JP3233551B2 - Air conditioner - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner constituting an indoor unit, for example, and more particularly to an improvement in a heat exchanger structure.

[0002]

2. Description of the Related Art An air conditioner generally used comprises an indoor unit arranged in a room to be air-conditioned and an outdoor unit arranged outdoors, and these units are connected to each other by a refrigerant pipe and electric wiring. .

[0003] From the user's side, there is a great demand for downsizing these units and reducing the installation space, and it is necessary for each manufacturer to increase the heat exchange capacity while satisfying such conditions.

[0004] In particular, in the indoor unit, a flat plate-like heat exchanger is conventionally arranged with a certain degree of inclination, but the height is large, and inevitably, a unit body accommodating this heat exchanger is required. The height dimension is also increased, and the mounting area of an indoor unit, which is commonly used in a wall-mounted manner, is increased.

In order to reduce the height of the indoor unit, a heat exchanger has been developed in which the above-mentioned flat heat exchanger is bent in a square shape when viewed from the side, and the intended purpose is satisfied to some extent. Results were obtained.

However, similarly to the plate-shaped heat exchanger, in this U-shaped heat exchanger, there is a large difference in the distance from the blower fan arranged on the rear side, and the heat exchanger circulates through the heat exchanger. A large difference occurs in the amount of heat exchange air. This difference translates into a reduction in heat exchange efficiency and a cause of airflow noise.

In view of such circumstances, there has been provided a heat exchanger formed in an inverted V-shape, as disclosed in, for example, Japanese Utility Model Laid-Open No. 4-57073. With this type of heat exchanger, it is possible to further reduce the height dimension as compared with the V-shaped heat exchanger.

[0008]

However, even in an indoor unit provided with an inverted V-shaped heat exchanger, there are many demands. As one of them, there is a problem of heat exchange capacity in the heat exchanger. That is, the fins forming the heat exchanger have a so-called strip shape that is narrow in the pressed state and long in the longitudinal direction.

A large number of these fins are arranged side by side with a small gap, and a heat exchange pipe is inserted into a mounting hole provided therein, expanded and fixed. Furthermore, an inverted V-shaped heat exchanger is obtained by bending the fin at a cut portion provided in the fin.

The fins have a uniform width even after being bent, and the capacity (volume) as a heat exchanger remains unchanged. Therefore, there is no increase in heat exchange capacity as compared with the conventional one.

On the other hand, it is conceivable to simply increase the capacity of the heat exchanger to increase the heat exchange capacity by increasing the number of heat exchange pipes in the airflow direction. However, there is a problem that the airflow noise is increased due to the turbulence of the airflow in the heat exchange pipe when the airflow passes through the heat exchanger.

That is, in a portion close to the fan, since the distance between the heat exchanger and the blower fan is short, the air flow disturbed by the heat exchange pipe when passing through the heat exchanger is:
After flowing out of the heat exchanger, it flows into the blower fan without being rectified.

Therefore, if the capacity of the heat exchanger is increased by simply increasing the number of pipes in the air flow direction of the heat exchanger in the portion close to the fan, the noise from the blower fan increases by the increased amount. Become.

The present invention has been made in view of the above circumstances, and an object thereof is to provide a heat exchanger formed in an inverted V-shape in a side view without increasing blowing noise. Another object of the present invention is to provide an air conditioner that increases the heat exchanger capacity and increases the heat exchange capacity.

[0015]

In order to satisfy the above object, an air conditioner according to the present invention is characterized in that, in the air conditioner according to the first aspect, an air inlet is provided at a front portion and an upper portion thereof, and an air outlet is provided at a lower portion of a front surface. a conditioner main body, the heat exchange air of the air conditioner heat exchanger and the air conditioning chamber is housed disposed within the body; and a blower fan of circular section leading to the heat exchanger, the heat exchanger includes a plurality A plurality of fins are arranged side by side with a small gap therebetween, and a fin tube type in which a heat exchange pipe is penetrated by these fins. The inverted V in side view is opposed to the front suction port and the upper suction port.
The front heat exchanger and the rear heat exchanger that are bent in the shape of a letter, and the fins that constitute the rear heat exchanger,
The length in the air flow direction is the length of the front heat exchanger.
It is characterized in that it is formed longer than the length of the fin in the heat exchange air flow direction.

In the second aspect, after the first aspect,
The side heat exchanger is installed along and along the main heat exchanger.
This main heat consists of a combination with an auxiliary heat exchanger
Heat exchange air flow direction consisting of the heat exchanger and the auxiliary heat exchanger
The length of the fins constituting the front heat exchanger is
It is characterized by being formed longer than the length in the air flow direction .

In order to satisfy the above-mentioned object, according to the present invention , a suction port is provided at a front portion and an upper portion thereof.
Air conditioning with outlets at the bottom front
And the heat housed and arranged inside the air conditioner body
Disconnect the heat exchange air from the heat exchanger and the air-conditioned room to the heat exchanger
In an air conditioner equipped with a circular fan fan,
In the above heat exchanger, many fins have a narrow gap
Heat exchange pipes penetrate these fins
Fin tube type.
And folded into an inverted V shape in side view so as to face the upper suction port
It consists of a bent front heat exchanger and a rear heat exchanger.
The fins that make up the front heat exchanger are
Exchange airflow in the uppermost part, which is the most distant part
The length in the direction is lower
It is characterized in that it is formed longer than the length in the heat exchange air flow direction .

In the fourth aspect, the portion of the front heat exchanger and the rear heat exchanger in which the length in the heat exchange air circulation direction is formed to be long in the front heat exchanger and the rear heat exchanger. At least three rows of heat exchange pipes are arranged side by side with respect to the direction, and a refrigerant inlet part for the heating operation is formed in the leeward row, and a refrigerant outlet part for the same operation is formed in the leeward row. I do.

In the fifth aspect, the leeward row of the heat exchange pipes having the refrigerant inlet and the leeward row of the heat exchange pipes having the refrigerant outlet are thermally isolated from each other. It is characterized by having.

In the sixth aspect of the present invention, the diameter of the heat exchange pipe in the windward side row is smaller than the diameter of the heat exchange pipe in the leeward side row. It is characterized by being performed.

According to a seventh aspect of the present invention, the pipe pitch of the heat exchange pipes in the leeward side of the row of heat exchange pipes thermally isolated from each other is more than the pipe pitch of the heat exchange pipes in the leeward side. Is also formed to be narrow.

In the eighth aspect of the present invention, the fin pitches of the fins constituting the heat exchangers in the leeward side row of the heat exchange pipe rows thermally isolated from each other in the leeward side row in the fifth aspect. Are formed wider than the fin pitch of the fins constituting the fin.

According to a ninth aspect of the present invention, the fins constituting the heat exchanger having no heat exchange pipe row among the front heat exchangers and the rear heat exchangers according to the fifth aspect of the present invention. A cut-and-raised slit is provided, and a cut-and-raised slit is not provided in a fin constituting a heat exchanger of a windward side row among heat exchange pipe rows that are thermally isolated from each other. In the tenth aspect, the front heat exchanger according to the first to ninth aspects is formed in an arc shape so as to surround a part of a peripheral surface of the blower fan.

[0024]

According to the first aspect of the present invention, the rear side of the front heat exchanger is provided.
As the heat exchanger capacity of the heat exchanger has been increased,
The portion becomes relatively far from the blower fan, so that the turbulence increased by the increased capacity is rectified before flowing into the blower fan.

According to the second aspect of the present invention, the main heat exchanger and the auxiliary heat
Heat exchange airflow in rear heat exchanger combined with heat exchanger
The length in the flow direction is longer than that of the front heat exchanger,
The amount increases, and the turbulence increased by the increase in the capacity is rectified before flowing into the blower fan.

According to the third aspect of the present invention, the capacity of the front heat exchanger farthest from the blower fan is larger than that of the portion near the fan.
The turbulence, which increases due to the increase in the capacity, is rectified before flowing into the blower fan.

According to the fourth aspect of the invention, the temperature of the refrigerant is high at the entrance during heating, but the temperature decreases at the exit due to heat exchange. Since this outlet is set as the heat exchange pipe on the windward side, a sufficient temperature difference with the heat exchange air at the portion where the capacity is increased can be obtained, and the heat exchange efficiency is good.

According to the fifth aspect of the present invention, the heat exchange between the inlet portion where the refrigerant is high and the outlet portion where the temperature is lowered is prevented by thermally intercepting the refrigerant. According to the sixth aspect of the present invention, since the diameter of the heat exchange pipes in the windward side that becomes the refrigerant outlet during heating is small, the flow rate of the refrigerant flowing in a liquefied state increases, and the heat transfer coefficient improves.

According to the seventh aspect of the present invention, since the heat exchange pipes in the windward side which are refrigerant outlets during heating have a narrow pipe pitch, the refrigerant flowing in a liquefied state is guided to a longer flow path, The heat transfer coefficient is improved.

According to the eighth aspect of the present invention, since the fin pitch of the heat exchanger fins in the windward side row is wide, the flow resistance to the heat exchange air can be prevented, and the heat exchange efficiency can be improved. According to the ninth aspect of the present invention, the flow resistance to the heat exchange air flowing through the fins is made uniform by limiting the positions of the cut and raised slits in the heat exchanger. According to the tenth aspect, the front heat exchanger having the increased capacity is formed in an arc shape, so that the flow of the heat exchange air is smooth and the blowing noise can be reduced.

[0031]

An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is convenient for explaining the first, second, fourth, fifth and tenth aspects.

The unit body 1, which is the air conditioner body,
It comprises a front panel 2 and a rear plate 3. Front panel 2
A front suction port 5a in which a grill 4 is fitted is provided on the front side of
And an upper suction port 5b into which the grill 6 is fitted is opened on the upper surface side.

In the unit body 1, a front suction port 5a is provided.
And a filter support 7 along both sides of the upper suction port 5b.
The air filter 8 is detachably mounted on the filter support.

Further, a heat exchanger 10 formed as described later is disposed opposite the front and upper suction ports 5a and 5b via the air filter 8. A cross flow fan 11, which is a blower fan having a circular cross section, is arranged so as to be covered by the heat exchanger 10.

The heat exchanger 10 and the cross flow fan 11 are both mounted and supported on the rear plate 3 via a support (not shown). The lower part on the front side of the heat exchanger 10 is inserted into a front drain pan 12, and the lower part on the rear side is inserted into a rear drain pan 13 integrally formed with the rear plate 3.

The front drain pan 12 and the rear drain pan 13 communicate with each other via a communication passage (not shown). Below the front drain pan 12, an outlet 14 is provided which opens to the lower part on the front side of the unit body 1.

The upper end of the rear plate 3 is provided with an upper suction port 5b.
The lowermost portion extends from the rear drain pan 13 to the outlet 14 through the side of the cross flow fan 11.

An outlet guide path 15 is formed by the lower surface of the front drain pan 12 and a part of the rear plate 3 extending from the side of the cross flow fan 11 to the outlet 14. A left-right louver 16 is provided on the lower surface of the front drain pan 12 so as to be located in the outlet guide path 15. A vertical louver 17 is provided at the outlet 14.

Next, the heat exchanger 10 will be described in detail. That is, the heat exchanger 10 is composed of a combination of a main heat exchanger 10A formed in an inverted V-shape and an auxiliary heat exchanger 10B provided straight and along a part of the main heat exchanger. .

The main heat exchanger 10A is first formed as a connected body in which an arc-shaped portion and a straight portion are connected to each other at their ends. A perforated cut is formed in the connecting portion between the arc-shaped portion and the straight portion, and the actual connecting portion is few. By bending a straight portion from this connection portion at a predetermined angle, an inverted V-shape is formed.

Then, the main heat exchanger 10 is
In the state where A is assembled, from the place where the arc-shaped part is located on the front side, this part is called the front heat exchanger 9A, and the straight part located behind it is called the rear heat exchanger 9B. .

The front heat exchanger 9A formed in an arc shape is
It is located at a position facing the front suction port 5a. The rear heat exchanger 9B that is inclined obliquely downward from the front to the rear is located at a position facing the upper suction port 5b via the auxiliary heat exchanger 10B.

The auxiliary heat exchanger 10B is provided on the upper side of the rear heat exchanger 9B in parallel to the rear heat exchanger 9B with a small gap therebetween. Therefore, the auxiliary heat exchanger 10B is directly opposed to the upper suction port 5b and obliquely. It will be inclined backward.

Main heat exchanger 10A and auxiliary heat exchanger 10
B is a so-called finned tube type including a number of radiating fins F arranged side by side with a narrow gap therebetween and a heat exchange pipe P penetrating through the radiating fins and fitted by the expanding means. is there.

In the main heat exchanger 10A, two rows of heat exchange pipes P are arranged along the longitudinal direction of the front heat exchanger 9A and the rear heat exchanger 9B, and the rows are arranged with a certain distance from each other. In the mutual rows, the positions are shifted from each other in a so-called staggered manner.

The heat exchange pipe P has a straight portion folded back into a long U-shape, and the U-shaped portion protrudes from one end of the fins F arranged side by side. The other end opening protrudes from the other end of the fin, and these open ends of the heat exchange pipe are connected by a U-bend 18, a three-way bend 19, or a jumper pipe 20.

Heat exchange pipe P in front heat exchanger 9A
Of the rows, the row facing the front suction port 5a is on the heat exchange air introduction side, and the row on the windward side Up corresponds to the row facing the transverse flow fan 11, and the leeward row Dp is on the side facing the air outlet side.
Call.

Similarly, in the row of heat exchange pipes P in the rear heat exchanger 9B, the row facing the upper suction port 5b is the heat exchange air introduction side.
The row on the opposite side corresponds to the air outlet side, and is referred to as the leeward row Dp.

The heat exchange pipes P in the auxiliary heat exchanger 10B are arranged in a line along the longitudinal direction of the fins F. The heat exchange pipe P is formed by folding back into a U-shape. The U-shaped portion protrudes from one end of the fin, and the other end opening protruding from the other end of the fin is connected by a U-bend 18.

The auxiliary heat exchanger 10B is located on the upper side of the rear heat exchanger 9B, and is directly opposed to the upper suction port 5b. Which corresponds to the windward side. Similarly, the heat exchange pipe row P corresponds to a windward row with respect to the heat exchange pipe P row of the rear heat exchanger 9B.

A single flow path is formed between the main heat exchanger 10A and the auxiliary heat exchanger 10B so as to communicate the heat exchange pipes P provided in the heat exchanger 10. Explaining with reference to the flow of the refrigerant during the heating operation, the leeward side row Dp of the rear heat exchanger 9B is provided with two refrigerant inlets 21 that are divided.

From one of the refrigerant inlets 21, once descends to the inclined lower end of the rear heat exchanger 9B, moves up the windward row Up, and further moves to the windward row Up of the front heat exchanger 9A. Then, at this intermediate portion, a branch path leading to one connection end of the three-way bend 19 is formed, moving to the leeward row Dp.

From the other refrigerant inlet 21, the front heat exchanger 9 A is once passed through the inclined upper end of the rear heat exchanger 9 B.
To the leeward row Dp. Then, it goes around the lower end of the front heat exchanger 9A via the jumper pipe 20a provided here, and further moves up the windward side Up. In the middle part, the branch path moves to the leeward row Dp, and a branch path is formed to be guided to the other connection end of the three-way bend 19.

The third connection end of the three-way bend 19 and the lowermost heat exchange pipe of the auxiliary heat exchanger 10B are connected by a jumper pipe 20b indicated by a two-dot chain line. Then, a flow path configuration communicating with the refrigerant outlet 22 which is the uppermost end of the auxiliary heat exchanger is provided.

The cross flow fan 11 is connected to the front heat exchanger 9A.
On the back side of the vehicle, is arranged to a certain extent lower than the center part in the vertical direction, and is located at a connection part between the front heat exchanger 9A and the rear heat exchanger 9B and a lower part of the rear heat exchanger 9B. Will do.

In particular, since the front heat exchanger 9A is formed in an arc shape and its bending direction extends from the front part to the rear part, the front heat exchanger is bent so as to surround a part of the peripheral surface of the cross flow fan 11. It has been completed.

The distance between the rear side edge of the front heat exchanger 9A and the surface of the cross flow fan 11 is gradually approaching and gradually increasing, and the difference in the change is the same as that of the conventional heat exchanger (for example, the actual open flat 4−).
57073).

Thus, the cross flow fan 11 is rotationally driven in accordance with the refrigeration cycle operation, and the front and upper suction ports 5 are rotated.
Air to be conditioned is sucked into the unit main body 1 from a and 5b. The heat exchange air flows through the front heat exchanger 9A disposed opposite to the front suction port 5a to perform heat exchange. At the same time, the heat exchange air flows through the rear heat exchanger 9B via the auxiliary heat exchanger 10B arranged opposite to the upper suction port 5a to perform heat exchange.

The heat exchange air that has exchanged heat with these heat exchangers 9A, 9B, 10B is blown from the transverse flow fan 11 through the blowout port 14 through the blowout guide path 15, thereby achieving air conditioning of the room to be conditioned.

In particular, the heat exchanger 10 is provided with a new auxiliary heat exchanger 10B in addition to the main heat exchanger 10A composed of the front heat exchanger 9A and the rear heat exchanger 9B. The heat exchange capacity (volume) of the whole vessel increases, and the heat exchange capacity can be increased accordingly.

The heat exchange air guided from the upper suction port 5b must flow through the auxiliary heat exchanger 10B and the rear heat exchanger 9B, and the air flow is disturbed by the amount of the auxiliary heat exchanger 10B. Become.

In other words, the length of the portion farthest from the cross flow fan 11 in the heat exchange air flow direction is longer than the length of the vicinity of the cross flow fan 11 in the heat exchange air flow direction. Airflow will be disturbed by minutes.

However, since the portion where the large turbulence occurs is far from the cross flow fan 11, the turbulence after exiting the heat exchanger 10 is rectified to some extent before reaching the cross flow fan 11, so that the heat exchange Even if the length in the air circulation direction is increased, there is no adverse effect on the blowing characteristics and noise.

The auxiliary heat exchanger 10B has a box-shaped unit main body 1 formed by forming the heat exchanger 10 in an inverted V-shape.
Since it is provided for a dead space generated inside the unit, the capacity of the unit main body 1 is maintained as it is, and the installation space is not affected.

The heat exchange pipes P are provided with a single row of auxiliary heat exchangers 10B along the rear heat exchanger 9B in which the heat exchange pipes P are arranged in two rows. A total of three rows will be provided side by side.

In the rear heat exchanger 9B and the auxiliary heat exchanger 10B arranged side by side, the refrigerant inlet 21 for the heating operation is set in the most leeward row Dp, and the auxiliary heat exchanger in the most leeward row Dp. The refrigerant outlet 22 at the time of the same operation is set to 10B.

The temperature of the refrigerant introduced into the refrigerant inlet 21 is high since it has been discharged from a compressor (not shown). The refrigerant flows through the entire heat exchanger 10 and exchanges heat with the heat exchange air to reduce the temperature. I do.

That is, the temperature of the refrigerant at the refrigerant outlet 22 set in the auxiliary heat exchanger 10B, which is the most upwind side row, is low, and the temperature difference with the heat exchange air guided there is small. Therefore, the temperature difference between the refrigerant on the upstream side and the refrigerant on the downstream side can be increased, and the heat exchange efficiency of the heat exchanger 10 is improved.

In addition, the auxiliary heat exchanger 10B is arranged with a small gap with respect to the rear heat exchanger 9B. Therefore, the heat exchangers 9B and 10B are completely completely thermally separated from each other, and the rear heat exchanger 9B having the refrigerant inlet 21 having a high temperature during the heating operation and the refrigerant outlet having a low temperature. The heat exchange with the auxiliary heat exchanger 10B provided with the heat exchanger 22 is prevented, thereby preventing the performance from deteriorating.

When the cooling operation is performed, the flow of the refrigerant is opposite to that in the heating operation, the refrigerant flows from the auxiliary heat exchanger 10B into the main heat exchanger 10A, and the amount of drain water generated is increased by the auxiliary heat exchange. Heat exchanger 10B is the most, but the auxiliary heat exchanger 10B
Is completely separated from and parallel to the rear heat exchanger 9B, and the generated drain water flows down to the drain pan along the longitudinal direction of the fins similarly to the rear heat exchanger 9B. There is no influence on the rear heat exchanger B without dripping into the exchanger 9B.

The front heat exchanger 9A is connected to the cross flow fan 1A.
Since the first heat exchanger 9A is formed in an arc shape so as to substantially surround a part of the peripheral surface of the first heat exchanger 1, the difference in the space between the front heat exchanger 9A and the cross flow fan 11 having the largest intake air volume is extremely small in each part.

Therefore, the difference between the maximum distance and the minimum distance in the distance between the front heat exchanger 9A and the cross flow fan 11 is extremely small, the suction pressure and the amount of suction air of the heat exchange air become constant, and the blowing noise is reduced. And an improvement in heat exchange efficiency.

An indoor unit as shown in FIG. 2A may be used. Although each part is simplified in the figure,
Since the configuration is basically the same as that of the embodiment shown in FIG. 1, the same portions are denoted by the same reference numerals and a new description will be omitted.
(The same applies hereinafter.) Here, the heat exchanger 100A is formed in an inverted V-shape, and includes an arc-shaped front heat exchanger 9A and a straight rear heat exchanger 90A described later.

That is, the heat exchanger pipes P are arranged in three rows in the rear heat exchanger 90A. In the fin F, notch slits 25 are intermittently provided between the first row of heat exchange pipes on the windward side and the second row of heat exchange pipes.

Therefore, the fin portion provided with the heat exchange pipes in the first row and the fin portion provided with the heat exchange pipes in the second and third rows are formed integrally, and are completely formed. Manufacturability and assemblability are improved as compared with the separated one, and thermal isolation is also achieved to some extent. As a result, almost the same effect as the heat exchanger structure shown in FIG. can get.

A heat exchanger 100B as shown in FIG.
May be. This heat exchanger 100B is also formed in an inverted V-shape, and the front heat exchanger 9A is still formed in an arc shape. The heat exchanger pipes P are arranged in three rows in the straight rear heat exchanger 90B.

Therefore, the rear heat exchanger 90B does not have a thermal isolation structure, but has almost the same structure as the heat exchanger structure shown in FIG. 1, such as the arrangement of the front heat exchanger 9A. Is obtained.

The heat exchanger 100C shown in FIG.
Is convenient to explain. This heat exchanger 100C also
An arc-shaped front heat exchanger 9 formed in an inverted V-shape and described later.
0C and a straight rear heat exchanger 9B.

In the front heat exchanger 90C, three rows of heat exchange pipes P are arranged only in the upper part, and the width of the fins F is two rows of heat exchange pipes arranged from the middle part to the lower part. It is longer than the provided part.

The upper portion of the front side heat exchanger 90C is separated from the cross flow fan 11, and the fin width in the air flow direction at this portion is increased. As a result, the heat exchanger structure shown in FIG. It is almost the same, and the same operation and effect can be obtained. The same applies to the effective use of dead space in the unit body 1.

The heat exchanger 100D shown in FIG.
It is convenient to explain and claim 7. This heat exchanger 100D is also formed in the shape of an inverted V and is a connected body of the arc-shaped front heat exchanger 9A and the straight rear heat exchanger 9B.

An auxiliary heat exchanger 10C, which will be described later, is arranged on the windward side of the rear heat exchanger 9B with a small gap.
In the auxiliary heat exchanger 10C, the width and length of the fin Fa are smaller and the heat exchange area is smaller than that described in FIG.

The diameter φd2 of the heat exchange pipe Pa arranged in the auxiliary heat exchanger 10C is equal to the diameter of the front and rear heat exchangers 9A and 9B.
A heat exchange pipe P having a diameter smaller than the diameter φd1 is used. And the pipe pitch b of the heat exchange pipe Pa is
It is set to be smaller than the pipe pitch a of the heat exchange pipe P of the rear heat exchanger 9B.

Although not shown, the setting of the refrigerant inlet and the refrigerant outlet during the heating operation is the same as that shown in FIG. Therefore, in the auxiliary heat exchanger 10C provided with the refrigerant outlet, the refrigerant mainly flows in a liquefied state.

The liquefied refrigerant has a smaller specific volume than the gaseous or gas-liquid two-layer refrigerant, and the velocity of the refrigerant flowing through the heat exchange pipe Pa is low. That is, the refrigerant transfer rate in the heat exchange pipe is small, and as a result, the heat exchange performance of the refrigerant with the heat exchange air tends to be poor.

Therefore, the diameter of the heat exchange pipe Pa in the auxiliary heat exchanger 10C is reduced to increase the refrigerant speed, or the pipe pitch b is reduced and the flow path length is increased, so that the auxiliary heat exchanger 10C Heat exchange performance can be improved.

The rear heat exchanger 9B and the auxiliary heat exchanger 10B shown in FIG. 5 are convenient for explaining claim 8. The basic configuration of each of the heat exchangers 9B and 10B is described in FIG.
Are the same as those shown in FIG.

Here, the fin pitch will be described. That is, the fin pitch c of the auxiliary heat exchanger 10B located on the leeward side is wider than the fin pitch d of the rear heat exchanger 9B located on the leeward side.

From this, even if the auxiliary heat exchanger 10B is newly disposed upstream of the rear heat exchanger 9B, the fin pitch c is larger than the fin pitch d of the rear heat exchanger. An increase in the flow resistance to the heat exchange air can be suppressed as much as possible, the wind speed distribution of the entire heat exchanger 100E including the rear heat exchanger 9B can be made uniform, and noise can be reduced and heat exchange efficiency can be improved.

The heat exchanger 100E shown in FIG.
Is convenient to explain. This heat exchanger 100E also
An arc-shaped front heat exchanger 9A formed in an inverted V-shape;
It is a connected body of the straight rear heat exchanger 9B, and the auxiliary heat exchanger 10B is arranged with a small gap on the windward side of the rear heat exchanger.

The front heat exchanger 9A and the rear heat exchanger 9B are provided with two rows of heat exchange pipes P, and the auxiliary heat exchanger 10B is provided with one row of heat exchange pipes P. It is the same as the heat exchanger shown in FIG.

Here, slits 30 are provided in the entire front heat exchanger 9A and a part of the rear heat exchanger 9B. These cut-and-raised slits 30 protrude from both sides of the fin F, and efficiently come into contact with heat exchange air guided along both sides of the fin.

In other words, the cut-and-raised slits 30 are provided between the heat exchange pipes P in each row of the front heat exchanger 9A and in parallel with the center of the heat exchange pipes. The rear heat exchanger 9B is provided between the heat exchange pipes P in the leeward row Dp in parallel with the centers of the heat exchange pipes.

However, between the heat exchange pipes P in the windward side Up in the rear heat exchanger 9B and the auxiliary heat exchanger 10B
Have no slits. This is achieved by arranging the auxiliary heat exchanger 10B along the rear heat exchanger 9B so that the rear heat exchanger 9B and the auxiliary heat exchanger 10B
The flow resistance of the heat exchange air flowing therethrough increases and the flow resistance increases. However, by providing the cut-and-raised slit 30 only at the above-described position, the flow resistance of the front heat exchanger 9a increases, Heat exchanger 100E including rear heat exchanger 9B
A uniform wind speed distribution is achieved, so that noise is reduced and heat exchange efficiency is improved.

In each of the embodiments described above, all of the front heat exchangers 9A, 9A
Although 0C is formed in an arc shape, and has the above-described effects, the present invention is not limited to this, and a structure as described below may be used.

As shown in FIG. 7A, the heat exchanger 100F is formed in an inverted V-shape, and the rear heat exchanger 9B
The auxiliary heat exchanger 10B is arranged along the line.

However, the front-side heat exchanger 90D here is bent in multiple stages and is formed in a substantially arc shape. The position of the front heat exchanger 90D is exactly the same as that described above with reference to FIG. 1, and although the actual flow path configuration is slightly different, there is basically no difference, and therefore, almost the same operation and effect. To play.

A heat exchanger 100G as shown in FIG.
It may be. The configuration other than that the front-side heat exchanger 90E is formed in two pieces is the same as that shown in FIG. Therefore, almost the same operation and effect can be obtained. In addition, it goes without saying that various modifications can be made without departing from the scope of the present invention.

[0099]

As described above, according to the first aspect of the present invention, the length of the fins of the rear heat exchanger in the heat exchange air flow direction is reduced.
Than the length of the fins of the front heat exchanger in the heat exchange airflow direction
The rear heat generated by the longer airflow direction
The heat exchanger capacity of the exchanger is increased, so that the heat exchange capacity is increased and the blowing noise is reduced.

According to the second aspect of the present invention, the rear heat exchanger is
A heat exchanger and an auxiliary heat exchanger provided along the main heat exchanger
Fins of the rear heat exchanger
Make the length of the heat exchange air flow direction longer than that of the front heat exchanger.
The heat exchanger capacity of the rear heat exchanger increases because
It is possible to obtain an increase in heat exchange capacity and a reduction in blowing noise.

According to the third aspect of the present invention, since the fins of the front heat exchanger have a longer length in the airflow direction in the vicinity of the fin than in the part distant from the blower fan, the heat exchanger capacity of the front heat exchanger increases. As a result, the heat exchange capacity can be increased, and the blowing noise can be reduced.

According to the fourth aspect of the invention, at least three rows of heat exchange pipes are juxtaposed at a portion where the length in the airflow direction is increased,
Since the refrigerant inlet portion for the heating operation is formed in the leeward side row and the refrigerant outlet part is formed in the leeward side row, the temperature difference between the refrigerant on the leeward side and the leeward side can be made large, and the heat exchange efficiency can be improved.

According to the fifth aspect of the present invention, the leeward row having the refrigerant inlet and the leeward row having the refrigerant outlet are thermally insulated from each other. Parts are thermally isolated, preventing heat exchange with each other.

According to the sixth aspect of the present invention, among the heat exchange pipe rows thermally isolated from each other, the diameter of the heat exchange pipes in the windward side row is formed smaller than that in the leeward side row. The flow rate of the flowing refrigerant increases, and the heat transfer coefficient improves.

According to the seventh aspect of the present invention, among the heat exchange pipe rows thermally isolated from each other, the pipe pitch of the heat exchange pipes in the windward side row is formed narrower than that in the leeward side row. The flowing refrigerant is guided to a longer flow path,
The heat transfer coefficient is improved.

According to the eighth aspect of the present invention, the fin pitch of the heat exchanger fins of the windward side row is formed wider than that of the leeward side row among the heat exchange pipe rows thermally insulated from each other. The flow resistance can be suppressed as much as possible, the wind speed distribution of the entire heat exchanger can be made uniform, the heat exchange efficiency can be improved, and the blowing noise can be reduced.

According to the ninth aspect of the present invention, the heat exchanger fin having no thermally interrupted heat exchange pipe row is provided with a cut-and-raised slit.
Since the cut and raised slits are not provided in the heat exchanger fins on the windward side row, the cut and raised slit distribution can be set to make the flow resistance to the heat exchange air flowing through the fins uniform, and the heat exchanger as a whole The wind speed distribution can be made uniform, the heat exchange efficiency can be improved, and the blowing noise can be reduced.

According to the tenth aspect of the present invention, since the front heat exchanger is formed in an arc shape so as to surround a part of the peripheral surface of the blower fan, the heat exchange air flows smoothly through the front heat exchanger.
Blow noise can be reduced.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an indoor unit of an air conditioner incorporating a heat exchanger, showing one embodiment of the present invention.

FIG. 2A is a schematic vertical sectional view of an air conditioner indoor unit incorporating a heat exchanger according to another embodiment. (B)
The schematic longitudinal section of the air conditioner indoor unit which incorporated a heat exchanger of another example.

FIG. 3 is a schematic longitudinal sectional view of an air conditioner indoor unit incorporating a heat exchanger according to still another embodiment.

FIG. 4 is a schematic longitudinal sectional view of an air conditioner indoor unit incorporating a heat exchanger according to still another embodiment.

FIG. 5 is a diagram illustrating a fin pitch between an auxiliary heat exchanger and a rear heat exchanger according to still another embodiment.

FIG. 6 is a schematic longitudinal sectional view of an air conditioner indoor unit incorporating a heat exchanger according to still another embodiment.

FIG. 7A is a schematic longitudinal sectional view of an air conditioner indoor unit incorporating a heat exchanger according to still another embodiment.
(B) is a schematic longitudinal sectional view of an air conditioner indoor unit incorporating a heat exchanger according to still another embodiment.

[Explanation of symbols]

5a: front inlet, 5b: upper inlet, 14: outlet, 1 ... air conditioner body (unit body), 10: heat exchanger, 11: blower fan (lateral fan), F: fin, P ... Heat exchange pipe, 9A: front heat exchanger, 9B: rear heat exchanger, 10B: auxiliary heat exchanger, 30: cut and raised slit.

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Susumu Nagakura 336 Tatehara, Fuji City, Shizuoka Prefecture Inside the Toshiba Fuji Plant (72) Inventor Koji Wada 336 Tatehara Field Fuji, Shizuoka Prefecture Inside the Toshiba Fuji Plant ( 72) Inventor Hideaki Suzuki 336 Tatehara, Fuji City, Shizuoka Prefecture Inside the Toshiba Fuji Factory (72) Inventor Yoshiro Nakamura 336 Tatehara Field Fuji in Shizuoka Prefecture Inside the Toshiba Fuji Factory (72) Inventor Takashi Kakigi Shizuoka Prefecture 336 Tatehara, Fuji City Inside the Toshiba Fuji Factory (56) References JP-A-6-26778 (JP, A) JP-A-4-222363 (JP, A) Jikai 56-811212 (JP, U) Japanese Utility Model Showa 62-192128 (JP, U) Japanese Utility Model Showa 63-99124 (JP, U) Japanese Utility Model Showa 62-187218 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F24F 1/00

Claims (10)

(57) [Claims] 1. An air conditioner main body having a suction port provided at a front part and an upper part thereof and a blow-off port provided at a lower part of a front surface, and a heat exchanger and an air-conditioned room housed and disposed inside the air conditioner main body. In an air conditioner having a blower fan having a circular cross section for guiding heat exchange air to a heat exchanger, the heat exchanger includes a plurality of fins arranged side by side with a narrow gap therebetween, and heat is applied to these fins. in finned tube type exchange pipe is penetrated consists of a said front suction port and the upper suction port and the front heat bent inverted V-shape in side view so as to face exchanger and the rear heat exchanger, the The fins that make up the rear heat exchanger are
The air conditioner is characterized in that the length in the direction is longer than the length in the heat exchange air flow direction of the fins constituting the front heat exchanger . 2. The rear heat exchanger comprises a main heat exchanger and the main heat exchanger.
Combination with an auxiliary heat exchanger provided along the heat exchanger
From the main heat exchanger and the auxiliary heat exchanger.
The length in the exchange air flow direction constitutes the front heat exchanger.
Fins that are longer than the length of the fins
The air conditioner according to claim 1, characterized in that. 3. A suction port is provided at a front portion and an upper portion thereof.
Air conditioner with an outlet at the bottom of the front
The main unit, and a heat exchanger and
And a circular cross section to guide the heat exchange air from the air-conditioned room to the heat exchanger.
In an air conditioner provided with a wind fan, the heat exchanger has a large number of fins with a narrow gap therebetween.
Heat exchange pipes penetrate these fins
Fin tube type.
And folded into an inverted V shape in side view so as to face the upper suction port
The fins that comprise the bent front heat exchanger and the rear heat exchanger, and constitute the front heat exchanger,
Exchange airflow in the uppermost part, which is furthest from the air
The length of the passage direction, put at the bottom is a blower fan site near
The air conditioner is formed to be longer than the length of the heat exchange air flow direction . 4. A portion of the front heat exchanger and the rear heat exchanger where the length of the heat exchange air flow direction is long, at least three rows of heat exchange pipes are arranged in the flow direction of the heat exchange air. 4. A refrigerant inlet portion during the heating operation is formed in the leeward row, and a refrigerant outlet portion during the same operation is formed in the leeward row.
The air conditioner as described. 5. The leeward row of the heat exchange pipes having the refrigerant inlet and the leeward rows of the heat exchange pipes having the refrigerant outlet are thermally isolated from each other. Item 4. The air conditioner according to Item 4. 6. The heat exchange pipe row of the windward side of the row of heat exchange pipes that are thermally isolated from each other is formed smaller than the diameter of the heat exchange pipe of the leeward side row. Item 6. The air conditioner according to Item 5. 7. The heat exchange pipes of the heat exchange pipes which are thermally insulated from each other, wherein the pipe pitch of the heat exchange pipes of the leeward row is formed narrower than the pipe pitch of the heat exchange pipes of the leeward row. The air conditioner according to claim 5, wherein 8. The fin pitch of the fins constituting the heat exchangers in the leeward side row of the heat exchange pipe rows thermally isolated from each other is greater than the fin pitch of the fins constituting the leeward side row heat exchangers. 6. The semiconductor device according to claim 5, wherein:
The air conditioner as described. 9. A slit formed by cutting and raising a fin constituting a heat exchanger which does not have a heat-exchanged heat exchange pipe row among the front heat exchanger and the rear heat exchanger, The air conditioner according to claim 5, wherein, of the heat exchange pipe rows that are thermally insulated from each other, the fins that constitute the heat exchangers in the windward row do not have cut-and-raised slits. 10. The air conditioner according to claim 1, wherein the front heat exchanger is formed in an arc shape so as to surround a part of a peripheral surface of the blower fan.