Fluid transfer device

Abstract

To provide a fluid conveying device for suppressing an induction effect.SOLUTION: A first injection port formed in a cylindrical shape or a truncated cone shape by a first partition plate and configured to inject a fluid, a second injection port formed in an annular shape by a second partition plate in an outer peripheral side of the first injection port so as to surround an outer periphery of the first injection port and configured to inject a fluid as an annular flow, and a third injection port formed in an annular shape by a third partition plate in an outer peripheral side of the second injection port so as to surround an outer periphery of the second injection port; And a third ejection port configured to eject the fluid as an annular jet, wherein at least one of the first partition plate, the second partition plate, and the third partition plate has a truncated conical shape, and when jet velocities of the air ejected from the first ejection port, the second ejection port, and the third ejection port are U1, U2, and U3, respectively, the jet is ejected such that U1 ≥ U2> U3.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a fluid transport device for efficiently transporting a fluid such as air for purposes such as heating and cooling. [Background technology]

[0002] When cooling or heating large spaces such as factories, warehouses, stadiums, and commercial kitchens, a fluid ejection nozzle 101 as shown in FIG. 5 is used as an outlet structure for delivering conditioned air to a specific target location. This fluid ejection nozzle 101 has a circular opening 103 formed in an air conditioning duct 102, and is fixed to the opening 103 with a flange-shaped member 104. A fixing member 105 having a rounded side portion is fixed to the flange-shaped member 104. A substantially semicircular nozzle body (ball portion) 106 is disposed within the fixing member 105 around its central axis so as to be movable in any direction, and a cylindrical ejection portion 107 is formed at the lower end of the nozzle body 106. This configuration allows conditioned air to be ejected in a specific direction. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Utility Model Application Publication No. 5-73441 Summary of the Invention [Problem to be solved by the invention]

[0004] In such a fluid ejection nozzle 101, when conditioned air A is blown out from the blowout portion 107 formed by a single nozzle (single nozzle), surrounding space air B is attracted near the blowout portion 107. For example, in the case of cooling operation in the summer, this space air B1 is hotter than the cooling air A1 blown out from the blowout portion 107, and due to the attraction effect, this hot air (space air B1) mixes with the conditioned air A, causing the temperature of the conditioned air A to increase by the time it reaches the location to be cooled, resulting in a problem of reduced cooling effectiveness. Also, in the case of heating operation in the winter, space air B2 is colder than the heating air A2 blown out from the blowout portion 107, and due to the attraction effect, this cold air (space air B2) mixes with the conditioned air A, causing the temperature of the conditioned air A to decrease by the time it reaches the location to be heated, resulting in a problem of reduced heating effectiveness.

[0005] The present invention is intended to solve such conventional problems, and has an object to provide a fluid transporting device that can suppress the induced effect and efficiently transport a fluid. [Means for solving the problem]

[0006] To achieve this object, the fluid transport device of the present invention has a nozzle portion that ejects conditioned air, which is a fluid. The nozzle portion is formed by a first partition plate having a cylindrical or truncated cone shape, which has a first inlet formed upstream in the blowing direction of the fluid and a first outlet formed downstream in the blowing direction of the fluid, a first outlet that ejects the fluid that has flowed in from the first inlet, and a second partition plate having a cylindrical shape, which has a second inlet formed upstream in the blowing direction of the fluid and a second outlet formed downstream in the blowing direction of the fluid, and a second jet port formed in an annular shape so as to surround the outer periphery of the jet port, and jetting the fluid flowing in from the second inlet from the second outlet as an annular jet; a third inlet formed on the outer periphery of the second jet port on the upstream side in the blowing direction of the fluid; and a third outlet formed on the downstream side in the blowing direction of the fluid, the third partition plate having a truncated cone shape formed so as to expand in diameter from the third inlet toward the third outlet, and the third partition plate is formed in an annular shape so as to surround at least a part of the outer periphery of the second jet port; and a third jet outlet that jets the fluid that has flowed in from the third inlet as an annular jet from the third outlet. The second inlet is located downstream of the third inlet in the blowing direction of the fluid, and the second outlet is located downstream of the third outlet in the blowing direction of the fluid, thereby achieving the desired object. [Effects of the Invention]

[0007] According to the present invention, by blowing jets from the first, second, and third jets, it is possible to reduce the shear force generated by the difference in jet velocity between the jets and the surrounding air, and by suppressing the entrainment of surrounding air due to the attraction effect, it is possible to suppress temperature changes, thereby suppressing performance degradation in cooling operation in summer and performance degradation in heating operation in winter. At the same time, it is possible to suppress the reduction in the jet velocity of the first and second jets, so that airflow with a high wind speed can be efficiently delivered to the target location. As a result, in summer, the faster the wind speed of the conditioned air, the lower the perceived temperature felt by humans. Therefore, it is possible to provide an air-conditioned space that feels even cooler than normal air-conditioned air during cooling operation in summer. [Brief explanation of the drawings]

[0008] [Figure 1] FIG. 1 is a diagram showing a configuration of a fluid transporting device according to a first embodiment of the present invention; [Figure 2] FIG. 1 is an enlarged cross-sectional view showing the configuration of a fluid transporting device according to a first embodiment of the present invention. [Figure 3] FIG. 10 is a diagram illustrating a change in the velocity distribution of a jet according to the first embodiment of the present invention. [Figure 4] FIG. 10 is a diagram showing a modified example of the fluid transporting device according to the first embodiment of the present invention. [Figure 5] FIG. 1 shows the configuration of a conventional fluid transport device. [Figure 6] 1 is a diagram showing a change in velocity distribution of a jet of a conventional fluid transport device. DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, an embodiment of the present invention will be described with reference to FIGS.

[0010] (Embodiment 1) As shown in FIG. 1, a fluid transporting device 1 of this embodiment is connected to an air conditioning duct 2.

[0011] The air conditioning duct 2 connects the fluid transport device 1 to an air conditioning device (not shown), and conditioned air is sent to the fluid transport device 1. In other words, in this embodiment, the fluid transport device 1 serves as an outlet for the conditioned air conditioned by the air conditioning device (not shown). As shown in the enlarged cross-sectional view of the fluid transport device 1 in FIG. 2, the fluid transport device 1 has a nozzle portion 3 that ejects conditioned air. The connecting portion (main body) of the fluid transport device 1 with the air conditioning duct 2 is approximately hemispherical, allowing the conditioned air to be efficiently sent from the air conditioning duct 2 to the nozzle portion 3. The fluid transport device 1 (approximately hemispherical portion) is held in place by conventional technology so as to be rotatable in any direction. The fluid transport device 1 and the nozzle portion 3 are made of metal or resin.

[0012] The nozzle section 3 has a first outlet 4 formed by a first partition plate 11, a second outlet 5 formed by a second partition plate 12, and a third outlet 6 formed by a third partition plate 13. The nozzle section 3 is generally cylindrical (including a truncated cone shape), with the first outlet 4 provided at the center of the generally cylindrical opening, the second outlet 5 provided annularly around the outer periphery of the first outlet 4, and the third outlet 6 provided annularly around the outer periphery of the second outlet 5. In other words, conditioned air blown from the air conditioning duct 2 is blown out from the first outlet 4, the second outlet 5, and the third outlet 6. The first partition plate 11, the second partition plate 12, and the third partition plate 13 are each held by a support member 10. The support member 10 is arranged so as not to interfere with the blowing of air, and is not shown in the drawings.

[0013] The first partition plate 11 is formed in a truncated cone shape, tapering from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the first jet outlet 4 in the blowing direction is larger than the opening area OUTa of the outlet (jet outlet) downstream of the first jet outlet 4 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the first jet outlet 4 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0014] The second partition plate 12 is formed in a truncated cone shape, tapering from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction (including the opening area of ​​the inlet of the first outlet 4) is larger than the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction (including the opening area of ​​the outlet of the first outlet 4). In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0015] The third partition plate 13 is formed in a truncated cone shape, and is formed so that it becomes thicker from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is smaller than the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are 1 > (inlet opening area / outlet opening area).

[0016] Next, the velocity distribution of the jets will be explained using Figure 3 when the ejection velocity of the first jet 7 (fluid) ejected from the first nozzle 4 of the nozzle portion 3 is U1, the ejection velocity of the second jet 8 (fluid) ejected from the second nozzle 5 is U2, and the ejection velocity of the third jet 9 (fluid) ejected from the third nozzle 6 is U3.

[0017] The opening area INa of the inlet upstream in the airflow direction of the first jet outlet 4 and the second jet outlet 5 is larger than the opening area OUTa of the outlet (jet outlet) downstream in the airflow direction. In other words, because the opening area OUTa of the outlet is smaller than the opening area INa of the inlet, the jet velocity U1 of the first jet 7 and the jet velocity U2 of the second jet 8 are faster than the jet velocity U3 of the third jet 9.

[0018] On the other hand, the opening area INa of the inlet upstream in the airflow direction of the third jet 6 is smaller than the opening area OUTa of the outlet (jet outlet) downstream in the airflow direction. In other words, since the opening area OUTa of the outlet is larger than the opening area INa of the inlet, the jet velocity U3 of the third jet 9 is slower than the jet velocity U1 of the first jet 7 and the jet velocity U2 of the second jet 8.

[0019] Therefore, the relationship between the jet velocity U1 of the first jet 7, the jet velocity U2 of the second jet 8, and the jet velocity U3 of the third jet 9 is U1, U2 > U3. In this embodiment, the jet velocity U1 of the first jet 7 and the jet velocity U2 of the second jet 8 may be the same, or the jet velocity U1 of the first jet 7 may be faster than the jet velocity U2 of the second jet 8. In this case, the opening areas (INa, OUTa) of the first jet nozzle 4 and the opening areas (INa, OUTa) of the second jet nozzle 5 are adjusted and formed so that the jet velocity U1 of the first jet 7 ejected from the first jet nozzle 4 is equal to or greater than the jet velocity U2 of the second jet 8 ejected from the second jet nozzle 5. In other words, since the jet velocities are related by U1 ≥ U2, it can also be said that the relationship between the jet velocities of U1, U2, and U3 is U1 ≥ U2 > U3.

[0020] In contrast, the velocity distribution of the jet of the conventional fluid transport device is as shown in FIG. 6, which shows the change in velocity distribution when conditioned air is ejected from a single nozzle (blowing part 107) as a jet with a cross-sectional average velocity U0. When the air conditioner is operated in this manner, the jet velocity U0 is uniformly distributed at a distance Z=0 from the blowout section 107. However, at the boundary between the conditioned air (first jet 7) and the surrounding space air B, an attraction effect occurs due to shear force caused by the difference in jet velocity between the conditioned air (first jet 7) and the surrounding space air B (jet velocity is zero), and the conditioned air (first jet 7) is transported while entraining the surrounding space air B. This progresses as the distance Z from the blowout section 107 increases, that is, as the conditioned air (first jet 7) travels downstream in the blowing direction, the velocity of the conditioned air (first jet 7) gradually decreases from the outside, and the temperature of the conditioned air (first jet 7) is affected by the ambient temperature. In other words, during cooling operation in the summer, the attraction effect causes the high-temperature air (space air B) to mix with the conditioned air A, and by the time it reaches the location to be cooled, the temperature of the conditioned air A has risen, resulting in a reduced heating effect. In addition, during heating operation in winter, the attraction effect causes low-temperature air (space air B) to mix with conditioned air A, and by the time it reaches the area to be heated, the temperature of conditioned air A has dropped, resulting in a reduced cooling effect.

[0021] In contrast to this, as shown in FIG. 3, in the velocity distribution of the jets in this embodiment, in the case of a triple nozzle, the relationship between the velocities of the jets at a distance Z=0 from the nozzle portion 3 is U1≧U2>U3.

[0022] In this case, if there is a difference in jet velocity between the first jet 7 and the second jet 8 (U1>U2), a shear force is generated due to the difference in jet velocity. However, since this difference is smaller than the difference in jet velocity compared to the surrounding space air B, the generated shear force is also small, and the attraction effect is suppressed. Note that, if the first jet 7 and the second jet 8 have the same jet velocity (U1=U2), no shear force is generated, and the attraction effect is similarly suppressed. Therefore, the decrease in the wind speed of the first jet 7 can be suppressed, and temperature changes can be suppressed.

[0023] Furthermore, because there is a difference in jet velocity between the second jet 8 and the third jet 9 (U2>U3), a shear force is generated by the difference in jet velocity, which similarly generates an attraction effect. However, since the difference in jet velocity is smaller than that in the surrounding space air B, the shear force is smaller, and the attraction effect is also smaller, which prevents a decrease in the wind speed of the second jet 8 and suppresses temperature changes. Note that it is desirable to set the jet velocity U3 of the third jet 9 to 1 / 2 or less of the jet velocity U2 of the second jet 8. This further suppresses the attraction effect of the surrounding space air B.

[0024] Furthermore, because there is a difference in jet velocity (U3 > 0) between the third jet 9 and the surrounding space air B (jet velocity is zero), a shear force is generated due to the jet velocity difference, which similarly produces an attraction effect. However, because the third jet 9 has a slower wind speed (U1 ≥ U2 > U3) than the first jet 7 and second jet 8, the difference in jet velocity with the surrounding space air B is smaller than in the case of a single nozzle, and the shear force is also smaller, which reduces the attraction effect and makes it possible to suppress the entrainment of the surrounding space air B. As a result, even if the distance Z from the nozzle portion 3 is large, the conditioned air (first jet 7, second jet 8, third jet 9) and the surrounding space air B do not easily mix, making it possible to suppress temperature changes in the conditioned air being jetted out.

[0025] Therefore, by varying the jet speed from each layer of the triple nozzle, the attraction effect of the surrounding space air B can be suppressed more than with the conventional fluid jet nozzle 101 (Figure 5), thereby suppressing temperature changes in the jets from each layer of the nozzle section 3 and suppressing performance degradation in cooling operation in summer and heating operation in winter. At the same time, since it is possible to suppress a decrease in the jet speed of the first jet 7 and the second jet 8, it is possible to efficiently deliver a high-speed airflow to the target location. As a result, in summer, the faster the air speed of the conditioned air, the lower the perceived temperature felt by humans. Therefore, it is possible to provide an air-conditioned space that feels even cooler than normal air-conditioned air during cooling operation in summer.

[0026] (Variation) Next, a modified example of the nozzle portion 3 will be described with reference to FIG.

[0027] 4(a) shows Modification 1, in which the first partition plate 11 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the first jet outlet 4 in the blowing direction is the same as the opening area OUTa of the outlet (jet outlet) downstream of the first jet outlet 4 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the first jet outlet 4 are 1 = (inlet opening area / outlet opening area).

[0028] The second partition plate 12 is formed in a truncated cone shape, tapering from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction (including the opening area of ​​the inlet of the first outlet 4) is larger than the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction (including the opening area of ​​the outlet of the first outlet 4). In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0029] The third partition plate 13 is formed in a truncated cone shape, and is formed so that it becomes thicker from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is smaller than the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are 1 > (inlet opening area / outlet opening area).

[0030] 4(b) shows Modification 2, in which the first partition plate 11 is formed in a truncated cone shape and is tapered from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the first outlet 4 in the blowing direction is larger than the opening area OUTa of the outlet (outlet) downstream of the first outlet 4 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the first outlet 4 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0031] The second partition plate 12 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction is the same as the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 are 1 = (inlet opening area / outlet opening area).

[0032] The third partition plate 13 is formed in a truncated cone shape, and is formed so that it becomes thicker from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is smaller than the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are 1 > (inlet opening area / outlet opening area).

[0033] 4(c) shows Modification 3, in which the first partition plate 11 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the first jet outlet 4 in the blowing direction is the same as the opening area OUTa of the outlet (jet outlet) downstream of the first jet outlet 4 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the first jet outlet 4 are 1 = (inlet opening area / outlet opening area).

[0034] The second partition plate 12 is formed in a cylindrical shape, and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction is the same as the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 are expressed as 1= (inlet opening area / outlet opening area).

[0035] The third partition plate 13 is formed in a truncated cone shape, and is formed so that it becomes thicker from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is smaller than the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are 1 > (inlet opening area / outlet opening area).

[0036] 4(d) shows Modification 4, in which the first partition plate 11 is formed in a truncated cone shape and is tapered from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the first outlet 4 in the blowing direction is larger than the opening area OUTa of the outlet (outlet) downstream of the first outlet 4 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the first outlet 4 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0037] The second partition plate 12 is formed in a truncated cone shape, tapering from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction (including the opening area of ​​the inlet of the first outlet 4) is larger than the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction (including the opening area of ​​the outlet of the first outlet 4). In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0038] The third partition plate 13 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is the same as the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are expressed as 1 = (inlet opening area / outlet opening area).

[0039] 4(e) shows Modification 5, in which the first partition plate 11 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the first jet outlet 4 in the blowing direction is the same as the opening area OUTa of the outlet (jet outlet) downstream of the first jet outlet 4 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the first jet outlet 4 are 1 = (inlet opening area / outlet opening area).

[0040] The second partition plate 12 is formed in a truncated cone shape, tapering from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction (including the opening area of ​​the inlet of the first outlet 4) is larger than the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction (including the opening area of ​​the outlet of the first outlet 4). In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 satisfy the relationship 1<(inlet opening area / outlet opening area).

[0041] The third partition plate 13 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is the same as the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are expressed as 1 = (inlet opening area / outlet opening area).

[0042] 4(f) shows a sixth modification, in which the first partition plate 11 is formed in a truncated cone shape, tapering from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet on the upstream side of the first outlet 4 in the blowing direction is This is larger than the opening area OUTa of the outlet (outlet) downstream in the airflow direction. That is, the opening area of ​​the inlet and the opening area of ​​the outlet of the first outlet 4 are 1<(inlet opening area / outlet opening area).

[0043] The second partition plate 12 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the second outlet 5 in the blowing direction is the same as the opening area OUTa of the outlet (outlet) downstream of the second outlet 5 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the second outlet 5 are 1 = (inlet opening area / outlet opening area).

[0044] The third partition plate 13 is formed in a cylindrical shape and has the same area from upstream to downstream in the blowing direction of the conditioned air (fluid). Specifically, the opening area INa of the inlet upstream of the third outlet 6 in the blowing direction is the same as the opening area OUTa of the outlet (outlet) downstream of the third outlet 6 in the blowing direction. In other words, the opening area of ​​the inlet and the opening area of ​​the outlet of the third outlet 6 are expressed as 1 = (inlet opening area / outlet opening area).

[0045] In the above-described first to sixth modifications, the opening areas (INa, OUTa) of the first jet nozzle 4, the opening areas (INa, OUTa) of the second jet nozzle 5, and the opening areas (INa, OUTa) of the third jet nozzle 6 are adjusted so that the jet velocity U1 of the first jet 7 ejected from the first jet nozzle 4 is equal to or greater than the jet velocity U2 of the second jet 8 ejected from the second jet nozzle 5, and so that the jet velocity U3 of the third jet 9 is slower than the jet velocity U1 of the first jet 7 and the jet velocity U2 of the second jet 8. As a result, the relationship between the jet velocities U1, U2, and U3 is U1 ≥ U2 > U3.

[0046] In addition, the shape of the nozzle portion 3 in this embodiment is not limited to a perfect circular cylindrical shape or a truncated cone shape, but can also be an approximately perfect circular (including a slightly elliptical) cylindrical shape or a truncated cone shape, as long as the relationship of the jet velocity is U1≧U2>U3, and the same effect can be achieved.

[0047] Furthermore, although the nozzle portion 3 of this embodiment is shaped as a triple-layer nozzle, a nozzle with a triple or more layer configuration can also achieve the same effect. Preferably, a triple to quintuple-layer nozzle is suitable. [Industrial Applicability]

[0048] The present invention can be used for fluid transport for purposes such as air conditioning. [Explanation of symbols]

[0049] 1 Fluid transport device 2. Air conditioning ducts 3 Nozzle section 4 1st spout 5 2nd spout 6 Third spout 7 First Jet 8 Second Jet 9 Third Jet 11 First partition 12 Second partition 13 Third partition 101 fluid ejection nozzle 102 Air conditioning duct 103 Opening 104 Flange-shaped member 105 Fixing member 106 Nozzle body 107 Speech bubble A. Air-conditioned air B Space Air

Claims

1. A fluid conveying device having a nozzle portion that ejects conditioned air, which is a fluid, The nozzle portion is a first outlet formed by a cylindrical or truncated conical first partition plate having a first inlet formed upstream in the blowing direction of the fluid and a first outlet formed downstream in the blowing direction of the fluid, the first outlet being for ejecting the fluid that has flowed in from the first inlet through the first outlet; a second jet outlet formed in an annular shape so as to surround the outer periphery of the first jet outlet by a cylindrical second partition plate having a second inlet formed on the upstream side in the blowing direction of the fluid and a second outlet formed on the downstream side in the blowing direction of the fluid, the second jet outlet being configured to jet the fluid that has flowed in from the second inlet from the second outlet as an annular jet; a third jet outlet having a third inlet formed on the upstream side of the outer periphery of the second jet outlet in the blowing direction of the fluid and a third outlet formed on the downstream side of the blowing direction of the fluid, the third jet outlet being formed in an annular shape so as to surround at least a part of the outer periphery of the second jet outlet by a third partition plate having a truncated cone shape formed so as to increase in diameter from the third inlet toward the third outlet, and jetting the fluid that has flowed in from the third inlet from the third outlet as an annular jet; and the second inlet is disposed downstream of the third inlet in a blowing direction of the fluid, The fluid transport device, wherein the second outlet is disposed downstream of the third outlet in a blowing direction of the fluid.

2. 2. The fluid transport device according to claim 1, wherein the opening area of ​​the first inlet of the first partition plate is larger than the opening area of ​​the first outlet of the first partition plate.

3. 3. The fluid transporting device according to claim 1, wherein the third partition plate has an opening area of ​​the third inlet that is smaller than an opening area of ​​the third outlet.

4. 4. A fluid transport device according to claim 1, wherein the fluid is ejected so that U1 ≧ U2 > U3, where U1 is the velocity at which the fluid is ejected from the first ejection port, U2 is the velocity at which the fluid is ejected from the second ejection port, and U3 is the velocity at which the fluid is ejected from the third ejection port.

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