WO2006077785A1 - Échangeur thermique à plaque - Google Patents

Échangeur thermique à plaque Download PDF

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Publication number
WO2006077785A1
WO2006077785A1 PCT/JP2006/300423 JP2006300423W WO2006077785A1 WO 2006077785 A1 WO2006077785 A1 WO 2006077785A1 JP 2006300423 W JP2006300423 W JP 2006300423W WO 2006077785 A1 WO2006077785 A1 WO 2006077785A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
exchange chamber
heat transfer
heat
plate
Prior art date
Application number
PCT/JP2006/300423
Other languages
English (en)
Japanese (ja)
Inventor
Iwao Sawada
Hiroshi Fukada
Kazunori Morinaga
Junichi Nakamura
Kenji Kusunoki
Original Assignee
Sasakura Engineering Co., Ltd.
Hisaka Works, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sasakura Engineering Co., Ltd., Hisaka Works, Ltd. filed Critical Sasakura Engineering Co., Ltd.
Priority to CN2006800013753A priority Critical patent/CN101137882B/zh
Priority to JP2006536990A priority patent/JP4321781B2/ja
Publication of WO2006077785A1 publication Critical patent/WO2006077785A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0075—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements the plates having openings therein for circulation of the heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another

Definitions

  • the present invention is formed by laminating a plurality of heat transfer plates so that a first heat exchange chamber and a second heat exchange chamber are alternately formed by sandwiching a spacer body serving as a seal therebetween.
  • plate-type heat exchangers it relates to plate-type heat exchangers that are used to heat and evaporate liquids such as water or to cool and condense water vapor.
  • Patent Document 1 as a prior art describes a plate-type heat exchanger having the above-described configuration as a second type of liquid to be evaporated such as seawater or water supplied to the first heat exchange chamber among the heat exchange chambers. It is used for evaporation, which is heated and boiled by a heating fluid such as heating steam supplied to the heat exchange chamber, and the steam introduced into the first heat exchange chamber of each of the heat exchange chambers is used as the second heat. It is proposed to be used for condensation by cooling with the cooling fluid supplied to the exchange chamber.
  • the prior art plate-type heat exchange described in Patent Document 1 uses one of the corners on the upper side of each heat transfer plate when it is used as an evaporator.
  • a steam outlet from each of the first heat exchange chambers is formed at a corner of the heat transfer plate, or at a part of the upper side of the heat transfer plate.
  • each of the first heat exchange chambers is provided with an inlet for the liquid to be evaporated, while the other of the two corners on the upper side of each heat transfer plate is heated to the second heat exchange chamber.
  • the fluid inlet is configured such that a heating fluid outlet from each of the second heat exchange chambers is provided at one of the two corners on the lower side of each of the heat transfer plates.
  • Patent Document 1 Japanese Patent Laid-Open No. 9-299927
  • the liquid to be evaporated supplied from the liquid inlet at one corner in the first heat exchange chamber is: Mainly, the pressure loss becomes the lowest, that is, in the first heat exchange chamber while boiling and evaporating, flowing in a substantially linear direction from the liquid inlet to the vapor outlet, while one of the second heat exchange chambers.
  • the heating fluid supplied from the heating fluid inlet at the corner is also substantially linear in the direction in which the pressure loss is lowest, that is, in the direction from the heating fluid inlet to the heating fluid outlet in the second heat exchange chamber.
  • the left and right or one side of the main flow in the direction facing the steam outlet in the first heat exchange chamber has a stagnation portion of the flow, while the second heat exchange chamber For heating indoors There is a stagnation part of the flow on the left or right or one side of the main flow in the direction facing the fluid outlet.
  • the liquid to be evaporated introduced into the first heat exchange chamber is heated by the heating fluid, and a part thereof flows toward the vapor outlet while boiling and evaporating.
  • the pressure of that portion rises due to the vapor evaporated from boiling, and the liquid to be evaporated becomes difficult to flow.
  • the liquid to be evaporated is originally expected and does not flow easily in the direction of the heating fluid inlet, and easily flows in the direction of the heating fluid outlet. Near the fluid inlet There is a problem that the first heat exchange chamber is prone to scale because it evaporates with a small amount of liquid to be evaporated.
  • the plate heat exchanger of the prior art when used as a steam condenser, the steam mainly condenses from the steam inlet to the condensed water outlet while condensing. While the cooling fluid flows almost linearly in the direction of the force, the cooling fluid mainly flows almost linearly in the direction of the force of the cooling fluid inlet force to the cooling fluid outlet in the second heat exchange chamber. As in the case described above, the left and right or one side portions of the first heat exchange chamber with respect to the flow in the diagonal direction, and the diagonal direction of the second heat exchange chamber in the diagonal direction.
  • claim 1 of the present invention provides:
  • Preliminary plate consisting of multiple heat transfer plates stacked so as to alternately form a first heat exchange chamber for generating steam or condensing steam and a second heat exchange chamber for heating or cooling.
  • Tunnel-like fluid passages configured to extend along the heat transfer plates are formed in the first heat exchange chamber and the second heat exchange chamber so that both ends thereof open to the heat exchange chambers.
  • Claim 2 of the present invention provides
  • the tunnel-like fluid passage is formed by a partition provided in a spacer body sandwiched between the heat transfer plates.”
  • Claim 3 of the present invention provides
  • the tunnel-like fluid passage is in contact with the ridgeline at the mountain-shaped ridges provided in the pair of heat transfer plates forming the heat exchange chamber in a linear manner. It is formed by doing.
  • Claim 4 of the present invention provides:
  • mountain-shaped ridges are formed by inflating and deforming a part of the heat transfer plate.”
  • Claim 5 of the present invention provides:
  • Preliminary plate consisting of multiple heat transfer plates stacked so as to alternately form a first heat exchange chamber for generating steam or condensing steam and a second heat exchange chamber for heating or cooling.
  • the heat transfer plates are stacked by arranging a plurality of ridges extending in a mountain range on the front and back surfaces of the heat transfer plates, the ridge lines and the back surfaces of the mountain transfer ridges on the surface of the heat transfer plate are stacked.
  • the ridgeline in each mountain-shaped ridge is in linear contact over the long part in each first heat exchange chamber and each second heat exchange chamber, and each mountain range in each first heat exchange chamber
  • a plurality of tunnel-shaped fluid passages are formed in the portion between the ridges so that both ends open into the first heat exchange chamber, while each of the second heat exchange chambers has the mountain range.
  • a plurality of tunnel-like fluid passages are formed in the part between the ridges so that both ends open into the second heat exchange chamber. It is characterized by that.
  • Claim 6 of the present invention provides: “In the description of claim 5, each mountain-shaped ridge in each heat transfer plate is formed by expanding and deforming a part of the heat transfer plate.”
  • Claim 7 of the present invention provides:
  • each mountain-shaped ridge in each heat transfer plate has a herringbone pattern arrangement as viewed from the stacking direction of the heat transfer plates.”
  • Claim 8 of the present invention provides
  • each mountain-shaped ridge in each heat transfer plate is intermittent.
  • Claim 9 of the present invention provides:
  • each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each rectangular heat transfer plate includes the corners of the upper side.
  • a steam outlet from each of the first heat exchange chambers or a steam inlet to each of the first heat exchange chambers at one corner or in the vicinity thereof or a part of the upper side is the other corner of both corners on the upper side.
  • a heating fluid inlet or a heating fluid outlet for each of the second heat exchange chambers or a cooling fluid inlet or a cooling fluid outlet for each of the second heat exchange chambers is provided in the vicinity thereof.
  • the lower side of the heat transfer plate has a liquid inlet to the first heat exchange chamber or each of the corners in the vicinity of or near the corner of the lower edge of the heat transfer plate.
  • 1st heat exchange chamber power condensation Outlet force Each of the second heat exchanges at or near the other corner that forms a diagonal with the heating fluid inlet or heating fluid outlet or the cooling fluid inlet or cooling fluid outlet of both corners on the lower side.
  • a heating fluid outlet or a heating fluid inlet to the chamber or a cooling fluid outlet or a cooling fluid inlet to each of the second heat exchange chambers is provided.
  • Claim 10 of the present invention includes
  • each rectangular heat transfer plate has a steam outlet or a steam inlet for each of the first heat exchange chambers at or near the center of the upper side.
  • a heating steam inlet to each of the second heat exchange chambers or a cooling fluid inlet to each of the second heat exchange chambers is located at or near one of the two corners.
  • a heating steam inlet to each of the second heat exchange chambers or a cooling fluid outlet to each of the second heat exchange chambers is provided, respectively.
  • a liquid supply port to be evaporated to one heat exchange chamber and a steam condensate outlet for heating to each second heat exchange chamber are provided, or a condensate outlet to each first heat exchange chamber is provided. It is characterized by that.
  • Claim 11 of the present invention provides:
  • each of the heat transfer plates has a rectangular shape when viewed from the stacking direction, and the upper side of each of the rectangular heat transfer plates has a substantially central portion of the upper side. Or a steam outlet or steam inlet force to each first heat exchange chamber in the vicinity thereof, or a heating fluid inlet to each second heat exchange chamber or each of the second heat exchange chambers at or near one of the corners on the upper side.
  • a cooling fluid inlet to the heat exchange chamber, a heating fluid outlet to the second heat exchange chamber or a cooling fluid outlet to the second heat exchange chamber is provided at or near the other corner
  • the evaporative liquid supply port for each first heat exchange chamber or the condensed water outlet for each first heat exchange chamber is provided at or near the lower side of each rectangular heat transfer plate.
  • a pair of heat transfer plates forming the heat exchange chamber in one or both of the first heat exchange chamber and the second heat exchange chamber
  • a pair of heat transfer plates forming the heat exchange chamber in one or both of the first heat exchange chamber and the second heat exchange chamber
  • a plurality of tunnel-like fluid passages configured to extend along the two sides so that both ends open into the heat exchange chamber, the fluid in the heat exchange chamber One end force flows into the tunnel-like fluid passage, and the other end force flows out.
  • Each of the tunnel-like fluid passages is constructed so that the fluid extends over the entire heat exchange chamber, thereby allowing the fluid to reach the entire heat exchange chamber. Can be guided over a wide range.
  • the liquid to be evaporated that has flowed into the tunnel-like fluid passage at the lower side passes through the passage without being displaced in the middle even if the pressure rises due to boiling evaporation. Since it flows in the direction toward the steam outlet, the liquid to be evaporated can be sufficiently supplied even near the heating fluid inlet.
  • each of the tunnel-like fluid passages can have the configuration described in claim 2, but by adopting the configuration described in claim 3 or claim 5, By laminating the heat plates, the tunnel-like fluid passages can be formed at the same time, so that assembly and disassembly are extremely easy and cleaning of each heat transfer plate is easy.
  • the mountain-like ridges in claim 3 and claim 5 are formed by inflating and deforming a part of the heat transfer plate.
  • the effective heat transfer area of each heat transfer plate can be increased, and the mountain-shaped ridges can be formed by pressing the metal plate, thereby reducing the manufacturing cost.
  • each tunnel-like fluid passage is formed by a ridge line in each mountain-shaped ridge provided on the surface of the heat transfer plate, and each of the tunnel-like fluid passages provided on the back surface of the heat transfer plate.
  • Form formed by linear contact with the ridgeline in the mountainous ridge Therefore, the height of each mountain-shaped ridge can be made lower than the case where a mountain-shaped ridge is provided only on one of the front and back surfaces of the heat transfer plate. Processing becomes easier and manufacturing costs can be reduced.
  • the heat transfer area can be further increased.
  • each of the mountain-shaped ridges has an intermittent configuration, so that the fluid flowing in the tunnel-shaped fluid passage formed by each of the mountain-shaped ridges is Since it enters and exits between adjacent tunnel-like fluid passages from the point of intermittent connection, it is possible to promote the spread of the fluid to the whole by interrupting as necessary within the range that does not impede the induction effect. There is an advantage that can be.
  • each of the tunnel-like fluid passages so as to extend over the entire second heat exchange chamber, the pressure loss is minimized, that is, from the heating fluid inlet to the heating fluid outlet. It can be guided over a wide range so as to prevent the pressure loss from flowing in the direction in which the pressure loss is the lowest and to reach the entire second heat exchange chamber.
  • the liquid to be evaporated that has flowed into the first heat exchange chambers from the liquid supply port to be evaporated evaporates by heating from the second heat exchange chamber, and heat transfer on both sides of the first heat exchange chamber.
  • Each of the tunnel-like fluid passages is formed at each mountain-like ridge in the plate and flows so that one end force flows into each tunnel-like fluid passage and the other end flows out.
  • the tunnel-like fluid passages flow in the direction in which the pressure loss is lowest, that is, in the direction from the liquid supply port to the vapor outlet.
  • each of the tunnel-like fluid passages is configured to extend and extend over the entire second heat exchange chamber, so that the pressure loss is minimized by each of the tunnel-like fluid passages. That is, it can be guided over a wide range so as to prevent the flow in the direction from the cooling fluid inlet to the cooling fluid outlet and to reach the entire second heat exchange chamber.
  • the steam that has flowed into the first heat exchange chambers from the steam inlet is condensed by cooling of the second heat exchange chamber force, and is placed on the heat transfer plates on both sides of the first heat exchange chamber.
  • Each tunnel-like fluid passage is formed so as to flow into one of the tunnel-like fluid passages formed in each mountain-shaped ridge, so that the other end force flows out.
  • the tunnel-like fluid passages cause the pressure loss to be lowest, that is, the steam inlet force also flows toward the condensed water outlet in the direction of the force. This can be prevented and guided over a wide range so as to reach the entire first heat exchange chamber.
  • the plate-type heat exchanger used for evaporation or condensation may be configured as described in claim 10 or as described in claim 11. Configure.
  • the ability to stagnate the flow in each of the first heat exchange chambers and each of the second heat exchange chambers can be reliably reduced, thereby greatly improving the evaporation capacity or the condensation capacity. This makes it possible to reduce the size and weight, and to greatly reduce the frequency of cleaning to remove scale.
  • FIG. 1 is a front view of a heat exchanger according to a first embodiment.
  • FIG. 2 is a side view of FIG.
  • FIG. 3 is an enlarged sectional view taken along line III-III in FIGS. 2, 5, and 6.
  • FIG. 3 is an enlarged sectional view taken along line III-III in FIGS. 2, 5, and 6.
  • FIG. 4 is an enlarged sectional view taken along line IV-IV in FIGS. 2, 5, and 6.
  • FIG. 4 is an enlarged sectional view taken along line IV-IV in FIGS. 2, 5, and 6.
  • FIG. 5 is an enlarged sectional view taken along line V-V in FIGS. 1 and 3.
  • FIG. 6 is an enlarged sectional view taken along line VI-VI in FIGS. 1 and 4.
  • FIG. 7 is a perspective view of a first heat transfer plate used in the heat exchanger.
  • FIG. 8 is a perspective view of a second heat transfer plate used in the heat exchanger.
  • FIG. 9 is a perspective view showing a modification of the first heat transfer plate.
  • FIG. 10 is a perspective view showing a modification of the second heat transfer plate.
  • FIG. 11 is a perspective view showing another modification of the first heat transfer plate.
  • FIG. 12 is a perspective view showing another modification of the second heat transfer plate.
  • FIG. 13 is a front view of a heat exchanger according to a second embodiment.
  • FIG. 14 is a side view of FIG.
  • FIG. 15 is an enlarged cross-sectional view taken along the line XV--XV in FIGS. 14, 17 and 18;
  • FIG. 16 is an enlarged sectional view taken along line XVI--XVI in FIGS. 14, 17 and 18.
  • FIG. 17 is an enlarged sectional view taken along lines XVII-XVII in FIGS. 13 and 16.
  • FIG. 18 is an enlarged sectional view taken along lines XVIII--XVIII in FIGS. 13 and 15.
  • FIG. 19 is a cross-sectional view of the same portion as FIG. 15 in a modification of the second embodiment.
  • FIG. 20 is a sectional view taken along line XX—XX in FIG.
  • FIG. 17 is a cross-sectional view of the same portion as FIG. 16 in a modification of the second embodiment.
  • FIG. 22 is a front view of heat exchange according to the third embodiment.
  • FIG. 23 is a side view of FIG.
  • FIG. 24 is an enlarged sectional view taken along the line XXIV—XXIV in FIG.
  • FIG. 25 is an enlarged sectional view taken along the line XXV—XXV in FIG.
  • FIG. 25 is a cross-sectional view of the same portion as FIG. 24 in the modification of the third embodiment.
  • FIG. 26 is a cross-sectional view of the same portion as FIG. 25 in a modification of the third embodiment.
  • ⁇ 28 A sectional view of the same portion as FIG. 24 in another modification of the third embodiment.
  • 29 A sectional view of the same portion as FIG. 25 in another modified example of the third embodiment.
  • FIGS. 1 to 12 show a relatively small plate-type heat exchanger 1 used for evaporation in the first embodiment.
  • the heat exchanger 1 includes a plurality of first heat transfer plates 2 made rectangular by a relatively thin metal plate and a plurality of second heat transfer plates 3 made rectangular by a relatively thin metal plate.
  • a spacer body 5 serving as a seal for forming the first heat exchange chamber 4 between the first heat transfer plate 2 and the second heat transfer plate 3 is sandwiched between the first heat transfer plate 2 and the second heat transfer plate 3, and the second heat transfer plate 3
  • the first heat transfer plate 2 and the first heat transfer plate 2 were alternately stacked so as to sandwich the space body 7 serving as a seal for forming the second heat exchange chamber 6, and this stacked body was disposed on one end face thereof.
  • the face plate 8 and the face plate 9 disposed on the other end face are fastened to each other with bolts 10.
  • Each of the heat transfer plates 2 and 3 has a steam outlet 11 communicating with the inside of each of the first heat exchange chambers 4 at one of the corners in the upper side or in the vicinity thereof.
  • Heating fluid inlets 12 communicating with the respective second heat exchange chambers 6 are formed in the other corners or in the vicinity of both corners, and these steam outlets 11 and heating fluid inlets 12 are provided. Is open in one or both of the double-sided plates 8 and 9.
  • the steam outlet 11 may be provided in a part of the upper side.
  • each of the heat transfer plates 2 and 3 has the first heat in each corner at or near the corner that forms a diagonal to the steam outlet 11 out of both corners on the lower side.
  • the vaporized liquid supply port 13 communicating with the inside of the exchange chamber 4 has the respective corners at or near the corner that forms a diagonal to the heating fluid inlet 12 among the two corners on the lower side thereof.
  • Heating fluid outlets (14) communicating with the heat exchange chamber (6) are respectively formed, and the liquid supply port (13) and the heating fluid outlet (14) are either one of the double-sided plates (8, 9) or Open to both Yes.
  • the liquid to be evaporated supplied from the liquid supply port 13 to be evaporated into each first heat exchange chamber 4 is heated by heat transfer from the second heat exchange chamber 6 on both sides.
  • the vapor generated by boiling and evaporating is discharged from the first heat exchange chamber 4 through the vapor outlet 11 together with a part of the liquid to be evaporated (brine) that has not evaporated.
  • the heating fluid such as heating steam supplied from the heating fluid inlet 12 into each of the second heat exchange chambers 6 is evaporated by heat transfer to the first heat exchange chamber 4 on both sides. After being heated, it is discharged as condensed water from the heating fluid outlet 14.
  • the first heat transfer plate 2 has a surface 2a, that is, the first heat transfer plate 2 attached to the first heat transfer plate 2, as shown in FIG.
  • a plurality of ridges 15 extending in a mountain range in the longitudinal direction are arranged in parallel or substantially in parallel at an appropriate interval on the surface looking into the exchange chamber 4, and the back surface 2b, that is, the first heat transfer.
  • a plurality of raised portions 16 extending in a mountain range in the lateral direction are arranged in parallel or substantially in parallel at an appropriate interval on the surface where the plate 2 looks into the second heat exchange chamber 6.
  • the second heat transfer plate 3 has a back surface 3b, that is, the second heat transfer plate 3 is connected to the first heat transfer plate 3 as shown in FIG.
  • a plurality of ridges 17 extending in a mountain shape in the vertical direction are arranged on the surface looking into the exchange chamber 4 in accordance with the arrangement of the mountain ridges 16 on the surface 2a of the first heat transfer plate 2.
  • the surface 3a thereof that is, the surface where the second heat transfer plate 3 looks into the second heat exchange chamber 6 is formed, for example, in a mountain range in the lateral direction.
  • a plurality of extending ridges 18 are arranged in parallel or substantially in parallel at appropriate intervals according to the arrangement of the mountain-shaped ridges 16 on the back surface 2b of the first heat transfer plate 2.
  • Each of the mountainous ridges 15, 16, 17, 18 is formed by bulging and deforming a part of the heat transfer plate.
  • each mountain-shaped ridge 15 on the surface 2a of the first heat transfer plate 2 and the second heat transfer plate By constructing the ridgeline of each mountain-shaped ridge 17 on the back surface 3b of the plate 3 so as to make a linear contact over its long part (preferably the entire length), the inside of each first heat exchange chamber 4 Of which In the first heat exchange chamber 4, for example, in the longitudinal direction, that is, in the direction from the vaporized liquid inlet 13 toward the vapor outlet 11, the portion between the mountainous ridges 15 and 17 that are in contact with each other.
  • a plurality of tunnel-like fluid passages 19 extending in a direction crossing the opening and having both ends opened into the first heat exchange chamber 4 are formed in parallel.
  • each mountain-shaped ridge 16 on the back surface 2b of the first heat transfer plate 2 and the second heat transfer plate The ridgeline of each mountain-shaped ridge 18 on the surface 3a of 3 is configured so as to come into linear contact over the long part (preferably the entire length) thereof, so that the inside of each second heat exchange chamber 6 Of the second heat exchanging chamber 6 between the mountain-shaped ridges 16 and 18 in contact with each other, for example, in the lateral direction, that is, from the heating fluid inlet 12 to the heating fluid outlet 14.
  • a plurality of tunnel-like fluid passages 20 extending in a direction crossing the opposite direction and having both ends open into the second heat exchange chamber 6 are formed in parallel.
  • the heating fluid such as heating steam that has flowed into each second heat exchange chamber 6 from the heating fluid inlet 12 passes into both sides of the second heat exchange chamber 6.
  • the heat transfer plates 2 and 3 flow into the tunnel-like fluid passages 20 formed by the mountainous ridges 16 and 18, and the tunnel-like fluid passages 20 have the lowest pressure loss.
  • the direction crossing the direction from the heating fluid inlet 12 toward the heating fluid outlet 14 is (2) While being guided so as to spread throughout the heat exchange chamber (6), the liquid to be evaporated that has flowed into the first heat exchange chamber (4) from the liquid supply port (13) is supplied from the second heat exchange chamber (6).
  • the vertical mountainous ridges 15, 17 described above As shown in Figs. 9 and 10, the mountain-shaped ridges 16 and 18 in the opposite direction are divided in such a way that they are divided at their intersections as shown in Figs. 7 and 8.
  • the vertical mountainous ridges 15 and 17 are configured to be continuous, while the horizontal mountainous ridges 16 and 18 are divided, for example, As shown in Fig. 11 and Fig. 12, the horizontal mountainous ridges 16 and 18 are configured to be continuous, while the vertical mountainous ridges 15 and 17 are configured to be intermittent. You can do it.
  • Each of the mountainous ridges 15, 16, 17, and 18 is separated from the heat transfer plates 2 and 3, and is attached to the heat transfer plates 2 and 3 by welding or the like.
  • the mountainous ridges 15, 16, 17 and 18 may be formed by bulging and deforming a part of each of the heat transfer plates 2 and 3 as described above. With this configuration, it is possible to increase the effective heat transfer area in each of the heat transfer plates 2 and 3 and to form the mountainous ridges by pressing the metal plate.
  • each tunnel-like fluid passage 19 in each first heat exchange chamber 4 is formed on the back surface of the mountain-shaped ridge 15 provided on the surface of the first heat transfer plate 2 and the second heat transfer plate 3.
  • the mountain-shaped ridges 17 are formed in linear contact with each other, and the tunnel-shaped fluid passages 20 in the second heat exchange chambers 6 are provided on the surface of the second heat transfer plate 3.
  • the ridge-like ridges 18 and the ridge-like ridges 16 provided on the back surface of the first heat transfer plate 2 are formed in linear contact with each other.
  • the height dimension can be made lower than when the mountain-shaped ridges are provided only on the front or back surface of the heat transfer plate.
  • each of the tunnel-like fluid passages 19, 20 described above is not limited to being formed by the above-described configuration, and a part or all of the tunnel-like fluid passages 19, 20 are interposed between the heat transfer plates 2, 3. It can be configured to be formed by an extension extending inwardly from the spacer bodies 5 and 7 which are also used as seals.
  • the plate-type heat exchanger 1 is used as an evaporator, but the plate-type heat exchanger 1 is used as a steam generator as described below. It can be used as a condenser. That is, when used as a condenser, the steam outlet 11 is used as a steam inlet for steam to be condensed, the liquid supply outlet 13 is used as a condensed water outlet, the heating fluid inlet 12 and One of the heating fluid outlets 14 is configured as a cooling fluid inlet and the other is configured as a cooling fluid outlet. In this case, it goes without saying that the arrow indicating the direction of flow in FIG. Nor.
  • FIGS. 13 to 18 show a plate type heat exchange according to the second embodiment.
  • the plate heat exchanger 31 used as an evaporator is made larger than that in the first embodiment.
  • the plate-type heat exchange 31 in the second embodiment includes a plurality of first heat transfer plates 32 which are rectangular with a relatively thin metal plate, and a rectangular shape with a relatively thin metal plate.
  • a plurality of the second heat transfer plates 33 are sandwiched between the first heat transfer plate 32 and the second heat transfer plate 33, and a seal body 35 for forming the first heat exchange chamber 34 is sandwiched between the second heat transfer plate 33 and the second heat transfer plate 33.
  • the heat plate 33 and the first heat transfer plate 32 are alternately laminated so as to sandwich the sealing body 37 for forming the second heat exchange chamber 36, and this laminated body is disposed on one end face of the face plate. 38 and the face plate 39 disposed on the other end surface are fastened to each other with bolts 40.
  • Each of the heat transfer plates 32, 33 has a horizontally long steam outlet 41 communicating with the inside of each of the first heat exchange chambers 34 at the substantially central portion on the upper side or in the vicinity thereof at both corners on the upper side.
  • Heating steam inlets 42a and 42b communicating with each of the second heat exchange chambers 36 are formed in a portion near the corners or both corners, respectively, and these steam outlet 41 and both heating steam inlets 42a and 42b are
  • the double-sided plates 38 and 39 are open to one or both of them.
  • the steam outlet 41 may be provided in a part of the upper side.
  • each of the heat transfer plates 32, 33 has evaporative liquid supply ports 43a, 43b communicating with each of the first heat exchange chambers 34 at or near the corners on the lower side thereof.
  • Heating steam condensate outlets 44 communicating with the respective second heat exchange chambers 36 are formed in the central part of the lower side or in the vicinity thereof, respectively, and both the liquid to be evaporated outlets 43a, 43b and the heating outlets are provided.
  • the steam condensate outlet 44 is open to one or both of the double-sided plates 38 and 39.
  • the liquid to be evaporated supplied from the both liquid supply ports 43a and 43b into each of the first heat exchange chambers 34 is used for heat transfer from the second heat exchange chamber 36 on both sides.
  • the vapor generated by boiling and evaporating is discharged from the first heat exchange chamber 34 through the vapor outlet 41 together with a part of the liquid to be evaporated (brine) that has not evaporated.
  • the heating steam supplied from both heating steam inlets 42a and 42b into each second heat exchange chamber 36 is cooled by heat transfer to the first heat exchange chamber 34 on both sides.
  • the condensed water is discharged from the condensed water outlet 44.
  • the first heat transfer plate 32 has the first heat transfer plate 32 in the first heat exchange chamber 34 as shown in FIG.
  • a plurality of raised portions 45 extending in a mountain range in the vertical direction are arranged in parallel at appropriate intervals on the desired surface (surface), and the first heat transfer plate 2 is placed in the second heat exchange chamber 36.
  • a plurality of raised portions 46 extending in a mountain range in the lateral direction are arranged in parallel at appropriate intervals on the desired surface (back surface).
  • the second heat transfer plate 33 has the second heat transfer plate 33 placed in the first heat exchange chamber 34 as shown in FIG.
  • a plurality of ridges 47 extending in a mountain range in the vertical direction are paralleled at an appropriate interval on the surface to be viewed (surface) according to the arrangement of the mountain ridges 46 on the surface of the first heat transfer plate 32.
  • a plurality of raised portions 48 extending in a mountain range in the lateral direction are formed on the surface (back surface) of the second heat transfer plate 33 viewed in the second heat exchange chamber 36.
  • the mountain-shaped ridges 46 on the back surface of the heat plate 32 they are arranged in parallel at appropriate intervals.
  • Each of the mountainous ridges 45, 46, 47, 48 is formed by expanding and deforming a part of the heat transfer plate.
  • the ridgeline of each mountain-shaped ridge 45 on the surface of the first heat transfer plate 32 and the second heat transfer plate 33 By constructing the ridgeline of each mountain-shaped ridge 47 on the surface of the first heat exchange chamber 34 in such a way as to make a linear contact over its long part (preferably the entire length), In the first heat exchange chamber 34, the portions between the mountain-shaped ridges 45, 47 that are in contact with each other For example, the both ends open into the first heat exchange chamber 34 extending in the longitudinal direction, that is, in a direction transverse to the vapor outlet 41 from both the vaporized liquid inlets 43. A plurality of tunnel-like fluid passages 49 are formed in parallel.
  • a plurality of tunnel-like fluid passages 50 that extend in a direction transverse to the direction and open at both ends into the second heat exchange chamber 36 are formed in parallel.
  • the heating steam having both the heating steam inlets 42a, 42b force flowing into each second heat exchange chamber 36 is transferred into the second heat exchange chamber 36 on the heat transfer plates on both sides thereof. It flows into the tunnel-like fluid passages 50 formed by the mountainous ridges 46 and 48 at 32 and 33, and the tunnel-like fluid passages 50 flow in the direction in which the pressure loss becomes the lowest.
  • the second steam exchange 42a, 42b is also used for the second heat exchange, for example, in the direction of the force toward the condensate outlet 44, for example, in the direction across it.
  • the liquid to be evaporated flowing from both the liquid supply ports 43a and 43b into the first heat exchange chambers 34 is guided from the second heat exchange chamber 36. While evaporating by heating, heat transfer plates on both sides of the first heat exchange chamber 34 It flows into each tunnel-like fluid passage 49 formed at each mountain-like ridge 45, 47 at 32, 33, and flows through the tunnel-like fluid passage 49 in the direction in which the pressure loss becomes the lowest. As shown by the arrows in FIG. 15, the second liquid supply ports 43a, 43b are directed from the vapor outlet 41 to the vapor outlet 41 in the direction of the force, for example, in the direction crossing them.
  • the vertical mountainous ridges 45, 47 and the horizontal mountainous ridges 46, 48 are divided at the intersections as shown in the figure.
  • the vertical mountainous ridges 45, 47 may be configured to be continuous, or the horizontal mountainous ridges may be configured.
  • the parts 46 and 48 can be configured to be continuous.
  • the mountain-shaped ridges on both the front and back surfaces of each first heat transfer plate 32 are bent in a square shape as shown in FIG.
  • the portions 45 'and 46' as a whole
  • the herringbone pattern is arranged as a whole
  • the mountain-like ridges on both the front and back surfaces of each second heat transfer plate 33 are formed in a square shape as shown in FIG.
  • the overall herringbone pattern can be rubbed.
  • the herringbone pattern By arranging the herringbone pattern in this way, the heat transfer area can be further increased.
  • the arrangement of the herringbone pattern is the same as in the first embodiment. What can be applied to is undeniable.
  • each of the mountain-shaped ridges is separated from each heat transfer plate, and is fixed to each heat transfer plate by welding or the like.
  • it may be configured as follows.
  • the plate-type heat exchanger 31 is used as an evaporator.
  • the plate-type heat exchanger 31 is used as a steam condenser. be able to.
  • the steam outlet 41 is a steam inlet
  • the liquid supply ports 43a and 43b are condensed water outlets
  • one of the heating steam inlets 42a and 42b is used.
  • the heating steam inlet 42a is configured as a cooling fluid inlet
  • the other heating steam inlet 42b is configured as a cooling fluid inlet.
  • the arrows indicating the flow direction in FIGS. 15 and 19 are all reversed. It goes without saying that it will be oriented.
  • FIGS. 22 to 25 show a third embodiment.
  • the plate-type heat exchange in the third embodiment includes a plurality of first heat transfer plates 62 that are rectangular with a relatively thin metal plate, and a rectangular shape with a relatively thin metal plate.
  • a plurality of heat transfer plates (63) are sandwiched between a first heat transfer plate (62) and a second heat transfer plate (63), and a sealing body (65) is formed to form a first heat exchange chamber (64).
  • the seal body 67 for forming the second heat exchange chamber 66 is sandwiched between them, and this laminated body is attached to a face plate 68 disposed on one end face thereof.
  • a face plate 69 disposed on the other end face is fastened to each other with bolts 70, and is configured.
  • Each of the heat transfer plates 62, 63 has a horizontally long steam outlet 71 communicating with the inside of each of the first heat exchange chambers 64 at the substantially central portion on the upper side thereof or in the vicinity thereof.
  • a heating fluid inlet 72a such as hot water communicating with the inside of each of the second heat exchange chambers 66 is provided at one of the corners or in the vicinity thereof, and each of the second heat exchange chambers is provided at or near the other corner.
  • a heating fluid outlet 72b communicating with each other is formed, and the steam outlet 71, the heating fluid inlet 72a, and the heating fluid outlet 72b are provided on one or both of the double-sided plates 68 and 69. It is open.
  • the steam outlet 71 may be provided in a part of the upper side.
  • the heat transfer plates 62, 63 are provided with evaporative liquid inlets 73a, 73b communicating with the first heat exchange chambers 64 at or near the left and right corners of the lower side thereof.
  • the two liquid-evaporated liquid inlets 73a and 73b are also open to one or both of the double-sided plates 68 and 69.
  • the liquid to be evaporated supplied from the both liquid inlets 73a and 73b into each first heat exchange chamber 64 is transferred to the heat from the second heat exchange chamber 66 on both sides. As a result, it is heated and boiled.
  • the evaporated vapor is discharged from the first heat exchange chamber 64 through the vapor outlet 71 together with a part of the liquid to be evaporated (brine) that has not evaporated.
  • the heating fluid supplied from the heating fluid inlet 72a into each of the second heat exchange chambers 66 transfers heat to the first heat exchange chamber 64 on both sides, and then the heating fluid. It is discharged from outlet 72b.
  • the first heat transfer plate 62 of the heat transfer plates 62, 63 includes the first heat transfer plate 62, as in the second embodiment.
  • Plate 62 For example, a plurality of raised portions 75 extending in a mountain shape in the vertical direction are arranged in parallel at appropriate intervals on the surface (surface) looking into the first heat exchange chamber 64, and the first heat transfer plate 62 is For example, a plurality of ridges 76 extending in a mountain range in the lateral direction are arranged in parallel at appropriate intervals on the surface (back surface) looking into the second heat exchange chamber 66.
  • the second heat transfer plate 63 has the second heat transfer plate as shown in FIG. 25, as in the second embodiment.
  • the second heat transfer plate 63 is arranged in parallel at an appropriate interval in accordance with the arrangement of the portions 76, and the second heat transfer plate 63 is formed on the surface (back surface) that is viewed in the second heat exchange chamber 66, for example, in a mountain range in the lateral direction.
  • a plurality of extending ridges 78 are arranged in parallel at appropriate intervals according to the arrangement of the mountainous ridges 76 on the back surface of the first heat transfer plate 62.
  • Each of the mountainous ridges 75, 76, 77, 78 is formed by bulging and deforming a part of the heat transfer plate.
  • first heat exchange chamber 64 in the portion between the mountain-shaped ridges 75 and 77 that are in contact with each other, for example, in the vertical direction, that is, from both the vaporized liquid inlets 73a and 73b to the vapor outlet 71 A plurality of tunnel-like fluid passages 79 that extend in a direction crossing the opposite direction and open at both ends into the first heat exchange chamber 74 are formed in parallel.
  • the second heat exchange chamber 66 is configured such that the ridgeline of each mountain-shaped ridge 78 on the back surface of the second heat exchange chamber 66 is in contact with the long part (preferably the entire length).
  • the portion between the mountainous ridges 76 and 78 that are in contact with each other for example, in the lateral direction, that is, from the heating fluid inlet 72a to the heating fluid outlet 72b.
  • a plurality of tunnel-like fluid passages 80 extending in a direction transverse to the direction of force and having both ends open into the second heat exchange chamber 66 are formed in parallel.
  • each second heat exchange chamber 66 from the heating fluid inlet 72a is transferred into the second heat exchange chamber 66 on both sides of the heat transfer plate.
  • 62, 63 which are formed by the respective mountainous ridges 76, 78, flow into the respective tunnel-like fluid passages 80, and flow through the tunnel-like fluid passages 80 in the direction in which the pressure loss becomes the lowest.
  • the second heat is applied from the heating fluid inlet 72a to the heating fluid outlet 72b with respect to the direction of the direction of force, for example, in the direction crossing this.
  • the liquid to be evaporated flowing into the first heat exchange chambers 64 from both the vaporized liquid inlets 73 a and 73 b is transferred from the second heat exchange chamber 66. While boiling and condensing by heating, the heat transfer process on both sides of the first heat exchange chamber 64 Flows into the tunnel-like fluid passages 79 formed by the mountainous ridges 75 and 77 at the gates 62 and 63, and the tunnel-like fluid passages 79 cause the pressure loss to become the lowest. As shown by the arrows in FIG. 24, the flow from both the liquid inlets 73a, 73b to the vapor outlet 71 is directed to the direction of the force, for example, the direction across the direction, etc. By being guided so as to spread throughout the first heat exchange chamber 64, it is possible to reliably reduce the stagnation of the flow in the first heat exchange chamber 64 and the second heat exchange chamber 66.
  • the above-described vertical mountain-shaped ridges 75 and 77 on the front side and the horizontal mountain-shaped ridges 76 and 78 on the back side are shown in the figure.
  • the vertical mountainous ridges 75, 77 are the same as in the first embodiment.
  • each mountain-shaped ridge on both the front and back surfaces of each first heat transfer plate 62 and each mountain on both front and back surfaces of each second heat transfer plate 63 are also described.
  • a herringbone pattern can be formed as a whole.
  • each of the mountainous ridges is connected to each heat transfer plate.
  • it may be configured separately from the heat transfer plate and fixed to each heat transfer plate by welding or the like.
  • the plate-type heat exchanger 61 is used as an evaporator.
  • the plate-type heat exchanger 61 is used as a steam condenser. be able to.
  • the steam outlet 71 is a steam inlet
  • the liquid supply ports 73a and 73b are condensed water outlets
  • the heating fluid inlet 72a is a cooling fluid inlet
  • the heating fluid outlet 72b is configured as a cooling fluid outlet.
  • the heating fluid inlet 72a into the second heat exchange chamber 66 is connected to the evaporative liquid supply port 7 from one corner on the upper side of the rectangle to one corner on the lower side. 3a, the heating fluid outlet 72b from the second heat exchange chamber 66 is moved to one corner of the upper side of the rectangle, while the second heat exchange chamber 66 is swept.
  • a partition portion 6 that integrally extends inwardly from the spacer body 67, a folded flow passage is formed by directing force from the fluid heating fluid inlet 72a to the heating fluid outlet 72b.
  • a plurality of tunnel-like fluid passages 80 are formed in the mountain-shaped ridges 76 and 78 in the folded flow passage, as in the third embodiment. ! What is it! /.
  • the flow resistance can be lowered by extending along the upper side of the steam outlet 71 on the upper side of the rectangle to the other corner of the upper side, while the second heat exchange is performed.
  • Heat transfer in the chamber 66 is caused to spread the heating fluid throughout the second heat exchange chamber 66 by forming a folded flow path by the partition 6.
  • it can be greatly accelerated, so the processing capacity for evaporation or condensation can be increased. It is particularly suitable when non-condensable liquid is used as the heating fluid.
  • the plate heat exchanger 61 can be configured as shown in FIG. 28 and FIG.
  • a plurality of tunnel-like fluid passages 80 are formed in each of the mountain-like ridges 76 and 78 in the two flow passages as in the third embodiment. Needless to say.
  • the flow resistance is reduced along the upper side of the steam outlet 71 to the other corner of the upper side.
  • heat transfer in the second heat exchange chamber 66 can be promoted by forming two flow passages by the partition 67 ⁇ , so that the processing capacity for evaporation or condensation can be increased. It is particularly suitable when steam is used as the heating fluid.
  • a tunnel-like fluid passage 80 for the heating fluid is provided in the second heat exchange chamber 66.
  • the mountainous ridges 76 and 78 are divided by a partition section 6 and 67 mm extending integrally from the spacer body 67, so that the partition section Needless to say, 67 ⁇ and 67 "can be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L’invention concerne un échangeur thermique à plaque formé par empilement d’une pluralité de plaques de transfert thermique (2) et (3) de façon à constituer entre celles-ci, de manière alternée, une première chambre d’échange thermique (4) générant ou condensant de la vapeur et une seconde chambre d’échange thermique (6) réchauffant ou refroidissant la vapeur. Des passages de fluide en forme de tunnel (19) et (20) formés pour s’étendre le long des plaques de transfert thermique (2) et (3) sont formés dans la première chambre d’échange thermique (4) et la seconde chambre d’échange thermique (6) pour que leurs deux extrémités puissent s’ouvrir vers l’intérieur des chambres d’échange thermique. Ainsi, les parties stagnantes des écoulements de fluide dans les chambres d’échange thermique (4) et (6) peuvent être réduites pour augmenter la capacité d’échange thermique tout en réduisant la taille et le poids de l’échangeur thermique de même que l’apparition de calamine.
PCT/JP2006/300423 2005-01-18 2006-01-16 Échangeur thermique à plaque WO2006077785A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN2006800013753A CN101137882B (zh) 2005-01-18 2006-01-16 板型热交换器
JP2006536990A JP4321781B2 (ja) 2005-01-18 2006-01-16 プレート型熱交換器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005010833 2005-01-18
JP2005-010833 2005-01-18

Publications (1)

Publication Number Publication Date
WO2006077785A1 true WO2006077785A1 (fr) 2006-07-27

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JP (1) JP4321781B2 (fr)
KR (1) KR20070100705A (fr)
CN (1) CN101137882B (fr)
TW (1) TWI371568B (fr)
WO (1) WO2006077785A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010013608A1 (fr) * 2008-07-29 2010-02-04 株式会社ササクラ Échangeur de chaleur à plaque utilisé comme évaporateur ou condenseur
JP2011149667A (ja) * 2010-01-25 2011-08-04 Mitsubishi Electric Corp プレート式熱交換器
JP2012154594A (ja) * 2011-01-28 2012-08-16 Mitsubishi Electric Corp プレート熱交換器及びその製造方法
JP2013142485A (ja) * 2012-01-10 2013-07-22 Hisaka Works Ltd プレート式熱交換器
CN105339753A (zh) * 2013-06-26 2016-02-17 三电控股株式会社 蓄冷材料容器

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT12048U1 (de) * 2010-03-23 2011-09-15 Stefan Ing Petters Vorrichtung zur übertragung von wärme
CN105403083B (zh) * 2015-12-30 2017-08-29 北京瑞宝利热能科技有限公司 一种具备蜂巢式海水换热器的海水源热泵***
CN106288886A (zh) * 2016-10-14 2017-01-04 陈琛 单片气体换热器

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JPS57137972U (fr) * 1981-02-20 1982-08-28
JPH09299927A (ja) * 1996-05-14 1997-11-25 Sasakura Eng Co Ltd プレート式造水装置
JP2000193390A (ja) * 1998-12-25 2000-07-14 Daikin Ind Ltd プレ―ト式熱交換器
JP2004517292A (ja) * 2001-01-04 2004-06-10 アルファ・ラバル・コーポレイト・エービー 伝熱プレート、プレートパックおよびプレート熱交換器

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SE505225C2 (sv) * 1993-02-19 1997-07-21 Alfa Laval Thermal Ab Plattvärmeväxlare och platta härför

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Publication number Priority date Publication date Assignee Title
JPS57137972U (fr) * 1981-02-20 1982-08-28
JPH09299927A (ja) * 1996-05-14 1997-11-25 Sasakura Eng Co Ltd プレート式造水装置
JP2000193390A (ja) * 1998-12-25 2000-07-14 Daikin Ind Ltd プレ―ト式熱交換器
JP2004517292A (ja) * 2001-01-04 2004-06-10 アルファ・ラバル・コーポレイト・エービー 伝熱プレート、プレートパックおよびプレート熱交換器

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010013608A1 (fr) * 2008-07-29 2010-02-04 株式会社ササクラ Échangeur de chaleur à plaque utilisé comme évaporateur ou condenseur
JP2011149667A (ja) * 2010-01-25 2011-08-04 Mitsubishi Electric Corp プレート式熱交換器
JP2012154594A (ja) * 2011-01-28 2012-08-16 Mitsubishi Electric Corp プレート熱交換器及びその製造方法
JP2013142485A (ja) * 2012-01-10 2013-07-22 Hisaka Works Ltd プレート式熱交換器
CN105339753A (zh) * 2013-06-26 2016-02-17 三电控股株式会社 蓄冷材料容器
CN105339753B (zh) * 2013-06-26 2017-06-30 三电控股株式会社 蓄冷材料容器

Also Published As

Publication number Publication date
JPWO2006077785A1 (ja) 2008-08-21
KR20070100705A (ko) 2007-10-11
CN101137882A (zh) 2008-03-05
JP4321781B2 (ja) 2009-08-26
CN101137882B (zh) 2011-05-11
TW200630582A (en) 2006-09-01
TWI371568B (en) 2012-09-01

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