CN112483401A

CN112483401A - Exhaust bearing seat and compressor

Info

Publication number: CN112483401A
Application number: CN201910856903.2A
Authority: CN
Inventors: 吴晶晶; 王学贵; 蔡江畔; 何东平; 陈圣坤
Original assignee: Fusheng Industrial Shanghai Co ltd
Current assignee: Fusheng Industrial Shanghai Co ltd
Priority date: 2019-09-11
Filing date: 2019-09-11
Publication date: 2021-03-12
Also published as: TWI719769B; TW202111212A

Abstract

The utility model provides an exhaust bearing seat and compressor, exhaust bearing seat installs in the end of the rotor of compressor, and two rotor locating holes have been seted up to exhaust bearing seat. Two resonance cavities which are independent from each other are arranged in the exhaust bearing seat and are respectively positioned on the opposite outer sides of the two rotor positioning holes. Two diversion holes are formed in the butt joint face, facing the compressor body, of the exhaust bearing seat, and the two resonance cavities are communicated with the inner cavity of the compressor through the two diversion holes respectively. The exhaust bearing seat is configured to generate Helmholtz resonance by gas in the inner cavity entering the two resonance cavities when the compressor runs, so as to respectively attenuate airflow pulsation of the two rotors of the compressor. Through the design, when the compressor runs, the exhaust bearing seat can utilize gas in the inner cavity to enter the two resonance cavities to respectively generate Helmholtz resonance, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated.

Description

Exhaust bearing seat and compressor

Technical Field

The disclosure relates to the technical field of compressors, in particular to an exhaust bearing seat and a compressor.

Background

The compressor is used as equipment capable of improving gas pressure and conveying gas, and is widely applied to the fields of petroleum, natural gas, chemical industry, metallurgy and the like. Screw compressors are an important member of many types of compressors. The periodic suction and exhaust of the existing screw compressor can cause the periodic fluctuation of the gas pressure and flow in the exhaust cavity, namely the airflow pulsation. The airflow pulsation not only reduces the volumetric efficiency of the screw compressor and increases the power consumption of the screw compressor, but also excites the vibration of the exhaust cavity to induce aerodynamic noise.

In order to solve the technical problem, an air pulsation attenuation flange is additionally arranged between an exhaust port and a bearing seat flange of the conventional screw compressor. As shown in fig. 1 and 2, a bypass flow channel 120 is provided inside the airflow pulsation reducing flange 100, a gas inlet 121 of the bypass flow channel 120 is located at one side of the exhaust port 110 of the airflow pulsation reducing flange 110, and a gas outlet 122 of the bypass flow channel 120 is located at the other side of the exhaust port 110. The screw compressor can generate airflow pulsation opposite to the original airflow pulsation by utilizing the design, so that airflow noise is mutually offset.

However, in the above-mentioned design for attenuating the gas pulsation of the conventional screw compressor, since the additional gas pulsation attenuation flange 100 is disposed between the discharge port and the bearing housing flange, rather than being disposed at the end of the rotor of the compressor (i.e., the portion of the rotor located at the bearing housing flange), the gas pulsation attenuation effect is poor. Moreover, an additional structure of the airflow pulsation attenuation flange 100 is required, and the exhaust port and the bearing seat flange are required to be structurally modified correspondingly. In addition, the airflow pulsation attenuation flange 100 and the bypass flow channel 120 have complex shapes, a large amount of complex calculation needs to be performed in the design process, and the requirement on the processing precision is high.

In addition, the periodic suction and exhaust of the existing screw compressor can cause periodic fluctuation of gas pressure and flow in the exhaust cavity, namely airflow pulsation. The airflow pulsation not only reduces the volumetric efficiency of the screw compressor and increases the power consumption of the screw compressor, but also excites the vibration of the exhaust cavity to induce aerodynamic noise.

Disclosure of Invention

It is a primary object of the present disclosure to overcome at least one of the above-mentioned deficiencies of the prior art and to provide an exhaust bearing housing with improved attenuation of gas flow pulsations.

Another primary object of the present disclosure is to overcome at least one of the above-mentioned drawbacks of the prior art and to provide a compressor having the above-mentioned discharge bearing support.

In order to achieve the purpose, the following technical scheme is adopted in the disclosure:

according to one aspect of the present disclosure, an exhaust bearing seat is provided, which mounts a terminal end of a rotor of a compressor, and the exhaust bearing seat is provided with two rotor positioning holes. Two resonance cavities which are mutually independent are arranged in the exhaust bearing seat, and the two resonance cavities are respectively positioned on the opposite outer sides of the two rotor positioning holes. Two diversion holes are formed in the butt joint face, facing the compressor body, of the exhaust bearing seat, and the two diversion holes respectively communicate the two resonance cavities with the inner cavity of the compressor. The exhaust bearing seat is configured to generate Helmholtz resonance by utilizing the gas in the inner cavity to enter the two resonance cavities when the compressor runs, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated.

According to one embodiment of the present disclosure, two slots are formed in the abutting surface of the exhaust bearing seat, a cover plate is detachably fastened to each of the two slots, and the two cover plates respectively seal the two slots to form two resonance cavities.

According to one embodiment of the disclosure, when the cover plate is fastened to the slot, the surface of the cover plate facing away from the slot is flush with the abutting surface of the exhaust bearing seat.

According to one embodiment of the present disclosure, the slot includes a first sub slot and a second sub slot. The first sub-slot is arranged on the butt joint surface of the exhaust bearing seat. The second sub-open groove is arranged at the bottom of part of the first sub-open groove. The thickness of the cover plate is equal to the depth of the first sub-slot, the shape of the orthographic projection of the cover plate on the butt joint surface is the same as the shape of the orthographic projection of the first sub-slot on the butt joint surface, and the cover plate is embedded in the first sub-slot when buckled in the slot. Wherein the resonant cavity is formed by the second sub-slot and the cover plate together.

According to one embodiment of the present disclosure, the cover plate is removably connected to the slot by a plurality of connectors. And the position of the connecting piece connected with the open groove is positioned at the part of the bottom of the first sub open groove, which is not provided with the second sub open groove.

According to one embodiment of the present disclosure, the two diversion holes are respectively opened in the two cover plates.

According to one embodiment of the present disclosure, the diversion hole is opened at a lower end of the cover plate.

According to one embodiment of the present disclosure, a sealing structure is provided between the cover plate and the slotted opening.

According to one embodiment of the present disclosure, at least one of the two resonant cavities is formed in the exhaust bearing seat by integral molding.

According to one embodiment of the present disclosure, the diversion hole is a circular hole, an oval, an oblong hole, a rectangular hole, or a regular polygonal hole.

According to one embodiment of the present disclosure, an orthographic projection of the resonant cavity on the abutting surface is shaped like a curved belt, and the orthographic projection of the resonant cavity is curved along a circular arc path.

According to one embodiment of the present disclosure, a circle center corresponding to an arc path on which an orthographic projection of the resonant cavity is located coincides with an axis of the rotor positioning hole corresponding to the resonant cavity.

According to one embodiment of the present disclosure, the radian of the circular arc path on which the orthographic projection of the resonant cavity is located is less than or equal to pi.

According to one embodiment of the present disclosure, orthographic projections of the two resonant cavities are oppositely arranged with the circular arc openings of the respective circular arc paths.

According to one embodiment of the present disclosure, the two rotor positioning holes are a first positioning hole and a second positioning hole, respectively, and the two resonant cavities are a first cavity corresponding to the first positioning hole and a second cavity corresponding to the second positioning hole, respectively. The aperture of the first positioning hole is larger than that of the second positioning hole, and then the volume of the first cavity is larger than that of the second cavity.

According to one embodiment of the present disclosure, an orthographic projection of the resonant cavity on the abutting surface is shaped like a curved belt, and the orthographic projection of the resonant cavity is curved along a circular arc path. The corresponding circle radius of the arc path where the orthographic projection of the first cavity is located is larger than that of the arc path where the orthographic projection of the second cavity is located.

According to one embodiment of the present disclosure, an orthographic projection of the resonant cavity on the abutting surface is shaped like a curved belt, and the orthographic projection of the resonant cavity is curved along a circular arc path. The strip width of the orthographic projection of the first cavity is larger than that of the orthographic projection of the second cavity.

According to one embodiment of the present disclosure, an orthographic projection of the resonant cavity on the abutting surface is shaped like a curved belt, and the orthographic projection of the resonant cavity is curved along a circular arc path. The radian of the arc path where the orthographic projection of the first cavity is larger than that of the arc path where the orthographic projection of the second cavity is located.

According to one embodiment of the present disclosure, the abutting surface of the exhaust bearing seat is provided with a first slot and a second slot, the slot of the first slot is detachably fastened with a first cover plate, the first cover plate seals the first slot to form the first cavity, the slot of the second slot is detachably fastened with a second cover plate, and the second cover plate seals the second slot to form the second cavity. The two diversion holes are respectively a first diversion hole arranged on the first cover plate and a second diversion hole arranged on the second cover plate, the first diversion hole is a long circular hole, and the second diversion hole is a circular hole.

According to one embodiment of the present disclosure, each of the resonant cavities includes a plurality of sub-resonant cavities, the sub-resonant cavities are arranged at intervals and located on the same side of the corresponding rotor positioning hole, the butt joint surface is provided with two sets of flow guide holes, each set of flow guide hole includes a plurality of sub-flow guide holes, and the plurality of sub-resonant cavities are respectively communicated with the inner cavity of the compressor through the plurality of sub-flow guide holes.

According to another aspect of the present disclosure, a compressor is provided. The compressor comprises a machine body and two rotors, wherein the machine body is provided with an inner cavity, and the rotors are arranged in the inner cavity in a penetrating mode. Wherein the compressor further comprises a discharge bearing seat as proposed by the present disclosure and specifically explained in the above embodiments. The exhaust bearing seat is mounted at the tail end of the rotor. The two rotors respectively penetrate through the two rotor positioning holes of the exhaust bearing seat, and the two flow guide holes respectively communicate the two resonance cavities with the inner cavity. When the compressor runs, the exhaust bearing seat utilizes the gas in the inner cavity to enter the two resonance cavities to respectively generate Helmholtz resonance, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated.

According to one embodiment of the present disclosure, the compressor further comprises a perforated plate type airflow pulsation damping device. The perforated plate type airflow pulsation attenuation device is arranged in an exhaust passage of the compressor and comprises a pipe body. The pipe cavity of the pipe body is internally provided with a first perforated plate, a partition plate and a second perforated plate which are sequentially arranged at intervals along the axial direction, so that the pipe cavity is divided into a first cavity, two resonance cavities and a second cavity which are sequentially arranged, the first perforated plate is provided with a first flow guide hole, the second perforated plate is provided with a second flow guide hole, the pipe body is provided with a first through hole communicated with the first cavity and a second through hole communicated with the second cavity, and the outer diameter of the pipe body is smaller than the inner diameter of the exhaust channel. The perforated plate type airflow pulsation attenuation device is configured to utilize gas in the exhaust passage to enter the two resonance cavities to respectively generate helmholtz resonance when the compressor runs, so that two opposite airflow pulsations are generated to be mutually counteracted.

According to the technical scheme, the exhaust bearing seat and the compressor provided by the disclosure have the advantages and positive effects that:

the exhaust bearing pedestal provided by the disclosure is internally provided with two mutually independent resonance cavities which are respectively positioned at the opposite outer sides of the two rotor positioning holes. Two diversion holes are formed in the butt joint face, facing the compressor body, of the exhaust bearing seat, and the two resonance cavities are communicated with the inner cavity of the compressor through the two diversion holes respectively. Through the design, when the compressor runs, the exhaust bearing seat can utilize gas in the inner cavity to enter the two resonance cavities to respectively generate Helmholtz resonance, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated. Compared with the prior art, the exhaust bearing seat provided by the disclosure is arranged at the tail end of the rotor of the compressor, so that the attenuation effect on the airflow pulsation is better.

Drawings

Various objects, features and advantages of the present disclosure will become more apparent from the following detailed description of preferred embodiments thereof, when considered in conjunction with the accompanying drawings. The drawings are merely exemplary illustrations of the disclosure and are not necessarily drawn to scale. In the drawings, like reference characters designate the same or similar parts throughout the different views. Wherein:

FIG. 1 is a prior art gas flow pulsation attenuation flange for a screw compressor;

FIG. 2 is a cross-sectional view of the airflow pulsation attenuating flange shown in FIG. 1;

FIG. 3 is a schematic diagram illustrating a construction of an exhaust bearing mount according to an exemplary embodiment;

FIG. 4 is a perspective view of the vent bearing mount shown in FIG. 1;

FIG. 5 is a schematic diagram of a vent bearing mount according to another exemplary embodiment;

FIG. 6 is a perspective view of a perforated plate airflow pulsation dampener shown in accordance with an exemplary embodiment;

FIG. 7 is another angular perspective view of the perforated plate-type airflow pulsation dampener shown in FIG. 6;

FIG. 8 is a perspective cross-sectional view of the perforated plate-type airflow pulsation dampener shown in FIG. 6;

FIG. 9 is a schematic structural view of the perforated plate type airflow pulsation reducing apparatus shown in FIG. 6;

fig. 10 is a partial plan cross-sectional view of the perforated plate-type airflow pulsation damper shown in fig. 6.

The reference numerals are explained below:

100. an airflow pulsation attenuation flange; a second cover plate 222;

110. an exhaust port; 2221. second flow guide holes.

120. A bypass flow channel; a perforated plate type airflow pulsation damping device;

121. an airflow inlet; a tube body 310;

122. an airflow outlet; 3101. a first orifice;

200. an exhaust bearing seat; 3102. a second orifice;

201. a first positioning hole; 3103. a first via;

202. a second positioning hole; 3104. a second via;

203. an exhaust port; 311, a separator;

204. a butt joint surface; 312. a first perforated plate;

211. a first slot; 3121, a first flow guide hole;

2111. a first sub slot; 313. a second perforated plate;

2112. a second sub slot; 3131. a second guiding hole;

212. a first cover plate; a first cavity 314;

212', first sub-cover plate 315, second cavity;

2121. a first flow guide hole; a first resonant cavity;

2122. a connecting member; 317. a second resonant cavity;

221. a second slot; a web.

Detailed Description

Exemplary embodiments that embody features and advantages of the present disclosure are described in detail below in the specification. It is to be understood that the disclosure is capable of various modifications in various embodiments without departing from the scope of the disclosure, and that the description and drawings are to be regarded as illustrative in nature, and not as restrictive.

In the following description of various exemplary embodiments of the disclosure, reference is made to the accompanying drawings, which form a part hereof, and in which are shown by way of illustration various exemplary structures, systems, and steps in which aspects of the disclosure may be practiced. It is to be understood that other specific arrangements of parts, structures, example devices, systems, and steps may be utilized, and structural and functional modifications may be made without departing from the scope of the present disclosure. Moreover, although the terms "over," "between," "within," and the like may be used in this specification to describe various example features and elements of the disclosure, these terms are used herein for convenience only, e.g., in accordance with the orientation of the examples described in the figures. Nothing in this specification should be construed as requiring a specific three dimensional orientation of structures in order to fall within the scope of this disclosure.

Referring to fig. 3, a schematic structural diagram of the exhaust bearing seat proposed by the present disclosure is representatively shown, and in the exemplary embodiment, the exhaust bearing seat proposed by the present disclosure is explained by taking the application to a twin-screw compressor as an example. Those skilled in the art will readily appreciate that many modifications, additions, substitutions, deletions, or other changes may be made to the specific embodiments described below in order to apply the relevant designs of the present disclosure to other types of compressors or other apparatuses, and such changes are within the scope of the principles of the exhaust bearing housing set forth in the present disclosure.

As shown in fig. 3, in the present embodiment, the exhaust bearing housing 200 proposed by the present disclosure is applied to a twin-screw compressor as an example. Specifically, the exhaust bearing housing 200 is mounted to the end of the rotor of the twin-screw compressor using a coupling structure, for example, a flange structure. The twin screw compressor includes two rotors, a first rotor and a second rotor (e.g., a male rotor and a female rotor), respectively. Two rotor positioning holes are formed in the exhaust bearing seat 200 and are respectively a first positioning hole 201 and a second positioning hole 202, the first positioning hole 201 can be used for enabling the tail end of the first rotor to penetrate through and be positioned, and the second positioning hole 202 can be used for enabling the tail end of the second rotor to penetrate through and be positioned. In addition, the exhaust bearing seat 200 is further opened with an exhaust hole 203, and the exhaust hole 203 is approximately positioned between the two rotor positioning holes and is communicated with the inner cavity of the double-screw compressor. Referring to fig. 4, a perspective view of a vent bearing block 200 embodying the principles of the present disclosure is representatively illustrated in fig. 4, wherein the structure of two cover plates (described in detail below) is specifically omitted. The structure, arrangement and functional relationship of the main components of the exhaust bearing seat 200 proposed by the present disclosure will be described in detail below with reference to the above drawings.

As shown in fig. 3 and 4, in the present embodiment, the discharge bearing housing 200 proposed by the present disclosure has an abutting surface 204 that abuts against the compressor block. Two independent resonant cavities are arranged in the exhaust bearing seat 200, and the two resonant cavities are respectively positioned on the opposite outer sides of the two rotor positioning holes. Two diversion holes are formed in the butt joint surface 204 of the exhaust bearing pedestal 200, and the two diversion holes respectively communicate the two resonance cavities with the inner cavity of the compressor. Through the above design, when the twin-screw compressor operates, the exhaust bearing seat 200 provided by the present disclosure can utilize gas in the inner cavity of the twin-screw compressor to enter the two resonance cavities, thereby respectively generating helmholtz resonance, and thus respectively attenuating the airflow pulsation of the two rotors of the compressor. Compared with the prior art, the exhaust bearing seat 200 provided by the present disclosure is arranged at the rotor end of the compressor, so that the attenuation effect on the air flow pulsation is better.

When the exhaust bearing housing 200 of the present disclosure is mounted at the end of the rotor of the compressor, the exhaust bearing housing 200 is connected and positioned with the end of the rotor through the rotor positioning hole, and is mounted in the body of the compressor in a butt joint manner through the exhaust bearing housing 200 itself and the butt joint surface 204. The compressor body has an opening communicating with the inner cavity thereof, and the discharge bearing housing 200 is mounted on and closed to the opening (the discharge port 203 of the discharge bearing housing 200 communicates with the inner cavity of the compressor via the opening). Accordingly, the exhaust bearing seat 200 is installed on the body of the compressor and forms an exhaust port of the compressor together with the opening thereof.

As shown in fig. 3 and 4, in the present embodiment, two slots are opened on the abutting surface 204 of the exhaust bearing seat 200, a cover plate is detachably fastened to each of the two slots, and the two cover plates respectively close the two slots to form the two resonant cavities. In other embodiments, the resonant cavity may also be formed in the exhaust bearing seat 200 by other methods or processes, such as integral casting, and the like, which is not limited to the embodiment.

In summary, for convenience of understanding, based on the design concept of the present disclosure and the structural features of the twin-screw compressor, in the following, the slot correspondingly formed at the outer side of the first positioning hole 201 is defined as a first slot 211, the cover plate buckled on the first slot 211 is defined as a first cover plate 212, and the flow guiding hole communicated with the first slot 211 is defined as a first flow guiding hole 2121. Correspondingly, the slot correspondingly formed outside the second positioning hole 202 is defined as a second slot 221, the cover plate buckled on the second slot 221 is defined as a second cover plate 222, and the flow guiding hole communicated with the second slot 221 is defined as a second flow guiding hole 2221.

Preferably, as shown in fig. 3, in the present embodiment, for at least one of the two resonant cavities, when the cover plate is snapped on the slot, the surface of the cover plate facing away from the slot may preferably be flush with the abutting surface 204 of the exhaust bearing seat 200.

Further, as shown in fig. 4, based on the design that the surface of the cover plate is flush with the docking surface 204, in the present embodiment, for at least one of the two resonant cavities, the slot may preferably include a first sub slot 2111 and a second sub slot 2112. Specifically, the first sub slot 2111 opens on the abutment surface 204 of the exhaust bearing housing 200. The second sub slot 2112 is opened at a part of the slot bottom of the first sub slot 2111, i.e. the slot opening of the second sub slot 2112 completely falls within the slot bottom range of the first sub slot 2111. On this basis, the thickness of the cover plate may preferably be equal to the groove depth of the first sub-slot 2111, and the shape of the orthographic projection of the cover plate on the abutting surface 204 is the same as the shape of the orthographic projection of the first sub-slot 2111 on the abutting surface 204. Accordingly, when the cover is snapped into the slot, the cover is inserted into the first sub-slot 2111. That is, the resonant cavity formed by the set of cover plates and slots is formed by the second sub-slot 2112 and the cover plate. That is, based on the design in which the slot includes the first sub slot 2111 and the second sub slot 2112, the volume of the resonant cavity in which the slot participates in formation is approximately equal to the volume of the second sub slot 2112.

Further, as shown in fig. 3, based on the design that the slot includes a first sub slot 2111 and a second sub slot 2112, in the present embodiment, for at least one of the two resonant cavities, the cover plate may be removably connected to the slot, preferably by a plurality of connectors 2122. On this basis, the position where the connecting piece 2122 is connected to the slot may be preferably located at a portion of the bottom of the first sub slot 2111 where the second sub slot 2112 is not opened. That is, by using the structural configuration of the first sub slot 2111 and the second sub slot 2112, the groove bottom of the first sub slot 2111, where the second sub slot 2112 is not opened, forms a step structure for the connection of the connecting element 2122. In other embodiments, no matter what structure is adopted for the slot, the cover plate can be detachably connected to the slot through the connecting member 2122, and the connection position of the connecting member 2122 and the slot can be flexibly adjusted according to the specific structure of the slot, which is not limited to this embodiment.

As mentioned above, in the present embodiment, the connector 2122 may preferably be a screw. In other embodiments, the connecting member 2122 may also be a rivet, and the present embodiment is not limited thereto. As shown in fig. 3, based on the design of the cover plate, in the present embodiment, two diversion holes may be preferably formed on two cover plates, respectively. In other embodiments, the diversion hole may be formed at other positions, and is not limited to this embodiment.

Preferably, as shown in fig. 3, the diversion holes may be preferably formed at the lower end of the cover plate in the present embodiment based on the design that the diversion holes are formed on the cover plate. Accordingly, the damping effect of the exhaust bearing seat 200 proposed by the present disclosure on the rotor airflow pulsation can be further improved. In other embodiments, the guiding holes may be formed in other positions of the cover plate, and the positions of the first guiding hole 2121 and the second guiding hole 2221 relative to the cover plate where they are located may be similar or the same, or may be different, which is not limited to this embodiment.

Preferably, as shown in fig. 3, since the present embodiment is applied to a twin-screw compressor as an example, referring to the structural features of the twin-screw compressor, the male rotor and the female rotor have different tooth profiles, and the outer diameter of the male rotor is generally larger than that of the female rotor. Accordingly, the first positioning hole 201 (for penetrating and positioning the male rotor) on the exhaust bearing seat 200 has a larger aperture than the second positioning hole 202 (for penetrating and positioning the female rotor). Meanwhile, based on the design that the guide holes are formed in the cover plate, in the present embodiment, the first guide holes 2121 may preferably be oblong holes, that is, holes having a substantially rectangular shape and circular arc shapes at both ends. Also, the second guide holes 2221 may preferably be circular holes. In other embodiments, no matter whether the diversion holes are formed on the cover plate or not, or other arrangement manners are adopted, the diversion holes may also be flexibly selected to be circular holes, oval holes, long circular holes, rectangular holes, regular polygonal holes, and the like, and the hole patterns of the first diversion hole 2121 and the second diversion hole 2221 may be the same or different, which is not limited to this embodiment.

In the present embodiment, the abutting surface 204 of the exhaust bearing seat 200 is provided with a slot, and a cover plate matched with the slot is buckled at the slot opening of the slot, that is, a resonant cavity is formed by the slot and the cover plate. On this basis, no matter whether the outer surface of the cover plate (the surface of the cover plate facing away from the slot) is flush with the abutting surface 204, the situation that the outer surface of the cover plate is flush with, recessed in, or protruded from the abutting surface 204 can be included, and when the cover plate is covered on the slot of the slot, the cover plate can be regarded as forming a part of the abutting surface 204. On the basis, in the present embodiment, the design that the diversion hole is formed in the cover plate can be actually understood as the extension or deformation of the basic concept that the diversion hole is formed in the abutting surface 204 of the exhaust bearing seat 200, and is not contradictory to the description that the diversion hole is formed in the abutting surface 204.

In other embodiments, the two resonant cavities may be formed in different manners, for example, one resonant cavity may be formed by the slot on the abutting surface 204 and the cover, and the other resonant cavity may be formed directly in the exhaust bearing seat 200 by other manners such as integral molding (casting), which should not be limited to this embodiment.

In other embodiments, even if the cover plate and the slot form a resonant cavity together, the diversion hole may not be formed on the cover body, but may be selectively formed at other positions of the abutting surface 204. The extension path of the diversion hole in the exhaust bearing seat 200 or the cover body is not limited to a straight line, and may be curved or zigzag. In addition, the opening positions or the extending forms of the two flow guiding holes respectively communicating with the two resonant cavities may not be completely the same, for example, one flow guiding hole is opened on the cover body, and the other flow guiding hole is not opened on the other cover body but opened on the other position of the abutting surface 204, which is not limited by the present embodiment.

As shown in fig. 3 and 4, in the present embodiment, for at least one of the two resonant cavities, the orthogonal projection of the resonant cavity on the abutting surface 204 may preferably be in the shape of a curved band, and the orthogonal projection of the resonant cavity in the shape of a curved band may preferably be curved along a circular arc path.

Preferably, as shown in fig. 4, based on the design that the orthographic projection of the resonant cavity on the abutting surface 204 is in a belt shape curved along an arc path, in this embodiment, for at least one of the two resonant cavities, the center of the circle corresponding to the arc path on which the orthographic projection of the resonant cavity is located coincides with the axis of the rotor positioning hole corresponding to the resonant cavity.

Preferably, as shown in fig. 4, based on the design that the shape of the orthographic projection of the resonant cavity on the abutting surface 204 is a belt shape curved along the circular arc path, in the present embodiment, for at least one of the two resonant cavities, the radian of the circular arc path of the orthographic projection of the resonant cavity on the abutting surface 204 may be preferably less than or equal to pi.

Preferably, as shown in fig. 4, the shape of the orthographic projection of the resonant cavity on the abutting surface 204 is a strip-shaped design curved along a circular arc path, and in the present embodiment, the two resonant cavities may preferably both adopt the above-mentioned strip-shaped design curved along a circular arc path. On the basis of the two resonant cavities, orthographic projections of the two resonant cavities are oppositely arranged by the arc openings of the respective arc paths.

As shown in fig. 3 and 4, since the present embodiment is applied to a twin-screw compressor as an example, referring to the structural characteristics of the twin-screw compressor, the male rotor and the female rotor have different tooth profiles, and the outer diameter of the male rotor is generally larger than that of the female rotor. Accordingly, the first positioning hole 201 (for penetrating and positioning the male rotor) on the exhaust bearing seat 200 has a larger aperture than the second positioning hole 202 (for penetrating and positioning the female rotor). In other embodiments, when the exhaust bearing seat 200 provided in the present disclosure is applied to a twin-screw compressor with other rotor structures, the aperture relationship between the two rotor positioning holes can also be flexibly adjusted according to the specific structure of the two rotors, and is not limited to this embodiment.

Preferably, as shown in fig. 4, based on the design that the aperture of the first positioning hole 201 is larger than that of the second positioning hole 202, in the present embodiment, the volume of the first cavity corresponding to the first positioning hole 201 may preferably be larger than that of the second cavity corresponding to the second positioning hole 202. Specifically, in the present embodiment, the area of the first cavity (which may also be understood as the size of the orthographic projection of the first cavity on the abutting surface 204) may be preferably larger than the area of the second cavity (which may also be understood as the size of the orthographic projection of the second cavity on the abutting surface 204), so that when the depths of the first cavity and the second cavity are substantially the same, the volume of the first cavity is larger than the volume of the second cavity. In other embodiments, when the first cavity and the second cavity have similar shapes and the area of the first cavity is larger than the area of the second cavity, the depth of the first cavity may be smaller than or equal to the depth of the second cavity. Alternatively, the area of the first cavity may be smaller than or equal to the area of the second cavity, but the design that the volume of the first cavity is larger than the volume of the second cavity can also be realized by designing the depth of the first cavity to be larger than the depth of the second cavity. Or, the shape of the first cavity is not limited to be the same as or similar to the shape of the second cavity, and the area or depth of the first cavity and the area or depth of the second cavity may be designed in other relationships, so as to achieve the purpose that the volume of the first cavity is greater than the volume of the second cavity, which is not limited to this embodiment.

Further, as shown in fig. 4, when the orthogonal projections of the two resonant cavities on the abutting surface 204 are both in the form of a belt curved along the arc path, in the present embodiment, the corresponding radius of the arc path on which the orthogonal projection of the first cavity is located may preferably be larger than the corresponding radius of the arc path on which the orthogonal projection of the second cavity is located.

Further, as shown in fig. 4, when the orthogonal projections of the two resonant cavities on the abutting surface 204 are both in the form of a belt curved along the arc path, in the present embodiment, the belt width of the orthogonal projection of the first cavity may preferably be larger than the belt width of the orthogonal projection of the second cavity.

Further, as shown in fig. 4, when the orthogonal projections of the two resonant cavities on the abutting surface 204 are both in the form of a belt curved along the arc path, in the present embodiment, the arc degree of the arc path on which the orthogonal projection of the first cavity is located may preferably be greater than or equal to the arc degree of the arc path on which the orthogonal projection of the second cavity is located. For example, the radians of the arc paths of the orthographic projections of the first and second cavities can be about pi.

Preferably, in the present embodiment, a sealing structure may be preferably provided between the cover plate and the slotted notch. The sealing structure can be a sealing gasket, a sealing ring and the like. The sealing structure can be made of materials with waterproof, moistureproof, anticorrosive and other performances. Through the design, the sealing effect between the groove and the cover plate can be optimized by the sealing structure, and the resonance effect of the resonance cavity is further improved. In other embodiments, when the machining accuracy of the cover plate and the groove is high, the sealing structure may not be provided, and the present embodiment is not limited thereto.

In other embodiments, as shown in fig. 5, at least one of the two resonant cavities may also adopt a design of multiple sub-resonant cavities. Specifically, for a resonant cavity designed by using a plurality of sub-resonant cavities, the sub-resonant cavities included in the resonant cavity are arranged at intervals and located on the same side of the rotor positioning hole corresponding to the resonant cavity, and the butt joint surface 204 is provided with a plurality of sub-guide holes corresponding to the plurality of sub-resonant cavities of the resonant cavity, and the plurality of sub-guide holes respectively communicate the plurality of sub-resonant cavities with the inner cavity of the compressor. Wherein, the structure shown in fig. 5 shows a design scheme that one resonant cavity comprises two sub-resonant cavities, and the other resonant cavity is a single structure, and what is specifically shown in fig. 5 is a second cover plate 222 and two first sub-cover plates 212' covering the second resonant cavity or the first sub-resonant cavity. In other embodiments, the first resonant cavity and the second resonant cavity respectively corresponding to the first positioning hole 201 and the second positioning hole 202 may both adopt a design of multiple sub-resonant cavities, or any one of the multiple sub-resonant cavities, and when both the two resonant cavities adopt a design of multiple sub-resonant cavities, the number of the sub-resonant cavities included in the two resonant cavities may be the same or different.

It should be noted herein that the exhaust bearing seats shown in the drawings and described in this specification are only a few examples of the many types of exhaust bearing seats that can employ the principles of the present disclosure. It should be clearly understood that the principles of the present disclosure are in no way limited to any of the details of the exhaust bearing housing or any of the components of the exhaust bearing housing shown in the drawings or described in the present specification.

Based on the above detailed exemplary description of the discharge bearing seat proposed by the present disclosure, the compressor proposed by the present disclosure will be exemplarily described below. Those skilled in the art will readily appreciate that various modifications, additions, substitutions, deletions, or other changes may be made to the specific embodiments described below in order to utilize the compressor's associated design in other types of compressors and other equipment, and such changes are within the principles of the compressor as set forth in the present disclosure.

In this embodiment, the compressor proposed by the present disclosure mainly includes a machine body, two rotors, and a discharge bearing housing proposed by the present disclosure and specifically described in the above embodiments. Specifically, the compressor body has an inner cavity, and two rotors wear to locate the inner cavity. The present disclosure proposes an exhaust bearing housing mounted at the end of the rotor. The two rotors respectively penetrate through the two rotor positioning holes of the exhaust bearing seat, and the two resonance cavities of the exhaust bearing seat are respectively communicated with the inner cavity of the machine body through the two flow guide holes. Accordingly, when the compressor provided by the present disclosure operates, the exhaust bearing seat can generate helmholtz resonance respectively by utilizing the gas in the inner cavity entering the two resonance cavities, so as to respectively attenuate the airflow pulsation of the two rotors of the compressor.

It should be noted herein that the compressors shown in the figures and described in this specification are but a few examples of the wide variety of compressors that can employ the principles of the present disclosure. It should be clearly understood that the principles of this disclosure are in no way limited to any of the details of the compressor or any of the components of the compressor shown in the drawings or described in this specification.

Based on the above design of the compressor proposed by the present disclosure, the present disclosure also provides a perforated plate type airflow pulsation damping device for being mounted on the compressor proposed by the present disclosure. As shown in fig. 6, which representatively illustrates a perspective view of a perforated plate type airflow pulsation damping device 300, as proposed by the present disclosure. In this exemplary embodiment, the perforated plate type air pulsation damping apparatus 300 proposed by the present disclosure is explained by taking an example applied to a twin-screw compressor proposed by the present disclosure. Those skilled in the art will readily appreciate that various modifications, additions, substitutions, deletions, or other changes may be made to the specific embodiments described below in order to utilize the related designs of the present disclosure in other types of compressors or similar devices, and still fall within the principles of the perforated plate-type airflow pulsation dampener 300 as set forth in the present disclosure.

As shown in fig. 6, in the present embodiment, the perforated plate type airflow pulsation reducing apparatus 300 proposed by the present disclosure is exemplified by being applied to a compressor (e.g., a twin-screw compressor) proposed by the present disclosure. The compressor further comprises a discharge channel in which the perforated plate-like airflow pulsation damper 300 is disposed, and the perforated plate-like airflow pulsation damper 300 comprises at least a tube body 310. Specifically, the tube body 310 has a lumen and two orifices, which will be designated as a first orifice 3101 and a second orifice 3102, respectively, in the following for ease of understanding and explanation. Referring to fig. 7-10, another angular perspective view of the perforated plate-type airflow pulsation dampener 300 is representatively illustrated in fig. 7; a perspective cross-sectional view of the perforated plate-type airflow pulsation damper 300 is representatively illustrated in fig. 8; a schematic view of the perforated plate-type airflow pulsation reducing apparatus 300 is representatively illustrated in fig. 9; a partial plan cross-sectional view of the perforated plate-type airflow pulsation damper 300 is representatively illustrated in fig. 10. The structure, arrangement and functional relationship of the main components of the perforated plate type airflow pulsation damping device 300 proposed by the present disclosure will be described in detail below with reference to the above drawings.

As shown in fig. 6 to 9, in the present embodiment, a first perforated plate 312, a partition plate 311, and a second perforated plate 313 are disposed in a lumen of a tube body 310 at intervals in order in an axial direction of the tube body 310, so that the lumen of the tube body 310 is partitioned by the first perforated plate 312, the partition plate 311, and the second perforated plate 313 into a first cavity 314, two resonant cavities, and a second cavity 315 in order in the axial direction. For ease of understanding and explanation, the two resonant cavities will be designated as a first resonant cavity 316 and a second resonant cavity 317 in the following. That is, first cavity 314, first resonant cavity 316, second resonant cavity 317, and second cavity 315 are sequentially arranged in the axial direction from first orifice 3101 to second orifice 3102. The first perforated plate 312 is provided with a first flow guiding hole 3121, and the second perforated plate 313 is provided with a second flow guiding hole 3131. The pipe body 310 is provided with a first through hole 3103 and a second through hole 3104. The first through hole 3103 is opened at a position of the tube body 310 corresponding to the first cavity 314, that is, the first through hole 3103 communicates with the first cavity 314. The second through hole 3104 is formed in the tube 310 at a position corresponding to the second cavity 315, i.e., the second through hole 3104 is communicated with the second cavity 315. In addition, the outer diameter of the pipe body 310 is smaller than the inner diameter of the exhaust passage. That is, when the perforated-plate type airflow pulsation damping device 300 is disposed in the airflow passage, a gap is formed between the tubular body 310 and the airflow passage in the radial cross-sectional direction. Through the above and design, when the compressor operates, the perforated plate type airflow pulsation damping device 300 provided by the present disclosure can utilize the gas in the exhaust channel to enter the two resonant cavities to respectively generate helmholtz resonance, so as to generate an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so as to utilize the airflow pulsation and the airflow pulsation generated by the compressor itself to cancel each other.

As shown in fig. 6 and 7, in the present embodiment, the radial cross section of the tube body 310 may preferably be circular, that is, the radial cross section of each segment of the lumen (the first cavity 314, the second cavity 315, the first resonance cavity 316 and the second resonance cavity 317) is circular. Through the design, the airflow flowing state in each cavity of the tube cavity can be optimized, so that the resonance effect of the two resonance cavities is optimized. In other embodiments, the radial cross section of the tube 310 may also be selected from other shapes, such as an ellipse, a polygon, etc., and is not limited to this embodiment.

In the present embodiment, the radial cross section of the discharge passage of the compressor is preferably circular. On this basis, when the radial section of the pipe body 310 is circular, it may be preferable to adopt a design in which the center of a corresponding circle of the radial section of the pipe body 310 coincides with the center of a corresponding circle of the radial section of the exhaust passage. With the above-described design, an annular gap can be formed between the pipe body 310 and the exhaust passage, and the width of the gap at each position in the radial direction is substantially the same.

Further, based on the design that the center of the corresponding circle of the radial cross section of the pipe body 310 coincides with the center of the corresponding circle of the radial cross section of the exhaust passage, in the present embodiment, the width of the gap in the radial direction may preferably be 0.5mm to 1.5 mm. The above design of the present disclosure aims to make the outer diameter of the pipe body 310 approach to the inner diameter of the exhaust channel as much as possible, and further optimize the resonance effect of the two resonance cavities, thereby optimizing the airflow pulsation attenuation effect of the perforated plate type airflow pulsation attenuation apparatus 300. Therefore, on the premise of ensuring the realization of processing and manufacturing, in other embodiments, the width of the gap may be less than 0.5mm or greater than 1.5mm, which is not limited by the present embodiment.

In the present embodiment, when the pipe body 310 is disposed in the exhaust passage so that the center of the corresponding circle of the radial cross section of the pipe body 310 coincides with the center of the corresponding circle of the radial cross section of the exhaust passage, the first port 3101 of the pipe body 310 is located farther from the exhaust port of the exhaust passage than the second port 3102 of the pipe body 310. Wherein, in the working process of the compressor, the path of the air flow discharged by the exhaust passage of the compressor is roughly as follows: the gas flow starts upstream of the exhaust channel, enters the first chamber 314 through the first orifice 3101, enters the exhaust channel from the first chamber 314 through the first through hole 3103, enters the second chamber 315 through the exhaust channel through the second through hole 3104, and exits the exhaust channel through the second orifice 3102. The airflow can flow between the first cavity 314 and the first resonant cavity 316 through the first guiding hole 3121, and the airflow can flow between the second cavity 315 and the second resonant cavity 317 through the second guiding hole 3131, so that the first resonant cavity 316 and the second resonant cavity 317 respectively generate helmholtz resonance, thereby generating an airflow pulsation opposite to the airflow pulsation generated by the compressor itself, and thus the airflow pulsation and the airflow pulsation generated by the compressor itself can be used to cancel each other. In addition, the portion between the exhaust port of the exhaust passage and the outer wall of the second orifice 3102 of the tube body 310 is relatively closed, that is, when the air flow is exhausted through the above path, the air flow can be exhausted only through the second orifice 3102 of the tube body 310, but cannot be exhausted through the gap between the exhaust port and the tube body 310.

As shown in fig. 8 and 9, in the present embodiment, the plane of the first perforated plate 312 may be preferably perpendicular to the axial direction of the pipe body 310. The plane of the second perforated plate 313 may preferably be perpendicular to the axial direction of the pipe body 310. Also, the plane of the partition 311 may preferably be perpendicular to the axial direction of the pipe body 310. That is, the first perforated plate 312, the second perforated plate 313 and the partition 311 are parallel to each other, and the first cavity 314, the second cavity 315, the first resonant cavity 316 and the second resonant cavity 317 are all cylindrical cavity structures. In other embodiments, at least one of the first perforated plate 312, the second perforated plate 313 and the partition 311 may be inclined in relation to the axial direction of the pipe 310, and the three of the first perforated plate 312, the second perforated plate 313 and the partition 311 are not limited to be parallel to each other, and the present embodiment is not limited thereto.

As shown in fig. 8 and 9, in the present embodiment, since the first cavity 314, the first resonant cavity 316, the second resonant cavity 317, and the second cavity 315 are sequentially arranged in the axial direction from the first orifice 3101 to the second orifice 3102, the first cavity 314 is closer to the exhaust port of the exhaust passage than the second cavity 315. In summary, the distance between the first perforated plate 312 and the first orifice 3101 may preferably be larger than the distance between the second perforated plate 313 and the second orifice 3102, i.e., the volume of the first cavity 314 may preferably be larger than the volume of the second cavity 315.

It should be noted that the difference between the volumes of the first cavity 314 and the second cavity 315 shown in fig. 8 and 9 is merely an exaggerated exemplary illustration. When the design that the volume of the first cavity 314 is larger than the volume of the second cavity 315 is adopted, the volume of the first cavity 314 is preferably slightly larger than the volume of the second cavity 315, for example, the difference between the distance between the first perforated plate 312 and the first nozzle 3101 and the distance between the second perforated plate 313 and the second nozzle 3102 may be about 1mm to 3 mm. In other embodiments, the volume of the first cavity 314 may be smaller than or equal to the volume of the second cavity 315, and is not limited to this embodiment.

As shown in fig. 6 to 9, the number of first through holes 3103 may preferably be greater than the number of second through holes 3104 in the present embodiment, based on the design in which the distance between the first perforated plate 312 and the first orifice 3101 is greater than the distance between the second perforated plate 313 and the second orifice 3102.

As shown in fig. 6 to 9, in the present embodiment, the first through holes 3103 are plural, the plural first through holes 3103 may preferably be arranged around the outer circumference of the pipe body 310, and the plural first through holes 3103 may preferably include plural sets axially spaced apart, each set of the first through holes 3103 is plural, and the plural first through holes 3103 of the same set are distributed around the outer circumference of the pipe body 310. Through the above design, the airflow in the first cavity 314 can be more uniform and stable when entering the exhaust channel through the first through hole 3103. In other embodiments, when there are a plurality of first through holes 3103, other arrangements may be adopted. Of course, the number of the first through holes 3103 is not limited to a plurality, and may be one, which is not limited to the present embodiment.

As shown in fig. 6 to 9, in the present embodiment, the second through holes 3104 are plural, the plurality of second through holes 3104 may preferably be arranged around the outer circumference of the pipe body 310, and the plurality of second through holes 3104 may preferably include a plurality of sets axially spaced apart, each set of second through holes 3104 being plural, the plurality of second through holes 3104 of the same set being distributed around the outer circumference of the pipe body 310. Through the above design, the airflow in the exhaust channel can enter the second cavity 315 through the second through hole 3104 more uniformly and stably. In other embodiments, when there are a plurality of second through holes 3104, other arrangements may be adopted. Of course, the number of the second through holes 3104 is not limited to a plurality, and may be one, which is not limited to the present embodiment.

Preferably, as shown in fig. 6, 8, and 9, based on the design in which the number of the first through holes 3103 is greater than the number of the second through holes 3104, and based on the design in which the plurality of sets of the first through holes 3103 and the second through holes 3104 are distributed around the outer circumference of the pipe body 310, in the present embodiment, the number of holes of each set of the first through holes 3103 and the number of holes of each set of the second through holes 3104 may preferably be equal, and the number of sets of the first through holes 3103 may preferably be greater than the number of sets of the second through holes 3104. In other embodiments, if the number of the first through holes 3103 is larger than the number of the second through holes 3104, and the number of the first through holes 3103 per group may be different from the number of the second through holes 3104 per group based on the above-mentioned design that the plurality of groups of the first through holes 3103 and the second through holes 3104 are distributed around the outer circumference of the tube 310, the number of the first through holes 3103 may be equal to or less than the number of the second through holes 3104, which is not limited by the present embodiment.

Preferably, based on the above-mentioned design that the plurality of sets of first through holes 3103 are distributed around the outer circumference of the pipe body 310, in the present embodiment, the plurality of sets of first through holes 3103 may be preferably uniformly arranged at intervals in the axial direction of the pipe body 310.

Preferably, based on the above-mentioned design that the plurality of sets of second through holes 3104 are distributed around the outer circumference of the tube body 310, in the present embodiment, the plurality of sets of second through holes 3104 may be preferably uniformly arranged at intervals along the axial direction of the tube body 310.

Further, when the plurality of sets of first through holes 3103 and the plurality of sets of second through holes 3104 are each designed to be arranged at regular intervals along the axis of the pipe body 310, the pitch of the adjacent two sets of first through holes 3103 in the axial direction of the pipe body 310 may further preferably be equal to the pitch of the adjacent two sets of second through holes 3104 in the axial direction of the pipe body 310.

In the present embodiment, the distance between the first perforated plate 312 and the partition 311 may preferably be equal to the distance between the second perforated plate 313 and the partition 311 in the axial direction of the pipe body 310, that is, the volume of the first resonance chamber 316 may preferably be equal to the volume of the second resonance chamber 317. It should be noted that the above preferred design is based on the tube body 310 having a uniform tubular structure with the same outer diameter at each position in the axial direction. In other embodiments, when the pipe 310 is a tubular structure with a non-uniform outer diameter, if the volume of the first resonant cavity 316 is equal to the volume of the second resonant cavity 317, the distance between the first perforated plate 312 and the partition 311 may be larger or smaller than the distance between the second perforated plate 313 and the partition 311, and the embodiment is not limited thereto.

As shown in fig. 6 to 8, in the present embodiment, the first perforated plate 312 may preferably be provided with a plurality of first deflector holes 3121. Through the design, the airflow between the first cavity 314 and the first resonant cavity 316 can be more uniform and stable. Meanwhile, each first guiding hole 3121 and the first resonant cavity 316 form a resonant cavity (helmholtz resonant cavity), and the design of the first guiding holes 3121 can be regarded as forming a plurality of resonant cavities connected in parallel. In other embodiments, the number of the first flow guiding holes 3121 is not limited to a plurality, and may be one, and is not limited to this embodiment.

Preferably, based on the design that the first perforated plate 312 is provided with the plurality of first deflector holes 3121, in the present embodiment, the plurality of first deflector holes 3121 may be preferably uniformly arranged on the first perforated plate 312.

As shown in fig. 6 to 8, in the present embodiment, the second perforated plate 313 may preferably be provided with a plurality of second deflector holes 3131. Through the design, the airflow between the second cavity 315 and the second resonant cavity 317 can be more uniform and stable. Meanwhile, each second guiding hole 3131 and the second resonant cavity 317 form a resonant cavity (helmholtz resonant cavity), and the design of the second guiding holes 3131 can be regarded as forming a plurality of resonant cavities connected in parallel. In other embodiments, the number of the second guiding holes 3131 is not limited to a plurality, and may be one, and is not limited to this embodiment.

Preferably, based on the design that the second perforated plate 313 is opened with the plurality of second flow guiding holes 3131, in the present embodiment, the plurality of second flow guiding holes 3131 may be opened on the second perforated plate 313, preferably in a uniform arrangement.

Further, based on a design in which both the first perforated plate 312 and the second perforated plate 313 are plural, in the present embodiment, the number of the first perforated plate 312 may be preferably equal to the number of the second perforated plate 313.

Further, based on the design in which the first perforated plate 312 and the second perforated plate 313 are uniformly arranged, while the number of the first perforated plates 312 is equal to the design of the second perforated plate 313, in the present embodiment, a plurality of first perforated plates 312 and a plurality of second perforated plates 313 may be preferably arranged in one-to-one correspondence in the axial direction of the pipe body 310.

As shown in fig. 10, which is specificA partial cross-sectional view of one of the resonant cavities of the tube of the perforated plate-type airflow pulsation damper proposed by the present disclosure is shown. Taking the first resonant cavity 316 as an example, the distance between the first perforated plate 312 and the baffle 311 in the axial direction of the pipe body (i.e., the depth of the first resonant cavity 316) is D, the thickness of the first perforated plate 312 is t, the diameter of the first baffle holes 3121 is D, and the perforation rate of the first perforated plate 312 (i.e., the sum of the areas of all the first baffle holes 3121 and/or the area of the first perforated plate 312 × 100%) is P. In this connection, the attenuation frequency f of the perforated-plate pulsation attenuation structure formed by the resonance chamber of the present invention is set to be lower than the attenuation frequency f of the perforated-plate pulsation attenuation structure_MPACan be expressed as:

as shown in fig. 6 to 9, in the present embodiment, the perforated plate type airflow pulsation damping device 300 according to the present disclosure may further preferably include a connection plate 320. Specifically, the connecting plate 320 is disposed at an end opening of the tube body 310, the end opening of the tube body 310 is opened at the connecting plate 320, and the connecting plate 320 can detachably fix the tube body 310 at the exhaust port of the exhaust passage. Here, the end orifice is the second orifice 3102 based on the design that the first orifice 3101 is farther from the exhaust port than the second orifice 3102 in the present embodiment.

Preferably, as shown in fig. 6 to 9, in the present embodiment, a description will be given taking an example in which a discharge flange is provided at a discharge port of a discharge passage of a compressor. On this basis, the connection plate 320 may preferably adopt a flange structure, so that the connection plate 320 is detachably connected to the exhaust flange of the compressor, and the gap between the pipe body 310 and the exhaust passage may be sealed at the exhaust port by the connection plate 320 in the flange structure.

It should be noted herein that the perforated plate-type airflow pulsation damping devices illustrated in the drawings and described in the present specification are but a few examples of the wide variety of perforated plate-type airflow pulsation damping devices that can employ the principles of the present disclosure. It should be clearly understood that the principles of the present disclosure are in no way limited to any of the details of the perforated plate-type gas flow pulsation damping device or any of the components of the perforated plate-type gas flow pulsation damping device shown in the drawings or described in the present specification.

In summary, the exhaust bearing seat provided by the present disclosure has two independent resonant cavities formed therein, and the two resonant cavities are located at opposite outer sides of the two rotor positioning holes, respectively. Two diversion holes are formed in the butt joint face, facing the compressor body, of the exhaust bearing seat, and the two resonance cavities are communicated with the inner cavity of the compressor through the two diversion holes respectively. Through the design, when the compressor runs, the exhaust bearing seat can utilize gas in the inner cavity to enter the two resonance cavities to respectively generate Helmholtz resonance, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated. Compared with the prior art, the exhaust bearing seat provided by the disclosure is arranged at the tail end of the rotor of the compressor, so that the attenuation effect on the airflow pulsation is better. Besides, the exhaust bearing seat does not need to be additionally provided with other structures.

Furthermore, the perforated plate type airflow pulsation damping device provided by the present disclosure is disposed in an exhaust passage of the compressor and includes a tube body. The pipe cavity of the pipe body is internally provided with a first perforated plate, a partition plate and a second perforated plate which are sequentially arranged at intervals along the axial direction so as to divide the pipe cavity into a first cavity, two resonance cavities and a second cavity which are sequentially arranged, the first perforated plate is provided with a first flow guide hole, the second perforated plate is provided with a second flow guide hole, and the pipe body is provided with a first through hole communicated with the first cavity and a second through hole communicated with the second cavity. Through the design, when the compressor runs, the perforated plate type airflow pulsation attenuation device can utilize gas in the exhaust channel to enter the two resonant cavities to respectively generate Helmholtz resonance, so that airflow pulsation is generated, the airflow pulsation is opposite to the airflow pulsation generated by the compressor, and the airflow pulsation generated by the compressor can be utilized to offset each other.

Based on the above description, when the compressor proposed by the present disclosure includes the exhaust bearing seat proposed by the present disclosure, when the compressor is in operation, the exhaust bearing seat is capable of generating helmholtz resonance by utilizing the gas in the inner cavity entering the two resonance cavities, so as to respectively attenuate the airflow pulsation of the two rotors of the compressor. Compared with the prior art, the exhaust bearing seat provided by the disclosure is arranged at the tail end of the rotor of the compressor, so that the attenuation effect on the airflow pulsation is better. Besides, the exhaust bearing seat does not need to be additionally provided with other structures.

Further, when the compressor proposed by the present disclosure simultaneously includes the exhaust bearing seat and the perforated plate type airflow pulsation damping device proposed by the present disclosure, in addition to the above-mentioned effects provided by the exhaust bearing seat, when the compressor is operated, the perforated plate type airflow pulsation damping device can utilize gas in the exhaust channel to enter the two resonance cavities to respectively generate helmholtz resonance, so as to generate an airflow pulsation, which is opposite to the airflow pulsation generated by the compressor itself, so that the airflow pulsation and the airflow pulsation generated by the compressor itself can be utilized to cancel each other.

Exemplary embodiments of a discharge bearing housing and compressor as set forth in the present disclosure are described and/or illustrated in detail above. Embodiments of the disclosure are not limited to the specific embodiments described herein, but rather, components and/or steps of each embodiment may be utilized independently and separately from other components and/or steps described herein. Each component and/or step of one embodiment can also be used in combination with other components and/or steps of other embodiments. When introducing elements/components/etc. described and/or illustrated herein, the articles "a," "an," and "the" are intended to mean that there are one or more of the elements/components/etc. The terms "comprising," "including," and "having" are intended to be inclusive and mean that there may be additional elements/components/etc. other than the listed elements/components/etc. Furthermore, the terms "first" and "second" and the like in the claims and the description are used merely as labels, and are not numerical limitations of their objects.

While the discharge bearing housing and compressor set forth in the present disclosure have been described in terms of various specific embodiments, those skilled in the art will recognize that the practice of the disclosure can be practiced with modification within the spirit and scope of the claims.

Claims

1. An exhaust bearing seat is arranged at the tail end of a rotor of a compressor, and is provided with two rotor positioning holes; the method is characterized in that:

two independent resonance cavities are arranged in the exhaust bearing seat and are respectively positioned on the opposite outer sides of the two rotor positioning holes;

the butt joint surface of the exhaust bearing seat facing the compressor body is provided with two flow guide holes which respectively communicate the two resonance cavities with the inner cavity of the compressor;

the exhaust bearing seat is configured to generate Helmholtz resonance by utilizing the gas in the inner cavity to enter the two resonance cavities when the compressor runs, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated.

2. The exhaust bearing pedestal according to claim 1, wherein the abutting surface of the exhaust bearing pedestal is provided with two slots, the two slots are respectively detachably buckled with a cover plate, and the two cover plates respectively close the two slots to respectively form two resonance cavities.

3. The exhaust bearing seat according to claim 2, wherein when the cover plate is fastened to the slot, a surface of the cover plate facing away from the slot is flush with a butt surface of the exhaust bearing seat.

4. The exhaust bearing housing of claim 3 wherein said slot comprises:

the first sub slot is arranged on the butt joint surface of the exhaust bearing seat; and

the second sub-slot is arranged at the bottom of part of the first sub-slot;

the thickness of the cover plate is equal to the depth of the first sub-slot, the shape of the orthographic projection of the cover plate on the butt joint surface is the same as the shape of the orthographic projection of the first sub-slot on the butt joint surface, and the cover plate is embedded in the first sub-slot when being buckled in the slot;

wherein the resonant cavity is formed by the second sub-slot and the cover plate together.

5. The exhaust bearing housing of claim 4 wherein said cover plate is removably connected to said slot by a plurality of connectors; and the position of the connecting piece connected with the open groove is positioned at the part of the bottom of the first sub open groove, which is not provided with the second sub open groove.

6. The exhaust bearing pedestal according to claim 2, wherein two of the guiding holes are respectively formed in two of the cover plates.

7. The exhaust bearing pedestal of claim 6, wherein the flow guide hole opens at a lower end of the cover plate.

8. The exhaust bearing cartridge of claim 2 wherein a seal is provided between said cover plate and said slotted opening.

9. The exhaust bearing seat according to claim 1, wherein at least one of the two resonant cavities is integrally formed in the exhaust bearing seat.

10. The exhaust bearing pedestal of claim 1, wherein the flow guide holes are circular holes, oval holes, oblong holes, rectangular holes, regular polygonal holes.

11. The exhaust bearing seat according to claim 1 wherein an orthographic projection of the resonant cavity on the abutment surface is shaped as a curved band and the orthographic projection of the resonant cavity is curved along a circular arc path.

12. The exhaust bearing pedestal according to claim 11, wherein a center of a circle corresponding to an arc path on which an orthographic projection of the resonant cavity is located coincides with an axis of the rotor positioning hole corresponding to the resonant cavity.

13. The exhaust bearing seat according to claim 11 wherein the arc of the arc path of the resonant cavity in which the orthographic projection is located is less than or equal to pi.

14. The exhaust bearing seat according to claim 11 wherein orthographic projections of two said resonant cavities are oppositely disposed with the circular arc openings of the respective circular arc paths.

15. The exhaust bearing pedestal according to claim 1, wherein the two rotor positioning holes are a first positioning hole and a second positioning hole, respectively, and the two resonant cavities are a first cavity corresponding to the first positioning hole and a second cavity corresponding to the second positioning hole, respectively; the aperture of the first positioning hole is larger than that of the second positioning hole, and then the volume of the first cavity is larger than that of the second cavity.

16. The exhaust bearing support of claim 15 wherein an orthographic projection of the resonant cavity on the abutment surface is shaped as a curved band and the orthographic projection of the resonant cavity is curved along a circular arc path; the corresponding circle radius of the arc path where the orthographic projection of the first cavity is located is larger than that of the arc path where the orthographic projection of the second cavity is located.

17. The exhaust bearing support of claim 15 wherein an orthographic projection of the resonant cavity on the abutment surface is shaped as a curved band and the orthographic projection of the resonant cavity is curved along a circular arc path; the strip width of the orthographic projection of the first cavity is larger than that of the orthographic projection of the second cavity.

18. The exhaust bearing support of claim 15 wherein an orthographic projection of the resonant cavity on the abutment surface is shaped as a curved band and the orthographic projection of the resonant cavity is curved along a circular arc path; the radian of the arc path where the orthographic projection of the first cavity is larger than that of the arc path where the orthographic projection of the second cavity is located.

19. The exhaust bearing support according to claim 15, wherein the abutting surface of the exhaust bearing support is provided with a first slot and a second slot, the slot of the first slot is detachably fastened with a first cover plate, the first cover plate closes the first slot to form the first cavity, the slot of the second slot is detachably fastened with a second cover plate, and the second cover plate closes the second slot to form the second cavity; the two diversion holes are respectively a first diversion hole arranged on the first cover plate and a second diversion hole arranged on the second cover plate, the first diversion hole is a long circular hole, and the second diversion hole is a circular hole.

20. The exhaust bearing seat according to claim 1, wherein each of the resonant cavities includes a plurality of sub-resonant cavities, the sub-resonant cavities are spaced apart and located on the same side of the corresponding rotor positioning hole, the abutting surface has two sets of flow guide holes, each set of flow guide hole includes a plurality of sub-flow guide holes, and the plurality of sub-flow guide holes respectively communicate the plurality of sub-resonant cavities with the inner cavity of the compressor.

21. A compressor comprises a machine body and two rotors, wherein the machine body is provided with an inner cavity, and the rotors are arranged in the inner cavity in a penetrating way; characterized in that the compressor further comprises:

the exhaust bearing housing according to any one of claims 1 to 20, mounted to an end of the rotor;

the two rotors respectively penetrate through two rotor positioning holes of the exhaust bearing seat, and the two flow guide holes respectively communicate the two resonance cavities with the inner cavity;

when the compressor runs, the exhaust bearing seat utilizes the gas in the inner cavity to enter the two resonance cavities to respectively generate Helmholtz resonance, so that the airflow pulsation of the two rotors of the compressor is respectively attenuated.

22. The compressor of claim 21, further comprising:

the board-like air current pulsation damping device of perforation locates in the exhaust passage of compressor, the board-like air current pulsation damping device of perforation includes:

the pipe comprises a pipe body, wherein a first perforated plate, a partition plate and a second perforated plate which are sequentially arranged at intervals along the axial direction are arranged in a pipe cavity so as to divide the pipe cavity into a first cavity, two resonance cavities and a second cavity which are sequentially arranged, the first perforated plate is provided with a first flow guide hole, the second perforated plate is provided with a second flow guide hole, the pipe body is provided with a first through hole communicated with the first cavity and a second through hole communicated with the second cavity, and the outer diameter of the pipe body is smaller than the inner diameter of an exhaust channel; the perforated plate type airflow pulsation attenuation device is configured to utilize gas in the exhaust passage to enter the two resonance cavities to respectively generate helmholtz resonance when the compressor runs, so that two opposite airflow pulsations are generated to be mutually counteracted.