Screw compressor

Abstract

The present application discloses a screw compressor, comprising: a housing; a pair of rotors; an internal exhaust channel, wherein the internal exhaust channel fluid connects the rotor exhaust outlet and the exhaust volume; and a plurality of mufflers, wherein the plurality of mufflers are arranged on at least a portion of the defining wall of the internal exhaust channel, wherein the plurality of mufflers include a plurality of resonant mufflers. The resonant muffler of the present application can prevent the structure of the resonant muffler from being destroyed by the exhaust pressure pulse, and at the same time can discharge the accumulated liquid in the muffler structure in real time, thereby ensuring the stability of the muffler effect, and therefore can be arranged in an internal exhaust channel where the exhaust pressure pulsation energy is very high. Moreover, the resonant muffler of the present application has an acoustic superstructure, and not only each resonant muffler has a good muffler effect and occupies a small space, but also a plurality of resonant mufflers with different predetermined natural frequencies can eliminate the noise in the internal exhaust channel within a wide frequency range.

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 tooth groove volume of the pair of rotors to mesh with each other, causing the change of the elementary volume composed of the tooth 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 with the working chamber, which causes unstable flow of gas, causing pressure pulsation during the suction and exhaust process, and then causing vibration and noise of the compressor. Summary of the invention

[0003] At least one object of the present application is to provide a screw compressor, comprising: a shell, the shell having a rotor cavity and an exhaust cavity, the rotor cavity and the exhaust cavity being fluidically connected; a pair of rotors, the pair of rotors being arranged in the rotor cavity, a compression cavity being able to be formed between the teeth of the pair of rotors and the shell, the pair of rotors having a rotor suction inlet and a rotor exhaust outlet, the pair of rotors being arranged so that as the pair of rotors rotate, the gas in the compression cavity can move from the rotor suction inlet to the rotor exhaust outlet; an internal exhaust channel, the internal exhaust channel fluidly connecting the rotor exhaust outlet and the exhaust cavity, wherein the internal exhaust channel is defined and formed by the rotor and a defining wall; and a plurality of silencers, the plurality of silencers being arranged on at least a portion of the defining wall of the internal exhaust channel, wherein the plurality of silencers include a plurality of resonance silencers, each of the resonance silencers being configured to have a predetermined natural frequency, so as to reduce the noise by resonating with a sound wave having the predetermined natural frequency in the noise in the internal exhaust channel.

[0004] According to the above content, the screw compressor also includes: a sliding valve, which is configured to be able to move axially relative to the pair of rotors, and the sliding valve has an exhaust end wall, and the exhaust end wall axially closes one end of the internal exhaust channel; wherein the plurality of silencers are arranged on the exhaust end wall.

[0005] According to the above content, the shell includes an exhaust shell, the exhaust shell has the exhaust volume cavity, the internal exhaust channel forms an internal exhaust hole on the exhaust shell, and the limiting wall includes the hole wall of the internal exhaust hole; wherein the silencer is arranged on the hole wall of the internal exhaust hole.

[0006] According to the above content, the shell includes a rotor shell, the rotor shell has the rotor cavity, the internal exhaust channel forms an internal exhaust hole on the rotor shell, and the limiting wall includes the hole wall of the internal exhaust hole; wherein the silencer is arranged on the hole wall of the internal exhaust hole.

[0007] According to the above, the plurality of silencers are formed integrally with the limiting wall.

[0008] According to the above content, the limiting wall includes a mounting plate, and the plurality of silencers are arranged on the mounting plate, wherein the mounting plate and the plurality of silencers are formed by a 3D printing process or a CNC machining process.

[0009] According to the above content, the limiting wall also includes a mounting groove, and the mounting plate is connected in the mounting groove.

[0010] According to the above content, the resonance silencer is an acoustic superstructure.

[0011] According to the above, at least a portion of the plurality of resonance silencing devices are configured to have different predetermined natural frequencies.

[0012] According to the above content, the limiting wall has a wall surface, and each of the resonance silencers includes a resonance cavity and a connecting pipe. The connecting pipe extends from the wall surface of the limiting wall into the interior of the resonance cavity and fluidly connects the resonance cavity and the internal exhaust channel.

[0013] According to the above content, the inner surface of the wall is a partial spherical surface.

[0014] According to the above, each of the resonance muffler devices further includes a pressure balance channel extending through the wall surface to fluidically connect the resonance chamber and the internal exhaust channel.

[0015] According to the above, each of the resonance muffler devices is configured to form the predetermined natural frequency through the volume of the resonance cavity, the length of the connecting pipe, the pressure balance channel and the inner diameter of the connecting pipe.

[0016] According to the above content, the plurality of silencers further include a plurality of interference silencers, and at least a portion of the plurality of interference silencers are arranged at intervals between the plurality of resonance silencers.

[0017] 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

[0018] Figure 1A is a three-dimensional structural diagram of a screw compressor according to an embodiment of the present application;

[0019] Figure 1B for Figure 1A A three-dimensional structural diagram of the screw compressor from another angle;

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

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

[0022] Figure 3A for Figure 2A A three-dimensional structural diagram of an embodiment of a slide valve in FIG.

[0023] Figure 3B for Figure 2A A three-dimensional structural diagram of another embodiment of the slide valve;

[0024] Figure 4A for Figure 3B A schematic structural diagram of an embodiment of a muffler device;

[0025] Figure 4B for Figure 3B A schematic structural diagram of another embodiment of the muffler device;

[0026] Figure 5A for Figure 4A Schematic diagram of the structure of the medium resonance silencing device;

[0027] Figure 5B for Figure 5A An axial cross-sectional view of the resonance muffler device shown;

[0028] Fig. 6A for Figure 1A A three-dimensional structural diagram of an embodiment of an exhaust housing;

[0029] Figure 6B for Figure 1A A three-dimensional structural diagram of a mounting portion in another embodiment of an exhaust housing;

[0030] Fig. 7A is a three-dimensional structural diagram of an embodiment of an exhaust casing in a screw compressor according to another embodiment of the present application;

[0031] Figure 7B A three-dimensional structural diagram of another embodiment of an exhaust casing in a screw compressor according to another embodiment of the present application;

[0032] Fig. 8A is a three-dimensional structural diagram of an embodiment of a rotor housing in a screw compressor according to yet another embodiment of the present application;

[0033] Figure 8B It is a three-dimensional structural diagram of another embodiment of the rotor housing in a screw compressor according to yet another embodiment of the present application. DETAILED DESCRIPTION

[0034] 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.

[0035] Figure 1A and Figure 1B A three-dimensional structural diagram of a screw compressor 100 according to an embodiment of the present application is shown, which is used to illustrate the external structure of the screw compressor 100. Figure 1A Shows a three-dimensional structural diagram from the front and back angles, Figure 1B 1 shows a three-dimensional structure diagram viewed from the back to the front. 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 motor housing 102, a rotor housing 103 and an exhaust housing 104 connected in sequence in the length direction. The motor housing 102 has an air inlet 105, which is mainly used to accommodate the motor 212 (see Figure 2A The rotor housing 103 has a rotor cavity 213 (see Figure 2A1 and 2) for accommodating a pair of rotors 221 and 222 for rotation therein. The exhaust housing 104 has an exhaust port 106 for discharging compressed gas. Thus, 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.

[0036] Figure 2A and Figure 2B Shown as Figure 1A The internal structure of the screw compressor 100 is shown. Figure 2A FIG. 2 shows a cross-sectional view of the screw compressor 100 along the line AA at the slide valve 210 . Figure 2B FIG. 2 shows a cross-sectional view of the screw compressor 100 along line BB. Figure 2A and Figure 2B As shown, a pair of rotors arranged roughly in parallel and side by side are accommodated in the rotor cavity 213, and the pair of rotors include a male rotor 221 and a female rotor 222, the male rotor 221 and the female rotor 222 are meshed with each other, and the male rotor 221 is connected to the motor 212, so that the pair of rotors can be driven by the motor 212 to rotate separately. The male rotor 221 and the female rotor 222 have axes parallel to each other, and the male rotor 221 and the female rotor 222 rotate around their respective axes. In this embodiment, the extension direction of the axis is the axial direction, and the pair of rotors can rotate around its axial direction.

[0037] The male rotor 221 and the female rotor 222 are each provided with a plurality of spiral teeth, and grooves are formed between adjacent teeth. The male rotor 221 and the female rotor 222 form a meshing structure through the teeth and the corresponding grooves, and form a separated compression chamber 225 together with the housing rotor. A pair of rotors has a rotor air intake inlet 223 and a rotor exhaust outlet 224. The gas is sucked into the compression chamber 225 from the rotor air intake inlet 223, and as the pair of rotors rotate, the compression chamber 225 gradually moves toward the rotor exhaust outlet 224. At the same time, the volume of the compression chamber 225 gradually decreases as the pair of rotors rotate, and the gas in the compression chamber 225 is gradually compressed. The compressed gas is discharged from the rotor exhaust outlet 224.

[0038] In this embodiment, the screw compressor 100 further includes a slide valve 210, which is disposed below a pair of rotors and extends axially along the pair of rotors. The slide valve 210 is connected to a drive device 231 so that the slide valve 210 can be driven by the drive device 231 to move axially. Through the movement of the slide valve 210, the slide valve 210 can close or block a portion of the compression chamber 225, thereby adjusting the size of the rotor exhaust outlet 224, and further adjusting the internal volume ratio or load of the screw compressor 100. The specific structure of the slide valve 210 is as follows: Figure 3A and Figure 3BThose skilled in the art can understand that, in some embodiments, the screw compressor may not include the slide valve 210, and other methods may be used to adjust the load of the screw compressor, or the load of the screw compressor may not be adjusted.

[0039] The exhaust housing 104 has an exhaust cavity 214 in fluid communication with the exhaust port 106, and the exhaust cavity 214 is in fluid communication with the rotor cavity 213, so that the gas in the rotor cavity 213 discharged from the rotor exhaust outlet 224 can be discharged from the exhaust port 106 through the exhaust cavity 214. Specifically, the housing 101 also includes an internal exhaust channel 218, and the gas discharged from the rotor exhaust outlet 224 is in fluid communication with the exhaust cavity 214 through the internal exhaust channel 218. The internal exhaust channel 218 is defined by a pair of rotors and a limiting wall. The specific structure of the exhaust housing 104 is shown in FIG6.

[0040] In this embodiment, the internal exhaust passage 218 is defined by a pair of rotors, the slide valve 210 and the exhaust housing 104. The internal exhaust passage 218 forms an internal exhaust hole 219 on the exhaust housing 104. The exhaust end wall 335 (see FIG. 33) of the slide valve 210 Figure 3A and Figure 3B ) closes one end of the internal exhaust passage 218 in the axial direction, and the other end of the internal exhaust passage 218 is in fluid communication with the exhaust chamber 214 through the internal exhaust hole 219. Figure 3A and Figure 3B ), a pair of rotors and the rotor housing 103 close the internal exhaust passage 218 in the circumferential direction. Thus, the internal exhaust passage 218 communicating with the rotor exhaust outlet 224 and the exhaust chamber 214 can be formed.

[0041] When the screw compressor 100 is running, the meshing of a pair of rotors 221 and 222 forms a discontinuous compression chamber 225, so that the compressed gas is intermittently discharged from the rotor exhaust outlet 224, thereby generating exhaust pressure pulsations with higher acoustic energy, causing vibration and noise of the screw compressor 100.

[0042] In this embodiment, the screw compressor 100 further includes a plurality of mufflers 340 (see Figure 3A , Figure 3B 6), these mufflers 340 are arranged on a part of the defining wall for defining the internal exhaust passage 218. Therefore, after the exhaust pressure pulsation is generated, the compressed gas in the screw compressor 100 can reduce the energy of the exhaust pressure pulsation on the flow path before flowing to the exhaust volume 214, that is, in the internal exhaust passage 218, thereby reducing the noise impact caused by the exhaust pressure pulsation.

[0043] Figure 3Aand Figure 3B 3D diagrams of two embodiments of the slide valve 210 . The silencer 340 of the two embodiments is disposed on the exhaust end wall 335 of the slide valve 210 . The only difference is that the silencer 340 is disposed in a different manner.

[0044] like Figure 3A and Figure 3B As shown, the slide valve 210 includes a slide valve body 338 and a head end 337 disposed at the head of the slide valve body 338. The slide valve body 338 has a pair of rotor contact surfaces 336, and the rotor contact surfaces 336 have a shape that matches with a pair of rotors. Figure 2B From the perspective of the embodiment, the pair of rotor contact surfaces 336 can contact with the pair of rotors and form a seal, thereby preventing the gas in the compression chamber 225 from leaking from between the pair of rotors and the rotor contact surfaces 336. When the slide valve 210 moves, the slide valve body 338 can close or cover a portion of the compression chamber 225, and the head end 337 is used to expose another portion of the compression chamber 225 to form the rotor exhaust outlet 224.

[0045] Combination Figure 2A From the perspective of FIG. 2 , the exhaust end wall 335 and the head end top wall 332 of the head end 337 are used to define the internal exhaust passage 218. That is, the compressed gas discharged from the rotor exhaust outlet 224 will flow into the exhaust volume 214 along the exhaust end wall 335 and the head end top wall 332 of the head end 337. In this embodiment, a plurality of silencers 340 are arranged on the exhaust end wall 335 of the head end 337 to reduce the noise caused by the exhaust pressure pulsation at the position closest to the exhaust pressure pulsation.

[0046] In such Figure 3A and Figure 3B In the illustrated embodiment, the slide valve 210 further includes a mounting portion 334, and the silencer 340 is disposed on the mounting portion 334. When manufacturing the slide valve 210, the mounting portion 334 and the silencer 340 are first formed as one piece by a 3D printing process or a CNC machining process, and then the mounting portion 334 is connected to the slide valve body 338 to set the silencer 340 on the exhaust end wall 335. As an example, the mounting portion 334 can be connected to the slide valve body 338 by interference connection, riveting, welding, gluing, etc. Figure 3A In the illustrated embodiment, the mounting portion 334 is a "V" shaped structure, and the mounting portion 334 is connected to the end of the slide valve body 338 by an interference fit through a connecting structure 339. The exhaust end wall 335 is formed by the mounting portion 334. Figure 3B In the illustrated embodiment, a pair of mounting grooves 333 are provided on the exhaust end wall 335 , the mounting portion 334 includes a pair of mounting plates, the silencer 340 is disposed on the pair of mounting plates, and the pair of mounting plates are respectively connected to the pair of mounting grooves 333 .

[0047] The mounting portion 334 can be made of the same material as the other parts of the slide valve 210, or can be made of different materials. In this embodiment, the mounting portion 334 is made of an aluminum alloy material with a certain expansion capacity, and the other parts of the slide valve 210 are made of cast steel or cast iron materials with higher strength.

[0048] Those skilled in the art will appreciate that, in some embodiments, the mounting portion 334 may not be included, and the silencers 340 may be directly formed integrally with the exhaust end wall 335. As an example, when manufacturing the slide valve 210, the entire slide valve 210 is integrally formed by a 3D printing process, so that the silencers 340 are directly formed on the exhaust end wall 335 of the slide valve 210. However, due to the high cost of 3D printing and CNC machining, the cost of an integrally formed slide valve is higher than that of a mounting portion 334 that can be manufactured separately.

[0049] Figure 4A and Figure 4B The structures of two embodiments of the muffler 340 are shown to illustrate the arrangement structure of the muffler 340. Figure 4A The middle muffler 340 only includes the resonance muffler 450, Figure 4B The silencer 340 includes a resonance silencer 450 and an interference silencer 460 .

[0050] like Figure 4A As shown, the mounting portion 334 is provided with a plurality of resonant silencers 450 arranged in sequence, and these resonant silencers 450 are acoustic superstructures. Each resonant silencer 450 has a predetermined natural frequency. These resonant silencers 450 reduce the excitation energy of the exhaust pressure pulsation by resonating with the sound waves having the same predetermined natural frequency in the noise in the internal exhaust passage 218, thereby reducing the exhaust noise. When at least a portion of these resonant silencers 450 have different predetermined natural frequencies, these resonant silencers 450 can reduce the exhaust noise in a wide frequency range.

[0051] As an example, these resonance silencers 450 are evenly arranged on the mounting portion 334, for example, in rows, and the resonance silencers 450 in each row are arranged at intervals, and the resonance silencers 450 between adjacent rows are staggered. Each resonance silencer 450 includes a resonance cavity 443, a connecting pipe 441, and a pressure balance channel 442. The resonance cavity 443 is generally cylindrical in shape, and its axial direction is arranged inside the mounting portion 334 along the thickness direction of the mounting portion 334. The connecting pipe 441 and the pressure balance channel 442 form holes on the outer surface of the mounting portion 334 to fluidically connect the resonance cavity 443 inside the mounting portion 334 and the internal exhaust channel 218 outside the mounting portion 334. The specific structure of each resonance silencer 450 will be combined with Figure 5A and Figure 5B Provide detailed explanation.

[0052] like Figure 4B As shown, the arrangement of the resonance muffler 450 is similar to Figure 4A The embodiments shown are the same, except that Figure 4B In the illustrated embodiment, the muffler 340 includes, in addition to the resonance muffler 450, several interference mufflers 460. These interference mufflers 460 are arranged at the intervals between adjacent resonance mufflers 450. As an example, an interference muffler 460 may also be arranged between the resonance muffler 450 and the edge of the mounting portion 334. These interference mufflers 460 reduce the exhaust noise by interfering with sound waves of a certain wavelength in the noise in the internal exhaust channel 218. As a specific example, each interference muffler 460 includes an interference channel 439, which forms a hole on the outer surface of the mounting portion 334 so that the internal exhaust channel 218 outside the mounting portion 334 is fluidically connected to the interference channel 439. The interference channel 439 serves as a bypass of the internal exhaust channel 218, and its length is an odd multiple of a quarter wavelength of the target noise, so that the gas can form an interference superposition with the noise after being reflected from the interference channel 439. On the other hand, air column resonance is excited in the interference channel 439, thereby forming a standing wave node at the junction of the outlet of the interference channel 439 (i.e., the hole formed by the interference channel 439 on the outer surface of the mounting portion 334) and the internal exhaust channel 218, thereby reducing the energy of the noise.

[0053] and Figure 4A Compared to the embodiment shown, Figure 4B The embodiment shown includes more silencers, which can achieve better silencer effect. However, more silencers will make the size of the hollow part in the mounting portion 334 larger, which may affect the strength of the mounting portion 334. Those skilled in the art can set an appropriate number of silencers according to the actual noise and the material and strength of the mounting portion 334.

[0054] Figure 5A and Figure 5B The specific structure of a resonance muffler 450 is shown, wherein Figure 5A is a schematic diagram of the structure of the resonance silencing device 450, Figure 5B for Figure 5A In order to more clearly illustrate the specific structure of the resonance muffler 450, Figure 5A The resonance silencer 450 in FIG. 4 schematically shows a cylindrical outer wall 544 around its resonance cavity 443 . The actual outer wall is formed by the mounting portions spaced apart between the resonance silencer 450 .

[0055] like Figure 5A and Figure 5B As shown, the mounting portion 334 has a wall 545 and a wall 546, and the resonance chamber 443 of the resonance muffler 450 is arranged between the wall 545 and the wall 546. The connecting pipe 441 extends a certain length from the wall 545 to the inside of the resonance chamber 443. The pressure balance channel 442 is arranged opposite to the connecting pipe 441, and the pressure balance channel 442 is located above the connecting pipe 441 and penetrates the wall 545. The extending directions of the connecting pipe 441 and the pressure balance channel 442 are substantially parallel and both are consistent with the axial direction of the resonance chamber 443. The connecting pipe 441 and the pressure balance channel 442 can fluidly connect the resonance chamber 443 and the internal exhaust channel 218 outside the mounting portion 334. As an example, the pressure balance channel 442 is arranged at the bottom of the wall 545, and the connecting pipe 441 is arranged at the top of the wall 545.

[0056] In this embodiment, the resonance cavity 443, the connecting pipe 441 and the pressure balance channel 442 together form a resonance silencer 450. By setting the volume of the resonance cavity 443, the length of the connecting pipe 441, the pressure balance channel 442 and the inner diameter of the connecting pipe 441, each resonance silencer 450 can have a predetermined natural frequency, and several resonance silencer devices 450 can have different predetermined natural frequencies.

[0057] The pressure balance channel 442 is used to balance the pressure inside and outside the resonance cavity 443. Specifically, the gas discharged from the rotor exhaust outlet 224 after compression will have a higher pressure and produce exhaust pressure pulsation. The pressure balance channel 442 can balance the pressure inside and outside the resonance cavity 443 to prevent the exhaust pressure pulsation from causing pressure shock to the resonance cavity 443. In addition, when the gas discharged from the rotor exhaust outlet 224 is mixed with liquids such as oil or water, the pressure balance channel 442 can also help to discharge the liquid in the resonance cavity 443 from the connecting pipe 441 in time, so as to avoid the resonance muffler 450 being affected by the liquid in the resonance cavity 443 and failing to reach the predetermined natural frequency as expected.

[0058] In order to further reduce the pressure shock caused by exhaust pressure pulsation on the resonance chamber 443, the inner surface of the wall 545 is also set to a partial spherical shape in this embodiment. It can be understood by those skilled in the art that when the mounting portion is made of a stronger material, the inner surface of the wall 545 can also be set to a plane or other shape.

[0059] In some embodiments, the mounting portion 334 may not include the wall 546, and the resonant cavity 443 may be directly defined by the sliding valve body or the mounting groove to further save materials for 3D printing or CNC machining, thereby saving costs.

[0060] The resonance silencer 450 of the present application can effectively avoid the influence of exhaust pressure pulsation on the resonance silencer 450 by setting the shape of the pressure balance channel 442 and the wall 545, and is suitable for working in an environment with high pressure and the presence of liquid. Therefore, it can be suitable for being set on the limiting wall of the internal exhaust channel of the compressor.

[0061] Fig. 6A is a three-dimensional structural diagram of an embodiment of the exhaust housing 104 in the screw compressor 100, Figure 6B FIG. 1 shows a specific structure of the mounting portion 634 in another embodiment of the exhaust housing 104. In order to more clearly show the structure of the mounting portion 634, Figure 6B In the embodiment of the exhaust housing shown, other parts of the exhaust housing are omitted. Fig. 6A , Figure 6B Combination Figure 2A As shown, the exhaust volume 214 in the exhaust housing 104 is in fluid communication with the internal exhaust passage 218, and the internal exhaust passage 218 forms an internal exhaust hole 219 on the wall surface of the exhaust housing 104. The hole wall 661 of the internal exhaust hole 219 extends substantially along the axial direction of the rotor to form a part of the defining wall of the internal exhaust passage 218, and the muffler 340 is disposed on the hole wall 661. Figure 6B In the illustrated embodiment, the exhaust housing includes a mounting portion 634, and the internal exhaust hole 219 is formed by the mounting portion 634. The muffler 340 is disposed on the mounting portion 634, and the mounting portion 634 is used to connect to other parts of the exhaust housing.

[0062] In this embodiment, the silencer 340 is disposed on both the slide valve 210 and the exhaust housing 104 for forming the internal exhaust passage 218. In some embodiments, the silencer 340 may be disposed on only one of the slide valve 210 or the exhaust housing 104.

[0063] Fig. 7A and Figure 7B The specific structures of two embodiments of the exhaust housing in the screw compressor according to another embodiment of the present application are shown, wherein in order to more clearly show the specific structure of the exhaust housing, Fig. 7A and Figure 7B The other parts of the screw compressor are omitted, and only the exhaust casing is shown. Fig. 7A and Figure 7BIn the two exhaust housing embodiments shown, the exhaust housing 704 has an exhaust cavity 214, and the internal exhaust passage forms an internal exhaust hole 719 on the exhaust housing 704. The internal exhaust hole 719 has a radial hole wall 762 and an axial hole wall 761. The axial hole wall 761 extends substantially along the axial direction of the rotor, and the radial hole wall 762 is substantially perpendicular to the axial hole wall 761 to form a part of the defining wall of the internal exhaust passage. The muffler 340 is arranged on each hole wall of the internal exhaust hole 719 through the mounting portion 734. Fig. 7A In the embodiment shown, the muffler 340 is disposed on the radial hole wall 762 of the internal exhaust hole 719. Figure 7B In the illustrated embodiment, the silencer 340 is disposed on the axial hole wall 761 of the internal exhaust hole 719. Those skilled in the art will appreciate that, when the space and strength of the internal exhaust hole can meet the requirements, the silencer 340 may also be disposed on both the axial hole wall 761 and the radial hole wall 762.

[0064] Fig. 8A and Figure 8B The specific structures of two embodiments of the rotor housing in a screw compressor according to another embodiment of the present application are shown, wherein in order to more clearly show the specific structure of the rotor housing, Fig. 8A and Figure 8B The other parts of the screw compressor are omitted in the figure, and only the rotor housing is shown. Fig. 8A and Figure 8B As shown, the rotor housing 803 has a rotor cavity 213, and the rotor cavity 213 is used to accommodate a pair of rotors rotating therein. In the screw compressor of this embodiment, the internal exhaust passage forms an internal exhaust hole 819 on the rotor housing 803. The internal exhaust hole 819 has a radial hole wall 862 and an axial hole wall 863, and the axial hole wall 863 extends approximately along the axial direction of the rotor, and the radial hole wall 862 is approximately perpendicular to the axial hole wall 863 to form a part of the defining wall of the internal exhaust passage. The muffler 340 is arranged on the radial hole wall 862 and the axial hole wall 863.

[0065] In such Fig. 8A In the embodiment of the rotor housing shown, the rotor housing 803 includes a mounting portion 834, and the internal exhaust hole 819 is formed by the mounting portion 834. The muffler 340 is disposed on the mounting portion 834, and the mounting portion 834 is used to connect to other parts of the rotor housing 803.

[0066] And in Figure 8B In an embodiment of the rotor housing, Fig. 8AThe difference of the embodiment shown is that the mounting portion is formed by three parts: mounting portion 834a, mounting portion 834b and mounting portion 834c, and a plurality of mufflers 340 are arranged on the mounting portions of these three parts. Three mounting grooves 833 are arranged at corresponding positions on the rotor housing 803, respectively used to install the mounting portions of these three parts.

[0067] It will be appreciated by those skilled in the art that, according to different embodiments of the screw compressor, the above Figure 3A and Figure 3B The slide valve shown, Figure 6A-6B He Ru Figure 7A-7B The exhaust housing shown and Figure 8A-8B The rotor housing shown can be used in combination or alone. It is only necessary to set a silencer on the limiting wall of the internal exhaust passage so that the silencer can reduce the energy of the exhaust pressure pulsation of the compressed gas before entering the exhaust chamber to reduce or eliminate the noise.

[0068] In existing screw compressors, the compressed gas discharged from the rotor exhaust outlet has an exhaust pressure pulsation with high acoustic energy, which causes vibration and noise of the screw compressor. In the process of entering the exhaust chamber from the rotor exhaust outlet through the internal exhaust channel, the compressed gas in the internal exhaust channel is usually at a high temperature and pressure, and often contains liquids such as oil or water.

[0069] In the screw compressor of the present application, the silencer is arranged in the internal exhaust channel, that is, on the flow path of the compressed gas discharged from the rotor exhaust outlet to the exhaust chamber, so that the noise can be eliminated more quickly and efficiently at the location closest to the exhaust pressure pulsation.

[0070] The resonance silencer of the present application has a pressure balance channel and a partially spherical wall shape, which can increase the ability of the resonance silencer to withstand pressure and prevent the structure of the resonance silencer from being destroyed by exhaust pressure pulses. At the same time, it can discharge the accumulated liquid in the silencer structure in real time to ensure the stability of the silencer effect. Therefore, it can be set in an internal exhaust channel where the exhaust pressure pulsation energy is very high.

[0071] In addition, the resonant silencer device of the present application has an acoustic superstructure, which achieves the purpose of reducing noise by forming resonance with sound waves of certain frequencies in the noise to reduce the energy of the exhaust pressure pulse. Not only does each resonant silencer device have a good silencer effect and occupies a small space, but multiple resonant silencer devices with different predetermined natural frequencies can also eliminate noise in the internal exhaust channel within a wide frequency range.

[0072] In addition, the resonance silencer of the present application can also be used in combination with other types of silencers such as interference silencers to achieve better silencer effects.

[0073] 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, characterized in that include: A housing (101), wherein the housing (101) has a rotor chamber (213) and an exhaust chamber (214), wherein the rotor chamber (213) and the exhaust chamber (214) are in fluid communication; A pair of rotors (221, 222), the pair of rotors (221, 222) being arranged in the rotor cavity (213), a compression cavity (225) being formed between the teeth of the pair of rotors (221, 222) and the housing (101), the pair of rotors (221, 222) having a rotor air intake inlet (223) and a rotor air exhaust outlet (224), the pair of rotors (221, 222) being arranged such that as the pair of rotors (221, 222) rotate, gas in the compression cavity (225) can move from the rotor air intake inlet (223) to the rotor air exhaust outlet (224); an internal exhaust passage (218) that fluidically connects the rotor exhaust outlet (224) and the exhaust volume (214), wherein the internal exhaust passage (218) is defined by the rotor (221, 222) and a defining wall; and a plurality of silencers (340), the plurality of silencers (340) being disposed on at least a portion of the defining wall (335, 661, 761, 762, 862, 863) of the internal exhaust passage (218), wherein the plurality of silencers (340) include a plurality of resonant silencers (450), each of the resonant silencers (450) being configured to have a predetermined natural frequency so as to reduce the noise in the internal exhaust passage (218) by forming resonance with a sound wave having the predetermined natural frequency; The limiting wall has a wall surface (545), and each of the resonance muffler devices (450) includes a resonance cavity (443) and a connecting pipe (441). The connecting pipe (441) extends from the wall surface (545) of the limiting wall into the interior of the resonance cavity (443) and fluidically connects the resonance cavity (443) and the internal exhaust channel (218).

2. The screw compressor according to claim 1, characterized in that Also includes: a slide valve (210), the slide valve (210) being configured to be movable in the axial direction relative to the pair of rotors (221, 222), the slide valve (210) having an exhaust end wall (335), the exhaust end wall (335) closing one end of the internal exhaust passage (218) in the axial direction; The plurality of silencers (340) are arranged on the exhaust end wall (335).

3. The screw compressor according to claim 1, characterized in that: The housing (101) comprises an exhaust housing (104, 704), the exhaust housing (104, 704) has the exhaust volume (214) therein, the internal exhaust passage (218) forms an internal exhaust hole (219, 719) on the exhaust housing (104, 704), and the limiting wall comprises a hole wall (661, 761, 762) of the internal exhaust hole (219, 719); The silencer (340) is arranged on the hole wall (661, 761, 762) of the internal exhaust hole (219, 719).

4. The screw compressor according to claim 1, characterized in that: The housing (101) comprises a rotor housing (803), the rotor housing (803) has the rotor cavity (213) therein, the internal exhaust passage (218) forms an internal exhaust hole (819) on the rotor housing (803), and the limiting wall comprises a hole wall (862, 863) of the internal exhaust hole (819); The silencer (340) is arranged on the hole wall (862, 863) of the internal exhaust hole (819).

5. The screw compressor according to any one of claims 1 to 4, characterized in that: The plurality of silencers (340) are formed integrally with the limiting walls (335, 661, 761, 762, 862, 863).

6. The screw compressor according to any one of claims 1 to 4, characterized in that: The limiting wall (335) includes a mounting plate (334), and the plurality of silencers (340) are arranged on the mounting plate (334), wherein the mounting plate (334) and the plurality of silencers (340) are formed by a 3D printing process or a CNC machining process.

7. The screw compressor according to any one of claims 6, characterized in that: The limiting wall (335) further includes a mounting groove (333), and the mounting plate (334) is connected in the mounting groove (333).

8. The screw compressor according to any one of claims 1 to 4, characterized in that: The resonance silencing device (450) is an acoustic superstructure.

9. The screw compressor according to claim 8, characterized in that: At least a portion of the plurality of resonance noise reduction devices (450) are configured to have different predetermined natural frequencies.

10. The screw compressor according to claim 1, characterized in that: The inner surface of the wall (545) is a partial spherical surface.

11. The screw compressor according to claim 10, characterized in that: Each of the resonance muffler devices (450) further includes a pressure balance passage (442) extending through the wall surface (545) to fluidically connect the resonance chamber (443) and the internal exhaust passage (218).

12. The screw compressor according to claim 11, characterized in that: Each of the resonance muffler devices (450) is configured to form the predetermined natural frequency through the volume of the resonance chamber (443), the length of the connecting pipe (441), the pressure balance channel (442), and the inner diameter of the connecting pipe (441).

13. The screw compressor according to claim 1, characterized in that: The plurality of noise reduction devices (340) further include a plurality of interference noise reduction devices (460), at least a portion of the plurality of interference noise reduction devices (460) being disposed at intervals between the plurality of resonance noise reduction devices (450).

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