JP7703054B2 - Air conditioners - Google Patents

Description

This disclosure relates to an air conditioner in which two blowers are arranged side by side in the width direction of the housing.

Conventionally, there is an air conditioner in which two blowers are arranged side by side in the width direction of the housing (see, for example, Patent Document 1). In the air conditioner of Patent Document 1, the inside of the housing is divided into a heat exchange chamber in which a heat exchanger is housed and an air blowing chamber in which the blower is housed, and a diffuser section that extends to the heat exchanger is provided in the blowing section of the blower. Air is sucked into the housing through an intake port formed on the air blowing chamber side of the housing, blown out from the blowing section of the blower, passes through the diffuser section and the heat exchanger, and is then discharged outside the housing through an outlet formed on the heat exchange chamber side of the housing.

The diffuser section is also designed to diffuse the air flow in the width direction, thereby achieving a uniform wind speed distribution in the width direction relative to the heat exchanger.

JP 2010-117110 A

However, in Patent Document 1, only a motor connected to the two blowers by a double shaft is provided between them, and if the distance between the two blowers is short, the air sucked in from the inlets of the two blowers interferes with each other, causing uneven loads on the two blowers. In addition, in Patent Document 1, a diffuser is provided at the blower section of the blower, and the diffuser is formed to diffuse the air flow in the width direction, so that the air blown out from the blower section of one blower passes through the diffuser section and then interferes with the air blown out from the blower section of the other blower and passes through the diffuser section, and the air blown out from the blower sections of the two blowers interfere with each other, causing increased blowing resistance. If the load on the two blowers becomes uneven or the blowing resistance increases, there is a problem that the operating efficiency decreases and the aerodynamic performance decreases.

The present disclosure has been made to solve the above-mentioned problems, and aims to provide an air conditioner that suppresses the decrease in operating efficiency that occurs due to uneven load on the two blowers and increased airflow resistance.

The air conditioner of the present disclosure comprises a housing having an intake port and two exhaust ports, two blowers arranged side by side inside the housing in the width direction and blowing air drawn in through the intake port out of a different one of the two exhaust ports, a partition plate provided between the two blowers, and an air guide plate provided on each edge of the two exhaust ports and protruding to the outside of the housing, wherein the two air guide plates are arranged to be located between the two exhaust ports and are arranged so that each of them forms an angle of 90° or less with respect to the opening plane of the exhaust port and are arranged so that each fits within the width of the exhaust port in the width direction .

According to the air conditioner of the present disclosure, since a partition plate is provided between the two blowers, even if the distance between the two blowers is close, it is possible to prevent the air sucked from the blowers from interfering with each other and causing the load on the two blowers to become uneven. In addition, two air guide plates are provided on the edges of the two air outlets, and the two air guide plates are provided so as to be located between the two air outlets and to be arranged so that the angle with respect to the opening surface of the air outlet on which each is provided is 90° or less. Therefore, the flow of air blown out from the air outlet is prevented from being diffused in the width direction, and the increase in the blowing resistance can be prevented. As a result, the load on the two blowers is prevented from becoming uneven and the blowing resistance is prevented from becoming large, so that a decrease in operating efficiency can be prevented.

1 is a front perspective view showing an air conditioner according to a first embodiment. FIG. FIG. 2 is a front perspective view of the air conditioner shown in FIG. 1 with a front panel removed. FIG. 2 is a front view showing the internal structure of an upper portion of the air conditioner according to the first embodiment. FIG. 4 is a front view of the blower shown in FIG. 3 with a fan casing removed. 2 is a schematic front view showing the flow of air within a housing of the air conditioner according to the first embodiment. FIG. 2 is an enlarged front perspective view of an upper structure of the air conditioner according to the first embodiment. FIG. 5A to 5C are diagrams illustrating the sizes of partition plates of the air conditioner according to the first embodiment. 5 is a diagram illustrating the position of the lower end of the partition plate of the air conditioner according to the first embodiment. FIG. 5A to 5C are diagrams illustrating the angle of the air guide plate of the air conditioner according to the first embodiment. 5 is a diagram illustrating the size of an air guide plate of the air conditioner according to the first embodiment. FIG. 5 is a diagram showing a control flow of the air guide plate performed by the control device during operation of the air conditioner according to the first embodiment. FIG. 13 is a diagram showing a control flow of the air guide plate performed by the control device when the operation of the air conditioner according to the second embodiment is stopped. FIG. 13 is a diagram showing a modified example of the control flow for the air guide plate performed by the control device during operation of the air conditioner according to the second embodiment. FIG.

The air conditioner 100 according to the embodiment will be described below with reference to the drawings. Note that the present disclosure is not limited to the embodiment described below. In addition, the size relationship of each component in the following drawings may differ from the actual one. In addition, in the following description, terms indicating directions (e.g., "up", "down", "right", "left", "front", "rear", etc.) are used as appropriate to facilitate understanding, but these terms are for the purpose of explanation and do not limit the present disclosure. Unless otherwise specified, these directional terms refer to the direction when the air conditioner 100 is viewed from the front. In addition, in each figure, items with the same reference numerals are the same or equivalent, and this is common throughout the entire specification.

Embodiment 1.
Fig. 1 is a front perspective view showing an air conditioner 100 according to embodiment 1. Fig. 2 is a front perspective view showing a state in which a front panel 2 is removed from the air conditioner 100 shown in Fig. 1. Fig. 3 is a front view showing the internal structure of an upper part of the air conditioner 100 according to embodiment 1. Fig. 4 is a front view showing a state in which fan casings 50a, 50b are removed from the blowers 5a, 5b shown in Fig. 3.

As shown in Figs. 1 and 2, the air conditioner 100 according to the first embodiment is, for example, a floor-standing type, and supplies conditioned air to an indoor space through a duct 60 (see Fig. 5 described later). The air conditioner 100 has a housing 1 that constitutes an outer shell, and a front plate 2 is provided on the front side of the housing 1. Inside the housing 1, two blowers 5a, 5b, a heat exchanger 6, a drain pan 7 that collects condensed water from the heat exchanger 6, and a control box 8 that houses the control device 30 are provided. The front plate 2 of the housing 1 is formed with an intake port 20 that takes in air into the inside of the housing 1. In addition, the upper surface 4 of the housing 1 is formed with air outlets 40a, 40b that blow air out to the outside of the housing 1. Inside the housing 1, an air passage is formed from the intake port 20 to the air outlets 40a, 40b. In addition, on one side (hereinafter referred to as the edge) of the peripheral portion of the air outlets 40a, 40b formed on the upper surface 4 of the housing 1, air guide plates 11a, 11b are provided which protrude outward from the housing 1, i.e. upward. The air guide plates 11a, 11b are provided on the edge of the air outlet 40a on the air outlet 40b side and the edge of the air outlet 40b on the air outlet 40a side, respectively. In other words, the two air guide plates 11a, 11b are provided so as to be positioned between the two air outlets 40a, 40b. Details of the air guide plates 11a, 11b will be described later.

The heat exchanger 6 is disposed on the rear side of the intake port 20 when viewed from the side where the front panel 2 of the housing 1 is disposed. The heat exchanger 6 is also disposed at an angle inside the housing 1.

The two blowers 5a and 5b are arranged inside the housing 1 above the heat exchanger 6 and below the air outlets 40a and 40b. The two blowers 5a and 5b are arranged side by side in the left-right direction (width direction). As shown in Figs. 3 and 4, the two blowers 5a and 5b are provided with fans 51a and 51b and fan casings 50a and 50b that cover the periphery of the fans 51a and 51b and are fixed to the upper surface 4 of the housing 1. Here, the fans 51a and 51b are composed of sirocco fans. The fans 51a and 51b of the two blowers 5a and 5b are connected to motors 9a and 9b, respectively. The fans 51a and 51b are driven by inverter control of the motors 9a and 9b. In the first embodiment, the motors 9a and 9b are respectively connected to the fans 51a and 51b of the two blowers 5a and 5b. However, this is not limited to this, and the same motor may be connected to the fans 51a and 51b of the two blowers 5a and 5b.

As shown in Figure 2, the drain pan 7 is positioned so as to collect moisture flowing down below the heat exchanger 6, which is arranged at an angle inside the housing 1.

The control device 30 is composed, for example, of dedicated hardware or a CPU (Central Processing Unit, also called a central processing unit, processing device, arithmetic unit, microprocessor, or processor) that executes a program stored in a memory unit (not shown).

When the control device 30 is a dedicated hardware, the control device 30 is, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination of these. Each of the functional units realized by the control device 30 may be realized by separate hardware, or each functional unit may be realized by a single piece of hardware.

When the control device 30 is a CPU, each function executed by the control device 30 is realized by software, firmware, or a combination of software and firmware. The software and firmware are written as programs and stored in a memory unit. The CPU realizes each function of the control device 30 by reading and executing the programs stored in the memory unit. Here, the memory unit stores various information, and includes, for example, a non-volatile semiconductor memory that allows data to be rewritten, such as a flash memory, an EPROM, and an EEPROM.

In addition, some of the functions of the control device 30 may be realized by dedicated hardware and some by software or firmware.

The control device 30 controls the fans 5a, 5b, etc. based on detection signals from various sensors (not shown) provided in the air conditioner 100 and operation signals from an operation unit (not shown), and controls the operation of the entire air conditioner 100.

Figure 5 is a schematic front view showing the air flow within the housing 1 of the air conditioner 100 according to embodiment 1. Note that the arrows in Figure 5 indicate the air flow.

As shown in Figure 5, air that flows into the housing 1 from the intake port 20 passes through the heat exchanger 6 to be conditioned, then branches while flowing upward and is sucked into the fan casings 50a, 50b of the blowers 5a, 5b. The conditioned air sucked into the fan casings 50a, 50b of the blowers 5a, 5b is blown out from the air outlets 40a, 40b formed on the top surface 4 of the housing 1, respectively, and supplied to the indoor space via the duct 60.

Figure 6 is an enlarged front oblique view of the upper structure of the air conditioner 100 according to embodiment 1. Figure 7 is a diagram explaining the size of the partition plate 10 of the air conditioner 100 according to embodiment 1. Figure 8 is a diagram explaining the position of the lower end of the partition plate 10 of the air conditioner 100 according to embodiment 1. Note that Figures 6 to 8 show the air conditioner 100 with the front plate 2 removed. Also, some parts have been omitted from Figures 7 and 8 to make the explanation easier to understand.

As shown in FIG. 6, a rectangular partition plate 10 is provided between the two blowers 5a and 5b installed in the left-right direction. In this way, by providing the partition plate 10 between the two blowers 5a and 5b, even if the distance between the two blowers 5a and 5b is close, the blowers 5a and 5b are prevented from competing with each other for the air flowing from the intake ports 20 below the blowers 5a and 5b (see part B in FIG. 5). Therefore, it is possible to prevent the air sucked in from the intake ports 52a and 52b of the blowers 5a and 5b from interfering with each other and causing the load on the two blowers 5a and 5b to become uneven. As a result, it is possible to prevent a decrease in operating efficiency due to a current value imbalance between the two blowers 5a and 5b, and to prevent a decrease in aerodynamic performance caused by a decrease in operating efficiency.

7, the width H1 in the height direction (vertical direction) of the partition plate 10 is larger than the diameter H2 of the suction ports 52a, 52b of the blowers 5a, 5b shown by the dashed lines. The width W1 in the depth direction (front-rear direction) of the partition plate 10 is larger than the width W2 in the depth direction of the suction ports 52a, 52b of the blowers 5a, 5b shown by the dashed lines. In this way, by making the area of the partition plate 10 larger than the opening area of the suction ports 52a, 52b of the blowers 5a, 5b, the blowers 5a, 5b are further prevented from competing with each other for the air that has flowed into the blowers 5a, 5b from the suction ports 20 below the blowers 5a, 5b. Therefore, the effect of preventing the air sucked in from the suction ports 52a, 52b of the blowers 5a, 5b from interfering with each other and causing uneven loads on the two blowers 5a, 5b can be improved. As a result, the effect of suppressing the decrease in operating efficiency can be improved, and the effect of suppressing the decrease in aerodynamic performance caused by the decrease in operating efficiency can be improved.

Furthermore, the partition plate 10 is provided so that its end on the suction port 20 side is located closer to the suction port 20 side than the end on the suction port 20 side of the suction ports 52a, 52b of the blowers 5a, 5b. That is, as shown in FIG. 8, the partition plate 10 is provided so that its lower end L1 is located lower than the lower end L2 of the suction ports 52a, 52b of the blowers 5a, 5b. In this way, by providing the partition plate 10 so that its lower end L1 is located closer to the suction port 20 side of the housing 1 than the lower end L2 of the suction ports 52a, 52b of the blowers 5a, 5b, the blowers 5a, 5b are further prevented from competing with each other for the air that has flowed into the blowers 5a, 5b from the suction ports 20 below the blowers 5a, 5b. This further enhances the effect of suppressing uneven loads on the two fans 5a, 5b caused by interference between the air sucked through the suction ports 52a, 52b of the fans 5a, 5b, and as a result, the effect of suppressing a decrease in operating efficiency can be further enhanced, and the effect of suppressing a decrease in aerodynamic performance caused by a decrease in operating efficiency can be further enhanced.

Figure 9 is a diagram explaining the angle of the air guide plate 11 of the air conditioner 100 according to embodiment 1. Figure 10 is a diagram explaining the size of the air guide plate 11 of the air conditioner 100 according to embodiment 1. Note that Figures 9 and 10 show the state in which the front plate 2 has been removed from the air conditioner 100. Also, in Figure 9, some parts are omitted for ease of understanding. Also, in Figure 9, different angles are shown for the air guide plate 11a and the air guide plate 11b, but this is for the purpose of explanation. The air guide plate 11a and the air guide plate 11b may be at the same angle or at different angles.

As shown in FIG. 9, the air guide plates 11a and 11b are provided so that the angle θ of the upper surface 4 of the housing 1 with respect to the opening surface of the air outlets 40a and 40b is 90° or less. In detail, the upper surfaces 11a1 and 11b1 (see FIG. 6) of the air guide plates 11a and 11b are provided so that the angle θ of the upper surfaces 11a1 and 11b1 of the air guide plates 11a and 11b with respect to the opening surface of the air outlets 40a and 40b is 90° or less. As shown in FIG. 6, the upper surfaces 11a1 and 11b1 of the air guide plates 11a and 11b have a rectangular shape, but are not limited thereto. Furthermore, the air guide plates 11a and 11b are provided with any length that fits within the projection plane X above the air outlets 40a and 40b when viewed from the front. Here, the width of the projection plane X in the left-right direction is the same as the width of the air outlets 40a and 40b in the left-right direction. In other words, the air guide plates 11a, 11b are provided so as to fall within the left-right widths of the air outlets 40a, 40b in which they are provided, respectively.

By providing the air guide plates 11a and 11b in this manner, the air flow blown out from the air outlets 40a and 40b (see part A in FIG. 5) is prevented from diffusing in the width direction, and the air flow resistance is prevented from increasing. If the air guide plates 11a and 11b are provided in at least a portion of the width of the air outlets 40a and 40b in the left-right direction, the effect of suppressing the diffusion of the blown air can be obtained. Therefore, even if the air guide plates 11a and 11b are provided so that they do not fit within the left-right width of the air outlets 40a and 40b in which they are provided, the effect of suppressing the air flow blown out from the air outlets 40a and 40b from diffusing in the width direction does not change much. Therefore, by providing the air guide plates 11a and 11b so that they fit within the left-right width of the air outlets 40a and 40b in which they are provided, it is not necessary to provide the air guide plates 11a and 11b unnecessarily long.

In addition, when the angle θ of the air guide plates 11a and 11b becomes small, the air flow resistance caused by the air guide plates 11a and 11b blocking the air blown out from the air outlets 40a and 40b increases, so the angle θ of the air guide plates 11a and 11b is preferably 30° or more. As shown in FIG. 10, the width W3 in the depth direction of the air guide plates 11a and 11b is smaller than the width W4 in the depth direction of the connection part of the duct 60 provided on the upper surface 4 of the housing 1. In other words, the length in the longitudinal direction of the air guide plates 11a and 11b is smaller than the connection part of the duct 60. This is to enable the duct 60 to be connected to the upper surface 4 of the housing 1 so as to cover the air outlets 40a and 40b. In addition, the width W3 in the depth direction of the air guide plates 11a and 11b is made larger than the width W5 in the depth direction of the air outlets 40a and 40b. In other words, the length of the air guide plates 11a, 11b in the longitudinal direction is made larger than the length of the edges of the air outlets 40a, 40b. This further suppresses the air flow blown out from the air outlets 40a, 40b from diffusing in the width direction, thereby enhancing the effect of suppressing the increase in air flow resistance.

As described above, the air conditioner 100 according to the first embodiment comprises a housing 1 having an intake port 20 and two exhaust ports 40a, 40b, two blowers 5a, 5b arranged side by side inside the housing 1 in the width direction and blowing air drawn in from the intake port 20 out of one of the two exhaust ports 40a, 40b, a partition plate 10 provided between the two blowers 5a, 5b, and air guide plates 11a, 11b provided on the edges of each of the two exhaust ports 40a, 40b and protruding to the outside of the housing 1, the two air guide plates 11a, 11b being arranged so as to be positioned between the two exhaust ports 40a, 40b, and so that the angle θ relative to the opening plane of the exhaust ports 40a, 40b at which they are provided is 90° or less.

According to the air conditioner 100 of the first embodiment, a partition plate 10 is provided between the two blowers 5a and 5b. Therefore, even if the distance between the two blowers 5a and 5b is close, it is possible to prevent the air sucked from the blowers 5a and 5b from interfering with each other and causing the load on the two blowers 5a and 5b to become uneven. In addition, two air guide plates 11a and 11b are provided on the edges of the two air outlets 40a and 40b, and the two air guide plates 11a and 11b are provided so as to be located between the two air outlets 40a and 40b, and are provided so that the angle θ with respect to the opening plane of the air outlets 40a and 40b at which they are provided is 90° or less. Therefore, the flow of air blown out from the air outlets 40a and 40b is prevented from being diffused in the width direction, and the blowing resistance can be prevented from increasing. As a result, uneven loads on the two fans 5a, 5b and increased blowing resistance are prevented, so that a decrease in operating efficiency can be suppressed.

In addition, in the air conditioner 100 according to embodiment 1, the two air guide plates 11a, 11b are arranged so as to fall within the width direction of the air outlets 40a, 40b in which they are respectively arranged.

According to the air conditioner 100 of embodiment 1, there is no need to make the air guide plates 11a, 11b unnecessarily long.

Furthermore, in the air conditioner 100 of embodiment 1, the area of the partition plate 10 is larger than the opening area of the intake ports 52a, 52b of the two blowers 5a, 5b.

According to the air conditioner 100 of the first embodiment, the blowers 5a and 5b are further prevented from competing with each other for the air flowing from the intake port 20 to the blowers 5a and 5b. Therefore, it is possible to enhance the effect of suppressing the air drawn from the intake ports 52a and 52b of the blowers 5a and 5b from interfering with each other and causing the load on the two blowers 5a and 5b to become uneven. As a result, it is possible to enhance the effect of suppressing the decrease in operating efficiency, and to enhance the effect of suppressing the decrease in aerodynamic performance caused by the decrease in operating efficiency.

Furthermore, in the air conditioner 100 according to embodiment 1, the end portion of the partition plate 10 on the suction port 20 side is positioned closer to the suction port 20 than the ends of the suction ports 52a, 52b of the two blowers 5a, 5b on the suction port 20 side.

According to the air conditioner 100 of the first embodiment, the blowers 5a and 5b are further prevented from competing with each other for the air flowing from the intake port 20 to the blowers 5a and 5b. Therefore, the effect of preventing the air drawn from the intake ports 52a and 52b of the blowers 5a and 5b from interfering with each other and causing uneven loads on the two blowers 5a and 5b can be further improved. As a result, the effect of preventing a decrease in operating efficiency can be further improved, and the effect of preventing a decrease in aerodynamic performance caused by a decrease in operating efficiency can be further improved.

In addition, in the air conditioner 100 according to embodiment 1, the two air guide plates 11a, 11b have a rectangular shape and are arranged so that their longitudinal direction runs along the respective edges of the two air outlets 40a, 40b, and are greater in length in the longitudinal direction than the respective edges of the two air outlets 40a, 40b.

According to the air conditioner 100 of embodiment 1, the air flow blown out from the air outlets 40a, 40b is further prevented from diffusing in the width direction, thereby enhancing the effect of preventing an increase in air flow resistance.

Embodiment 2.
Hereinafter, the second embodiment will be described, but explanations of parts that overlap with the first embodiment will be omitted, and parts that are the same as or equivalent to the first embodiment will be given the same reference numerals.

In the air conditioner 100 according to the first embodiment, the angle θ of the air guide plates 11a and 11b is set to be 90° or less, and the angle θ is constant. In contrast, in the air conditioner 100 according to the second embodiment, the angle θ of the air guide plates 11a and 11b is set to be variable at an angle of 90° or less. Therefore, in the second embodiment, a motor for the air guide plate (not shown) that is connected to each of the two air guide plates 11a and 11b and rotates them is provided separately from the motors 9a and 9b. In the second embodiment, the motor for the air guide plate is connected to each of the two air guide plates 11a and 11b, but this is not limited thereto, and the same motor for the air guide plate may be connected to the two air guide plates 11a and 11b. However, in the second embodiment, the motors 9a and 9b are connected to the fans 51a and 51b of the two blowers 5a and 5b, respectively.

The control device 30 detects the loads of the motors 9a and 9b that drive the fans 51a and 51b of the blowers 5a and 5b. Here, the method of detecting the loads of the motors 9a and 9b may be, for example, a method of detecting the current value input to the motors 9a and 9b using a current sensor, but is not limited thereto, and other methods such as detecting the power consumption of the motors 9a and 9b may also be used. Then, when the difference ΔL between the load of the motor 9a and the load of the motor 9b exceeds a first threshold value Th1 set in advance, the control device 30 rotates the air guide plates 11a and 11b so that the angle θ of the air guide plates 11a and 11b is reduced by a first angle θ1 set in advance. Here, ΔL is an absolute value.

In addition, when the difference ΔL between the load of the motor 9a and the load of the motor 9b is equal to or less than the second threshold value Th2 (<Th1) set in advance, the control device 30 rotates the air guide plates 11a and 11b so that the angle θ of the air guide plates 11a and 11b is increased by the second angle θ2 set in advance. Here, the first angle θ1 and the second angle θ2 may be the same value or different values. In this way, the loads of the two motors 9a and 9b are detected, and the angle θ of the air guide plates 11a and 11b is controlled according to the difference ΔL between the load of the motor 9a and the load of the motor 9b. By doing so, it is possible to suppress uneven loads on the two blowers 5a and 5b, suppress a decrease in operating efficiency caused by a current value imbalance between the two blowers 5a and 5b, and suppress a decrease in aerodynamic performance caused by a decrease in operating efficiency.

In the second embodiment, a restricting structure is provided to prevent the angle θ of the air guide plates 11a and 11b from exceeding 90°. The restricting structure is, for example, a stopper provided at a position where the air guide plates 11a and 11b collide when the angle θ is 90°.

FIG. 11 is a diagram showing a control flow of the air guide plates 11a and 11b performed by the control device 30 when the air conditioner 100 according to the first embodiment is in operation.
The control flow of the air guide plates 11a, 11b when the air conditioner 100 is in operation will be described below with reference to Fig. 11. When the air conditioner 100 starts to operate, or when the air volume setting is changed, the process proceeds to step S101.

(Step S101)
The control device 30 detects the loads of the two motors 9a and 9b and determines whether the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than a first threshold value Th1 set in advance. If the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than the first threshold value Th1 (YES), the process proceeds to step S102. On the other hand, if the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is not greater than the first threshold value Th1 (NO), the process repeats step S101.

(Step S102)
The control device 30 rotates the air guide plates 11a and 11b so that the angle θ of the air guide plates 11a and 11b becomes smaller by a preset first angle θ1.

(Step S103)
The control device 30 detects the loads of the two motors 9a and 9b, and determines whether the difference ΔL between the load of the motor 9a and the load of the motor 9b is smaller than a preset second threshold value Th2. If the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is smaller than the second threshold value Th2 (YES), the process proceeds to step S104. On the other hand, if the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is not smaller than the second threshold value Th2 (NO), the process returns to step S102.

(Step S104)
The control device 30 maintains the angle θ of the air guide plates 11a and 11b. In other words, no processing is performed.

(Step S105)
The control device 30 detects the loads of the two motors 9a and 9b and determines whether the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than the first threshold value Th1. If the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than the first threshold value Th1 (YES), the process returns to step S102. On the other hand, if the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is not greater than the first threshold value Th1 (NO), the process proceeds to step S106.

Note that step S105 is a process that assumes a case where the difference ΔL between the load of motor 9a and the load of motor 9b fluctuates due to an external factor. With this process, even if the difference ΔL between the load of motor 9a and the load of motor 9b becomes larger than the first threshold value Th1 due to an external factor, the process can be returned to step S102, and the process (steps S102 to S103) of reducing the difference ΔL between the load of motor 9a and the load of motor 9b can be performed again.

(Step S106)
The control device 30 detects the loads of the two motors 9a and 9b, and determines whether or not a state in which the difference ΔL between the load of the motor 9a and the load of the motor 9b is smaller than the second threshold value Th2 has continued for a preset fixed time T1 or more. If the control device 30 determines that the state in which the difference ΔL between the load of the motor 9a and the load of the motor 9b is smaller than the second threshold value Th2 has continued for a fixed time T1 or more (YES), the process proceeds to step S107. On the other hand, if the control device 30 determines that the state in which the difference ΔL between the load of the motor 9a and the load of the motor 9b is smaller than the second threshold value Th2 has not continued for a fixed time T1 or more (NO), the process returns to step S104.

(Step S107)
The control device 30 rotates the air guide plates 11a and 11b so that the angle θ of the air guide plates 11a and 11b becomes larger by a preset second angle θ2.

(Step S108)
The control device 30 detects the loads of the two motors 9a and 9b and determines whether the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than the second threshold value Th2. If the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than the second threshold value Th2 (YES), the process returns to step S101. On the other hand, if the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is not greater than the second threshold value Th2 (NO), the process returns to step S107.

FIG. 12 is a diagram showing a control flow of the air guide plates 11a, 11b performed by the controller 30 when the operation of the air conditioner 100 according to the first embodiment is stopped.
The control flow of the air guide plates 11a, 11b when the operation of the air conditioner 100 is stopped will be described below with reference to Fig. 12. When the operation of the air conditioner 100 is stopped, the process proceeds to step S201.

(Step S201)
The control device 30 rotates the air guide plates 11a and 11b so that the angle θ of the air guide plates 11a and 11b becomes 90°.

This ensures that the air guide plates 11a and 11b are always in the same position after the air conditioner 100 resumes operation.

FIG. 13 is a diagram showing a modified example of the control flow for the air guide plates 11a and 11b performed by the controller 30 during operation of the air conditioner 100 according to the first embodiment.
The control flow of the air guide plates 11a and 11b during operation of the air conditioner 100 may be a simpler control flow than the control flow shown in Fig. 11, as shown in Fig. 13. In other words, when the control device 30 determines that the difference ΔL between the load of the motor 9a and the load of the motor 9b is greater than the first threshold value Th1, the control device 30 may only perform processing to reduce the angle θ of the air guide plates 11a and 11b until the difference ΔL becomes smaller than the second threshold value Th2.

As described above, the air conditioner 100 according to embodiment 2 includes motors 9a and 9b which drive the two blowers 5a and 5b, respectively, and a control device 30 which rotates the two air guide plates 11a and 11b in accordance with the load difference ΔL between the two motors 9a and 9b.

According to the air conditioner 100 of the second embodiment, the two air guide plates 11a, 11b are rotated according to the difference in load ΔL between the two motors 9a, 9b. This prevents the loads of the two blowers 5a, 5b from becoming uneven, and suppresses a decrease in operating efficiency caused by a current imbalance between the two blowers 5a, 5b, thereby suppressing a decrease in aerodynamic performance caused by a decrease in operating efficiency.

1 housing, 2 front plate, 4 (housing) upper surface, 5a blower, 5b blower, 6 heat exchanger, 7 drain pan, 8 control box, 9a motor, 9b motor, 10 partition plate, 11 air guide plate, 11a air guide plate, 11a1 (air guide plate) upper surface, 11b air guide plate, 11b1 (air guide plate) upper surface, 20 intake port, 30 control device, 40a outlet, 40b outlet, 50a fan casing, 50b fan casing, 51a fan, 51b fan, 52a intake port, 52b intake port, 60 duct, 100 air conditioner.

Claims (9)

A housing having an intake port and two exhaust ports;
Two fans arranged side by side in a width direction inside the housing and configured to blow air drawn in through the intake port out of different ones of the two exhaust ports;
A partition plate provided between the two blowers;
a wind guide plate provided on each edge of the two air outlets and protruding outward from the housing;
The two air guide plates are
The air outlets are provided between the two air outlets, and are provided such that the angle of each of the air outlets with respect to the opening plane of the air outlet is 90° or less ,
Each of the air outlets is provided so as to be within the width of the air outlet in the width direction.
Air conditioner. A housing having an intake port and two exhaust ports;
Two fans arranged side by side in a width direction inside the housing and configured to blow air drawn in through the intake port out of different ones of the two exhaust ports;
A partition plate provided between the two blowers;
a wind guide plate provided on each edge of the two air outlets and protruding outward from the housing;
The two air guide plates are
The air outlets are provided between the two air outlets, and are provided such that the angle of each of the air outlets with respect to the opening plane of the air outlet is 90° or less,
The two air guide plates have a rectangular shape, and are provided so that the longitudinal direction thereof is along the edges of the two air outlets, and the length in the longitudinal direction is greater than the length of the edges of the two air outlets.
Air conditioner. A housing having an intake port and two exhaust ports;
Two fans arranged side by side in a width direction inside the housing and configured to blow air drawn in through the intake port out of different ones of the two exhaust ports;
A partition plate provided between the two blowers;
a wind guide plate provided on each edge of the two air outlets and protruding outward from the housing;
The two air guide plates are
The air outlets are provided between the two air outlets, and are provided such that the angle of each of the air outlets with respect to the opening plane of the air outlet is 90° or less,
A motor for driving each of the two blowers;
a control device that rotates the two air guide plates in accordance with a difference in load between the two motors. The control device includes:
The air conditioner according to claim 3, wherein when a difference in load between the two motors exceeds a preset first threshold, the two air guide plates are rotated so that the angles of the two air guide plates become smaller by a preset first angle. The control device includes:
The air conditioner according to claim 4, wherein the two air guide plates are rotated such that the angles of the two air guide plates become smaller than the first angle until a difference in load between the two motors becomes smaller than a preset second threshold value that is smaller than the first threshold value. The control device includes:
6. The air conditioner according to claim 5, wherein, when a state in which a difference in load between the two motors is smaller than the second threshold value continues for a predetermined period of time or longer, the two air guide plates are rotated so that the angles of the two air guide plates become larger by a predetermined second angle. The control device includes:
The air conditioner according to claim 6, wherein the two baffle plates are rotated such that the angles of the two baffle plates become larger by the second angle until a difference in load between the two motors becomes larger than the second threshold value. The air conditioner according to any one of claims 1 to 7 , wherein an area of the partition plate is larger than an opening area of the intake ports of the two fans. The air conditioner according to claim 8 , wherein an end portion of the partition plate on the suction port side is located closer to the suction port side than end portions of the suction ports of the two blowers on the suction port side.

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