JP2009058203A - Heat exchange device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchange device with heat exchange flow paths formed of flat plates and swollen parts, having improved heat exchanging performance by suppressing a three-dimensional flow in the heat exchange flow paths. <P>SOLUTION: The heat exchange device comprises the first heat exchange flow paths formed with the flat plates arranged at predetermined intervals, the second heat exchange flow paths formed with the first heat exchange flow paths arranged at predetermined intervals, and the swollen parts connected to the ends of the first heat exchange flow paths. A with E of the swollen part is E=(A+B)×(sinβ/sinα)-B, where A is a space between the first heat exchange flow paths, B is a space between the second heat exchange flow paths, and α (0<α≤π/2) and β (α<β<π-α) are the angles of boundary lines between each the first heat exchange flow path and the second heat exchange flow path and the swollen part to the first heat exchange flow path and to the second heat exchange flow path, respectively. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention is a counter flow type heat exchange in which two fluids having different temperatures are circulated through independent fluid passages and heat is transferred from one fluid to the other fluid through a heat transfer surface of a plate constituting the fluid passages. Related to the vessel.

  A heat exchange device that heats a high-temperature fluid and a low-temperature fluid in thermal contact with each other through a heat conductor and applies heat from a high-temperature fluid to a low-temperature fluid is a boiler for a thermal power generation, a distillation device, a chemical reaction device, Widely used in technical fields such as manufacturing equipment. In addition, an apparatus that recovers and uses heat from a discarded high-temperature fluid is used for effective use of energy or improvement of thermal efficiency. Furthermore, the heat exchange device is also used when cooling a high temperature fluid with a low temperature fluid.

  An example of an application field in which a heat exchange device can be effectively applied is a regeneration cycle gas turbine. By exchanging heat between the turbine exhaust and the compressed intake air, the heat energy remaining in the exhaust can be recovered and the compressed intake air prior to combustion can be heated to save fuel and gas As the turbine compression ratio is lowered, the theoretical thermal efficiency with the Carnot cycle efficiency as the limit value can be expected, so the application of the heat exchange device is beneficial.

  Although the structure of the heat exchange device varies depending on the purpose of use, in order to increase the efficiency of heat exchange, it is necessary to increase the heat transfer area on the high heat side and the low heat side. Conventionally, an invention has been made in which a fluid passage for heat exchange is divided into a plurality of parts (for example, see Patent Document 1).

  However, even though it is convenient for heat exchange between a plurality of different liquids, it is structurally required to have an end plate and fluid is supplied and discharged by a pipe. I could not say it. A heat exchange apparatus capable of exchanging a large amount of exhaust gas and a large amount of compressed air from a compressor with a small pressure loss at a high temperature of the gas turbine has not reached satisfactory performance.

  On the other hand, in a heat exchange device, there is a heat exchange device that performs heat exchange using a cross flow in which two fluids flow orthogonally (for example, see Patent Document 2) or a parallel flow in which two fluids flow in the same direction in parallel. However, heat exchange devices used in heat engines and the like often have two fluids in the form of gas, and require a large fluid contact area for heat exchange, and are generally imposed on heat engines. From the viewpoint of general thermal requirements, counter flow type heat exchange devices are desirable for almost all heat exchange.

  For this reason, some have been devised to realize counterflow (see Patent Document 3). According to Patent Document 3, a fluid introduction enormous part and a fluid exhaust enormous part are formed at both ends of a flat flow path formed in a spiral shape so as to maintain a small interval, and fluid is discharged from the introduction enormous part. The fluid is passed through the flat channel in the process of passing through the enormous volume. A plurality of such flat channels are used, and a counter flow is realized by opposing the direction in which the first fluid flows in the flat channel and the direction in which the second fluid flows in the flat channel.

Japanese Patent Publication 1-14515 JP-A-2005-282904 JP 2002-350073 A

  However, in the heat exchange device of Patent Document 3, the flow of the two fluids flowing from the enormous portion into the flat flow path is a flow close to the counterflow, but a three-dimensional flow such as an oblique flow different from the counterflow Was found to occur. When a three-dimensional flow is generated in the fluid in the flat flow path, the heat exchange performance may be deteriorated because it is separated from the counter flow. For this reason, in order to further improve the heat exchange performance, it is necessary to suppress the generation of a three-dimensional flow and bring it closer to an ideal counter flow.

  Accordingly, an object of the present invention is to reduce the heat of the heat exchange device by suppressing the three-dimensional flow in the heat exchange channel in the heat exchange device having a heat exchange channel and a huge portion made of a flat plate. It is to improve exchange performance.

  In order to achieve the above object, a first configuration of the present invention includes a first heat exchange channel formed by arranging flat plates at a predetermined interval, and the first heat exchange channel. A second heat exchange channel formed by disposing the first heat exchange channel and an enormous portion connected to an end of the first heat exchange channel, the width of the enormous portion E represents the interval between the first heat exchange channels as A, the interval between the second heat exchange channels as B, the first heat exchange channel and the second heat exchange channel, and the enormous amount. The angle between the boundary line and the first heat exchange channel is α (0 <α ≦ π / 2), and the angle between the second heat exchange channel is β (α <β <π−α). ), The heat exchange device is characterized by satisfying a relationship of E = (A + B) × (sin β / sin α) −B.

  The second configuration is the heat exchange device according to the first configuration, wherein the enormous portion is formed at both ends of the first heat exchange channel.

  In the third configuration, the first heat exchange channel formed by arranging flat plates at a predetermined interval and the first heat exchange channel at a predetermined interval are arranged. Connected to the end of the second heat exchange flow path, the first enormous portion connected to the end of the first heat exchange flow path, the second heat exchange flow path formed by The first enormous part width E1 and the second enormous part width E2 have an interval between the first heat exchange channels as A, and the second heat exchange flow The interval between the paths is B, and the angle between the boundary line between the first heat exchange channel and the second heat exchange channel and the enormous portion with the first heat exchange channel is α (0 <α .Ltoreq..pi. / 2), where .beta. (.Alpha. <. Beta. <. Pi .-. Alpha.) Is the angle formed with the second heat exchange channel, E1 = (A + B) .times. (Sin .beta. / Sin .alpha.)-B, E2 = (A + B) .times. (Sin β / sin α) -A It is a heat exchange device characterized by satisfying the relationship.

  In the fourth configuration, the first heat exchange channel, the second heat exchange channel, and the enormous portion are configured by bending a single continuous plate. It is a heat exchange apparatus as described in the structure.

  By configuring as described above, in the heat exchange device having the heat exchange flow path configured by a flat plate and the enormous portion, the three-dimensional flow in the heat exchange flow path is suppressed, and the heat of the heat exchange device is reduced. Exchange performance can be improved.

[First Embodiment]
A first embodiment of the present invention will be described with reference to the drawings. In the description, after describing the internal structure of the heat exchange device 1, the external structure of the heat exchange device 1 will be described.

(Internal structure of heat exchange device 1)
The internal structure of the heat exchange device 1 will be described with reference to FIGS. 1 to 3.

  FIG. 1 is a cross-sectional perspective view illustrating the internal structure of the heat exchange device 1 according to the first embodiment. 2A and 2B are schematic views of the flow path of the heat exchange device 1, wherein FIG. 2A is a perspective view and FIG. 2B is a cross-sectional view.

  As shown in FIG. 1, the inside of the box 30 of the heat exchange device 1 is partitioned by a thin heat transfer material plate P so as to be separated into a fluid passage through which the first fluid flows and a fluid passage through which the second fluid flows. It is done. In FIG. 1, fluid passages through which twelve sets of first fluids flow are fixed inside the box 30 while maintaining a predetermined interval therebetween.

  As shown in FIG. 2, the fluid passage through which the first fluid flows includes a first heat exchange channel 10 that is partitioned by facing a thermally conductive plate P having a flat cross section in a narrow range in a flat shape, The first fluid introducing enormous portion 11 and the first fluid deriving enormous portion 12 are formed at both ends. Each enormous part 11 and 12 is connected to the first fluid in an airtight state. On the other hand, the fluid passage through which the second fluid flows is formed by the second heat exchange channel 20 and the second fluid introduction part 21 and the second fluid outlet part 22 formed at both ends thereof. In the present embodiment, the second fluid introduction part 21 and the second fluid lead-out part 22 are formed to have a triangular cross section.

  The fluid passage of the first fluid fixes and supports the enormous portions 11 and 12 and the side surfaces of the first heat exchange channel 10 to a sealing portion (described later) on the side surface of the box. Therefore, the space formed by the gap defined by the heat transfer material plate P constituting the fluid passage of the first fluid and the heat transfer material plate P constituting the adjacent fluid passage is used for the first heat exchange. It becomes a shape (Z-shape) similar to the flow path 10 and constitutes the second heat exchange flow path 20.

  The second fluid introduction part 21 and the second fluid lead-out part 22 at both ends of the second heat exchange channel 20 are externally connected by the heat-resistant material box 30 so as to include a plurality of fluid passages of the first fluid. Formed by partitioning. Note that the box body 30 has heat in the second heat exchange channel 20 sandwiched between the first heat exchange channels 10 in a portion adjacent to the first heat exchange channel 10 of the fluid passage of the first fluid. The first heat exchange channel 10 is formed with a predetermined gap so that heat exchange similar to the exchange can be performed.

  There may be a method of releasing the second fluid by opening the discharge part of the second heat exchange channel 20 to the environment, but in many cases, the second fluid is considered in consideration of high exhaust gas temperature and filtration. Are collected and discharged in place by a conduit. Moreover, since the heat | fever which the 2nd fluid hold | maintains is utilized, since the utilization method guide | induced to another heat exchanger is also considered, installation of the 2nd fluid derivation | leading-out part 22 is required.

  The box body 30 has a function of fixing the constituent members of the heat exchange device such as the first fluid introducing enormous portion 11 and supporting the flow path, a function of fixing and supporting a sealing portion described later, and a fluid passage of the second fluid. Fulfills the function of forming. The box 30 can also be used as a support member when the heat exchange device is fixed to an external device. In this case, it is necessary to consider the strength required for the structure.

  The flow of the fluid in this embodiment is demonstrated using FIG. In FIG. 2, the flow indicated by the solid line arrow is the flow of the first fluid, and the flow indicated by the broken line arrow is the flow of the second fluid.

  As shown in FIG. 2A, the first fluid is introduced into the first fluid introduction enormous portion 11. The first fluid introduced into the first fluid introduction enormous part 11 reaches the first fluid deriving enormous part 12 after passing through the first heat exchange channel 10. Thereafter, the first fluid is discharged out of the apparatus through the first fluid deriving enormous portion 12. On the other hand, the second fluid is similarly introduced from the second fluid introduction part 21 and passes through the second heat exchange channel 20 formed so as to be sandwiched between the first heat exchange channels 10, It reaches the fluid outlet 22.

  Since it is configured in this manner, the low temperature first fluid is supplied to the first fluid introduction enormous portion 11 and passed through the first heat exchange channel 10 while the high temperature second fluid is supplied to the second fluid introduction portion. When the first heat exchange channel 10 and the second heat exchange channel 20 are passed through the second heat exchange channel 20, heat exchange is performed on the plate P made of heat transfer material between the first heat exchange channel 10 and the second heat exchange channel 20. Done. As a result, heat is applied from the second fluid to the first fluid. Further, the flow of the first fluid in the first heat exchange channel 10 and the flow of the second fluid in the second heat exchange channel 20 are counterflow type, and are used for heat exchange. Is the best.

  The first fluid and the second fluid are not mixed with each other because the heat transfer material plate P is used as a partition wall. Further, the cross-sectional area of the plate P made of the heat transfer material is very large compared to the cross-sectional area of the fluid flow path. For this reason, even when the flow rate and flow rate of the fluid are large, it is possible to sufficiently transfer heat to the fluid that flows oppositely.

  The amount of fluid that can pass through the first heat exchange channel 10 and the second heat exchange channel 20 can be selected according to the installation interval of the plates P. In addition, in FIG. 1, 12 fluid passages for the first fluid are shown, but it can be selected by design in consideration of the amount of fluid, the amount of heat transfer, the temperature of the fluid, etc., realizing a large heat exchanger In this case, a larger number of channels can be provided than in the present embodiment.

  The characteristic part of this embodiment is demonstrated using FIG. FIG. 3 is a diagram for explaining the relationship between the heat exchange flow path and the enormous portion, wherein (a) and (b) are diagrams for explaining the design procedure of the enormous portion, and (c) is the structure of the enormous portion designed. FIG.

  In general, when constructing a counter flow type heat exchange device, it is said that a portion where a first fluid and a second fluid flow in or out, generally called a header, is difficult to achieve a geometrically ideal flow path configuration. ing. In this embodiment, a structure provided with a reasonable transition function is provided so that a mathematical solution that provides a fundamental solution to this problem can be applied to the heat exchange device.

  As shown in FIG. 3A, when designing the enormous part, first, a boundary line (auxiliary line zz) is formed at the boundary between the first heat exchange channel 10 and the enormous parts 11 and 12. Pull. Then, the width A of the first heat exchange channel 10 and the reference width C serving as a reference on the enormous portion side corresponding to the first heat exchange channel 10 satisfy the following expression (1). Constitute.

C / A = sin β / sin α (1)
However, 0 <α ≦ π / 2 and α <β <π−α.

At the same ratio, the width B of the second heat exchange channel 20 and the reference width D corresponding to the second heat exchange channel 20 also satisfy the same ratio as described above ( 2),
D / B = sin β / sin α (= C / A) (2)
Configure to meet.

Next, as shown in FIG. 3 (b), the width E of the enormous portion is set to the following equation (3),
E = (C + D) −B, ie
E = (A + B) × (sin β / sin α) −B (3)
Configure to meet.

  As in the above procedure, the width E of the enormous portion is determined using the facts in elementary mathematics (see FIG. 3C). FIG. 3C illustrates the first fluid derivation enormous portion 12. With this configuration, the same two-dimensional structure is obtained regardless of the cross section. For this reason, the generation of a three-dimensional flow other than the enormous part is suppressed, and the flow of the first heat exchange channel and the second heat exchange channel is made closer to the ideal counter flow, thereby improving the heat exchange performance. Can do. In addition, since the same two-dimensional structure is used in any cross section, it is sufficient to make the same member repeatedly, so that the manufacture is easy.

(External structure of heat exchange device 1)
The external structure of the heat exchange device 1 will be described with reference to FIG. 4A and 4B are diagrams illustrating the external structure of the heat exchanging device 1. FIG. 4A is a perspective view of the front side in FIG. 1, FIG. 4B is a perspective view of the back side in FIG. 1, and FIG. FIG. The figure of (c) is the figure seen from the arrow direction in (a).

  As shown in FIG. 4A, a sealing portion 40 is disposed on the surface side of FIG. In the sealing portion 40, an introduction hole 41 is formed at a position corresponding to the first fluid introduction enormous portion 11, and an outlet hole 42 is formed at a position corresponding to the first fluid deriving enormous portion 12.

  As shown in FIG. 4B, a sealing portion 50 is disposed on the back side of FIG. In the sealing part 50, an introduction hole 51 is formed at a position corresponding to the second fluid introduction part 21, and a lead-out hole 52 is formed at a position corresponding to the second fluid lead-out part 22.

  The sealing part 40 and the sealing part 50 seal the fluid while ensuring a hole leading to the fluid passage inside the heat exchange device 1. The sealing portions 40 and 50 are made of a material such as a heat resistant alloy or ceramic. Since the sealing parts 40 and 50 are in contact with the fluid for heat exchange, they are required to have heat resistance and low thermal conductivity. Therefore, although ceramic is preferable, a composite material of a heat-resistant alloy and ceramic, or a metallized ceramic can be selected in consideration of hermetically sealing with a heat exchange member.

  Further, the sealing portions 40 and 50 are the first heat exchange channel 10, the second heat exchange channel 20, the first fluid introduction enormous portion 11, the first fluid deriving enormous portion 12, and the second fluid introduction. The end edges of the portion 21 and the second fluid lead-out portion 22 are hermetically sealed by means such as welding, brazing, or ceramic adhesive.

  Since the connection parts of various pipes, which will be described later, are mounted adjacent to the sealing part, the holes 41, 42, 51, 52 of the sealing parts 40, 50 are compatible with each part of the heat exchange device and the pipe of the connection part. Provide to do.

  As shown in FIG. 4C, ducts 61, 62, 63, and 64 are disposed in the holes 41, 42, 51, and 52 of the sealing portions 40 and 50, respectively. In the present embodiment, the first fluid is introduced from the duct 61 and led out from the duct 62. On the other hand, the second fluid is introduced from the duct 63 and led out from the duct 64.

  In the present embodiment, the first fluid is introduced and led out from the front surface side, and the second fluid is introduced and led out from the back surface side. However, the present invention is not limited to this. The direction in which the first fluid and the second fluid flow can be changed as appropriate, and accordingly, the position and shape of the hole and the position of the duct connected to the hole can be changed as appropriate.

(Modification of heat exchange device 1)
The modification of the heat exchange apparatus 1 is demonstrated using FIG.5 and FIG.7. 5 to 7 are schematic diagrams for explaining a modification of the first embodiment. In FIGS. 5 and 6, the portion painted in black is the flow path of the first fluid.

  In the present embodiment, the heat exchange channels 10 and 20 are arranged in a straight line, but the present invention is not limited to this. As shown in FIGS. 5A and 5B, the heat exchange channels 10 and 20 may have a curved portion. By providing the heat exchange channels 10 and 20 with curved portions, the surface area of the channels can be further secured, and the heat exchange performance can be enhanced.

  Further, as shown in FIG. 6A, two internal structures of the present embodiment may be arranged symmetrically.

  In the present embodiment, the auxiliary line zz is designed as a straight line, but the present invention is not limited to this. As shown in FIG. 6B, the auxiliary line zz may be designed as a circle. By making the auxiliary line z-z circular, a partition wall for configuring the second flow path becomes unnecessary, and the box body 30 can be configured in a cylindrical shape. Thus, if comprised in a column shape, the circumference of a cylinder outer peripheral part will become larger than the circumference of the part in which the enormous part inside a cylinder is arrange | positioned. Then, the room for selection of the means for connecting the flow path to the header, such as providing an enormous portion, is expanded, and the opposed heat exchange device can be easily realized.

  As shown in FIG. 7A, a relaxation curve may be added to the enormous portion while keeping the width of the enormous portion of the figure constant. If the flow path cross-section is rounded by the relaxation curve, the resistance received by the fluid can be reduced. In addition, the device can be easily manufactured by adding a relaxation curve.

  As shown in FIG. 7B, an enormous portion can be further added by using the design method of the present embodiment. Specifically, the flow path is provided between the enormous parts configured by the design method of the present embodiment, and the enormous part connected to the flow path is formed. Thereby, the enormous part can be arranged in a staggered manner.

[Second Embodiment]
A second embodiment of the present invention will be described with reference to FIGS. Members having the same action as described above are denoted by the same reference numerals and description thereof is omitted. FIG. 8 is a cross-sectional perspective view illustrating the internal structure of the heat exchange device 2 according to the second embodiment. FIG. 9 is a schematic diagram of the flow path of the heat exchange device 2, wherein (a) is a perspective view and (b) is a cross-sectional view.

  As shown in FIGS. 8 and 9, in the present embodiment, the first heat exchange channel 70 and the second heat exchange channel 80 are bent as if a single flat plate P is bent. It is configured to be continuous so that the cross-sectional shape can be drawn with a single stroke.

  As shown in FIGS. 8 and 9, the fluid passage through which the first fluid flows includes the first heat exchange channel 70, the first fluid introduction enormous portion 71 and the first fluid outlet portion 72 formed at both ends thereof. Consists of On the other hand, the fluid passage through which the second fluid flows is composed of the second heat exchange channel 20, the second fluid introduction enormous portion 81 and the second fluid outlet portion 82 formed at both ends thereof.

Here, the width E1 of the first fluid introduction enormous part (first enormous part) 71 and the width E2 of the second fluid introduction enormous part (second enormous part) 81 are configured to satisfy the same formula as described above. To do. That is, an angle formed by a boundary line (auxiliary line zz) between the first heat exchange channel and the second heat exchange channel and the enormous portion with the first heat exchange channel is α (0 <Α ≦ π / 2), and the angle formed with the second heat exchange channel is β (α <β <π−α), the following equation (4):
E1 = (A + B) × (sin β / sin α) −B,
E2 = (A + B) × (sin β / sin α) −A (4)
Configure to meet.

  Even if it is the structure like this embodiment, the same effect can be acquired. In addition, by configuring each heat exchange channel with a single plate, it is not necessary to weld the partition walls during production, and a heat exchange device that is easy to produce can be constructed.

[Other Embodiments]
In the above-described embodiment, the heat exchange device has been described as being used for heat exchange between gases, but it can be used not only for heat exchange between gases, but also for heat exchange between gases and liquids, or between liquids. is there. For example, there is heating air for heating using hot waste water or cooling air for cooling by river water. However, except for such special applications, in the heat exchange device, the pressure of the first fluid and the pressure of the second fluid are often different. For this reason, when pressure resistance is taken into consideration, ribs or butting may be provided in the flow path in a direction that does not hinder the flow of fluid depending on the conditions under which the heat exchange device is used. Further, in a use state where steam is generated and the pressure becomes high, it is necessary to optimize the structure of the fluid passage according to the properties of the fluid, such as considering pressure resistance.

  The present invention can be used in a heat exchange device that exchanges heat between two fluids (gas, liquid, etc.).

The cross-sectional perspective view explaining the internal structure of the heat exchange apparatus 1 which concerns on 1st Embodiment. The schematic diagram of the flow path of the heat exchange apparatus 1 which concerns on 1st Embodiment. The figure explaining the relationship between the heat exchange flow path and the enormous part. The figure explaining the external structure of the heat exchange apparatus 1 which concerns on 1st Embodiment. The schematic diagram for demonstrating the modification of 1st Embodiment. The schematic diagram for demonstrating the modification of 1st Embodiment. The schematic diagram for demonstrating the modification of 1st Embodiment. The cross-sectional perspective view explaining the internal structure of the heat exchange apparatus 2 which concerns on 2nd Embodiment. The schematic diagram of the flow path of the heat exchange apparatus 2 which concerns on 2nd Embodiment.

Explanation of symbols

P ... plate, 1 ... heat exchange device, 2 ... heat exchange device, 10 ... first heat exchange channel, 11 ... first fluid introduction enormous part, 12 ... first fluid deriving enormous part, 20 ... second Heat exchange flow path, 21 ... second fluid introduction part, 22 ... second fluid lead-out part, 30 ... box, 40 ... sealing part, 41 ... introduction hole, 42 ... lead-out hole, 50 ... sealing part, 51 ... Introduction hole, 52 ... Leading hole, 61 ... Duct, 62 ... Duct, 63 ... Duct, 64 ... Duct, 70 ... First heat exchange channel, 71 ... First fluid introduction enormous part, 72 ... First fluid Deriving section, 80 ... second heat exchange channel, 81 ... second fluid introducing enormous section, 82 ... second fluid deriving section

Claims (4)

A first heat exchange channel formed by arranging flat plates at a predetermined interval;
A second heat exchange channel formed by disposing the first heat exchange channel at a predetermined interval;
A huge portion connected to an end of the first heat exchange channel,
The width E of the huge part is
The interval between the first heat exchange channels is A,
The interval between the second heat exchange channels is B,
The angle between the boundary line of the first heat exchange channel and the second heat exchange channel and the enormous portion with the first heat exchange channel is α (0 <α ≦ π / 2), If the angle between the two heat exchange channels is β (α <β <π−α),
E = (A + B) × (sin β / sin α) −B
A heat exchange device characterized by satisfying the above relationship.   The heat exchanging device according to claim 1, wherein the enormous portion is formed at both ends of the first heat exchange channel. A first heat exchange channel formed by arranging flat plates at a predetermined interval;
A second heat exchange channel formed by disposing the first heat exchange channel at a predetermined interval;
A first enormous portion connected to an end of the first heat exchange channel;
A second enormous portion connected to an end of the second heat exchange channel,
The width E1 of the first huge portion and the width E2 of the second huge portion are:
The interval between the first heat exchange channels is A,
The interval between the second heat exchange channels is B,
The angle between the boundary line of the first heat exchange channel and the second heat exchange channel and the enormous portion with the first heat exchange channel is α (0 <α ≦ π / 2), If the angle between the two heat exchange channels is β (α <β <π−α),
E1 = (A + B) × (sin β / sin α) −B,
E2 = (A + B) × (sin β / sin α) −A
A heat exchange device characterized by satisfying the above relationship.   The heat exchange device according to claim 3, wherein the first heat exchange channel, the second heat exchange channel, and the enormous portion are configured by bending a single continuous plate.

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