CN215723879U - New fan - Google Patents

Abstract

The utility model relates to a new fan technical field, in particular to new fan. The new fan includes: a housing; the total heat exchanger is arranged in the shell, is communicated with the fresh air cavity and the air supply cavity in the shell and is communicated with the return air cavity and the exhaust air cavity in the shell; the first fan is arranged in the shell and drives fresh air to flow; the second fan is arranged in the shell and drives the exhaust air to flow; the heat exchanger is arranged in an air supply cavity in the shell; and the internal circulation air door is arranged between the air return cavity and the air supply cavity and used for controlling whether the air return cavity and the air supply cavity are communicated or not and controlling whether the return air entering the air return cavity flows to the air supply cavity or not through the internal circulation air door. Based on this, can effectively improve the temperature control performance of new fan.

Description

New fan

Technical Field

The utility model relates to a new fan technical field, in particular to new fan.

Background

The fresh air machine is an effective air purification device which discharges indoor dirty air to the outside on one hand and sends outdoor fresh air to the inside on the other hand, so that the indoor air can be kept clean and healthy.

However, in the related art, the temperature control performance of the fresh air blower is poor, and the requirement of indoor temperature is difficult to accurately meet.

Disclosure of Invention

One technical problem to be solved by the present disclosure is: the temperature control performance of the fresh air machine is improved.

In order to solve the above technical problem, the first aspect of the present disclosure provides a new fan, which includes:

the air conditioner comprises a shell, a fan cover and a fan cover, wherein the fan cover, the fan cover and the fan cover are arranged on the shell;

the total heat exchanger is arranged in the shell, is communicated with the fresh air cavity and the air supply cavity and is communicated with the return air cavity and the exhaust air cavity;

the first fan is arranged in the shell and drives fresh air to flow;

the second fan is arranged in the shell and drives the exhaust air to flow;

the heat exchanger is arranged in the air supply cavity; and

the internal circulation air door sets up between return air chamber and supply-air chamber for whether the control return air chamber communicates with the supply-air chamber, whether the return air that gets into the return air chamber flows to the supply-air chamber via the internal circulation air door in order to control.

In some embodiments of the present invention, the,

a first driving cavity is arranged in the shell, a first fan is arranged in the first driving cavity, the first driving cavity is arranged between the internal circulation air door and the air supply cavity along the flowing direction of return air from the return air cavity to the air supply cavity, and the internal circulation air door controls whether the return air cavity is communicated with the air supply cavity by controlling whether the return air cavity is communicated with the first driving cavity; and/or the presence of a gas in the gas,

be equipped with the second drive chamber in the casing, the second fan sets up in the second drive intracavity, second drive chamber with exhaust between the chamber intercommunication to and return air chamber between be equipped with the bypass air door, the bypass air door is through controlling whether intercommunication in return air chamber and second drive chamber, whether control the return air directly follow the air exit and discharge not through total heat exchanger.

In some embodiments, the first fan and the second fan are stacked in a longitudinal direction and at least partially overlap in a first transverse direction, the first transverse direction being a direction in which the fresh air opening and the supply air opening are arranged side by side, the longitudinal direction being a direction perpendicular to the first transverse direction and the second transverse direction, and the second transverse direction being a direction in which the fresh air opening and the exhaust air opening are arranged side by side.

In some embodiments, a return air channel is provided in the housing, the return air channel communicates with the return air inlet through the return air chamber, the return air channel is arranged side by side in the longitudinal direction with the second fan and at least partially overlaps in the first transverse direction, and the return air channel is arranged side by side in the second transverse direction with the first fan.

In some embodiments, the total heat exchanger includes a first flow channel and a second flow channel arranged in a crossing manner, a first inlet and a first outlet of the first flow channel are respectively communicated with the fresh air cavity and the air supply cavity, a second inlet and a second outlet of the second flow channel are respectively communicated with the return air cavity and the air supply cavity, and in the longitudinal direction, the first inlet and the second inlet are located on one side where the first fan is located, and the first outlet and the second outlet are located on one side where the second fan is located.

In some embodiments, the first fan is arranged between the total heat exchanger and the air supply cavity along the flowing direction of fresh air from the fresh air cavity to the air supply cavity; and/or the second fan is arranged between the total heat exchanger and the air exhaust cavity along the flowing direction of the return air from the return air cavity to the air exhaust cavity.

In some embodiments, an exhaust passage is provided in the housing, the total heat exchanger is communicated with the second fan through the exhaust passage, the exhaust passage is located on one side of the total heat exchanger in the longitudinal direction, the longitudinal direction is a direction perpendicular to a first transverse direction and a second transverse direction, the first transverse direction is a direction in which the fresh air opening and the air supply opening are arranged side by side, and the second transverse direction is a direction in which the fresh air opening and the exhaust opening are arranged side by side.

In some embodiments, the first fan and the second fan are arranged side by side in the longitudinal direction, and in the longitudinal direction, the total heat exchanger is located on the side where the first fan is located, and the exhaust passage is located on the side where the second fan is located.

In some embodiments, the first fan and/or the second fan is a horizontal centrifugal fan.

In some embodiments, the fresh air machine comprises at least one of:

the fresh air door is arranged at the fresh air port to control the opening and closing of the fresh air port;

the air exhaust air door is arranged at the air exhaust port to control the opening and the closing of the air exhaust port;

the first filter screen is arranged on a flow path between the fresh air inlet and the total heat exchanger;

the second filter screen is arranged on a flow path between the air return opening and the total heat exchanger;

and the third filter screen is arranged on a flow path between the first fan and the heat exchanger.

Based on the embodiment of the disclosure, the new fan can realize an internal circulation mode and a wind mixing mode, and the indoor temperature is more effectively adjusted, so that the temperature control performance of the new fan can be effectively improved.

Other features of the present disclosure and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.

Drawings

In order to more clearly illustrate the embodiments of the present disclosure 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 introduced below, it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and for those skilled in the art, other drawings can be obtained according to the drawings without inventive exercise.

Fig. 1 is a schematic perspective view of a new fan in an embodiment of the present disclosure when a first end plate is removed.

Fig. 2 is a schematic top view of a new fan with a first end plate removed according to an embodiment of the disclosure.

Fig. 3 is a schematic bottom view of the new blower with the second end plate removed according to the embodiment of the disclosure.

Fig. 4 is a schematic perspective view of the fresh air machine in the embodiment of the disclosure when the second side plate is removed.

Fig. 5 is a schematic perspective view of the fresh air fan according to the embodiment of the disclosure when a portion of the first side plate is removed.

Fig. 6 is a schematic perspective view of the fresh air fan according to the embodiment of the disclosure when the whole first side plate is removed.

FIG. 7 is a schematic perspective view of an inner circulation damper in an embodiment of the present disclosure.

Fig. 8 is a schematic flow path diagram of fresh air and return air flowing through the total heat exchanger in an embodiment of the disclosure.

Fig. 9 is a schematic flow path diagram of fresh air in an embodiment of the disclosure.

Fig. 10 is a schematic view of a first portion of the flow path of return air flowing to the exhaust outlet in an embodiment of the disclosure.

Fig. 11 is a schematic view of a second portion of the flow path of return air flowing to the exhaust outlet in an embodiment of the disclosure.

Fig. 12 is a schematic perspective view illustrating the return air flowing to the air outlet according to the embodiment of the present disclosure.

Fig. 13 is a schematic flow path diagram of the new fan in the full heat exchange mode in the embodiment of the present disclosure.

Fig. 14 is a schematic flow path diagram of the new blower in the bypass mode in the embodiment of the disclosure.

Fig. 15 is a schematic flow path diagram of the new fan in the internal circulation mode according to the embodiment of the disclosure.

Fig. 16 is a schematic flow path diagram of the fresh air fan in the air mixing mode in the embodiment of the present disclosure.

Fig. 17 shows a block diagram of a controller in an embodiment of the disclosure.

Description of reference numerals:

10. a fresh air machine;

1. a housing; 11. a fresh air port; 12. an air supply outlet; 13. an air return opening; 14. an air outlet; 15. a fresh air cavity; 16. an air supply cavity; 17. an air return cavity; 18. an exhaust chamber; 191. a first drive chamber; 192. a second drive chamber; 193. a fresh air channel; 194. an air exhaust channel; 195. an air return channel; 1a, a first end plate; 1b, a second end plate; 1c, a first side plate; 1d, a second side plate; 1e, a third side plate; 1f, a fourth side plate;

2. a total heat exchanger; 21. a first inlet; 22. a first outlet; 23. a second inlet; 24. a second outlet; 25. a first flow passage; 26. a second flow passage;

31. a first fan; 32. a second fan;

4. a heat exchanger;

51. a fresh air door; 52. an air exhaust air door; 53. an internal circulation damper; 54. a bypass damper; 55. a frame; 56. a valve plate; 57. an opening;

61. a first filter screen; 62. a second filter screen; 63. a third filter screen;

71. a first access door; 72. a second access door;

8. a controller; 81. a memory; 82. a processor; 83. a communication interface; 84. a bus;

H. longitudinal direction; l, a first transverse direction; w, the second transverse direction.

Detailed Description

The technical solutions in the embodiments of the present disclosure will be clearly and completely described below with reference to the drawings in the embodiments of the present disclosure, and it is obvious that the described embodiments are only a part of the embodiments of the present disclosure, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the disclosure, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments disclosed herein without any inventive step, are intended to be within the scope of the present disclosure.

Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.

In the description of the present disclosure, it should be understood that the terms "first", "second", etc. are used to define the components, and are used only for convenience of distinguishing the corresponding components, and if not otherwise stated, the terms have no special meaning, and thus, should not be construed as limiting the scope of the present disclosure.

In addition, technical features involved in different embodiments of the present disclosure described below may be combined with each other as long as they do not conflict with each other.

Fig. 1-16 schematically illustrate the structure of the fresh air machine of the present disclosure.

For convenience of description, the orientation and positional relationship are first defined using the coordinate system in fig. 1. Wherein, the coordinate axis L represents a first transverse direction L, which may also be referred to as a first direction L, a first horizontal direction L, or a left-right direction L; the coordinate axis W represents a second lateral direction W, which is perpendicular to the first lateral direction L, and may also be referred to as a second direction W, a second horizontal direction L, or a front-rear direction W; the coordinate axis H represents a longitudinal direction H, which is perpendicular to both the first transverse direction L and the second transverse direction W, and may also be referred to as a third direction H or an up-down direction H.

Referring to fig. 1, the new blower 10 includes a casing 1, a first blower 31, a second blower 32, and a total heat exchanger 2.

The casing 1 provides a mounting base for other structural components of the fresh air fan 10, such as the total heat exchanger 2, the first fan 31, the second fan 32, and the like. Referring to fig. 1-5, a fresh air inlet 11, an air supply outlet 12, a return air inlet 13 and an air exhaust outlet 14 are arranged on the casing 1, and a fresh air cavity 15, an air supply cavity 16, a return air cavity 17 and an air exhaust cavity 18 which are separated from each other are arranged in the casing 1. The fresh air cavity 15 and the exhaust air cavity 18 are respectively communicated with the outdoor through a fresh air inlet 11 and an exhaust outlet 14, the air supply cavity 16 and the return air cavity 17 are respectively communicated with the indoor through an air supply outlet 12 and a return air inlet 13, namely, the fresh air cavity 15 is communicated with the outdoor through the fresh air inlet 11, the air supply cavity 16 is communicated with the indoor through the air supply outlet 12, the return air cavity 17 is communicated with the indoor through the return air inlet 13, and the exhaust air cavity 18 is communicated with the outdoor through the exhaust outlet 14.

Specifically, referring to fig. 1 to 5, in some embodiments, the fresh air opening 11 and the supply air opening 12 are arranged side by side along a first transverse direction L, and the exhaust air opening 14 and the return air opening 13 are also arranged side by side along the first transverse direction L, in which case, the fresh air opening 11 and the exhaust air opening 14 are arranged at a first end of the housing 1 along the first transverse direction L, and the supply air opening 12 and the return air opening 13 are arranged at a second end of the housing 1 opposite to the first end along the first transverse direction L. Meanwhile, the fresh air chamber 15 and the supply air chamber 16 are arranged side by side along the first transverse direction L, and the return air chamber 17 and the discharge air chamber 18 are also arranged side by side along the first transverse direction L. The fresh air chamber 15 and the exhaust air chamber 18 are arranged side by side along the second lateral direction W, and the supply air chamber 16 and the return air chamber 17 are arranged side by side along the second lateral direction W. As can be seen, the first transverse direction L is the parallel arrangement direction between the fresh air inlet 11 and the air supply outlet 12, between the fresh air cavity 15 and the air supply cavity 16, between the air return inlet 13 and the air exhaust outlet 14, and between the air return cavity 17 and the air exhaust cavity 18; the second horizontal direction W is the parallel arrangement direction between the fresh air inlet 11 and the air outlet 14, between the fresh air cavity 15 and the air outlet cavity 18, between the return air inlet 13 and the air supply outlet 12, and between the return air cavity 17 and the air supply cavity 16.

The first fan 31 and the second fan 32 serve as a driving mechanism, and are provided inside the housing 1 for driving the airflow to flow. The first fan 31 is used for driving fresh air to flow. The fresh air flows from the fresh air inlet 11 to the air supply outlet 12 under the action of the first fan 31. The second fan 32 is used to drive the exhaust air flow. The indoor air flows from the air return opening 13 to the air outlet 14 under the action of the second fan 32, and the air is discharged to the outside.

The total heat exchanger 2 is arranged in the shell 1 and used for realizing the total heat exchange process between fresh air and exhaust air. The total heat exchanger 2 is communicated with the fresh air cavity 15 and the air supply cavity 16, so that fresh air energy entering the fresh air cavity 15 reaches the air supply cavity 16 and can enter a room through the air supply opening 12. Meanwhile, the total heat exchanger 2 communicates the return air chamber 17 and the exhaust air chamber 18, so that the return air entering the return air chamber 17 can reach the exhaust air chamber 18 and can be discharged to the outside through the exhaust outlet 14. Referring to fig. 8 to 9 and fig. 11, a flow path of the total heat exchanger 2 through which fresh air flows is referred to as a first flow path 25, and a flow path through which return air flows is referred to as a second flow path 26. The first flow channel 25 has a first inlet 21 and a first outlet 22, the first inlet 21 is communicated with the fresh air chamber 15, the first outlet 22 is communicated with the air supply chamber 16, and meanwhile, the first inlet 21 is communicated with the first outlet 22, so that the fresh air chamber 15 is communicated with the air supply chamber 16 through the first flow channel 25. The second flow path 26 has a second inlet 23 and a second outlet 24, the second inlet 23 communicating with the return air chamber 17, the second outlet 24 communicating with the discharge air chamber 18, and the second inlet 23 communicating with the second outlet 24, so that the second flow path 26 communicates the return air chamber 17 with the discharge air chamber 18. And, the first flow channel 25 and the second flow channel 26 cross each other.

Based on the arrangement, when the fresh air and the return air which have temperature difference and pressure difference between the fresh air and the return air flow through the total heat exchanger 2, the heat transfer and mass transfer phenomena can be presented, and the total heat exchange process is realized. For example, when the air conditioner runs in summer, the fresh air obtains cold from the exhaust air, the temperature is reduced, and meanwhile, the fresh air is dried by the exhaust air, and the moisture content is reduced. For example, when the air conditioner runs in winter, the fresh air obtains heat from the exhaust air, and the temperature rises. Therefore, based on the total heat exchange process of the total heat exchanger 2, the fresh air can recover energy from the exhaust air.

Therefore, the total heat exchanger 2 is utilized to exchange heat between fresh air and exhaust air, and the air supply temperature can be adjusted to a certain degree. However, the total heat exchanger 2 can only adjust the supply air temperature in a small range and is difficult to realize a fine temperature control process due to the temperature difference and the pressure difference between the fresh air and the exhaust air. Affecting the overall temperature control performance of the fresh air machine 10.

In view of the above circumstances, this disclosure improves the structure of new fan 10 to improve the temperature control performance of new fan 10, make new fan 10 can adjust supply air temperature more effectively.

Referring to fig. 1-4, in the embodiment of the present disclosure, the fresh air blower 10 includes not only the casing 1, the total heat exchanger 2, the first blower 31, and the second blower 32, but also the heat exchanger 4 and the internal circulation damper 53. The heat exchanger 4 is disposed in the air blowing chamber 16. The internal circulation damper 53 is disposed between the return air chamber 17 and the supply air chamber 16, and is used for controlling whether the return air chamber 17 is communicated with the supply air chamber 16, so as to control whether the return air entering the return air chamber 17 flows into the supply air chamber 16 through the internal circulation damper 53.

By adding the heat exchanger 4 in the air supply cavity 16, the air flowing into the air supply cavity 16 can exchange heat with the heat exchange medium in the heat exchanger 4 when flowing through the heat exchanger 4. Wherein, the heat exchange medium in the heat exchanger 4 can be liquid such as water. The heat exchanger 4 may be in communication with a compressor system (not shown).

The internal circulation air door 53 is additionally arranged between the air return cavity 17 and the air supply cavity 16, so that the air return cavity 17 and the air supply cavity 16 can be communicated or disconnected, and the air return entering the air return cavity 17 from the air return opening 13 can be controlled to flow to the air supply cavity 16 or not, and the heat exchange with the heat exchanger 4 is realized.

Based on the heat exchanger 4 and the internal circulation damper 53, the fresh air machine 10 can realize an internal circulation mode and a mixed air mode.

The internal circulation mode is a working mode in which indoor return air enters the fresh air machine 10 through the return air inlet 13, does not flow to the exhaust outlet 14, flows into the air supply cavity 16, flows through the heat exchanger 4, and then returns to the indoor through the air supply outlet 12, thereby realizing the internal circulation of the indoor air. The corresponding gas flow path is exemplarily shown in fig. 15. Referring to fig. 15, when the air conditioner is in the internal circulation mode, the fresh air is not introduced into the room, but only the return air is subjected to internal circulation, at this time, if the heat exchanger 4 is opened, the fresh air fan 10 integrally plays a role of an indoor unit of the air conditioner, and the temperature of the return air is adjusted by using the heat exchanger 4, so that the temperature of the indoor air can be effectively adjusted. Wherein, not leading into the new trend, can be through setting up the new trend air door 51 that is used for controlling the opening and closing of new trend 11 in new trend 11 department, come the control to realize. The internal circulation mode of opening the heat exchanger 4 is particularly suitable for the situation that the indoor temperature is required to be adjusted, but the outdoor air has quality problems such as pollution, and the like, and can adjust the temperature of the indoor air and meet the indoor temperature adjustment requirement while introducing no outdoor fresh air.

The air mixing mode is a working mode in which the fresh air is fed into the room and the return air is introduced into the room together, so that the fresh air and the return air are mixed and then flow into the air supply cavity 16 to exchange heat with the heat exchanger 4, and then flow into the room through the air supply outlet 12. The corresponding gas flow path is exemplarily shown in fig. 16. Referring to fig. 16, in the air mixing mode, both the fresh air and the return air are introduced into the room, and the fresh air and the return air flow into the room after exchanging heat at the heat exchanger 4, so that the indoor temperature can be more effectively adjusted compared with the case of introducing the fresh air into the room.

Compared with the condition that only fresh air flows through the heat exchanger 4, the air quantity flowing through the heat exchanger 4 is increased after the return air is introduced, the air flow sent into the room after flowing through the heat exchanger 4 is increased, and meanwhile, the indoor air flow is enhanced, so that the air sent into the room can more quickly and fully reach all corners of the room, the temperature of the indoor air is more effectively improved, and the situation that the indoor space is large and the fresh air quantity is small is particularly obvious.

And, compared with the situation that only the fresh air flows through the heat exchanger 4, after the return air is introduced, because the temperature of the return air is consistent with the indoor actual temperature and has a small difference with the target temperature, after the fresh air is mixed with the return air, the difference between the temperature of the mixed air and the target temperature is smaller than the difference between the fresh air and the target temperature, therefore, when the fresh air and the return air flow through the heat exchanger 4 together, the heat exchanger 4 can quickly adjust the air temperature to the target temperature, and the effective regulation and control of the air supply temperature are realized. For example, if the outdoor temperature is 35 ℃, the indoor target temperature is 22 ℃, the indoor actual temperature is 27 ℃, and only the fresh air is introduced, the temperature of the fresh air is 32 ℃ before the fresh air flows through the heat exchanger 4, in this case, it is difficult to adjust the indoor temperature to the target temperature by introducing only fresh air, it is difficult to satisfy the actual demand of the user, based on the scheme of the embodiment of the present disclosure, in this case, the internal circulation damper 53 may be opened to guide the indoor return air to the air supply cavity 16, so that after the indoor return air and the fresh air are mixed, the fresh air which flows through the heat exchanger 4 together with the fresh air at the temperature of 32 ℃ is mixed with the return air at the temperature of 27 ℃, the temperature of the mixed air is lower than the original temperature of the fresh air at the temperature of 32 ℃, for example, approximately 28 ℃, so that when the mixed air flows through the heat exchanger 4, the heat exchanger 4 only needs to provide a small amount of heat exchange, and the gas temperature can be quickly adjusted to the target temperature of 22 ℃ to meet the user requirement.

Therefore, compared with the condition that only fresh air flows through the heat exchanger 4, the air mixing mode can conveniently process the temperature load of the whole house and adjust the temperature of the supplied air to the target temperature more quickly.

In addition, the mixed air mode also has certain advantages compared with the internal circulation mode. For example, compared with the internal circulation mode, the air mixing mode has the advantages that indoor return air and outdoor fresh air are sent into the room in the air mixing mode, and the fresh air is fresh and pure, so that the indoor air quality is improved, the oxygen content of the indoor air is increased, the carbon dioxide content is reduced, and the comfort of the indoor environment is improved.

The mixed air mode can be started under the condition that the indoor temperature does not reach the standard, especially, the mixed air mode can be started under the condition that the indoor temperature is required to be adjusted, the outdoor air quality is good, but the indoor temperature is difficult to reach the target temperature only by sending fresh air to the indoor space.

It is thus clear that, based on inner loop air door 53 and the heat exchanger 4 that set up, new fan 10 can enough realize the inner loop mode, also can realize mixing the wind mode, the working method is nimble various, can adapt to manifold actual demand better, and, no matter the inner loop mode, still mix the wind mode, all can utilize the heat exchanger 4 and the heat transfer that gets into the gas (return air or the mixed wind of return air and new trend) in the air supply chamber 16, come to adjust air supply temperature, more high-efficient and satisfy indoor heat load's processing demand more meticulously, therefore, can effectively promote new fan 10's temperature control performance.

Referring to fig. 1, in some embodiments, a first driving chamber 191 is provided in the housing 1, the first blower 31 is provided in the first driving chamber 191, and the first driving chamber 191 is disposed between the inner circulation damper 53 and the supply chamber 16 along the flow direction of the return air from the return air chamber 17 to the supply chamber 16. The internal circulation damper 53 controls whether the return air chamber 17 communicates with the supply air chamber 16 by controlling whether the return air chamber 17 communicates with the first drive chamber 191.

In the above arrangement, the internal circulation damper 3 is located between the return air cavity 17 and the first driving cavity 191 for accommodating the first fan 31, and whether the return air cavity 17 is communicated with the air supply cavity 16 can be controlled by controlling whether the return air cavity 17 is communicated with the first driving cavity 191, so as to control whether the return air flows into the air supply cavity 16 and exchange heat with the heat exchanger 4. Under this condition, because the return air is at the in-process that flows to the supply-air chamber 16 from return air chamber 17, first fan 31 can flow through, therefore, on the one hand, first fan 31 can play the drive effect to the flow of return air to supply-air chamber 16, make the return air more smoothly flow to supply-air chamber 16, on the other hand, return air and new trend can take place to mix in first fan 31 department, make the two under the effect of first fan 31, mix more evenly, consequently, under the effect of first fan 31, the mist of new trend and return air can be when flowing through heat exchanger 4, more evenly and fully and heat transfer with heat exchanger 4, thereby can adjust supply air temperature to the target temperature more accurately high-efficiently, further promote new fan 10's temperature control performance.

In addition, referring to fig. 1-3 and fig. 5-6, in some embodiments, a second driving chamber 192 is disposed in the casing 1, the second blower 32 is disposed in the second driving chamber 192, the second driving chamber 192 is communicated with the air exhaust chamber 18, and a bypass damper 54 is disposed between the second driving chamber 192 and the return air chamber 17, and the bypass damper 54 controls whether the return air is directly exhausted from the air outlet 14 without passing through the total heat exchanger 2 by controlling whether the return air chamber 17 is communicated with the second driving chamber 192.

In the above arrangement, the second driving chamber 192 is used for accommodating the second fan 32, and the second driving chamber 192 is used as a bypass duct for the air discharge process, and the on-off relationship with the return air chamber 17 is controlled by the bypass damper 54. Based on this, when necessary, the bypass damper 54 can be controlled to open, so that the indoor air entering the return air chamber 17 does not flow through the total heat exchanger 2, but directly flows from the second driving chamber 192 to the exhaust air chamber 18, and finally flows out to the outside from the exhaust outlet 14, and the exhaust process without passing through the total heat exchanger 2 is realized. The operation mode of the new air blower 10 corresponding to the exhaust process without passing through the total heat exchanger 2 may be referred to as a bypass mode.

In the bypass mode, the exhaust air can be discharged to the outside without passing through the total heat exchanger 2, and therefore, the exhaust air resistance is low and the exhaust air smoothness is high. Because work when bypass mode, the return air does not exchange heat with the new trend, discharges to outdoor promptly, consequently, this kind of bypass mode is particularly useful for the less situation of indoor outer difference in temperature (for example transition season), because, under the less circumstances of indoor outer difference in temperature such as transition season, even the new trend does not exchange heat with the return air at total heat exchanger 2 department, also not big to the influence of indoor temperature to adopt bypass mode, can not under the condition that does not excessively influence indoor temperature, realize the process of airing exhaust more smoothly high-efficiently.

Moreover, in the above arrangement, the second driving cavity 192 for accommodating the second fan 32 is directly used as a bypass air duct, and other special bypass air ducts are not additionally provided, which has the advantages of simple structure, simplified air duct structure, and reduced overall size of the fresh air fan 10, and on the other hand, during the bypass air exhaust process, the second fan 32 can drive the indoor air to flow to the air outlet 14, thereby realizing a smoother and more efficient bypass air exhaust process.

As can be seen, based on the second driving chamber 192 and the bypass damper 54, the fresh air machine 10 can realize the bypass mode based on a relatively simple and compact structure, and can smoothly and efficiently perform the bypass air discharge. The bypass mode, the internal circulation mode based on the heat exchanger 4 and the internal circulation damper 53 and the air mixing mode can be switched on to meet the actual requirement more flexibly.

In order to further reduce the overall machine size, in the previously described embodiments, the first fan 31 and the second fan 32 may be arranged one above the other in the longitudinal direction H and at least partially overlapping in the first transverse direction L, see fig. 1 and 8-11. As an example, in the case where the first and second fans 31 and 32 are respectively provided to the first and second driving cavities 191 and 192, referring to fig. 8, the first and second driving cavities 191 and 192 are arranged side by side in the longitudinal direction H and at least partially overlap in the first transverse direction L, so that the first and second fans 31 and 32 are arranged side by side in the longitudinal direction H and at least partially overlap in the first transverse direction L.

The first fan 31 and the second fan 32 are stacked in the longitudinal direction H, so that the first fan and the second fan are not located in the same layer but located in different layers, thereby forming a double-layer arrangement. If the longitudinal direction H is taken as the up-down direction, the first fan 31 and the second fan 32 are arranged up and down at this time, forming a double-layer arrangement form.

The first fan 31 and the second fan 32 at least partially overlap in the first transverse direction L, meaning that the first fan 31 and the second fan 32 are not completely staggered in the first transverse direction L and are no longer arranged at both ends of the housing 1 in the first transverse direction L.

It can be seen that, based on the above arrangement, the first fan 31 and the second fan 32 are arranged in a double-layer manner that the first fan 31 and the second fan 32 are partially overlapped in the first transverse direction L and layered in the longitudinal direction H, in this case, since the first fan 31 and the second fan 32 are no longer arranged at the two transverse ends of the housing, the unit space can be more fully utilized, the size (which may be referred to as the length) of the fresh air fan 10 in the first transverse direction L is reduced, and the effective reduction of the size of the whole air conditioner is realized.

Moreover, the first fan 31 and the second fan 32 adopt a double-layer arrangement mode of partially overlapping on the first transverse L and layering on the longitudinal H, and only one internal circulation air door 53 and one bypass air door 54 are needed, so that the working requirements of an internal circulation mode, a mixed air mode and a bypass mode can be met simultaneously, and an air door is not needed to be specially arranged in addition to adjust and realize the mixed air mode, so that the structure is simplified, meanwhile, the occupied space of the air door is reduced, and the whole size of the unit is reduced.

In the case where the first fan 31 and the second fan 32 are arranged in the double layer as described above, referring to fig. 1 and 5 as an example, a return air passage 195 is provided in the housing 1, the return air passage 195 communicates with the return air opening 13 through the return air chamber 17, the return air passage 195 is arranged side by side with the second fan 32 in the longitudinal direction H and at least partially overlaps in the first transverse direction L, and the return air passage 195 is arranged side by side with the first fan 31 in the second transverse direction W. In this way, the first fan 31 and the return air passage 195 are arranged side by side in the upper layer, and the second fan 32 is arranged in the lower layer of the two, so that the whole layout is simple and compact.

In addition, in the case where the first fan 31 and the second fan 32 adopt the above-described double-layer arrangement, as a layout of the total heat exchanger 2, referring to fig. 8, in the longitudinal direction H of the casing 1, the first inlet 21 and the second inlet 23 of the total heat exchanger 2 are located on the side where the first fan 31 is located, while the first outlet 22 and the second outlet 24 of the total heat exchanger 2 are located on the side where the second fan 32 is located. In this case, if the longitudinal direction H is taken as the up-down direction, the orientation of the first fan 31 with respect to the second fan 32 is taken as the up direction, and the orientation of the second fan 32 with respect to the first fan 31 is taken as the down direction, the first inlet 21 and the second inlet 23 are arranged above the first outlet 22 and the second outlet 24, the first outlet 22 and the second outlet 24 are arranged below the first inlet 21 and the second inlet 23, the first inlet 21 and the second inlet 23 are both located on the upper layer as with the first fan 31, and the first outlet 22 and the second outlet 24 are both located on the lower layer as with the second fan 32. With such an arrangement, it is more convenient for the first fan 31 and the second fan 32 to cooperate with the total heat exchanger 2 to respectively drive the fresh air flow and the exhaust air flow, and it is advantageous to reduce the size (which may be referred to as thickness) of the whole fresh air fan 10 in the longitudinal direction H.

In each of the above embodiments, the first fan 31 and the second fan 32 may be disposed upstream or downstream of the total heat exchanger 2.

For example, referring to fig. 9, in some embodiments, the first fan 31 is disposed between the total heat exchanger 2 and the blowing chamber 16 along the flow direction of the fresh air from the fresh air chamber 15 to the blowing chamber 16, and in this case, the first fan 31 is disposed downstream of the total heat exchanger 2 and upstream of the blowing chamber 16 along the flow direction of the fresh air, so that the fresh air can flow through the total heat exchanger 2 more uniformly than in the case where the first fan 31 is disposed upstream of the total heat exchanger 2, which helps to achieve a more uniform total heat exchange process of the fresh air and the exhaust air at the total heat exchanger 2.

For another example, referring to fig. 11, in some embodiments, the second fan 32 is disposed between the total heat exchanger 2 and the exhaust chamber 18 along the flow direction of the return air from the return air chamber 17 to the exhaust chamber 18, and in this case, the second fan 32 is disposed downstream of the total heat exchanger 2 along the exhaust direction and upstream of the exhaust chamber 18, so that the fresh air can flow more uniformly through the total heat exchanger 2 than in the case where the second fan 32 is upstream of the total heat exchanger 2, which helps to achieve a more uniform total heat exchange process of the fresh air and the exhaust air at the total heat exchanger 2.

It can be seen that arranging at least one of the first fan 31 and the second fan 32 downstream of the enthalpy exchanger 2 facilitates a more uniform enthalpy exchange process of fresh air and return air at the enthalpy exchanger 2. When the first fan 31 and the second fan 32 are uniformly arranged at the downstream of the total heat exchanger 2, both the fresh air and the return air can uniformly flow through the total heat exchanger 2, so that the heat exchange between the fresh air and the return air is more uniform and sufficient, and the exhaust energy can be more effectively recovered. Also, when the first fan 31 and the second fan 32 are both disposed downstream of the total heat exchanger 2, it is more convenient to achieve the aforementioned double-layer arrangement between the first fan 31 and the second fan 32 that is partially overlapped in the first transverse direction L and layered in the longitudinal direction H.

When the second fan 32 is located downstream of the total heat exchanger 2, referring to fig. 8 and 11, in some embodiments, a discharge air passage 194 is provided in the casing 1, the total heat exchanger 2 communicates with the second fan 32 through the discharge air passage 194, and the discharge air passage 194 is located on one side of the total heat exchanger 2 in the longitudinal direction H. Specifically, when the first fan 31 and the second fan 32 are arranged side by side in the longitudinal direction H, the total heat exchanger 2 is located on the side where the first fan 31 is located, and the exhaust duct 194 is located on the side where the second fan 32 is located, and at this time, if the orientation of the first fan 31 with respect to the second fan 32 is upward and the orientation of the second fan 32 with respect to the first fan 31 is downward, the total heat exchanger 2 is located on the upper side together with the first fan 31, and the exhaust duct 194 is located on the lower side together with the second fan 32.

Based on the above arrangement, the total heat exchanger 2 can be conveniently communicated with the second fan 32 located at the downstream of the total heat exchanger 2 without excessively increasing the thickness of the whole machine (i.e. the size of the new fan 10 along the longitudinal direction H), so that the space of the unit can be more fully utilized.

The disclosure will be further described with reference to the embodiments shown in fig. 1-16.

As shown in fig. 1 to 16, in this embodiment, the fresh air blower 10 includes a casing 1, a total heat exchanger 2, a first fan 31, a second fan 32, an internal circulation damper 53, a bypass damper 54, and a heat exchanger 4.

As can be seen from fig. 1 to 5, in this embodiment, the housing 1 is substantially cubic and includes a first end plate 1a, a second end plate 1b, a first side plate 1c, a second side plate 1d, a third side plate 1e, and a fourth side plate 1 f. The first end plate 1a and the second end plate 1b are oppositely arranged along the longitudinal direction H. The first side panel 1c and the second side panel 1d are oppositely arranged along the second lateral direction W. The fourth side panel 1f and the third side panel 1e are oppositely arranged along the first transverse direction L. The first side plate 1c, the second side plate 1d, the third side plate 1e and the fourth side plate 1f are sequentially connected end to serve as enclosing plates of the shell 1, and a hollow cubic space with two open ends is formed. The first end plate 1a and the second end plate 1b are connected to opposite ends of the enclosing plate in the longitudinal direction H, respectively, closing the open ends of the cubic space.

The third side plate 1e is provided with a fresh air inlet 11 and an air outlet 14. The fresh air opening 11 and the air discharge opening 14 are arranged in sequence in the direction from the second side plate 1d to the first side plate 1c, and are both communicated with the outdoor. The fourth side plate 1f is provided with an air supply outlet 12 and an air return outlet 13. The supply port 12 and the return port 13 are arranged in order in the direction from the second side plate 1d to the first side plate 1c, and are both communicated with the indoor space. So, fresh air inlet 11 and air exit 14 arrange in the same end along first horizontal L of casing 1, supply-air outlet 12 and return-air inlet 13 arrange in the other end along first horizontal L of casing 1, and all arrange side by side along first horizontal L between fresh air inlet 11 and supply-air outlet 12 and between return-air inlet 13 and air exit 14, simultaneously, all arrange side by side along the second horizontal W between fresh air inlet 11 and the air exit 14 and between supply-air outlet 12 and the return-air inlet 13. As shown in fig. 1, a fresh air door 51 is disposed at the fresh air inlet 11 to control opening and closing of the fresh air inlet 11, and further control whether fresh air is introduced into the room through the fresh air blower 10. As shown in fig. 6, an exhaust damper 52 is provided at the outlet of the exhaust port 14 to control the opening and closing of the exhaust port 14, and further to control whether or not the indoor air is exhausted to the outside.

The shell 1 is divided into a plurality of cavities by sheet metal parts, including a fresh air cavity 15, an air supply cavity 16, an air return cavity 17, an air exhaust cavity 18, a first driving cavity 191 and a second driving cavity 192.

The fresh air chamber 15 and the air supply chamber 16 are sequentially arranged along the direction from the third side plate 1e to the fourth side plate 1d, are spaced from each other, and are respectively located at two ends of the housing 1 along the first transverse direction L. The discharge chamber 18 and the return chamber 17 are arranged in this order in the direction from the third side plate 1e and the fourth side plate 1d, and are spaced from each other at both ends of the housing 1 in the first transverse direction L. Meanwhile, the fresh air chamber 15 and the exhaust air chamber 18 are sequentially arranged along the direction from the second side plate 1d to the first side plate 1c, and are spaced from each other and respectively located at two ends of the housing 1 along the second transverse direction W. The supply air chamber 16 and the return air chamber 17 are arranged in this order in the direction from the second side plate 1d to the first side plate 1c, and are spaced from each other, at both ends of the casing 1 in the second transverse direction W, respectively. Thus, in the first transverse direction L, the fresh air chamber 15 and the exhaust air chamber 18 are located at the same end of the housing 1, and the supply air chamber 16 and the return air chamber 17 are located at the other end of the housing 1. In the second transverse direction W, the fresh air chamber 15 and the supply air chamber 16 are located at the same end of the housing 1, and the return air chamber 17 and the discharge air chamber 18 are located at the other end of the housing 1. The fresh air cavity 15 and the return air cavity 17 and the air supply cavity 16 and the air exhaust cavity 18 are arranged diagonally.

The fresh air opening 11 is communicated with the outdoor and fresh air cavity 15 to introduce outdoor fresh air. The blowing port 12 communicates the blowing chamber 16 with the room to blow air into the room. The return air inlet 13 communicates the indoor and return air chamber 17 to draw out the indoor air. The exhaust port 14 communicates the exhaust chamber 18 with the outside to exhaust the air to the outside.

The first and second driving cavities 191 and 192 are used to accommodate the first and second fans 31 and 32, respectively. The first and second driving chambers 191 and 192 are layered in the longitudinal direction H and are disposed between the fresh air chamber 15 and the discharge air chamber 18 and the supply air chamber 16 and the return air chamber 17 in the first transverse direction L and are completely overlapped in the first transverse direction L such that they are disposed to face each other in the longitudinal direction H. The first driving cavity 191 is closer to the first end plate 1a than the second driving cavity 192, and the second driving cavity 192 is closer to the second end plate 1b than the first driving cavity 191, that is, the first driving cavity 191 and the second driving cavity 192 are sequentially arranged along a direction from the first end plate 1a to the second end plate 1b, so that a two-layer arrangement manner facing up and down is formed therebetween.

As shown in fig. 1 to 3 and fig. 8, in this embodiment, the first fan 31 and the second fan 32 are both horizontal centrifugal fans, and both of them are respectively disposed in the first driving cavity 191 and the second driving cavity 192, so as to form a double-layer arrangement manner facing up and down. The air outlet of the first fan 31 faces the air supply cavity 16, and is communicated with the air supply cavity 16 to drive the airflow to flow into the air supply cavity 16, and then flow into the room through the air supply outlet 12. The outlet of the second fan 32 faces the exhaust chamber 18 and communicates with the exhaust chamber 18 to drive the airflow to flow into the exhaust chamber 18 and then flow out to the outside through the exhaust outlet 14.

The total heat exchanger 2 is disposed in the casing 1 between the fresh air chamber 15 and the first driving chamber 191 and between the exhaust chamber 18 and the second driving chamber 192, so that the first fan 31 and the second fan 32 are located downstream of the total heat exchanger 2 in the air supply direction and the air exhaust direction, respectively.

As shown in fig. 4, 8 to 9, and 10, in this embodiment, the total heat exchanger 2 has a substantially hexahedral shape, and is internally provided with a first flow passage 25 and a second flow passage 26 that intersect each other. The inlet and outlet of the first flow channel 25 are referred to as a first inlet 21 and a first outlet 22, respectively, and the inlet and outlet of the second flow channel 26 are referred to as a second inlet 23 and a second outlet 24, respectively. Wherein, as shown in fig. 8, the first inlet 21 and the first outlet 22 and the second inlet 23 and the second outlet 24 are diagonally arranged, respectively, while the first inlet 21 and the second inlet 23 are close to the first end plate 1a with respect to the first outlet 22 and the second outlet 24 so that the first inlet 21 and the second inlet 23 are located above the first outlet 22 and the second outlet 24. Specifically, in the longitudinal direction H, the first inlet 21 and the second inlet 23 are located substantially at the same level as the first drive chamber 191 to form a first layer flow passage, and the first outlet 22 and the second outlet 24 are located below the first layer flow passage to form a second layer flow passage.

As shown in fig. 4 and 8, in this embodiment, the first inlet 21 is communicated with the fresh air cavity 15 to realize the communication between the first flow channel 25 and the fresh air cavity 15. As can be seen from fig. 2, a first filter 61 is disposed between the first inlet 21 and the fresh air inlet 11, so that the first filter 61 is located in the flow path between the fresh air inlet 11 and the total heat exchanger 2, and can filter the fresh air flowing to the total heat exchanger 2. First filter screen 61 can be well effect filter screen to carry out well effect through carrying out the new trend and filter, realize effectively purifying the new trend.

With continued reference to fig. 4 and 8, in this embodiment, the first outlet 22 communicates with the first driving chamber 191 through the fresh air channel 193 to communicate the first flow passage 25 with the first driving chamber 191, and further communicate the first flow passage 25 with the blowing chamber 16. The fresh air channel 193 is obliquely arranged from bottom to top and can be obtained by being separated by sheet metal parts.

In addition, as can be seen from fig. 4, 8 and 10, in this embodiment, the second inlet 23 communicates with the return air chamber 17 through a return air passage 195 to communicate the second flow passage 26 with the return air chamber 17. The return air duct 195 is obliquely arranged from bottom to top, and may be partitioned by a sheet metal member. In the longitudinal direction H, the return air passage 195 is located on the side of the second drive chamber 192 close to the first end plate 1a, on the same layer as the first drive chamber 191, and is arranged side by side with the first drive chamber 191 along the second transverse direction W, on the side of the first drive chamber 191 close to the return air chamber 17 along the second transverse direction W. As can be seen from fig. 2, in this embodiment, a second filter 62 is disposed between the second inlet 23 and the return air inlet 13, so that the second filter 62 is disposed between the return air inlet 13 and the total heat exchanger 2 to filter the return air flowing to the total heat exchanger 2. The second filter 62 may be a coarse filter, which is more suitable for the characteristics of less return air impurities and higher cleanliness.

With continued reference to fig. 4 and 8, the second outlet 24 communicates with the second drive chamber 192 through the exhaust passage 194 to communicate the second flow passage 26 with the second drive chamber 192 and, thus, the second flow passage 26 with the exhaust chamber 18. In the longitudinal direction H, the exhaust air passage 194 is located on the side of the total heat exchanger 2 close to the second end plate 1b, or on the side of the second outlet 24 and the first outlet 22 away from the second inlet 23 and the first inlet 21, forming a third layer of flow passage. The air exhaust channel 194 extends horizontally and can be separated by sheet metal parts.

Returning to fig. 1, in this embodiment, the heat exchanger 4 is integrally disposed in the air supply cavity 16, located between the air outlet of the first fan 31 and the air supply opening 12, and is used for exchanging heat with the air flowing from the first fan 31 into the air supply cavity 16, so that the air entering the air supply cavity 16 flows into the room through the air supply opening 12 after exchanging heat with the heat exchange medium in the heat exchanger 4. Moreover, as can be seen from fig. 2, in this embodiment, a third filter screen 63 is disposed between the heat exchanger 4 and the air outlet of the first fan 31, so as to filter the air flowing from the first fan 31 to the heat exchanger 4, and prevent impurities in the air from blocking the heat exchanger 4 and affecting the heat exchange performance and the heat exchange effect of the heat exchanger 4. As an example, the third filter 63 is a high efficiency filter to efficiently filter the gas flowing to the heat exchanger 4, thereby more reliably ensuring the cleanliness of the gas flowing to the heat exchanger 4.

The inner circulation damper 53 and the bypass damper 54 are respectively disposed between the return air passage 195 and the first drive chamber 191 and between the return air chamber 17 and the second drive chamber 192. Specifically, the internal circulation damper 53 is disposed on a side wall of the first driving chamber 191 facing the return air passage 195, and controls whether the return air passage 195 communicates with the first driving chamber 191, thereby controlling whether the return air chamber 17 communicates with the supply air chamber 16, and further controlling whether the return air is introduced into the supply air chamber 16, thereby implementing an internal circulation mode or a mixed air mode. The bypass damper 54 is disposed on the side wall of the second driving chamber 192 facing the return air chamber 17, and controls whether to exhaust air without passing through the total heat exchanger 2 by controlling whether the return air chamber 17 is communicated with the second driving chamber 192 or not, thereby implementing a bypass mode.

Based on the setting mode of this embodiment, new fan 10 simple structure is compact, and whole size is less, and space utilization is higher, and has multiple new trend operating mode such as total heat exchange mode, bypass mode, inner loop mode and the mode of mixing the wind and multiple air conditioner operating mode such as refrigeration, heating, dehumidification and air supply, can carry out new trend load processing and indoor heat load processing according to the demand of difference, realizes multiple functions such as new trend introduction, indoor purification and changes in temperature control.

As shown in fig. 8, in this embodiment, the new blower 10 forms a three-layer structure in the first transverse direction L and forms a three-layer structure in the longitudinal direction H. The three-stage structure in the first horizontal direction L is shown by four vertical dotted lines in fig. 8, and is respectively a first stage from the fresh air inlet 11 to the first driving cavity 191 and the second driving cavity 192, a second stage corresponding to the first driving cavity 191 and the second driving cavity 192, and a third stage from the first driving cavity 191 and the second driving cavity 192 to the air supply outlet 12. The first, second and third sections may also be referred to as front, middle and rear sections. The three-layer structure formed in the longitudinal direction H, which is indicated by four horizontal dashed lines in fig. 8 as being divided, is a first layer in which the first inlet 21 and the second inlet 23 of the total heat exchanger 2 are located, a second layer in which the first outlet 22 and the second outlet 24 of the total heat exchanger 2 are located, and a third layer located on the side of the first outlet 22 and the second outlet 24 remote from the first inlet 21 and the second inlet 23, respectively. The first, second and third layers may also be referred to as upper, middle and lower layers. The three layers are divided mainly for the front section of the three layers.

The whole new fan 10 adopts the three-section three-layer layout mode, so that the length size is small, the thickness size is small, the length size of the whole machine can be reduced on the premise of not obviously increasing the thickness of the machine set, the space of the machine set is fully utilized, the size of the whole machine is effectively reduced, and the whole machine is convenient to install.

In addition, based on the arrangement of this embodiment, the fresh air flow path and the exhaust air flow path are shown in fig. 9 and fig. 10 to 11, respectively.

Fig. 9 shows the entire flow path of fresh air from the fresh air inlet 11 to the room through the blower 12. For the sake of convenience of distinction, in fig. 9, the flow channel of the air during the whole fresh air blowing process (which may be referred to as a blowing flow channel) is indicated by a bold solid line with black, and the flow direction of the air during the blowing process is indicated by a line with an arrow. As shown in fig. 9, in this embodiment, when fresh air needs to be sent into the room, the first fan 31 may be opened, and the fresh air damper 51 may be opened, so that the outdoor fresh air flows into the room through the fresh air port 11, the fresh air chamber 15, the first flow channel 25 of the total heat exchanger 2, the first driving chamber 191, the air supply chamber 16, and the air supply port 12 in sequence under the driving of the first fan 31. Wherein, when passing through the total heat exchanger 2, referring to fig. 8, it is possible to perform total heat exchange with the indoor air flowing to the outdoor side passing through the total heat exchanger 2. In addition, in the process of flowing through the air supply cavity 16, the fresh air flows through the heat exchanger 4, can exchange heat with the heat exchange medium in the heat exchanger 4, and performs a refrigeration or heating isothermal humidity adjustment process under the action of the heat exchanger 4. Therefore, in the whole indoor air supply process, the fresh air can be subjected to twice heat exchange through the total heat exchanger 2 and the heat exchanger 4 in sequence.

Fig. 10 to 11 show the entire flow path of the indoor air from the return air opening 13 to the outside of the room through the discharge opening 14. For the sake of convenience of distinction, in fig. 10 to 11, the flow path of the gas during the whole exhaust process (which may be referred to as an exhaust path) is indicated by a bold solid line with black, and the flow direction of the gas during the exhaust process is indicated by a line with an arrow. As shown in fig. 10 to 11, in this embodiment, when it is necessary to discharge the indoor air to the outside, the second fan 32 may be opened, and the exhaust damper 52 may be opened, and the bypass damper 54 and the internal circulation damper 53 may be closed, so that the indoor air flows to the outside through the return air inlet 13, the return air chamber 17, the return air passage 195, the second flow passage 26 of the total heat exchanger 2, the exhaust passage 194, the second drive chamber 192, the exhaust air chamber 18, and the exhaust outlet 14 in this order by being driven by the second fan 32. Since the exhaust chamber 18 and the air inlet of the second drive chamber 192 are located on different sides of the total heat exchanger 2 in the second transverse direction W, the air will undergo a flow process on both sides of the second transverse direction W of the total heat exchanger 2 during the entire exhaust process. For convenience of understanding, in fig. 10 and 11, two flow paths of the gas before and after flowing to the exhaust passage 194 during exhaust are indicated by solid lines with arrows and broken lines with arrows, respectively. If the front and rear in fig. 10 are front and rear, during the air discharge, as shown in fig. 10, the indoor air first enters the air return chamber 17 located on the front side, then flows through the air return duct 195 also located on the front side, flows toward the total heat exchanger 2, then flows toward the rear side as shown in fig. 11, flows into the second drive chamber 192 via the air discharge duct 194, flows from the rear to the front in the second drive chamber 192, and then, as shown in fig. 10, flows to the air outlet of the second drive chamber 192, bends, flows into the air discharge chamber 18, and finally is discharged through the air outlet 14. For a clearer understanding, the flow path of the indoor air when flowing to the total heat exchanger 2 is further shown by a solid line with arrows in fig. 12.

Based on the above descriptions of the flow paths of the fresh air supply process and the air exhaust process with reference to fig. 9 to 12, the following descriptions respectively describe four fresh air operation modes of the fresh air fan 10, namely, a total heat exchange mode, a bypass mode, an internal circulation mode and an air mixing mode.

In the total heat exchange mode, the fresh air door 51 and the exhaust air door 52 are both opened, the internal circulation air door 53 and the bypass air door 54 are both closed, and the first fan 31 and the second fan 32 are opened, so that outdoor fresh air is sent into the room, and indoor air is discharged to the outside. The gas flow paths in this mode are shown in fig. 13, where solid lines a and dashed lines B with arrows represent the flow paths for fresh air and exhaust air, respectively. Referring to fig. 13 in combination with fig. 9, in the total heat exchange mode, the flow path of the fresh air is: fresh air inlet 11, fresh air cavity 15, first filter screen 61, total heat exchanger 2, fresh air channel 193, first fan 31, third filter screen 63, heat exchanger 4 and air supply outlet 12. Meanwhile, referring to fig. 13, and as can be seen from fig. 10 to 12, the flow path of the exhaust air is: the air return inlet 13, the air return cavity 17, the air return channel 195, the second filter screen 62, the total heat exchanger 2, the air exhaust channel 194, the second fan 32, the air exhaust cavity 18 and the air exhaust outlet 14. In the process, when fresh air and exhaust air flow through the total heat exchanger 2, heat exchange and moisture exchange are carried out, and the heat of the exhaust air is recovered. In the whole process, the heat exchanger 4 can be selectively opened or closed according to whether further temperature control requirements exist. When further temperature control is required, the heat exchanger 4 can be opened, so that fresh air flowing out of the total heat exchanger 2 can exchange heat with a heat exchange medium in the heat exchanger 4 when flowing through the heat exchanger 4, refrigeration or heating is carried out, and the temperature is further changed.

In the bypass mode, the fresh air damper 51, the exhaust air damper 52 and the bypass damper 54 are all opened, the internal circulation damper 53 is closed, and the first fan 31 and the second fan 32 are opened, so that outdoor fresh air is sent into the room, and indoor air is discharged to the outside through the bypass channel. Fig. 14 shows the gas flow path in this mode, where solid lines a and B with arrows represent the flow paths of fresh air and exhausted air, respectively. Referring to fig. 14, and referring to fig. 9, in the bypass mode, the flow path of the fresh air is: fresh air inlet 11, fresh air cavity 15, first filter screen 61, total heat exchanger 2, fresh air channel 193, first fan 31, third filter screen 63, heat exchanger 4 and air supply outlet 12. Meanwhile, referring to fig. 14, the flow path of the exhaust air is: the air return opening 13, the air return cavity 17, the second fan 32, the exhaust cavity 18 and the exhaust opening 14. In the process, the heat exchanger 4 can be selectively opened or closed according to whether the temperature control requirement exists. When the temperature control is required, the heat exchanger 4 is opened, so that the fresh air can exchange heat with the heat exchange medium in the heat exchanger 4 when flowing through the heat exchanger 4, refrigeration or heating is carried out, and temperature regulation is realized.

In the internal circulation mode, the fresh air door 51, the exhaust air door 52, and the bypass air door 54 are all closed, the internal circulation air door 53 is opened, the first fan 31 is opened, and the second fan 32 is closed, so that fresh air is not fed into the room and exhausted to the outside, but only the internal circulation of the indoor air is performed. Fig. 15 shows the gas flow path in this mode, in which the solid line with arrows B indicates the flow path of the circulating wind. As shown in fig. 15, in the internal circulation mode, the flow paths of the circulating wind are: the air return inlet 13, the air return cavity 17, the air return channel 195, the internal circulation air door 53, the first fan 31, the air supply cavity 16 and the air supply outlet 12. In the process, the heat exchanger 4 can be opened to refrigerate, heat or dehumidify the circulating air and adjust the temperature and humidity of the indoor air.

In the air mixing mode, the fresh air door 51, the exhaust air door 52 and the internal circulation air door 53 are all opened, the bypass air door 54 is closed, and the first fan 31, the second fan 32 and the heat exchanger 4 are all opened, so that outdoor fresh air is sent into the room, and the indoor air flows through two paths, wherein one path of the indoor air flows into the room together with the fresh air after flowing through the heat exchanger 4, and the other path of the indoor air flows out of the room. Fig. 16 shows the gas flow paths in this mode, where the solid lines a and B with arrows represent the flow paths of fresh air and return air, respectively, and the two branches of the solid line B represent the flow paths of two portions of return air flowing indoors and outdoors, which may be referred to as the flow path of mixed air and the flow path of discharged air, respectively. Referring to fig. 15, the flow path of the fresh air and the flow path of the exhaust air are the same as the flow path of the fresh air flowing through and the flow path of the exhaust air in the total heat exchange mode, respectively, and the flow path of the mixed air is the same as the flow path of the circulating air in the internal circulation mode, specifically, the flow path of the fresh air is: a fresh air inlet 11, a fresh air cavity 15, a first filter screen 61, a total heat exchanger 2, a fresh air channel 193, a first fan 31, a third filter screen 63, a heat exchanger 4 and an air supply outlet 12; the flow path of the exhaust air is as follows: the air return inlet 13, the air return cavity 17, the air return channel 195, the second filter screen 62, the total heat exchanger 2, the exhaust channel 194, the second fan 32, the exhaust cavity 18 and the exhaust outlet 14; the flow path of the mixed air is as follows: the air return inlet 13, the air return cavity 17, the air return channel 195, the internal circulation air door 53, the first fan 31, the third filter screen 63, the heat exchanger 4 and the air supply outlet 12. In the process, the fresh air carries out heat exchange and heat exchange with the exhaust air when flowing through the full heat exchanger 2 on the one hand, and on the other hand, when flowing through the first fan 31, the fresh air is mixed with the mixed air and then flows to the heat exchanger 4 together, and exchanges heat with the heat exchange medium in the heat exchanger 4, so that the problem of part of indoor heat loads can be solved when the fresh air is provided indoors, and the indoor temperature is adjusted to the target temperature more quickly.

The four fresh air modes of the total heat exchange mode, the bypass mode, the internal circulation mode and the air mixing mode can meet different ventilation requirements. For example, the full heat exchange mode can be suitable for the weather condition with large indoor and outdoor temperature difference. Bypass mode, may be appropriate for transitional seasons. The internal circulation mode can be suitable for the condition that the outdoor air state is bad and is not suitable for introducing fresh air. The mixed air mode can be suitable for the condition that has the fast temperature control demand. In the four fresh air modes, if the heat exchanger 4 is opened, the heat exchanger 4 can perform various air conditioner adjusting modes such as refrigeration, heating or dehumidification according to actual requirements, and the indoor temperature and humidity load processing requirements are met.

It can be seen that the new fan 10 of this embodiment can switch between different working modes such as total heat exchange mode, bypass mode, inner loop mode and the mode of mixing the wind, and the working method is nimble various, and not only can satisfy new trend load demand, can also satisfy indoor heat load demand, and temperature control performance is better.

Note that, in the four fresh air modes, although the open/close states of the fresh air damper 51, the exhaust air damper 52, the internal circulation damper 53, and the bypass damper 54 actually change, fig. 13 to 16 do not show the open states, and fig. 13 to 16 show only the open states of the fresh air damper 51, the exhaust air damper 52, the internal circulation damper 53, and the bypass damper 54.

The opening and closing of the fresh air damper 51, the exhaust air damper 52, the internal circulation damper 53, and the bypass damper 54 can be achieved by rotation or movement. For example, fig. 7 shows a structure of an inner circulation damper 53 that is rotatably opened and closed. As shown in fig. 7, the internal circulation damper 53 includes a frame 55 and a valve plate 56, the frame 55 is provided with an opening 57, and the valve plate 56 is rotatably provided at the opening 57 and rotates to control the opening and closing of the opening 57, thereby controlling the opening and closing of the gas flow passage.

In summary, the fresh air blower 10 provided by the embodiment of the present disclosure has a compact structure, is flexible to use, and has a better temperature control performance.

Based on the fresh air machine 10 of the embodiment of the disclosure, the disclosure also provides a control method, a controller, a fresh air system and a computer readable storage medium.

The control method comprises the steps of opening the internal circulation air door 53, enabling return air entering the return air cavity 17 through the return air inlet 13 to flow into the air supply cavity 16 through the internal circulation air door 53, exchanging heat with the heat exchanger 4 in the air supply cavity 16, and enabling the return air to enter the room through the air supply outlet 12. Also, in some embodiments, while the return air that enters the return air chamber 17 via the return air inlet 13 is caused to flow into the blowing chamber 16 via the internal circulation damper 53, the fresh air is also caused to flow into the blowing chamber 16.

The controller 8 includes a memory 81 and a processor 82 coupled to the memory, the processor 82 being configured to execute the control method of the embodiments of the present disclosure based on instructions stored in the memory 81.

For example, referring to fig. 17, in some embodiments, controller 8 includes a memory 81, a processor 82, a communication interface 83, and a bus 84. The memory 81 is used to store instructions. The processor 82 is coupled to the memory 81 and is configured to execute control methods implementing the foregoing embodiments based on instructions stored by the memory 131. The memory 81, the processor 82, and the communication interface 83 are connected by a bus 84.

The memory 81 may be a high-speed RAM memory or a non-volatile memory (non-volatile memory) or the like. The memory 81 may also be a memory array. The storage 81 may also be partitioned and the blocks may be combined into virtual volumes according to certain rules. The processor 82 may be a central processing unit CPU, or an application Specific Integrated circuit asic, or one or more Integrated circuits configured to implement the control method of the heat pump system of the present invention.

The fresh air system comprises a fresh air fan 10 of the embodiment of the disclosure and a controller 8 of the embodiment of the disclosure.

The computer readable storage medium stores computer instructions that are executed by the processor to perform the control method of the disclosed embodiments.

The above description is only exemplary of the present disclosure and is not intended to limit the present disclosure, and any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure.

Claims (10)

1. A new fan (10), comprising:

the air conditioner comprises a shell (1), wherein a fresh air inlet (11), an air supply outlet (12), an air return inlet (13) and an air exhaust outlet (14) are arranged on the shell (1), a fresh air cavity (15), an air supply cavity (16), an air return cavity (17) and an air exhaust cavity (18) which are separated from each other are arranged in the shell (1), the fresh air cavity (15) and the air exhaust cavity (18) are respectively communicated with the outside through the fresh air inlet (11) and the air exhaust outlet (14), and the air supply cavity (16) and the air return cavity (17) are respectively communicated with the inside through the air supply outlet (12) and the air return inlet (13);

the total heat exchanger (2) is arranged in the shell (1), is communicated with the fresh air cavity (15) and the air supply cavity (16), and is communicated with the air return cavity (17) and the exhaust cavity (18);

the first fan (31) is arranged in the shell (1) and drives fresh air to flow;

a second fan (32) which is disposed in the housing (1) and drives the exhaust air to flow;

the heat exchanger (4) is arranged in the air supply cavity (16); and

and the internal circulation air door (53) is arranged between the air return cavity (17) and the air supply cavity (16) and is used for controlling whether the air return cavity (17) is communicated with the air supply cavity (16) or not so as to control whether the return air entering the air return cavity (17) flows into the air supply cavity (16) or not through the internal circulation air door (53).

2. The new fan (10) of claim 1,

a first driving cavity (191) is arranged in the shell (1), the first fan (31) is arranged in the first driving cavity (191), the first driving cavity (191) is arranged between the internal circulation air door (53) and the air supply cavity (16) along the flowing direction of return air from the air return cavity (17) to the air supply cavity (16), and the internal circulation air door (53) controls whether the air return cavity (17) is communicated with the air supply cavity (16) by controlling whether the air return cavity (17) is communicated with the first driving cavity (191); and/or the presence of a gas in the gas,

be equipped with second drive chamber (192) in casing (1), second fan (32) set up in second drive chamber (192), second drive chamber (192) with communicate between exhaust chamber (18), and with be equipped with bypass air door (54) between return air chamber (17), bypass air door (54) are through control return air chamber (17) with whether second drive chamber (192) communicate, come whether control return air does not pass through total heat exchanger (2) and directly follow air exit (14) are discharged.

3. The new fan (10) according to claim 1, characterized in that said first fan (31) and said second fan (32) are arranged one above the other in a longitudinal direction (H) and at least partially overlap in a first transversal direction (L), said first transversal direction (L) being the direction of side by side arrangement of said new air opening (11) and said supply air opening (12), said longitudinal direction (H) being the direction perpendicular to said first transversal direction (L) and a second transversal direction (W), said second transversal direction (W) being the direction of side by side arrangement of said new air opening (11) and said exhaust air opening (14).

4. The new fan (10) according to claim 3, characterized in that a return air channel (195) is provided in the casing (1), said return air channel (195) communicating with said return air inlet (13) through said return air chamber (17), said return air channel (195) being arranged side by side with said second fan (32) in said longitudinal direction (H) and at least partially overlapping in said first transversal direction (L), said return air channel (195) being arranged side by side with said first fan (31) in said second transversal direction (W).

5. The new fan (10) according to claim 3, wherein the total heat exchanger (2) comprises a first flow channel (25) and a second flow channel (26) arranged crosswise, a first inlet (21) and a first outlet (22) of the first flow channel (25) communicating with the new air chamber (15) and the blowing chamber (16), respectively, a second inlet (23) and a second outlet (24) of the second flow channel (26) communicating with the return air chamber (17) and the blowing chamber (16), respectively, the first inlet (21) and the second inlet (23) being located on the side of the first fan (31) and the first outlet (22) and the second outlet (24) being located on the side of the second fan (32) in the longitudinal direction (H).

6. The fresh air machine (10) according to any of claims 1 to 5, wherein the first fan (31) is arranged between the total heat exchanger (2) and the supply air chamber (16) in the flow direction of fresh air from the fresh air chamber (15) to the supply air chamber (16); and/or the second fan (32) is arranged between the total heat exchanger (2) and the exhaust cavity (18) along the flowing direction of the return air from the return air cavity (17) to the exhaust cavity (18).

7. The new fan (10) according to claim 6, wherein an exhaust duct (194) is provided in the casing (1), the total heat exchanger (2) communicates with the second fan (32) through the exhaust duct (194), the exhaust duct (194) is located on one side of the total heat exchanger (2) along a longitudinal direction (H), the longitudinal direction (H) is a direction perpendicular to a first transverse direction (L) and a second transverse direction (W), the first transverse direction (L) is a side-by-side arrangement direction of the new air opening (11) and the supply air opening (12), and the second transverse direction (W) is a side-by-side arrangement direction of the new air opening (11) and the exhaust air opening (14).

8. The new fan (10) according to claim 7, characterized in that said first fan (31) and said second fan (32) are arranged side by side along said longitudinal direction (H) in which said total heat exchanger (2) is located on the side where said first fan (31) is located and said exhaust air duct (194) is located on the side where said second fan (32) is located.

9. The fresh air machine (10) as claimed in any of claims 1 to 5 wherein said first fan (31) and/or second fan (32) is a horizontal centrifugal fan.

10. The fresh air machine (10) as claimed in any of claims 1-5, wherein said fresh air machine (10) comprises at least one of:

the fresh air door (51) is arranged at the fresh air port (11) to control the opening and closing of the fresh air port (11);

the air exhaust air door (52) is arranged at the air exhaust opening (14) to control the opening and closing of the air exhaust opening (14);

a first filter (61) provided in a flow path between the fresh air port (11) and the total heat exchanger (2);

a second filter (62) provided in a flow path between the return air inlet (13) and the total heat exchanger (2);

and the third filter screen (63) is arranged on a flow path between the first fan (31) and the heat exchanger (4).

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