Patent Application
20240293767
The present application is based upon and claims the benefit of priority from Japanese Patent Application No. 2020-219259 filed with the Japan Patent Office on Dec. 28, 2020, the entire disclosure of which is entirely incorporated herein by reference.
The present disclosure relates to a gas-liquid separator that separates gas and liquid in a gas-liquid two-phase fluid.
In the prior art, a gas-liquid separator that swirls a gas-liquid two-phase fluid flowing through a pipe member by a swirling flow generator and separates the gas-liquid two-phase fluid into gas and liquid (see Patent Literature 1: JP 2010-104906 A, for example) is known.
In a conventional gas-liquid separator, the swirling flow generator includes blades extending spirally from the central axis of the pipe member. The distal ends of the blades in the pipe radial direction are continuous around the entire circumference of the pipe member when the pipe member is viewed from the axial direction thereof. Accordingly, there is no gap extending in the axial direction between adjacent blades. In addition, each of the blades contacts the inner circumferential surface of the pipe member along the entire length of the blade. When the gas-liquid two-phase fluid is at a low flow rate, the liquid does not become fine particles but naturally separates from the gas before swirling to become water droplets attached to the inner circumferential surface of the pipe member. The liquid in the form of water droplets flows along the pipe axial direction within the pipe member by the flow of gas. However, the flow is obstructed by the blades of the swirling flow generator because the blades are in contact with the inner circumferential surface of the pipe member. For this reason, it is necessary to provide a drain pipe at a position upstream of the swirling flow generator in the flow direction of the gas-liquid two-phase fluid to guide the water droplets to a water storage tank before the water droplets flow into a region where the swirling flow generator is located.
However, in the case where the drain pipe is provided and/or the drain pipe is connected to the water storage tank, such configuration deteriorates the degree of freedom to arrange various members of the gas-liquid separator and hinders cost reduction as the gas-liquid separator.
The present disclosure has been made in view of the above issues, and an object of the present disclosure is to provide a gas-liquid separator capable of collecting liquid at a position downstream of a swirling flow generator regardless of a flow rate of a gas-liquid two-phase fluid.
In order to achieve the above object, a gas-liquid separator of the present disclosure includes a pipe member through which a gas-liquid two-phase fluid flows, the gas-liquid two-phase fluid including gas and liquid; and a swirling flow generator within the pipe member. The swirling flow generator is configured to swirl the gas-liquid two-phase fluid to separate the gas and the liquid therefrom. The swirling flow generator includes blades that are spirally curved about a central axis of the pipe member. Each of the blades comprises a distal end in a pipe radial direction of the pipe member. The distal ends of the blades are continuous over an entire circumference of the pipe member when the pipe member is viewed from an axial direction thereof. A communication portion is provided between the pipe member and the swirling flow generator by forming a bulging portion. The bulging portion is formed on an inner circumferential surface of the pipe member to extend in the axial direction. The communication portion is configured to communicate a first space upstream of the swirling flow generator with a second space downstream of the swirling flow generator.
Hereinafter, an embodiment of a gas-liquid separator of the present disclosure is described based on a first embodiment illustrated in the drawings.
(First Embodiment) First, a configuration of the gas-liquid separator in the first embodiment is described separately with headings “Entire System Configuration of Application Example”, “Detailed Configuration of Gas-liquid Separator”, and “Detailed Configuration of Swirling Flow Generator”.
(Entire System Configuration of Application Example)
An intake passage 2 includes an intake port 2a at an end thereof. The intake passage 2 is provided with an air cleaner 4 for filtering intake gas, a compressor 5a of a turbocharger 5, an intercooler 6 for cooling intake gas, and a throttle valve 7 for adjusting the amount of the intake gas in this order from the intake port 2a side. The exhaust passage 3 is provided with a turbine 5b of the turbocharger 5, an exhaust purification catalyst 8 for purifying exhaust gas, and an exhaust throttle valve 9 for adjusting the flow rate of the exhaust gas in this order from the internal combustion engine 1 side. Note that a muffler 10 is provided downstream of the exhaust throttle valve 9, and an exhaust port 3a is formed downstream of the muffler 10.
The intake passage 2 and the exhaust passage 3 are connected by a low-pressure EGR passage 11 and a high-pressure EGR passage 12.
The “EGR” is an abbreviation of “exhaust gas recirculation” which is a technique of taking out a portion of the exhaust gas after combustion in the internal combustion engine 1 and taking in the exhaust gas again and is also referred to as exhaust gas recirculation.
The low-pressure EGR passage 11 connects the intake passage 2 upstream of the compressor 5a and the exhaust passage 3 downstream of the exhaust purification catalyst 8. On the other hand, the high-pressure EGR passage 12 connects the intake passage 2 downstream of the compressor 5a and the exhaust passage 3 upstream of the turbine 5b. Thereby, in the low-pressure EGR passage 11, the exhaust gas that passes through the turbine 5b returns to the intake side of the compressor 5a. In the high-pressure EGR passage 12, the exhaust gas before flowing into the turbine 5b returns to the intake side that passes through the compressor 5a.
The low-pressure EGR passage 11 is provided with an EGR cooler 13 and a low-pressure EGR valve 14. The EGR cooler 13 is configured to cool the exhaust gas guided to the intake passage 2. The low-pressure EGR valve 14 is configured to adjust the flow rate of the exhaust gas recirculated to the intake passage 2 via the low-pressure EGR passage 11. The high-pressure EGR passage 12 is provided with a high-pressure EGR valve 15. The high-pressure EGR valve 15 is configured to adjust the flow rate of the exhaust gas recirculated to the intake passage 2 via the high-pressure EGR passage 12.
In the low-pressure EGR passage 11, the exhaust gas can be recirculated without reducing the turbine passage exhaust amount of the turbocharger 5, and the NOx reduction effect is large. However, it is concerned that condensed water may be generated by cooling the EGR gas in the EGR cooler 13 or by mixing the EGR gas with the air during cold weather. Therefore, in the exhaust gas recirculation system S of the first embodiment, the gas-liquid separator 16 is provided at a position downstream of the low-pressure EGR valve 14 and upstream of the compressor 5a of the turbocharger 5 (a position surrounded by an alternate long and short dash line X shown in
(Detailed Configuration of Gas-liquid Separator)
The pipe member 21 has a first end that communicates with the intake port 2a and the low-pressure EGR valve 14 and a second end that communicates with the compressor 5a of the turbocharger 5 and exhaust gas in a state where gas and particulate liquid (condensed water) are mixed (hereinafter, referred to as “gas-liquid two-phase fluid”) flows. Further, the pipe member 21 is disposed such that a central axis O1 is arranged along the horizontal direction when mounted on the vehicle. The pipe member 21 is formed by connecting three pipes, namely, a first pipe 25, a second pipe 26, and a third pipe 27. The first pipe 25, the second pipe 26, and the third pipe 27 are sequentially connected from the upstream side in the flow direction of the gas-liquid two-phase fluid (the right side in
In the following description, the axial direction of the pipe member 21 (direction along the central axis O1) is referred to as a “pipe axial direction”, and the radial direction of the pipe member 21 (direction orthogonal to the central axis O1) is referred to as a “pipe radial direction”. Further, the circumferential direction of the pipe member 21 (the circumferential direction about the central axis O1) is referred to as a “pipe circumferential direction”.
The first pipe 25 is a straight pipe member in which the swirling flow generator 22 is provided. The first pipe 25 includes a swirling region 22a, a tapered region 25b, and a stepped portion 25c therewithin. The swirling region 22a is a region in which the swirling flow generator 22 is disposed. The tapered region 25b is a region in which the inner diameter dimension of the first pipe 25 gradually increases toward the fluid exiting side. The stepped portion 25c is a portion on which the second pipe 26 abuts. Here, the tapered region 25b is formed on the fluid exiting side of the swirling region 22a. The stepped portion 25c is formed on the fluid exiting side of the tapered region 25b. The inner diameter dimension of the first pipe 25 increases in the order of the swirling region 22a, the tapered region 25b, and the stepped portion 25c.
In addition, a bulging portion 25d is formed on an inner circumferential surface 25a of the first pipe 25. The bulging portion 25d is formed by protruding or denting a part of the inner circumferential surface 25a outwardly in the pipe radial direction to have steps. The bulging portion 25d has a groove-like shape and extends in the pipe axial direction. Also, the bulging portion 25d extends from an end portion (not illustrated) on the fluid entering side of the first pipe 25 at least to an end portion on the fluid exiting side of the swirling region 22a. Further, the bulging portion 25d has a predetermined width dimension W along the horizontal direction. A central position 25e of the bulging portion 25d in the pipe circumferential direction is positioned below the central axis O1 of the pipe member 21 in the vertical direction.
Moreover, the bulging portion 25d includes a bottom surface 25f which is flat in the horizontal direction. The bulging portion 25d has a depth H (i.e., a distance between the inner circumferential surface 25a of the first pipe 25 and the bottom surface 25f of the bulging portion 25d). The depth H of the bulging portion 25d includes end portions and the central position 25e in the pipe circumferential direction. The depth His the shallowest at the central position 25e and gradually deepens toward both end portions in the pipe circumferential direction.
The second pipe 26 is a T-shaped pipe member including a horizontal portion 26a and a vertical portion 26b. The horizontal portion 26a is connected to the first pipe 25. The vertical portion 26b is connected to the horizontal portion 26a in an orthogonal state.
The horizontal portion 26a includes a first end that is inserted into the first pipe 25. The first end of the horizontal portion 26a is in contact with the inner circumferential surface 25a of the first pipe 25 when inserted into the first pipe 25. Also, the first end of the horizontal portion 26a abuts the stepped portion 25c. The axial direction of the horizontal portion 26acoincides with the central axis O1 of the pipe member 21 and extends in the horizontal direction.
A drain opening 26c is formed at a connection portion between the horizontal portion 26a and the vertical portion 26b. The horizontal portion 26a and the vertical portion 26bcommunicate with each other. The drain opening 26c opens in the gravity direction (downward in the vertical direction of the central axis O1). The vertical portion 26b extends from the horizontal portion 26a along the gravity direction. As a result, the liquid separated from the gas-liquid two-phase fluid flows down by its weight through the vertical portion 26bvia the drain opening 26c.
In addition, the vertical portion 26b is connected to a contracted or tapered portion 26d. In the tapered portion 26d, the distribution area for the liquid gradually becomes smaller downward at the intermediate portion. A distal end opening 26e is formed at the distal end (lower end) of the tapered portion 26d. Because of the tapered portion 26d, the opening area of the distal end opening 26e is smaller than that of the drain opening 26c. The vertical portion 26b, the drain opening 26c, the tapered portion 26d, and the distal end opening 26e correspond to a drain pipe.
The third pipe 27 is a straight pipe member that is inserted into a second end of the horizontal portion 26a of the second pipe 26. The third pipe 27 has an outer diameter in which a gap a is generated between the outer circumferential surface of the third pipe 27 and the inner circumferential surface of the horizontal portion 26a when the third pipe 27 is inserted into the second pipe 26. A spacer 28 is fitted in the gap a. The spacer 28 has a cylindrical shape surrounding the entire outer circumferential surface of the third pipe 27 and is in contact with the horizontal portion 26a of the second pipe 26 and the third pipe 27. That is, the second end of the horizontal portion 26a is closed by the spacer 28. The third pipe 27 is inserted into the second pipe 26 until a first end portion 27a is positioned above the drain opening 26c. In addition, the third pipe 27 includes a vent 27b penetrating the circumferential surface of the third pipe 27. The vent 27b is formed at a position where the third pipe 27 protrudes from the second pipe 26. The vent 27b is connected to a second end portion 24b of the bypass pipe 24.
The water storage tank 23 includes a tank body 23a disposed below the vertical portion 26b of the second pipe 26. The tank body 23a includes a first opening 23b formed on an upper surface, a second opening 23c formed on a side surface, and a drain opening (not shown) formed on a bottom surface.
The first opening 23b is connected to the distal end opening 26e of the vertical portion 26b via a communication pipe 23d. The second opening 23c is connected to a first end portion 24a of the bypass pipe 24. The drain opening can be opened and closed as appropriate. The drain opening can be opened when the liquid stored in the tank body 23a reaches a certain amount to discharge the stored liquid to the outside of the tank.
The bypass pipe 24 is a tubular member with both ends open. The bypass pipe 24 includes the first end portion 24a connected to the second opening 23c of the tank body 23a and the second end portion 24b connected to the vent 27b of the third pipe 27. Accordingly, the internal space of the tank body 23a communicates with the inside of the third pipe 27 via the bypass pipe 24.
(Detailed Configuration of Swirling Flow Generator) The swirling flow generator 22 of the first embodiment is disposed in the swirling region 22a of the first pipe 25 to define the flow direction of the gas-liquid two-phase fluid flowing through the pipe member 21 and to swirl the gas-liquid two-phase fluid to be a swirling flow. As illustrated in
As illustrated in
Each of the blades 32 (four blades in this embodiment) protrudes in the pipe radial direction from the outer circumferential surface 31a of the blade support portion 31 and provided at equal angular intervals around the axial direction O2 of the blade support portion 31 about the axial direction O2 of the blade support portion 31 so that the blades spirally surround the blade support portion 31. When the swirling flow generator 22 is disposed in the swirling region 22a, the axial direction O2 of the blade support portion 31 coincides with the central axis O1 of the pipe member 21. Therefore, in a state where the swirling flow generator 22 is disposed in the swirling region 22a, each of the blades 32 extends to be spirally curved about the central axis O1 of the pipe member 21.
When the swirling flow generator 22 is disposed in the swirling region 22a, the distal ends 32a of the blades 32, except for a portion facing the bulging portion 25d on the inner circumferential surface 25a of the first pipe 25, contact the inner circumferential surface 25a of the first pipe 25 (the inner circumferential surface of the pipe member 21). A winding angle θ1 of each of the blade 32 with respect to the blade support portion 31 is set to about 90°. The “winding angle θ1” is an angle formed by a protruding direction L1 of the end portion 32b of the blade 32 on the fluid entering side and a protruding direction L2 of an end portion 32c of the blade 32 on the fluid exiting side when the swirling flow generator 22 is viewed from the pipe axial direction as shown in
In the swirling flow generator 22, the winding angle θ1 of each of the blades 32 (four blades in this embodiment) is set to about 90°. Accordingly, the distal ends 32a of the blades 32 are continuous over the entire circumferences of the pipe members 21 when viewed from the pipe axial direction, as illustrated in
The gas-liquid separator 16 of the first embodiment includes a communication portion 34 between the inner circumferential surface 25a of the first pipe 25, which is the pipe member 21, and the distal end 32a of the blade 32 of the swirling flow generator 22. The communication portion 34 is formed by providing the bulging portion 25d on the inner circumferential surface 25a of the first pipe 25 in which the swirling flow generator 22 is disposed. In other words, the communication portion 34 is formed on the inner circumferential surface 25a of the first pipe 25. The communication portion 34 is a space that extends in the pipe axial direction and communicates a first space X on the upstream side (fluid entering side) of the swirling region 22a where the swirling flow generator 22 is disposed (see
In addition, the height of the communication portion 34 is coincident with the depth H of the bulging portion 25d. The height of the communication portion 34 is set to be the lowest at the center position in the pipe circumferential direction and the highest at both end portions in the pipe circumferential direction. The height of the communication portion 34 (i.e., the depth H of the bulging portion 25d) is set at about 5% of the radius dimension of the pipe member 21 at the lowest center position in the pipe circumferential direction. A width dimension of the communication portion 34 in the horizontal direction is coincident with the width dimension W of the bulging portion 25d. The width dimension of the communication portion 34 is set to about 15% of the circumferential length of the inner circumferential surface of the pipe member 21 (the inner circumferential surface 25a of the first pipe 25) in the swirling region 22a.
Next, operations of the gas-liquid separator 16 of the first embodiment are described separately with headings “Liquid Collecting at High Flow Rate” and “Liquid Collecting at Low Flow Rate”
(Liquid Collecting at High Flow Rate) In the exhaust gas recirculation system S illustrated in
When the flow rate of the gas-liquid two-phase fluid is relatively high (for example, 20 m/s to 110 m/s at a high flow rate), the condensed water becomes fine particles and flows in a mixed phase together with the gas.
In the gas-liquid separator 16 of the first embodiment, as illustrated in
Therefore, as illustrated in
On the other hand, as illustrated in
As described above, in the gas-liquid separator 16 of the first embodiment, when the gas-liquid two-phase fluid flows at a high flow rate, the gas-liquid two-phase fluid is swirled by the swirling flow generator 22, and the gas and the liquid can be separated by centrifugal force. The gas-liquid separator 16 of the first embodiment guides the liquid toward the inner circumferential surface 25a of the first pipe 25 and attaches the liquid to the inner circumferential surface 25a, so that the liquid can be collected in the water storage tank 23 while suppressing re-scattering of the liquid.
(Liquid Collecting at Low Flow Rate) In the exhaust gas recirculation system S of the first embodiment, when the flow rate of the gas-liquid two-phase fluid is relatively slow (at a low flow rate, for example, 5 m/s to 20 m/s), the condensed water is less likely to be fine particles. In this case, as illustrated in
On the other hand, the liquid adhering to the inner circumferential surface 25a of the first pipe 25 cannot flow in a mixed phase together with the gas. The liquid flows toward the swirling region 22a while adhering to the inner circumferential surface 25a of the first pipe 25 by the flow of the gas.
In the first embodiment, the swirling flow generator 22 includes the blades 32 surrounding the blade support portion 31. The distal ends 32a of the blades 32 in the pipe radial direction are in contact with the inner circumferential surface 25a of the first pipe 25, and the winding angle θ1 of each of the blades 32 with respect to the blade support portion 31 is set to about 90°. In addition, the distal ends 32a of the blades 32 are continuous over the entire circumference of the pipe member 21 when viewed from the pipe axial direction. The communication portion 34 is provided between the inner circumferential surface 25a of the first pipe 25 and the blade 32 of the swirling flow generator 22. The communication portion 34 is formed by the bulging portion 25d on the inner circumferential surface 25a of the first pipe 25, which is the pipe member 21. The communication portion 34 extends in the pipe axial direction between the first pipe 25 and the swirling flow generator 22 and communicates the first space X upstream of the swirling region 22a with the second space Y downstream of the swirling region 22a.
Therefore, the liquid (water droplet) separated from the gas before flowing into the swirling region 22a flows through the communication portion 34 horizontally to the central axis O1 inside the pipe member 21 so that the liquid (water droplet) flows into the second space Y from the first space X. That is, the liquid adhering to the inner circumferential surface 25a of the first pipe 25 can smoothly pass through the swirling region 22a without being obstructed by the swirling flow generator 22.
The liquid that has passed through the swirling region 22a passes through the tapered region 25b while adhering to the inner circumferential surface 25a of the first pipe 25, and flows into the second pipe 26. The liquid flowing into the second pipe 26 flows while being attached to an inner circumferential surface 26f of the second pipe 26 and flows into the drain opening 26c to flow down the vertical portion 26b. Then, the liquid is discharged through the distal end opening 26e and stored in the tank body 23a.
As described above, in the gas-liquid separator 16 of the first embodiment, even when the flow rate of the gas-liquid two-phase fluid is relatively low, and the gas and the liquid are naturally separated before passing through the swirling region 22a, the liquid can flow through the communication portion 34 provided between the inner circumferential surface 25a of the first pipe 25 and the blade 32. Therefore, even if the distal ends 32a of the blades 32 are continuous over the entire circumference of the pipe member 21 when viewed from the pipe axial direction, the flow of the liquid is not obstructed by the blades 32, and the liquid can be collected on the fluid exiting side of the swirling flow generator 22. As a result, regardless of the flow rate of the gas-liquid two-phase fluid, the liquid can be collected at the position downstream of the swirling flow generator 22.
Further, in the gas-liquid separator 16 of the first embodiment, the communication portion 34 consists of the bulging portion 25d that is formed on the inner circumferential surface 25a of the first pipe 25, which is the pipe member 21, and extends in the pipe axial direction. Therefore, it is unnecessary to form a partial notch or recess in the distal end 32a of the blade 32 of the swirling flow generator 22, and thus the swirling flow generator 22 can be easily formed.
In addition, the bulging portion 25d, which forms the communication portion 34, has a groove-like shape to extend in the pipe axial direction. Therefore, the shape of the communication portion 34 can be easily set to the desired shape by adjusting the width dimension W in the horizontal direction and the depth H of the bulging portion 25d.
In addition, the bulging portion 25d formed on a part of the inner circumferential surface 25a of the first pipe 25. That is, the width dimension W of the bulging portion 25d is shorter than the circumferential length of the inner circumferential surface 25a. Therefore, the communication portion 34 becomes a space formed in a portion of the pipe circumferential direction between the inner circumferential surface 25a of the first pipe 25 and the blade 32. Thereby, the distal ends 32a of the blades 32, except for a portion facing the bulging portion 25d, contact the inner circumferential surface 25a of the first pipe 25. Therefore, the swirling flow generator 22 is supported by the pipe member 21 and thus the strength of the swirling flow generator 22 against vibration can be ensured.
Also, in the gas-liquid separator 16 of the first embodiment, the central position of the communication portion 34 in the pipe circumferential direction (the central position 25e of the bulging portion 25d in the pipe circumferential direction) is positioned below the central axis O1 of the pipe member 21 in the gravity direction when viewed in the pipe axial direction. As a result, the liquid flowing down to the lower portion of the pipe member 21 by its weight can flow into the communication portion 34, so that the liquid can be smoothly collected.
Particularly, in the first embodiment, the central position of the communication portion 34 (central position 25e) in the pipe circumferential direction is positioned below the central axis O1 of the pipe member 21 in the vertical direction. This ensures that the liquid flowing down to the lower portion of the pipe member 21 by gravity can reliably flow into the communication portion 34.
Moreover, in the gas-liquid separator 16 of the first embodiment, the gap a is generated between the second pipe 26 and the third pipe 27. Therefore, the liquid adhering to the inner circumferential surface 26f of the second pipe 26 enters the gap a, which prevents the liquid adhering to the inner circumferential surface 26f from flowing into the third pipe 27. In addition, the third pipe 27 on the fluid exiting side is inserted into the second pipe 26. Accordingly, an increase in the outer diameter dimension of the pipe member 21 can be suppressed, and a space required for installing the gas-liquid separator 16 can be suppressed.
In the first embodiment, the spacer 28 is attached to the second end of the horizontal portion 26a of the second pipe 26 to close the gap a, thereby, preventing the gas from leaking out between the second pipe 26 and the third pipe 27 and allowing the gas to flow smoothly into the third pipe 27.
In addition, in the first embodiment, the third pipe 27 and the water storage tank 23 communicate with each other via the bypass pipe 24. Therefore, the airflow through the third pipe 27 creates a negative pressure inside the water storage tank 23 and thus the flow of the liquid flowing down the vertical portion 26b can be smoothed. In the embodiment illustrated in
Although the gas-liquid separator of the present disclosure has been described based on the first embodiment, the specific configuration of the gas-liquid separator is not limited to the first embodiment. Any modifications, additions, and the like of the design of the gas-liquid separator are allowed without departing from the gist of the invention according to each of the claims.
In the gas-liquid separator 16 of the first embodiment, the central position of the communication portion 34 in the pipe circumferential direction (the central position 25e of the bulging portion 25d in the pipe circumferential direction) is positioned vertically below the central axis O1 of the pipe member 21. However, the position of the communication portion 34 is not limited thereto. For example, as illustrated in
As a result, even if a part of the liquid adhering to the inner circumferential surface 25a of the first pipe 25 flows in the pipe circumferential direction by the swirling flow, the liquid can flow into the communication portion 34. Therefore, in the gas-liquid separator 16, the flow of the liquid is not obstructed by the swirling flow generator 22, and the liquid can be appropriately collected downstream of the swirling flow generator 22.
Note that the swirling direction by the swirling flow generator 22 is not limited to the clockwise direction illustrated in
Further, in the gas-liquid separator 16 of the first embodiment, the bulging portion 25d is formed by protruding or denting a part of the inner circumferential surface 25a outwardly in the pipe radial direction to have the steps. However, the configuration of the bulging portion 25d is not limited thereto. The bulging portion 25d may be formed by progressively protruding a portion of the inner circumferential surface 25a of the first pipe 25 outward in the pipe radial direction. That is, in the gas-liquid separator 16, the communication portion 34 may be formed by such a bulging portion 25d. In particular, the circumferential shape of the first pipe 25 viewed from the pipe axial direction may include a perfect circle in the upper half of the pipe from the horizontal line L passing through the central axis O1 and an ellipse in the lower half of the pipe from the horizontal line L, as illustrated in
The swirling flow generator 22 includes a plurality of blades 32 all having the same shape, and the trajectory along the distal ends 32a of the blades 32 draws a circle about the central axis O1 when viewed from the pipe axial direction. Therefore, in the swirling region 22a, a gap or clearance is created between the inner circumferential surface 25a of the first pipe 25 and the distal end 32a of the blade 32 in the region below the horizontal line L, which becomes the communication portion 34.
Moreover, in the example illustrated in
In the gas-liquid separator 16 of the first embodiment, the swirling flow generator 22 includes the conical blade support portion 31 and the plurality of blades 32 protruding from the outer circumferential surface 31a of the blade support portion 31. However, the shape of the swirling flow generator 22 is not limited to that of the first embodiment. For example, the swirling flow generator may be formed from a spirally twisted plate member. That is, the present disclosure can be applied to any gas-liquid separator including a swirling flow generator including one or more blades that are spirally curved about the central axis O1 of the pipe member 21 and whose distal end in the pipe radial direction is continuous over the entire circumference of the pipe member 21 when viewed from the pipe axial direction.
In addition, in the first embodiment, the swirling flow generator 22 includes four blades 32 each of which is set to have the winding angle θ1 of about 90°. However, the number of the blades 32 is not limited to four and the angle of the winding angle θ1 is not limited to about 90°. The number of the blades 32 and the angle of the winding angle θ1 may be set as desired as long as the distal ends 32a of the blades 32 are continuous over the entire circumference of the pipe member 21 in the swirling flow generator 22 when viewed from the pipe axial direction.
In the first embodiment, the water storage tank 23 is connected to the distal end opening 26e of the vertical portion 26b. However, the vertical portion 26b and the water storage tank 23 may not necessarily be installed. The liquid discharged from the drain opening 26c may be directly discharged to the outside of the pipe member 21 without being stored. Further, the bypass pipe 24 is not necessarily provided.
In the first embodiment, even in the exhaust gas recirculation system S, the gas-liquid separator 16 is installed at the position downstream of the low-pressure EGR valve 14 and the position upstream of the compressor 5a of the turbocharger 5 (the position surrounded in the alternate long and short dash line X in
In addition, in the first embodiment, the internal combustion engine 1 is a diesel engine mounted on a vehicle. However, the present disclosure is not limited thereto, and the internal combustion engine 1 may be a gasoline engine.
In the first embodiment, the gas-liquid separator 16 is applied to the exhaust gas recirculation system S of the internal combustion engine 1. However, the application of the gas-liquid separator 16 is not limited to the above example. For example, the gas-liquid separator 16 may be applied to a refrigeration cycle device to separate the gas refrigerant and the liquid refrigerant. That is, the gas-liquid separator of the present disclosure may be applied to a device that separates gas and liquid from a gas-liquid two-phase fluid.
In addition, the shape of the pipe member 21, the connection point of the first pipe 25 and the like, the diameter dimensions of the pipes, the material to be used, and the like are not limited to those illustrated in the first embodiment and may be set as desired.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2020-219259 | Dec 2020 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2021/048474 | 12/27/2021 | WO |
