CN212690358U

CN212690358U - Silencer and compressor comprising same

Info

Publication number: CN212690358U
Application number: CN202021349907.6U
Authority: CN
Inventors: 周易; 褚伟彦; 王海军
Original assignee: Shanghai Highly Electrical Appliances Co Ltd
Current assignee: Shanghai Highly Electrical Appliances Co Ltd
Priority date: 2020-07-10
Filing date: 2020-07-10
Publication date: 2021-03-12
Anticipated expiration: 2030-07-10

Abstract

The utility model provides a muffler reaches compressor including it, the compressor includes bearing and cylinder, the muffler includes: the boss is provided with a shaft hole and sleeved on the bearing through the shaft hole; the outer extension part is connected with the periphery of the bottom of the boss and surrounds the boss and the bearing to form a silencing cavity; the silencing cavity is a communicated whole and is provided with the guide channel with the axial minimum cross-sectional area of a so as to guide the high-speed airflow rushed out of the cylinder, thereby realizing multiple silencing effects; the internal height H of the silencer and the area a of the flow guide channel are reasonably designed, and the noise reduction function of the silencer is optimized by controlling the ratio of the internal height H to the area a of the flow guide channel within a certain range.

Description

Silencer and compressor comprising same

Technical Field

The utility model belongs to the technical field of the compressor, especially, relate to a muffler of compressor.

Background

In general, a hermetic compressor includes a motor for generating a driving force in an inner space of a casing, and a cylinder coupled to the motor for compressing a refrigerant. The hermetic compressor may be classified into a reciprocating compressor, a scroll compressor, and a rotary compressor according to a refrigerant compression mechanism. Among them, the reciprocating compressor, the scroll compressor, and the rotary compressor compress a refrigerant using a rotational force of a motor.

Fig. 1 is a schematic structural view illustrating a related art rotary compressor. The housing 2 includes an upper cover 1 and a lower cover. The motor 3 of the compressor is placed inside the casing 2. The motor 3 has a crankshaft 4, and the rotational force of the motor is transmitted to the cylinder 5 through the crankshaft 4.

In practical applications, the high-speed gas flowing out from the cylinder 5 generates noise, and the noise has a wide frequency range. In order to reduce noise, an upper silencer 901 is further installed on the upper bearing 4, and the upper silencer 901 and the upper bearing 4 enclose to form a silencing cavity. Part of high-speed gas flowing out of the cylinder 5 is discharged from an air outlet hole of the upper bearing and enters a silencing cavity of the upper silencer. Because the flow area of the gas changes suddenly, airflow pulsation is easy to generate, so that the gas in the silencing cavity flows back and forth, the noise energy is repeatedly dissipated, and the noise reduction effect is achieved. However, the cavity height of the existing silencer is not optimized, the structure of the internal cavity is single, multiple silencing effects cannot be realized, and the noise reduction effect is poor.

SUMMERY OF THE UTILITY MODEL

To the defect among the prior art, the utility model aims at providing a muffler reaches compressor including it aims at improving the noise reduction to current rotary compressor exhaust noise.

The utility model provides a muffler for the compressor, the compressor includes bearing and cylinder, the muffler includes:

the boss is provided with a shaft hole and sleeved on the bearing through the shaft hole; and

the extension part is connected with the periphery of the bottom of the boss and forms a silencing cavity with the boss and the bearing in an enclosing manner;

the silencing cavity is provided with a flow guide channel, the minimum cross-sectional area of the flow guide channel along the axial direction is a, so that high-speed airflow rushed out of the cylinder is guided, and multiple silencing effects can be realized;

the range of the ratio of the inner height H of the silencing cavity to the cross-sectional area a of the flow guide channel is more than or equal to 0.1 and less than or equal to 2 of H/a, the unit of H is millimeter, and the unit of a is square millimeter.

Optionally, a ratio of an inner height H of the sound attenuation cavity to a radial cross-sectional area a of the flow guide channel is 0.1 ≦ H/a ≦ 0.2, where H is expressed in millimeters, and a is expressed in square millimeters.

Optionally, the muffler covers the bearing, and forms a central symmetry or a central asymmetry multi-petal sound-deadening chamber between the bearing, each petal structure of the multi-petal sound-deadening chamber is a sound-deadening sub-chamber, the sound-deadening sub-chambers are communicated with each other, and the flow guide channel is located between two adjacent petal structures along the axial minimum cross section.

Optionally, in the multi-petal sound-deadening cavity structure, the number of the sound-deadening sub-cavities ranges from 2 to 6.

Optionally, in the multi-petal sound-deadening cavity structure, the number of the sound-deadening sub-cavities ranges from 4 to 6.

Optionally, the extending portion is provided with a plurality of screw holes in an inward concave portion between two adjacent noise reduction sub-cavities, and the inward concave portion is screwed with the bearing through bolts penetrating through the screw holes.

Optionally, the effective noise reduction frequency domain of the silencer on the airflow noise is 400Hz to 1600 Hz.

Optionally, the bearing of the compressor includes an upper bearing and a lower bearing, and the upper bearing or the lower bearing is provided with the muffler, or the upper bearing and the lower bearing are respectively provided with the muffler.

Optionally, the boss is provided with an air outlet; or the circumference edge of the shaft hole of the boss is provided with a groove, and the groove and the bearing enclose to form an opening.

The embodiment of the utility model provides a compressor, including above-mentioned arbitrary silencer.

Compared with the prior art, the utility model beneficial effect lie in:

the utility model discloses a muffler has the amortization chamber height of optimizing, the ratio of the interior height of reasonable design muffler and conductance channel area, when the ratio of the interior height of amortization chamber and conductance channel area is in a basically definite proportion scope, the sound pressure that produces in the muffler is of unequal size, and the sound wave of phase place difference offsets each other in certain extent, and is more effective to the dissipation of noise energy; for compressors with different shapes, the silencer has more controllable and superior noise reduction effect compared with the prior art.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the application.

Drawings

Other features, objects and advantages of the invention will become more apparent upon reading of the detailed description of non-limiting embodiments with reference to the following drawings:

FIG. 1 is a cross-sectional view of a prior art compressor;

fig. 2 is a schematic structural view of an upper silencer in the compressor of the present invention;

FIG. 3 is a cross-sectional view taken along line A-A of FIG. 2;

fig. 4 is a top view of an assembly schematic of an upper muffler in a compressor according to the present invention;

FIG. 5 is a cross-sectional view taken along line B-B of FIG. 4;

fig. 6 is a schematic structural view of an upper silencer in the compressor of the present invention;

FIG. 7 is a graph showing the relationship between the ratio (H/a) of the inner height of the sound-deadening chamber to the area of the flow-guiding passage and the noise of the discharge gas flow of the compressor.

Reference numerals

1 upper cover

2 casing

3 electric machine

31 crankshaft

4 Upper bearing

41 through hole

5 air cylinder

6 lower bearing

9 upper silencer

91 screw hole

92 boss

93 air outlet holes

94 axle hole

95 epitaxial portion

951 junction of boss and extension

96 silencing cavity

961 flow guide channel

97 sound-deadening subchamber

Detailed Description

Detailed descriptions will be given below of embodiments of the present invention. Although the invention will be described and illustrated in connection with certain specific embodiments, it should be understood that the invention is not limited to these embodiments. On the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the scope of the invention as defined by the appended claims.

Furthermore, in the following detailed description, numerous specific details are set forth in order to provide a better understanding of the present invention. It will be understood by those skilled in the art that the present invention may be practiced without these specific details. In other instances, well-known structures and components have not been described in detail so as not to obscure the present invention.

In order to solve the technical problem, the utility model provides a muffler reaches compressor including it. As shown in fig. 1, the upper bearing 4 is mounted with an upper muffler, which is covered on the upper bearing 4, for attenuating noise of high-speed gas flowing out from the cylinder 5. The compressor shown in the embodiment is a single-cylinder compressor, and the pump body structure thereof includes one cylinder 5, in other embodiments, the compressor can also be a double-cylinder compressor, and the pump body structure thereof includes an upper cylinder and a lower cylinder.

As shown in fig. 1 to 3, a boss 92 is provided at the middle of the upper muffler, and a continuous extension 95 is provided at the outer periphery of the bottom of the boss 92. The middle part of the silencer is provided with a shaft hole 94 which is sleeved outside the through hole 41 of the bearing, and an outer extension part 95 covers the disc part of the bearing. The boss 92, the extension 95, the junction 951 of the boss and the extension, and the bearing enclose a sound damping chamber 96.

Specifically, referring to fig. 3 and 5, the ratio H/a of the inner height H of the sound-deadening chamber 96 to the axial cross-sectional area a (hereinafter referred to as the flow guide channel area) of the flow guide channel 961 is in a range of 0.1 ≦ H/a ≦ 2(H is in mm, and a is in mm). The cross-sectional area a here represents the smallest cross-sectional area of the flow-guiding channel in the axial direction. That is, as can be seen from fig. 4, the boss 92 has a multi-lobe structure, and the cross-sectional area of the flow guide channel 961 cut along the direction B-B at the central position of the connection portion of two adjacent lobe structures is the minimum cross-sectional area.

Further, the ratio H/a of the inner height H of the sound-deadening chamber 96 to the radial cross-sectional area a of the flow-guiding passage 961 is in a range of 0.1 ≦ H/a ≦ 0.2 (mm for H, mm for a). Specifically, the value of the ratio H/a may be selected according to needs, for example, 0.12, 0.15, or 0.18, and the like, and may also be further greater than 0.2, for example, 0.3,0.4, and the like. In order to achieve the noise reduction effect, the ratio range considers the spatial limitation of each product type, including the installation and adjustment of the sizes of the stator, the rotor and the crankshaft, the overcoming of the influence of the holding force and the deflection under high rotating speed, and has high practicability.

The circumferential edge of the sound-deadening chamber 96 is at points that are not equidistant from the axial hole 94. Specifically, the outer periphery of the bottom of the boss 92 is in a multi-petal shape with a central symmetry, and the wide part of the petal shape forms a plurality of noise reduction sub-cavities 97 which are connected by a flow guide channel 961 at the narrow part. As shown in fig. 2, the chamber of the muffling chamber 96 is an integral body, and the plurality of muffling sub-chambers 97 are communicated by a flow guide channel 961 formed at a narrow position, so that airflow pulsation is easily generated due to sudden change of the flow area of the gas, and the gas in the integral muffling chamber 96 flows back and forth, thereby achieving a better noise reduction effect.

In other embodiments, by setting the boss 92 to be a non-centrosymmetric form, the shape and size of each noise reduction sub-cavity are different, so as to provide various paths for the gas to flow back and forth, and generate asymmetric disturbance to the high-speed airflow ejected by the cylinder 5, which also falls within the protection scope of the present invention.

As shown in fig. 7, when the above-mentioned silencer structure is adopted and the ratio (H/a) of the inner height of the silencing cavity 96 to the area of the flow guide channel 961 is set within the above-mentioned range, the compressor has a better noise reduction effect in a wider frequency domain than the existing silencer technology, in this embodiment, the noise reduction effect in the frequency domain of 400Hz to 1600Hz is improved to different degrees, and can be up to 8dB at most.

Data acquisition in fig. 7 is from the single cylinder compressor who has set up the muffler of the sub-chamber 97 of four silencers at the upper bearing, can deduce from this, and upper bearing 4 and lower bearing 6 when single cylinder compressor set up the muffler of the sub-chamber 97 of four silencers respectively, or set up the muffler of the sub-chamber 97 of other quantity silencers respectively, or set up on double cylinder compressor the utility model discloses a during the muffler, the noise reduction effect will probably be more obvious.

The utility model discloses a on the basis, the peripheral shape of amortization subchamber 97 is not limited to smooth arcuation to produce different air current pulsation routes in single subchamber, also fall equally within the protection scope of the utility model.

Further, as shown in fig. 6, the number of the sound-deadening sub-chambers 97 ranges from 2 to 6, preferably from 4 to 6, according to the space requirement and the actual requirement in the compressor, and the area a of the flow-guiding passage 961 is kept unchanged, so that the noise reduction effect of the formed sound-deadening chamber 96 is better.

As shown in fig. 2, the recessed portion of the outer extension 95 of the muffler has a screw hole 91, and the screw hole 91 is screwed to the upper bearing 4 by a bolt.

As shown in fig. 4, the upper damper is fitted over the upper bearing 4, and the shaft hole 94 is fitted to the outside of the through hole 41 of the upper bearing 4, and the edge of the extended portion 95 comes into contact with the disk portion of the upper bearing 4.

Similarly, the lower muffler covers the lower bearing 6, the shaft hole 94 is sleeved outside the through hole of the lower bearing 6, and the edge of the extending portion 95 is in contact with the disk portion of the lower bearing 6.

It should be noted that the edge of the outer extension 95 of the muffler and the bearing may be hermetically connected by laser welding or gluing.

In an alternative embodiment, the boss 92 is provided with an air outlet hole 93 for discharging high-speed air, or a groove is formed along the circumferential edge of the shaft hole 94 of the boss 92, and the groove and the upper bearing 4 or the lower bearing 6 surround to form an opening for discharging high-speed air.

To sum up, compared with the prior art, the utility model discloses a muffler has following advantage:

the noise reduction effect can be enhanced only by changing the ratio of the height in the silencing cavity to the minimum cross-sectional area of the flow guide channel, and the compressor system with the sound absorber limited by the internal structure of the compressor has advantages;

and secondly, the noise reduction effect of the frequency domain from 400Hz to 1600Hz is improved to different degrees, and the silencer has obvious noise reduction effect on the noise generated when the running rotating speed of the compressor is high, medium and low.

The foregoing is a more detailed description of the present invention, taken in conjunction with specific alternative embodiments, and it is not intended that the invention be limited to the specific embodiments shown and described. To the utility model belongs to the technical field of ordinary technical personnel, do not deviate from the utility model discloses under the prerequisite of design, can also make a plurality of simple deductions or replacement, all should regard as belonging to the utility model discloses a protection scope.

Claims

1. A muffler for a compressor, the compressor including a bearing and a cylinder, the muffler comprising:

the boss is provided with a shaft hole and sleeved on a bearing of the compressor through the shaft hole; and

the silencing cavity is provided with a flow guide channel, and the minimum cross-sectional area of the flow guide channel along the axial direction is a;

2. The muffler according to claim 1, wherein a ratio of an inner height H of the muffling chamber to a radial cross-sectional area a of the flow-guiding passage is in a range of 0.1 ≦ H/a ≦ 0.2.

3. The muffler of claim 1, wherein the muffler cover is fitted to the bearing to form a central symmetrical or central asymmetrical multi-lobed muffling chamber with the bearing, each lobe structure of the multi-lobed muffling chamber is a muffling sub-chamber, the muffling sub-chambers are communicated with each other, and the minimum cross section of the flow guide channel in the axial direction is located between two adjacent lobe structures.

4. The muffler of claim 3, wherein the number of muffler subchambers in the multi-lobed muffler chamber structure ranges from 2 to 6.

5. The muffler of claim 4, wherein the number of muffler subchambers in the multi-lobed muffler chamber structure ranges from 4 to 6.

6. The muffler of claim 3, wherein the recessed portion of the extension between two adjacent muffler cavities is provided with a plurality of screw holes, and the recessed portion is screwed with the bearing by bolts passing through the screw holes.

7. The silencer of claim 1, wherein the effective noise reduction frequency range for the silencer is 400Hz to 1600 Hz.

8. The muffler of claim 1, wherein the bearing of the compressor comprises an upper bearing and a lower bearing, and wherein the upper bearing or the lower bearing is provided with the muffler, or wherein the upper bearing and the lower bearing are provided with the muffler, respectively.

9. The silencer of claim 1, wherein the boss is provided with an air outlet hole, or a groove is formed in a circumferential edge of the shaft hole of the boss, and the groove and the bearing enclose an opening.

10. A compressor, characterized by comprising a muffler as claimed in any one of claims 1 to 9.