CN215723737U - Air conditioner - Google Patents

Abstract

The disclosure relates to the technical field of air conditioners, in particular to an air conditioner. The air conditioner includes: the mixing section is used for mixing return air and fresh air; an air supply section arranged downstream of the mixing section in a first direction and configured to supply air to the room; and the surface cooling section is arranged between the mixing section and the air supply section along the first direction and comprises a first surface cooler and a second surface cooler, the first surface cooler and the second surface cooler are arranged on the same cross section perpendicular to the first direction and are arranged side by side along the second direction perpendicular to the first direction in sequence, a water inlet of the first surface cooler is connected with a water supply pipeline, a water outlet of the first surface cooler and a water outlet of the second surface cooler are connected with a water return pipeline, and a water outlet of the first surface cooler is connected with a water inlet of the second surface cooler. Based on this, can cancel the reheat process of transition season heater, reduce the energy waste.

Description

Air conditioner

Technical Field

The disclosure relates to the technical field of air conditioners, in particular to an air conditioner.

Background

In order to meet the constant temperature and humidity requirements of cigarette factories and other occasions, the air conditioner generally comprises a surface cooler and a heater which are arranged between a mixing section and an air supply section, and the heater is arranged between the surface cooler and the air supply section. In the transition season, the surface air cooler is required to be used for dehumidification, and the air temperature is low after dehumidification, so that the dehumidified air needs to be reheated by the heater behind the surface air cooler. The cold and hot offsetting process has the problem of energy waste.

Disclosure of Invention

The present disclosure is directed to an air conditioner to reduce energy waste.

In order to achieve the above object, the present disclosure provides an air conditioner including:

the mixing section is used for mixing return air and fresh air;

an air supply section arranged downstream of the mixing section in a first direction and configured to supply air to the room; and

the surface cooling section is arranged between the mixing section and the air supply section along the first direction and comprises a first surface cooler and a second surface cooler, the first surface cooler and the second surface cooler are arranged on the same cross section perpendicular to the first direction and are arranged side by side along the second direction perpendicular to the first direction in sequence, a water inlet of the first surface cooler is connected with a water supply pipeline, a water outlet of the first surface cooler and a water outlet of the second surface cooler are connected with a water return pipeline, and a water outlet of the first surface cooler is connected with a water inlet of the second surface cooler.

In some embodiments, the air conditioner includes a first valve through which the water outlet of the first surface cooler is connected to the water return line and the water inlet of the second surface cooler, and the first valve controls whether communication is established between the water outlet of the first surface cooler and the water return line and between the water outlet of the first surface cooler and the water inlet of the second surface cooler.

In some embodiments, the air conditioner includes a second valve disposed on a pipe between the first valve and the water outlet of the first surface cooler for regulating the amount of water flowing through the first surface cooler; and/or the air conditioner comprises a third valve, the third valve is connected with the water inlet of the second surface air cooler and the water supply pipeline and controls the connection and disconnection between the water inlet of the second surface air cooler and the water supply pipeline.

In some embodiments, the mixing section has a fresh air inlet, and the first surface air cooler is closer to the fresh air inlet than the second surface air cooler in the second direction; and/or the windward area of the first surface air cooler is larger than the windward area of the second surface air cooler.

In some embodiments, the ratio of the frontal area of the first surface air cooler to the frontal area of the second surface air cooler is 55: 45.

in some embodiments, the air conditioner includes a partition disposed between the first surface cooler and the second surface cooler to partition air flowing to the first surface cooler and the second surface cooler.

In some embodiments, the air conditioner includes a filtering section disposed between the mixing section and the surface cooling section along a first direction, and including a first filter and a second filter disposed on the same cross-section perpendicular to the first direction and sequentially arranged side by side along a second direction, the first filter filtering an air flow passing through the first surface cooler, and the second filter filtering an air flow passing through the second surface cooler.

In some embodiments, the air conditioner includes an air volume adjusting device disposed between the mixing section and the surface cooling section along a first direction, the air volume adjusting device adjusting a distribution of air flowing from the mixing section between the first surface air cooler and the second surface air cooler.

In some embodiments, the air volume adjusting device includes a first air volume adjusting valve and a second air volume adjusting valve, the first air volume adjusting valve and the second air volume adjusting valve are arranged on the same cross section perpendicular to the first direction and are arranged side by side in sequence along a direction from the second direction, the first air volume adjusting valve adjusts an air volume flowing through the first surface air cooler, and the second air volume adjusting valve adjusts an air volume flowing through the second surface air cooler.

In some embodiments, the air volume adjusting device is disposed between the mixing section and the filtering section of the air conditioner in the first direction.

Based on this disclosed embodiment, when the transition season, can let in the partly return water of first surface cooler into second surface cooler, improve the temperature of intaking of second surface cooler for the air after the second surface cooler is handled can mix through the air after with first surface cooler dehumidification, improves the air supply temperature, thereby cancels the reheat process of heater, reduces the energy extravagant.

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 structural diagram of an air conditioner in an embodiment of the present disclosure.

Fig. 2 is a schematic water circuit diagram of a first surface cooler and a second surface cooler in an embodiment of the disclosure.

Fig. 3 is a psychrometric chart of an air conditioner according to an embodiment of the present disclosure.

Fig. 4 is a schematic diagram illustrating a flow state of chilled water in a first surface air cooler and a second surface air cooler when an air conditioner according to an embodiment of the present disclosure is in a maximum cooling mode.

Fig. 5 is a schematic view of the heat and humidity processing process when the air conditioner is in the maximum cooling capacity mode according to the embodiment of the disclosure.

Fig. 6 is a schematic view illustrating a flow state of chilled water in first and second surface coolers when an air conditioner according to an embodiment of the present disclosure is in a dehumidification mode.

Fig. 7 is a schematic view of a heat and humidity processing process when the air conditioner is in the dehumidification mode according to the embodiment of the disclosure.

Fig. 8 is a schematic view illustrating a flow state of chilled water in first and second surface coolers when an air conditioner according to an embodiment of the present disclosure is in a transition season mode.

Fig. 9 is a schematic view of the heat and humidity treatment process when the air conditioner is in the transition season mode according to the embodiment of the disclosure.

Fig. 10 is a schematic structural diagram of a controller according to an embodiment of the disclosure.

Description of reference numerals:

10. an air conditioner; 20. a controller; 201. a memory; 202. a processor; 203. a communication interface; 204. a bus;

1. a box body; 11. a first temperature and humidity detector; 12. a second temperature and humidity detector; 13. a third temperature and humidity detector; 14. a fourth temperature and humidity detector; 15. a fifth temperature and humidity detector; 16. a sixth temperature and humidity detector; 17. a seventh temperature and humidity detector; 18. a separator;

2. a return air section; 21. an air return opening; 22. a return air fan;

3. an air exhaust section; 31. an air outlet; 32. an air valve;

4. a mixing section; 41. a fresh air inlet;

5. a filtration section; 51. a first filter; 52. a second filter;

6. a surface cooling section; 61. a first surface air cooler; 62. a second surface air cooler; 63. a first valve; 64. a second valve; 65. a third valve; 66. a water supply line; 67. a water return pipeline;

71. a heating section; 72. a heater; 73. a humidification stage; 74. a humidifier;

8. an air supply section; 81. an air supply outlet; 82. an air supply fan;

9. an air volume adjusting device; 91. a first air volume adjusting valve; 92. a second air volume adjusting valve;

x, a first direction; y, second 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 is to be understood that the orientation or positional relationship indicated by the directional terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal" and "top, bottom", etc., are generally based on the orientation or positional relationship shown in the drawings, and are presented only for the convenience of describing and simplifying the disclosure, and in the absence of a contrary indication, these directional terms are not intended to indicate and imply that the device or element being referred to must have a particular orientation or be constructed and operated in a particular orientation, and therefore, should not be taken as limiting the scope of the disclosure; the terms "inner and outer" refer to the inner and outer relative to the profile of the respective component itself.

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.

In some situations, an air conditioner is required to provide a constant temperature and humidity environment. For example, in a combined factory such as a cigarette factory, in order to meet the requirements of the production process, an air conditioner is required to provide a constant temperature and humidity process environment for a workshop.

The tobacco processing process generally comprises the steps of leaf storage, shred storage, rolling, filter stick forming, raw material (including tobacco raw materials and tobacco materials) storage, shred production and processing and the like. Each link corresponds to a different production area. The areas corresponding to the links of leaf storage, silk making, rolling, filter stick forming and the like have high requirements on temperature and humidity, and the temperature and humidity are expected to be kept constant, so that a constant-temperature and constant-humidity air conditioner is usually arranged to regulate the temperature and humidity of the corresponding areas, so that the areas can be kept at constant temperature and constant humidity.

In order to meet the requirements of constant temperature and constant humidity, the air conditioner is generally provided with a plurality of heat and humidity treatment means such as a surface cooler, a heater, a humidifier and the like. As a typical air conditioning structure, referring to fig. 1, an air conditioner 10 includes an air return section 2, an air discharge section 3, a mixing section 4, a filtering section 5, a surface cooling section 6, a heating section 71, a humidifying section 73, and a blowing section 8, which are sequentially arranged along a first direction X.

The air return section 2 comprises an air return opening 21 and an air return fan 22, and the air return opening 21 is arranged on the box body 1 of the air conditioner 10 and is communicated with the indoor space so as to enable the return air to enter the air return section 2; the return air blower 22 is provided inside the cabinet 1 and communicates with the exhaust section 3 to send return air, which has entered the return air section 2 via the return air inlet 21, to the exhaust section 3.

The air exhaust section 3 is arranged between the air return section 2 and the mixing section 4 and is communicated with the air return section 2 and the mixing section 4. The exhaust section 3 comprises an exhaust opening 31. The air outlet 31 is disposed on the box 1 and communicates with the outdoor environment to discharge part of the return air entering the air discharge section 3 to the outdoor. The return air entering the exhaust section 3 is partially exhausted to the outside through the exhaust port 31 by the drive of the return air blower 22, and the other part continues to flow downstream and flows into the mixing section 4. As an example, the exhaust section 3 is communicated with the mixing section 4 through an air valve 32, and the air valve 32 is used for adjusting the proportion of the return air flowing to the mixing section 4 to the total return air volume, and further adjusting the proportion of the fresh air mixed with the return air in the mixing section 4. Generally, how much return air is discharged from the air outlet 31, how much fresh air is taken in from the fresh air inlet 41.

The mixing section 4 is arranged between the air exhaust section 3 and the filtering section 5 and used for mixing fresh air and return air. The mixing section 4 comprises a fresh air inlet 41. The fresh air inlet 41 is arranged on the box body 1 and communicated with the outdoor environment for fresh air to enter. Fresh air entering the mixing section 4 through the fresh air inlet 41 is mixed with return air flowing into the mixing section 4 from the exhaust section 3. The fresh and return air is mixed and then flows downstream continuously to the filtering section 5.

The filtering section 5 is arranged between the mixing section 4 and the surface cooling section 6 and is used for filtering the airflow flowing to the surface cooling section 6.

The surface cooling section 6 is disposed between the filtering section 5 and the heating section 71, and is used for dehumidifying air. The surface cooling section 6 comprises a surface cooler. The surface cooler is filled with chilled water, and the air is cooled and dehumidified by utilizing the heat exchange between the chilled water and the air.

The heating section 71 is provided between the surface cooling section 6 and the air blowing section 8, and includes a heater 72 for secondarily heating the dehumidified air.

The humidification stage 73 is disposed between the heating stage 71 and the blowing stage 8 and includes a humidifier 74 for humidifying air flowing to the blowing stage 8.

The blowing section 8 is disposed downstream of the humidifying section 73 for blowing air into the room. The air supply section 8 includes an air supply outlet 81 and an air supply fan 82. The air supply port 81 is provided in the casing 1 and communicates with the indoor space. The air supply fan 82 is disposed in the cabinet 1, and is configured to drive air to flow into the room through the air supply outlet 81, thereby achieving indoor air supply.

As an example, as shown in fig. 1, the air return opening 21, the air outlet 31, the fresh air inlet 41 and the air supply opening 81 are all disposed on the side wall of the box body 1 and are all located on the same side of the longitudinal central axis of the box body 1, specifically, in fig. 1, the air return opening 21, the air outlet 31, the fresh air inlet 41 and the air supply opening 81 are all disposed on the top wall of the box body 1.

In the working process, return air enters the return air section 2 through the return air inlet 21 under the action of the return air fan 22 and flows to the exhaust section 3, part of the return air is exhausted to the outside through the exhaust outlet 31 according to the fresh air proportion, the other part of the return air enters the mixing section 4 and is mixed with fresh air entering the mixing section 4 through the fresh air inlet 41, the fresh and return air is filtered through the filtering section 5 after being mixed, then enters the surface cooling section 6, is cooled and dehumidified by a surface cooler of the surface cooling section 6, then continuously flows to the downstream, and finally flows to the indoor through the air supply outlet 81 under the action of the air supply fan 82.

In order to achieve a sufficient dehumidification effect, low-temperature chilled water (for example, low-temperature chilled water at 7 ℃) is generally introduced into the surface air cooler, so that although effective dehumidification can be achieved, the air temperature is too low, generally, the air temperature after dehumidification by the surface air cooler is about 16-19 ℃, and therefore, if the air after dehumidification is not processed, the air supply temperature difference is too large, the indoor temperature requirement is difficult to meet, and the problem is particularly obvious under the working condition that the requirement on the indoor temperature is high in transition seasons and the like.

In order to solve the problem of low air temperature after surface cooling and dehumidification, the means adopted in the related art is that after the surface cooling section 6 cools and dehumidifies the air to the machine dew point L1, the dehumidified air is heated again by the heating section 71, so that the air is reheated to the air supply state point meeting the requirement, and then is sent to the room by the air supply section 8. Although the mode of reheating the heating section 71 after dehumidification in the surface cooling section 6 can meet the temperature and humidity regulation and control requirements in the environment with high humidity and low temperature such as a transition season and the like, the mode is a cold and heat offsetting mode, which wastes heat and cold, so that the problem of energy waste exists, and the annual energy consumption of a power center is high. For the air conditioner with smaller cooling load in summer or larger air supply volume design, the required reheating volume is particularly obvious, and the problem of energy waste is more prominent. The machine dew point L1 refers to the saturation point of the air corresponding to the average temperature of the cold coil surface.

In view of the above circumstances, the present disclosure provides an air conditioner, a control method thereof, a controller, an air conditioning system, and a storage medium, which reduce energy waste by improving the air conditioner.

Fig. 1-10 schematically illustrate an air conditioner and controller of the present disclosure. The arrows in fig. 1 indicate the air flow direction. The arrows in fig. 4, 6 and 8 indicate the water flow direction.

Referring to fig. 1, in the air conditioner provided in the embodiment of the present disclosure, the surface cooling section 6 disposed between the mixing section 4 and the blowing section 8 in the first direction X does not include only one surface cooler but includes two surface coolers, which are a first surface cooler 61 and a second surface cooler 62, respectively.

As shown in fig. 1, the first surface cooler 61 and the second surface cooler 62 are arranged on the same section (may be referred to as the same cross section) perpendicular to the first direction X, and are arranged side by side in sequence along a second direction Y perpendicular to the first direction X. If the second direction Y is taken as the direction from top to bottom, the first surface air cooler 61 is on the top, the second surface air cooler 62 is on the bottom, and the first surface air cooler 61 and the second surface air cooler 62 are opposite to each other up and down to form an upper layer and a lower layer of surface air coolers. Thus, the air flowing from the mixing section 4 to the surface cooling section 6 may be divided into two portions, one portion flowing through the first surface air cooler 61 and the other portion flowing through the second surface air cooler 62, that is, the first surface air cooler 61 and the second surface air cooler 62 may be in contact with one portion and the other portion of the air flowing to the surface cooling section 6, respectively. As an example, as shown in fig. 1, in the second direction Y, the first surface cooler 61 is closer to the fresh air inlet 41 than the second surface cooler 62. The windward area of the first surface air cooler 61 is larger than that of the second surface air cooler 62, for example, the ratio of the windward areas is 55: 45. the windward areas of the first surface air cooler 61 and the second surface air cooler 62 refer to the effective areas of the two facing the air flowing towards the two, and are the effective contact areas of the two with the incoming air.

Meanwhile, as shown in fig. 2, the inlet of the first surface cooler 61 is connected to a water supply line 66. The water outlet of the first surface cooler 61 and the water outlet of the second surface cooler 62 are both connected with a water return pipeline 67. The water outlet of the first surface cooler 61 is connected with the water inlet of the second surface cooler 62. In this way, a portion of the return water of the first surface cooler 61 may flow to the second surface cooler 62 as needed.

Based on the above arrangement, in the transition season, a part of the backwater of the first surface air cooler 61 may be led to the second surface air cooler 62, and the air passing through the second surface air cooler 62 is dry-cooled, so that the air treated by the second surface air cooler 62 may be mixed with the dehumidified air of the first surface air cooler 61 to increase the supply air temperature. Because whole process need not to utilize heating section 71 to carry out reheat to the air after the dehumidification, can reach required air supply temperature, does not have the cold and hot offset problem that has not had both the cooling and has the heating, consequently, can effectively reduce the energy waste. Dry cooling means cooling without dehumidification or cooling with dehumidification of only a small amount.

Fig. 8 shows a flow state of chilled water in the first surface cooler 61 and the second surface cooler 62 in the transition season. As shown in fig. 8, when in the transitional season, the water inlet of the first surface cooler 61 may be communicated with the water supply line 66, the water outlet of the first surface cooler 61 and the water outlet of the second surface cooler 62 may be communicated with the water return line 67, and the water outlet of the first surface cooler 61 may be communicated with the water inlet of the second surface cooler 62. Thus, referring to fig. 8, in operation, the low temperature (e.g., 7 ℃) chilled water provided by the water supply line 66 enters the first surface air cooler 61, exchanges heat with the air flowing through the first surface air cooler 61 in the first surface air cooler 61, cools and dehumidifies the air, turns into high temperature (e.g., 12 ℃) chilled water, flows out of the first surface air cooler 61, flows partially to the return line 67, enters the second surface air cooler 62, exchanges heat with the air flowing through the second surface air cooler 62, and dry cools the partially air. The air after being dry-cooled by the second surface air cooler 62 is secondarily mixed with the air after being cooled and dehumidified by the first surface air cooler 61 in the process of flowing downstream, and because the high-temperature chilled water flowing out of the first surface air cooler 61 is introduced into the second surface air cooler 62, the temperature of the air after being dry-cooled by the second surface air cooler 62 is higher than that of the air after being cooled and dehumidified by the first surface air cooler 61, so that the air obtained by secondarily mixing the air after being dry-cooled by the second surface air cooler 62 with the air after being cooled and dehumidified by the first surface air cooler 61 is higher than that of the air after being cooled and dehumidified by the first surface air cooler 61 before being mixed, and the temperature is increased, so that the secondary heating is not needed by the heater 72 of the heating section 71.

Fig. 3 shows a psychrometric chart of the air conditioner 10 according to an embodiment of the present disclosure. Referring to fig. 3, if the air supply state point of the air conditioner 10 according to the embodiment of the present disclosure in the transition season is counted as the first air supply state point S2, it can be understood that the temperature of the first air supply state point S2 is higher than the temperature of the machine dew point L1, and at this time, the air supply process implemented by the cooling table 6 may be referred to as the first air supply state point S2 air supply, and the operation mode of the air conditioner 10 may be referred to as the transition season mode.

Fig. 9 exemplarily shows a specific heat and humidity processing procedure of the air conditioner 10 in the transition season. Referring to fig. 9 in conjunction with fig. 3, in some embodiments, in a transition season, the return air N and the fresh air W are mixed in the mixing section 4, when the fresh air and the return air are mixed, the ratio of the fresh air is 30%, after the fresh air and the return air are mixed, 67% of the mixed air M flows to the first surface air cooler 61 to be cooled and dehumidified, and reaches a state point L2, the temperature and the humidity of the state point L2 are lower than those of the machine dew point L1, another 33% of the mixed air M flows to the second surface air cooler 62 to be dry-cooled, and reaches a state point M1, the temperature and the humidity of the state point M1 are higher than those of the machine dew point L1, and then the two air flows out of the surface cooling section 6 to be secondarily mixed, the mixed air reaches a first supply state point S2, the temperature corresponding to the first supply state point S2 is higher than that corresponding to the machine dew point L1, and the humidity corresponding to the first supply state point S2 is substantially the same as the humidity corresponding to the machine dew point L1, the humiture of the air that reaches first air supply state point S2 comparatively accords with the humiture demand of the indoor constant temperature and humidity state point N (the temperature is 25 ℃ usually, and the humidity is 56% RH) of transition season, can not lead to indoor temperature to be on the low side because machine dew point L1 air supply temperature is on the low side, consequently, under this condition, the air after the secondary mixes can directly be sent to indoorly via air supply section 8, and need not to pass through the reheat of heating section 71 again, consequently, energy consumption is less, can effectively save energy.

It can be seen that, through two-layer surface cooler about setting up on same cross section, and be connected to the water inlet of second surface cooler 62 with the delivery port of first surface cooler 61 in the two-layer surface cooler, can provide the cold water of different temperatures for first surface cooler 61 and second surface cooler 62, realize the first air supply state point S2 air supply process of non-reheat in the season of transiting, because can cancel by machine dew point L1 to the heating zone 71 reheat process of first air supply state point S2, consequently, can avoid cold and hot energy waste that offsets and cause, realize energy-conserving purpose.

In the case where the air conditioner 10 includes the first surface air cooler 61 and the second surface air cooler 62, referring to fig. 1, the filter section 5 of the air conditioner 10 may include a first filter 51 and a second filter 52, the first filter 51 and the second filter 52 being disposed on the same cross section perpendicular to the first direction X and being sequentially arranged side by side along the second direction Y, the first filter 51 filtering an air flow passing through the first surface air cooler 61, and the second filter 52 filtering an air flow passing through the second surface air cooler 62.

The first filter 51 and the second filter 52 corresponding to the first surface cooler 61 and the second surface cooler 62 are arranged at the upstream of the surface cooling section 6, so that the air passing through the first surface cooler 61 and the second surface cooler 62 is relatively clean, and the normal operation of the first surface cooler 61 and the second surface cooler 62 is not influenced by impurities in the air.

To increase the flexibility of use of the air conditioner 10, referring to fig. 2, in some embodiments, the air conditioner 10 includes a first valve 63, an outlet of the first surface cooler 61 is connected to a water return line 67 and an inlet of the second surface cooler 62 through the first valve 63, and the first valve 63 controls whether communication is established between the outlet of the first surface cooler 61 and the water return line 67, and between the outlet of the first surface cooler 61 and the inlet of the second surface cooler 62.

Based on above-mentioned setting, can utilize first valve 63 to control the break-make between the delivery port of first surface cooler 61 and the water inlet of second surface cooler 62, make not only can communicate the delivery port of first surface cooler 61 and the water inlet of second surface cooler 62 in the transition season, realize the first air supply state point S2 air supply of non-reheat, can also be as required, under other conditions such as plum rain season and summer heat weather, the delivery port of first surface cooler 61 and the water inlet disconnection of second surface cooler 62, satisfy the air supply demand of other conditions such as plum rain season and summer heat weather, it is more nimble to use.

Fig. 6 exemplarily shows a flow state of the chilled water in the surface cooling section 6 in the plum rain season. In the plum rain season, the indoor cooling load is small, the humidity load is dominant, after the surface air cooler dehumidifies, the air supply temperature at the dew point L1 of the machine can cause the indoor temperature to be too low, and meanwhile, compared with the transition season, the indoor required temperature is relatively high in the plum rain season. In order to meet the indoor temperature and humidity requirements in the plum rain season, referring to fig. 6, in the plum rain season, the water inlet of the first surface air cooler 61 may be communicated with the water supply pipeline 66, the water outlet of the first surface air cooler 61 may be communicated with the water return pipeline 67, and the water inlet of the second surface air cooler 62 may be disconnected from the water supply pipeline 66 and the water outlet of the first surface air cooler 61. Thus, as shown in fig. 6, in the rainy season, no chilled water flows through the second surface air cooler 62, and the second surface air cooler 62 does not bear any heat and humidity load, in which case, the temperature and humidity of the portion of the mixed air flowing through the second surface air cooler 62 are not substantially changed when the mixed air flows through the second surface air cooler 62, so that the temperature of the portion of the mixed air flowing through the first surface air cooler 61 is increased when the mixed air is secondarily mixed with the portion of the mixed air flowing through the first surface air cooler 61, and the air at the second air supply state point S1 is obtained. Since the temperature of the air flowing out of the second surface air cooler 62, to which no chilled water is supplied at all, is relatively higher than that of the air flowing out of the second surface air cooler 62, to which no chilled water is supplied at all, in the transition season, the temperature of the air at the second supply state point S1, which is obtained by mixing, is higher than that of the air at the first supply state point S2, that is, the temperature of the air at the second supply state point S1 is higher than not only the machine dew point L1 but also the first supply state point S2.

The air supply process in the case where only the first surface cooler 61 is operated, the second surface cooler 62 does not introduce the chilled water, and any heat and humidity load is not borne may be referred to as a second state point S1 air supply process. The air supply at the second state point S1 can meet the indoor temperature and humidity requirements in the case where the humidity load is dominant, such as in the rainy season, and therefore, the air flowing out of the surface cooling section 6 can be directly sent into the room through the air supply section 8 without secondary heating through the heating section 71.

Fig. 7 exemplarily shows a specific heat dehumidification process of the air conditioner 10 in a plum rain season. Referring to fig. 7 in conjunction with fig. 3, in some embodiments, the return air N and the fresh air W are mixed in the mixing section 4, when the fresh air is mixed, the fresh air ratio is 30%, after the fresh air is mixed, 67% of the mixed air M flows to the first surface air cooler 61, is cooled and dehumidified to reach a state point L2, the temperature and humidity of the state point L2 are respectively lower than those of the machine dew point L1, another 33% of the mixed air M directly flows out of the second surface air cooler 62, is secondarily mixed with the air flowing out of the state point L2 from the first surface air cooler 61, the mixed air state reaches a second supply state point S1, the temperature of the second supply state point S1 is higher than those of the first supply state point S1 and the machine dew point L1, the humidity of the first supply state point S2 is substantially the same as those of the first supply state point S1 and the machine dew point L1, the humiture of the air that reaches second air supply state point S1 comparatively accords with the humiture demand of the indoor constant temperature and humidity state point N (the temperature is 25 ℃ usually, and the humidity is 56% RH), can not lead to indoor temperature to be low because machine dew point L1 air supply temperature is low on the one hand, consequently, under this condition, the air after the secondary mixing can directly be sent to indoorly via air supply section 8, and need not to pass through the reheat of heating section 71 again, consequently, energy consumption is less, can effectively save energy.

It can be seen that, based on the first surface air cooler 61 and the second surface air cooler 62, and the second surface air cooler 62 is not subjected to any heat and humidity load in the rainy season, the air supply process of the second air supply state point S1 without reheating in the rainy season can be realized, and the reheating process of the heating section 71 from the machine dew point L1 to the second air supply state point S1 can be cancelled, so that the energy consumption can be reduced, and the energy can be saved.

Meanwhile, only the first surface air cooler 61 cools and dehumidifies, and the second surface air cooler 62 does not bear any working mode of heat and humidity load, so that the device is not limited to be applied to plum rain seasons, and can also be applied to other conditions that the indoor heat production is smaller than that in hot days in summer, the indoor cold load is reduced, and the humidity load occupies a dominant position. The operation mode in which the air conditioner 10 blows air at the second blowing state point S1 in the rainy season and with a decrease in the amount of heat generated in the room may be referred to as a dehumidification mode.

In addition, referring to fig. 2, in some embodiments, the air conditioner 10 further includes a third valve 65 on the basis of the first valve 63, wherein the third valve 65 connects the water inlet of the second surface cooler 62 to the water supply line 66 and controls the connection and disconnection between the water inlet of the second surface cooler 62 and the water supply line 66. Also, in some embodiments, the third valve 65 controls not only the opening and closing of the water inlet of the second surface cooler 62 and the water supply line 66, but also the flow of chilled water from the water supply line 66 into the second surface cooler 62.

Based on the above setting, can utilize third valve 65 to control the break-make between the water inlet of second surface cooler 62 and the water supply pipe 66, make not only can be in the transition season, under the circumstances that plum rain season or indoor heat production volume reduce, make disconnection between the water inlet of second surface cooler 62 and the water supply pipe 66, realize the first air supply state point S2 air supply and the air supply of second air supply state point S1 of non-reheat, can also be in summer hot weather, when required cold volume is great, make the water inlet of second surface cooler 62 and water supply pipe 66 communicate, realize conventional machine dew point L1 air supply process, satisfy great cold volume demand.

In summer, when the outdoor weather is hot (the temperature is more than 35 ℃), the indoor cold load and the humidity load are both large, and an operation mode of supplying air by adopting a machine dew point L1 is required, and the operation mode is called as a maximum cold supply mode.

Fig. 4 exemplarily shows a flow state of cold feed water in the first surface cooler 61 and the second surface cooler 62 in case of hot outdoor weather in summer. Referring to fig. 4, when the weather is hot in summer, the water inlet of the first surface air cooler 61 may be communicated with the water supply pipeline 66, the water outlet of the first surface air cooler 61 and the water outlet of the second surface air cooler 62 may be communicated with the water return pipeline 67, the water outlet of the first surface air cooler 61 may be disconnected from the water inlet of the second surface air cooler 62, and the water inlet of the second surface air cooler 62 may be communicated with the water supply pipeline 66, so as to supply air at the machine dew point temperature L1. Under the condition, the first surface air cooler 61 and the second surface air cooler 62 bear heat and humidity loads, low-temperature chilled water is introduced into the second surface air cooler 62, the working state of the air conditioner 10 is consistent with that of a conventional air conditioner, and the requirement of high cooling capacity in summer on hot weather can be met.

Fig. 5 exemplarily shows a specific heat and humidity treatment process of the air conditioner 10 in summer hot weather. Referring to fig. 5 and fig. 3, in summer with hot weather, return air N and fresh air W are mixed in the mixing section 4, when the fresh air and the return air are mixed, the proportion of the fresh air is 30%, the fresh air and the return air are mixed, then flow through the surface cooling section 6, are cooled and dehumidified by the first surface air cooler 61 and the second surface air cooler 62 to a machine dew point L1, and then are directly sent to the room through the air supply section 8.

It can be seen that, based on the first surface air cooler 61, the second surface air cooler 62, the first valve 63 and the third valve 65, the air conditioner 10 can be switched among the transition season mode, the dehumidification mode and the maximum cooling capacity mode, so as to flexibly meet the indoor constant temperature and humidity requirements under different conditions, such as the transition season, the plum rain season, the indoor heat production reduction, the summer hot weather and the like.

To further increase the flexibility of use of the air conditioner 10, referring to fig. 2, in some embodiments, the air conditioner 10 includes not only the first valve 63, but also a second valve 64. The second valve 64 is disposed on a pipe between the first valve 63 and the outlet of the first surface cooler 61, and regulates the amount of water flowing through the first surface cooler 61. Thus, in each mode, the second valve 64 can be used to regulate the amount of water flowing through the first surface cooler 61, and thus, different air supply requirements can be met more flexibly.

As a further modification of the above-described embodiments, referring to fig. 1, the air conditioner 10 includes an air volume adjusting device 9, the air volume adjusting device 9 being disposed between the mixing section 4 and the surface cooling section 6 along the first direction X, the air volume adjusting device 9 adjusting a distribution amount of air flowing out from the mixing section 4 between the first surface cooler 61 and the second surface cooler 62. Specifically, as shown in fig. 1, in some embodiments, the air volume adjusting device 9 is disposed between the mixing section 4 and the filtering section 5 of the air conditioner 10 along the first direction X and includes a first air volume adjusting valve 91 and a second air volume adjusting valve 92, the first air volume adjusting valve 91 and the second air volume adjusting valve 92 are disposed on the same cross section perpendicular to the first direction X and are disposed side by side in sequence along the second direction Y, the first air volume adjusting valve 91 adjusts the air volume flowing through the first surface air cooler 61, and the second air volume adjusting valve 92 adjusts the air volume flowing through the second surface air cooler 62.

Based on air regulation device 9 that sets up, can adjust the distribution condition of mixed wind between first surface cooler 61 and second surface cooler 62 in a flexible way, adjust the dehumidification amount of wind through first surface cooler 61 and second surface cooler 62, and then satisfy the requirement to the air supply humiture in a flexible way under the different situation. For example, the air volume mixture of 67% at the first surface air cooler 61 and 33% at the second surface air cooler 62 in the transition season mode, the dehumidification mode and the maximum cooling capacity mode can be adjusted by the air volume adjusting device 9.

With continued reference to fig. 1, in some embodiments, the air conditioner 10 includes a partition 18. The partition 18 is disposed between the first surface cooler 61 and the second surface cooler 62, and in the case where the first filter 51 and the second filter 52 are respectively disposed upstream of the first surface cooler 61 and the second surface cooler 62, the partition 18 is simultaneously located between the first filter 51 and the second filter 52, specifically, the partition 18 extends from a space between the first air volume adjusting valve 91 and the second air volume adjusting valve 92 to a space between the first surface cooler 61 and the second surface cooler 62 in the first direction X. The partition 18 may be specifically a partition plate.

The provision of the partition 18 for dividing the air flowing to the first surface air cooler 61 and the second surface air cooler 62 prevents the air from mixing before flowing to the first surface air cooler 61 and the second surface air cooler 62, which is advantageous for maintaining the flow rate of the air flowing to the first surface air cooler 61 and the second surface air cooler 62 at a desired ratio, and in particular, the partition 18, in cooperation with the air volume adjusting device 9, may maintain the flow rate of the air flowing to the first surface air cooler 61 and the second surface air cooler 62 at a ratio adjusted by the air volume adjusting device 9, which facilitates the air supply process more suitable for practical needs.

In addition, in order to conveniently know the temperature and humidity conditions of various places in real time, referring to fig. 1, in some embodiments, the air conditioner 10 includes a temperature and humidity detector for detecting the temperature and humidity. For example, a first temperature and humidity detector 11, a second temperature and humidity detector 12, a third temperature and humidity detector 13, a fourth temperature and humidity detector 14, and a fifth temperature and humidity detector 15 are respectively disposed in the return air inlet 21, the fresh air inlet 41, the supply air outlet 81, the exhaust air section 3, and the mixing section 4, and detect the return air temperature and humidity, the fresh air temperature and humidity, the supply air temperature and humidity, the exhaust air temperature and humidity, and the mixed air temperature and humidity. For another example, a sixth temperature/humidity detector 16 and a seventh temperature/humidity detector 17 are respectively disposed at the first surface cooler 61 and the second surface cooler 62, and are configured to detect the temperature/humidity of the air flowing to the first surface cooler 61 and the second surface cooler 62. The detection results of the temperature and humidity detectors can be used as a regulation and control basis in the working process of the air conditioner 10, so that the temperature and humidity regulation process which is more in line with the actual requirements can be realized.

With continued reference to fig. 1, in some embodiments, the air conditioner 10 includes both the heating section 71 and the humidification section 73 in the case of including the first surface air cooler 61 and the second surface air cooler 62, where the heating section 71 and the humidification section 73 are not operated in the transition season mode, the dehumidification mode, and the maximum cooling capacity mode, but may be operated in other situations such as the winter season.

To sum up, the air conditioner 10 provided by the embodiment of the present disclosure can realize the temperature and humidity regulation process of double-surface cold-to-water temperature, can adapt to the control of indoor temperature and humidity in different environments, and meet the constant temperature and humidity regulation and control requirements in the rainy and humid seasons in spring and summer on the premise of eliminating reheating after temperature reduction, thereby achieving the purpose of energy saving.

Based on the air conditioner 10 of the foregoing embodiments, the present disclosure also provides a control method of the air conditioner 10, which includes:

in a transition season, the water inlet of the first surface air cooler 61 is communicated with the water supply pipeline 66, the water outlet of the first surface air cooler 61 and the water outlet of the second surface air cooler 62 are communicated with the water return pipeline 67, the water outlet of the first surface air cooler 61 is communicated with the water inlet of the second surface air cooler 62, so that water flowing out of the first surface air cooler 61 is partially distributed to the second surface air cooler 62, air supply at a first air supply state point S2 is achieved, and the temperature of the first air supply state point S2 is higher than the temperature of a machine dew point L1.

Also, in some embodiments, the control method further comprises:

in plum rain season, the water inlet of the first surface air cooler 61 is communicated with the water supply pipeline 66, the water outlet of the first surface air cooler 61 is communicated with the water return pipeline 67, the water inlet of the second surface air cooler 62 is connected between the water outlet of the first surface air cooler 61 and the water supply pipeline 66, air supply is achieved at a second air supply state point S1, and the temperature of the second air supply state point S1 is higher than that of the first air supply state point S2.

Additionally, in some embodiments, the control method further comprises:

in summer hot weather, the water inlet of the first surface cooler 61 is communicated with the water supply pipeline 66, the water outlet of the first surface cooler 61 and the water outlet of the second surface cooler 62 are communicated with the water return pipeline 67, the water outlet of the first surface cooler 61 is disconnected with the water inlet of the second surface cooler 62, the water inlet of the second surface cooler 62 is communicated with the water supply pipeline 66, and air supply of the machine dew point temperature L1 is achieved.

In addition, referring to fig. 10, the present disclosure also provides a controller 20, which includes a memory 201 and a processor 202 coupled to the memory, wherein the processor 202 is configured to execute the control method of the foregoing embodiments based on instructions stored in the memory 201.

For example, referring to fig. 10, in some embodiments, controller 20 includes a memory 201, a processor 202, a communication interface 203, and a bus 204. The memory 201 is used to store instructions. The processor 202 is coupled to the memory 201 and configured to execute a control method implementing the foregoing embodiments based on instructions stored by the memory 201. The memory 201, the processor 202 and the communication interface 203 are connected by a bus 204.

The memory 201 may be a high-speed RAM memory or a non-volatile memory (non-volatile memory) or the like. The memory 201 may also be a memory array. The storage 201 may also be partitioned, and the blocks may be combined into virtual volumes according to certain rules. The processor 202 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 methods of the heat pump system of the present disclosure.

Still another aspect of the present disclosure provides an air conditioning system including the air conditioner 10 of the foregoing embodiments and the controller 20 of the foregoing embodiments.

Yet another aspect of the present disclosure also provides a computer-readable storage medium. The computer readable storage medium stores computer instructions. The computer instructions are executed by the processor to perform the control method of the foregoing 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. An air conditioner (10), characterized by comprising:

the mixing section (4) is used for mixing return air and fresh air;

an air supply section (8) arranged downstream of the mixing section (4) along a first direction (X) and adapted to supply air to the room; and

surface cooling section (6), along first direction (X) arrange in mix section (4) with between air supply section (8), and include first surface cooler (61) and second surface cooler (62), first surface cooler (61) with second surface cooler (62) are arranged in the perpendicular to on the same cross-section of first direction (X), and along the perpendicular to second direction (Y) of first direction (X) arrange side by side in proper order, the water inlet of first surface cooler (61) is connected with water supply pipe (66), the delivery port of first surface cooler (61) with the delivery port of second surface cooler (62) all is connected with return water pipeline (67), just the delivery port of first surface cooler (61) with the water inlet of second surface cooler (62) is connected.

2. The air conditioner (10) according to claim 1, wherein the air conditioner (10) comprises a first valve (63), the water outlet of the first surface cooler (61) is connected with the water return line (67) and the water inlet of the second surface cooler (62) through the first valve (63), and the first valve (63) controls whether the communication between the water outlet of the first surface cooler (61) and the water return line (67) and the communication between the water outlet of the first surface cooler (61) and the water inlet of the second surface cooler (62) are established.

3. An air conditioner (10) as claimed in claim 2, characterized in that the air conditioner (10) comprises a second valve (64), the second valve (64) being arranged on a pipe between the first valve (63) and the water outlet of the first surface cooler (61) for regulating the amount of water flowing through the first surface cooler (61); and/or the air conditioner (10) comprises a third valve (65), the third valve (65) is connected with the water inlet of the second surface air cooler (62) and the water supply pipeline (66), and controls the connection and disconnection between the water inlet of the second surface air cooler (62) and the water supply pipeline (66).

4. Air conditioner (10) according to claim 1, characterized in that the mixing section (4) has a fresh air inlet (41), the first surface air cooler (61) being closer to the fresh air inlet (41) than the second surface air cooler (62) in the second direction (Y); and/or the windward area of the first surface cooler (61) is larger than the windward area of the second surface cooler (62).

5. The air conditioner (10) of claim 4, wherein the ratio of the windward area of the first surface air cooler (61) to the windward area of the second surface air cooler (62) is 55: 45.

6. the air conditioner (10) of claim 1, wherein the air conditioner (10) includes a partition (18), the partition (18) being disposed between the first surface air cooler (61) and the second surface air cooler (62) to partition air flowing to the first surface air cooler (61) and the second surface air cooler (62).

7. Air conditioner (10) according to claim 1, characterized in that the air conditioner (10) comprises a filtering section (5), the filtering section (5) being arranged between the mixing section (4) and the surface cooling section (6) along the first direction (X) and comprising a first filter (51) and a second filter (52), the first filter (51) and the second filter (52) being arranged on the same section perpendicular to the first direction (X) and being arranged side by side in sequence along the second direction (Y), the first filter (51) filtering the air flow through the first surface cooler (61), the second filter (52) filtering the air flow through the second surface cooler (62).

8. Air conditioner (10) according to any of claims 1-7, characterized in that the air conditioner (10) comprises an air volume adjusting device (9), the air volume adjusting device (9) being arranged between the mixing section (4) and the surface cooling section (6) along the first direction (X), the air volume adjusting device (9) adjusting the distribution of the air flowing out from the mixing section (4) between the first surface cooler (61) and the second surface cooler (62).

9. An air conditioner (10) according to claim 8, characterized in that the air volume adjusting device (9) comprises a first air volume adjusting valve (91) and a second air volume adjusting valve (92), the first air volume adjusting valve (91) and the second air volume adjusting valve (92) are arranged on the same cross section perpendicular to the first direction (X) and are arranged side by side in sequence along the second direction (Y), the first air volume adjusting valve (91) adjusts the air volume flowing through the first surface air cooler (61), and the second air volume adjusting valve (92) adjusts the air volume flowing through the second surface air cooler (62).

10. Air conditioner (10) according to claim 8, characterized in that said air volume regulating device (9) is arranged between said mixing section (4) and a filtering section (5) of said air conditioner (10) along said first direction (X).

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