JP7546192B2 - Fluid Transport Device - Google Patents

Description

The present invention relates to a fluid transport device for efficiently transporting fluids such as air for purposes such as heating and cooling.

When cooling or heating large spaces such as factories, warehouses, stadiums, and commercial kitchens, a fluid ejection nozzle 101 as shown in FIG. 14 is used as an outlet structure for directing conditioned air to a target location. This fluid ejection nozzle 101 has a circular opening 103 formed in an air conditioning duct 102, a brim-shaped member 104 fixed to the opening 103, and a fixed member 105 with an R-shaped side portion fixed to the brim-shaped member 104. A substantially semicircular nozzle body (ball portion) 106 is disposed within the fixed member 105 so as to be movable in any direction around its central axis, and the lower end side of the nozzle body 106 has a cylindrical blowing portion 107. This configuration allows conditioned air to be blown out in a spot in any direction.

Japanese Utility Model Application Publication No. 5-73441

When conditioned air A is blown out from the blowing portion 107 in such a fluid ejection nozzle 101, the surrounding space air (ambient air B) is attracted near the blowing portion 107. For example, in the case of cooling operation in the summer, the ambient air B is hotter than the cold conditioned air A (cooling air) blown out from the blowing portion 107, and this hot air reaches the target cooling area due to the attraction effect, reducing the cooling effect. Similarly, in the case of heating operation in the winter, the ambient air B, which is colder than the warm conditioned air A (heating air) blown out from the blowing portion 107, reaches the target heating area due to the attraction effect, reducing the heating effect.

In addition, in the case of such a fluid ejection nozzle 101, when the conditioned air A reaches the location to be cooled, the jet may hit a person directly, for example, and the person may feel uncomfortable due to the wind pressure caused by the flow speed and wind noise around the ears. In addition, for example, in the case of air conditioning in a factory, if there are manufactured products, manufacturing equipment, liquids, etc. that need to be avoided from being affected by the wind pressure at the point where the jet reaches, other fluid transport means are required.

In addition, in the case of a stratified air conditioning system, which is another fluid transport means, the problems associated with the wind pressure of the fluid ejection nozzle 101 described above can be solved. However, in a stratified air conditioning system, when a transient change in pressure occurs in the space, for example when a shutter in a factory is opened, the gas remaining in the living area will flow out. In that case, there is a problem that time and energy are lost until the temperature and humidity become appropriate again.

The present invention aims to solve these problems and provide a fluid transport device that can efficiently transport fluid while suppressing the attraction effect, and minimize discomfort caused by wind pressure.

To achieve this object, the fluid transport device of the present invention comprises:
A nozzle portion for ejecting conditioned air is provided.
The nozzle portion is
A first jet outlet;
a second jet outlet formed in an annular shape on an outer circumferential side of the first jet outlet so as to surround an outer circumferential side of the first jet outlet and jetting the fluid as an annular jet;
a third jet outlet that is adjacent to an outer periphery of the second jet outlet and is formed in an annular shape so as to surround an outer periphery of the second jet outlet and jets out a fluid as an annular jet,
When the flow velocities (wind speeds) of the air blown out from the first outlet, the second outlet, and the third outlet are U1, U2, and U3, respectively,
The intended purpose is achieved by blowing out air in such a manner that U2>U1 and U2>U3.

According to the present invention, by making the jet velocity of the jets ejected from the first and third nozzles slower than that of the jet ejected from the second nozzle, the jet ejected from the third nozzle can reduce the shear force caused by the speed difference between the jet ejected from the second nozzle and the surrounding fluid, making it possible to suppress the attraction of surrounding fluid due to the attraction effect. In addition, the jet ejected from the first nozzle is transported far away by the jet ejected from the second nozzle, and the jet ejected from the second nozzle is decelerated by the jet ejected from the first nozzle, making it possible to transport the jet far away while suppressing the ejection speed. Therefore, by creating an ejection speed difference between the three nozzles, it is possible to suppress the attraction of surrounding fluid and transport the conditioned air far away while suppressing the wind speed, making it possible to create a comfortable air-conditioned space that minimizes discomfort caused by the wind pressure of the fluid.

FIG. 1 is an explanatory diagram showing a configuration of a fluid transporting device according to a first embodiment of the present invention; FIG. 1 is an enlarged cross-sectional view showing a configuration of a fluid transporting device according to a first embodiment of the present invention; FIG. 11 is a cross-sectional view showing a change in the velocity distribution of a jet of a conventional fluid transport device (comparative example); FIG. 1 is a cross-sectional view showing a change in the velocity distribution of a jet according to the first embodiment of the present invention (Example); FIG. 11 is an enlarged cross-sectional view showing the configuration of a fluid transporting device according to a second embodiment of the present invention. FIG. 11 is an enlarged cross-sectional view showing the configuration of a fluid transporting device according to a third embodiment of the present invention. FIG. 11 is a perspective view of a fluid transporting device according to a fourth embodiment of the present invention; FIG. 13 is a perspective view of an extension part which is a component of a fluid transporting device according to a fourth embodiment of the present invention; FIG. 11 is a cross-sectional view of a fluid transporting device according to a fourth embodiment of the present invention. FIG. 13 is a cross-sectional view simulating a peeled region in a structure similar to that of the fourth embodiment of the present invention. FIG. 13 is a cross-sectional view simulating a peeled region in a structure similar to that of the fourth embodiment of the present invention. 1A is a perspective view of a first modified example of the fourth embodiment of the present invention; FIG. 1B is a cross-sectional view of the first modified example of the fourth embodiment of the present invention; 2 is a cross-sectional view of a second modification of the fourth embodiment of the present invention; FIG. 1 is an explanatory diagram showing the configuration of a conventional fluid transport device;

The fluid transport device according to the present invention has a nozzle section that sprays conditioned air, the nozzle section having a first outlet, a second outlet formed in an annular shape on the outer periphery of the first outlet so as to surround the outer periphery of the first outlet and spraying the fluid as an annular jet, and a third outlet formed in an annular shape adjacent to the outer periphery of the second outlet so as to surround the outer periphery of the second outlet and spraying the fluid as an annular jet, and the flow speed (wind speed) of the air blown out from the first outlet, the second outlet and the third outlet are U1, U2 and U3, respectively, such that U2>U1 and U2>U3.

With this configuration, the jet ejected from the third nozzle can reduce the shear force caused by the speed difference between the jet ejected from the second nozzle and the surrounding fluid, making it possible to suppress the attraction of surrounding fluid due to the attraction effect. In addition, the jet ejected from the first nozzle is transported far away by the jet ejected from the second nozzle, and the jet ejected from the second nozzle is slowed down by the jet ejected from the first nozzle, making it possible to transport the air far away while suppressing the ejection speed. Therefore, by creating a difference in ejection speed using three nozzles, it is possible to suppress the attraction of surrounding fluid and transport the conditioned air far away while suppressing the wind speed, thereby providing a comfortable air-conditioned space with as little discomfort as possible caused by the wind pressure of the fluid.

The air flow rate from the first and third air outlets may be set to be U1 ≧ U3.

The device may also have a first flow path communicating with the first outlet, a second flow path communicating with the second outlet, and a third flow path communicating with the third outlet, and be connected to a single air conditioning duct.

The total area of the first, second and third jets may be set to be larger than the cross-sectional area of the throttling section where the cross-sectional area of the conditioned air is smallest inside the fluid transport device. This reduces the wind speed of the jets from each jet and inhibits the attraction of surrounding fluids, further enhancing the effect of transporting the conditioned air long distances while suppressing the wind speed.

The first flow path, the second flow path, and the third flow path may each have a frustum shape on their outer periphery.

A speed increasing mechanism may also be provided to increase the flow rate of air flowing through the second flow path.

The speed increasing mechanism may also be an impeller provided upwind of the second outlet and an electric motor that provides a rotational driving force to the impeller.

Also, a first pressure loss element may be provided in the first flow path so that U1<U2.

The first pressure loss element may also be a wind turbine.

The first pressure loss element may be set so that the length of the first flow path is longer than the length of the second flow path. This makes it possible to set U2 > U1 by making the flow rate of the first flow path smaller than the flow rate of the second flow path.

Also, a second pressure loss element may be provided in the third flow path so that U3<U2.

The second pressure loss element may be set so that the length of the third flow path is longer than the length of the second flow path. This makes it possible to set the flow rate of the third flow path to be less than the flow rate of the second flow path, so that U2 > U3.

In addition, a rotor may be provided in the axial center of the first flow path and the second flow path, the rotor having a windmill section as a pressure loss element in the first flow path and an impeller section as a speed increasing mechanism in the second flow path, and the rotational force of the windmill section generated by the air flowing through the first flow path may be used as a rotational drive source for the impeller section.

Also, a third pressure loss element may be provided in the third flow path so that U3<U2.

This configuration allows for the creation of a jet flow in which U1, U2, and U3 satisfy the relationships U1<U2 and U3<U2. In addition, since there is no need to use an electric motor as a driving source for the speed-up impeller, no electrical parts or electrical work are required, and energy consumption can be reduced.

The following describes an embodiment of the present invention with reference to the drawings.

(Embodiment 1)
As shown in FIG. 1, the fluid transporting device 1 of the first embodiment is connected to an air conditioning duct 2. That is, in this embodiment, the fluid transporting device 1 is an outlet for conditioned air. As shown in the enlarged cross-sectional view of the fluid transporting device 1 in FIG. 2, the fluid transporting device 1 has a nozzle portion 3 that is a circular outlet for ejecting conditioned air. The nozzle portion 3 has a first outlet 4 for ejecting a fluid, a second outlet 5 that is formed in an annular shape so as to surround the outer periphery of the first outlet 4 and ejects the fluid as an annular jet, and a third outlet 6 that is formed in an annular shape so as to surround the outer periphery of the second outlet 5 and ejects the fluid as an annular jet. The first outlet 4 is provided in the center of the nozzle portion 3 and ejects a cylindrical air flow. The second outlet 5 is provided adjacent to the outer periphery of the first outlet 4. Similarly, the third outlet 6 is provided adjacent to the outer periphery of the second outlet 5. The first flow path 4a is an air passage that connects the first jet 4 and the air conditioning duct 2 on the upstream side of the first jet 4. Similarly, the second flow path 5a connects the second jet 5 and the air conditioning duct 2, and the third flow path 6a is an air passage that connects the third jet 6 and the air conditioning duct 2. When the jet velocity of the jet (first jet 7) that is jetted from the first jet 4 is U1, the jet velocity of the jet (second jet 8) that is jetted from the second jet 5 is U2, and the jet velocity of the jet (third jet 9) that is jetted from the third jet 6 is U3, the jets are jetted from the first jet 4, the second jet 5, and the third jet 6 so that U2 is the largest, that is, U1<U2 and U3<U2. More preferably, the jets are jetted so that U2>U1>U3.

As mentioned above, at the point where a fast air current and a slow air current meet, the slow air current is attracted to the faster air current. The greater the speed difference, the greater the amount of attraction.

In the fluid conveying device 1 of this embodiment, as described above, the wind speed U2 of the second jet 8 is faster than the adjacent third jet 9 on the outer periphery side. In other words, an attraction effect is generated by creating a speed difference at the boundary between the second jet 8 and the third jet 9. Also, an attraction effect is generated at the boundary between the third jet 9 and the surrounding air B due to the speed difference. Due to this attraction effect, the second jet 8 is conveyed while entraining the third jet 9, and the third jet 9 is conveyed while entraining the surrounding air B. With this configuration of blowing, the speed difference between the third jet 9 and the surrounding air B at the outermost periphery is smaller than the speed difference when the second jet 8 and the surrounding air B come into direct contact with each other, so the attraction effect of the surrounding air B can be suppressed. In other words, the second jet 8 with the fast wind speed U2 does not come into direct contact with the surrounding air B, and the surrounding air B is attracted to the third jet 9 with a slow wind speed, so the amount of attraction is suppressed. In this way, it is possible to suppress the temperature rise of the conditioned air blown out from the nozzle portion 3 during cooling operation, or the temperature drop during heating operation, and to suppress the performance degradation of cooling operation in summer and heating operation in winter.

Furthermore, by making the wind speed U2 of the second jet 8 greater than the wind speed U1 of the first jet 7, an attraction effect also occurs at the boundary between the second jet 8 and the first jet 7. That is, the second jet 8 is transported while entraining the first jet 7, which is the conditioned air. In addition, since the second jet 8 has a fast wind speed U2, it can transport the conditioned air to a long distance. The first jet 7 surrounded by the second jet 8 reaches a long distance while being attracted by the second jet 8. In addition, since the first jet 7 has a relatively slow wind speed U1, it is possible to suppress the discomfort caused by the direct jet hitting the body or the wind noise around the ears. It is also effective, for example, in the air conditioning of a factory, when there are manufactured products, manufacturing equipment, liquids, etc. that should be avoided from being affected by the wind pressure at the point where the jet reaches.

Figure 3 is an explanatory diagram showing the change in velocity distribution when conditioned air A is ejected as a jet with a wind speed of U0 (cross-sectional average velocity) from a single nozzle (single nozzle) as a comparative example. Figure 4 is an explanatory diagram showing the change in velocity distribution when conditioned air A is ejected as a first jet 7 with a wind speed of U1 (cross-sectional average velocity) from a first nozzle of the nozzle section, as a second jet 8 with a wind speed of U2 (cross-sectional average velocity) from a second nozzle, and as a third jet 9 with a wind speed of U3 (cross-sectional average velocity) from a third nozzle, with the respective velocities being U1<U2 and U3<U2, as an example.

As shown in Figure 3, when conditioned air A is ejected from the fluid ejection nozzle 101 of the prior art, the air speed U0 is uniformly distributed at distance Z = 0. However, at the boundary between the conditioned air A and the surrounding air B, an attraction effect occurs due to the speed difference, and the conditioned air A is transported while entraining the surrounding air B. This effect progresses as it travels downstream, and the speed of the conditioned air gradually decreases from the outside, and the temperature of the conditioned air is affected by the surrounding temperature. For example, in the case of cooling operation in the summer, the conditioned air is warmed by the surrounding high-temperature fluid, reducing the cooling performance, and in the case of heating operation in the winter, the conditioned air is cooled by the surrounding low-temperature fluid, reducing the heating performance.

In Fig. 3, the dotted lines indicate the areas influenced by the conditioned air A and the room air (ambient air B). At distance Z = _Z2 , the area influenced by the ambient air B on the periphery, i.e., the area transported while attracting the ambient air B, is large. On the other hand, it is shown that the area transported mainly as the conditioned air A (mainly the area of air ejected from the fluid ejection nozzle) is small. In other words, at distance Z = _Z2 , it can be seen that the area felt as air blown out from the fluid ejection nozzle portion 101 is narrow, and the cooling or heating effect is small.

On the other hand, as shown in FIG. 4, in the case of the fluid conveying device 1 according to the present embodiment, at distance Z=0, the velocity distribution of the first jet 7 and the velocity of the third jet 9 are small, and the velocity of the second jet 8 is large. At this time, an attraction effect occurs at the boundary between the second jet 8 and the third jet 9 due to the velocity difference. Also, an attraction effect occurs at the boundary between the third jet 9 and the surrounding air B due to the velocity difference. Due to this attraction effect, the second jet 8 is conveyed while entraining the first jet 7 and the third jet 9, and the third jet 9 is conveyed while entraining the surrounding air B. However, by reducing the velocity of the third jet 9, the velocity difference between the blown air-conditioned air (third jet 9) and the surrounding air B becomes small at the outermost periphery. Therefore, the attraction effect of the surrounding air B can be suppressed, and the deterioration of the performance of the cooling operation in summer and the heating operation in winter can be suppressed.

In FIG. 4, the dotted lines indicate the areas influenced by the conditioned air A and the room air (ambient air B). At distance Z= _Z2 , the area influenced by the ambient air B on the outer periphery, i.e., the area where the ambient air B is attracted and transported by the third jet 9, is a part of the outer periphery of the blown jet. On the other hand, the area influenced by the conditioned air A is mainly the area of the first jet 7, the mixed area of the first jet 7 and the second jet 8, and the mixed area of the second jet 8 and the third jet 9. That is, it is shown that the conditioned air A can reach a wide range, although the wind speed is slow in the area influenced by the conditioned air A. Thus, at distance Z= _Z2 , the area felt as air blown out from the nozzle portion 3 is wide, and cooling or heating is possible.

In this embodiment, the relationship between the wind speed U1 of the first jet 7, the wind speed U2 of the second jet 8, and the wind speed U3 of the third jet 9 has been described as U2>U1 and U2>U3, but it is possible to achieve better results by setting it as U2>U1>U3. In other words, by ensuring the wind speed, i.e., the air volume, of the first jet 7 in the center, it is possible to ensure the amount of heat supplied. Note that the magnitude relationship between the wind speed U1 of the first jet 7 and the wind speed U3 of the third jet 9 may be U1>U3.

In addition, by making the third jet 9 slower than the first jet 7, the second jet 8, which is decelerated by the shear force associated with the speed difference, tends to spread preferentially to the outer periphery (the extension side of the third jet outlet 6). This contributes to the jet of conditioned air A spreading over a wide area. In addition, the first jet 7 needs to be slower than the second jet 8, but the first jet 7 needs to cover the transport flow rate of the conditioned air A to a certain extent, and it must be avoided that the transport flow rate of the conditioned air A would be reduced due to excessive deceleration. In other words, making the first jet 7 faster than the third jet 9 is more suitable for achieving the above-mentioned purpose.

In this embodiment, three adjacent nozzles (first nozzle 4, second nozzle 5, third nozzle 6) have been described, but the present invention is not limited to this form. That is, it is sufficient to have a third nozzle 6 at the outermost periphery, a second nozzle 5 adjacent to the inner periphery of the third nozzle 6, and a first nozzle 4 on the inner periphery of the second nozzle 5 and ejecting in a cylindrical shape at the center. For example, the first nozzle 4 and the second nozzle 5 may not be adjacent to each other, and a fourth nozzle and an additional nozzle may be provided between them, or there may be a closed area.

(Embodiment 2)
As shown in FIG. 5, the fluid conveying device 1 of the second embodiment is attached to the air conditioning duct 2, and has a first outlet 4, a second outlet 5, and a third outlet 6, as in the first embodiment. A feature of this embodiment is that a speed-up mechanism is provided to increase the wind speed U2 of the second jet 8. As the speed-up mechanism, an impeller 10 is provided at the windward position of the second outlet 5, i.e., in the second flow path 5a, and an electric motor 11 is connected to the impeller 10 to provide a rotational driving force. In this embodiment, the electric motor 11 is disposed in the first flow path 4a. The impeller 10 has a cylindrical portion having the same diameter as the wall surface of the first flow path 4a, and is provided with blades on its outer periphery. That is, the inner periphery side of the cylindrical portion of the impeller 10 becomes a part of the first flow path 4a, and the outer periphery side of the cylindrical portion of the impeller 10 becomes the second flow path 5a. The impeller 10 rotates the blades together with the cylindrical portion by driving the electric motor 11. The rotation of the impeller 10 can increase the wind speed flowing through the second flow passage 5a, and as a result, the wind speed U2 of the second jet 8 can be increased.

Furthermore, pressure loss elements 12, 13 may be provided at the windward positions of the first and third jets 4, 6, i.e., in the first and third flow paths 4a, 6a, respectively. The pressure loss element 12 in this embodiment is a wall portion provided in the first flow path 4a to reduce the flow path cross-sectional area of the first flow path 4a. The pressure loss element 13 is a wall portion provided in the third flow path 6a to reduce the flow path cross-sectional area of the third flow path 6a. The pressure loss element 12 reduces the wind speed flowing through the first flow path 4a and the wind speed U1 of the first jet, and the pressure loss element 13 reduces the wind speed flowing through the third flow path 6a and the wind speed U3 of the third jet. The size of the pressure loss elements 12, 13 can also be adjusted to adjust the wind speed U1 of the first jet 7 and the wind speed U3 of the third jet 9.

This configuration makes it easy to configure the jets so that the wind speed U1 emitted from the first nozzle 4, the wind speed U2 emitted from the second nozzle 5, and the wind speed U3 emitted from the third nozzle 6 are U1 < U2 and U3 < U2. Note that in this embodiment, the pressure loss elements 12 and 13 are shown as having protrusions in the flow path, but they may also be configured by narrowing the flow path, etc. Alternatively, the pressure loss elements 12 and 13 may be configured by punching metal or a filter.

(Embodiment 3)
As shown in Fig. 6, the fluid transport device 1 of the third embodiment is attached to an air conditioning duct 2 in the same manner as in the first embodiment, and has a first outlet 4, a second outlet 5, and a third outlet 6. A feature of this embodiment is that a windmill 14 is provided as a windmill section at a position upwind of the first outlet 4, i.e., in the first flow path 4a. Also, an impeller 15 is provided as an impeller section at a position upwind of the second outlet 5, i.e., in the second flow path 5a, and is connected to the windmill 14. In other words, the windmill 14 and the impeller 15 have the same rotation axis and form a single rotating body.

To explain in more detail, the windmill 14 is installed to block the first flow path 4a as a pressure loss element for the first flow path 4a, and the windmill 14 rotates due to the pressure difference between upwind and downwind. In other words, the rotor in which the windmill 14 and impeller 15 are integrated rotates using the air flowing through the first flow path 4a as power. The first flow path 4a has a smaller flow path diameter downstream of the windmill 14, so as to increase the wind speed (wind speed U1 of the first jet 7) sprayed from the first nozzle 4.

As described above, a part of the boundary between the first flow path 4a and the second flow path 5a is shaped like a truncated cone, with the diameter decreasing downstream, so that the flow path diameter of the first flow path 4a becomes smaller downstream of the windmill 14. The blades of the impeller 15 are provided in the second flow path 5a, which is the outer periphery of this truncated cone-shaped part. In other words, the impeller 15 rotates together with the truncated cone-shaped wall surface of the first flow path 4a (and the second flow path 5a). The impeller 15 is connected to the windmill 14 by a rotating shaft to form a single rotating body. Since the blades of the impeller 15 are provided on the truncated cone-shaped wall surface, the impeller 15 functions as a mixed flow fan. In other words, the impeller 15 is a mechanism for increasing the speed of the air flowing through the second flow path 5a.

With this configuration, the windmill 14 rotates due to the pressure difference between its upwind and downwind sides, and at the same time, it plays the role of a pressure loss element for the first flow path 4a. Furthermore, the rotational force obtained by the rotation of the windmill 14 can be used as the rotation drive source for the impeller 15. The jets can be easily configured so that the wind speed U1 emitted from the first nozzle 4, the wind speed U2 emitted from the second nozzle 5, and the wind speed U3 emitted from the third nozzle 6 are U1<U2 and U3<U2. Furthermore, since there is no need to use an electric motor as the drive source for the speed-up impeller 15, no electrical components or electrical work are required, and energy consumption can be reduced.

As in the second embodiment, a pressure loss element 13 may be provided in the third flow path 6a to reduce the wind speed U3 of the third jet 9.

(Embodiment 4)
FIG. 7 is a perspective view of a fluid transporting device of a fourth embodiment. FIG. 8 is a perspective view of an extension part constituting the fluid transporting device of this embodiment. FIG. 9 is a cross-sectional view of the fluid transporting device of this embodiment. FIGS. 10 and 11 are cross-sectional views showing the internal flow of the air-conditioning air flowing in the fluid transporting device and the separation area of the internal flow in a case where the expansion angle of each flow path is larger than that of this embodiment. FIG. 12 is a perspective view (a) and a cross-sectional view (b) of a modified example 1 of this embodiment. FIG. 13 is a cross-sectional view of a modified example 2 of this embodiment. In addition, in FIGS. 9 to 13, the bolts and nuts constituting the extension part are omitted.

As shown in FIG. 7, the fluid transport device 1 of the fourth embodiment is attached to an air conditioning duct 2 (not shown) in the same manner as in the first embodiment, and has a first outlet 4, a second outlet 5, and a third outlet 6 at the tip of the nozzle portion 3. The nozzle portion 3 has an extension portion 37 that expands from the throttling portion 51, where the flow path cross-sectional area of the fluid transport device 1 is the smallest, toward the tip outlets (the first outlet 4, the second outlet 5, and the third outlet 6). A feature of this embodiment is that the total area of the first outlet 4, the second outlet 5, and the third outlet 6 (the area within the area shown by the dashed line as the outlet periphery 30 in FIG. 7) is configured to be larger than the flow path cross-sectional area of the nozzle portion 3, where the flow path cross-sectional area of the air-conditioned air is the smallest inside the fluid transport device 1 (the area within the area shown by the dashed line as the throttling portion periphery 31 in FIG. 7).

To explain in more detail, as shown in Figures 8 and 9, the extension 37 has a first partition plate 32, a second partition plate 33, and a third partition plate 34, which are in the shape of a truncated cone with the central axis being the concentric axis X. The first flow path 4a, the second flow path 5a, and the third flow path 6a are formed with the first partition plate 32, the second partition plate 33, and the third partition plate 34 as the outer peripheral surfaces. The three partition plates, the first partition plate 32, the second partition plate 33, and the third partition plate 34, are formed in the shape of a thin hollow truncated cone. The first partition plate 32 and the second partition plate 33, and the second partition plate 33 and the third partition plate 34 are each held by six bolts 35 and six nuts 36. The extension 37 is connected to the outer periphery of the main body side of the fluid transport device 1 by three bolts 35 and three nuts 36.

Since the third partition plate 34 has a truncated cone shape, the end of the third partition plate 34 on the fluid transport device 1 body side forms the smallest part of the flow path cross-sectional area in the extension section 37, i.e., the throttle section 51.

The inner diameters of the partitions have the following relationship: first partition 32 < second partition 33 < third partition 34. Therefore, as described above, as shown in FIG. 9, the first flow path 4a is formed on the inner periphery of the first partition 32, the second flow path 5a is formed in the area between the first partition 32 and the second partition 33, and the third flow path 6a is formed in the area between the second partition 33 and the third partition 34.

As shown in FIG. 9, in this embodiment, the first partition plate 32, the second partition plate 33, and the third partition plate 34 are gradually enlarged so that the opening angles 39, 40, and 41 are 6°, 12°, and 20°, respectively. The opening angle here is defined as the angle at which each partition plate opens in the direction of the concentric axis X, as shown in FIG. 9.

The blowing wind speeds U1, U2, and U3 from the first nozzle 4, second nozzle 5, and third nozzle 6 are determined by the expansion rate of the flow path cross-sectional area of the first flow path 4a, second flow path 5a, and third flow path 6a. That is, as described above, the first partition plate 32 has a truncated cone shape that expands toward the first nozzle 4 side, so the wind speed changes according to the ratio of the inlet side cross-sectional area _S1i to the outlet side cross-sectional area _S1o of the first flow path 4a. For example, if the wind speed at the inlet is U0, the wind speed U1 at the first nozzle 4 is
U1=U0× _S1i / _S1o
The same is true for the wind speed U2 at the second jet port 5 and the wind speed U3 at the third jet port 6, and by adjusting the expansion rates of the flow path cross-sectional areas of the first flow path 4a, the second flow path 5a, and the third flow path 6a, it becomes possible to jet the first jet 7, the second jet 8, and the third jet 9 so that U1<U2 and U3<U2.

As mentioned above, at the contact point between the airflow and the still air around it, the still air is attracted to the airflow, generating a flow. However, the amount of attraction decreases as the airflow speed decreases. In other words, if the volume of conditioned air ejected from the fluid transport device 1 is the same, the larger the area of the first jet 4, second jet 5, and third jet 6, the lower the wind speed of the first jet 7, second jet 8, and third jet 9, and therefore the amount of attraction of still outside air by each jet decreases.

In this embodiment, the total area of the first nozzle 4, the second nozzle 5, and the third nozzle 6 (in this embodiment, the area surrounded by the nozzle periphery 30) is configured to be larger than the flow path cross-sectional area of the periphery of the throttling section 51 (throttling section periphery 31). Therefore, the difference in speed between the first jet 7, the second jet 8, and the third jet 9 ejected from the first nozzle 4, the second jet 5, and the third jet 6 and the surrounding stationary outside air becomes small, making it possible to suppress the amount of outside air that is attracted. In other words, it is possible to suppress the deterioration of performance in cooling operation in the summer and the deterioration of performance in heating operation in the winter.

In addition, by reducing the wind speed of the first jet 7, the second jet 8, and the third jet 9, the wind speed at a point a certain distance away can also be suppressed. This makes it possible to suppress the discomfort felt by the direct impact of the jets and the wind noise around the ears.

In other words, the larger the ejection area, the more the aforementioned effect can be enhanced. To achieve this, in this embodiment, the opening angles 39, 40, 41 of the first partition plate 32, the second partition plate 33, and the third partition plate 34 can be set large in order to increase the total area of the first ejection port 4, the second ejection port 5, and the third ejection port 6.

However, due to the nature of air as a fluid, it is generally known that if the expansion angle of the flow path is set to 14° or more, the airflow cannot flow along the wall surface and a separation region that forms a vortex occurs. The expansion accuracy of the flow path in this embodiment is the angle formed by adjacent partition plates, which is the angle formed by adjacent partition plates when the extension portion 37 is cut by a plane including the concentric axis X.

The behavior of the fluid in this separation region will be explained. This separation region can have a number of adverse effects depending on where it occurs. This time, we will describe the case where a fixed amount of conditioned air is created from the fluid transport device 1.

For example, as shown in FIG. 10, if a separation region D of the internal flow C occurs other than around the first nozzle 4, the second nozzle 5, and the third nozzle 6, i.e., upstream of the first flow path 4a, the second flow path 5a, and the third flow path 6a, the pressure of the air conditioner required to create the conditioned air will increase, resulting in increased power consumption by the air conditioner.

Also, as shown in FIG. 11, when a separation region D of the internal flow C occurs around the first nozzle 4, second nozzle 5, and third nozzle 6, i.e., near the downstream ends of the first flow path 4a, second flow path 5a, and third flow path 6a, the ejection area of the first nozzle 4, second nozzle 5, and third nozzle 6 is substantially reduced. Therefore, a high wind speed region is formed near the nozzle, and outside air flows E into the fluid transport device 1 before ejection. Since these phenomena lead to an increase in the amount of attraction, it is desirable to set the expansion angle of each flow path to 14° or less.

In this embodiment, the expansion angles 42, 43, 44 of the first flow path 4a, the second flow path 5a, and the third flow path 6a are set to 6°, 6°, and 8°, respectively. This setting allows the total area of the first jet 4, the second jet 5, and the third jet 6 to be set sufficiently large without generating a separation region D, thereby suppressing the wind speed of the first jet 7, the second jet 8, and the third jet 9.

In this embodiment, the first partition plate 32, the second partition plate 33, and the third partition plate 34 are shaped like a truncated cone, but they may be shaped like a truncated pyramid. Alternatively, the first partition plate 32, the second partition plate 33, and the third partition plate 34 may be a combination of a truncated cone shape and a truncated pyramid shape.

In addition, in this embodiment, the first flow path 4a, the second flow path 5a, and the third flow path 6a are gradually enlarged, but they do not necessarily have to be gradually enlarged. For example, as shown in FIG. 12(a), if the total area of the first jet 4, the second jet 5, and the third jet 6 can be made larger than the flow path cross-sectional area of the throttling section 51, the third partition plate 34 may be structured as a hollow circular tube (not shown, but the same applies to the first partition plate 32 and the second partition plate 33). However, as shown in FIG. 12(b), if a sudden expansion section 45 is formed at the connection between the throttling section 51 and the third flow path 6a, a separation region D of the internal flow C is created. Therefore, more pressure than necessary is required to send out the air, which increases the power consumption of the air conditioner.

In addition, in this embodiment, the first partition plate 32 is longer than the second partition plate 33 and is extended upstream. That is, the first flow path 4a is longer than the second flow path 5a and the third flow path 6a. With this configuration, the ratio of the inlet area to the outlet area of the first flow path 4a can be increased to slow down the wind speed U1 at the first nozzle 4. Also, by lengthening the first flow path 4a, the wind speed U1 at the first nozzle 4 can be slowed down. In this way, the conditions U1<U2 and U3<U2 may be satisfied by appropriately changing the lengths of the first flow path 4a and the third flow path 6a.

The wind speed of each outlet is determined by dividing the volume of air flowing through each flow path by the area of each outlet. Therefore, for example, if the area of the third outlet 6 is made smaller than the area of the second outlet 5, U3 > U2 should not be satisfied. For example, the third flow path 6a should be made longer than the second flow path 5a. With this configuration, the pressure loss of the third flow path 6a becomes greater than the pressure loss of the second flow path 5a, and the volume of conditioned air flowing through the third flow path 6a can be suppressed to set U3 < U2.

In addition, in this embodiment, the upstream end of the first flow path 4a extends upstream of the second flow path 5a and the third flow path 6a, but this is not necessarily the case. For example, as shown in FIG. 13, the first partition plate 32 and the second partition plate 33 may be provided only near the nozzle. However, in order to expand the flow paths while suppressing peeling within each flow path, it is necessary to ensure an appropriate flow path length.

In addition, in this embodiment, the extension 37 is structured to be attached to the main body of the fluid transport device 1, but this is not particularly limited, and the main body of the fluid transport device 1 and the extension 37 may be configured as one unit.

The present invention can be used to transport fluids for purposes such as air conditioning.

REFERENCE SIGNS LIST 1 Fluid transport device 2 Air conditioning duct 3 Nozzle portion 4 First outlet 4a First flow path 5 Second outlet 5a Second flow path 6 Third outlet 6a Third flow path 7 First jet 8 Second jet 9 Third jet 10 Impeller 11 Electric motor 12 Pressure loss element of first outlet 13 Pressure loss element of third outlet 14 Windmill 15 Impeller 30 Outer periphery of outlet 31 Outer periphery of throttle portion 32 First partition plate 33 Second partition plate 34 Third partition plate 35 Bolt 36 Nut 37 Extension portion 39, 40, 41 Opening angle 42, 43, 44 Expansion angle 45 Sudden expansion portion 51 Throttle portion 101 Fluid ejection nozzle 102 Air conditioning duct 103 Opening 104 Flange-shaped member 105 Fixing member 106 Nozzle body 107 Blowing part A Conditioned air B Ambient air C Internal flow D Separation region E Inflow X Concentric axis

Claims (11)

A fluid conveying device having a nozzle portion that ejects conditioned air,
The nozzle portion is
A first jet outlet;
a second jet outlet formed in an annular shape on an outer circumferential side of the first jet outlet so as to surround an outer circumferential side of the first jet outlet and jetting the fluid as an annular jet;
a third jet outlet that is adjacent to an outer periphery of the second jet outlet and is formed in an annular shape so as to surround an outer periphery of the second jet outlet and jets out a fluid as an annular jet ;
a first flow passage communicating with the first ejection port;
a first partition plate that defines the first flow path on an inner peripheral side;
a second flow passage communicating with the second ejection port;
a second partition plate that forms the second flow path in a region sandwiched between the first partition plate and the second partition plate;
a third flow passage communicating with the third ejection port;
a third partition plate that forms the third flow path in a region sandwiched between the second partition plate and the third partition plate,
The first partition plate and the third partition plate have a frustum shape with an opening angle,
The opening angle of the third partition plate is larger than the opening angle of the first partition plate,
The second partition plate has a cylindrical shape with no opening angle,
a total area of the first outlet, the second outlet, and the third outlet is larger than a flow path cross-sectional area of a throttle portion at which a flow path cross-sectional area of the conditioned air is smallest inside the fluid transporting device,
When the flow velocities of the air blown out from the first outlet, the second outlet, and the third outlet are U1, U2, and U3, respectively,
A fluid transport device that blows out fluid so that U2>U1, U2>U3 , and U1≧U3 . 2. The fluid transfer device of claim 1, which is connected to an air conditioning duct. 3. The fluid transporting device according to claim 1, further comprising an acceleration mechanism for increasing a flow velocity of the air flowing through the second flow passage. 4. The fluid transport device according to claim 3 , wherein the speed increasing mechanism comprises an impeller provided at a position upwind of the second ejection port, and an electric motor for applying a rotational driving force to the impeller. 5. The fluid transporting device according to claim 1 , wherein a first pressure loss element is provided in the first flow path so that U1<U2 holds. 6. The fluid transport device according to claim 5 , wherein the first pressure loss element is a wind turbine. 7. The fluid transporting device according to claim 6 , wherein the first pressure loss element is configured such that the length of the first flow passage is longer than the length of the second flow passage. 8. The fluid transporting device according to claim 1 , wherein a second pressure loss element is provided in the third flow path, so that U3<U2 holds. 9. The fluid transporting device according to claim 8 , wherein the second pressure loss element is a third flow path having a length longer than a length of the second flow path. a rotor is provided at a center portion of the first flow passage and the second flow passage in an axial direction;
The rotating body is
A wind turbine portion as a pressure loss element in the first flow path;
an impeller portion as a speed increasing mechanism in the second flow path,
3. The fluid transport device according to claim 2 , wherein a rotational force of a windmill portion generated by air flowing through said first flow passage is used as a rotational drive source for said impeller portion. 11. The fluid transporting device according to claim 10 , wherein a third pressure loss element is provided in the third flow path so that U3<U2.

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