CN209944714U

CN209944714U - Silencing device and air conditioner

Info

Publication number: CN209944714U
Application number: CN201920818698.6U
Authority: CN
Inventors: 高文栋
Original assignee: Midea Group Co Ltd; Handan Midea Air Conditioning Equipment Co Ltd
Current assignee: Midea Group Co Ltd; Handan Midea Air Conditioning Equipment Co Ltd
Priority date: 2019-05-31
Filing date: 2019-05-31
Publication date: 2020-01-14
Anticipated expiration: 2029-05-31

Abstract

The utility model discloses a silencing device and air conditioner, silencing device includes: the shell is provided with an air inlet, an air outlet and a silencing channel for communicating the air inlet and the air outlet; and the silencing plate is arranged in the silencing passage, a plurality of silencing holes are formed in the silencing plate, flowing media flowing from the air inlet to the air outlet pass through the silencing holes, and the overflowing areas of at least two silencing holes are different. The utility model discloses technical scheme can improve the noise cancelling effect.

Description

Silencing device and air conditioner

Technical Field

The utility model relates to an air conditioner technical field, in particular to silencing device and air conditioner.

Background

In the process of compressing the refrigerant by the compressor, the noise caused by the pressure pulsation is transmitted to the indoor unit along with the pipeline to cause the indoor unit to generate low-frequency abnormal sound, and in order to reduce the sound transmitted by the indoor unit, a noise eliminator is generally arranged in the pipeline assembly of the outdoor unit.

SUMMERY OF THE UTILITY MODEL

The utility model mainly aims at providing a silencing device aims at improving noise cancelling effect.

In order to achieve the above object, the present invention provides a silencing apparatus, including:

the shell is provided with an air inlet, an air outlet and a silencing channel for communicating the air inlet and the air outlet; and

the silencing plate is arranged in the silencing passage, a plurality of silencing holes are formed in the silencing plate, flowing media flowing from the air inlet to the air outlet pass through the silencing holes, and the overflowing areas of at least two silencing holes are different.

Optionally, the sound-deadening holes extend along the plate surface of the sound-deadening plate to have an elongated shape.

Optionally, the width of each of the muffling holes is the same, and the length of at least two of the muffling holes is different.

Optionally, the extension directions of the muffling holes are the same, and the muffling holes are arranged at intervals along the same direction.

Optionally, the interval between two adjacent silencing holes is 1mm-4 mm.

Optionally, the width of the bloop is 4mm-8 mm.

Optionally, the sound deadening hole has a penetrating direction inclined with respect to an axial direction of the sound deadening channel.

Optionally, the number of the muffling holes is 9-15.

The utility model also provides an air conditioner, include:

a compressor;

an exhaust pipe in communication with the compressor;

the air return pipe is communicated with the compressor; and the number of the first and second groups,

a muffler device connected to the exhaust pipe or the muffler, the muffler device comprising:

Optionally, the ratio of the diameter of the silencing passage of the silencing device to the inner diameter of the exhaust pipe is 1.3-1.5;

the ratio of the diameter of the silencing passage of the silencing device to the inner diameter of the muffler is 1.3-1.5.

The utility model discloses in, after the refrigerant got into the amortization passageway with the fluid form, flowed through the bloop, at the in-process of flowing through the bloop, because the bloop has changed the original flow path of refrigerant, so the refrigerant velocity of flow can change, means that the pressure pulsation of refrigerant can produce the change promptly. For the sound-absorbing plates with the same sound-absorbing holes, the pressure pulsation after flowing through the sound-absorbing holes with the same size is the same, and the pressure pulsation cannot be compensated with each other, so that the effect of attenuation cannot be achieved. And the utility model discloses in because the overflowing area of a plurality of bloops is different, a plurality of bloops's size is inconsistent promptly, after the refrigerant flowed through the acoustical panel, the pressure pulsation's of the refrigerant that flows out from different bloops phase angle is different, so make the crest and the trough of the different pressure pulsation that flow out from different bloops can compensate each other to make pressure pulsation obtain the decay, the realization is fallen the noise of the different frequencies that different pulsation arouses and is made an uproar, the noise cancelling effect has been improved greatly.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed to be used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.

Fig. 1 is a schematic structural diagram of an embodiment of an air conditioner according to the present invention;

FIG. 2 is a schematic view of a portion of the piping associated with the compressor of FIG. 1;

FIG. 3 is a cross-sectional view of the muffler assembly of FIG. 2;

FIG. 4 is a cross-sectional view of the acoustical panel of FIG. 3;

fig. 5 is a schematic sectional view of a silencer in an embodiment of the air conditioner of the present invention.

The reference numbers illustrate:

reference numerals	Name (R)	Reference numerals	Name (R)
				10	Silencing device	121	Silencing hole
11	Shell body	122	Rib
				111	Air inlet	123	Long hole wall
112	Air outlet	20	Compressor with a compressor housing having a plurality of compressor blades
				113	Silencing channel	21	Exhaust pipe
12	Sound-deadening plate	22	Air return pipe

The objects, features and advantages of the present invention will be further described with reference to the accompanying drawings.

Detailed Description

It should be noted that, if directional indications (such as upper, lower, left, right, front and rear … …) are involved in the embodiment of the present invention, the directional indications are only used to explain the relative position relationship between the components, the motion situation, etc. in a specific posture (as shown in the drawings), and if the specific posture is changed, the directional indications are changed accordingly.

The utility model provides an silencing device.

In the embodiment of the present invention, as shown in fig. 1 to 4, the silencer device 10 includes a casing 11, a silencer board 12, and the like.

Wherein, the housing 11 has an air inlet 111, an air outlet 112, and a sound deadening passageway 113 communicating the air inlet 111 and the air outlet 112. In one embodiment, the housing 11 is substantially tubular, and the inner bore of the tubular forms the sound-deadening passageway 113. In one embodiment, the housing 11 is a substantially square housing 11 having a square sound attenuating passageway 113 formed therein. In addition, the housing 11 may also have other shapes, and the shape of the housing 11 in the embodiment of the present invention is not limited, and any shape of the housing 11 may be used.

In this embodiment, the sound-deadening plate 12 is installed in the sound-deadening channel 113, the air inlet 111 and the air outlet 112 of the sound-deadening channel 113 are separated, the sound-deadening holes 121 are formed through the sound-deadening plate 12, two ends of the sound-deadening channel 113 are communicated through the sound-deadening holes 121, the sound-deadening holes 121 allow a flowing medium flowing from the air inlet 111 to the air outlet 112 to pass through, and in the air conditioner, the flowing medium is a refrigerant.

In the above, the flow areas of at least two of the muffling holes 121 are different, for example, in an embodiment, the flow areas of any two muffling holes 121 are different; alternatively, in one embodiment, the flow areas of only some of the muffling holes 121 are different, and the flow areas of the remaining muffling holes 121 are the same. In this embodiment, the difference in the flow area of the two muffling holes 121 means that the two muffling holes 121 are different in size, for example, for the strip-shaped muffling hole 121, the two muffling holes 121 are different in length or width, or both in length and width. The two sound deadening holes 121 are different in aperture for the circular sound deadening holes 121.

The utility model discloses in, after the refrigerant got into amortization passageway 113 with the fluid form, flowed through bloop 121, at the in-process of flowing through bloop 121, because bloop 121 has changed the original flow path of refrigerant, so the refrigerant velocity of flow can change, means that the pressure pulsation of refrigerant can produce the change promptly. The sound-deadening plates 12 having the same size of the sound-deadening holes 121 do not exhibit the effect of attenuation because the pressure pulsation after flowing through the sound-deadening holes 121 having the same size is the same and cannot be compensated for each other. And the utility model discloses in because the overflowing area of a plurality of bloops 121 is different, a plurality of bloops 121's size is inconsistent promptly, after the refrigerant flowed through abatvoix 12, the pressure pulsation's of the refrigerant that flows out from different bloops 121 phase angle is different, so make the crest and the trough of the different pressure pulsation that flow out from different bloops 121 can compensate each other, thereby make pressure pulsation obtain the decay, the realization falls the noise of the different frequencies that different pulsation arouses and makes an uproar, the noise cancelling effect has been improved greatly.

In one embodiment, the sound absorbing holes 121 extend along the plate surface of the sound absorbing plate 12 and have an elongated shape. In this embodiment, the strip-shaped muffling hole 121 has smaller flow resistance and smaller loss of refrigerant pressure compared to a small circular hole. Alternatively, the width B of each muffling hole 121 is the same, and the length L of at least two muffling holes 121 is different. In this embodiment, the length L of the strip-shaped muffling hole 121 is changed instead of the width B, so that more muffling holes 121 can be formed in the muffling plate 12, and the flow dividing effect is better. In addition, in this embodiment, the width B of the muffling hole 121 is the same, and the length L is different, which facilitates the processing of the muffling hole 121.

In an embodiment, the extension directions of the muffling holes 121 are the same, and the muffling holes 121 are arranged at intervals along the same direction, so that the pressure pulsation interaction area of the refrigerant flowing out of two adjacent muffling holes 121 is larger, and the action effect is better.

In one embodiment, the sound-deadening passage 113 is a circular passage, and the sound-deadening plate 12 is a circular plate. Since the sound-absorbing plate 12 is a circular plate, when a plurality of sound-absorbing holes 121 are formed therein, each of the sound-absorbing holes 121 may extend to a side edge of the sound-absorbing plate 12, and the sound-absorbing holes 121 formed in at least one semicircle of the sound-absorbing plate 12 have different lengths, which facilitates the processing and molding of the sound-absorbing holes 121. In this embodiment, the length of the sound-deadening holes 121 passing through the axis of the sound-deadening plate 12 is longest, and the length of the sound-deadening holes 121 gradually decreases in a direction away from the sound-deadening holes 121 having the longest length.

In an embodiment, the distance b between two adjacent muffling holes 121 is 1mm to 4mm, for example, the distance b between two adjacent muffling holes 121 is 1mm, 3mm, or 4mm, which can be specifically set as required. If the interval b between two adjacent sound-absorbing holes 121 is too small, the structural strength of the sound-absorbing plate 12 is too low, and the sound-absorbing plate 12 is easily broken; if the distance b between two adjacent sound-deadening holes 121 is too large, the number of sound-deadening holes 121 provided in the sound-deadening plate 12 is small, and the effect of attenuating pressure pulsation of different frequencies is poor. Therefore, in the present embodiment, the interval b between two adjacent noise canceling holes 121 is set to be 1mm to 4mm, which can avoid the above phenomenon.

In an embodiment, the width B of the muffling hole 121 is 4mm to 8mm, for example, the width B of the muffling hole 121 is 4mm, 5mm, or 8mm, and the like, which can be specifically set as required. If the width B of the muffling hole 121 is too small, the flow area is too small, and the pressure loss after the refrigerant passes through the muffling hole 121 is large. If the width B of the muffling hole 121 is too large, it means that the number of muffling holes 121 provided in the muffling plate 12 is small, and thus the effect of attenuating pressure pulsations of different frequencies is poor; and also tends to result in the structural strength of the sound-absorbing panel 12 being too low and the sound-absorbing panel 12 being broken. Therefore, in the present embodiment, the width B of the muffling hole 121 is set to 4mm to 8mm, which can prevent the above phenomenon.

In one embodiment, the number of the silencing holes 121 is 9-15. For example, 9, 12, or 15 sound-deadening holes 121, etc. may be provided in the sound-deadening panel 12, and may be specifically provided as needed. If the number of the muffling holes 121 is too small, the total flow area is too small, which results in a large pressure loss after the refrigerant passes through the muffling holes 121 and a poor attenuation effect on pressure pulsation of different frequencies. If the number of the sound-deadening holes 121 is too large, the structural strength of the sound-deadening plate 12 tends to be too low, and the sound-deadening plate 12 is likely to be broken. Therefore, in the present embodiment, the number of the muffling holes 121 is set to 9 to 15, which can prevent the above phenomenon from occurring. In this embodiment, the sound-deadening plate 12 is formed by combining a plurality of ribs 122 arranged at intervals in the same direction, and the gap between two adjacent ribs 122 constitutes a sound-deadening hole 121. For example, in the embodiment in which the sound-deadening plate 12 is a circular plate, with one surface passing through the axis of the sound-deadening plate 12 as a plane of symmetry, the lengths of the plurality of ribs 122 located on the same side of the plane of symmetry are all different, and the length of the rib 122 gradually increases in the direction closer to the plane of symmetry. In one embodiment, the ribs 122 can be individually fixed to the housing 11, for example, each rib 122 is welded to the housing 11 or clamped to the housing 11. In an embodiment, a plurality of ribs 122 are disposed in a ring, and both ends of each rib 122 are fixed to the ring, specifically, the ribs 122 may be inserted into the ring by slotting on the inner peripheral wall of the ring, or the ribs 122 may be directly welded to the ring, and the ring is fixed to the housing. In one embodiment, the ribs 122 and the ring are integrally formed, which can greatly reduce the number of manufacturing processes. The number of the ribs 122 is 10-16, for example, 10, 14 or 16 ribs, etc.

In one embodiment, the penetrating direction of the muffling hole 121 is parallel to the axial direction of the muffling channel 113, that is, the muffling hole 121 is a straight hole, so that the flowing direction of the refrigerant in the muffling hole 121 is the same as the flowing direction of the refrigerant in the muffling channel 113.

Referring to fig. 5, in an embodiment, the penetrating direction of the muffling hole 121 is inclined with respect to the axial direction of the muffling channel 113, so that when the refrigerant flows into the muffling hole 121, the direction of the refrigerant changes, and the flow velocity changes, which is beneficial to attenuate the pressure pulsation at the muffling plate 12. In this embodiment, the muffling hole 121 has two long hole walls 123 disposed oppositely, and the extending direction of the long hole walls 123 along the penetrating direction of the muffling hole 121 is inclined with respect to the axial direction of the muffling channel 113, that is, the inclination of the penetrating direction of the muffling hole 121 with respect to the axial direction of the muffling channel 113 means that the long hole walls 123 are inclined with respect to the axial direction of the muffling channel 113. In this embodiment, the angle α of the penetration direction of the muffling hole 121 inclined with respect to the axial direction of the muffling channel 113 is 45 °, which is not only beneficial to better attenuating the pressure pulsation, but also can avoid the excessive change of the flow velocity of the refrigerant due to the excessive inclination angle α. The angle α of the insertion direction of the muffling hole 121 inclined with respect to the axial direction of the muffling passage 113 may be 30 ° or 60 °.

The utility model discloses still provide an air conditioner, this air conditioner includes compressor 20, blast pipe 21, muffler 22 and silencing device 10, and above-mentioned embodiment is referred to this silencing device 10's concrete structure, because this air conditioner has adopted the whole technical scheme of above-mentioned all embodiments, consequently has all beneficial effects that the technical scheme of above-mentioned embodiment brought at least, and the repeated description is no longer given here. Wherein, the exhaust pipe 21 and the return pipe 22 are both communicated with the compressor 20; the discharge pipe 21 and the return pipe 22 are connected by a four-way valve, and the refrigerant discharged from the compressor 20 flows out through the discharge pipe 21, and the refrigerant after heat exchange in the evaporator and the condenser flows back to the compressor 20 through the return pipe 22.

In one embodiment, the muffler device 10 is connected to the exhaust pipe 21. Specifically, the exhaust pipe 21 is composed of two sections of pipe bodies, the casing 11 of the muffler device 10 is connected to the two sections of pipe bodies, and the muffling channel 113 is communicated with the two sections of pipe bodies, so that the refrigerant flows from one section of pipe body to the other section of pipe body through the muffling channel 113. Specifically, since the compressor 20 generates pressure pulsation, which is a small disturbance signal and varies in harmonic fashion with time, the state of the fluid inside the pipe is complicated, noise is radiated, and the pressure pulsation at the discharge port of the compressor 20 is maximized. Therefore, in the present embodiment, by connecting the muffler device 10 to the exhaust pipe 21, which is equivalent to installing the muffler device 10 at the exhaust port of the compressor 20, after the refrigerant enters the muffling channel 113 in a fluid form and flows out through the muffling holes 121, the flow rate of the refrigerant changes, and since the refrigerant flows out from the muffling holes 121 with different sizes and is divided into a plurality of different refrigerant by the muffling holes 121, the flow rate of each refrigerant flowing out from different muffling holes 121 is different, and the phase angle of the pressure pulsation is also different, and the muffling holes 121 with different sizes divide a large simple harmonic pulsation force from the exhaust port of the compressor 20 into a plurality of small and different pressure pulsations, so that the peaks and valleys of the different pressure pulsations compensate each other, and the pressure pulsations are attenuated.

In one embodiment, the ratio of the diameter D of the silencing passage 113 of the silencing device 10 to the inner diameter D of the exhaust pipe 21 is 1.3-1.5, for example, the ratio of the diameter D of the silencing passage 113 of the silencing device 10 to the inner diameter D of the exhaust pipe 21 is 1.3, 1.4, 1.5, or the like. In this embodiment, the diameter D of the muffling channel 113 is larger than the inner diameter D of the exhaust pipe 21, so that the refrigerant flows into the muffling channel 113 as an expansion section, so that the flow velocity of the refrigerant is changed, and the flow velocity of the refrigerant is changed again when the refrigerant flows through the muffling hole 121, thereby facilitating the reduction of pressure pulsation. In addition, since the muffling plate 12 is disposed in the large-sized muffling passage 113, even if the refrigerant flows through the muffling holes 121, the refrigerant flow velocity is largely changed due to the small muffling holes 121, but the total flow area of the plurality of muffling holes 121 is small relative to the flow area of the exhaust pipe 21, and therefore, the loss of the refrigerant pressure due to the disposition of the muffling plate 12 can be largely reduced. The ratio of the diameter D of the muffling channel 113 to the inner diameter D of the exhaust pipe 21 is set to 1.3 to 1.5, which is obtained based on the consideration of the relationship among the diameter D of the muffling channel 113, the number of muffling holes 121, the flow area, and the inner diameter D of the exhaust pipe 21, so as to avoid a large influence on the refrigerant pressure.

In one embodiment, the muffler assembly 10 is coupled to the muffler 22. The muffler device 10 is attached to the muffler pipe 22, whereby the pressure pulsation can be also attenuated. In addition, in an embodiment, a ratio of the diameter D of the sound deadening channel 113 of the sound deadening device 10 to the inner diameter of the muffler 22 is 1.3 to 1.5, and similarly, a ratio of the diameter D of the sound deadening channel 113 of the sound deadening device 10 to the inner diameter of the muffler 22 is 1.3, 1.4, 1.5, or the like. In this embodiment, the diameter D of the muffling channel 113 is larger than the inner diameter of the muffler 22, so that the refrigerant flows into the muffling channel 113 as an expansion section, thereby changing the flow rate of the refrigerant, and the flow rate of the refrigerant changes again when the refrigerant flows through the muffling hole 121, thereby facilitating the reduction of pressure pulsation. In addition, since the muffling plate 12 is disposed in the large-sized muffling passage 113, even if the refrigerant flows through the muffling holes 121, the refrigerant flow velocity is largely changed due to the small muffling holes 121, but the total flow area of the plurality of muffling holes 121 is small relative to the flow area of the muffler 22, and therefore, the loss of the refrigerant pressure due to the disposition of the muffling plate 12 can be largely reduced. The ratio of the diameter D of the muffling channel 113 to the inner diameter of the muffler 22 is set to 1.3-1.5, which is obtained based on the consideration of the relationship among the diameter D of the muffling channel 113, the number of muffling holes 121, the flow area, and the inner diameter of the muffler 22, so as to avoid a large influence on the refrigerant pressure.

The above only is the preferred embodiment of the present invention, not limiting the scope of the present invention, all the equivalent structure changes made by the contents of the specification and the drawings under the inventive concept of the present invention, or the direct/indirect application in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A sound-deadening device, comprising:

2. The acoustic silencer device of claim 1 wherein said silencing holes are elongated extending along the face of said panel.

3. The acoustic abatement apparatus of claim 2, wherein each of the abatement holes has a same width, and at least two of the abatement holes have different lengths.

4. The acoustic silencer device according to claim 2 wherein said silencing holes extend in the same direction, and a plurality of said silencing holes are spaced in the same direction.

5. The acoustic silencer device according to claim 4 wherein the spacing between adjacent ones of said silencing holes is between 1mm and 4 mm.

6. The acoustic abatement apparatus of claim 2, wherein the width of the abatement aperture is from 4mm to 8 mm.

7. The acoustic silencer device according to claim 1, wherein the direction of penetration of the silencing holes is inclined with respect to the axial direction of the silencing passage.

8. The acoustic silencer device according to any one of claims 1 to 7 wherein the number of the silencing holes is 9 to 15.

9. An air conditioner, comprising:

a compressor;

an exhaust pipe in communication with the compressor;

the acoustic abatement apparatus of any one of claims 1-8, connected to the exhaust pipe or the muffler.

10. The air conditioner according to claim 9, wherein the ratio of the diameter of the silencing passage of the silencing device to the inner diameter of the exhaust pipe is 1.3 to 1.5;