JP2012206019A - Pressure exchange device - Google Patents

Pressure exchange device Download PDF

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Publication number
JP2012206019A
JP2012206019A JP2011073730A JP2011073730A JP2012206019A JP 2012206019 A JP2012206019 A JP 2012206019A JP 2011073730 A JP2011073730 A JP 2011073730A JP 2011073730 A JP2011073730 A JP 2011073730A JP 2012206019 A JP2012206019 A JP 2012206019A
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fluid
pressure
rotating
path
seawater
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JP5657450B2 (en
Inventor
Yoshifumi Hirosawa
Norihiro Teramoto
Akira Shozaki
憲博 寺本
晃 庄▲崎▼
慶文 廣澤
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Kubota Corp
株式会社クボタ
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    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02ATECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A20/00Water conservation; Efficient water supply; Efficient water use
    • Y02A20/124Water desalination
    • Y02A20/131Reverse-osmosis

Abstract

PROBLEM TO BE SOLVED: To provide a pressure exchange device, allowing reduction in size and cost without lowering the treatment flow rate.SOLUTION: The pressure exchange device 10 includes: a rotator 40 having a pressure transmission part disposed around a shaft center, the pressure transmission part including a first flow passage 41 and a second flow passage 42 which are formed to communicate with each other; a first lateral member 20 having a first fluid inflow path 21 for guiding high-pressure condensed seawater Hi to the first flow passage 41, a second fluid outflow path 22 for guiding high-pressure seawater Ho from the second flow passage 42, a second fluid inflow path 23 for guiding low-pressure seawater Li from the first flow passage 41 and a first fluid outflow path 24 for guiding low-pressure condensed seawater Lo from the first flow passage 41; and a second lateral member 30 rotatably holding the rotator 40 with the first lateral member 20 through a holding member 11. Pressure balance is adjusted by high-pressure condensed seawater Hi or high-pressure seawater Ho entered to a gap between the rotator 40 and the first and second lateral members and a gap between the rotator 40 and the holding member 11.

Description

  The present invention relates to a pressure exchange device that exchanges pressure between a first fluid and a second fluid.

  In seawater desalination facilities that use reverse osmosis membrane devices, the excess pressure of high-pressure concentrated seawater, which is high-pressure concentrated fluid drained from the reverse osmosis membrane device, is reduced by low-pressure seawater, which is the concentrated fluid supplied to the reverse osmosis membrane device. A pressure exchanging device used for boosting is provided.

  As shown in FIG. 11, Patent Document 1 describes a pressure exchange device including a rotor 80 in which a plurality of tubular pressure transmission units are arranged around a rotation axis.

  As the rotor 80 rotates, the pressure exchange device causes the high-pressure concentrated seawater supplied to the high-pressure inlet-side port 82 and the low-pressure seawater supplied to the low-pressure inlet-side port 81 to come into contact with each other by the pressure transmission unit. The low-pressure seawater boosted by the pressure of the seawater is drained as high-pressure seawater from the high-pressure outlet-side port 83, and the low-pressure concentrated seawater that has been transmitted by the low-pressure seawater supplied to the low-pressure inlet-side port 81 It is configured to drain from.

  As shown in FIG. 12, Patent Document 2 describes a pressure exchanging device including a rotating body 90 including a pair of rotating plates 91 and 92 and a shaft 93 connecting the rotating plates 91 and 92. Yes.

  One rotating plate 91 guides the low-pressure seawater supplied to the low-pressure inlet side port 95 to the pressure transmission unit 96 and the high-pressure seawater drained from the pressure transmission unit 96 to the high-pressure outlet side port 97. A flow path 91b is formed.

  The other rotary plate 92 has a flow path 92b for guiding the high-pressure concentrated seawater supplied to the high-pressure inlet side port 94 to the pressure transmission unit 96, and the low-pressure concentrated seawater drained from the pressure transmission unit 96 at the low-pressure outlet side port 98. A flow path 92a is formed to guide the flow.

  The pressure exchanging device converts the high-pressure concentrated seawater supplied to the high-pressure inlet-side port 94 and the low-pressure seawater supplied to the low-pressure inlet-side port 95 in the tubular pressure transmission unit 96 as the rotating body 90 rotates. The low-pressure seawater that has been brought into contact and drained as high-pressure seawater from the high-pressure outlet side port 97 is increased by the pressure of the high-pressure concentrated seawater. It is configured to drain from the low pressure outlet side port 98.

US Patent Application Publication No. 2008090903 Chinese Patent Application Publication No. 200710056401

  In the pressure exchanging device described in Patent Document 1, since the processing flow rate to which pressure is transmitted is determined depending on the cross-sectional area of the tubular pressure transmission portion disposed in the rotor 80, in order to increase the processing flow rate, It is necessary to increase the number of transmission parts or to increase the cross-sectional area per pressure transmission part. In any case, the rotor 80 becomes large, and the pressure exchange device becomes large accordingly. The weight also increases.

  In general, the rotor 80 is formed of an expensive material such as ceramics in order to satisfy conditions such as weight reduction, high rigidity, wear resistance, and a low friction coefficient. Along with this, there is a problem that material costs and manufacturing costs increase.

  Furthermore, the torque required to rotate the large rotor 80 also increases, requiring more energy than the case of rotating the small rotor 80, and there is a problem that efficiency is lowered. For these reasons, it has been extremely difficult to increase the processing flow rate per pressure exchange device.

  Therefore, a large number of pressure exchange devices have been installed in a large-scale seawater desalination facility that desalinates a large amount of seawater. However, when the number of installed pressure exchange devices increases, there is a problem that the construction and management of piping connecting the pressure exchange devices becomes complicated.

  In the pressure exchanging device described in Patent Document 2, each of the flow path 91b formed in one rotary plate 91 and the flow path 92b formed in the other rotary plate 92 extends along the axial direction inside the rotary body. Since the flow path formed in the circumferential direction communicates with the remaining flow path, a thickness for forming the flow path on the rotating plates 91 and 92 is required. For this reason, there is a problem that the rotating plates 91 and 92 become large and material costs and processing costs increase.

  Further, when the weight increases due to an increase in the size of the rotating plates 91 and 92, torsional and bending stress acting on the shaft portion 93 when the rotating body 90 rotates increases, and the shaft portion 93 is thickened to prevent deformation and breakage. In addition to this, there is a problem in that the energy required for rotation increases and efficiency decreases.

  An object of the present invention is to provide an efficient pressure exchange device that can be made compact and cost-effective without reducing the processing flow rate.

  In order to achieve the above-mentioned object, the first characteristic configuration of the pressure exchange device according to the present invention is that pressure is applied between the first fluid and the second fluid as described in claim 1 of the claims. A pressure exchanging device for exchanging, wherein a first flow path through which a first fluid flows in and out from one end side and a second flow path from which the second fluid flows in and out from the one end side are communicated with each other. The pressure transmission unit is a second body that is pressure-exchanged between the rotating body disposed around the rotation axis, the first fluid inflow path that guides the first fluid to the first flow path, and the first fluid. The first fluid that is pressure-exchanged between the second fluid outflow path that guides the fluid from the second flow path, the second fluid inflow path that guides the second fluid to the second flow path, and the second fluid A first fluid outflow path that guides the first flow path from the first flow path, a first side member formed in a thickness direction, and the rotating body as a first flow path. And a second side member that is rotatably held between the side members via a holding member, and the first flow path and the second flow path pass through the rotating body. The pressure balance adjusting mechanism is configured to adjust the pressure balance of the pressure exchanging portion by the first fluid or the second fluid.

  According to the above configuration, the rotating body rotates in the space defined by the first side member, the second side member, and the holding member, and flows into the first flow path from the first fluid inflow path. The second fluid pressure-transmitted from one fluid flows out from the second flow path to the second fluid outflow path, and the first fluid pressure-transmitted from the second fluid flowing into the second flow path from the second fluid inflow path is While the operation of flowing out from the first flow path to the first fluid outflow path is continuously performed, the gap between the rotating body and the first and second side members, and between the rotating body and the holding member The first fluid or the second fluid enters the gap. If the gap is too narrow, a large sliding resistance is generated. If the gap is too wide, the amount of fluid leakage increases and the pressure exchanging efficiency decreases. Therefore, the gap is preferably set to about 1 to 100 μm.

  The first fluid or the second fluid that has entered the gap between the rotating body and the first side member presses the rotating body toward the second side member. The first fluid or the second fluid that has entered the gap between the rotating body and the second side member presses the rotating body toward the first side member. The fluid that has entered both gaps prevents the rotating body from rotating while always sliding with the first side member or the second side member. The first fluid or the second fluid that has entered the gap between the rotating body and the holding member prevents the rotating body from rotating while always sliding with the inner peripheral surface of the holding member.

  As described above, the rotating body smoothly rotates because sliding with the surrounding first and second side members and the holding member is reduced by the first fluid or the second fluid entering the gap. In addition, since wear can be reduced, durability can be improved without using expensive wear-resistant materials. Furthermore, it is necessary to rotationally drive the rotating body even when the rotating body is formed to have a large diameter to increase the processing flow rate and the cross-sectional areas of the first flow path and the second flow path constituting the pressure transmission unit are increased. Energy can be kept low.

  At this time, since the pressure balance adjusting mechanism adjusts the pressure balance of the pressure exchanging portion by the first fluid or the second fluid that has entered the gap, the first lateral member or the second side member is displaced in the axial direction of the rotating body. It is possible to prevent deformation of the side member and the holding member due to the fluid pressure. That is, since the first side member, the second side member, the holding member, and the rotating body are prevented from sliding with each other, the rotating body can be smoothly rotated to improve the efficiency.

  The first flow path, the second flow path, and the communication section of both flow paths constitute a pressure transmission section, and the first fluid or the second fluid is caused to flow into the pressure transmission section from one end side of the rotating body. A pressure transmission unit configured by a straight pipe as described in Patent Document 1 by exchanging pressure between the fluid and the second fluid and causing the first fluid or the second fluid to flow out from the one end side; In comparison, when the pressure exchange process with the same flow rate is performed, the length of the rotating body in the direction of the rotation axis can be shortened, so that the apparatus can be made compact and the cost can be reduced. Moreover, even when it is necessary to increase the flow rate of the pressure exchange process, the length of the rotating body in the direction of the rotation axis can be shortened, so that an extreme increase in size of the apparatus can be avoided.

  Furthermore, since the first fluid inflow channel and the outflow channel, the second fluid inflow channel and the outflow channel are formed only in the first side member, piping connected to the inflow channel or the outflow channel of each fluid is connected to the first side. Compared to the case where pipes connected to each inflow or outflow path are installed on both ends of the rotating body like conventional devices, the installation space including the pipes is compact. Furthermore, workability such as piping installation work and maintenance work is improved.

  In the second characteristic configuration, as described in the second aspect, in addition to the first characteristic configuration described above, the first side member is at least opposed to the rotating body in the first fluid inflow path. A first fluid inflow passage opening formed on the surface side so as to communicate with the plurality of first flow paths along the circumferential direction of the rotator, and a surface of the second fluid inflow path facing the rotator. A second fluid inflow passage opening formed so as to communicate with a plurality of second flow paths along a circumferential direction of the rotating body, and the pressure balance adjusting mechanism is configured to The first fluid inflow passage, the second fluid outflow passage, the second fluid inflow passage, and the first fluid outflow passage, which are formed in the member, are opposed to the respective opening portions of the rotating body facing each other. The pressure receiving area on the side facing the first side member is substantially the same as the pressure receiving area on the side facing the second side member of the rotating body. In that it includes a pressure receiving portion.

  When the first fluid is dispersed and flows into the plurality of first flow paths from the first fluid inflow path opening of the first fluid inflow path, the pressure of the first fluid is between the adjacent first flow paths of the rotating body. This also acts on the end surface of the first and second members and presses the rotating body toward the second side member. Similarly, when the second fluid is distributed and flows into the plurality of second flow paths from the second fluid inflow path opening of the second fluid inflow path, the pressure of the second fluid is changed to the first flow adjacent to the rotating body. It also acts on the end surfaces between the paths, and presses the rotating body toward the second side member.

  However, the pressure balance adjusting mechanism is configured so that the first fluid inflow path, the second fluid outflow path, the second fluid inflow path, and the first fluid outflow path formed in the first side member are opposed to the rotating body. The pressure-receiving area on the surface facing the first side member of the rotating body and the pressure-receiving area on the surface facing the second side member of the rotating body are substantially the same as each opening on the surface side. Therefore, the force for pressing the rotating body toward the second side member and the force for pressing the rotating body toward the first side member are balanced, and the rotating body is in the first lateral direction. It does not slide unilaterally on the member or the second side member, and can rotate smoothly.

  In the third feature configuration, as described in claim 3, in addition to the second feature configuration described above, the first side member is at least opposed to the rotating body in the first fluid inflow path. On the surface side, the first inclined portion formed to expand in diameter so as to communicate with the plurality of first flow paths along the circumferential direction of the rotating body, and the facing of the rotating body in the second fluid inflow path And a second inclined portion formed on the surface side so as to communicate with the plurality of second flow paths along the circumferential direction of the rotating body, and the inclined direction of the first inclined portion and the second The inclination direction of the inclined portion is set to be the same, and torque is applied to the rotating body by the energy of the first fluid flowing into the first flow path and the energy of the second fluid flowing into the second flow path. And the pressure balance adjusting mechanism includes a first fluid formed on the first side member. On the facing surface of the inlet, the second fluid outflow passage, the second fluid inflow passage, and the first fluid outflow passage on the surface facing the rotating body, and the surface of the second side member facing the rotating body It is in the point provided with the recessed part which makes the said each opening part and the same outline and area which oppose each said opening part formed.

  When the first fluid is dispersed and flows into the plurality of first flow paths from the first fluid inflow path, the first fluid flowing along the first inclined portion flows along the circumferential direction of the rotating body, Torque that acts on the wall surface of the flow path to rotate the rotating body is generated.

  When the second fluid is dispersed and flows into the plurality of second flow paths from the second fluid inflow path, the second fluid flowing along the second inclined portion flows along the circumferential direction of the rotating body, Torque is generated to press the wall surface of the flow path and rotate the rotating body.

  Since the inclination direction of the first inclined portion and the inclination direction of the second inclined portion are set to be the same, the rotational torque generated by the first fluid and the rotational torque generated by the second fluid are in the same direction.

  Since the rotating body can be rotated by at least the energy of the first fluid flowing into the first flow path and the energy of the second fluid flowing into the second flow path, no external power is required. As the rotating body rotates, the inflow and outflow of the first fluid to the pressure transmission unit and the outflow and inflow of the second fluid are switched, so that a separate channel switching mechanism is not required.

  Here, when the first fluid flows dispersedly into the plurality of first flow paths from the first fluid inflow path, the pressure of the first fluid also acts on the end surface between the adjacent first flow paths of the rotating body. Then, the rotating body is pressed toward the second side member. Similarly, when the second fluid is distributed and flows into the plurality of second flow paths from the second fluid inflow path, the pressure of the second fluid also acts on the end surface between the adjacent first flow paths of the rotating body. Then, the rotating body is pressed toward the second side member. However, the second side member has the first fluid inflow path, the second fluid outflow path, the second fluid inflow path, and the first fluid outflow path facing each opening on the facing surface side of the rotating body. Since the recesses having the same contour and area as each opening are formed, the first fluid and the second fluid also flow into each recess and act on the other end surface of the rotator to place the rotator on the first side. Since the pressing is performed toward the side member, the pressing force acting on both end faces of the rotating body is balanced and the pressing position is also symmetric, and the rotating body slides unilaterally on the first side member or the second side member. In such a case, the shaft of the rotating body is not inclined and does not slide with the holding portion, and can rotate smoothly.

  In the fourth feature configuration, as described in claim 4, in addition to any of the first to third feature configurations described above, a first end cover disposed outside the first side member. And a second end cover disposed outside the second side member, wherein the first end flow is communicated with at least the first fluid inflow path or the second fluid inflow path, respectively. An inlet or a second fluid inlet is formed, and the pressure balance adjusting mechanism includes a first closed space defined by at least the first side member and the first end cover, and the first fluid or the second fluid. A first communication path formed in the first end cover, and a second closed space defined by at least the second side member and the second end cover, Directing the first fluid or the second fluid to the second closed space; , In that it includes a second communication passage formed in the second side member.

  Since the first fluid or the second fluid has entered the gap between the rotating body and the first side member, the outward pressure acts on the first side member. However, at least in the first closed space defined by the first side member and the first end cover, the first fluid or the second fluid is passed through the first communication passage formed in the first end cover. Since the fluid is guided, the pressure in the direction of the rotating body acts on the first side member, and the pressing force acting on both surfaces of the first side member balances. Since a situation in which the pressure is distorted by the pressure is avoided, the gap between the rotating body and the first side member is kept constant, and the rotating body can be smoothly rotated to improve efficiency.

  Similarly, since the first fluid or the second fluid has entered the gap between the rotating body and the second side member, the outward pressure acts on the second side member. However, at least in the second closed space defined by the second side member and the second end cover, the first fluid or the second fluid is passed through the second communication passage formed in the second side member. Since the second fluid is guided to the second closed space, the pressure in the direction of the rotating body acts on the second side member, and the pressing force acting on both surfaces of the second side member is balanced. Since the situation in which the two side members are distorted in the direction of the rotation axis by the pressure of the fluid is avoided, the gap between the rotating body and the second side member is kept constant, and the rotating body can be rotated smoothly. The efficiency is improved.

  In addition to any of the first to fourth characteristic configurations described above, the fifth characteristic configuration includes a cylindrical casing that houses the holding portion, and the pressure balance as described in claim 5. The adjusting mechanism includes an outer peripheral closed space defined by the first and second side members, the outer peripheral surface of the holding member, and the inner peripheral surface of the casing, a gap between the rotating body and the holding member, and the outer peripheral closing. A third communication passage is formed in the holding member so as to communicate with the space.

  According to the above configuration, the gap between the rotating body and the first side member and the second side member enters the gap between the outer peripheral surface of the rotating body and the inner peripheral surface of the holding member. The fluid enters the outer peripheral closed space between the outer peripheral surface of the holding member and the inner peripheral surface of the casing via the third communication passage formed in the holding member.

  The pressure of the fluid guided to the outer peripheral closed space is substantially equal to the pressure of the fluid acting on the gap between the rotating body and the inner peripheral surface of the holding member, and the pressing force acting on both the inner peripheral surface and the outer peripheral surface of the holding member Therefore, even if the holding member is thinned, a situation in which it is distorted in the radial direction is avoided. Therefore, the gap between the rotating body and the holding member does not widen during operation, and the predetermined gap is held, so that it can rotate smoothly and efficiency is improved.

  In addition to the above-described fourth or fifth feature configuration, the sixth feature configuration is a support shaft supported at both ends by the first side member and the second side member, as described in claim 6. The rotating body is formed with an insertion space through which the support shaft is inserted along the direction of the rotation axis, and the first side member or the second side member has a first fluid or a fluid in the insertion space. A fourth communication path for guiding the second fluid is formed.

  According to the above-described configuration, the support shaft is inserted into the insertion space formed in the rotating body, and both ends are supported by the first side member and the second side member. The first fluid or the second fluid is introduced into the first closed space and the second closed space, and the pressure in the direction of the rotating body is also applied to the support portions of the support shafts of the first side member and the second side member, respectively. Is working. By guiding the first or second fluid to the insertion space via the fourth communication passage formed in the first side member or the second side member, the first side member and the second side member are guided. The support portion of the support shaft of the member is pressed in the outer direction of the first side member and the second side member, and the support portion of the support shaft of the first side member and the second side member is rotated on the support portion. By balancing with the pressure acting in the direction, there is no situation where the vicinity of the support portion of the support shaft of the first side member and the second side member is distorted along the rotation axis direction. Can be prevented from expanding and contracting in the axial direction.

  In the seventh feature configuration, as described in claim 7, in addition to any of the first to sixth feature configurations described above, the first fluid supplied to the first fluid inflow passage is reverse osmosis. A high-pressure concentrated fluid drained from the membrane device, wherein the second fluid supplied to the second fluid inflow path is a fluid to be concentrated supplied to the reverse osmosis membrane device.

  According to the above-described configuration, the fluid to be concentrated supplied to the reverse osmosis membrane device can be pressurized by the pressure of the high-pressure concentrated fluid drained from the reverse osmosis membrane device. It can be used as effective energy without throwing away excess pressure.

  As described above, according to the present invention, it is possible to provide an efficient pressure exchange device that can be made compact and cost-effective without reducing the processing flow rate.

Outline flow chart of seawater desalination facility Sectional drawing explaining a pressure exchange device It is explanatory drawing of a rotary body, Comprising: (a) is a front view, (b) is sectional drawing, (c) is a rear view. It is explanatory drawing of a 1st side member, (a) is a front view, (b) is a cross-sectional schematic diagram, (c) is a rear view. It is explanatory drawing of a 2nd side member, Comprising: (a) is a front view, (b) is a cross-sectional schematic diagram, (c) is a rear view. (A) is the sectional view on the AA line of the 1st fluid inflow passage shown in Drawing 4 (c), (b) is the BB sectional view on the 2nd fluid outflow passage shown in Drawing 4 (c), (c ) Is a cross-sectional view of the second fluid inflow passage shown in FIG. 4C, and FIG. 4D is a cross-sectional view of the first fluid outflow passage shown in FIG. Explanatory drawing which shows the position of each inflow path and each outflow path formed in each flow path formed in the rotating body and the first side member. Explanatory drawing of the rotary body by another embodiment (A) is explanatory drawing of the pressure exchange apparatus by another embodiment, (b) is explanatory drawing of the 2nd closed space by another embodiment. (A) is explanatory drawing of the pressure exchange apparatus by another embodiment, (b) is explanatory drawing of the 2nd closed space by another embodiment. Explanatory drawing of conventional pressure exchange device Explanatory drawing of conventional pressure exchange device

  Hereinafter, preferred embodiments of the pressure exchange device according to the present invention will be described.

  As shown in FIG. 1, the seawater desalination facility includes a pretreatment unit 1 that removes contaminants in seawater, a filtered seawater tank 2 that stores seawater pretreated by the pretreatment unit 1, and a filtered seawater tank 2. The supply pump 3 that supplies the stored seawater to the safety filter, the safety filter 4 that removes fine foreign matter in the seawater to prevent the reverse osmosis membrane device 6 from being clogged, and the seawater that has passed through the safety filter 4 is pressurized. A high-pressure pump 5 and a reverse osmosis membrane device 6 to which pressurized seawater is supplied are provided. Various salts in the seawater are removed by the reverse osmosis membrane device 6 and desalinated so that it can be used as drinking water or industrial water.

  The reverse osmosis membrane device 6 is a device that exudes fresh water from which various salts in seawater have been removed to the other side of the reverse osmosis membrane by applying pressure to the seawater on one side of the osmosis membrane. Needs to make seawater a predetermined pressure higher than the osmotic pressure.

  The reverse osmosis membrane device 6 cannot desalinate all of the supplied seawater. For example, 40% of the seawater supplied to the reverse osmosis membrane device 6 is desalinated and drained, but the remaining 60% is not desalinated and drained as high-pressure concentrated seawater with very high pressure.

  Therefore, a pressure exchange device 10 that recovers and uses surplus pressure of high-pressure concentrated seawater drained from the reverse osmosis membrane device 6 as effective energy is provided.

  40% of the seawater supplied from the filtered seawater tank 2 to the reverse osmosis membrane device 6 is boosted to a predetermined pressure higher than the osmotic pressure by the high-pressure pump 5, for example, 6.9 MPa. The remaining 60% of seawater (hereinafter referred to as “low pressure seawater”) supplied to the reverse osmosis membrane device 6 is the excess pressure (from the high pressure concentrated seawater drained from the reverse osmosis membrane device 6 by the pressure exchange device 10 ( 6.75 MPa) and the pressure is increased to 6.9 MPa by the booster pump 7.

  That is, the pressure exchanging device 10 boosts the low-pressure seawater Li that is the fluid to be concentrated by the pressure of the high-pressure concentrated seawater Hi drained from the reverse osmosis membrane device 6, and reverses it as the high-pressure seawater Ho via the booster pump 7. While supplying to the osmosis membrane apparatus 6, the pressure exchange process which drains the low pressure concentrated seawater Lo after the said pressure was collect | recovered with the low pressure seawater Li supplied to the pressure exchange apparatus 10 is performed.

  In this way, the pressure exchange device 10 uses the excess pressure of the high-pressure concentrated seawater Hi drained from the reverse osmosis membrane device 6 to increase the pressure of the low-pressure seawater Li supplied to the reverse osmosis membrane device 6 without throwing away the reverse pressure. Since a part of pressure required for the filtration by the osmosis membrane device 6 is compensated, the energy efficiency of the entire seawater desalination facility is improved.

  As shown in FIG. 2, the pressure exchanging device 10 is a rotating body that rotates around a support shaft 43 in a space defined by a first side member 20, a second side member 30, and a holding member 11. 40, a casing 13 having an inner circumferential cylindrical shape that accommodates the pressure exchanging portion, and a first end cover 14 that seals the casing end surface of the accommodated first side member 20 side. The second end cover 15 and the like for sealing the casing end face on the second side member 30 side accommodated are provided.

  The casing 13 is formed of a material having corrosion resistance to seawater and having a certain degree of strength, such as a resin material, FRP, or a metal material such as duplex stainless steel or super duplex stainless steel. A high-strength metal tube such as stainless steel may be coated with a resin material or ceramic to add corrosion resistance. Thereby, an inexpensive material with inferior corrosion resistance can be used, and the cost can be reduced.

  The first side member 20, the second side member 30, the rotating body 40, and the holding member 11 are corrosion resistant to seawater, such as ceramics such as alumina, FRP, or duplex stainless steel or super duplex stainless steel. Therefore, a sufficiently strong material can be used. When duplex stainless steel or super duplex stainless steel is used, the opposing surfaces of the rotating body 40 and the first side member 20 and the second side member 30 are nitrided, alumina or the like It is preferable to form a wear-resistant layer that is thermally sprayed, overlay welded, or HIP treated to reduce the coefficient of friction.

  Since there is a gap between each end face of the rotating body 40 and the first side member 20 and the second side member 30, and a gap between the outer periphery of the rotating body 40 and the holding member 11, each fluid enters the gap.

  If the gap is too narrow, the rotating body 40 and the first side member 20 or the second side member 30, and the rotating body 40 and the holding member 11 slide to provide resistance to rotation. For example, about 1 to 100 μm is preferable because the amount of leakage into the fluid is too large and the pressure exchange efficiency decreases.

  As shown in FIGS. 2 and 3 (a), 3 (b), and 3 (c), the low pressure after the high pressure concentrated seawater Hi flows into the rotating body 40 from the end face 40a on one end side and the pressure is exchanged. The first flow path 41 through which the concentrated seawater Lo flows out, and the second flow path 42 through which the high-pressure seawater Ho flows out after the low-pressure seawater Li flows in from the end face 40a on the one end side and the pressure is exchanged. Sixteen sets of pressure transmission parts formed so as to communicate with each other on the end face 40b side of the other end side of 40 are arranged radially around the rotation axis. In the present embodiment, the high-pressure concentrated seawater Hi and the low-pressure concentrated seawater Lo are the first fluid, and the low-pressure seawater Li and the high-pressure seawater Ho are the second fluid.

  Each first flow path 41 and each second flow path 42 are formed so as to penetrate in the direction of the rotation axis of the rotating body 40. Both end surfaces 40a and 40b of the rotating body 40 have substantially the same shape. Note that the cross-sectional area of the first flow path 41 and the cross-sectional area of the second flow path 42 are formed to be equal to each other, so that pressure loss is unlikely to occur.

  The rotating body 40 is formed with an insertion space 44 through which the support shaft 43 is inserted along the rotational axis direction. The insertion space 44 is formed sufficiently large with respect to the diameter of the support shaft 43, and the clearance between the outer periphery of the support shaft 43 and the inner periphery of the insertion space 44 is the rotating body 40, the first side member 20, and the second side. The gap is wider than the gap of the member 30.

  As shown in FIG. 2, both ends of the support shaft 43 are supported by the first side member 20 and the second side member 30. The support shaft 43 is fixed by being tightened with a double nut in a state in which male screws are cut at both ends and the male screw portions are inserted into openings formed in the first side member 20 and the second side member 30, respectively. . The support shaft 43 and the nut function as a pressing mechanism, and the distance between the central portions of the first side member 20 and the second side member 30 can be adjusted by adjusting the tightening of the nut.

  The clearance between the rotating body 40 and the first side member 20 and the clearance between the rotating body 40 and the second side member 30 are the tightening condition of the nut for attaching the support shaft 43 and the nut for attaching the second end cover 36 to the casing 11. It can be adjusted by changing the tightening degree of the spacer and the width of the spacer 35. Since the gap can be set at an appropriate interval and the amount of fluid entering the gap can be adjusted, it is possible to prevent a decrease in pressure exchange efficiency. In addition, the spacer can be made of an elastic member, and the thickness can be adjusted by changing the tightening of the bolt, or the adjustment range of the gap can be changed by changing the thickness and elastic force of the elastic member.

  As shown in FIGS. 2 and 4A, 4B, and 4C, the first side member 20 has a first fluid that guides the high-pressure concentrated seawater Hi to the first flow path 41 of the rotating body 40. The second fluid outflow passage 22 that guides the high-pressure seawater Ho pressure-exchanged between the inflow passage 21 and the high-pressure concentrated seawater Hi from the second flow path 42 and the second fluid outflow path 22 that guides the low-pressure seawater Li to the second flow path 42. A two-fluid inflow path 23 and a first fluid outflow path 24 that guides the low-pressure concentrated seawater Lo pressure-exchanged between the low-pressure seawater Li and the first flow path 41 are formed in the thickness direction.

  The first fluid inflow passage 21 is formed with an enlarged diameter so as to communicate with the plurality of first flow paths 41 along the circumferential direction of the rotating body 40 from the opening 21 a to the opening 21 b of the first side member 20. In addition, a flow path wall 21c as a first inclined portion is provided. The second fluid outflow passage 22 is formed with an enlarged diameter so as to communicate with the plurality of second flow paths 42 along the circumferential direction of the rotating body 40 from the opening 22 a to the opening 22 b of the first side member 20. In addition, a flow path wall 22c as a second inclined portion is provided. The second fluid inflow path 23 is formed with an enlarged diameter so as to communicate with the plurality of second flow paths 42 along the circumferential direction of the rotating body 40 from the opening 23 a to the opening 23 b of the first side member 20. Further, a flow path wall 23c as a second inclined portion is provided. The first fluid outflow passage 24 is formed with an enlarged diameter so as to communicate with the plurality of first flow paths 41 along the circumferential direction of the rotating body 40 from the opening 24 a to the opening 24 b of the first side member 20. In addition, a flow path wall 24c as a first inclined portion is provided.

  The inclination direction of the flow path wall 21c and the inclination direction of the flow path wall 23c are set in the same direction with respect to the circumferential direction (see FIGS. 6A and 6C). The inclination direction of the wall 22c is set to be opposite to the circumferential direction (see FIGS. 6A and 6B), and the inclination direction of the flow path wall 23c and the inclination direction of the flow path wall 24c are circumferential. It is set so as to be opposite to the direction (see FIGS. 6C and 6D), and each inflow path and outflow path constitute a torque applying mechanism.

  The first fluid inflow passage 21 is formed with an enlarged diameter so as to communicate with the plurality of first flow paths 41 along the circumferential direction of the rotating body 40 from the opening 20 a to the opening 21 b of the first side member 20. Therefore, the high-pressure concentrated seawater Hi is dispersed along the flow path wall 21 c and flows into the plurality of first flow paths 41.

  At this time, the high-pressure concentrated seawater Hi flows along the circumferential direction of the rotator 40 and applies a pressure to the wall surface of the first flow path 41, that is, generates torque that rotates the rotator 40.

  The second fluid outflow passage 22 is formed with an enlarged diameter so as to communicate with the plurality of second flow paths 42 along the circumferential direction of the rotating body 40 from the opening 22 a to the opening 22 b of the first side member 20. Therefore, the high-pressure seawater Ho flowing through the plurality of adjacent second flow paths 42 merges and flows out through the flow path wall 22c.

  At this time, the high-pressure seawater Ho applies pressure to the wall surface of the second flow path 42 in a direction that increases the cross-sectional area of the water flowing from the second flow path 42 to the second fluid outflow path 22, that is, rotates. A torque for rotating the body 40 is generated.

  Since the inclination direction of the flow path wall 21c and the inclination direction of the flow path wall 22c are set to be reversed, it occurs when the high-pressure concentrated seawater Hi flows into the first flow path 41 from the first fluid inflow path 21. And the torque generated when the high-pressure seawater Ho flows out from the second flow path 42 to the second fluid outlet path 22 are in the same direction.

  That is, since the torque for rotating the rotating body 40 is generated by the energy of the high-pressure concentrated seawater Hi flowing into the rotating body 40 and the high-pressure seawater Ho flowing out of the rotating body 40, the rotating body 40 is rotated only by any one of the energies. A larger torque can be generated than in the case.

  Similarly, the torque applied to the rotating body 40 by the energy when the low-pressure seawater Li flows into the second flow path 42 from the second fluid inflow path 23 and the low-pressure concentrated seawater Lo are transferred from the first flow path 41 to the first fluid. The torque applied to the rotating body 40 by the energy when flowing out to the outflow path 24 is also in the same direction.

  As described above, the torque application mechanism includes the energy of the high-pressure concentrated seawater Hi flowing into the first flow path 41, the energy of the high-pressure seawater Ho flowing out of the second flow path 42, and the low-pressure seawater flowing into the second flow path 42. Torque for rotating the rotating body 40 is generated by the energy of Li and the energy of the low-pressure concentrated seawater Lo flowing out from the first flow path 41.

  Therefore, external power for rotating the rotator 40 is not required. Further, since the inflow and outflow of the first fluid and the outflow and inflow of the second fluid are switched with the rotation of the rotating body 40, a separate flow path switching mechanism becomes unnecessary.

  The first side member 20 is formed with a fourth communication passage 18 that guides the high-pressure concentrated seawater Hi into the insertion space 44. The insertion space 44 and the fourth communication path 18 function as a pressure balance adjustment mechanism. In the present embodiment, the fourth communication path 18 is configured to guide the high-pressure concentrated seawater Hi flowing into the first closed space 16 through the first communication path 17 to the insertion space 44. However, the configuration may be such that the fourth communication path is formed in the second side member 30. Further, the high pressure seawater Ho may be guided to the insertion space 44 instead of the high pressure concentrated seawater Hi.

  The support shaft 43 is inserted into an insertion space 44 formed in the rotating body 40, and both ends are supported by the first side member 20 and the second side member 30. High-pressure concentrated seawater Hi and high-pressure seawater Ho are guided to the first closed space 16 and the second closed space 38, and also rotate to the support portions of the support shafts 43 of the first side member 20 and the second side member 30, respectively. Pressure toward the body 40 is acting.

  By guiding the high-pressure concentrated seawater Hi to the insertion space 44 via the fourth communication path 18 formed in the first side member 20, the support shaft 43 of the first side member 20 and the second side member 30 is supported. The support portion is pressed from the inside toward the outside of the first side member 20 and the second side member 30. The first side member 20 is balanced by balancing the force pressing in the outward direction with the pressure acting in the direction of the rotating body 40 on the support portion of the support shaft 43 of the first side member 20 and the second side member 30. In addition, since the situation in which the vicinity of the support portion of the support shaft 43 of the second side member 30 is distorted along the rotational axis direction is eliminated, expansion and contraction of the support shaft 43 in the axial direction can be prevented.

  As shown in FIG. 2, the first end cover 14 includes a first fluid inlet 25 that communicates with the first fluid inlet 21, a second fluid outlet 26 that communicates with the second fluid outlet 22, A second fluid inlet 27 that communicates with the two-fluid inlet 23 and a first fluid outlet 28 that communicates with the first fluid outlet 24 are formed and screwed to the casing 13 with bolts. A seal 19 is disposed in a circumferential direction on the contact surface of the first end cover 14 with the casing 13, and fluid is prevented from leaking outside the casing 13.

  Further, a concave portion is formed in the central portion of the first end cover 14 facing the first side member 20, and the first closed space 16 is constituted by the concave portion and the outer side surface of the first side member 20. The high-pressure concentrated seawater Hi flows into the first closed space 16 by the first communication passage 17 that communicates the first fluid inflow passage 21 and the first closed space 16. The first closed space 16 and the first communication path 17 constitute a pressure balance adjusting mechanism, and the pressure of the high-pressure concentrated seawater Hi flowing into the first closed space 16 from the first communication path 17 is caused by the first side member 20. It acts so as to press toward the rotating body 40.

  The force that presses the first side member 20 toward the rotating body 40 is balanced with the pressing force that the first or second fluid in the rotating body 40 acts on the first side member 20. Even if the side member is thinned, a situation in which it is distorted in the direction of the rotational axis due to the pressure of the fluid is avoided, the gap between the rotating body 40 and the first side member 20 is kept constant, and the rotating body can be smoothly rotated. It becomes possible.

  The second side member 30 is configured to support the holding member 11 and the support shaft 43 with the first side member 20.

  The second side member 30 has the same shape as the openings 21b, 22b, 23b, 24b at the positions facing the openings 21b, 22b, 23b, 24b of the first side member 20 (same as the same contour). Concave portions 31a, 32a, 33a, 34a having an opening of (area) are formed. The recesses 31a, 32a, 33a, 34a constitute a pressure balance adjusting mechanism. Here, the end surface 40b of the rotating body 40 facing the recesses 31a, 32a, 33a, 34a serves as a pressure receiving portion that presses the rotating body 40 against the first side member 20.

  When the high-pressure concentrated seawater Hi is dispersed and flows into the plurality of first flow paths 41 from the first fluid inflow path 21, the pressure of the high-pressure concentrated seawater Hi is an end surface between the adjacent first flow paths 41 of the rotating body 40. The pressure of the high-pressure seawater Ho acts on 40a, presses the rotating body 40 toward the second side member 30, and the high-pressure seawater Ho flows out from the plurality of second flow paths 42 to the second fluid outflow path 22. It acts on the end surface 40a between the adjacent 2nd flow paths 42 of the rotary body 40, and presses the rotary body 40 to the 2nd side member 30 side.

  Similarly, when the low-pressure seawater Li is dispersed and flows from the second fluid inflow path 23 into the plurality of second flow paths 42, the pressure of the low-pressure seawater Li is between the adjacent second flow paths 42 of the rotating body 40. The pressure of the high-pressure seawater Ho rotates when acting on the end surface 40a, pressing the rotating body against the second side member, and the low-pressure concentrated seawater Lo flows out from the plurality of first flow paths 41 to the first fluid outflow path 24. It acts on the end surface 40a between the adjacent 1st flow paths 41 of the body 40, and presses the rotary body 40 to the 2nd side member 30 side.

  Thus, since the fluid flowing into and out of the first flow path 41 and the second flow path acts on the end surface 40a, the force that is pressed toward the second side member 30 side acts on the rotating body 40. The first fluid and the second fluid also flow into the recesses 31a, 32a, 33a, and 34a formed in the second side member, and act on the end surface 40b of the rotator 40 so that the rotator 40 is moved to the first side. Since the pressing is performed toward the member 20 side, the pressing forces acting on the both end faces 40a and 40b are balanced and the distribution of the pressing force is also equal, and the rotating body 40 is unilaterally applied to the first side member 20 or the second side member 30. It will not slide and can rotate smoothly.

  That is, since each opening part 21b-24b and recessed part 31a-34a are in the same shape and a position which opposes, when the fluid flows in, the pressure receiving area which acts on the end surface 40a of the rotary body 40 is the pressure receiving part of the end surface 40b. In addition, the place where pressure is applied is also opposed in the axial direction, and the rotating body is not displaced in the axial direction.

  A sealing plate 36 is disposed outside the second side member 30 via a spacer 35. The sealing plate 36 is provided with a seal 37 around it. The second end cover 15 is screwed to the casing 13 with bolts so as to press the sealing plate 36 toward the second side member 30, and the second side member 30, the casing 13, and the sealing plate 36 are connected to each other. A second closed space 38 is defined by the second end cover 15 to be pressed.

  The spacer 35 is configured to maintain the distance between the second side member 30 and the sealing plate 36 at a distance defined by the thickness of the spacer 35.

  Note that a second communication passage 39 that guides the fluid in the pressure transmission portion to the second closed space 38 is formed in the recess 31 a of the second side member 30 in the thickness direction. The second closed space 38 and the second communication passage 39 constitute a pressure balance adjustment mechanism.

  The fluid in the pressure transmission part flows into the second closed space 38 via the second communication path 39, and the pressure in the pressure transmission part is transmitted to the second closed space 38 via the second communication path 39, It acts to press the side member 30 toward the rotating body 40.

  Since the high-pressure concentrated seawater Hi and the high-pressure seawater Ho in the rotating body 40 balance with the pressing force acting on the second side member 30, the second side member is distorted in the direction of the rotation axis by the fluid pressure even if the second side member is thinned. Such a situation is avoided, the gap between the rotating body 40 and the second side member 30 is kept constant, and the rotating body can be smoothly rotated.

  As described above, the first lateral member 20 and the second lateral member 30 are pressurized outward in the axial direction by the fluid in the rotating body 40, but as described above, the first lateral member 20 The high-pressure concentrated seawater Hi supplied to the first fluid inflow passage 21 through the first communication passage 17 is guided to the first closed space 16 on the outer side of the second side member 30, and the second communication passage 39 is provided outside the second side member 30. Thus, a second closed space 38 to which the fluid in the first channel 41 and the second channel 42 is guided is formed.

  That is, pressure is transmitted from the fluid having the same pressure to the first closed space 16 and the second closed space 38. Since the forces acting on both surfaces of the first side member 20 and the second side member 30 are balanced, the first side member 20 and the second side member 30 are respectively in the direction of the rotation axis of the rotating body 40. Distortion can be prevented, and useless stress is not applied to the support shaft 43.

  The spacer 35 has a thickness such that the sealing plate 36 slightly protrudes from the end surface of the casing 13. By changing the thickness of the spacer 35, the pressing force of the second side member 30 in the direction of the rotating body 40 is changed, so that it is formed between the both end faces 40a, 40b of the rotating body 40 and the side members 20, 30. The gap can be adjusted.

  In addition, if the opening part which connects the inner peripheral surface and outer peripheral surface of the spacer 35 is formed in the spacer 35, and it is comprised so that the fluid of the 2nd closed space 38 may be guide | induced to the outer peripheral side of the spacer 35, the spacer 35 will be There is no distortion in the radial direction due to the pressure of the fluid.

  Further, not only on the second side member 30 side but also on the first side member 20 side, the same spacer and sealing plate are provided, and by changing the width of the spacer in the rotation axis direction, or both spacers By changing the width in the direction of the rotational axis, the gaps formed between the both end faces 40a, 40b of the rotating body 40 and the side members 20, 30 may be adjustable.

  The holding member 11 is configured by a cylindrical member having an inner peripheral diameter slightly larger than the diameter of the rotating body 40 and slightly longer than the length of the rotating body 40 in the rotation axis direction. A third communication passage 45 is formed through the peripheral surface of the holding member 11, and the high-pressure concentrated seawater Hi or the high-pressure seawater Lo that has entered the gap between the rotating body 40 and the holding member 11 is held via the third communication passage 45. It is configured to flow into the outer peripheral closed space 46 defined by the outer peripheral surface of the member 11 and the inner peripheral surface of the casing 13. The third communication passage 45 and the outer peripheral closed space 46 constitute a pressure balance adjustment mechanism.

  Note that the holding member 11 can be configured by a plurality of holding members divided in the axial direction or the circumferential direction, and a gap is provided in the divided portion, and the gap can be used as the third communication path 45. is there.

  The fluid that has entered the gap between the outer circumferential surface of the rotating body 40 and the inner circumferential surface of the holding member 11 through the gap between the rotating body 40 and the first side member 20 and the second side member 30 is held by the holding member 11. The outer peripheral closed space 46 between the outer peripheral surface of the holding member 11 and the inner peripheral surface of the casing 13 enters through the third communication passage 45 formed in the above.

  The pressure of the fluid guided to the outer peripheral closed space 46 is substantially equal to the pressure of the fluid acting on the gap between the rotating body 40 and the inner peripheral surface of the holding member 11, and is applied to both the inner peripheral surface and the outer peripheral surface of the holding member 11. Since the applied pressing force is balanced, a situation in which the holding member 11 is distorted in the radial direction even when the holding member 11 is thinned is avoided. Therefore, the gap between the rotating body 40 and the holding member 11 does not widen during operation, and the predetermined gap is held, so that it can rotate smoothly.

  The specific pressure exchange processing operation of the pressure exchange device 10 configured as described above will be described.

  As shown in FIG. 7, the rotating body 40 has 16 sets of pressure transmission portions 44, that is, first flow paths 41a to 41p and second flow paths 42a to 42p arranged radially around the rotation axis. Yes. The areas indicated by the two-dot chain line in FIG. 7 are the opening 21 b of the first fluid inflow path 21, the opening 22 b of the second fluid outflow path 22, and the second fluid inflow path 23 of the first side member 20. The area | region corresponding to the opening part 23b and the opening part 24b of the 1st fluid outflow path 24 is represented.

  Six adjacent first flow paths 41c, 41b, 41a, 41p, 41o, 41n communicate with the first fluid inflow path 21 at the same time, and the first flow paths 41c, 41b communicate with the second fluid outflow path 22. , 41a, 41p, 41o, 41n and the second flow paths 42c, 42b, 42a, 42p, 42o, 42n communicating with each other in the rotating body 40 are simultaneously communicated. Six adjacent second flow paths 42f, 42g, 42h, 42i, 42j, and 42k are simultaneously communicated with the second fluid inflow path 23, and the second flow paths 42f, 42g are connected to the first fluid outflow path 24. , 42h, 42i, 42j, and 42k communicate with the first flow paths 41f, 41g, 41h, 41i, 41j, and 41k that communicate with each other in the rotating body 40.

  When the high-pressure concentrated seawater Hi that has flowed into the first fluid inflow path 21 is dispersed and flows into each of the first flow paths 41c, 41b, 41a, 41p, 41o, and 41n, the high-pressure concentrated seawater Hi The rotating torque is applied to the rotating body 40 as indicated by the one-dot chain line arrow in FIG.

  The pressure of the high-pressure concentrated seawater Hi that has flowed into the first flow paths 41c, 41b, 41a, 41p, 41o, and 41n is that of the second flow paths 42c, 42b, 42a, 42p, 42o, and 42n that communicate with each other in the rotating body 40. The high pressure seawater Ho is transmitted to the seawater, and flows out from the second flow paths 42c, 42b, 42a, 42p, 42o, 42n to the second fluid outflow path 22.

  When the high-pressure seawater Ho flows out from the second flow paths 42c, 42b, 42a, 42p, 42o, 42n to the second fluid outflow path 22, it flows along the flow path wall 22c so as to widen the flow. A clockwise torque is applied to 40 as indicated by a dashed line arrow in FIG.

  When the low-pressure seawater Li that has flowed into the second fluid inflow path 23 is dispersed and flows into each of the second flow paths 42f, 42g, 42h, 42i, 42j, and 42k, the low-pressure seawater Li enters the flow path wall 23c. A clockwise torque is applied to the rotator 40 as indicated by a dashed line arrow in FIG.

  The pressure of the low-pressure seawater Li that has flowed into the second flow paths 42f, 42g, 42h, 42i, 42j, and 42k is concentrated in the first flow paths 41f, 41g, 41h, 41i, 41j, and 41k that communicate with each other in the rotating body 40. The low-pressure concentrated seawater Lo is transmitted to the seawater, and flows out from the first flow paths 41f, 41g, 41h, 41i, 41j, 41k to the first fluid outflow path 24.

  When the low-pressure concentrated seawater Lo flows out from the first flow paths 41f, 41g, 41h, 41i, 41j, 41k to the first fluid outflow path 24, it flows along the flow path wall 24c so as to widen the flow and rotates. A clockwise torque is applied to the body 40 as indicated by a dashed line arrow in FIG.

  As described above, the torque applied to the rotating body 40 by the high-pressure concentrated seawater Hi flowing into the first flow path 41 from the first fluid inflow path 21, and the low-pressure seawater flowing out from the second flow path 42 to the second fluid outflow path 22. The torque that Lo gives to the rotating body 40, the torque that the low-pressure seawater Li flowing into the second flow path 42 from the second fluid inflow path 23 gives to the rotating body 40, and the first flow path 41 to the first fluid outflow path 24 The torque applied to the rotating body 40 by the low-pressure concentrated seawater Lo flowing out is in the same direction, and in this embodiment, the rotating body 40 rotates clockwise.

  Thus, by the rotation of the rotating body 40, the first fluid inflow path 21 and the second fluid outflow path 22, which communicate with the set of the first flow path 41 and the second flow path 42 constituting a certain pressure transmission unit, The second fluid inflow path 23 and the first fluid outflow path 24 are switched, and the transmission of pressure from the high-pressure concentrated seawater Hi to the high-pressure seawater Ho and the transmission of pressure from the low-pressure seawater Li to the low-pressure concentrated seawater Lo are continuously performed. In other words, the pressure exchange process between the first fluid and the second fluid is continuously performed.

  In the first flow path 41 and the second flow path 42, concentrated seawater and seawater are mixed. However, since each fluid has a difference in salt concentration, a certain amount of the boundary portion is always mixed by diffusion. The region only swings within the first flow path 41 and the second flow path 42 while acting like a piston.

  As shown in FIG. 7, first flow paths 41d, 41e, 41l that do not communicate with any of the first fluid inflow path 21, the second fluid outflow path 22, the second fluid inflow path 23, and the first fluid outflow path 24, 41m and the second flow paths 42d, 42e, 42l, and 42m do not exchange pressure.

  In the present embodiment, the first fluid inflow passage 21, the second fluid outflow passage 22, the second fluid inflow passage 23, and the first fluid outflow passage 24 are provided with the first flow path and the second flow path as the rotating body rotates. However, the number of communication at the same time is not limited to this. Note that if the number of lines communicating at the same time is small and the number of lines not communicating with any of them is large, the pulsation of water drained from the apparatus increases. Moreover, if the number of fluids that do not communicate with either the fluid inflow path or the fluid outflow path is small, the amount of leakage from the high pressure fluid to the low pressure fluid increases.

  The rotating body 40 is configured to rotate by the energy of the high-pressure concentrated seawater Hi and the low-pressure seawater Li flowing into the rotating body 40 and the high-pressure seawater Ho and the low-pressure concentrated seawater Lo flowing out of the rotating body 40. A larger torque can be applied than when rotating only with the energy of each fluid.

  When the shape of the flow path walls 21c, 22c, 23c, 24c changes, the direction of the flow of the fluid flowing into each flow path from the inflow path and the flow of the fluid flowing out from each flow path to the outflow path changes, and is added to the rotating body. Since the torque changes, the rotational speed of the rotating body changes. That is, the rotation speed of the rotating body 40 depends on the shape of the flow path walls 21c, 22c, 23c, and 24c. Since the processing flow rate of the pressure exchange device depends on the number of rotations of the rotator 40, the processing flow rate of the pressure exchange device can be easily adjusted by changing the shape and adjusting the number of rotations of the rotator 40. For example, the processing flow rate can be easily adjusted by preparing and replacing first side members having different shapes.

  As described above, the first side member 20 is formed with the first fluid inflow path 21, the first fluid outflow path 24, the second fluid inflow path 23, and the second fluid outflow path 22, and one end side of the rotating body 40. The first fluid or the second fluid is caused to flow into the pressure transmission unit from the pressure, the pressures of the first fluid and the second fluid are exchanged in the rotating body 40, and the second fluid or the first fluid is caused to flow out from the one end side. Because of the configuration, when performing pressure exchange processing at the same flow rate, the rotating body is used when performing pressure exchange processing at the same flow rate as compared to a pressure transmission unit configured with a straight pipe as in a conventional pressure exchange device. The length in the direction of the rotation axis of the rotating body can be shortened, making it possible to reduce the size and cost of the device, and even when the flow rate of the pressure exchange process needs to be increased, Extremely large equipment can be avoided by shortening the length.

  Furthermore, since the first fluid inflow channel and the outflow channel, the second fluid inflow channel and the outflow channel are formed only in the first side member 20, piping connected to the inflow channel or the outflow channel of each fluid is connected to the first side. The pipe installation work and maintenance may be performed as compared with the case where pipes connected to the fluid inflow path or the outflow path are respectively installed at both ends of the rotating body as in the conventional apparatus. Workability such as work is improved. That is, the installation space including the piping is reduced because the piping is gathered on the first side member 20 side. Further, maintenance can be performed from the second side member 30 side without piping without removing the piping, thereby improving maintainability.

  In the above-described embodiment, the first flow channel 41 and the second flow channel 42 are formed so that the cross-sectional area thereof is equal, so that excessive pressure loss due to the change of the flow channel cross-sectional area can be reduced. However, the cross-sectional areas of the first flow path 41 and the second flow path 42 need not be completely equal.

  In the above-described embodiment, the first flow path 41 and the second flow path 42 are configured to communicate with each other on the end face 40b side on the other end side of the rotating body 40, but as shown in FIG. It may be configured to communicate with the end face 40a side at a position separated by a predetermined distance. That is, the communicating portion may be an arbitrary position between the end surface 40a and the end surface 40b. Since the end surface 40a and the end surface 40b of the rotating body 40 have the same shape and the same area, the pressure balance in the axial direction of the rotating body 40 is good.

  Further, as shown in FIG. 8 (b), the end face 40b side of the rotating body 40 of the first flow path 41 and the second flow path 42 is configured to be closed except for some openings 40c and 40d. May be.

  The cross-sectional shape of the first flow path 41 and the second flow path 42 may be a circular shape such as a perfect circle or an ellipse, or a polygonal shape such as a triangle or a square. By changing the number and the cross-sectional shape, the total capacity of the pressure transmission unit 44 can be changed and the processing flow rate of the pressure exchange device 10 can be changed. In addition, the cross-sectional shape of the 1st flow path 41 and the 2nd flow path 42 shown to Fig.3 (a) is preferable at the point which can take a large aperture ratio with respect to the cross section of a rotary body.

  In the above-described embodiment, the holding member 11 and the second side member 30 are configured separately. However, the holding member 11 and the second side member 30 are integrally formed in a cup shape and closed by the first side member 20. You may comprise so that the rotary body 40 may be arrange | positioned in the space formed.

  In the above-described embodiment, a pair of each inflow path and outflow path, such as the first fluid inflow path 21, the second fluid outflow path 22, the second fluid inflow path 23, and the first fluid outflow path 24, that is, respectively. Although one structure is provided in total, four inflow paths and two outflow paths may be provided. In the case where a plurality of fluids are provided, the inflow passages and the outflow passages are preferably arranged symmetrically around the rotation axis from the viewpoint of the pressure balance between the fluids flowing into and out of the rotation body 40.

  In the above-described embodiment, the torque applying mechanism flows into the first flow path 41 or the energy of the concentrated seawater that flows out from the first flow path 41 and the second flow path 42, or the second The torque is applied to the rotator 40 by the energy of the seawater flowing out from the flow path 42, but the torque applying mechanism flows into the first flow path 41 at least from the concentrated seawater flowing out from the first flow path 41. What is necessary is just to comprise so that a torque may be provided to the rotary body 40 with energy or the energy of the seawater which flows in into the 2nd flow path 42, and flows out of the 2nd flow path 42. FIG.

  When only one of the energies is used, the first flow path 41 is arranged on the outer side in the radial direction of the rotating body 40 than the second flow path 42, so the high-pressure concentrated seawater Hi that flows into the first flow path 41 is used. Energy efficiency is good when it is configured to apply torque to the rotating body 40 using the energy of the above.

  In the above-described embodiment, the configuration in which the rotating body 40 rotates by the energy of the first fluid and the second fluid has been described. However, the driving shaft is connected to the rotating body 40 and is rotated by external power such as a driving machine. May be. Since the rotating body 40 can be rotationally driven by external power, stable rotation can be obtained, and the reliability of the apparatus is improved.

  In the above-described embodiment, the second end cover and the holding member have been described separately, but the second end cover and the holding member may be configured integrally.

  In the above-described embodiment, the holding member and the casing have been described separately. However, the holding member may function as a casing without including the casing. However, in this case, the pressure balance adjusting mechanism for the inner periphery and the outer periphery of the holding member is not provided.

  In the above-described embodiment, the second closed space has been described as one space. However, the spacer 35 includes a partition wall 38c that partitions the second closed space 38. For example, as illustrated in FIGS. 9A and 9B. As described above, the space 38a into which the high-pressure fluid flows and the space 38b into which the low-pressure fluid flows are divided into two spaces. The high pressure fluid flows into the space 38a from the communication passage 39a, and the communication passage 39b into the space 38b. The low-pressure fluid may be configured to flow in.

  Furthermore, for example, as shown in FIG. 10B, the first fluid inflow path 21, the second fluid outflow path 22, the second fluid inflow path 23, and the first fluid outflow path formed in the first side member 20. 24 are divided into four spaces (two spaces 38a into which high-pressure fluid flows in and two spaces 38b into which low-pressure fluid flows in) at positions corresponding to 24 so that the corresponding fluid flows into the respective spaces. It may be configured. Thus, by dividing the second closed space into a plurality of spaces, the pressing force acting on both surfaces of the second side member can be equalized, so that the deformation of the second side member is further suppressed. The

  In the above-described embodiment, the spacer 35 and the second end cover 36 have been described separately. However, as shown in FIG. 10A, the spacer 35 and the second end cover 36 are integrally configured to form the second side. A second closed space may be formed between the member 30 and the member 30.

  In any of the embodiments described above, the configuration in which the high-pressure concentrated seawater is introduced into the first fluid inflow passage and the low-pressure seawater that is the concentrated fluid is introduced into the second fluid inflow passage has been described. Low-pressure seawater that is a concentrated fluid may be flowed in, and high-pressure concentrated seawater may be flowed into the second fluid inflow path.

  The specific configuration of the pressure exchanging device described above is not limited to the description of the embodiment, and it is needless to say that the design can be appropriately changed within the scope of the effects of the present invention.

6: Reverse osmosis membrane device 10: Pressure exchange device 11: Holding member 13: Casing 14: First end cover 15: Second end cover 16: First closed space 17: First communication passage 18: Fourth communication passage 20: First side member 21: first fluid inflow path 21a: opening 21b: opening 21c: flow path wall 22: second fluid outflow path 22a: opening 22b: opening 22c: flow path wall 23: second fluid Inflow path 23a: Opening 23b: Opening 23c: Channel wall 24: First fluid outflow path 24a: Opening 24b: Opening 24c: Channel wall 30: Second side members 31a, 32a, 33a, 34a: Recess 35: Spacer 36: Sealing plate 37: Seal 38: Second closed space 39: Second communication path 40: Rotating body 41: First flow path 42: Second flow path 43: Support shaft 44: Insertion space 45: Third communication path 46: outer peripheral closed space Hi: high-pressure concentrated seawater (concentration Body)
Li: Low-pressure seawater (concentrated fluid)
Ho: High-pressure seawater (concentrated fluid)
Lo: Low-pressure concentrated seawater (concentrated fluid)

Claims (7)

  1. A pressure exchange device for exchanging pressure between a first fluid and a second fluid,
    A pressure transmission part formed so that the first flow path through which the first fluid flows in and out from one end side and the second flow path through which the second fluid flows in and out from the one end side communicates with each other around the rotation axis A rotating body arranged in
    A first fluid inflow path for guiding the first fluid to the first flow path; a second fluid outflow path for guiding the second fluid pressure-exchanged with the first fluid from the second flow path; A second fluid inflow path for guiding two fluids to the second flow path, and a first fluid outflow path for guiding the first fluid pressure-exchanged with the second fluid from the first flow path have a thickness. A first lateral member formed in a direction;
    A pressure exchanging portion configured by a second side member that rotatably holds the rotating body with a first side member via a holding member;
    The first channel and the second channel are formed so as to penetrate the rotating body,
    A pressure exchanging device comprising a pressure balance adjusting mechanism for adjusting the pressure balance of the pressure exchanging section by the first fluid or the second fluid.
  2. The first side member is formed at least on the surface facing the rotating body in the first fluid inflow path so as to communicate with the plurality of first flow paths along the circumferential direction of the rotating body. A first fluid inflow passage opening and a second fluid inflow passage formed on the opposite surface side of the rotary body so as to communicate with a plurality of second flow paths along the circumferential direction of the rotary body. Two fluid inlet passage openings,
    The pressure balance adjusting mechanism is configured such that the first fluid inflow path, the second fluid outflow path, the second fluid inflow path, and the first fluid outflow path, which are formed in the first side member, face the rotating body. The pressure receiving area of the rotating body facing the first side member of the rotating body and the pressure receiving area of the rotating body facing the second side member of the rotating body are substantially the same. The pressure exchange device according to claim 1, further comprising a pressure receiving portion.
  3. The first side member is expanded in diameter so as to communicate with a plurality of first flow paths along a circumferential direction of the rotating body at least on a surface facing the rotating body in the first fluid inflow passage. The diameter of the first inclined part formed on the opposite side of the second fluid inflow path to the rotating body is increased so as to communicate with the plurality of second flow paths along the circumferential direction of the rotating body. A second inclined portion formed by
    The inclination direction of the first inclined part and the inclination direction of the second inclined part are set to be the same,
    A torque applying mechanism that applies torque to the rotating body by energy of the first fluid flowing into the first flow path and energy of the second fluid flowing into the second flow path;
    The pressure balance adjusting mechanism is
    Each opening of the first fluid inflow path, the second fluid outflow path, the second fluid inflow path, and the first fluid outflow path facing the rotating body formed in the first side member;
    3. The pressure exchange according to claim 2, further comprising: a concave portion formed on a surface of the second side member facing the rotating body and having the same contour and area as each of the openings facing each of the openings. apparatus.
  4. A first end cover disposed outside the first side member; and a second end cover disposed outside the second side member;
    The first end cover is formed with a first fluid inlet or a second fluid inlet that communicates with at least the first fluid inlet or the second fluid inlet, respectively.
    The pressure balance adjusting mechanism is
    A first closed space defined by at least the first side member and the first end cover;
    A first communication path formed in the first end cover so as to guide the first fluid or the second fluid to the first closed space;
    A second closed space defined by at least the second side member and the second end cover;
    A second communication path formed in the second side member so as to guide the first fluid or the second fluid to the second closed space;
    The pressure exchange device according to any one of claims 1 to 3, further comprising:
  5. A cylindrical casing for accommodating the holding portion;
    The pressure balance adjusting mechanism is
    An outer peripheral closed space defined by the first and second side members, the outer peripheral surface of the holding member, and the inner peripheral surface of the casing;
    5. The pressure exchanging apparatus according to claim 1, further comprising a third communication passage formed in the holding member so as to communicate the clearance between the rotating body and the holding member and the outer peripheral closed space. .
  6. A support shaft supported at both ends by the first side member and the second side member;
    The rotating body is formed with an insertion space through which the support shaft is inserted along the rotation axis direction.
    The pressure exchange device according to claim 4 or 5, wherein a fourth communication passage for guiding the first fluid or the second fluid to the insertion space is formed in the first side member or the second side member.
  7.   The first fluid supplied to the first fluid inflow passage is a high-pressure concentrated fluid drained from the reverse osmosis membrane device, and the second fluid supplied to the second fluid inflow passage is supplied to the reverse osmosis membrane device. The pressure exchange device according to claim 1, wherein the fluid is a fluid to be concentrated.
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Publication number Priority date Publication date Assignee Title
WO2014163018A1 (en) * 2013-04-03 2014-10-09 株式会社 荏原製作所 Seawater desalination system and energy recovery apparatus
WO2014163019A1 (en) * 2013-04-05 2014-10-09 株式会社 荏原製作所 Seawater desalination system and energy recovery apparatus
CN107152422A (en) * 2017-06-01 2017-09-12 西安交通大学 A kind of residual pressure recovering equipment with Integral rotary valve plate

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US6537035B2 (en) * 2001-04-10 2003-03-25 Scott Shumway Pressure exchange apparatus
US7815421B2 (en) * 2004-08-07 2010-10-19 Ksb Aktiengesellschaft Channel form for a rotating pressure exchanger

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Publication number Priority date Publication date Assignee Title
US10019A (en) * 1853-09-13 Improvement in the manufacture of plain and figured fabrics
US6537035B2 (en) * 2001-04-10 2003-03-25 Scott Shumway Pressure exchange apparatus
US7815421B2 (en) * 2004-08-07 2010-10-19 Ksb Aktiengesellschaft Channel form for a rotating pressure exchanger

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014163018A1 (en) * 2013-04-03 2014-10-09 株式会社 荏原製作所 Seawater desalination system and energy recovery apparatus
US10207224B2 (en) 2013-04-03 2019-02-19 Ebara Corporation Seawater desalination system and energy recovery apparatus
CN105073231A (en) * 2013-04-03 2015-11-18 株式会社荏原制作所 Seawater desalination system and energy recovery apparatus
JPWO2014163018A1 (en) * 2013-04-03 2017-02-16 株式会社荏原製作所 Seawater desalination system and energy recovery device
JPWO2014163019A1 (en) * 2013-04-05 2017-02-16 株式会社荏原製作所 Seawater desalination system and energy recovery device
US10065152B2 (en) 2013-04-05 2018-09-04 Ebara Corporation Seawater desalination system and energy recovery apparatus
WO2014163019A1 (en) * 2013-04-05 2014-10-09 株式会社 荏原製作所 Seawater desalination system and energy recovery apparatus
CN107152422A (en) * 2017-06-01 2017-09-12 西安交通大学 A kind of residual pressure recovering equipment with Integral rotary valve plate

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