GAS WATER HEATER

FIELD

The present disclosure relates to the technical field of household appliances, and in particular, to a gas water heater.

BACKGROUND

At present, a gas water heater is the most convenient and economical device for quickly heating water, and has energy conversion efficiency exceeding 90%. Compared with an electric water heater, the gas water heater is more energy-saving and more in line with requirements of carbon peaking and carbon neutralization. However, when the gas water heater is working normally, it will produce a lot of noise, especially low-frequency noise, which is difficult to be blocked, and brings a bad experience to people who are near the water heater.

SUMMARY

The present disclosure aims to at least solve one of the technical problems existing in the related art. Therefore, the present disclosure provides a gas water heater, to greatly reduce noise and an air inlet resistance.

A gas water heater according to an embodiment of a first aspect of the present disclosure includes: a bottom housing having an opening; a burner mounted at the bottom housing; and a cover plate assembly mounted at the bottom housing and covering the opening. The cover plate assembly includes a first cover plate and a second cover plate. The second cover plate is located between the burner and the first cover plate. The cover plate assembly has an air inlet channel located between the first cover plate and the second cover plate. The first cover plate has a first flow inlet in communication with the air inlet channel. The second cover plate has a second flow inlet distant from the first flow inlet. The second flow inlet is in communication with the air inlet channel and an air inlet of the burner.

With the gas water heater according to the embodiments of the present disclosure, by providing a multi-layer cover plate structure, each layer of cover plate has a weaken effect on internal noise, which enhances a sound insulation effect. Moreover, a cavity between the cover plates is utilized to form a long air inlet channel, which can greatly increase a path length of the noise propagating outwards along the air inlet channel, and effectively improve a transmission loss of the outward propagation of noise. Moreover, air inlet noise is basically eliminated, and the flow channel resistance is greatly reduced.

According to an embodiment of the present disclosure, the second flow inlet includes a first through hole group and a second through hole group, the first through hole group is disposed at a position close to a primary air inlet of the burner, and the second through hole group is disposed at a position adjacent to a secondary air inlet of the burner.

By independently designing the first through hole group and the second through hole group, which are used for air inlet, for the primary air inlet and the secondary air inlet, a flow quantity proportion of primary air inlet and a flow quantity proportion of secondary air inlet may be improved, which helps the burner to obtain a better burning effect, and lowers a content of harmful gases such as CO in a smoke gas.

According to an embodiment of the present disclosure, a flow cross-sectional area of the first through hole group is A1, and a flow cross-sectional area of the second through hole group is A2, where 1≤A1/A2≤2.

According to an embodiment of the present disclosure, a flow cross-sectional area of the first flow inlet is P1, and a flow cross-sectional area of the second flow inlet is P2, where 1.5≤P2/P1≤3.

By designing a second flow inlet located inside to have a flow cross-sectional area greater than a first flow inlet located outside, a flow channel resistance caused by the air inlet channel may be eliminated, turbulent noise in the air inlet channel may be further reduced, and generation of sound whistling at the second flow inlet is prevented.

According to an embodiment of the present disclosure, the burner is mounted in a lower region of the bottom housing, the second flow inlet is located in a lower region of the second cover plate, and the first flow inlet is located in an upper region of the first cover plate.

In this way, a length of the air inlet channel is basically equivalent to a height of the whole machine, which can greatly increase a path length of the noise propagating outwards along the air inlet channel. Moreover, an external first flow inlet is located at a top end. When the whole machine is mounted at a wall, the first flow inlet is basically located in a region close to a roof in the room, which brings no wind feeling to the user, with a better use experience.

According to an embodiment of the present disclosure, the first cover plate is provided with a side wall plate facing towards the bottom housing. The side wall plate has a flange bent inwards. The second cover plate is mounted at a side of the flange facing away from the bottom housing.

According to an embodiment of the present disclosure, a sound attenuation component is disposed in the air inlet channel, and the sound attenuation component is mounted at the first cover plate and/or the second cover plate.

According to an embodiment of the present disclosure, the sound attenuation component includes a plurality of regions, the plurality of regions respectively corresponds to different positions of the bottom housing in a front-rear direction, and a sound attenuation parameter in one of at least two regions of the plurality of regions of the sound attenuation component is different from a sound attenuation parameter in another one of the at least two regions.

According to an embodiment of the present disclosure, the sound attenuation component has a sound attenuation cavity, and the sound attenuation cavity has a sound attenuation hole at a wall surface of the sound attenuation cavity facing towards the bottom housing.

According to an embodiment of the present disclosure, the sound attenuation component has a plurality of sound attenuation cavities, the plurality of sound attenuation cavities is arranged in an array, and each sound attenuation cavity has a plurality of sound attenuation holes arranged in an array.

According to an embodiment of the present disclosure, a volume of one of at least two sound attenuation cavities of the plurality of sound attenuation cavities is different from a volume of another one of the at least two sound attenuation cavities; and/or a flow cross-sectional area of a sound attenuation hole corresponding to the one of the at least two sound attenuation cavities is different from a flow cross-sectional area of a sound attenuation hole corresponding to the other one of the at least two sound attenuation cavities; and/or a density of the sound attenuation holes corresponding to the one of the at least two sound attenuation cavities is different from a density of the sound attenuation holes corresponding to the other one of the at least two sound attenuation cavities.

According to an embodiment of the present disclosure, the sound attenuation component includes a plurality of baffles, and an angle between a normal line of at least a part of each of the plurality of baffles and an airflow direction in the air inlet channel is smaller than 30°.

According to an embodiment of the present disclosure, the baffle is in an arc shape and is bent away from the first flow inlet.

According to an embodiment of the present disclosure, a sealing gasket is sandwiched between the cover plate assembly and the bottom housing.

One or more of the above technical solutions in the embodiments of the present disclosure have at least one of the following technical effects.

By providing the multi-layer cover plate structure, each layer of cover plate has a weaken effect on internal noise, which enhances a sound insulation effect. Moreover, a cavity between the cover plates is utilized to form a long air inlet channel, which can greatly increase the path length of outward propagation of the noise along the air inlet channel, and effectively improve a transmission loss of the outward propagation of noise. Moreover, air inlet noise is basically eliminated, and the flow channel resistance is greatly reduced.

Further, by independently designing the first through hole group and the second through hole group, which are used for air inlet, for the primary air inlet and the secondary air inlet, the flow quantity proportion of primary air inlet and the flow quantity proportion of secondary air inlet may be improved, which helps the burner to obtain a better burning effect, and lowers the content of harmful gases such as CO in the smoke gas.

Additional aspects and advantages of the present disclosure will be given in part in the following description, or become apparent in part from the following description, or can be learned from practicing of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to clearly explain technical solutions of embodiments of the present disclosure, drawings used in the description of the embodiments are briefly described below. Obviously, the drawings as described below are merely some embodiments of the present disclosure. Based on these drawings, other drawings can be obtained by those skilled in the art without creative effort.

FIG. 1 is a first schematic view of a structure of a noise reduction device according to an embodiment of the present disclosure;

FIG. 2 is a second schematic view of a structure of a noise reduction device according to an embodiment of the present disclosure;

FIG. 3 is a first exploded view of a gas water heater according to an embodiment of the present disclosure;

FIG. 4 is a first exploded view of a noise reduction device according to an embodiment of the present disclosure;

FIG. 5 is a second exploded view of a gas water heater according to an embodiment of the present disclosure;

FIG. 6 is a third exploded view of a gas water heater according to an embodiment of the present disclosure;

FIG. 7 is a third schematic view of a structure of a noise reduction device according to an embodiment of the present disclosure;

FIG. 8 is a fourth exploded view of a gas water heater according to an embodiment of the present disclosure;

FIG. 9 is a fifth exploded view of a gas water heater according to an embodiment of the present disclosure;

FIG. 10 is a sixth exploded view of a gas water heater according to an embodiment of the present disclosure;

FIG. 11 is a schematic view of a structure of an air inlet channel of a gas water heater according to an embodiment of the present disclosure;

FIG. 12 is a first schematic view of a structure of a cover plate assembly of a gas water heater according to an embodiment of the present disclosure;

FIG. 13 is a second schematic view of a structure of a cover plate assembly of a gas water heater according to an embodiment of the present disclosure;

FIG. 14 is a first exploded view of a partial structure of a gas water heater according to an embodiment of the present disclosure;

FIG. 15 is a first schematic view of a structure of a sound attenuation component of a gas water heater according to an embodiment of the present disclosure;

FIG. 16 is a second schematic view of a structure of a sound attenuation component of a gas water heater according to an embodiment of the present disclosure;

FIG. 17 is a second exploded view of a partial structure of a gas water heater according to an embodiment of the present disclosure;

FIG. 18 is a third schematic view of a structure of a sound attenuation component of a gas water heater according to an embodiment of the present disclosure;

FIG. 19 is a fourth schematic view of a structure of a sound attenuation component of a gas water heater according to an embodiment of the present disclosure;

FIG. 20 is a fifth schematic view of a structure of a sound attenuation component of a gas water heater according to an embodiment of the present disclosure;

FIG. 21 is a sixth schematic view of a structure of a sound attenuation component of a gas water heater according to an embodiment of the present disclosure;

REFERENCE NUMERALS

- bottom housing 100;
- burner 140, heat exchanger 150, fan system 160, smoke pipe 161, sealing gasket 171, sealing ring 172; sound attenuation component 200, base 210, sound attenuation cavity 220, first region 221, second region 222, sound attenuation hole 230, baffle 240, support plate 250;
- first cover plate 310, first flow inlet 311, side wall plate 312, flange 313;
- second cover plate 320, second flow inlet 321, first through hole group 322, second through hole group 323;
- air inlet channel 330;
- front cover plate 420, panel 421, left side plate 422, right side plate 423.

DETAILED DESCRIPTION

Implementations of the present disclosure are described in further detail below in combination with the accompanying drawings and embodiments. The following embodiments are used to illustrate the present disclosure, but are not used to limit the scope of the present disclosure.

In the embodiments of the present disclosure, serial numbers edited by components themselves, such as “first” and “second”; (1), (2), (3); step 1, step 2, and the like are only used to distinguish the described objects, and do not have any sequential or technical meaning. Unless otherwise specified, “plurality” means at least two. The terms “comprising,” “including,” “having,” “containing,” and the like used in the embodiments of the present disclosure are each open-ended term, i.e., mean including but not limited to. The term “and/or” in the embodiments of the present disclosure only represents a relationship between correlated objects, including three relationships. For example, “A and/or B” may mean three situations: A only, B only, or both A and B.

In the embodiments of the present disclosure, words “exemplary” or “for example” are used to indicate an example, illustration, or description. Any embodiment or design solution described as “exemplary” or “for example” in the embodiments of the present disclosure should not be construed as being more preferred or advantageous over other embodiments or design solutions. Exactly, the use of the words “exemplary” or “for example” is intended to present related concepts in a specific manner. Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art of the present disclosure. In the event of any inconsistency, the meaning described in this specification or the meaning derived from the contents described in this specification shall prevail.

In descriptions of the embodiments of the present disclosure, it should be noted that, the orientation or the position indicated by technical terms such as “center,” “longitudinal,” “lateral,” “over,” “below,” “front,” “rear,” “left,” “right,” “vertical,” “horizontal,” “top,” “bottom,” “inner,” and “outer” should be construed to refer to the orientation and the position as shown in the drawings, and is only for the convenience of describing the embodiments of the present disclosure and simplifying the description, rather than indicating or implying that the pointed device or element must have a specific orientation, or be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present disclosure.

In the descriptions of the embodiments of the present disclosure, it should be noted that, unless otherwise clearly specified and limited, terms such as “connect,” “couple,” and the like should be understood in a broad sense. For example, it may be a fixed connection or a detachable connection or connection as one piece; a mechanical connection or an electrical connection; a direct connection or an indirect connection through an intermediate. For those of ordinary skill in the art, the specific meaning of the above terms in the embodiments of the present disclosure should be understood according to specific situations.

In the embodiments of the present disclosure, unless expressly stipulated and defined otherwise, the first feature “on” or “under” the second feature may mean that the first feature is in direct contact with the second feature, or the first and second features are in indirect contact through an intermediate. Moreover, the first feature “above” the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply mean that the level of the first feature is higher than that of the second feature. The first feature “below” the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply mean that the level of the first feature is smaller than that of the second feature.

In descriptions of the present disclosure, descriptions with reference to the terms “an embodiment,” “some embodiments,” “examples,” “specific examples,” or “some examples” etc., mean that specific features, structure, materials, or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the described specific features, structures, materials or characteristics may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine the different embodiments or examples and the features of the different embodiments or examples described in this specification without contradicting each other.

A noise reduction device for a gas water heater and a gas water heater according to the embodiments of the present disclosure are described below with reference to FIG. 1 to FIG. 21.

As shown in FIG. 1 and FIG. 2, the noise reduction device for the gas water heater according to the embodiments of the present disclosure includes a base 210. The base 210 has a surface facing towards a noise source. The noise source may be a fan system 160, a heat exchange system, and a burner 140 of the gas water heater. A surface having sound attenuation holes 230 in FIG. 1 and FIG. 2 is the surface.

The base 210 may be made of plastic, metal, ceramic, or other materials.

The base 210 has a plurality of sound attenuation cavities 220 formed therein. The plurality of sound attenuation cavities 220 are arranged at intervals along the surface of the base 210. Adjacent sound attenuation cavities 220 are partitioned by an entity in the base 210.

The sound attenuation cavity 220 may be in a cuboid shape or a spherical shape or other shapes. A region of the base 210 where no sound attenuation cavity 220 is provided may be a thin-walled structure, to reduce a weight of a sound attenuation component.

The surface has sound attenuation holes 230. Each of the plurality of sound attenuation cavities 220 is in communication with outside through respective sound attenuation holes 230.

The sound attenuation hole 230 may be in a circular shape, triangular shape, square shape, or the like.

When the gas water heater is working, the fan system 160, the heat exchange system, and the burner 140 generate working noise. When the noise propagates outwards, the noise may be propagated to the sound attenuation cavities 220 through the sound attenuation holes 230. Energy of the noise is consumed by a plurality of times of reflections in the sound attenuation cavities 220.

Especially for low-frequency noise generated when the gas water heater is working, each of sound absorption materials such as sound insulation cotton in the related art may be effective. The noise reduction device according to the embodiments of the present disclosure may absorb the low-frequency noise through cooperation of the sound attenuation cavities 220 with the sound attenuation holes 230.

The noise reduction device for the gas water heater according to the embodiment of the present disclosure can achieve a plurality of times of reflections of noise through a structure of the sound attenuation cavities 220 with the sound attenuation holes, thereby consuming energy of the low-frequency noise and reducing the influence on a user.

In some embodiments, as shown in FIG. 2, the surface includes a plurality of regions. A volume of a sound attenuation cavity 220 corresponding to one of at least two regions of the plurality of regions is different from a volume of a sound attenuation cavity 220 corresponding to another one of the at least two regions; and/or a flow cross-sectional area of a sound attenuation hole 230 corresponding to the one of the at least two regions is different from a flow cross-sectional area of a sound attenuation hole 230 corresponding to the other one of the at least two regions; and/or a density of sound attenuation holes 230 corresponding to the one of the at least two regions is different from a density of sound attenuation holes 230 corresponding to the other one of the at least two regions.

When the noise reduction device is mounted in the gas water heater, as shown in FIG. 5 and FIG. 8, the first region 221 faces towards the burner 140 and the heat exchanger 150. In some embodiments, the first region 221 faces towards a burning chamber of the burner 140 and the heat exchanger 150. A second region 222 faces towards the fan system 160, at which A facing towards B means that projections of A and B substantially coincide with each other in a front-rear direction.

A volume of one of at least two sound attenuation cavities 220 is different from a volume of another one of at least two sound attenuation cavities 220; and/or a flow cross-sectional area of a sound attenuation hole 230 corresponding to the one of at least two sound attenuation cavities 220 is different from a flow cross-sectional area of a sound attenuation hole 230 corresponding to the other one of at least two sound attenuation cavities 220; and/or a density of sound attenuation holes 230 corresponding to the one of at least two sound attenuation cavities 220 is different from a density of sound attenuation holes 230 corresponding to the other one of at least two sound attenuation cavities 220.

In other words, there is a difference in at least one of the three parameters, that is, the volume of the sound attenuation cavity 220, the flow cross-sectional area of the sound attenuation hole 230, and the density of the sound attenuation holes 230 corresponding to the sound attenuation cavity 220, between the at least two sound attenuation cavities 220. In this way, the sound generated by the gas water heater may be attenuated according to different frequency characteristics of burning noise, water flow noise, and flow-induced noise of the gas water heater.

In some embodiments, when the noise reduction device is mounted in the gas water heater, a volume of a sound attenuation cavity 220 facing towards the burner 140 and the heat exchanger 150 is greater than a volume of a sound attenuation cavity 220 facing towards the fan system 160.

Through research, the inventor finds that noise sources of normal operation of the gas water heater include burning noise, fan noise, gas injection noise, mechanical vibration noise, and water flow noise. The burning noise has obvious low-frequency characteristics and strong penetrability. Noise of a fan and water pump has obvious high-frequency characteristics, is sharp and harsh, and has a poor auditory experience.

By designing the volume of the sound attenuation cavity 220 facing towards the burner 140 and the heat exchanger 150 to be larger, the low-frequency noise may be better absorbed.

As shown in FIG. 2, projection areas of two sound attenuation cavities 220 with different volumes on the surface are different. For example, in FIG. 2, a projection area of a sound attenuation cavity 220 in the second region 222 on the surface is greater than a projection area of a sound attenuation cavity 220 in the first region 221 on the surface.

Depths of the two sound attenuation cavities 220 with different volumes in a direction perpendicular to the surface may be the same, which facilitates processing.

In other embodiments of the present disclosure, the depths of the two sound attenuation cavities 220 with different volumes in the direction perpendicular to the surface may also be designed differently.

In some embodiments, when the noise reduction device is mounted in the gas water heater, a quantity of sound attenuation holes 230 corresponding to the sound attenuation cavity 220 facing towards the burner 140 and the heat exchanger 150 is smaller than a quantity of sound attenuation holes 230 corresponding to the sound attenuation cavity 220 facing towards the fan system 160. By designing a larger quantity of the sound attenuation holes 230 corresponding to the sound attenuation cavity 220 facing towards the fan system 160, high-frequency noise may be better absorbed.

The plurality of sound attenuation cavities 220 are arranged in an array along the surface. Each sound attenuation cavity 220 has a plurality of sound attenuation holes 230 arranged in an array. In this way, each of a relatively large quantity of sound attenuation cavities 220 and sound attenuation holes 230 occurs in each region, which can realize multi-region sound attenuation.

In some embodiments, the volume V of the sound attenuation cavity 220 satisfies: 10 mm³≤V≤455 mm³. After a lot of research, the inventor finds that the sound attenuation cavity 220 satisfying this volume range may better absorb noise ranging from 200 Hz to 800 Hz. Working noise of the gas water heater is basically located in this range. For example, V=100 mm³, or V=200 mm³, or V=300 mm³, or V=400 mm³.

In some embodiments, the sound attenuation hole 230 may be circular. The circular sound attenuation hole 230 is convenient for processing. The sound attenuation hole 230 has a diameter D, where 0.6 mm≤D≤2 mm. Through a lot of research, the inventor finds that the sound attenuation hole 230 in this size range may better introduce the noise ranging from 200 Hz to 800 Hz. The working noise of the gas water heater is basically located in this range. For example, D=0.8 mm, or D=1.0 mm, or D=1.5 mm.

In some embodiments, the surface includes a first region 221 and a second region 222.

A volume of a sound attenuation cavity 220 in the first region 221 is V1, a diameter of a sound attenuation hole 230 in the first region 221 is D1, and a quantity of sound attenuation holes 230 corresponding to each sound attenuation cavity 220 in the first region 221 is N1, where 60 mm³≤V1≤455 mm³, 0.6 mm≤D1≤2 mm, 50≤N1≤75. For example, V1=200 mm³, D1=1 mm, N1=66. The first region 221 in this form may better absorb noise at a frequency of about 300 Hz.

A volume of a sound attenuation cavity 220 in the second region 222 is V2, a diameter of a sound attenuation hole 230 in the second region 222 is D2, and a quantity of sound attenuation holes 230 corresponding to each sound attenuation cavity 220 in the second region 222 is N2, where 10 mm³≤V2≤80 mm³, 0.6 mm≤D2≤2 mm, 76≤N2≤120. For example, V1=50 mm³, D1=1.2 mm, N1=99. The second region 222 in this form may better absorb noise at a frequency ranging from about 600 Hz to 800 Hz.

The noise reduction device according to the embodiments of the present disclosure may also be used in combination with other sound insulation components. The embodiments of the present disclosure are specifically described below from two different structural forms.

First, combined with a multi-layer plate, noise in an air inlet channel is absorbed,

As shown in FIG. 4, the noise reduction device may further include a first cover plate 310 and a second cover plate 320. When the working noise of the gas water heater is transmitted forwards, the noise needs to at least penetrate the second cover plate 320 and the first cover plate 310. The second cover plate 320 and the first cover plate 310 may reflect most of the working noise directly transmitted outwards. The second cover plate 320 and the first cover plate 310 may block a direct transmission path of the noise.

The air inlet channel is formed between the first cover plate 310 and the second cover plate 320. The base 210 is mounted into the air inlet channel. The air inlet channel is located between the first cover plate 310 and the second cover plate 320.

As shown in FIG. 4, the first cover plate 310 is provided with a first flow inlet 311. The first flow inlet 311 is in communication with the air inlet channel, and may be a through hole formed at the first cover plate 310. The through hole passes through the first cover plate 310.

As shown in FIG. 4, the first flow inlet 311 may include a plurality of through holes formed at the first cover plate 310. The through hole may have a variety of shapes, including but not limited to shapes of parallelogram, triangle, circle, and other polygons.

The plurality of through holes of the first flow inlet 311 may be symmetrically arranged along a central axis of the air inlet channel. In this way, air inlet is balanced. A smoothness degree of an airflow in the air inlet channel can be improved. For example, in an embodiment shown in FIG. 3, the first flow inlet 311 includes a triangular through hole located at a center of the first flow inlet 311 and a plurality of parallelogram through holes arranged in mirror images at two sides of the triangular through hole.

The second cover plate 320 is provided with a second flow inlet 321. The second flow inlet 321 is in communication with the air inlet channel and an air inlet of the burner 140. As shown in FIG. 3 and FIG. 4, the second flow inlet 321 is at a position where the second cover plate 320 faces away from the first flow inlet 311. For example, in response to the first flow inlet 311 being located at a lower part of the first cover plate 310, the second flow inlet 321 is located at an upper part of the second cover plate 320. In response to the first flow inlet 311 being located at an upper part of the first cover plate 310, the second flow inlet 321 is located at a lower part of the second cover plate 320. In this way, a length of the air inlet channel is long enough.

The first cover plate 310 and the second cover plate 320 may be a sheet metal structure. In this way, the cover plate assembly has strong fire resistance performance and protection performance.

A main function of the air inlet channel is to introduce an outside air into the burner 140, but the working noise of the gas water heater is also propagated outwards through the air inlet channel. The gas water heater according to the embodiments of the present disclosure may greatly increase a path length of outward propagation of the noise along the air inlet channel through a design of at least double cover plates, with an increase greater than 500%. A transmission loss of the outward propagation of the noise is effectively improved.

In the related art, some structures have also been designed to extend the air inlet channel, but each of them is a pipe-type structure. On the one hand, due to a limitation of a volume of the whole gas water heater, a length increase is limited. On the other hand, a prolonged air inlet channel has a small flow cross-sectional area, which generates air inlet noise instead.

The noise reduction device for the gas water heater according to the embodiments of the present disclosure, through the design of at least double cover plate, the air inlet channel is formed between the cover plates and has a same width as the whole machine, which can increase the flow cross-sectional area of the air inlet channel. Moreover, the air inlet channel is linear, with a small flow channel resistance and a small difference in cross-sectional areas. Flow of a flow field in the flow channel is uniform. An air-inlet flow velocity gradient is small. Turbulent noise generated is small. In this way, the air inlet noise may be basically eliminated. Moreover, an air inlet pressure basically has no loss, which does not influence burning efficiency of the burner 140.

In addition, in the related art, each of air inlet holes is each provided at a back part of the whole machine. After the whole machine is mounted at a wall, a distance between the air inlet hole and the wall is small, and generally ranges from 10 mm to 20 mm only, with a large flow channel resistance.

In the noise reduction device for the gas water heater according to the embodiments of the present disclosure, the first flow inlet 311 is formed at a front part of the whole machine. The air inlet is not blocked by an external structure. In this way, the air inlet resistance of the air inlet channel can be greatly reduced. An overall flow channel resistance is reduced by 70% through experimental calculation.

With the noise reduction device for the gas water heater according to the embodiments of the present disclosure, by providing a structure of multi-layer front cover plates 420, each layer of cover plate has a weaken effect on internal noise, which enhances a sound insulation effect. Moreover, a cavity between the cover plates is utilized to form a long and wide air inlet channel, which can greatly increase the path length of the outward propagation of the noise along the air inlet channel, and effectively improve the transmission loss of the outward propagation of the noise. The air inlet noise may be basically eliminated, and the flow channel resistance is greatly reduced.

In some embodiments, as shown in FIG. 3 and FIG. 4, the second flow inlet 321 may include a first through hole group 322 and a second through hole group 323. The first through hole group 322 is disposed at a position close to a primary air inlet of the burner 140, and the second through hole group 323 is disposed at a position adjacent to a secondary air inlet of the burner 140.

It can be understood that the burner 140 includes a primary air inlet and a secondary air inlet. The primary air inlet is in communication with a fuel-gas air inlet channel of the burner 140. An air is sucked by a negative pressure generated by a fuel gas passing at a high speed. The secondary air inlet directly introduces the air. By independently designing the first through hole group 322 and the second through hole group 323, which are used for air inlet, for the primary air inlet and the secondary air inlet, a flow quantity proportion of primary air inlet and a flow quantity proportion of secondary air inlet may be improved, which helps the burner 140 to obtain a better burning effect, and lowers a content of harmful gases such as CO in a smoke gas.

For example, in the embodiment shown in FIG. 3, the primary air inlet of the burner 140 is at a right side of the burner 140, and the secondary air inlet of the burner 140 is at a bottom of the burner 140. Correspondingly, the first through hole group 322 and the second through hole group 323 as shown in FIG. 3 are designed. The first through hole group 322 is at a right side, and the second through hole group is at a left side. Moreover, the first through hole group is longer in length and extends more upwards, to adapt to the primary air inlet.

Through holes in the first through hole group 322 and the second through hole group 323 may have various shapes. For example, in embodiments shown in FIG. 3 and FIG. 4, each of the first through hole group 322 and the second through hole group 323 may include a plurality of long-strip-shaped through holes, and each through hole in the first through hole group 322 has a length longer than each through hole in the second through hole group 323. Alternatively, each of the first through hole group 322 and the second through hole group 323 may include a plurality of circular through holes, and each through hole in the first through hole group 322 has a radius greater than each through hole in the second through hole group 323.

In other embodiments of the present disclosure, the first through hole group 322 and the second through hole group 323 may also be designed in other shapes, such as in a shape of a polygon or the like.

In some embodiments, a flow cross-sectional area of the first through hole group 322 is A1, and a flow cross-sectional area of the second through hole group 323 is A2, where 1≤A1/A2≤2. By designing the flow cross-sectional area of the first through hole group 322 to be larger, a proportion of primary air inlet may be increased, which is helpful in a reduction in emission of harmful gases such as CO and NO. During actual design, a value of A1/A2 may be adjusted according to a specific burning situation. For example, A1/A2=1.5, or A1/A2=1.8, and the like.

Second, combined with a single-layer plate, the noise propagating outwards is directly absorbed.

As shown in FIG. 6, the noise reduction device may further include a front cover plate 420. The base 210 is mounted at an inner side of the front cover plate 420, and the surface is a surface facing away from the front cover plate 420

The front cover plate 420 is mounted at a front surface of the gas water heater, and is used for reflecting noise propagating forwards.

The front cover plate 420 may be a housing structure. In some embodiments, the front cover plate 420 may be a one-piece structure, to reduce a pore of the front cover plate 420 as much as possible, or the front cover plate 420 may be a one-piece non-porous structure. In this way, radiated noise at a front part of the gas water heater can be reduced.

As shown in FIG. 7, the front cover plate 420 includes a panel 421, and a left side plate 422 and a right side plate 423 that are connected to the panel 421. The panel 421, the left side plate 422, and the right side plate 423 are formed as a one-piece structure. In this way, there is no pore between the plates, which can reduce noise transmitted backwards.

A rear cover plate and the front cover plate 420 may be a sheet metal structure. In this way, each of the rear cover plate and the front cover plate 420 has strong fire resistance performance and protection performance. Alternatively, each of the rear cover plate and the front cover plate 420 may be a plastic housing structure. In this way, each of the rear cover plate and the front cover plate 420 is light in weight and easy to mold. A flame retardant may also be added to the plastic rear cover plate and the plastic front cover plate 420 to enhance the fire resistance performance.

The present disclosure also provides a gas water heater.

As shown in FIG. 3 and FIG. 6, the gas water heater according to the embodiments of the present disclosure includes a bottom housing 100, a burner 140, a heat exchanger 150, a fan system 160, and the noise reduction device according to any one of the above embodiments. The noise reduction device is at least located at a front side of the heat exchanger 150 and a front side of the fan system 160. The noise reduction device is used to absorb the working noise propagating forwards.

The bottom housing 100 is used for supporting main functional devices of the gas water heater, and the main functional devices of the gas water heater may be mounted at the bottom housing 100.

The bottom housing 100 has an opening, and the main functional devices of the gas water heater may be mounted at the bottom housing 100 from the opening.

The bottom housing 100 may be a housing structure. In some embodiments, the bottom housing 100 may be a one-piece structure, to reduce a pore between the bottom housing 100 and a rear mounting wall, or the bottom housing 100 may be a one-piece non-porous structure. In this way, radiation noise at the back part of the gas water heater can be reduced, and a reflection of back noise at the mounting wall can be weakened.

As shown in FIG. 3, FIG. 9, and FIG. 10, the bottom housing 100 may include a back plate and a side plate. The back plate is located at a rear end of the bottom housing 100. The opening is located at a front end of the bottom housing 100. A side wall is connected to the back plate. Moreover, the side walls may include four plates, i.e., an upper plate, a lower plate, a left plate, and a right plate. The back plate and the side wall may be an integrated structure. In this way, there is no pore between the plates, which can reduce the noise transmitted backwards.

As shown in FIG. 5, the bottom housing 100 may include a back plate, a top plate, and a bottom plate. The back plate is located at the rear end of the bottom housing 100. The top plate is connected to an upper end of the back plate, and is bent forwards. The bottom plate is connected to a lower end of the back plate, and is bent forwards. The back plate, the top plate, and the bottom plate may be an integrated structure. In this way, there is no pore between the plates, which can reduce the noise transmitted backwards.

The bottom housing 100 may be a metal housing structure. In this way, the bottom housing 100 has a large strength and good fire resistance performance. Alternatively, the bottom housing 100 may have a plastic housing structure. In this way, the bottom housing 100 is light in weight and easy to form. The flame retardant may also be added to the plastic bottom housing 100 to enhance the fire resistance performance.

The burner 140, the heat exchanger 150, and the fan system 160 are mounted to the bottom housing 100. The burner 140, the heat exchanger 150, and the fan system 160 may be mounted to the bottom housing 100 through a screw connection structure, a snap structure, or other structures.

The heat exchanger 150 may be in communication with the burning chamber of the burner 140. An oxidizing agent (air) enters the burner 140 through the air inlet of the burner 140, and is mixed with the fuel gas and burned in the burning chamber. Heat exchange is performed on water to be heated and a high-temperature air at the heat exchanger 150. The heat exchanger 150 may be located at the upper end of the burner 140.

The noise reduction device for the gas water heater according to the embodiment of the present disclosure can achieve a plurality of times of reflections of noise through a structure of the sound attenuation cavities with the sound attenuation holes, thereby consuming energy of noise and reducing the influence on a user.

In some embodiments, as shown in FIG. 3, FIG. 9, and FIG. 10, a sealing gasket 171 is sandwiched between the cover plate assembly and the bottom housing 100. The sealing gasket 171 may block a gap between the bottom housing 100 and the first cover plate 310, and isolate a path of directly outward propagation of noise there. The sealing gasket 171 may have a shape similar to an outer periphery of the bottom housing 100, such as have a square annular shape. The sealing gasket 171 may be sealing cotton.

In some embodiments, as shown in FIG. 3, FIG. 9, and FIG. 10, the gas water heater may further include a sealing ring 172. A smoke pipe 161 of the fan system 160 penetrates a top plate of the bottom housing 100. The sealing ring 172 is sleeved outside the smoke pipe 161, and is clamped between the smoke pipe 161 and the top plate of the bottom housing 100. In this way, a gap between the smoke pipe 161 and the bottom housing 100 can be blocked, and the path of the directly outward propagation of noise there can be isolated.

The sealing ring 172 may include two sub-sections with different outer diameters. In this way, a stepped surface is formed at an exterior of the sealing ring 172. During mounting, a sub-section with a shorter outer diameter is extended into a through hole of the bottom housing 100. The stepped surface abuts against the top plate of the bottom housing 100. In this way, a sealing structure having a plurality of surfaces combined with each other can be formed, with a better sound insulation effect.

The sealing ring 172 may be made of silica gel. The sealing ring 172 made of silica gel is heat resisting. In this way, an aging time of the sealing ring 172 in a high temperature environment of the smoke pipe 161 can be prolonged.

As shown in FIG. 9 and FIG. 10, the gas water heater according to the embodiments of the present disclosure includes a bottom housing 100, a burner 140, and a cover plate assembly.

As shown in FIG. 9, the gas water heater may further include a heat exchanger 150.

The gas water heater may be a natural air inlet type or a forcible exhaust type. A forcible-exhaust-type gas water heater may further include a fan system 160. As shown in FIG. 9, the fan system 160 may be mounted at an upper end of the heat exchanger 150.

The cover plate assembly is mounted at the bottom housing 100. Moreover, the cover plate assembly covers the opening, and may be located at the front end of the bottom housing 100.

As shown in FIG. 9 to FIG. 14, the cover plate assembly includes a first cover plate 310 and a second cover plate 320. That is, a front end of the gas water heater is at least a double-layer cover plate structure.

The second cover plate 320 is located between the burner 140 and the first cover plate 310. The bottom housing 100, the second cover plate 320, and the first cover plate 310 are arranged sequentially from rear to front.

In this way, when the working noise of the gas water heater is transmitted forwards, the noise needs to at least penetrate the second cover plate 320 and the first cover plate 310. The second cover plate 320 and the first cover plate 310 may reflect most of the working noise directly transmitted outwards. The second cover plate 320 and the first cover plate 310 may block the direct transmission path of the noise.

As shown in FIG. 11, the cover plate assembly has an air inlet channel 330. The air inlet channel 330 is located between the first cover plate 310 and the second cover plate 320. The air inlet channel 330 is formed between the first cover plate 310 and the second cover plate 320.

As shown in FIG. 9, FIG. 11, and FIG. 12, the first cover plate 310 is provided with a first flow inlet 311. The first flow inlet 311 is in communication with the air inlet channel 330, and may be the through hole formed at the first cover plate 310. The through hole passes through the first cover plate 310.

As shown in FIG. 9 and FIG. 12, the first flow inlet 311 may include a plurality of through holes formed at the first cover plate 310. The through hole may have a variety of shapes, including but not limited to shapes of parallelogram, triangle, circle, and other polygons.

The plurality of through holes of the first flow inlet 311 may be symmetrically arranged along the central axis of the air inlet channel 330. In this way, the air inlet is balanced. The smoothness degree of the airflow in the air inlet channel 330 can be improved. For example, in the embodiments shown in FIG. 9 and FIG. 12, the first flow inlet 311 includes a triangular through hole located at the center of the first flow inlet 311 and a plurality of parallelogram through holes arranged in mirror images at the two sides of the triangular through hole.

The second cover plate 320 is provided with a second flow inlet 321, and the second flow inlet 321 is in communication with the air inlet channel 330 and an air inlet of the burner 140. As shown in FIG. 9 and FIG. 11, the second flow inlet 321 is at a position where the second cover plate 320 faces away from the first flow inlet 311. For example, in response to the first flow inlet 311 being located at the lower part of the first cover plate 310, the second flow inlet 321 is disposed at the upper part of the second cover plate 320. In response to the first flow inlet 311 being located at the upper part of the first cover plate 310, the second flow inlet 321 is disposed at the lower part of the second cover plate 320. In this way, the length of the air inlet channel 330 is long enough.

The main function of the air inlet channel 330 is to introduce the outside air into the burner 140, but the working noise of the gas water heater is also propagated outwards through the air inlet channel 330. The gas water heater according to the embodiments of the present disclosure may greatly increase the path length of the outward propagation of the noise along the air inlet channel 330 through the design of at least double cover plates, with the increase greater than 500%, effectively improving the transmission loss of the outward propagation of the noise.

In the related art, some structures have also been designed to extend the air inlet channel, but each of them is a pipe-type structure. On the one hand, due to the limitation of the volume of the whole gas water heater, the length increase is limited. On the other hand, the prolonged air inlet channel has a small flow cross-sectional area, which generates the air inlet noise instead.

The gas water heater according to the embodiments of the present disclosure, through the design of at least double cover plate, the air inlet channel 330 is formed between the cover plates, and has the same width as the whole machine, which can increase the flow cross-sectional area of the air inlet channel 330. Moreover, the air inlet channel 330 is linear, with a small flow channel resistance and a small difference in cross-sectional areas. The flow of the flow field in the flow channel is uniform. The air-inlet flow velocity gradient is small. The turbulent noise generated is small. In this way, the air inlet noise may be basically eliminated. Moreover, the air inlet pressure basically has no loss, which does not influence the burning efficiency of the burner 140.

In addition, in the related art, each of the air inlet holes is provided at the back part of the whole machine. After the whole machine is mounted at the wall, the distance between the air inlet hole and the wall is small, and generally ranges from 10 mm to 20 mm only, with a large flow channel resistance.

In the noise reduction device for the gas water heater according to the embodiments of the present disclosure, the first flow inlet 311 is provided at the front part of the whole machine. The air inlet is not blocked by the external structure. In this way, the air inlet resistance of the air inlet channel 330 may be greatly reduced. The overall flow channel resistance is reduced by 70% through experimental calculation.

With the noise reduction device for the gas water heater according to the embodiments of the present disclosure, by providing the structure of multi-layer cover plates, each layer of cover plate has the weaken effect on the internal noise, which enhances the sound insulation effect. Moreover, the cavity between the cover plates is utilized to form a long and wide air inlet channel 330, which can greatly increase the path length of the outward propagation of the noise along the air inlet channel 330, and effectively improve the transmission loss of the outward propagation of the noise. The air inlet noise may be basically eliminated, and the flow channel resistance is greatly reduced.

In some embodiments, as shown in FIG. 9, the burner 140 is mounted in a lower region of the bottom housing 100, the first flow inlet 311 is located in an upper region of the first cover plate 310, and the second flow inlet 321 is located in a lower region of the second cover plate 320.

In this way, the length of the air inlet channel 330 is basically same as a height of the whole machine, which can greatly increase the path length of the noise propagating outwards along the air inlet channel 330. Moreover, an external first flow inlet 311 is located at a top end. When the whole machine is mounted at the wall, the first flow inlet 331 is basically located in a region close to a roof in the room, which brings no wind feeling to the user, with a better use experience.

In some embodiments, a flow cross-sectional area of the first flow inlet 311 is P1, and a flow cross-sectional area of the second flow inlet 321 is P2, where 1.5≤P2/P1≤3.

It can be understood that by designing a second flow inlet 321 located inside to have a flow cross-sectional area greater than a first flow inlet 311 located outside, a flow channel resistance caused by the air inlet channel 330 may be eliminated, turbulent noise in the air inlet channel 330 may be further reduced, and generation of sound whistling at the second flow inlet 321 is prevented. For example, in some embodiments, P2/P1=2, or P2/P1=2.5.

In the actual design, the flow cross-sectional area of the first flow inlet 311 may be adjusted according to a maximum load of the gas water heater. The larger the maximum load of the gas water heater, the larger the flow cross-sectional area of the first flow inlet 311, to ensure that the fuel gas in the burner 140 may be fully burned. The maximum load of the gas water heater may be 25 kW, 30 kW, 34 kW, and the like. The flow cross-sectional area P1 of the first flow inlet 311 may range from 2000 mm²to 3500 mm². For example, P1=2500 mm².

In some embodiments, as shown in FIG. 10 and FIG. 13, the second flow inlet 321 may include a first through hole group 322 and a second through hole group 323. The first through hole group 322 is disposed at the position close to the primary air inlet of the burner 140, and the second through hole group 323 is disposed at the position close to the secondary air inlet of the burner 140.

It can be understood that the burner 140 includes a primary air inlet and a secondary air inlet. The primary air inlet is in communication with the fuel-gas air inlet channel of the burner 140. The air is sucked by the negative pressure generated by the fuel gas passing at a high speed. The secondary air inlet directly introduces the air. By independently designing the first through hole group 322 and the second through hole group 323, which are used for air inlet, for the primary air inlet and the secondary air inlet, the flow quantity proportion of primary air inlet and the flow quantity proportion of secondary air inlet may be improved, which helps the burner 140 to obtain a better burning effect, and lowers the content of harmful gases such as CO in the smoke gas.

For example, in embodiments shown in FIG. 9 and FIG. 10, the burner 140 has a primary air inlet at the right side of the burner 140 and a secondary air inlet at a bottom of the burner 140. Correspondingly, the first through hole group 322 and the second through hole group 323 as shown in FIG. 10 are designed. The first through hole group 322 is at the right side, and the second through hole group is at the left side. Moreover, the first through hole group has a longer length and extends more upwards, to adapt to the primary air inlet.

The through holes in the first through hole group 322 and the second through hole group 323 may have various shapes. For example, in an embodiment shown in FIG. 10, each of the first through hole group 322 and the second through hole group 323 may include a plurality of long-strip-shaped through holes, and each through hole in the first through hole group 322 has a length longer than each through hole in the second through hole group 323. Alternatively, in an embodiment shown in FIG. 13, each of the first through hole group 322 and the second through hole group 323 may include a plurality of circular through holes, and each through hole in the first through hole group 322 has a radius greater than each through hole in the second through hole group 323.

In some embodiments, a flow cross-sectional area of the first through hole group 322 is A1, and a flow cross-sectional area of the second through hole group 323 is A2, where 1≤A1/A2≤2. By designing the flow cross-sectional area of the first through hole group 322 to be larger, the proportion of primary air inlet may be increased, which is helpful to the reduction in the emission of harmful gases such as CO and NO. During actual design, the value of A1/A2 may be adjusted according to the specific burning situation. For example, A1/A2=1.5, or A1/A2=1.8, and the like.

In some embodiments, as shown in FIG. 11, the first cover plate 310 is provided with a side wall plate 312 facing towards the bottom housing 100. The side wall plate 312 has a flange 313 bent inwards, and the second cover plate 320 is mounted at a side of the flange 313 facing away from the bottom housing 100.

In this embodiment, the second cover plate 320 may be mounted in the first cover plate 310, and the second cover plate 320 is located at a front side of the flange 313. In this way, the integrally-formed cover plate assembly is easier to mount, and only the first cover plate 310 needs to be mounted at the bottom housing 100. For example, the flange 313 of the first cover plate 310 is assembled with the bottom housing 100 through a snap structure or threaded connection structure.

Alternatively, a sealing structure may also be mounted at a connection of the flange 313 of the first cover plate 310 and the bottom housing 100, to prevent the noise from propagating from a gap between the bottom housing 100 and the cover plate assembly.

In other embodiments of the present disclosure, the second cover plate 320 may also be designed outside the first cover plate 310. As shown in FIG. 12 and FIG. 13, the second cover plate 320 is mounted at a rear side of the first cover plate 310. During assembly, the second cover plate 320 needs to be connected to the bottom housing 100. For example, the second cover plate 320 is connected to the bottom housing 100 through a snap structure or threaded connection structure.

Alternatively, the second cover plate 320 is located at the rear side of the first cover plate 310, and the sealing structure may also be mounted at a connection between the second cover plate 320 and the bottom housing 100, to prevent the noise from propagating from the gap between the bottom housing 100 and the cover plate assembly. The sealing gasket 171 is sandwiched between the cover plate assembly and the bottom housing 100. The sealing gasket 171 may block a gap between the bottom housing 100 and the second cover plate 320, and isolate a path of directly outward propagation of noise there. The sealing gasket 171 may have a shape similar to the outer periphery of the bottom housing 100, such as a square annular shape. The sealing gasket 171 may be the sealing cotton.

The gas water heater according to the embodiments of the present disclosure may also further include other sound attenuation components 200. The sound attenuation components 200 may be mounted in the air inlet channel 330. As shown in FIG. 9, FIG. 10, and FIG. 14, a sound attenuation component 200 is disposed in the air inlet channel 330. The sound attenuation component 200 is mounted at the second cover plate 320 and/or the first cover plate 310. A thickness of the sound attenuation component 200 in the front-rear direction is smaller than a thickness of the air inlet channel 330 in the front-rear direction. In this way, a sufficient channel for flowing of air inlet can be left.

The first cover plate 310 and the second cover plate 320 themselves may reflect most of the working noise directly transmitted outwards. Combined with the sound attenuation component 200 arranged in the air inlet channel 330, a part of the noise is reflected by the second cover plate 320, most of the noise penetrating the second cover plate 320 is absorbed by the sound attenuation component 200, and the rest of a small amount of noise is reflected by the first cover plate 310 again. In this way, the sound attenuation effect is better.

The sound attenuation component 200 may be mounted at the second cover plate 320 or the first cover plate 310 in a variety of manners, including manners of sticking, a snap connection, a screw connection, and the like.

The sound attenuation component 200 may have a plurality of structural forms. The embodiments of the present disclosure are specifically described below from four different structural forms.

First, the sound attenuation component 200 is sound absorption cotton.

In this implementation, the sound absorption cotton is provided in the air inlet channel 330, and may be adhered to the first cover plate 310 or the second cover plate 320. Moreover, a thickness of the sound absorption cotton in the front-rear direction may be smaller than a width of the air inlet channel 330 in the front-rear direction. In this way, a sufficiently large air inlet channel can be left, to reduce the air inlet resistance.

The sound absorption cotton may include a plurality of regions with different parameters. These regions are distributed in a direction perpendicular to the front-rear direction. The parameter includes at least one of a volume-weight or a thickness. In this way, different regions have different sound absorption effects. Parameters of the sound absorption cotton in different regions may be designed according to different noise characteristics of various parts of the gas water heater.

The sound attenuation component 200 includes a plurality of regions. The plurality of regions corresponds to different positions of the bottom housing 100 in the front-rear direction, respectively. A sound attenuation parameter in one of at least two regions of the plurality of regions of the sound attenuation component 200 is different from a sound attenuation parameter in another one of the at least two regions.

Through research, the inventor finds that noise sources of normal operation of the gas water heaters include burning noise, fan noise, gas injection noise, mechanical vibration noise, and water flow noise. The burning noise has obvious low-frequency characteristics and strong penetrability. The noise of the fan and water pump has obvious high-frequency characteristics, is sharp and harsh, and has a poor auditory experience.

By providing a plurality of regions with different sound attenuation parameters, various noises may be eliminated in a targeted manner.

For example, the sound absorption cotton may include a first region and a second region. The first region faces towards the burner 140 and the heat exchanger 150. In some embodiments, the first region faces towards the burning chamber of the burner 140 and the heat exchanger 150. The second region faces towards the fan system 160, at which A facing towards B means that the projections of A and B in the front-rear direction substantially coincide with each other.

A volume-weight of the first region is greater than a volume-weight of the second region, or a thickness of the first region is greater than a thickness of the second region.

Second, the sound attenuation component 200 is a structure of sound attenuation cavities with sound attenuation holes.

In this implementation, the sound attenuation component 200 has sound attenuation cavities 220. The sound attenuation cavity 220 has a sound attenuation hole 230 at a wall surface of the sound attenuation cavity 220 facing towards the bottom housing 100.

As shown in FIG. 14 to FIG. 16, the sound attenuation component 200 includes a base 210.

A surface (rear surface) of the base 210 facing towards the bottom housing 100 has sound attenuation holes 230, and the sound attenuation holes 230 is in communication with the sound attenuation cavities 220.

When the gas water heater is working, a part of the noise is reflected by the second cover plate 320. Most of the noise penetrating the second cover plate 320 is propagated to the sound attenuation cavities 220 through the sound attenuation holes 230 and may be absorbed through the plurality of times of reflections in the sound attenuation cavities 220. A very small amount of noise is reflected by the first cover plate 310. In this way, the overall sound attenuation effect is better.

As shown in FIG. 16, the sound attenuation component 200 has a plurality of sound attenuation cavities 220. The plurality of sound attenuation cavities 220 are arranged in an array. Each sound attenuation cavity 220 has a plurality of sound attenuation holes 230 arranged in an array.

In this way, the noise of each region can be absorbed through the sound attenuation holes 230 and the sound attenuation cavities 220.

In some embodiments, the volume of the one of the at least two sound attenuation cavities 220 is different from the volume of the other one of the at least two sound attenuation cavities 220; and/or the flow cross-sectional area of the sound attenuation hole 230 corresponding to the one of the at least two sound attenuation cavities 220 is different from the flow cross-sectional area of the sound attenuation hole 230 corresponding to the other one of the at least two sound attenuation cavities 220; and/or the density of the sound attenuation holes 230 corresponding to the one of the at least two sound attenuation cavities 220 is different from the density of the sound attenuation holes 230 corresponding to the other one of the at least two sound attenuation cavities 220.

In other words, there is a difference in the at least one of the three parameters, that is, the volume of the sound attenuation cavity 220, the flow cross-sectional area of the sound attenuation hole 230, and the density of the sound attenuation holes 230 corresponding to the sound attenuation cavity 220, between the at least two sound attenuation cavities 220. In this way, the sound generated by the gas water heater may be attenuated according to different frequency characteristics of the burning noise, water flow noise, and flow-induced noise of the gas water heater.

In some embodiments, as shown in FIG. 16 and FIG. 17, the volume of the sound attenuation cavity 220 facing towards the burner 140 and the heat exchanger 150 is greater than the volume of the sound attenuation cavity 220 facing towards the fan system 160.

Through research, the inventor finds that the noise sources of the normal operation of the gas water heater include burning noise, fan noise, gas injection noise, mechanical vibration noise, and water flow noise. The burning noise has obvious low-frequency characteristics and strong penetrability. The noise of the fan and water pump has obvious high-frequency characteristics, is sharp and harsh, and has a poor auditory experience.

By designing the volume of the sound attenuation cavity 220 facing towards the burner 140 and the heat exchanger 150 to be larger, the low-frequency noise may be better absorbed.

In some embodiments, the quantity of the sound attenuation holes 230 corresponding to the sound attenuation cavity 220 facing towards the burner 140 and the heat exchanger 150 is smaller than the quantity of the sound attenuation holes 230 corresponding to the sound attenuation cavity 220 facing towards the fan system 160. By designing a larger quantity of the sound attenuation holes 230 corresponding to the sound attenuation cavity 220 facing towards the fan system 160, the high-frequency noise may be better absorbed.

In one embodiment, as shown in FIG. 17, the base 210 may include a first region 221 and a second region 222. The first region 221 faces towards the burner 140 and the heat exchanger 150. In some embodiments, the first region 221 faces towards the burning chamber of the burner 140 and the heat exchanger 150. The second region 222 faces towards the fan system 160, at which A facing towards B means that the projections of A and B in the front-rear direction substantially coincide with each other.

A volume of a sound attenuation cavity 220 in the second region 222 is V2, a diameter of a sound attenuation hole 230 in the second region 222 is D2, and a quantity of sound attenuation holes 230 corresponding to each sound attenuation cavity 220 in the second region 222 is N2, where 10 mm³≤V2≤80 mm³, 0.6 mm≤D2≤2 mm, 76≤N2≤120. For example, V1=50 mm³, D1=1.2 mm, N1=99. The second region 222 in this form may better absorb the noise at the frequency ranging from about 600 Hz to 800 Hz.

Third, the sound attenuation component 200 is a labyrinth-type silencer.

In this implementation, as shown in FIG. 18 to FIG. 21, the sound attenuation component 200 includes a plurality of baffles 240. An angle between a normal line of at least a part of each of the plurality of baffles 240 and an airflow direction in the air inlet channel 330 is smaller than 30°. The plurality of baffles 240 are arranged at intervals for air flowing.

In other words, the baffle 240 substantially faces towards a direction of a connection line of the second flow inlet 321 and the first flow inlet 311. In this way, when the noise is transmitted from the second flow inlet 321 to the first flow inlet 311, the noise can be reflected by the baffle 240.

The labyrinth-type silencer may reflect the noise multiple times in a labyrinth-type flow channel, which consumes the energy of the noise, achieves a purpose of reducing the noise, and can greatly weaken the noise propagated outwards through the air inlet channel 330.

As shown in FIG. 18 to FIG. 20, the baffle 240 is in an arc shape and is bent away from the first flow inlet 311. In this way, the noise reflected by the baffle 240 basically faces towards the second flow inlet 321. Moreover, the baffle 240 has a small resistance for air inlet from the first flow inlet 311 to the second flow inlet 321.

As shown in FIG. 18 to FIG. 20, quantity and distribution of baffles 240 may have a variety of forms. As shown in FIG. 18, the baffles 240 have a short length, a large quantity, and are symmetrically arranged at left and right sides. As shown in FIG. 19, the baffles 240 have a long length, a small quantity, and are symmetrically arranged at the left and right sides. As shown in FIG. 20, the baffles 240 have a long length, a small quantity, and are arranged asymmetrically.

In other embodiments of the present disclosure, the baffle 240 may be in a flat plate shape. As shown in FIG. 21, the baffle 240 is in a flat plate shape, and the plurality of baffles 240 are arranged at intervals for air flowing.

The flat-plate-shaped baffle 240 and the arc-shaped baffle 240 may be mixed for use.

In the embodiments shown in FIG. 18 to FIG. 21, the sound attenuation component 200 includes a support plate 250. Each of the baffles 240 is mounted at the support plate 250. The support plate 250 is re-connected to the cover plate assembly. For example, the support plate 250 may be adhered to an inner side surface of the first cover plate 310.

Fourth, the sound attenuation component 200 is a combination of the above-described structures.

For example, the sound attenuation component 200 is a combination of the sound absorption cotton and the structure of the sound attenuation cavities with the sound attenuation holes. The sound absorption cotton is used in a region facing towards the fan system 160. In this way, noise in a medium-high frequency band ranging from 600 Hz to 1000 Hz can be better absorbed. The structure of the sound attenuation cavities with the sound attenuation holes is used in the region facing towards the burner 140 and the heat exchanger 150. Therefore, noise in a low-frequency band of 300 Hz can be better absorbed.

Other combination forms are not introduced in detail here.

Finally, it should be noted that each of the above embodiments is used only to illustrate, rather than to limit, the technical solutions of the present disclosure. Although the present disclosure has been described in detail with reference to the foregoing embodiments, it is conceivable for those skilled in the art that modifications can be made to the technical solutions described in the foregoing embodiments, or equivalent replacements can be made to some or all of the technical features in the technical solutions described in the foregoing embodiments. These modifications or equivalent replacements do not depart the essence of corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present disclosure.

The above implementations are only used to illustrate the present disclosure, but are not used to limit the present disclosure. Although the present disclosure has been described in detail with reference to the embodiments, those skilled in the art should understand that various combinations, modifications, or equivalent substitutions of the technical solutions of the present disclosure do not depart from the spirit and scope of the technical solutions of the present disclosure, and shall fall within the scope of the claims of the present disclosure.

Number	Date	Country	Kind
202210459498.2	Apr 2022	CN	national
202210459508.2	Apr 2022	CN	national
202221024859.2	Apr 2022	CN	national

	Number	Date	Country
Parent	PCT/CN2023/090549	Apr 2023	WO
Child	18913720		US

GAS WATER HEATER

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CPC

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Priority Claims (3)

CROSS-REFERENCE TO RELATED APPLICATIONS

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