JP2008275193A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner capable of suppressing the surging phenomenon and improving energy consuming efficiency by applying a constitution capable of changing a volume of a ventilation flue according to operating conditions such as a cooling operation and a heating operation. <P>SOLUTION: This air conditioner comprises an impeller 5, a scroll portion for guiding the air to a back face of the impeller 5, and a cross-flow fan 4 disposed at a downstream side of the impeller 5 in a state of being opposed to the scroll portion 7, and having a stabilizer 8 partitioning a suction opening 2a and a supply opening 11, and the ventilation flue 10 is composed of the scroll portion 7A, the stabilizer 8 and side wall plates 9 disposed at both sides in the axial direction of the impeller. A ventilation flue cross-section changing mechanism 15 is disposed to reduce an area of the axial both sides or axial central portion of the impeller 5 in a cross-section of the ventilation flue at a supply opening 11 side of the impeller 5 in the cooling operation with respect to the heating operation. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an air conditioner including a cross flow fan.

  In a conventional air conditioner, an indoor heat exchanger is arranged in parallel with the cross flow fan upstream of the cross flow fan, and a casing front plate for partitioning the inlet and the outlet is provided at the lower part of the indoor heat exchanger. An air passage is constituted by the casing front plate, the indoor heat exchanger, and the casing rear plate for guiding air to the back of the cross flow fan. And the bottom part of the casing rear plate is formed so that the height in the vicinity of both ends is lower than the height in the vicinity of the central part in the front view of the outlet (see, for example, Patent Document 1).

  In a conventional air conditioner, especially during cooling operation, the heat exchanger gets wet and the air passage area decreases and the pressure loss increases, so at both ends of the air outlet where the air velocity is slow, the air conditioner External air easily flows into the interior, and surging phenomenon is likely to occur. When the surging phenomenon occurs during the cooling operation, dew condensation occurs inside the air outlet and the air conditioner, and dew drops from the air conditioner, which causes a problem. Therefore, in general, in the conventional air conditioner having the above-described configuration, the dynamic pressure at both ends of the air outlet is increased by forming a casing front plate so as to cover a part of both ends of the air outlet. This suppresses the occurrence of the surging phenomenon.

JP-A-9-229403

  In a conventional air conditioner, the casing front plate that covers part of both ends of the air outlet is fixed to both ends of the air outlet, so that the dynamic pressure at both ends of the air outlet causes a surging phenomenon. Not only during easy cooling operation, but also during heating operation, there is a problem that it is operated while being increased and extra power is consumed.

  The present invention has been made to solve the above-described problems, and suppresses the occurrence of surging phenomenon by adopting a configuration in which the volume of the ventilation path can be changed according to operating conditions such as cooling operation and heating operation. In addition, an object is to obtain an air conditioner that improves energy consumption efficiency.

  An air conditioner according to the present invention includes an impeller, a scroll portion that guides air to the back surface of the impeller, and a stabilizer that is disposed relative to the scroll portion on the downstream side of the impeller, and partitions the inlet and the outlet. A scroll portion and a stabilizer that are provided with a cross flow fan and that have a ventilation path composed of a scroll portion, a stabilizer, and side wall plates arranged on both sides in the axial direction of the impeller, and that constitute the ventilation path according to the operating conditions. And a ventilation path cross-section changing mechanism that changes the volume of the ventilation path by displacing the at least one wall surface of the side wall plate to the ventilation path side or the opposite side of the ventilation path.

  According to the present invention, the ventilation path cross-section changing mechanism displaces the wall surface configuring the ventilation path so as to have the volume of the ventilation path according to the operating conditions such as cooling operation and heating operation, thereby suppressing the occurrence of the surging phenomenon. In addition, an object is to obtain an air conditioner that improves energy consumption efficiency.

The best mode for carrying out the present invention will be described below with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a side cross-sectional view during cooling operation of an air conditioner according to Embodiment 1 of the present invention, and FIG. 2 is a perspective view of a scroll unit during cooling operation of the air conditioner according to Embodiment 1 of the present invention. 3 is a perspective view of the scroll portion during heating operation of the air conditioner according to Embodiment 1 of the present invention, FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 1, and FIG. FIG. 6 is a cross-sectional view of the blown airflow in the air conditioner according to Embodiment 1 of the present invention, and FIG. 6 is a cross-sectional view when the air conditioner is switched from the cooling operation to the heating operation.

  In FIG. 1, an air conditioner 1A includes a design panel 2 having a suction port 2a, a heat exchanger 3, a cross flow fan 4 including an impeller 5 and a diffuser 6, a side wall plate 9, and a ventilation path cross-section changing mechanism 15. Have. Further, the diffuser 6 includes a scroll portion 7A and a stabilizer 8.

  The scroll portion 7A includes a rectangular flat plate-like rear wall 7a, a bottom wall 7b projecting vertically from one side of the long side of the back wall 7a, a tip of the bottom wall 7b, and a long side of the back wall 7a. It has a guide wall 7c that connects the sides. As shown in FIGS. 2 and 3, the scroll portion 7A is formed in a hollow body in which openings formed by the back wall 7a, the bottom wall 7b, and the guide wall 7c are closed. Moreover, the guide wall 7c is formed of a flexible member. The scroll portion 7A is arranged with one long side at the lower end and horizontally. Hereinafter, the length direction of the long side of the back wall 7a is defined as the width direction.

  The design panel 2 projects in an arch shape from the other side of the long side of the back wall 7a toward the front of the tip of the bottom wall 7b. The stabilizer 8 is disposed so as to protrude in detail from the tip of the design panel 2 protruding from the scroll portion 7A in the direction of the impeller 5 described later, and is disposed at a position facing the scroll portion 7A. Side wall plates 9 are attached so as to cover the openings on both sides in the width direction formed by the scroll portion 7 </ b> A and the design panel 2.

  The suction port 2a is formed in the shape of a bar on the front surface and upper surface of the design panel 2. An opening surrounded by the lower ends of the scroll portion 7 </ b> A, the design panel 2, and the side wall plate 9 constitutes the air outlet 11. Further, a ventilation path 10 leading from the suction port 2 a to the blower outlet 11 is formed in a space surrounded by the scroll portion 7 </ b> A, the stabilizer 8, the design panel 2, and the side wall plate 9. That is, the air outlet 11 is formed at the lowest end of the ventilation path 10.

  A cylindrical impeller 5 is disposed in the path of the ventilation path 10 so that its axial direction is aligned with the width direction of the design panel 2 and the scroll portion 7A and is rotatable about the axis. At this time, the scroll portion 7A is disposed on the back side of the impeller 5, and the scroll portion 7A guides the air sucked from the suction port 2a to the back surface of the impeller 5. Further, the heat exchanger 3 is disposed in the ventilation path 10 on the suction port 2a side of the impeller 5 so as to cover the impeller 5 in a Λ shape.

In the air conditioner 1 </ b> A configured as described above, the air sucked from the suction port 2 a passes through the heat exchanger 3, flows through the impeller 5, passes through the diffuser 6, and enters the room from the outlet 11. To be released.
At this time, the airflow on the suction side and the airflow on the blowout side are partitioned by the stabilizer 8. Here, the suction side refers to a portion of the ventilation path 10 closer to the suction port 2 a than the impeller 5, and the blowout side refers to a portion of the ventilation path 10 closer to the outlet 11 than the impeller 5. Moreover, let the airflow on the blowing side be the blowing airflow.

As shown in FIGS. 1, 4 and 5, the air passage cross-section changing mechanism 15 includes a rod-like top portion 16 a and a rod-like engagement column 16 b that protrudes perpendicularly to the top portion 16 a from the intermediate portion in the longitudinal direction of the top portion 16 a. And a T-type pressing tool 16, a motor 17, a gear 18, and a displacement control unit 19. And the ventilation path cross-section change mechanism 15 is arrange | positioned so that it may be included in the scroll part 7A below the arrangement | positioning position of the impeller 5. FIG.
The displacement control unit 19 has a CPU (not shown) as a control means, and a program for causing the CPU to control the rotation drive of the motor 17 in accordance with switching between the cooling operation and the heating operation of the air conditioner 1A. It has a written ROM (not shown) and the like.

  The top portion 16a of the pressing tool 16 is arranged along the back surface of the guide wall 7c and with its length direction aligned with the direction of the airflow. Here, the surface of the guide wall 7c on the side of the ventilation path 10 is defined as the front surface, and the surface opposite to the ventilation path 10 is defined as the back surface. The engaging column 16b protrudes from the top portion 16a so as to be perpendicular to the back surface of the guide wall 7c, and the front end side of the engaging column 16b is engaged with the gear 18. Further, the motor 17 is arranged so that the rotational torque can be transmitted to the gear 18. As a result, the pressing tool 16 can reciprocate in the length direction of the engaging column 16 b in accordance with the rotational drive of the motor 17.

Next, the operation of the ventilation path cross-section changing mechanism 15 during the cooling operation and the heating operation of the air conditioner 1A will be described.
First, operation | movement of the ventilation path cross-section change mechanism 15 at the time of air_conditionaing | cooling operation is demonstrated with reference to FIG.1, FIG.2, FIG.4 and FIG.
The side sectional view of FIG. 1 is the vicinity of the central portion in the width direction of the air conditioner 1A, and further, the sectional view of the guide plate 7c in the vicinity of one end portion in the width direction of the air conditioner 1A is also shown with a broken line. Yes.

  During the cooling operation, the CPU of the displacement control unit 19 controls the rotational drive of the motor 17 so as to rotate the gear 18 in the direction in which the engagement column 16b is moved toward the back surface of the guide wall 7c. Then, the CPU of the displacement control unit 19 stops the rotation of the motor 17 when the top portion 16a is moved to the ventilation path 10 side by a predetermined distance after contacting the back surface of the guide wall 7c. At this time, the guide wall 7c formed of a flexible member is pressed in the direction perpendicular to the surface of the guide wall 7c and toward the ventilation path 10, so that the width of the guide wall 7c is as shown in FIG. A portion closer to the center in the direction (the axial direction of the impeller 5) protrudes from the blower outlet 11 to a portion near the lower portion of the impeller 5 toward the ventilation path 10 from both ends in the width direction.

  Thereby, the ventilation path 10 at the time of air_conditionaing | cooling operation is the surface of the guide wall 7c shown by the broken line in FIG. 6, the wall surface on the blower outlet 11 side of the stabilizer 8 (hereinafter referred to as the stabilizer blowout wall surface 8a), and the side wall plate 9 Is a region surrounded by opposing wall surfaces (hereinafter referred to as side wall surface 9a). At this time, the protruding amount of the guide wall 7c toward the ventilation path 10 in the cross section of the ventilation path during the cooling operation is gradually increased from both ends in the width direction of the guide wall 7c toward the center in the width direction. It is changing smoothly. The cross section of the ventilation path refers to a cross section of the ventilation path 10 perpendicular to the direction of the blown airflow downstream from the impeller 5.

  Moreover, in the ventilation path 10, the static pressure near the center part in the width direction of the guide wall 7c is lower than the static pressure on the both end sides of the guide wall 7c, and both ends in the width direction of the guide wall 7c due to the difference in static pressure. The force that gathers from the center to the center acts on the airflow. However, as the guide wall 7c moves toward the center of the guide wall 7c in the width direction, the amount of protrusion of the guide wall 7c increases toward the ventilation path 10, so that the dynamic pressure increases toward the center of the guide wall 7c in the width direction. It increases compared to both ends in the width direction. The dynamic pressure increased on the center side acts in the direction in which the airflow is directed from the center portion in the width direction of the guide wall 7c having a high flow velocity toward both ends in the width direction of the guide wall 7c having a low flow velocity.

  Due to the dynamic pressure increased at the center portion in the width direction of the guide wall 7c, the force that directs the air flow from the center portion to both ends in the width direction of the guide wall 7c is caused by the difference in static pressure. Since the force is greater than the force to gather from both ends in the width direction to the center, the dynamic pressure is increased on both ends in the width direction of the guide wall 7c. That is, the dynamic pressure at both ends in the width direction of the ventilation path 10 is increased.

Next, the operation of the ventilation path cross-section changing mechanism 15 during the heating operation will be described with reference to FIGS. 3, 5, and 6.
When switching from the cooling operation to the heating operation, as shown in FIG. 5, the CPU of the displacement control unit 19 rotates the gear 18 in the reverse direction to the cooling operation so that the top portion 16 a is separated from the back surface of the guide wall 7 c. In addition, the rotational drive of the motor 17 is controlled. Since the top portion 16a is separated from the guide wall 7c and there is no force to press the back surface of the guide wall 7c, the guide wall 7c extends from one end to the other end in the width direction as shown in FIG. The part which protrudes to the ventilation path 10 side is lost, and it planarizes.

  Thereby, the ventilation path 10 at the time of heating operation turns into the area | region enclosed by the surface of the guide wall 7c shown by the continuous line of FIG. 6, the stabilizer blowing wall surface 8a, and the side wall surface 9a. That is, in the vicinity of the central portion in the width direction of the guide wall 7c, there is no portion protruding to the ventilation path 10 side during the cooling operation, and the ventilation path cross-sectional area during the heating operation downstream from the impeller 5 is It is larger than the cross-sectional area of the ventilation path during operation.

  At this time, since the projecting portion of the guide wall 7c toward the ventilation path 10 is eliminated, the dynamic pressure on the center side in the width direction of the guide wall 7c in the ventilation path 10 is reduced as compared with the cooling operation. That is, since the force that directs the airflow from the center portion in the width direction of the guide wall 7c to the both end portions in the width direction is also reduced, the dynamic pressure at both ends in the width direction of the ventilation path 10 is larger in the heating operation than in the cooling operation. Is greatly reduced.

According to this Embodiment 1, the ventilation path cross-sectional area change mechanism 15 is arrange | positioned so that the guide wall 7c may be displaced according to switching of a cooling operation and a heating operation, and a ventilation path cross-sectional area may be switched.
That is, in the cross section of the ventilation path downstream from the impeller 5 during the cooling operation, the center portion in the width direction of the guide wall 7c of the scroll portion 7A, which was flat during the heating operation, is closer to the ventilation path 10 side than both ends in the width direction. The cross-sectional area of the ventilation path is made smaller than that during heating operation. As a result, the dynamic pressure is increased at both ends in the width direction of the ventilation path 10, so that the surging phenomenon during the cooling operation can be suppressed.

Furthermore, at the time of heating operation, the guide wall 7c projected to the ventilation path 10 side is returned to the original state and the guide wall 7c is flattened, so that both ends of the ventilation path 10 on the downstream side of the impeller 5 in the width direction. The dynamic pressure is significantly lower than the dynamic pressure during cooling operation.
Accordingly, the dynamic pressure loss of the blown airflow during the heating operation is significantly suppressed, and the energy consumption efficiency during the heating operation can be improved.

  Here, in the above description, the central portion in the width direction of the guide wall 7c in the cross section of the ventilation path is protruded from the both ends toward the ventilation path 10 to increase the dynamic pressure at both ends of the ventilation path 10. The means for increasing the dynamic pressure at both ends in the width direction of the passage 10 is not limited to projecting the center portion in the width direction of the guide wall 7c toward the ventilation passage 10 from both ends.

Hereinafter, the first to fifth embodiments for increasing the dynamic pressure at both ends in the width direction of the ventilation path 10 will be briefly described with reference to FIGS. 7 to 11.
FIG. 7 is a cross-sectional view of the blown air flow in the air conditioner showing the first embodiment of the present invention, FIG. 8 is a cross-sectional view of the blown air flow in the air conditioner showing the second embodiment of the present invention, FIG. 9 is a cross-sectional view of a blown air flow in an air conditioner showing a third embodiment of the present invention, FIG. 10 is a cross-sectional view of a blown air flow in an air conditioner showing a fourth embodiment of the present invention, FIG. 11 is a cross-sectional view of a blown air flow path in an air conditioner showing a fifth embodiment of the present invention. 7 to 11, the same reference numerals are used for the same or corresponding parts as in the above description.

  As will be described later, in each embodiment, the amount of protrusion of the surface of the guide wall 7c, the stabilizer outlet wall surface 8a, and the side wall surface 9a toward the ventilation path 10 can be switched between the cooling operation and the heating operation. However, in any case, the amount of protrusion of each wall surface into the ventilation path 10 is switched between the cooling operation and the heating operation using a mechanism equivalent to the above-described ventilation path cross-section changing mechanism 15.

The first embodiment will be described.
In FIG. 7, the surface of the guide wall 7c indicated by a solid line is that during heating operation, and the surface of the guide wall 7c indicated by a broken line is that during cooling operation.
That is, during cooling operation, both end portions in the width direction of the guide wall 7c protrude from the center portion in the width direction to the ventilation path 10 side. In this case, compared with the heating operation in which the guide wall 7c is flat across the width direction, the both end portions of the guide wall 7c during the cooling operation protrude toward the ventilation path 10, and thus the cross-sectional area of the ventilation path is reduced. To do. Therefore, the dynamic pressure at both ends in the width direction of the guide wall 7c during cooling operation (both ends in the width direction of the ventilation path 10) increases compared to during heating operation.

Next, the second and third embodiments will be described.
8 and 9, the surface of the stabilizer outlet wall surface 8a indicated by a solid line is that during heating operation, and the stabilizer outlet wall surface 8a indicated by a broken line is that during cooling operation.
And in FIG. 8, the stabilizer blowing wall surface 8a is protruded in the ventilation path 10 from the both ends of the width direction, so that it approaches the center part of the width direction. Moreover, in FIG. 9, both ends of the width direction of the stabilizer blowing wall surface 8a are protruded from the center part in the width direction to the ventilation path 10 side.

  Each of FIGS. 8 and 9 replaces the amount of protrusion of the wall surface of the guide wall 7c to the ventilation path 10 side by switching between the heating operation and the cooling operation, and the stabilizer outlet wall surface 8a protrudes to the ventilation path 10 side. Only the amount can be switched between heating operation and cooling operation. Therefore, both ends of the stabilizer 8 in the width direction (in the width direction of the ventilation path 10) are changed in the same manner as when the amount of protrusion of the wall of the guide wall 7c to the ventilation path 10 is switched between the heating operation and the cooling operation. The dynamic pressure at both ends is increased.

Next, the fourth and fifth embodiments will be described.
10 and 11, the surface of the side wall surface 9a indicated by a solid line is that during heating operation, and the surface of the side wall surface 9a indicated by a broken line is that during cooling operation.
In FIG. 10, the side wall plate 9, which was flat during the heating operation, is protruded into the air passage 10 through the central portion in the direction (longitudinal direction) perpendicular to the width direction of the air passage 10 during the cooling operation. Yes. Moreover, in FIG. 11, the both ends of the vertical direction of the side wall board 9 which were planar at the time of heating operation are protruded in the ventilation path 10 at the time of air_conditionaing | cooling operation.
As shown in FIGS. 10 and 11, during the cooling operation, the cross-sectional area of the ventilation path 10 at both ends in the width direction of the ventilation path 10 is reduced compared with that during the heating operation, and the dynamic pressure at both ends of the ventilation path 10 in the width direction is reduced. Is increased.

As described above, in the first embodiment and the first to fifth embodiments, the ventilation passage cross-section changing mechanism 15 is ventilated so that the volume of the ventilation passage 10 is suitable for operating conditions such as cooling operation and heating operation. The wall surface which comprises the path 10 is displaced. That is, the wall surface of the guide wall 7c of the scroll portion 7A constituting the air passage 10 and both axial sides of the stabilizer outlet wall surface 8a or the central portion in the axial direction protrude toward the air passage side or the side wall surface 9a. The air passage cross-sectional area is reduced compared with that during heating operation during cooling operation by projecting to the side.
As a result, the dynamic pressure is increased at both ends in the width direction of the ventilation path 10, so that the surging phenomenon during the cooling operation can be suppressed. Accordingly, it is possible to prevent dew dripping during cooling operation. Moreover, since the displacement of the wall surface during the cooling operation is eliminated during the heating operation, the dynamic pressure loss of the airflow on the blowout side can be significantly suppressed. Therefore, the energy consumption efficiency at the time of heating operation can be improved.

  In the above description, the ventilation path cross-sectional area change mechanism 15 is configured to reduce the ventilation path cross-sectional area during cooling operation compared to that during heating operation. In other words, the ventilation path cross-section change mechanism 15 is reduced during cooling operation. This is equivalent to reducing the volume of the ventilation path (volume of the ventilation path 10 surrounded by the diffuser 6) as compared with the heating operation.

  In the first embodiment and the first to fifth embodiments, the wall surface of the guide wall 7c, the stabilizer outlet wall surface 8a, and the side wall surface 9a are described as being displaced. A plurality of the wall surfaces of the guide wall 7c, the stabilizer outlet wall surface 8a, and the side wall surface 9a are combined, and the selected wall surface is more in the cooling operation than in the heating operation when the ventilation path volume downstream from the impeller 5 is in the heating operation. You may displace so that it may become small. Thereby, each wall surface is displaced using the other ventilation path cross-section change mechanism which has only a small displacement amount from the ventilation path cross-section change mechanism 15 which displaced the guide wall 7c, the stabilizer blowing wall surface 8a, and the side wall surface 9a alone. However, if the variation of the total ventilation path volume is equivalent to that of the single displacement, the same effect as the displacement of any one of the guide wall 7c, the stabilizer outlet wall surface 8a, and the side wall surface 9a is obtained. can get.

Further, the protruding amount of the wall surface of the guide wall 7c, the stabilizer outlet wall surface 8a, and the side wall surface 9a may be switched such that the ventilation path volume during cooling operation is partially smaller than the ventilation path volume during heating operation. . That is, the guide wall 7c, the scroll wall surface 8, and a part of the side wall plate 9 only need to protrude toward the ventilation path 10 during the cooling operation as compared with the heating operation. As a result, the volume of the ventilation path downstream of the impeller 5 during the cooling operation is smaller than that during the heating operation, so the dynamic pressure of the airflow in the ventilation path 10 is increased during the cooling operation and surging. The phenomenon is suppressed. Further, if the wall surface displacement during the cooling operation is eliminated during the heating operation, the dynamic pressure loss of the airflow on the blowing side can be suppressed, and the energy consumption efficiency during the heating operation can be improved.
However, if it is configured as in the general first embodiment and the first to fifth embodiments, the surging phenomenon can be effectively suppressed while suppressing the dynamic pressure loss during the cooling operation as much as possible.

  The guide wall 7c, the stabilizer 8 and the side wall plate 9 are made of a material that expands at the internal temperature of the air conditioner 1A during the heating operation than at the internal temperature of the air conditioner 1A during the cooling operation. In the cooling operation, compared to the heating operation, either the wall surface of the guide wall 7c or the stabilizer outlet wall surface 8a is protruded to the side of the width direction or the central part in the axial direction through the air passage 10 side, or the side wall surface 9a is provided with the air passage. You may make it protrude in 10 side. In this case, the guide wall 7c, the stabilizer 8, and the side wall plate 9 itself also serve as the above-described ventilation path cross-section changing mechanism 15.

  In addition, a water absorbing member or the like is provided at the lower end portion of the guide wall 7c of the scroll portion 7A as an integral or separate component in order to prevent dripping of condensation due to mixing of cool air and warm air during cooling operation. Also good.

Embodiment 2. FIG.
FIG. 12 is a side sectional view of an air conditioner according to Embodiment 2 of the present invention, FIG. 13 is a perspective view of a blower outlet area changing mechanism for an air conditioner according to Embodiment 2 of the present invention, and FIG. It is the ventilation path sectional drawing of the blowing airflow in the air conditioner which concerns on Embodiment 2. FIG. 12 to 14, the same reference numerals are given to the same portions as those in the first embodiment, and the description thereof is omitted.

In FIG. 12, the air conditioner 1 </ b> B has a scroll portion 7 </ b> B and a blower outlet area changing mechanism 21. The scroll portion 7B includes a back wall 7a, a bottom wall 7b, and a guide wall 7d. The guide wall 7d has the same shape as the above-described guide wall 7c, but no flexible member is used. Further, as shown in FIG. 13, the air outlet area changing mechanism 21 includes a motor 17, a drive plate rotation shaft 17 a, a displacement control unit 19, and a drive plate 22 having a triangular outer shape and a plate shape. .
The drive plate rotation shaft 17a is disposed along the width direction of the guide wall 7d at the lower end of the guide wall 7d, and is rotatable about the axis.

The drive plate rotation shaft 17a is adapted to transmit the rotational torque of the motor 17, and is rotated according to the rotation of the motor 17 around the axis.
The drive plate 22 is attached so that one side thereof is aligned with the drive plate rotation shaft 17a, and is rotatable in conjunction with the rotation around the drive plate rotation shaft 17a.

  During the cooling operation of the air conditioner 1 </ b> B, the CPU of the displacement control unit 19 causes the drive plate 22 to block a part on the outlet 11 side from the lower part of the outlet 11 that is the lowermost end of the ventilation path 10. The rotational drive of the motor 17 is controlled. Further, during the heating operation, the displacement control unit 19 controls the rotational drive of the motor 17 so as to eliminate a part of the outlet 11 of the air outlet 11 by the drive plate 22.

  Next, a change in the area (air circulation air flow area) of the ventilating region in the air outlet 11 during the heating operation and the cooling operation will be described with reference to FIG. In FIG. 14, the broken line indicates the drive plate 22 that closes the air outlet 11 during the cooling operation. Further, during the heating operation, the drive plate 22 illustrated by the solid line is rotated so as to eliminate the blockage of the air outlet 11.

  Further, during the cooling operation, the size of the air circulation air area is obtained by subtracting the area of the drive plate 22 indicated by the broken line from the area of the air outlet 11 and is smaller than the area of the air outlet 11. ing. At this time, the drive plate 22 protrudes most into the air outlet 11 at the center in the width direction of the air outlet 11. That is, during the cooling operation, the area of the central portion in the width direction of the air outlet 11 is reduced as compared with the heating operation. As a result, the dynamic pressure increases at the central portion in the width direction of the outlet 11, and this dynamic pressure acts in a direction in which the airflow is directed from the center side of the guide wall 7 c having a high flow velocity to both end portions having a low flow velocity. Therefore, the dynamic pressure at both ends in the width direction of the air outlet 11 is increased.

  During the heating operation, the drive plate 22 protruding into the air outlet 11 is moved to the outside of the air outlet 11 that does not hinder the flow of the airflow, and the lower end of the air outlet 11 becomes flat across the width direction, The area of the air outlet 11 is an air circulation area. Therefore, since the dynamic pressure is reduced in the central portion in the width direction of the air outlet 11 as compared with the cooling operation, the force for directing the airflow from the central portion in the width direction of the air outlet 11 to both ends is also reduced. That is, in the heating operation, the dynamic pressure decreases at both ends in the width direction of the air outlet 11 as compared with the cooling operation.

According to the second embodiment, the air outlet area changing mechanism 21 rotates the drive plate 22 so that the air circulation air area of the air outlet 11 is suitable for operating conditions such as cooling operation and heating operation. . That is, a part of the air outlet 11 is closed by the drive plate 22 so that the area of the central portion in the width direction of the air outlet 11 is reduced during the cooling operation as compared with that during the heating operation. Is controlled so that the dynamic pressure at the center of the air outlet 11 is lowered. Thereby, the dynamic pressure of the both ends of the width direction of the blower outlet 11 at the time of air_conditionaing | cooling operation increases compared with the time of heating operation, and the dynamic pressure of the width direction both ends of the blower outlet 11 is decreased at the time of heating operation.
Therefore, the same effect as in the first embodiment can be obtained.
In addition, since only a part of the outlet 11 is switched between the closing of the outlet 11 and the closing of the outlet, during the cooling operation and the heating operation, any one of the guide wall 7d, the stabilizer outlet wall surface 8a, and the side wall surface 9a is used. As compared with the control of the above-described ventilation path cross-section changing mechanism 15 that has been displaced and protruded toward the ventilation path 10, the control of the air outlet area changing mechanism 21 can be simplified.

  In the second embodiment, the shape of the drive plate 22 is formed in a triangle, and a part of the air outlet 11 is closed so that the dynamic pressure increases at the center in the width direction of the air outlet 11 during the cooling operation. Although described as a thing, it is not limited to what increases the dynamic pressure of the center part of the width direction of the blower outlet 11, and increases the dynamic pressure of the width direction both ends of the blower outlet 11. FIG. The drive plate 22 is formed such that the amount of protrusion into the blower outlet 11 increases from the center in the width direction of the blower outlet 11 toward both ends, and a part of the blower outlet 11 is formed by the drive plate 22 during cooling operation. When the air outlet is closed, the air circulation air area may be reduced at both ends in the width direction of the air outlet 11 so that the dynamic pressure on both ends of the air outlet 11 increases.

  Moreover, the drive plate 22 uses the drive mechanism (not shown) which drives the wind direction control board (not shown) to the up-down-and-left-right direction provided normally in the blow-out port 11 of the air conditioner 1B. The drive plate 22 may be rotated so as to close the cover 11.

It is a sectional side view at the time of the air_conditioning | cooling operation of the air conditioner which concerns on Embodiment 1 of this invention. It is a perspective view of the scroll part at the time of air_conditionaing | cooling operation of the air conditioner which concerns on Embodiment 1 of this invention. It is a perspective view of the scroll part at the time of the heating operation of the air conditioner which concerns on Embodiment 1 of this invention. It is IV-IV arrow principal part sectional drawing of FIG. It is sectional drawing when an air conditioner switches from air_conditionaing | cooling operation to heating operation in FIG. It is a ventilation path sectional view of the blowing air current in the air harmony machine concerning Embodiment 1 of this invention. It is a ventilation path sectional view of the blowing air current in the air harmony machine showing the 1st embodiment of this invention. It is a ventilation path sectional drawing of the blowing airflow in the air conditioner which shows the 2nd embodiment of this invention. It is a ventilation path sectional drawing of the blowing airflow in the air conditioner which shows the 3rd embodiment of this invention. It is a ventilation path sectional drawing of the blowing airflow in the air conditioner which shows the 4th embodiment of this invention. It is a ventilation path sectional drawing of the blowing airflow in the air conditioner which shows the 5th embodiment of this invention. It is a sectional side view of the air conditioner which concerns on Embodiment 2 of this invention. It is a perspective view of the blower outlet area change mechanism of the air conditioner concerning Embodiment 2 of this invention. It is a ventilation path sectional drawing of the blowing airflow in the air conditioner which concerns on Embodiment 2 of this invention.

Explanation of symbols

  1A, 1B Air conditioner, 2a Suction port, 4 Cross flow fan, 5 Impeller, 7A, 7B Scroll part, 8 Stabilizer, 9 Side wall plate, 10 Ventilation path, 11 Air outlet, 15 Ventilation path cross-section change mechanism, 21 Blow Exit area change mechanism.

Claims (7)

An impeller, a scroll portion for guiding air to the back of the impeller, and a crossflow fan disposed on the downstream side of the impeller relative to the scroll portion and having a stabilizer that partitions the suction port and the outlet, In the air conditioner that forms the ventilation path from the scroll portion, the stabilizer, and the side wall plates arranged on both sides in the axial direction of the impeller,
The volume of the ventilation path is changed by displacing at least one wall surface of the scroll portion, the stabilizer, and the side wall plate constituting the ventilation path corresponding to the operating condition to the ventilation path side or the side opposite to the ventilation path. An air conditioner comprising an air passage cross section changing mechanism.   The ventilation path cross-section changing mechanism reduces the area of the both sides in the axial direction of the impeller or the central part in the axial direction in the ventilation path cross section on the outlet side of the impeller during the cooling operation by reducing the area compared to the heating operation. The air conditioner according to claim 1, wherein the air passage volume is changed.   The ventilation path cross-section changing mechanism is configured such that the axially opposite sides or the axially central part of the wall surface of the scroll portion constituting the ventilation path protrudes toward the ventilation path side and the axially opposite sides or the axially central part is The air conditioner according to claim 2, wherein the area is reduced.   The ventilation path cross-section changing mechanism is configured such that the axially opposite sides of the stabilizer wall surface or the axially central portion of the stabilizer that constitutes the ventilation path protrudes toward the ventilation path, and the areas of the axially opposite sides or the axially central portion are projected. The air conditioner according to claim 2, wherein the air conditioner is reduced.   The air conditioner according to claim 2, wherein the ventilation path cross-section changing mechanism reduces the area on both sides in the axial direction by projecting the wall surface of the side wall plate constituting the ventilation path toward the ventilation path. .   The ventilation path cross-section changing mechanism is configured such that the axially opposite sides or the axially central part of both wall surfaces of the scroll portion and the stabilizer constituting the ventilation path protrude toward the ventilation path side, or the wall surface of the side wall plate Projecting toward the ventilation path side, and projecting the axially opposite sides or the axially central part of at least one wall surface of the scroll part and the stabilizer toward the ventilation path side, the axially opposite sides or the axially centered part The air conditioner according to claim 2, wherein the area of the portion is reduced. An impeller, a scroll portion that guides air to the rear surface of the impeller, and a cross flow fan that is disposed on the downstream side of the impeller relative to the scroll portion and has a stabilizer that partitions the suction port and the outlet. In the air conditioner configured to form a ventilation path from the scroll portion, the stabilizer, and side wall plates arranged on both sides in the axial direction of the impeller,
It is provided with a blower outlet area changing mechanism that reduces the area of both sides in the axial direction or the central part in the axial direction of the blower outlet that is the lowermost end of the ventilation path during cooling operation. Air conditioner.

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