CN221195404U - Exhaust bearing seat and screw compressor - Google Patents

Abstract

The present utility model provides an exhaust bearing block for supporting a screw shaft in a compressor, and a screw compressor, comprising: bearing frame body, exhaust gas inlet, exhaust runner, helmholtz silencer and expansion silencer, helmholtz silencer has through-hole and cavity, expansion silencer has the inflation chamber, helmholtz silencer with expansion silencer integrate respectively in the bearing frame body.

Description

Exhaust bearing seat and screw compressor

Technical Field

The utility model relates to an exhaust bearing seat with a built-in silencing structure, in particular to an exhaust bearing seat with a built-in silencing structure for a screw compressor.

Background

In a conventional screw compressor, a screw shaft of a screw provided in a compressor housing is generally supported by a discharge bearing block. The noise of the screw compressor is mainly derived from the exhaust noise. As the rotor rotates, the gas in the different tooth slots is periodically exhausted and the exhaust pressure is constantly fluctuating, thereby generating periodic exhaust noise. The exhaust noise is affected by the tooth slot exhaust rate, i.e., the rotational speed, and the higher the rotational speed, the higher the exhaust noise frequency. Therefore, for the noise reduction of the inverter screw compressor, the noise to be reduced is not just a few high-amplitude points, but noise on a frequency band corresponding to the rotation speed band of the inverter screw compressor needs to be reduced. Therefore, the existing silencer for the variable frequency screw compressor is complicated in arrangement.

As a conventional means for eliminating exhaust noise of the screw compressor, a muffler and its assembly are generally added behind the exhaust bearing housing. For example, a multistage low pressure drop muffler for a compressor is known. The multi-stage low pressure drop muffler is designed to silence a wide range of frequencies, minimize pressure drop, improve fluid flow, and increase compressor efficiency. However, this muffler requires that each muffler member be attached to the compressor by welding, and has problems in that the number of parts of the compressor increases, the processing is complicated, and the production cost increases.

In addition, a refrigerant compressor is also known, which includes a main casing, a screw compressor provided in the main casing, and a first muffler unit disposed in the main casing. In the refrigerant compressor, a shell window is provided in a compressor shell, and a muffler unit including a perforated pipe is disposed next to the shell window in order to improve the sound deadening effect. In the refrigerant compressor, the perforated pipe is assembled in the exhaust bearing seat, but the space of the perforated pipe is smaller, and the noise reduction effect is not obvious.

Disclosure of utility model

In view of the above problems in the prior art, an object of the present application is to provide an exhaust bearing housing with a built-in noise reducing structure, which has a good noise reducing effect, a simple structure, and easy assembly.

According to a first aspect of the present application, there is provided a discharge bearing housing for supporting a screw shaft in a compressor. The exhaust bearing housing includes: bearing frame body, exhaust inlet, exhaust runner, helmholtz silencer and expansion silencer, helmholtz silencer have through-hole and cavity, expansion silencer have expansion chamber, helmholtz silencer and expansion silencer integrate respectively in the bearing frame body.

According to some embodiments of the application, in the exhaust bearing housing described above, optionally, the cavity of the helmholtz silencer is integrally formed in the housing body by casting.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, the helmholtz silencer comprises a perforated plate provided in the housing body, the perforated plate being formed with through holes.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, the expansion chamber of the expansion silencer is integrally formed in the housing body by casting.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, a cover plate is provided on a side of the expansion chamber of the expansion silencer.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, the helmholtz silencer includes a side helmholtz silencer disposed laterally of the exhaust gas inlet and a rear helmholtz silencer disposed directly behind the exhaust gas inlet.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, the exhaust bearing housing comprises a plurality of helmholtz silencers and a plurality of expansion silencers.

According to some embodiments of the application, in the exhaust bearing housing of any of the embodiments described above, optionally, the exhaust bearing housing comprises 2 helmholtz silencers and 4 expansion silencers.

According to some embodiments of the present application, in the exhaust bearing housing of any one of the above embodiments, optionally, cross-sectional areas of the through holes of the respective plurality of helmholtz silencers are different from each other, and volumes of the cavities of the respective plurality of helmholtz silencers are different from each other, and further, flow areas of the expansion chambers of the respective plurality of expansion silencers are different from each other.

According to some embodiments of the present application, in the exhaust bearing housing of any of the above embodiments, optionally, a cross section of each expansion chamber of the plurality of expansion mufflers is square, circular or hexagonal.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, the exhaust bearing housing is configured to have an exhaust gas flow rate in a range of 3m/s to 25 m/s.

According to some embodiments of the application, in the exhaust bearing housing of any of the above embodiments, optionally, the exhaust bearing housing is configured to have an exhaust gas flow rate in a range of 8m/s to 18 m/s.

According to some embodiments of the application, in the exhaust bearing seat of any of the embodiments above, optionally, the exhaust bearing seat is a side exhaust bearing seat.

According to some embodiments of the application, in the exhaust bearing seat of any of the embodiments above, optionally, the exhaust bearing seat is an axial exhaust bearing seat.

According to a second aspect of the present application there is provided a screw compressor employing a discharge bearing housing as described in any one of the embodiments above.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the exhaust bearing seat and the screw compressor adopting the exhaust bearing seat, the Helmholtz silencer and the expansion silencer are integrated in the bearing seat body of the exhaust bearing seat, so that the number of parts of the exhaust silencer can be reduced, and the technical effect of effectively reducing exhaust noise with a simplified structure is achieved.

Drawings

Fig. 1 is a schematic cross-sectional view illustrating an exhaust bearing housing according to some embodiments of the application.

Fig. 2 is a schematic cross-sectional view of an exhaust bearing housing according to some embodiments of the present application, as viewed from the line A-A in fig. 1 in the direction of an arrow, and is a diagram for explaining the structure of a helmholtz silencer.

Fig. 3 is a schematic cross-sectional view showing an exhaust bearing housing according to some embodiments of the present application, as viewed from the line B-B in fig. 1 in the direction of an arrow, and is a diagram for explaining the structure of an expansion silencer.

Fig. 4 is a partial schematic cross-sectional view illustrating an alternative manner of a helmholtz silencer according to some embodiments of the present application.

Fig. 5 is a schematic cross-sectional view illustrating an alternative manner of expansion silencer according to some embodiments of the present application.

Fig. 6 is a schematic cross-sectional view illustrating another form of exhaust muffler according to some embodiments of the present application.

Fig. 7 is a schematic cross-sectional view of the exhaust bearing housing as viewed from the line C-C in fig. 6 in the direction of an arrow, which is a diagram for explaining the structure of the helmholtz silencer, according to some embodiments of the present application.

Description of the reference numerals

1. 1 'Helmholtz silencer, 1a cavity, 1b' through hole, 1c perforated plate, 1d partition wall, 2 'expansion silencer, 2a, 2a' expansion chamber, 2b cover plate, 3 'exhaust inlet, 4' exhaust runner, 5 'bearing seat body, 100' exhaust bearing seat

Detailed Description

The present disclosure is described in detail below. In the following paragraphs, the different aspects of the embodiments are defined in more detail. Aspects so defined may be combined with any other aspect or aspects unless explicitly stated to be non-combinable. In particular, any feature or features may be combined with one or more other features may be desired and advantageous.

The terms "first," "second," and the like in this disclosure are merely for convenience of description to distinguish between different constituent components having the same name, and do not denote a sequential or primary or secondary relationship.

Furthermore, when an element is referred to as being "on" another element, it can be directly on the other element or be indirectly on the other element with one or more intervening elements interposed therebetween. In addition, when an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element with one or more intervening elements interposed therebetween. Like reference numerals refer to like parts throughout.

The description of the orientation or positional relationship indicated by "upper", "lower", "top", "bottom", "front", "rear", "inner" and "outer", etc. is used in this disclosure for convenience of description of the present disclosure only, and is not intended to indicate or imply that the apparatus referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the scope of the application.

Hereinafter, an exhaust bearing housing according to some embodiments of the present application will be described in detail with reference to the accompanying drawings.

Fig. 1 is a schematic cross-sectional view illustrating an exhaust bearing housing according to some embodiments of the application. Fig. 2 is a schematic cross-sectional view of an exhaust bearing housing according to some embodiments of the present application, as viewed from the line A-A in fig. 1 in the direction of an arrow, and is a diagram for explaining the structure of a helmholtz silencer. Fig. 3 is a schematic cross-sectional view showing an exhaust bearing housing according to some embodiments of the present application, as viewed from the line B-B in fig. 1 in the direction of an arrow, and is a diagram for explaining the structure of an expansion silencer.

The discharge bearing housing 100 shown in fig. 1 is provided at one end of the screw compressor for supporting a screw shaft of a screw in the screw compressor. The present application is not limited to the screw compressor and the screw, and may be any configuration capable of realizing the functions of the compressor, and therefore, a specific description and illustration of the configuration of the screw compressor and the screw are omitted here.

As shown in fig. 1, the exhaust bearing housing 100 includes a housing body 5, an exhaust gas inlet 3 that opens on one side of the housing body 5, and an exhaust gas flow passage 4 that is formed inside the housing body 5 and is continuous with the exhaust gas inlet 3. The exhaust gas of the compressor flows from the exhaust gas inlet 3 into the exhaust bearing housing 100.

In the exhaust gas bearing housing 100 shown in fig. 1, a helmholtz silencer 1 is formed in a side wall of the bearing housing body 5 on the side of the exhaust gas inlet 3. As shown in fig. 1 and 2 (fig. 2 is a cross-sectional view taken in the direction A-A in fig. 1), the helmholtz silencer 1 includes a cavity 1a formed in a side wall, and a through hole 1b that communicates the cavity 1a with an exhaust runner 4. The gas flowing from the exhaust gas inlet 3 into the exhaust gas flow passage 4 flows into the cavity 1a via the through hole 1b. The sound wave generated by the air flow flowing into the cavity 1a repeatedly collides with the cavity wall of the cavity 1a at the cavity 1a and is reflected, and the reflected sound waves interfere with each other, so that the energy of the sound wave is dispersed and consumed, thereby functioning as a sound deadening.

The helmholtz silencer 1 is based on its principle of operation, the smaller the cross-sectional area of the through hole 1b, the larger the volume of the cavity 1a, the lower the frequency of clipping, and conversely, the larger the cross-sectional area of the through hole 1b, the smaller the volume of the cavity 1a, the higher the frequency of clipping. Therefore, by providing a plurality of helmholtz silencers each having through holes of different sectional area sizes and cavities of different volumes, noise of different frequencies can be silenced. In the example shown in fig. 1 and 2, two helmholtz silencers 1 are arranged side by side. As shown in fig. 1 and 2, the helmholtz silencer on the left side in the drawing has a smaller cross sectional area of the through hole on the left side and a larger cross sectional area of the through hole on the right side than the helmholtz silencer on the right side, and the volume of the cavity on the left side is larger and the volume of the cavity on the right side is smaller. In this case, the left-side helmholtz silencer can attenuate noise having a relatively low frequency, and the right-side helmholtz silencer can attenuate noise having a relatively high frequency.

As shown in fig. 1, a partition wall 1d is provided between the cavities 1a and 1a of the two helmholtz silencers 1 and 1. The thickness L6 of the partition wall 1d is preferably 10mm or more to prevent deformation or breakage of the partition wall 1d due to vibration in the cavities 1a, 1 a. On the other hand, a space L5 is provided between the through holes 1b, 1b of the two helmholtz silencers 1, respectively, and the space L5 is preferably 20mm or more so that the silencing effect of the two helmholtz silencers 1, 1 on noise having different frequencies can be fully exerted.

In the embodiment of the present application, there is no limitation on the shape of the cavity 1a and the through hole 1b, for example, the cavity 1a and the through hole 1b may be formed in a geometric shape such as a square, a circle, or a hexagon in cross section, respectively, or may be formed in any other irregular shape. From the viewpoint of ease of manufacture, for example, it is conceivable to form the cross section as square or circular.

In addition, in some embodiments of the present application, the helmholtz silencer 1 may be provided with, for example, a perforated plate 1c as shown in fig. 4. The perforated plate 1c is provided with a plurality of through holes 1b'. By providing the perforated plate 1c, it is equivalent to forming a plurality of helmholtz silencers connected in series. Thus, the noise reduction effect can be further improved.

In addition, in some embodiments of the present application, a helmholtz silencer or a perforated plate may be provided also immediately behind the exhaust gas inlet, whereby the effect of reducing noise can be further improved.

Next, referring to fig. 1 and 3, an expansion silencer 2 in an exhaust bearing housing 100 in some embodiments of the present application will be described.

In the exhaust gas bearing housing 100 shown in fig. 1, an expansion silencer 2 is formed in a side wall of the bearing housing body 5 on the other side (the side opposite to the side on which the helmholtz silencer is provided) of the exhaust gas inlet 3. After flowing through the helmholtz silencer 1, the air flow flows into the expansion silencer 2.

In the bearing housing body 5, one expansion muffler may be provided, or a plurality of expansion mufflers may be provided. In the example shown in fig. 1, 4 expansion silencers 2 are provided. The number of expansion mufflers is not limited, and may be selected as needed. The expansion silencer 2 comprises an expansion chamber 2a. In fig. 3, a cross-sectional view of one of the expansion silencer 2 is shown as seen from the direction B-B in fig. 1. In a typical exhaust bearing housing, a flow passage is provided as indicated by a circular portion in fig. 3. In the bearing housing body 5 of some embodiments of the present application, as shown in fig. 3, an expansion chamber 2a is further provided around the exhaust runner 4. The air flow flowing out of the helmholtz silencer 1 flows in the same flow passage not as the expansion chamber 2a, and then enters the same flow passage as the expansion chamber, so that the sectional area through which the air flow flows is suddenly changed, the sound wave is reflected, the noise is attenuated, and the effect of reducing the noise is achieved.

In the case where a plurality of expansion silencers (for example, 4 expansion silencers are provided in fig. 1) are provided, the flow area of each expansion silencer is different. Since the boundary line between the flow path and the expansion chamber is the same and the flow area of the expansion chamber is obtained by multiplying the length of the expansion chamber by the length of the boundary line, the flow area of the expansion chamber 2a is represented by the length of the expansion chamber 2a in fig. 1. As can be seen from fig. 1. The expansion chambers of the 4 expansion silencers 2 each have different flow areas L1, L2, L3, and L4, respectively, so that noise having different frequencies caused by different rotational speeds can be silenced. In contrast, the smaller the flow area is, the larger the flow area is, the noise of lower frequency can be suppressed. In addition, the thickness of the expansion chamber 2a may be, for example, 20mm to 50mm, preferably 25mm to 35mm, and may be, for example, 30mm. In addition, the cross-sectional shape of the inflation lumen may be any shape, for example, square, circular, hexagonal, etc.

In addition, in the case of forming the expansion chamber of the expansion silencer in the housing body 5 of the exhaust housing 100 by casting, the casting difficulty is high, and therefore, as shown in fig. 5, it is also conceivable to cast a part of the cross-sectional shape of the expansion chamber 2a in the housing body 5, and thereafter, to form the complete cross-sectional shape of the expansion chamber 2a by providing the cover plate 2b on one side of the expansion chamber 2 a. By providing the cover plate 2b, the casting work of the exhaust bearing housing 5 and the subsequent cleaning work of the cast iron pieces can be made easier.

Referring now to fig. 6 and 7, another exhaust bearing housing 100' according to some embodiments of the present application is described. In describing the exhaust bearing housing 100 'shown in fig. 6 and 7, only the differences from the exhaust bearing housing 100 shown in fig. 1 to 3 in the exhaust bearing housing 100' will be described, and the duplicate description of the same parts will be omitted.

In the exhaust bearing housing 100 shown in fig. 1, the helmholtz silencer 1 and the expansion silencer 2 are formed in the housing body 5 along the radial direction of the exhaust bearing housing 100. In contrast, in the exhaust bearing housing 100' shown in fig. 6, the helmholtz silencer 1' and the expansion silencer 2' are formed in the housing body 5' along the axial direction of the exhaust bearing housing 100 '. In this case, the exhaust runner 4 'is branched into two runners 4' a and 4'b, and therefore, as shown in a sectional view in fig. 7 as seen along line C-C in fig. 6, expansion silencers 2a' are provided around the respective two runners 4'a and 4' b.

With the exhaust bearing housing 100' shown in fig. 6 and 7 in which the helmholtz silencer 1' and the expansion silencer 2' are formed in the axial direction, the same technical effects as those of the exhaust bearing housing 100 shown in fig. 1 to 3 can be obtained.

In the embodiment of the present application, the number of the helmholtz silencers and the expansion silencers is not particularly limited, and the helmholtz silencers and the expansion silencers may be designed according to the frequency band in which noise is to be reduced, for example, the number of the helmholtz silencers may be 1 or 2 or more, and the number of the expansion silencers may be 1 to 3 or 4 or more.

In addition, with the exhaust bearing housing 100, 100' in the above-described embodiment, on the one hand, if the flow rate of the air flow is set too low, the silencing effect is not ideal, and on the other hand, if the flow rate is set too high, the flow pressure loss is excessively large. Thus, for example, it is possible to set the exhaust gas flow rate to 3 to 25m/s, and preferably, for example, 8 to 18m/s.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present application, and not for limiting the same; although the application has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the application, and are intended to be included within the scope of the appended claims and description. In particular, the technical features mentioned in the respective embodiments may be combined in any manner as long as there is no structural conflict. The present application is not limited to the specific embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the claims.

Claims (15)

1. An exhaust bearing housing for supporting a screw shaft in a compressor, the exhaust bearing housing comprising: bearing frame body, exhaust gas inlet, exhaust runner, helmholtz silencer and expansion silencer, helmholtz silencer has through-hole and cavity, expansion silencer has the inflation chamber, helmholtz silencer with expansion silencer integrate respectively in the bearing frame body.

2. The exhaust bearing housing of claim 1, wherein the cavity of the helmholtz silencer is integrally formed in the housing body by casting.

3. The exhaust bearing housing of claim 1, wherein the helmholtz silencer comprises a perforated plate disposed in the housing body, the perforated plate having through holes formed therein.

4. An exhaust gas bearing housing according to any one of claims 1 to 3, wherein the expansion chamber of the expansion silencer is integrally formed in the housing body by casting.

5. The exhaust bearing housing of claim 4, wherein a cover plate is provided laterally of the expansion chamber of the expansion silencer.

6. An exhaust bearing housing according to any one of claims 1 to 3, wherein the helmholtz silencer comprises a side helmholtz silencer arranged laterally of the exhaust gas inlet and a rear helmholtz silencer arranged directly behind the exhaust gas inlet.

7. An exhaust bearing housing according to any one of claims 1 to 3, comprising a plurality of said helmholtz silencers and a plurality of said expansion silencers.

8. The exhaust bearing housing of claim 7, comprising 2 of said helmholtz silencers and 4 of said expansion silencers.

9. The exhaust bearing housing of claim 7, wherein cross-sectional areas of the through holes of the respective plurality of helmholtz silencers are different from each other, and volumes of the cavities of the respective plurality of helmholtz silencers are different from each other, and further, flow areas of the expansion chambers of the respective plurality of expansion silencers are different from each other.

10. The exhaust bearing housing of claim 9, wherein the expansion chamber of each of the plurality of expansion silencers has a square, circular or hexagonal cross-section.

11. A housing according to any one of claims 1 to 3, wherein the housing is configured to provide an exhaust gas flow rate in the range 3m/s to 25 m/s.

12. The exhaust bearing housing of claim 11, wherein the exhaust bearing housing is configured to provide an exhaust gas flow rate in the range of 8m/s to 18 m/s.

13. A chock according to any of claims 1 to 3, in which the chock is a lateral chock.

14. A housing according to any one of claims 1 to 3, wherein the housing is an axial exhaust housing.

15. A screw compressor employing a discharge bearing housing according to any one of claims 1 to 14.