JP5871740B2 - Ejector - Google Patents

Description

  The present invention relates to an ejector.

  2. Description of the Related Art Ejectors that mix and eject a main fluid and a suction fluid sucked into the main fluid are widely used. Patent Document 1 discloses a gas-liquid mixer that mixes gas and liquid by providing a spiral body that converts a liquid flow into a swirling flow before a gas suction port.

Japanese Utility Model Publication No. 4-53437

  When the swirl flow generating means for swirling the main fluid is provided in the ejector, there is a problem that the suction amount of the suction fluid decreases.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to improve the suction amount of a suction fluid in an ejector including a swirl flow generating means for swirling a main fluid.

An ejector according to the present invention includes an inlet into which a main fluid flows, a diameter-reduced portion that is provided on the downstream side of the inlet, and that reduces the flow passage cross-sectional area of the main fluid; The swirling flow generating means to flow in, the one or two suction ports through which the suction fluid sucked by the negative pressure generated by the swirling flow of the main fluid that has passed through the reduced diameter portion, and the mixed fluid of the main fluid and the suction fluid are An inner outlet pressure at which the pressure changes along the inner circumference of the main fluid passage at a position where one or two suction ports form an opening in the inner wall of the main fluid passage. distribution is formed, the openings, Ri positions near opposite to the lowest pressure portions of the pressure is the lowest among the inner circumferential pressure distribution, the inner circumferential pressure distribution, and the lowest pressure portions of the two positions, a maximum pressure of 2 points And an elliptical isobaric pressure in a cross section perpendicular to the direction of travel of the main fluid. The position that intersects the long axis of the wire is the lowest pressure part, the position that intersects the short axis of the elliptical isobaric line is the highest pressure part, and the opening of one or two suction ports is not in contact with the highest pressure part Yes, with no suction ports other than one or two suction ports .
The ejector according to the present invention includes an inlet into which the main fluid flows, a diameter-reduced portion provided on the downstream side of the inlet, for reducing the cross-sectional area of the main fluid, and a swirling of the main fluid in the reduced-diameter portion. The swirling flow generating means that flows in as a flow, the plurality of suction ports through which the suction fluid sucked by the negative pressure generated by the swirling flow of the main fluid that has passed through the reduced diameter portion, and the mixed fluid of the main fluid and the suction fluid flow out. And an inner peripheral pressure distribution in which the pressure changes along the inner periphery of the main fluid channel at a position where the plurality of suction ports form openings in the inner wall of the main fluid channel. The opening is located at a position facing the lowest pressure portion where the pressure is lowest in the inner peripheral pressure distribution, and the swirl flow generating means is a swirl blade installed in the flow path of the main fluid and swirling the main fluid. The swirl vane is provided with a plurality of blades, and the inner pressure distribution is the number of blades. And having a plurality of minimum pressure portions formed accordingly, each of the openings of the plurality of suction ports is opposed to each of the plurality of minimum pressure portions and does not include any suction ports other than the plurality of suction ports. .

  According to the present invention, it is possible to improve the suction amount of the suction fluid in the ejector including the swirl flow generating means for swirling the main fluid.

It is a longitudinal cross-sectional view which shows the ejector of Embodiment 1 of this invention. It is a perspective view which shows the turning blade with which the ejector of Embodiment 1 of this invention is provided. It is the DD sectional view taken on the line in FIG. It is the EE sectional view taken on the line in FIG. It is a figure which shows the fluid analysis result of the pressure distribution of the main fluid which flows through the inside of an ejector provided with a swirl | wing blade. It is a figure which shows the fluid analysis result of the pressure distribution of the main fluid which flows through the inside of an ejector provided with a swirl | wing blade. It is a figure which shows the pressure distribution in the most restrictive part in the cross section cut | disconnected by the plane perpendicular | vertical to the main fluid advancing direction. It is the figure which represented typically the case where the negative pressure part angle in FIG. 7 is 0 degree. It is the figure which represented typically the case where the negative pressure part angle in FIG. 7 is 45 degrees. It is the figure which represented typically the case where the negative pressure part angle in FIG. 7 is 90 degrees. It is the figure which represented typically the case where the negative pressure part angle in FIG. 7 is 135 degrees. It is a graph which shows the relationship between negative pressure part angle (theta) and the flow volume of the suction fluid suck | inhaled from a suction port. It is a longitudinal cross-sectional view which shows the ejector of Embodiment 2 of this invention. It is the FF sectional view taken on the line in FIG. It is the GG sectional view taken on the line in FIG. It is a longitudinal cross-sectional view which shows the ejector of Embodiment 3 of this invention. It is the HH sectional view taken on the line in FIG. It is a longitudinal cross-sectional view which shows the ejector of Embodiment 4 of this invention. It is a longitudinal cross-sectional view which shows the ejector of Embodiment 5 of this invention. It is the JJ sectional view taken on the line in FIG.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, the same code | symbol is attached | subjected to the element which is common in each figure, and the overlapping description is abbreviate | omitted.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view showing an ejector according to Embodiment 1 of the present invention. FIG. 2 is a perspective view showing a swirl blade provided in the ejector 1 shown in FIG. 3 is a cross-sectional view taken along the line DD in FIG. 4 is a cross-sectional view taken along line EE in FIG.

  As shown in FIG. 1, the ejector 1 according to the present embodiment includes an inlet 2 into which a main fluid flows, a reduced diameter portion 3 that reduces the cross-sectional area of the main fluid, a most narrowed portion 5, and an enlarged diameter portion. 6 and the outlet 7 are disposed in this order from the upstream side along the traveling direction (flow direction) of the main fluid. In this embodiment, the cross-sectional shape of the internal space of the inflow port 2, the reduced diameter portion 3, the most narrowed portion 5, the enlarged diameter portion 6, and the outflow port 7 is all circular.

  The inner diameter of the inflow port 2 is constant along the traveling direction of the main fluid (hereinafter referred to as “main fluid traveling direction”). That is, the inflow port 2 has a substantially cylindrical internal space. The inner diameter of the reduced diameter portion 3 is continuously reduced in the main fluid traveling direction. That is, the reduced diameter portion 3 has a substantially conical internal space. The inner diameter of the reduced diameter portion 3 is minimum at the downstream end of the reduced diameter portion 3. The inner diameter of the most narrowed portion 5 is equal to the inner diameter of the downstream end of the reduced diameter portion 3. The inner diameter of the expanded diameter portion 6 is continuously expanded toward the main fluid traveling direction. That is, the enlarged diameter portion 6 has a substantially conical internal space. The inner diameter of the enlarged diameter portion 6 is minimum at the upstream end of the enlarged diameter portion 6. The inner diameter of the most restrictive portion 5 is equal to the inner diameter of the upstream end of the enlarged diameter portion 6. The taper angle of the enlarged diameter portion 6 is smaller than the taper angle of the reduced diameter portion 3. The inner diameter of the outlet 7 is constant along the main fluid traveling direction. That is, the outflow port 7 has a substantially cylindrical internal space. The inner diameter of the outflow port 7 is equal to the inner diameter of the downstream end of the enlarged diameter portion 6 (the maximum inner diameter of the enlarged diameter portion 6).

  When the main fluid flows through the ejector 1, negative pressure is generated in the main fluid at the most restrictive portion 5. The suction fluid is sucked from the suction port 4 using this negative pressure. The suction port 4 is formed so as to penetrate from the outer peripheral side toward the inner wall of the most restrictive portion 5, and an opening 41 is formed in the inner wall of the most restrictive portion 5 so as to communicate with the inside of the most restrictive portion 5. The length of the most restricting portion 5 in the main fluid traveling direction is substantially equal to the width of the suction port 4 in the main fluid traveling direction.

  The ejector 1 further includes swirl vanes 8 as swirl flow generating means for causing the main fluid to flow into the reduced diameter portion 3 as swirl flow SF. In the present embodiment, the swirl vane 8 is disposed at a downstream position in the inflow port 2 near the reduced diameter portion 3. As shown in FIG. 2, the swirl vane 8 has a cylindrical cylindrical portion 8a having an outer diameter substantially equal to the inner diameter of the inflow port 2, and a blade 8b fixed to the inner wall of the cylindrical portion 8a. In the present embodiment, two blades 8b are provided. By providing such swirl vanes 8 to form the swirl flow SF of the main fluid, the suction fluid can be refined and mixed with the main fluid. However, in the present invention, the shape of the swirl vane 8 is not limited to the configuration shown in FIG. 2, and the number of blades may be one, or may be three or more.

  The ejector 1 includes an attachment angle of the swirl blade 8 in the rotation direction around the center line of the main fluid flow path (hereinafter, simply referred to as “attachment angle of the swirl blade 8”), and swirl in the main fluid traveling direction. It is preferable to include an adjusting means (not shown) capable of adjusting one or both of the attachment position of the blade 8 (hereinafter simply referred to as “attachment position of the swirl blade 8”). Although the mechanism of such an adjustment means is not specifically limited, For example, it can comprise as follows. A claw (not shown) is provided on the outer peripheral surface of the cylindrical portion 8a of the swirl vane 8, and holes that can be fixed by engaging the claw on the inner peripheral surface of the inflow port 2 are provided at a plurality of different positions. When the inside of the inlet 2 is fixed, the hole on the inner peripheral surface of the inlet 2 with which the claw of the cylindrical portion 8a is engaged is selected from a plurality of holes, so that the swirl vane 8 is placed at the center of the flow path of the main fluid. The mounting angle of the swirl vane 8 is adjusted by rotating around the line, or the swirl vane 8 is moved in the main fluid traveling direction to install the swirl vane 8 (ie, the distance between the swirl vane 8 and the suction port 4). It is possible to configure an adjusting means that can adjust the above.

  As shown in FIG. 3, the suction port 4 is provided at a position offset to one side from the center of the most restrictive portion 5. Thereby, the suction fluid flowing in from the suction port 4 flows in from the tangential direction of the inner periphery of the most restrictive portion 5 (main fluid flow path). The inflow direction of the suction fluid flowing from the suction port 4 is the forward direction with respect to the swirl direction (rotation direction) of the swirl flow SF of the main fluid formed by the swirl vanes 8. With such a configuration, the flow of the suction fluid flowing from the suction port 4 can be prevented from interfering with the swirling flow SF of the main fluid, and the suction amount can be improved. Moreover, as shown in FIG. 4, the cross-sectional shape which cut | disconnected the suction port 4 by the plane perpendicular | vertical to the flow direction of a suction fluid is a rectangular shape (rectangular shape).

  FIG. 5 and FIG. 6 are diagrams showing the fluid analysis results of the pressure distribution of the main fluid flowing in the ejector 1 having the swirl vanes 8. FIG. 5 shows the respective pressure distributions of the three cross-sections behind the most restrictive portion 5, that is, the cross-section AA, the cross-section BB, and the cross-section CC. Is displayed as a negative pressure part. However, in FIG. 5 and FIG. 6, the suction port 4 is not modeled for easy understanding of the phenomenon of pressure distribution, and instead of the most restricting portion 5 as in an ejector 1D shown in FIG. The analysis was performed using a model in which the stepped enlarged diameter portion 10 and the straight portion 11 were provided.

  When the cross section AA, the cross section BB, and the cross section CC at the flow rate of 12 L / min are viewed, the elliptical negative pressure distribution formed by overlapping two circles advances while rotating backward. I understand that Furthermore, when the flow rate is changed and compared with 9 L / min and 6 L / min, it can be seen that the rotation angle of the negative pressure distribution of the elliptical shape or the two circles of the same cross section is the same regardless of the flow rate.

  FIG. 6 shows the pressure distribution in the section AA at a constant flow rate over time. When the pressure distribution of 0.1 second to 0.4 second shown in FIG. 6 is seen, it is found that the pressure distribution is in a steady state and the pressure distribution does not change over time.

  As can be seen from the analysis results shown in FIGS. 5 and 6, the pressure distribution on the downstream side of the reduced diameter portion 3 in the ejector 1 having the swirl vanes 8 shows a constant tendency regardless of the flow rate and time. That is, in the cross section (hereinafter, referred to as “vertical cross section in the traveling direction”) of the main fluid flow path on the downstream side of the reduced diameter portion 3 along a plane perpendicular to the main fluid traveling direction, The position of the region in which the height increases is constant without changing with the flow rate or time.

  On the other hand, as will be described below, the pressure distribution in the flow path of the main fluid in the vertical cross section in the traveling direction depends on the shape of the swirling blade 8, the mounting angle of the swirling blade 8, or the mounting position of the swirling blade 8. Change.

  FIG. 7 is a view showing the pressure distribution in the most restrictive portion 5 in the vertical cross section in the traveling direction. In the example shown in FIG. 7, the distance between the suction port 4 and the swirl vane 8 is fixed, and the pressure distribution in the vertical cross section in the traveling direction is changed by changing the mounting angle of the swirl vane 8 to four different angles. .

  8 to 11 are diagrams schematically showing the four diagrams shown in FIG. 7 separately. 8 to 11, the pressure distribution in the most narrowed portion 5 in the vertical cross section in the traveling direction is represented by isobars. These isobaric lines have a lower pressure (that is, a larger negative pressure) as the inner isobaric lines. As shown in FIGS. 8 to 11, an elliptical negative pressure portion (negative pressure region) as a whole is generated in the most narrowed portion 5 in the vertical cross section in the traveling direction. The pressure in the vicinity of the inner periphery of the most restrictive portion 5 varies along the circumferential direction. Hereinafter, the pressure distribution along the inner circumference of the most restrictive portion 5 is referred to as an “inner circumference pressure distribution”. In the inner peripheral pressure distribution of the most restrictive portion 5, the pressure is lowest (that is, the negative pressure is maximum) at the position where it intersects the major axis of the elliptical negative pressure portion, and intersects the minor axis of the elliptical negative pressure portion. The pressure at the position is highest (ie, negative pressure is minimum or positive). 8 to 11, the position where the pressure is lowest (that is, the negative pressure is maximum) in the inner peripheral pressure distribution of the most restrictive portion 5 is represented as the lowest pressure portion X. Is the maximum pressure portion Y (ie, the negative pressure is minimum or positive pressure). In the present embodiment, in the inner peripheral pressure distribution of the most narrowed portion 5, the lowest pressure portion X occurs at two locations, and the highest pressure portion Y also occurs at two locations.

  As shown in FIGS. 8 to 11, an opening 41 is formed by the suction port 4 on the inner wall of the most restrictive portion 5 (main fluid flow path). In the present embodiment, the opening 41 is formed in a range in which the central angle with respect to the center O of the most narrowed portion 5 is 90 ° in the vertical cross section in the traveling direction.

  If the shape of the swirling blade 8, the mounting angle of the swirling blade 8, and the mounting position of the swirling blade 8 are the same, the positions of the lowest pressure portion X and the highest pressure portion Y do not change depending on the flow rate and time of the main fluid. Is constant. The positions of the lowest pressure part X and the highest pressure part Y can be changed as shown in FIG. 8 to FIG. 11 by making the attachment position of the swirl vane 8 constant and changing the attachment angle of the swirl vane 8. Alternatively, the positions of the lowest pressure part X and the highest pressure part Y can be changed as shown in FIGS. 8 to 11 by making the attachment angle of the swirl blade 8 constant and changing the attachment position of the swirl blade 8.

  Here, in FIGS. 8 to 11, an angle formed by a straight line connecting the center O of the most restrictive portion 5 and one lowest pressure portion X with respect to a horizontal line in the drawing is defined as a negative pressure portion angle θ. 8 shows a case where the negative pressure portion angle θ is 0 ° (comparative example), FIG. 9 shows a case where the negative pressure portion angle θ is 45 ° (comparative example), and FIG. 10 shows that the negative pressure portion angle θ is 90 °. FIG. 11 shows the case where the negative pressure part angle θ is 135 ° (this embodiment). FIG. 12 is a graph showing the relationship between the negative pressure portion angle θ and the flow rate of the suction fluid sucked from the suction port 4 (hereinafter referred to as “suction amount”).

  As shown in FIG. 12, the suction amount of the suction fluid is maximized when the negative pressure portion angle θ is 135 ° among the negative pressure portion angle θ of 0 °, 45 °, 90 °, and 135 °. This is due to the following reason. As shown in FIG. 11, when the negative pressure portion angle θ is 135 °, the position of the opening 41 of the suction port 4 is a position facing the lowest pressure portion X. Thereby, since the big negative pressure of the minimum pressure part X can fully be exerted on the suction port 4, the pressure which acts on the suction port 4 can be made low enough (namely, a negative pressure is made large enough). As a result, the suction amount of the suction fluid can be increased. When the negative pressure portion angle θ is 135 °, the position of the opening 41 of the suction port 4 is a position not in contact with the maximum pressure portion Y. As a result, the positive pressure of the maximum pressure portion Y can be prevented from reaching the suction port 4 and the pressure acting on the suction port 4 can be lowered (that is, the negative pressure can be increased). Can be made larger.

  On the other hand, as shown in FIG. 9, when the negative pressure portion angle θ is 45 °, the position of the opening 41 of the suction port 4 is the position facing the highest pressure portion Y and the lowest pressure portion X. It is a position that does not oppose (does not touch). As a result, the positive pressure of the maximum pressure portion Y reaches the suction port 4, so that the pressure acting on the suction port 4 cannot be made sufficiently low (that is, the negative pressure is made sufficiently large), and suction of suction fluid is performed. The amount becomes smaller.

  As shown in FIG. 8, when the negative pressure portion angle θ is 0 °, the lowest pressure portion X is in contact with one end of the opening 41 of the suction port 4, and the opening 41 of the suction port 4 is the lowest. It is not facing (directly facing) the pressure part X. For this reason, the large negative pressure of the lowest pressure part X cannot be sufficiently exerted on the suction port 4. Further, since the other end of the opening 41 of the suction port 4 is in contact with the maximum pressure portion Y, the positive pressure of the maximum pressure portion Y reaches the suction port 4. For this reason, when the negative pressure portion angle θ is 0 °, the pressure acting on the suction port 4 cannot be made sufficiently low (that is, the negative pressure is made sufficiently large), and the suction amount of the suction fluid is reduced. Becomes smaller. Also when the negative pressure part angle θ shown in FIG. 10 is 90 °, the suction amount of the suction fluid becomes small for the same reason as when the negative pressure part angle θ is 0 °.

  From the above, it can be seen that the suction amount of the suction fluid can be sufficiently improved by configuring the opening 41 of the suction port 4 to face the lowest pressure portion X in the vertical cross section in the traveling direction. As shown in FIG. 11, the ejector 1 of the present embodiment is configured such that the position of the opening 41 of the suction port 4 faces the lowest pressure part X in the vertical cross section in the traveling direction. For this reason, according to the ejector 1 of this embodiment, the suction | attraction amount of a suction fluid can fully be improved. In addition, even when a flow path configuration in which a pressure loss body having a large pressure loss is added to the downstream side of the ejector 1, natural suction from the suction port 4 can be made possible.

  As described above, the position of the opening 41 of the suction port 4 is configured to face the lowest pressure portion X by making the attachment position of the swirl blade 8 constant and setting the attachment angle of the swirl blade 8 to an appropriate angle. It is possible. Alternatively, it is possible to configure the position of the opening 41 of the suction port 4 to face the lowest pressure portion X by making the mounting angle of the swirling blade 8 constant and setting the mounting position of the swirling blade 8 to an appropriate position. It is. In this case, the position of the opening 41 of the suction port 4 is opposed to the lowest pressure part X by adjusting one or both of the mounting angle of the swirl blade 8 and the mounting position of the swirl blade 8 by the adjusting means as described above. Alternatively, in the design stage, an appropriate mounting angle and mounting position of the swirl blade 8 such that the position of the opening 41 of the suction port 4 is opposed to the lowest pressure portion X is determined, as described above. The swirl vanes 8 may be fixed or integrally formed with the main body of the ejector 1 without using any adjustment means.

  Moreover, in the ejector 1 of this embodiment, when the adjustment means as described above is provided, the attachment angle of the swirl blade 8 and the attachment position of the swirl blade 8 are set so that the suction amount of the suction fluid is maximized. It is desirable that one or both of these are adjusted. This makes it possible to maximize the suction amount of the suction fluid.

  As shown in FIG. 11, in this embodiment, the lowest pressure portion X is positioned substantially at the center of the opening 41 of the suction port 4 in the vertical cross section in the traveling direction. Since the pressure can be exerted on the mouth 4, the pressure acting on the suction mouth 4 can be further reduced (that is, the negative pressure can be made sufficiently large). As a result, the suction amount of the suction fluid can be increased. Thus, in the present invention, it is particularly preferable that the lowest pressure portion X is positioned in the vicinity of the center of the opening 41 of the suction port 4 in the vertical cross section in the traveling direction. However, in the present invention, the minimum pressure portion X does not necessarily have to be positioned near the center of the opening 41 of the suction port 4, and it is sufficient that the minimum pressure portion X is included in the range of the opening 41 of the suction port 4.

  As described above, when the negative pressure portion angle θ shown in FIG. 11 is 135 °, unlike the case shown in FIGS. 8 to 10, the opening 41 of the suction port 4 is not in contact with the maximum pressure portion Y. . In the present invention, it is preferable that the opening 41 of the suction port 4 is in a position not in contact with the maximum pressure portion Y as described above. As a result, the positive pressure of the maximum pressure portion Y can be prevented from reaching the suction port 4 and the pressure acting on the suction port 4 can be lowered (that is, the negative pressure can be increased). Can be made larger. On the other hand, unlike this embodiment, when the opening 41 of the suction port 4 is too large in the circumferential direction, or extremely when the entire circumference on the circumference of the most restrictive portion 5 is the suction port 4 Since a part of the opening 41 of the suction port 4 comes into contact with the maximum pressure portion Y, the positive pressure of the maximum pressure portion Y reaches the suction port 4 and the negative pressure acting on the suction port 4 becomes small. The suction amount of the suction fluid is reduced.

  As shown in FIG. 4, in this embodiment, the cross-sectional shape of the suction port 4 cut along a plane perpendicular to the flow direction of the suction fluid is a rectangular shape with the main fluid traveling direction as the short side. The negative pressure formed by the swirling flow of the main fluid that has passed through the reduced diameter portion 3 becomes smaller as the main fluid advances. For this reason, if the suction port 4 has a shape spreading in the main fluid traveling direction, the negative pressure acting on the suction port 4 may be weakened. In this embodiment, by making the cross-sectional shape of the suction port 4 the above shape, the length of the suction port 4 in the main fluid traveling direction can be shortened with the same cross-sectional area as compared with the case where the cross-sectional shape is circular, for example. Therefore, the negative pressure acting on the suction port 4 can be sufficiently increased without reducing the cross-sectional area of the suction port 4. For this reason, the suction amount of the suction fluid can be further increased.

Embodiment 2. FIG.
Next, the second embodiment of the present invention will be described with reference to FIG. 13 to FIG. The description is omitted. FIG. 13 is a longitudinal sectional view showing the ejector according to the second embodiment of the present invention. 14 is a cross-sectional view taken along line FF in FIG. 15 is a cross-sectional view taken along the line GG in FIG.

  As shown in FIG. 14, in the ejector 1 </ b> A of the second embodiment, the suction port 4 </ b> A has an inner wall of the most restrictive portion 5 from the outer peripheral side along a straight line passing through the center of the most restrictive portion 5 in the vertical cross section in the traveling direction. It is formed so as to penetrate through toward. As shown in FIG. 15, the cross-sectional shape obtained by cutting the suction port 4A along a plane perpendicular to the flow direction of the suction fluid is circular. In the ejector 1A of the second embodiment, although not shown, by setting the attachment angle and the attachment position of the swirler 8 so that the negative pressure portion angle θ is substantially 90 °, as in FIG. The opening 41A formed on the inner wall of the most restrictive portion 5 (main fluid flow path) by the suction port 4A can be configured to face the lowest pressure portion X.

Embodiment 3 FIG.
Next, the third embodiment of the present invention will be described with reference to FIG. 16 and FIG. 17. The description will focus on the differences from the first embodiment described above, and the same or corresponding parts will be denoted by the same reference numerals. The description is omitted. FIG. 16 is a longitudinal sectional view showing an ejector according to Embodiment 3 of the present invention. 17 is a cross-sectional view taken along line HH in FIG.

  As shown in FIG. 17, in the ejector 1B of the third embodiment, two suction ports 4B and 4C are provided. The position of the opening 41B formed by the suction port 4B on the inner wall of the most restrictive portion 5 (main fluid flow path) and the position of the opening 41C formed by the suction port 4C on the inner wall of the most restrictive portion 5 (main fluid flow path). Are different positions in the circumferential direction.

  Depending on the number of blades 8b of the swirl vane 8, etc., the minimum pressure portion X in the inner peripheral pressure distribution may be formed at a plurality of locations. In such a case, a plurality of suction ports 4B and 4C are provided as in the ejector 1B of the third embodiment, and the openings 41B and 41C are positioned to face each of the plurality of lowest pressure portions X. By doing so, the suction amount of the suction fluid can be further improved.

Embodiment 4 FIG.
Next, a fourth embodiment of the present invention will be described with reference to FIG. 18. The description will focus on the differences from the first embodiment described above, and the same or corresponding parts will be denoted by the same reference numerals. Is omitted. FIG. 18 is a longitudinal sectional view showing an ejector according to Embodiment 4 of the present invention.

  As shown in FIG. 18, the ejector 1 </ b> D according to the fourth embodiment includes a step-shaped enlarged diameter portion 10 and a straight portion 11 instead of the most narrowed portion 5 as compared with the ejector 1 according to the first embodiment. Yes. The inner diameter of the straight portion 11 formed on the downstream side of the reduced diameter portion 3 is slightly larger than the inner diameter of the downstream end of the reduced diameter portion 3 (the minimum inner diameter of the reduced diameter portion 3), and along the main fluid traveling direction. It is constant. At the boundary between the reduced diameter portion 3 and the straight portion 11, a stepped diameter enlarged portion 10 whose inner diameter increases stepwise is formed. The suction port 4 is formed so as to penetrate the inner wall in the vicinity of the upstream end of the straight portion 11 (that is, in the vicinity of the stepped enlarged diameter portion 10). In the ejector 1D, the opening 41 formed in the inner wall near the upstream end of the straight portion 11 by the suction port 4 is the lowest pressure portion X in the inner peripheral pressure distribution formed along the inner periphery near the upstream end of the straight portion 11. The mounting angle and the mounting position of the swirl vane 8 are set so as to face each other. According to the ejector 1D of the fourth embodiment, the same effects as those of the first embodiment can be obtained.

Embodiment 5 FIG.
Next, the fifth embodiment of the present invention will be described with reference to FIG. 19 and FIG. The description is omitted. FIG. 19 is a longitudinal sectional view showing an ejector according to a fifth embodiment of the present invention. 20 is a cross-sectional view taken along line JJ in FIG.

  The ejector 1E of the fifth embodiment is the same as the ejector 1 of the first embodiment except that the configuration of the swirling flow generating means is different. As shown in FIG. 19, in the ejector 1E of the fifth embodiment, the swirl vane 8 is omitted. As shown in FIG. 20, the main fluid inlet 12 through which the main fluid flows is provided in the inlet 2 of the ejector 1 </ b> E along the tangential direction of the inner periphery of the inlet 2. In the configuration shown in the figure, the two main fluid inlets 12 are arranged at positions (point-symmetric positions) that differ in angle by 180 ° with respect to the center of the inlet 2. In the ejector 1E of the fifth embodiment, the main fluid flows into the inlet 2 from the main fluid introduction port 12, whereby a swirling flow of the main fluid is formed, and the swirling flow flows into the reduced diameter portion 3. .

  When a swirl flow is generated with the configuration of the ejector 1E described above, the distance between the main fluid introduction port 12 and the suction port 4, the arrangement position (angle) of the main fluid introduction port 12 with respect to the suction port 4, or the main flow By changing the number of body introduction ports 12, the inner peripheral pressure distribution at the location where the suction port 4 is formed is changed, and the opening 41 formed by the suction port 4 on the inner wall of the flow path of the main fluid has the inner peripheral pressure distribution. It can be configured to face the lowest pressure part X. Thereby, the suction amount of the suction fluid can be sufficiently improved.

  Although the embodiments of the ejector of the present invention have been described above, the main fluid and the suction fluid in the ejector of the present invention may be any of gas, liquid, solid (powder), and any combination. But you can.

1, 1A, 1B, 1C, 1D, 1E Ejector, 2 inlet, 3 reduced diameter part,
4, 4A, 4B, 4C Suction port, 5 Most narrowed part, 6 Expanded part, 7 Outlet, 8 Swivel blade,
8a Cylindrical part, 8b blade, 10 step-shaped enlarged diameter part, 11 straight part,
12 Main fluid inlet, 41, 41A, 41B, 41C Open

Claims (4)

An inlet into which the main fluid flows,
A reduced diameter portion that is provided on the downstream side of the inlet and reduces the cross-sectional area of the flow path of the main fluid;
A swirl flow generating means for causing the main fluid to flow into the reduced diameter portion as a swirl flow;
One or two suction ports through which a suction fluid sucked by a negative pressure generated by a swirling flow of the main fluid that has passed through the reduced diameter portion passes;
An outlet through which a mixed fluid of the main fluid and the suction fluid flows out;
With
At a position where the one or two suction ports form an opening in the inner wall of the main fluid channel, an inner peripheral pressure distribution is formed in which the pressure changes along the inner periphery of the main fluid channel, opening, Ri positions near opposite to the lowest pressure portions of the pressure is the lowest among the inner circumferential pressure distribution,
The inner peripheral pressure distribution has two lowest pressure portions and two highest pressure portions, and intersects with a major axis of an elliptical isobar in a vertical cross section in a traveling direction perpendicular to the traveling direction of the main fluid. The position is the lowest pressure part, and the position that intersects the minor axis of the elliptical isobar is the highest pressure part,
The opening of the one or two suction ports is in a position not in contact with the maximum pressure portion;
An ejector having no suction port other than the one or two suction ports . An inlet into which the main fluid flows,
A reduced diameter portion that is provided on the downstream side of the inlet and reduces the cross-sectional area of the flow path of the main fluid;
A swirl flow generating means for causing the main fluid to flow into the reduced diameter portion as a swirl flow;
A plurality of suction ports through which a suction fluid sucked by a negative pressure generated by a swirling flow of the main fluid that has passed through the reduced diameter portion passes;
An outlet through which a mixed fluid of the main fluid and the suction fluid flows out;
With
At a position where the plurality of suction ports form openings in the inner wall of the main fluid flow path, an inner peripheral pressure distribution in which the pressure changes along the inner periphery of the main fluid flow path is formed. Ri position near facing to the lowest pressure portions of the pressure is the lowest among the inner circumferential pressure distribution,
The swirl flow generating means is installed in a flow path of the main fluid, and is composed of swirl vanes that swirl the main fluid,
The swirler includes a plurality of blades,
The inner peripheral pressure distribution has a plurality of the lowest pressure portions formed according to the number of the blades,
Each of the openings of the plurality of suction ports is opposed to each of the plurality of minimum pressure portions,
An ejector having no suction ports other than the plurality of suction ports . The swirl flow generating means is installed in a flow path of the main fluid, and is composed of swirl vanes that swirl the main fluid,
Adjustment capable of adjusting one or both of the swivel blade attachment angle in the rotation direction around the center line of the main fluid flow path and the swivel blade attachment position in the main fluid traveling direction The ejector according to claim 1, further comprising means.   The suction fluid flowing in from the suction port flows in from a tangential direction of an inner periphery of the flow path of the main fluid, and an inflow direction of the suction fluid is a forward direction with respect to a swirling flow of the main fluid. The ejector according to any one of 1 to 3.

Images