100 according to an embodiment of the present application is shown to illustrate the external structure of the screw compressor 100. Figure 1A is a three-dimensional structural diagram of a screw compressor 100, Figure 1B for Figure 1A A top view of the Figure 1A and Figure 1B As shown, the screw compressor 100 includes a housing 101, which is generally in the shape of a long cylinder and includes a rotor housing 102 and an exhaust housing 104 connected in sequence in the length direction. The rotor housing 102 has an air inlet 105, and the rotor housing 102 is mainly used to accommodate the motor 212 and the rotor assembly 221 (see Figure 2B ) rotates therein. The exhaust housing 104 has an exhaust port 106, and the exhaust housing 104 is used to discharge the compressed gas from the exhaust port 106. Therefore, after the gas enters the housing 101 from the air inlet 105, it flows roughly along the length direction and is discharged from the housing 101 from the exhaust port 106 after being compressed.

[0042] Figure 2A-2D Shown as Figure 1A The internal structure of the screw compressor 100 is shown. Figure 2A An exploded view of a screw compressor 100 is shown, Figure 2B A cross-sectional view of the screw compressor 100 along line AA is shown. Figure 2C FIG. 2 shows a cross-sectional view of the screw compressor 100 along line BB. Figure 2D FIG. 2 shows a cross-sectional view of the screw compressor 100 along line CC. Figure 2A-2DAs shown, in this embodiment, the screw compressor 100 is a twin-screw compressor. The rotor group 221 includes a pair of rotors arranged in parallel and side by side, and the pair of rotors includes a male rotor and a female rotor. It can be understood by those skilled in the art that only the male rotor is shown in the cut-away position shown in the figure. The male rotor and the female rotor are meshed with each other, and the male rotor is connected to the motor 212 so that the pair of rotors can be driven by the motor 212 and rotate separately. A pair of rotors have axes parallel to each other, and the male rotor and the female rotor rotate around their respective axes. In this embodiment, the extension direction of the axis is the axial direction of the rotor group 221, the direction around the axial direction is the circumferential direction of the rotor group 221, and the direction perpendicular to the axial direction and the circumferential direction is the radial direction of the rotor group 221.

[0043] The male rotor and the female rotor are each provided with a plurality of spiral teeth, and grooves are formed between adjacent teeth. The male rotor and the female rotor form a meshing structure through their respective teeth and corresponding grooves, and form a plurality of separated compression chambers 225 together with the rotor housing 102. The rotor group 221 has a rotor inlet 222 and a rotor outlet 223. The rotor inlet 222 is located at the left end of the rotor group 221 and is fluidly connected to the air inlet 105. The rotor outlet 223 is located at the right end of the rotor group 221 and is fluidly connected to the exhaust port 106. Each compression chamber 225 moves independently from the rotor inlet 222 to the rotor outlet 223 in the axial direction. The gas is sucked into the compression chamber 225 from the rotor inlet 222, and as the rotor group 221 rotates, the compression chamber 225 gradually moves toward the rotor outlet 223. At the same time, the volume of the compression chamber 225 gradually decreases as the rotor group 221 rotates, and the gas in the compression chamber 225 is gradually compressed. The compressed gas is discharged from the rotor outlet 223 .

[0044] The exhaust housing 104 has an exhaust passage 217 therein. The exhaust port 106 is located in the middle of the exhaust housing 104 , and the rotor outlet 223 is in fluid communication with the exhaust port 106 through the exhaust passage 217 , so that the compressed gas discharged from the rotor outlet 223 is discharged from the exhaust port 106 through the exhaust passage 217 .

[0045] When the screw compressor 100 is running, the meshing of a pair of rotors of the rotor group 221 forms a discontinuous compression chamber 225, so that the compressed gas is intermittently discharged from the rotor outlet 223, and then flows through the exhaust channel 217 and is discharged from the exhaust port 106, thereby generating exhaust pressure pulsations with higher acoustic energy, causing vibration and noise of the screw compressor 100.

[0046] In order to reduce the noise impact caused by exhaust pressure pulsation, the screw compressor 100 further includes at least one muffler group 240, which is arranged in the exhaust passage 217 to eliminate the noise in the exhaust passage 217. In this embodiment, at least one muffler group 240 includes one muffler group. It can be understood by those skilled in the art that, according to the space size of the exhaust passage 217 and the space size of the muffler group 240, at least one muffler group 240 can also include more muffler groups, and these muffler groups can be connected in the exhaust passage 217 in a serial connection or in a parallel connection.

[0047] Specifically, each muffler group 240 includes 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 each other and spaced apart along the axial direction of the rotor group 221, and the partition plate 243 is connected between the front end plate 241 and the rear end plate 242 to divide the space between the front end plate 241 and the rear end plate 242 into a plurality of muffler chambers 248. In the present embodiment, the muffler group 240 also includes a sealing plate 249, which is connected to the outer edges of the front end plate 241 and the rear end plate 242 so that the sealing plate 249 closes each muffler chamber 248 around the axial direction of the rotor group 221. That is, the sealing plate 249, the front end plate 241 and the rear end plate 242 jointly define a closed muffler space, and the partition plate 243 divides the closed muffler space into a plurality of muffler chambers 248. In this embodiment, the front end plate 241 and the rear end plate 242 are arranged substantially in parallel and perpendicular to the axial direction, and the partition plate 243 is connected between the front end plate 241 and the rear end plate 242 in the radial direction.

[0048] Each muffler chamber 248 has a muffler inlet 245 and a muffler outlet 246. The muffler inlet 245 is arranged on the front end plate 241, and the muffler outlet 246 is arranged on the rear end plate 242. The muffler inlet 245 of each muffler chamber 248 is independently connected to the rotor outlet 223 fluid, and the muffler outlet 246 of each muffler chamber 248 is independently connected to the exhaust port 106 fluid. That is, after the compressed gas discharged from the rotor outlet 223 enters the muffler chamber 248 through each muffler inlet 245, it is discharged from the corresponding muffler outlet 246 and then discharged from the exhaust port 106. The cross-sectional area of ​​the muffler inlet 245 and the muffler outlet 246 is smaller than the cross-sectional area of ​​the muffler chamber 248. Due to the change in cross-sectional area, the muffler group 240 can form an expansion type muffler group. When the compressed gas enters the muffler cavity 248 through the muffler inlet 245 and is discharged from the muffler outlet 246, the sound wave energy is consumed, so the muffler group 240 can reduce noise. Figure 2D The cross-sectional areas on the axial section at the muffler inlet and the muffler outlet are shown.

[0049] In the present embodiment, the exhaust housing 104 of the housing 101 includes an exhaust outer housing 214 and an exhaust inner housing 213, and the exhaust inner housing 213 is disposed inside the exhaust outer housing 214. An inner channel 219 in fluid communication with the rotor outlet 223 is defined in the exhaust inner housing 213, and the inner channel 219, the exhaust outer housing 214, and the exhaust inner housing 213 together define an exhaust channel 217. In the present embodiment, the muffler group 240 is disposed at the axial end of the exhaust inner housing 213, the front end plate 241 of the muffler group 240 abuts against the end of the exhaust inner housing 213, and the sealing plate 249 of the muffler group 240 is connected to the inner wall of the exhaust outer housing 214 to fix the position of the muffler group 240 in the exhaust housing 104. As an example, the sealing plate 249 is welded to the exhaust outer housing 214. The exhaust passage 217 includes an annular passage 218 defined by the exhaust inner casing 213, the exhaust outer casing 214, and the front end plate 241 of the muffler group 240. The annular passage 218 is arranged around the exhaust inner casing 213. Each muffler inlet 245 on the front end plate 241 is in fluid communication with the annular passage 218. The inner passage 219 forms an inner casing outlet 215 on the exhaust inner casing 213, and the inner casing outlet 215 is in fluid communication with the annular passage 218. Therefore, after entering the exhaust casing 104, the compressed gas discharged from the rotor outlet 223 is first discharged from the inner casing outlet 215 to the annular passage 218 through the inner passage 219, and then enters the muffler group 240 through the muffler inlet 245, and is discharged from the muffler outlet 246 after being silenced by the muffler group 240, and finally discharged from the exhaust port 106.

[0050] As a specific embodiment, in order to match the annular channel 218, the muffler group 240 also includes a shroud 247 arranged inside the sealing plate 249. The shroud 247 and the sealing plate 249 are radially opposite and spaced. Several partition plates 243 are radially connected between the sealing plate 249 and the shroud 247 to define a number of muffler cavities 248 arranged side by side around the axial direction, and a hollow portion 244 is formed between these muffler cavities 248. On the axial section of the muffler group 240, the hollow portion 244 is roughly the same size as the end of the exhaust inner shell 213, and the muffler cavities 248 arranged side by side have a size that roughly matches the annular channel 218, which will reduce the pressure loss of the compressed gas entering and exiting the muffler group 240 from the annular channel 218. As a more specific example, the hollow portion 244 extends from the middle to the bottom, that is, the muffler cavities 248 arranged side by side along the circumference are not arranged as a full circle. Each muffler inlet 245 and muffler outlet 246 are correspondingly arranged at the lower corner of each muffler cavity 248, such as the corner formed by the partition plate 243 and the sealing plate 249, or the corner formed by the partition plate 243 and the enclosure plate 247. This arrangement is conducive to the lubricating oil and other liquid droplets mixed in the compressed gas to be discharged from the muffler outlet 246 after entering the muffler cavity 248 along with the compressed gas.

[0051] In the embodiment shown in the figure, the inner housing air outlet 215 includes a pair of inner housing air outlets 215a and 215b. The inner channel 219 first extends approximately axially in the exhaust inner housing 213, and then extends radially to both sides of the exhaust inner housing 213 to form the inner housing air outlets 215a and 215b located on both sides of the exhaust inner housing 213. In this arrangement, even if the muffler group 240 abuts against the front end of the exhaust inner housing 213 in the axial direction, the inner housing air outlets 215a and 215b can be fluidly connected to the annular channel 218 from both sides.

[0052] Those skilled in the art will appreciate that, although the sealing plate 249 is included in the present embodiment, in other embodiments, the sealing plate may not be included, and the front end plate 241 and the rear end plate 242 may be directly connected to the inner wall of the exhaust casing 104 to define a closed sound-absorbing space.

[0053] Thus, after the compressed gas enters the exhaust passage 217, the screw compressor 100 can pass through the muffler group 240 to eliminate the noise in the exhaust passage 217. The sound wave is reflected at the cross-sectional area change points of the muffler inlet 245, the muffler cavity 248 and the muffler outlet 246 to reduce the sound wave energy, thereby reducing the noise.

[0054] The muffler group 240 sets the muffler frequency and muffler amount for eliminating noise in the exhaust passage 217 by setting the number of muffler chambers 248, the axial length of the muffler chambers 248, the cross-sectional area ratio of the muffler inlet 245 to the muffler chamber 248, and the cross-sectional area ratio of the muffler outlet 246 to the muffler chamber 248.

[0055] Specifically, the main elimination frequency of the muffler chamber 248 is mainly determined by the axial length of the muffler chamber 248. The shorter the length, the higher the main elimination frequency. In the present embodiment, since the front end plate 241 and the rear end plate 242 are arranged in parallel, the main elimination frequencies of each muffler chamber 248 are approximately the same. In some other embodiments, the front end plate 241 and the rear end plate 242 may be arranged non-parallel so that each muffler chamber 248 has a different main elimination frequency. In the case where the front end plate is not parallel to the rear end plate, the axial length of a muffler chamber is generally preliminarily estimated by the axial center distance of the two end plates, and then based on the projected area of ​​the muffler inlet and the muffler outlet on the cross section, the initial area ratio is calculated, and then the transmission loss curve (Transmission Loss curve) is simulated, and finally the final size parameters of the muffler chamber are determined.

[0056] The upper limit frequency of effective sound attenuation of the sound-absorbing chamber 248 is mainly determined by the number of the sound-absorbing chambers 248. The more the number of sound-absorbing chambers 248 in a space of the same size, the higher the upper limit frequency of effective sound attenuation.

[0057] The noise reduction of the muffler cavity 248 is mainly determined by the cross-sectional area ratio of the muffler inlet 245 to the muffler cavity 248, and the cross-sectional area ratio of the muffler outlet 246 to the muffler cavity 248 (ie, the expansion ratio). The larger the expansion ratio, the greater the noise reduction.

[0058] Figure 3A-3D Another embodiment of an exhaust housing 304 is shown, wherein Figure 3A is a three-dimensional structural diagram of the exhaust housing 304, Figure 3B for Figure 3A An exploded diagram of Figure 3C is a cross-sectional view of the exhaust housing 304 along line DD, Figure 3D FIG. 3 is a cross-sectional view of the exhaust housing 304 along line EE. Figure 3A-3D As shown, in this embodiment, the exhaust housing 304 no longer includes an exhaust inner housing, but an axially extending exhaust channel 317 is directly formed in the exhaust housing 304 , and the exhaust channel 317 is defined by the cavity wall 316 of the exhaust housing 304 , so that the exhaust channel 317 fluid connects the rotor outlet 223 and the exhaust port 306 .

[0059] The structure of the muffler group 340 is also different from that of the muffler group 240. Specifically, the muffler group 340 does not include a sealing plate, and the shapes of the front end plate 341 and the rear end plate 342 thereof match the inner surface shape of the cavity wall 316, so that the front end plate 341 and the rear end plate 342 can be directly connected to the cavity wall 316, thereby forming a closed muffler space between the front end plate 341, the rear end plate 342 and the cavity wall 316. The partition plate 343 is radially connected between the front end plate 341 and the rear end plate 342 to separate the closed muffler space into a plurality of muffler chambers 348. Each muffler chamber 348 has a muffler inlet 345 and a muffler outlet 346 correspondingly arranged on the front end plate 341 and the rear end plate 342. In the present embodiment, the edges of the front end plate 441, the rear end plate 442 and the partition plate 443 are connected to the cavity wall 416, for example, by welding, interference fitting or integral casting.

[0060] In this embodiment, the muffler group 340 further includes a barrel 352, which is connected between the front end plate 341 and the rear end plate 342. The barrel 352 defines a connecting passage 358 extending in the axial direction, and the connecting passage 358 penetrates the front end plate 341 and the rear end plate 342 to directly connect the rotor outlet 223 and the exhaust port 306. In this embodiment, the barrel 352 is connected to the middle of the front end plate 341 and the rear end plate 342, and the partition plate 343 is radially connected between the barrel 352 and the cavity wall 316, so that a plurality of muffler chambers 348 are arranged side by side around the connecting passage 358 outside the barrel 352. By providing the barrel 352 and the connecting passage 358, most of the compressed gas can be discharged through the connecting passage 358 without passing through the muffler group 340, so the muffler group 340 has little effect on the pressure loss of the compressed gas. In this embodiment, the muffler inlet 345 and the muffler outlet 346 of the plurality of muffler cavities 348 are arranged on the front end plate 341 and the rear end plate 342 near the barrel 352, and are evenly arranged circumferentially around the barrel 352. On the axial section of the exhaust housing 304, the exhaust port 306 can cover the connecting channel 358 and the muffler outlet 346, so that the compressed gas can be directly discharged from the exhaust port 306 after flowing through the connecting channel 358 or the muffler group 340. This can further reduce the pressure loss of the compressed gas. The cross-sectional area of ​​the muffler inlet 345 and the muffler outlet 346 is smaller than the cross-sectional area of ​​the muffler cavity 348, so that when the compressed gas enters the muffler cavity 348 through the muffler inlet 345 and is discharged from the muffler outlet 346, the sound wave energy is consumed, so the muffler group 340 can reduce noise.

[0061] Figure 4A-4C Another embodiment of an exhaust housing 404 is shown, wherein Figure 4A is an exploded view of the exhaust housing 404, Figure 4Bis a cross-sectional view of the exhaust housing 404 along line FF, Figure 4C FIG. 4 is a cross-sectional view of the exhaust housing 404 along line GG. Figure 4A-4C As shown, the difference between the exhaust housing 404 and the exhaust housing 304 is that the structure of the muffler group 440 is different from that of the muffler group 340. Specifically, the muffler group 440 also includes a front end plate 441 and a rear end plate 442 arranged substantially in parallel, and a muffler inlet 445 and a muffler outlet 446 respectively arranged on the front end plate 441 and the rear end plate 442, and the muffler inlet 445 and the muffler outlet 446 are arranged correspondingly to reduce the pressure loss of the compressed gas. However, in this embodiment, the partition plate 443 of the muffler group 440 is no longer arranged in a radial shape, but is arranged in a "well" shape to define a square muffler chamber 448. The edges of the front end plate 441, the rear end plate 442 and the partition plate 443 are connected to the cavity wall 416, for example, by welding. The cross-sectional areas of the muffler inlet 445 and the muffler outlet 446 are smaller than the cross-sectional area of ​​the muffler chamber 448, so that when the compressed gas enters the muffler chamber 448 through the muffler inlet 445 and is discharged from the muffler outlet 346, the sound wave energy is consumed, so the muffler group 440 can reduce noise.

[0062] Figure 5A-5C Another embodiment of an exhaust housing 504 is shown, wherein Figure 5A is an exploded view of the exhaust housing 504, Figure 5B The exhaust housing 504 is Figure 3B The cross-sectional view at the DD line in the figure, Figure 5C The exhaust housing 504 is Figure 3B The cross-sectional view at the EE line in FIG. Figure 5A-5CAs shown, the exhaust housing 504 is different from the exhaust housing 304 in that the structure of the muffler group 540 is different from that of the muffler group 340. Specifically, the muffler group 540 also includes a front end plate 541 and a rear end plate 542 arranged substantially in parallel, and a muffler inlet 545 and a muffler outlet 546 respectively arranged on the front end plate 541 and the rear end plate 542, and the muffler inlet 545 and the muffler outlet 546 are arranged correspondingly to reduce the pressure loss of the compressed gas. However, in this embodiment, the barrel 552 no longer penetrates 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 muffler cavity 558 in the barrel 552. And the partition plate 543 is radially connected between the barrel 552 and the cavity wall 516, so that a plurality of muffler cavities 548 are arranged side by side around the muffler cavity 558 outside the barrel 552. The edges of the front plate 541, the rear plate 542 and the partition plate 543 are connected to the cavity wall 516, for example, by welding. The cross-sectional areas of the muffler inlet 545 and the muffler outlet 546 are smaller than the cross-sectional areas of the muffler chamber 548 and the muffler chamber 558, so that when the compressed gas passes through the muffler inlet 545 into the muffler chamber 548 or the muffler chamber 558 and then is discharged from the muffler outlet 546, the sound wave energy is consumed, so that the muffler group 540 can reduce noise.

[0063] Figure 6 Another embodiment of an exhaust housing 604 is shown, wherein Figure 6 The exhaust housing 604 is shown in Figure 3B The cross-sectional view at the EE line in FIG. Figure 6 As shown, the structure of the exhaust housing 604 is roughly the same as that of the exhaust housing 404, except that two muffler groups 640a and 640b with the same structure are provided in the exhaust housing 604 in this embodiment. The structures of the muffler group 640a and the muffler group 640b are the same as those of the muffler group 440, except that the lengths of the muffler chambers in the axial direction are different. The front end plate 641a and the rear end plate 642a of the muffler group 640a and the front end plate 641b and the rear end plate 642b of the muffler group 640b are roughly arranged in parallel, and the muffler inlet 645a and the muffler outlet 646a of the muffler group 640a and the muffler inlet 645b and the muffler outlet 646b of the muffler group 640b are arranged correspondingly to reduce the pressure loss of the compressed gas. Moreover, the cross-sectional area of ​​each muffler inlet and outlet is smaller than the cross-sectional area of ​​the muffler chamber, so that the compressed gas discharged from the rotor outlet 223 can flow through the muffler group 640a and the muffler group 640b in sequence, so that the sound wave energy is consumed, and thus the muffler group 540 can reduce noise.

[0064] Fig. 7A and Figure 7BAnother embodiment of a muffler assembly 740 is shown. Fig. 7A is a three-dimensional structural diagram of the muffler group 740, Figure 7B FIG. 7 is a top view of the muffler assembly 740. Fig. 7A and Figure 7B As shown, in this embodiment, the muffler group 740 also includes a front end plate 741 and a rear end plate 742, and a muffler inlet 745 and a muffler outlet 746 respectively arranged on the front end plate 741 and the rear end plate 742, and the muffler inlet 745 and the muffler outlet 746 are arranged correspondingly to reduce the pressure loss of the compressed gas. However, in this embodiment, the front end plate 741 and the rear end plate 742 are no longer arranged in parallel, but are arranged in a broken line shape. The partition plate 743 of the muffler group 740 is arranged in a "well" shape to define a trapezoidal muffler cavity 748. The cross-sectional area of ​​the muffler inlet 745 and the muffler outlet 746 is smaller than the cross-sectional area of ​​the muffler cavity 748, so that when the compressed gas enters the muffler cavity 748 through the muffler inlet 745 and then is discharged from the muffler outlet 746, the sound wave energy is consumed, so the muffler group 740 can reduce noise.

[0065] Figure 8A-B FIG. 8 shows the specific structure of another embodiment of the exhaust housing 804. Fig. 8A A three-dimensional structural diagram of the exhaust housing 804 is shown. Figure 8B Shows Fig. 8A Exploded diagram of Fig. 8A and Figure 8B As shown, the structure of the exhaust housing 804 is roughly the same as that of the exhaust housing 104, except that the structure of the muffler group 840 is different from that of the muffler group 240, and the position of the exhaust port 806 is different from that of the exhaust port 106. Specifically, the muffler group 840 includes a front end plate 841, a rear end plate 842, a sealing plate 849 and a surrounding plate 847. The front end plate 841 and the rear end plate 842 are arranged opposite to each other and spaced apart in the axial direction, and the surrounding plate 847 and the sealing plate 849 are arranged opposite to each other and spaced apart in the radial direction. The surrounding plate 847 and the sealing plate 849 are connected between the front end plate 841 and the rear end plate 842, and several partition plates (not shown in the figure, see Figure 2D The partition plate 243 shown in the figure is used to form several muffler chambers, and a hollow portion 844 is formed between these muffler chambers. The muffler principle of the muffler group 840 is the same as that of the muffler group 240, which will not be repeated here. Unlike the muffler group 240, the rear end plate 842 no longer closes the hollow portion 844, but only closes each muffler chamber. In other words, the hollow portion 844 is directly connected to the exhaust port 806 fluid. Compared with the muffler group 240, the rear end plate 842 is set in this way. On the one hand, it can reduce the material usage of the rear end plate 842, and on the other hand, it can reduce the possibility that the gas in the exhaust channel impacts the rear end plate 842, causing the rear end plate 842 to vibrate and generate noise.

[0066] Further integration Figure 2D As shown, after the droplets of lubricating oil and the like mixed in the compressed gas enter the silencer cavity along with the compressed gas, part of the liquid can be discharged from the silencer outlet along with the airflow, and the other part of the liquid accumulates at the bottom corners of each silencer cavity under the action of gravity, and is discharged from the silencer outlet after accumulating to a certain amount. The liquid discharged from the silencer outlet is discharged from the exhaust port 806 together with the airflow formed by the compressed gas.

[0067] In this embodiment, the exhaust housing 804 also includes an exhaust outer housing 814 and an exhaust inner housing 813, and the exhaust port 806 is arranged at the bottom of the end surface of the exhaust outer housing 814. This arrangement can make it easier for droplets such as lubricating oil mixed in the compressed gas to be discharged from the exhaust housing 804 in a timely manner.

[0068] Fig. 9A Shows Figure 2A A comparison diagram of the muffler performance of a muffler chamber 248 in the muffler group and a muffler chamber including an inlet pipe and an outlet pipe, Fig. 9B Show Figure 2A A comparison chart of the sound-absorbing performance of multiple sound-absorbing chambers 248 and the overall sound-absorbing chamber without a partition plate, wherein the horizontal axis is the sound wave frequency and the vertical axis is the transmission loss of the sound wave. When the size of the sound-absorbing chamber 248 remains unchanged and the inlet and outlet cross-sectional areas are the same, curve 981 shows the sound-absorbing effect of the sound-absorbing chamber including the inlet pipe and the outlet pipe, and curve 982 shows the sound-absorbing effect of the sound-absorbing chamber 248 including only the muffler inlet and the muffler outlet of the opening shape; curve 983 shows the sound-absorbing effect of the overall sound-absorbing chamber without a partition plate, and curve 984 shows the sound-absorbing effect of multiple sound-absorbing chambers including a partition plate.

[0069] like Fig. 9A As shown, the sound reduction amount of the silencer chamber 248 including only the silencer inlet and the silencer outlet at certain frequencies is less than that of the silencer including the inlet pipe and the outlet pipe, but it can also play a certain role in sound reduction. The sound reduction amount at frequencies above 1400Hz is equivalent to that of the silencer including the inlet pipe and the outlet pipe, and the sound reduction amount in some frequency bands (900-1400Hz) is even higher. And the silencer that does not include the inlet pipe and the outlet pipe can greatly reduce the pressure loss of the compressed gas in the process of flowing through the silencer group. By setting a plurality of silencer chambers 248 arranged side by side, the sound reduction range can be increased and the sound reduction amount can be compensated.

[0070] like Fig. 9BAs shown, the upper limit frequency of effective sound elimination of multiple sound elimination chambers including partitions can reach about 2750Hz, while the sound elimination effect of the whole sound elimination chamber without partitions above about 1700Hz is not ideal. Therefore, in the same size space, the more sound elimination chambers are set, the higher the upper limit frequency of effective sound elimination.

[0071] In existing screw compressors, the compressed gas flowing through the exhaust channel has an exhaust pressure pulsation with high acoustic energy, which causes vibration and noise of the screw compressor. The size of the exhaust channel is limited, especially the length in the axial direction. The muffler set in the exhaust channel needs to meet the size requirements and avoid excessive pressure loss caused by the muffler to the compressed gas.

[0072] In the screw compressor of the present application, a silencer group formed by arranging the silencer chambers of multiple expansion silencers side by side is arranged in the exhaust channel, which not only makes full use of the space of the exhaust channel, but also increases the upper limit of the plane wave, so that the upper limit of the effective silencer frequency is higher and more noise can be eliminated.

[0073] Furthermore, the muffler inlet and the muffler outlet of the muffler group of the present application are open in shape and do not include an inlet pipe and an outlet pipe, so the muffler group will not cause excessive pressure loss to the compressed gas.

[0074] In addition, by providing silencer chambers with different axial lengths, the silencer group of the present application can also eliminate noise in the exhaust passage within a wide frequency range.

[0075] Although the present disclosure has been described in conjunction with the examples of the embodiments summarized above, it is obvious to those of ordinary skill in the art that various alternatives, modifications, variations, improvements and / or substantially equivalent solutions, whether known or now or foreseeable in the near future, may be apparent. Therefore, the examples of the embodiments of the present disclosure as stated 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. Therefore, the present disclosure is intended to include all known or earlier developed alternatives, modifications, variations, improvements and / or substantially equivalent solutions. The technical effects and technical problems in this specification are exemplary rather than restrictive. It should be noted that the embodiments described in this specification may have other technical effects and may solve other technical problems.

Claims

1. A screw compressor, Features include: A housing having an air intake port and an air exhaust port; a rotor group, the rotor group being accommodated in the housing and rotating in the axial direction, the rotor group having a rotor inlet and a rotor outlet, the rotor group being configured to compress the gas sucked from the rotor inlet and discharge it 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; An exhaust passage, wherein the exhaust passage fluidly connects the rotor outlet and the exhaust port so that the compressed gas discharged from the rotor outlet passes through the exhaust passage and is discharged from the exhaust port; as well as at least one muffler group, the muffler group being arranged in the exhaust passage to eliminate noise in the exhaust passage, the muffler group comprising a front end plate, a rear end plate and a plurality of partition plates, the front end plate and the rear end plate being arranged opposite to each other and spaced apart along the axial direction of the rotor group, each of the partition plates being connected between the front end plate and the rear end plate to divide the space between the front end plate and the rear end plate into a plurality of muffler chambers, each of the muffler chambers having a muffler inlet and a muffler outlet, each of the muffler inlets being independently connected to the rotor outlet fluid, and each of the muffler outlets being independently connected to the exhaust port fluid; Wherein, the muffler inlet is arranged on the front end plate, the muffler outlet is arranged on the rear end plate, and the cross-sectional area of ​​each muffler inlet and each muffler outlet is smaller than the cross-sectional area of ​​the muffler chamber.

2. The screw compressor according to claim 1, Features: The plurality of muffler chambers in each muffler group are arranged side by side around the axial direction of the rotor group.

3. The screw compressor according to claim 1, Features: The exhaust passage is defined by a cavity wall, and the front end plate and the rear end plate of the muffler group are connected to the cavity wall; The cavity wall closes the muffler cavity axially around the rotor assembly.

4. The screw compressor according to claim 1, Features: The muffler group includes a sealing plate connected to the front end plate and the rear end plate, and the sealing plate closes the muffler chamber around the axial direction of the rotor group.

5. The screw compressor according to claim 1, Features: The screw compressor also includes a barrel, which is connected between the front end plate and the rear end plate. The barrel defines a connecting channel, which directly fluidically connects the rotor outlet and the exhaust port, and the connecting channel extends axially along the rotor group, wherein the plurality of muffler chambers are arranged around the connecting channel on the outside of the barrel.

6. The screw compressor according to claim 5, Features: In an axial cross section, the exhaust port can cover the connecting passage and the muffler outlet.

7. The screw compressor according to claim 1, Features: The housing comprises an exhaust outer housing and an exhaust inner housing, wherein the exhaust inner housing is disposed inside the exhaust outer housing, the exhaust passage is defined between the exhaust outer housing and the exhaust inner housing and inside the exhaust inner housing, and the exhaust passage comprises an annular passage surrounding the exhaust inner housing; Wherein, an inner shell air outlet is provided on the exhaust inner shell, and the inner shell air outlet and the muffler inlet of the muffler group are fluidically connected through the annular channel.

8. The screw compressor according to claim 1, Features: The front end plate and the rear end plate are arranged in parallel.

9. The screw compressor according to claim 1, Features: The front end plate and the rear end plate are arranged non-parallel to each other, so that at least a portion of the plurality of muffler cavities have different lengths along the axial direction of the rotor group.

10. The screw compressor according to claim 1, Features: The front end plate and the rear end plate are arranged perpendicular to the axial direction of the rotor group.

11. The screw compressor according to claim 1, Features: At least a portion of the muffler inlets in the muffler group are formed by openings in the front end plate, and at least a portion of the muffler outlets in the muffler group are formed by openings in the rear end plate; and / or The muffler group is an expansion type muffler.

12. The screw compressor according to claim 1, Features: The at least one muffler group includes a plurality of muffler groups, the plurality of muffler groups are arranged along the axial direction of the rotor group, and the muffler inlets and muffler outlets of adjacent muffler groups are aligned.

13. The screw compressor according to claim 1, Features: The muffler group is configured to set the muffler frequency and muffler amount for eliminating noise in the exhaust passage by the number of the muffler chambers, the axial length of the muffler chambers along the rotor group, the cross-sectional area ratio of the muffler inlet to the muffler chamber, and the cross-sectional area ratio of the muffler outlet to the muffler chamber.

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