KR101347612B1 - Heat source machine and refrigerating cycle apparatus - Google Patents

Abstract

An object of the present invention is to provide a heat source device and a refrigeration cycle apparatus capable of reducing fan input by improving the blowing performance of a fan grill.
The present invention relates to a heat source apparatus and a refrigeration cycle apparatus having a fan and a fan grill, wherein the fan grill has a front portion through which the mainstream of the airflow made by the fan is passed, and a side portion disposed along the direction of the mainstream. The front part has a rectangular shape when viewed from the front, and the vent part is provided on the side part, and an air flow adjusting part is installed between the front part and the side part to adjust the air flow passing through the front part and the side part. The airflow adjusting part has a plate shape in which the length dimension along the direction of the mainstream is larger than the thickness dimension.

Description

HEAT SOURCE MACHINE AND REFRIGERATING CYCLE APPARATUS}

The present invention relates to a heat source device and a refrigeration cycle apparatus.

In recent years, the energy-saving performance improvement of refrigeration cycle apparatuses, such as a heat pump water heater and an air conditioner, has become a bigger subject, and the expectation to reduce the fan input of the heat source machine which comprises such a refrigeration cycle apparatus is also large. As a background art of this technical field, Unexamined-Japanese-Patent No. 2010-181116 (patent document 1) is mentioned. This publication describes an air conditioner, wherein a notch portion in which an air passage is formed is provided in a frame that forms a blower grill outer periphery.

Japanese Patent Publication No. 2010-181116

However, in this well-known example, the blowing performance was not fully considered. Specifically, in this well-known example, although the ventilation resistance was reduced by providing an opening part in the fan grill side surface, it does not have a structure which suppresses the turbulence of the airflow in the part which distinguishes a front part and a side part, but does not have a fan input. There was a fear of getting higher.

Then, an object of this invention is to provide the heat source machine which can reduce a fan input by improving the blowing performance of a fan grill.

In order to solve the said subject, this invention employ | adopts the structure of a claim, for example.

That is, the present invention is a heat source device having a fan and a fan grill, wherein the fan grill has a front portion through which the mainstream of the airflow made by the fan passes, and a side portion disposed along the direction of the mainstream. The front part has a square shape when viewed from the front, and a ventilation part is provided in the side part, and an air flow adjusting part is installed between the front part and the side part to adjust the air flow passing through the front part and the side part. The airflow adjusting part has a plate shape in which the length dimension along the direction of the mainstream is larger than the thickness dimension.

According to the present invention, the fan input can be reduced by reducing the ventilation resistance.

1 is a perspective view of an entire heat source machine according to a first embodiment.
Fig. 2 is a front view of the entire fan grill of the heat source machine according to the first embodiment.
3 is a perspective view of the fan grill in the heat source apparatus according to the first embodiment;
4 is a cross-sectional view illustrating a cross section taken along a line 3A-3A in FIG. 3.
Fig. 5 is a side view of each part of the fan grill of the heat source machine according to the first embodiment.
Fig. 6 is a front perspective view of each part of the fan grill of the heat source machine according to the first embodiment.
7 is a center sectional view of a fan grill of a heat source machine according to Example 1;
8 is a center sectional view of a fan grill of a heat source machine according to Example 2;
9 is a partial front view of the fan grill of the heat source machine according to the third embodiment.

Hereinafter, an embodiment will be described with reference to the drawings.

Example 1

As shown in FIG. 1, the heat source unit 100 includes a front panel 101 and a fan grille 102 provided on the front side of the heat source 100, and the heat exchanger 104 is provided by the ventilation of the fan 103 as the fan 103 rotates. Heat exchange is taking place. On the other hand, the heat source device 100 is also called a heat pump unit. As the fan 103, a propeller fan is used specifically.

The heat exchanger 104 consists of a heat exchanger tube and a heat exchange fin, is formed in an L shape, is located over the back and side surfaces of the heat source 100, and is disposed on the suction side of the fan 103. In the heat exchanger 104, the air vented by the fan 103 and the heat medium in the heat exchanger tube exchange heat through the heat exchanger tube and the heat exchange fins.

The fan grill 102 has a front portion 106 for passing the mainstream 120 of the air flow produced by the fan, and a side portion 107 disposed along the direction of the mainstream. The side portion 107 includes a ventilation portion. Is installed. Specifically, the side surface portion 107 is provided with a plurality of plate-shaped side ribs 203 along the front surface portion 106 and in a direction crossing the side surface portions 107. That is, among the air streams discharged from the fan grill 102, the air flow to the front is the main stream 120, and as the other air streams, the air flow 111 at each part and the air flow at the center of the side as the air flow 110 to the side ( 113, a short circuit wind 114, which is a stream of air 112 at an intermediate position between the corners and the center, and a stream of air entering the heat exchanger from the front panel 101.

2 shows a front view of the fan grill 102. The fan grill 102 has a square shape when viewed from the front, and the upper, lower, left, and right sides are roughly the same shape. The opening part 105 of the front panel 101 which is a ventilation opening from the fan 103 is shown as the broken line circle 105a.

FIG. 3 is a perspective view of the fan grill 102 in FIG. 1, and broken lines 102a are outline outlines of the fan grill 102. The mouth ring 330 which is a cylindrical ventilation part is provided in the fan 103 side from the opening part 105 of the front panel 101 which is a ventilation opening from the fan 103. As shown in FIG. Through this mouth ring 330, the mainstream 120, which is an air flow to the front, is sucked out.

Moreover, the airflow through the mouth ring 330 is sucked out to bend along the front panel surface by the Coanda effect not only in the front side but also in the side, for example, the airflow 113 of a center part, and the airflow 111 to each part. Becomes Since the fan grill 102 becomes an outlet resistance, the flow to this side arises as a flow which leaks from the grill side surface since the liquor 120 is inhibited compared with the case where the grill is not provided, for example.

4 is a cross-sectional view taken along the line 3A-3A including the fan grill 102 and the fan 103 from the front panel 101 of FIG. 3 at a position on the front left of the heat source 100. 5 and 6 are views of the fan grill right angle portion 210 shown in FIG. 2 as viewed from the side and inclined front, respectively.

The front teeth 202 and the side teeth 203 are plate-shaped meats provided so as not to come into contact with the rotating fan when foreign matter, in particular, a human finger is accidentally inserted into the rotating fan 103. The side face 203 is a plate-shaped flesh having a plate width 3B, and the directivity of the airflow is improved.

On the other hand, as shown in FIG. 2, the front surface flesh 202 which extends radially radially from the center disc 220 is inclined or curved with respect to the front surface part, and the surface 202S of the heat source device 100 It is seen from the front side. As a result, by redirecting the velocity energy of the swirling component of the air flow from the rotating fan 103, it has a function of recovering the static pressure and improving the air blowing performance together with the protection function. Since the fan grill 102 is formed of synthetic resin by injection molding, it can be manufactured easily.

And the fan grill 102 is provided between the front part 106 and the side part 107, and the airflow adjustment part which adjusts the airflow which passes through the front part 106 and the said side part 107 is provided. Hereinafter, this airflow adjustment part is arrange | positioned downstream from an upstream airflow adjustment part mentioned later, and is called a downstream airflow adjustment part for convenience.

The downstream airflow adjusting portion is constituted by the outer rib 204. The outer rib 204 protrudes from the front position 300 of the front panel 101, and the ventilation by the fan 103 is also laterally from the side space between the front panel 101 and the outer rib 204. Since it exits as the airflow 110, the opening area of the fan grill 102 increases, the ventilation resistance decreases, and the air blowing performance improves, so the fan input decreases. In FIG. 3, front face 202 is hidden within outer rib 204. In addition, in this embodiment, although the outer rib 204 has such a function not only as a function of airflow adjustment but also a function as a reinforcement rib, it makes such a name, but as an airflow adjustment part, it does not have a function as a reinforcement rib especially. May be used. The same applies to the inner rib 205 described later.

The outer rib 204 has a plate shape whose length dimension along the direction of the liquor 120 is larger than the thickness dimension. Since the outer rib 204 is a cylindrical structure having a length 204A, the airflow toward the front is discharged with high directivity. This high directivity makes it difficult for airflow to diffuse laterally, so that energy consumption during diffusion is suppressed and the fan input is lowered. In addition, when the diffusion causes air to be heat exchanged to stay in the vicinity of the heat source 100, the heat exchange performance is lowered, but because it is avoided, the energy saving performance of the entire apparatus is improved.

Furthermore, an upstream side airflow adjustment part parallel to a downstream side airflow adjustment part is provided in an upstream side rather than a downstream side airflow adjustment part. The upstream side airflow adjustment part is constituted by the inner rib 205. That is, the inner rib 205 is provided on the front panel 101 side of the outer rib 204.

The inner ribs 205 support the side ribs 203 to improve the strength of the fan grill 102, and, like the outer ribs 204, the main stream 110 that is laterally and the main stream that is forward. It has a function of suppressing 120 from mixing in the region 302 in the oblique direction from the front panel. That is, the flow velocity of the air flow 110 toward the side decreases with respect to the front panel front side. At this time, when the airflow 110 to the side and the mainstream 120 to the front are mixed, the fan input is increased because the blowing energy is dissipated due to the generation of vortex. In addition, since the air heat exchanged by mixing becomes difficult to diffuse around, the overall heat exchange performance is lowered. Therefore, although the energy saving performance of the whole apparatus falls, they are avoided in this embodiment, contributing to the improvement of energy saving performance.

As shown to FIG. 1, FIG. 2, the side surface flesh 203 arrange | positioned at the side surface part 107 is set so that the space | interval of side surface flesh 203 may become large as it moves away from the center part of the fan grill 102. As shown to FIG. . Referring to FIG. 2, the distance between the side ribs 203 is gradually increased as 2A, 2B, 2C as the center portion 211 of the fan grill 102 approaches the corner portion 210. For example, The distance 2C at each part is twice as large as the distance 2A at the center. Since the interval is gradually changing, the wind speed of the air stream emitted is also gradually changing continuously. At this time, in a place where there is a large difference in the flow velocity of the air flow, a vortex is generated to fill a large speed difference, resulting in a loss of blowing energy, leading to an increase in fan input, but in the present embodiment, it is avoided, and the blowing performance is improved. It contributes to reducing fan input. At this time, since the center space | interval 2A is close to the fan opening part 105, making it narrow makes it difficult for a finger to enter and improves safety. On the other hand, since each part of the fan grille 102 is separated from the front panel opening 105, there is no fear that a finger touches the fan, so that the gap 2C is increased to increase the opening area of the fan grille 102 and ventilate. Lowering the resistance improves the blowing performance.

In addition, as shown to FIG. 1, FIG. 2, the side surface flesh 203 arrange | positioned at the side surface part 107 sets so that the inclination angle with respect to the side surface part 107 may become large, as it falls from the center part of the fan grill 102. As shown in FIG. It is. Referring to FIG. 2, the angles 2D and 2E to the horizontal of the side ribs 203 also increase gradually and nearly continuously as they approach the corner portions from the center of the fan grill 102. Thus, the airflow emitted with directivity is emitted laterally in a radial shape. Therefore, as compared with the case where the airflows are discharged in parallel, energy loss caused by friction between the airflows, collision of the airflows, and the like can be suppressed. Moreover, in general, since the respective portions of the fan grill 102 are separated from the front panel opening 105, the flow rate of the air flow is slow, and the air flow tends to stay. At this time, since the air which should be heat exchanged stays, there is a possibility that the heat exchange performance is lowered and the energy saving performance is lowered. In addition, more blowing energy is required in order to remove the airflow remaining, so that the fan input is increased and the energy saving performance is lowered.

In addition, as shown to FIG. 1, FIG. 2, the side surface flesh 203 arrange | positioned at the side surface part 107 is set so that the dimension of the direction which cross | intersects the side surface part 107 may become large, as it moves away from the center part of a fan grill. have. Referring to FIG. 2, since the width 2N in the radial direction of the side teeth 203 of the leg portion 210 is longer than the width 2M of the center portion 211, the directivity of the airflow is increased.

In addition, in the present embodiment, as described above, since the spacing of the flesh is larger than that of the center portion 2A, as in the corner portions 2C, the leakage of the air flow in the corner portions 210 is improved, and the air flow hardly stays. For this reason, it contributes to the improvement of energy saving performance. On the other hand, the airflow at the center of the fan grill 102 is increased in directivity so that the airflow is discharged in parallel with the front panel 101 by the side ribs 203. Therefore, since the short circuit wind 114 which returns to the heat exchanger 104 side from the front panel 101 side and heat-exchanged high temperature airflow enters the heat exchanger 104 is suppressed, it contributes to the improvement of energy saving performance. . On the other hand, if the side of the fan grill 102 is blocked, the short circuit can be better prevented. However, according to the present embodiment, even when the side is opened, the effect of reducing the short circuit airflow 114 is reduced. There is.

On the other hand, for example, when the outer shape of the fan grill 102 is circular when viewed from the front of the front panel 101, the side ribs 203 of the fan grill 102 are positioned near the front panel opening 105 having a high wind speed. It becomes a big ventilation resistance. In addition, since it is close to the opening, a human finger is likely to come into contact with the fan 103, so it is necessary to narrow the interval between the side walls 203, resulting in large ventilation resistance. On the other hand, in the case of each shape as in the present embodiment, since the side ribs 203 are located at a position far from the front panel opening portion 105 in particular, the wind speed is lowered, and it is difficult to become a ventilation resistance, and the fan input is lowered. Can be suppressed.

As shown in FIG. 4, the air attracting part 401 is provided in each part of the fan grill 102 between the front panel 101 and the front surface flesh 202. As shown in FIG. Here, the flow 410 in which the airflow which exited the front panel opening part 105 bends by the Coanda effect etc. in the front panel 101 arises. On the other hand, the airflows 414 and 415 directed toward the front panel become the mainstream 120. The wind speed is slower on the side away from the opening portion 105, and the heat exchanged air flow easily tends to stay, and the heat exchange performance tends to decrease. However, in the present embodiment, since the outer ribs 204 are cylindrical in the mainstream direction to increase directivity, the airflow 416 along the outer ribs 204 is easy to join the mainstream 120 and is easily blown.

The airflow 411 passing through the side ribs 203 flows to avoid the side ribs 203 when passing between the side ribs 203, and the air flows 601a and 601b which sandwich the side ribs 203 intersect. do. Here, the thickness 3B of the side teeth 203 is thin with respect to the length 3A. Therefore, as shown in FIG. 6, the airflow 601a, 601b which collides and collides with the side flesh 203 smoothly branches in the branch part 601c near the side meat 203, and joins part 601d. ) Joins smoothly. For this reason, the loss of airflow due to the formation of vortices and the peeling of the flow is unlikely to occur, and the fan input reduction can be suppressed. Moreover, since the side wall 203 has a plate shape and thin plate thickness, since the opening area of the side surface of the fan grill 102 increases and a pressure loss falls, it is preferable. On the other hand, when the length 3A of the side ribs 203 is long when the airflow 401 passes through, it becomes a resistor and causes a loss, but in this embodiment, the length is appropriate.

As shown in FIG. 4, the airflow 413 passing between the inner rib 205 and the outer rib 204 has high directivity by the inner rib, and for example, the front panel (such as the airflow 412). The flow that goes to the 101 side and joins the air flow 411 is weakening. In addition, with respect to the airflow 417 along the outer rib 204, since the thickness of the outer rib 204 is thin and the length is appropriate, the loss by the confluence of the airflow 417 and the airflow 416 is reduced.

As shown in FIG. 2, for example, the lateral meat spacing is the minimum size of 7 mm at 2A close to the grill center 211 and the maximum size of 14 mm at 2C close to the corner 210, about twice the minimum size. do. Here, in JIS-C0922, as an inspection probe, an inspection probe (diameter 12 mm, length 80 mm) for an adult based on an adult's finger, and an inspection probe for a child (diameter 5.6 based on a child's finger) Mm, length 44 mm). In the fan grille 102 of this embodiment, the minimum spacing dimension is larger than the diameter (5.6 mm) of the inspection probe for the child, but the inspection probe for the child is short in length, so that the fan 103 can be inserted even from the fan grill center 211. Not reach) On the other hand, in each part 210, although an adult test | inspection probe (diameter 12mm) for a long length is insertable, since the distance to the front panel opening part 105 becomes far, it does not reach even if it inserts. Therefore, it is considered safe.

As shown in FIG. 5, the outer rib 204 has a plate shape, the length 204A of the rib is 13 mm, the thickness 204B of the rib is 2.6 mm, and the thickness is 1 with respect to the length of the liquor 120 direction. It becomes ratio less than / 5 times and is thin. Moreover, it is thin about 1/200 with respect to the length 475mm of one side of a front side. The thin thickness thus contributes to the increase of the fan grill opening ratio and reduces the loss. Moreover, since the longitudinal direction is parallel to the mainstream which is the airflow toward the front, it contributes to the improvement of the directivity of the airflow 120 toward the front. On the other hand, the cross-sectional shape of the inner rib 205 is a rod shape in which the ratio of the length 205A and the thickness 205B of the inner rib is close to 1/1. Therefore, the sensitivity of the angle when the airflow flows into the rib is Low, contributing to the reduction of losses.

In addition, in the fan grill 102, the space | interval of an upstream airflow adjustment part and the upstream end of a fan grill is equal to or more than the space | interval of a downstream airflow adjustment part and an upstream airflow adjustment part. Referring to FIG. 5, for the distance 3D from the front panel surface 300 to the inner rib 205 and the distance 3E from the inner rib 205 to the outer rib 204, 3D is represented. Equal to or larger than 3E is preferable because the opening area to the side airflow is increased to reduce the pressure loss, or the directivity of the airflow 110 to the side is improved. For example, it is preferable that 3D be 5 times or more, such as 21 mm and 3E.

For example, it is preferable that the width 3A of the side meat 203 is 5.8 mm, the thickness 3B of the meat 3.2 mm, and the ratio of the width and the thickness is 1.5 times or more. In addition, the side ribs 203 are inclined at an angle equal to the angle 3C from the horizontal (for example, about 8 degrees from the horizontal direction) so that the air flow 110 toward the side is more easily radiated. At this time, since the side surface of the fan grill 102 becomes an inclined surface, the opening area is increased to reduce the pressure loss, and airflow in the direction falling from the front panel 101 is generated without generating airflow parallel to the front panel surface 300. As a result, the short circuit airflow 114 is less likely to occur and contributes to improving energy saving performance.

7 is a cross-sectional view of the center disc 220 of the fan grill 102. The left side is the region 501 on the fan 103 side toward the ground, and the right side is the region 502 on the suction side on the atmospheric side. The center disc 220 binds the front flesh 202 to improve the strength of the entire pan grill 102 as a strength member.

[Example 2]

Next, Example 2 of this invention is described using FIG. The fan grill 102 according to the second embodiment differs from the fan grill 102 according to the first embodiment only in the structure of the central disc 220. In the following, only differences from the first embodiment will be described. Since the other structures are basically the same as those in the first embodiment, the description is omitted.

In the fan grill 102 of Example 1, as shown in FIG. 7, the fixed vortex 510 is formed by receiving the shear force by the airflow 120 toward the front from the fan 103 in the vicinity of the center disc 220. There is a risk of loss between the fixed vortex 510 and the air stream 120 forward. In addition, in the present Example shown in FIG. 8, the space | gap 520 is formed in the center disc 220. As shown in FIG. At this time, since the fixed vortex 510 by the mainstream 120 is formed in the void 520, the area where the fixed vortex 510 and the mainstream 120 contact each other becomes narrow, so that the loss caused by the fixed vortex 510 is reduced. Can be reduced. Therefore, the air blowing performance can be improved and the fan input can be reduced.

The shape of the void 520 is preferable as long as the shape of the void is the same as that of the central disk 220 because the vortex is stably formed. If the position of the center disc 220 does not come out to the side 502 which sucks out from the front surface flesh 202, friction loss with the mainstream 120 will disappear, and fan input will fall. Therefore, it is preferable that the front end surface of the center disc 220 is arrange | positioned on the same plane as the front surface flesh 202. As shown in FIG. Since the depth of the space | gap 520 deepens also the friction loss between the inner wall surface of the center disk 220 and a fixed vortex, when it is deep, it is desirable to suppress it to about the same dimension as the radius of the space | gap 520.

[Example 3]

Next, Example 3 of this invention is described using FIG. The fan grill 102 according to the third embodiment differs from the fan grill 102 according to the first embodiment only in the structure of the side ribs 203. In the following, only differences from the first embodiment will be described. Since the other structures are basically the same as those in the first embodiment, the description is omitted.

As shown in FIG. 2, the side face 203 in Example 1 was comprised radially, but the side face 203 in Example 3 has the fan 103 as shown in FIG. It is inclined to the rotation direction 601 of ().

The airflow 110 from the fan 103 to the side is released as the swinging airflow 602 in the direction according to the rotation of the fan 103, but according to the present embodiment, the side ribs 203 are along the turning direction. Because swirl airflow 602 is released along side flesh 203, losses are less likely to occur. Therefore, the air blowing performance is improved, the fan input is lowered, contributing to the improvement of energy saving performance.

100: heat source machine
101: front panel
102: pan grill
103: fan
104: heat exchanger

Claims (7)

As a heat source machine having a fan and a fan grill,
The fan grill has a front portion through which the main stream of air flow made by the fan passes, and a side part disposed along the direction of the main stream,
The front portion has a square shape when viewed from the front,
The side part is provided with a ventilation portion,
Between the front portion and the side portion, an air flow adjusting portion for adjusting the air flow passing through the front portion and the side portion is provided,
The airflow adjusting part has a plate shape in which the length dimension along the direction of the mainstream is larger than the thickness dimension,
The upstream side airflow adjustment part parallel to the said airflow adjustment part is provided in an upstream side than the said airflow adjustment part,
The interval between the upstream side airflow adjustment part and the upstream end part of the said fan grill is equal to or more than the space | interval of the said airflow adjustment part and the upstream side airflow adjustment part. The method of claim 1,
The heat source device characterized in that a plurality of plate-shaped flesh is disposed on the side surface portion along the front surface portion and in a direction crossing the side surface portion. 3. The method of claim 2,
The heat arranged in the side part is set so that the space | interval of flesh becomes large as it moves away from the center of a pan grill. 3. The method of claim 2,
The flesh disposed on the side portion is set so that the inclination angle with respect to the side portion is increased as it is separated from the center of the fan grill. 3. The method of claim 2,
The heat disposed in the side part is set so that the dimension of the direction which cross | intersects the said side part becomes large as it moves away from the center part of a fan grill. delete The refrigeration cycle apparatus provided with the heat source group in any one of Claims 1-5.

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