JPH0972685A - Plate type heat exchanger - Google Patents
Plate type heat exchangerInfo
- Publication number
- JPH0972685A JPH0972685A JP22938595A JP22938595A JPH0972685A JP H0972685 A JPH0972685 A JP H0972685A JP 22938595 A JP22938595 A JP 22938595A JP 22938595 A JP22938595 A JP 22938595A JP H0972685 A JPH0972685 A JP H0972685A
- Authority
- JP
- Japan
- Prior art keywords
- plate
- heat exchanger
- passage hole
- lateral direction
- corners
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
Classifications
-
- 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
- F28F3/042—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 in the form of local deformations of the element
- F28F3/046—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 in the form of local deformations of the element the deformations being linear, e.g. corrugations
-
- 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
- F28D9/0031—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 paired plates touching each other
- F28D9/0043—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、四隅に液の出入口
となる通路孔を設けた複数枚のプレートを積層してなる
プレート式熱交換器に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate heat exchanger in which a plurality of plates each having a passage hole serving as a liquid inlet / outlet at four corners are laminated.
【0002】[0002]
【従来の技術】一般に、プレート式熱交換器は、複数枚
のプレートをガスケットを介して積層してプレート相互
間に複数の流路を形成し、これら流路に異種の液を交互
に流通して両液間でプレートを介して熱交換を行なって
いる。2. Description of the Related Art Generally, in a plate heat exchanger, a plurality of plates are laminated with a gasket interposed therebetween to form a plurality of flow paths between the plates, and different kinds of liquids are alternately flowed through these flow paths. Heat is exchanged between the two liquids through the plate.
【0003】このようなプレート式熱交換器において
は、図3に示す如き、プレート(11)が使用されてい
る。このプレート(11)は、矩形状金属板の四隅に液の
出入口となる通路孔(12)を設け、その中間に凹凸形状
をした伝熱面(13)を設けたもので、一側上下の通路孔
(12)(12)を伝熱面(13)と連通し、かつ、他側上下
の通路孔(12)(12)を伝熱面(13)と2重に遮断する
ように合成ゴム等の耐熱性を有する弾性材から製作され
たガスケット(14)を装着し、これを交互に平面上で1
80°回転させて、即ち、上下反転させて積層すること
により複数の流路を有するプレート式熱交換器を形成し
ている。In such a plate heat exchanger, a plate (11) as shown in FIG. 3 is used. This plate (11) is provided with passage holes (12) serving as liquid inlets and outlets at four corners of a rectangular metal plate, and an uneven heat transfer surface (13) provided in the middle thereof. Synthetic rubber so that the passage holes (12) (12) communicate with the heat transfer surface (13) and the passage holes (12) (12) above and below the other side are doubly blocked from the heat transfer surface (13). Install a gasket (14) made of a heat-resistant elastic material such as
The plate heat exchanger having a plurality of flow paths is formed by rotating by 80 °, that is, by inverting and stacking.
【0004】[0004]
【発明が解決しようとする課題】ところで、この種のプ
レート式熱交換器においては、処理流量が大きい場合に
は、通路孔(12)での流速に限界があるため、通路孔
(12)の開口面積を大きく設計する必要がある。ところ
が、従来のプレート式熱交換器は、プレート(11)の通
路孔(12)の平面形状が円形であるため、通路孔(12)
の開口面積を大きくするためには、図4に示すように、
通路孔(12)の径を大きくしなければならない。しか
し、通路孔(12)の径を大きくすれば、通路孔(12)の
縦寸法も必然的に大きくなり、図4に示すように、同じ
寸法のプレート素材を用いても、伝熱面(13)の縦方向
の寸法が減少するため、通路孔(12)の径が小さい図3
に示すプレート(11)に比べ伝面収率(素材面積に対す
る伝熱面積の割合)が大幅に低下する。そのため、必要
とする伝熱面積を確保するためには、プレート(11)の
枚数を増枚しなければならず、コストの増大につながる
という問題があった。By the way, in this type of plate heat exchanger, when the processing flow rate is large, the flow velocity in the passage hole (12) is limited. It is necessary to design the opening area to be large. However, in the conventional plate heat exchanger, since the planar shape of the passage hole (12) of the plate (11) is circular, the passage hole (12)
In order to increase the opening area of, as shown in FIG.
The diameter of the passage hole (12) must be increased. However, if the diameter of the passage hole (12) is increased, the vertical dimension of the passage hole (12) is inevitably increased. As shown in FIG. 4, even if a plate material having the same size is used, the heat transfer surface ( Since the vertical dimension of 13) is reduced, the diameter of the passage hole (12) is small.
The surface yield (ratio of heat transfer area to material area) is significantly lower than that of the plate (11). Therefore, in order to secure the required heat transfer area, it is necessary to increase the number of plates (11), which leads to an increase in cost.
【0005】そこで、斯かる問題を解決するため、図5
に示すように、プレート(11)の四隅に縦方向(プレー
ト両側周縁と平行方向)よりも横方向(プレート上下周
縁と平行方向)で大きな開口寸法を有する長円形の通路
孔(12)を設けている。これでは、長円形の通路孔(1
2)の縦寸法が図3に示した円形の通路孔(12)と同じ
であるが、幅寸法が大きいため、伝熱面(13)の縦方向
の寸法を減少させずに大きな開口面積を確保することが
できる。これにより、大きな処理流量に対応できるとと
もに、伝面収率の低下を防ぐことが可能である。しか
し、長円形の通路孔(12)の長手の中心線が横方向に配
置されているため、通路孔(12)の縁からプレート(1
1)の周縁に至るプレート周縁部(15)に幅の狭い部分
(S)が長いスパン(P)にわたって存在する。そのた
め、プレート周縁部(15)の機械的強度が著しく低下し
てプレート(11)の取扱い上で損傷を引起こすととも
に、このプレート(11)に大きな内圧がかかった場合に
は、長いスパン(P)にわたって存在するプレート周縁
部(15)の幅の狭い部分(S)が変形してシール性能の
低下を招く問題があった。Therefore, in order to solve such a problem, FIG.
As shown in FIG. 5, elliptical passage holes (12) having a larger opening size in the lateral direction (parallel to the upper and lower peripheral edges of the plate) are provided at the four corners of the plate (11) than in the vertical direction (parallel direction to both peripheral edges of the plate). ing. This is an oval passage hole (1
The vertical dimension of 2) is the same as the circular passage hole (12) shown in FIG. 3, but the large width dimension allows a large opening area without reducing the vertical dimension of the heat transfer surface (13). Can be secured. As a result, it is possible to cope with a large processing flow rate and prevent a decrease in surface yield. However, since the longitudinal center line of the oblong passage hole (12) is arranged laterally, the plate (1
A narrow portion (S) exists over a long span (P) in the plate peripheral portion (15) reaching the peripheral edge of (1). Therefore, the mechanical strength of the plate peripheral portion (15) is remarkably reduced, causing damage in handling the plate (11), and when a large internal pressure is applied to the plate (11), a long span (P ), There is a problem that the narrow portion (S) of the plate peripheral portion (15) existing over the entire area is deformed and the sealing performance is degraded.
【0006】本発明は、プレート周縁部の強度向上と伝
面収率の向上を両立させることを目的とする。An object of the present invention is to improve the strength of the peripheral portion of the plate and the yield of the transmission surface at the same time.
【0007】[0007]
【課題を解決するための手段】前述した目的を達成する
ために、本発明は、プレートの四隅に設けられた通路孔
の平面形状が縦方向よりも横方向で大きな開口寸法を有
する長円形あるいは概長円形であって、その長手の中心
線が横方向に対して任意の角度で回転して配置されてい
る。In order to achieve the above-mentioned object, the present invention provides an oval shape in which the planar shape of the passage holes provided at the four corners of the plate has a larger opening dimension in the horizontal direction than in the vertical direction. It has a substantially oval shape, and its longitudinal center line is arranged so as to rotate at an arbitrary angle with respect to the lateral direction.
【0008】本発明によれば、プレートの四隅に設けら
れた通路孔の平面形状を縦方向よりも横方向で大きな開
口寸法を有する長円形あるいは概長円形にするととも
に、その長手の中心線を横方向に対して任意の角度で回
転して配置させているから、大きな処理流量を確保しな
がら伝面収率を大幅に向上することができるととに、通
路孔の縁からプレートの周縁に至るプレート周縁部の幅
の狭い部分を少なくすることができる。According to the present invention, the planar shape of the passage holes provided at the four corners of the plate is made to be an oval or a substantially oval having a larger opening dimension in the lateral direction than in the longitudinal direction, and the longitudinal center line is Since it is rotated at an arbitrary angle with respect to the lateral direction, the transfer surface yield can be greatly improved while ensuring a large processing flow rate. It is possible to reduce the narrow portion of the peripheral edge of the plate.
【0009】[0009]
【発明の実施の形態】以下、本発明のプレート式熱交換
器を図面に示す実施の形態に基づいて説明する。BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a plate heat exchanger of the present invention will be described based on an embodiment shown in the drawings.
【0010】図1は本発明のプレート式熱交換器におい
て使用されるプレート(1)を示すものである。このプ
レート(1)は、矩形状金属板の四隅に液の出入口とな
る通路孔(2)を設け、この通路孔(2)の平面形状が
縦方向よりも横方向で大きな開口寸法を有する長円形で
あって、その長手の中心線が上側左右の通路孔(2)
(2)はプレート(1)の中央部から両側方に向って斜
降し、かつ、下側左右の通路孔(2)(2)はプレート
(1)の両側方から中央部に向って斜降するように横方
向に対して任意の角度で回転して配置されている。この
プレート(1)の中間には、凹凸形状をした伝熱面
(3)が設けられるとともに、一側上下の通路孔(2)
(2)を伝熱面(3)と連通し、かつ、他側上下の通路
孔(2)(2)を伝熱面(3)と2重に遮断するように
合成ゴム等の耐熱性を有する弾性材から製作されたガス
ケット(4)を装着している。FIG. 1 shows a plate (1) used in the plate heat exchanger of the present invention. This plate (1) is provided with passage holes (2) serving as liquid inlets and outlets at four corners of a rectangular metal plate, and the passage hole (2) has a planar shape having a larger opening dimension in the horizontal direction than in the vertical direction. It has a circular shape, and the center line of its length is the upper and left passage holes (2).
(2) slopes down from the center of the plate (1) toward both sides, and the lower left and right passage holes (2) and (2) slope down from both sides of the plate (1) toward the center. It is arranged by rotating at an arbitrary angle with respect to the lateral direction so as to descend. In the middle of the plate (1), a heat transfer surface (3) having an uneven shape is provided, and the passage holes (2) above and below one side are provided.
(2) is connected to the heat transfer surface (3), and heat resistance of synthetic rubber or the like is set so as to doubly block the upper and lower passage holes (2) and (2) from the heat transfer surface (3). The gasket (4) made of the elastic material is attached.
【0011】このようにプレート(1)の四隅に設けた
通路孔(2)の平面形状を縦方向よりも横方向で大きな
開口寸法を有する長円形としたことにより、図5に示し
た従来例とほぼ同等の伝面収率を確保することができ
る。即ち、大きな処理流量を確保するために伝面収率を
犠牲にして通路孔(12)の径を大きく設計していた図4
に示した従来例よりも同じ処理流量を確保しながら伝面
収率を大幅に向上させることが可能となった。As described above, the planar shape of the passage holes (2) provided at the four corners of the plate (1) is an elliptical shape having a larger opening size in the horizontal direction than in the vertical direction. It is possible to secure a surface transmission yield almost equal to That is, in order to secure a large processing flow rate, the diameter of the passage hole (12) is designed to be large at the sacrifice of the transmission surface yield.
As compared with the conventional example shown in (1), the surface treatment yield can be significantly improved while securing the same processing flow rate.
【0012】また、長円形の平面形状を有する通路孔
(2)をその長手の中心線を横方向に対して任意の角度
で回転させて配置することにより、図5に示した従来例
で問題となっていた長いスパン(P)にわたって存在し
ていたプレート周縁部(5)の幅の狭い部分(S)を少
なくすることができ、プレート周縁部(5)の機械的強
度を向上するとともに、大きな内圧でも変形しない構造
とすることできる。Further, by arranging the passage hole (2) having an elliptical plane shape by rotating the longitudinal center line at an arbitrary angle with respect to the lateral direction, there is a problem in the conventional example shown in FIG. It is possible to reduce the narrow portion (S) of the plate peripheral edge portion (5) existing over the long span (P), which improves the mechanical strength of the plate peripheral edge portion (5) and A structure that does not deform even under a large internal pressure can be provided.
【0013】さらに、図5に示した従来例に比べプレー
ト(1)の中央部に向っての通路孔(2)の断面ぬれ長
さ(L)が大きいため、液がプレート(1)の中央部に
流れ易くなり、これにより偏流が減少して伝熱性能の向
上が図れる。Further, since the cross-sectional wetting length (L) of the passage hole (2) toward the center of the plate (1) is larger than that of the conventional example shown in FIG. 5, the liquid is in the center of the plate (1). It becomes easier to flow to the part, and this reduces uneven flow and improves heat transfer performance.
【0014】図2は本発明の他の実施の形態を示すもの
で、プレート(1)の四隅に設けられた液の出入口とな
る長円形の平面形状を有する通路孔(2)の長手の中心
線を、図1に示した実施の形態とは逆の方向、即ち、上
側左右の通路孔(2)(2)はプレート(1)の両側方
から中央部に向って斜降し、かつ、下側左右の通路孔
(2)(2)はプレート(1)の中央部から両側方に向
って斜降するように横方向に対して任意の角度で回転さ
せたものであり、図1に示した実施の形態と同様の伝熱
収率や機械的強度向上効果を有する。FIG. 2 shows another embodiment of the present invention, in which the longitudinal center of the passage hole (2), which is provided at the four corners of the plate (1) and has an elliptical planar shape for the inlet and outlet of the liquid. The line is in the opposite direction to the embodiment shown in FIG. 1, that is, the upper and left passage holes (2) (2) descend from both sides of the plate (1) toward the center, and The lower left and right passage holes (2) (2) are rotated at an arbitrary angle with respect to the lateral direction so as to descend from the central portion of the plate (1) toward both sides. It has the same effect of improving the heat transfer yield and mechanical strength as the embodiment shown.
【0015】尚、以上の実施の形態では、通路孔(2)
の平面形状が長円形の場合について説明したが、通路孔
(2)の平面形状は概長円形でもよい。In the above embodiment, the passage hole (2) is used.
Although the planar shape of No. 2 has been described as an elliptical shape, the planar shape of the passage hole (2) may be approximately an elliptic shape.
【0016】[0016]
【発明の効果】以上説明したように、本発明によれば、
プレートの四隅に設けられた通路孔の平面形状を縦方向
よりも横方向で大きな開口寸法を有する長円形あるいは
概長円形にするとともに、その長手の中心線を横方向に
対して任意の角度で回転して配置させているから、大き
な処理流量を確保しながら伝面収率を大幅に向上するこ
とができるとともに、通路孔の縁からプレートの周縁に
至るプレート周縁部の幅の狭い部分を少なくすることが
でき、これによりプレート周縁部の機械的強度を向上し
て大きな内圧でも変形しない構造とすることできるとい
う優れた効果を有する。As described above, according to the present invention,
The planar shape of the passage holes provided at the four corners of the plate should be an ellipse or an approximately ellipse with a larger opening dimension in the lateral direction than in the vertical direction, and its longitudinal centerline should be at an arbitrary angle with respect to the lateral direction. Since they are placed in rotation, the transfer surface yield can be significantly improved while ensuring a large processing flow rate, and the narrow portion of the plate peripheral edge from the edge of the passage hole to the peripheral edge of the plate can be reduced. This has an excellent effect that the mechanical strength of the peripheral portion of the plate is improved and the structure does not deform even with a large internal pressure.
【0017】また、プレートの中央部に向っての通路孔
の断面ぬれ長さが大きいため、液がプレートの中央部に
流れ易くなり、偏流が減少して伝熱性能の向上が図れる
という優れた効果を有する。Also, since the cross-sectional wetting length of the passage hole toward the central portion of the plate is large, the liquid easily flows into the central portion of the plate, uneven flow is reduced, and heat transfer performance is improved. Have an effect.
【図1】本発明の実施の形態のプレート式熱交換器のプ
レートを示す平面図である。FIG. 1 is a plan view showing a plate of a plate heat exchanger according to an embodiment of the present invention.
【図2】本発明の他の実施の形態のプレート式熱交換器
のプレートを示す平面図である。FIG. 2 is a plan view showing a plate of a plate heat exchanger according to another embodiment of the present invention.
【図3】従来のプレート式熱交換器のプレートを示す平
面図である。FIG. 3 is a plan view showing a plate of a conventional plate heat exchanger.
【図4】従来のプレート式熱交換器のプレートを示す平
面図である。FIG. 4 is a plan view showing a plate of a conventional plate heat exchanger.
【図5】従来のプレート式熱交換器のプレートを示す平
面図である。FIG. 5 is a plan view showing a plate of a conventional plate heat exchanger.
1 プレート 2 通路孔 3 伝熱面 4 ガスケット 5 プレート周縁部 L 断面ぬれ長さ 1 Plate 2 Passage Hole 3 Heat Transfer Surface 4 Gasket 5 Plate Perimeter L Cross Section Wetting Length
Claims (1)
複数枚のプレートを積層してなるプレート式熱交換器に
おいて、 プレートの四隅に設けられた通路孔の平面形状が縦方向
よりも横方向で大きな開口寸法を有する長円形あるいは
概長円形であって、その通路孔の長手の中心線が横方向
に対して任意の角度で回転して配置されていることを特
徴とするプレート式熱交換器。1. A plate heat exchanger comprising a stack of a plurality of plates each having a passage hole serving as a liquid inlet / outlet at the four corners, wherein the passage holes provided at the four corners of the plate have a planar shape more than that in the vertical direction. A plate type characterized by being an oval or a substantially oval having a large opening size in the lateral direction, in which the longitudinal center line of the passage hole is arranged to rotate at an arbitrary angle with respect to the lateral direction. Heat exchanger.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22938595A JP3670725B2 (en) | 1995-09-06 | 1995-09-06 | Plate heat exchanger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22938595A JP3670725B2 (en) | 1995-09-06 | 1995-09-06 | Plate heat exchanger |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0972685A true JPH0972685A (en) | 1997-03-18 |
JP3670725B2 JP3670725B2 (en) | 2005-07-13 |
Family
ID=16891366
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP22938595A Expired - Fee Related JP3670725B2 (en) | 1995-09-06 | 1995-09-06 | Plate heat exchanger |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3670725B2 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2000022364A1 (en) * | 1998-10-15 | 2000-04-20 | Ebara Corporation | Plate type heat exchanger |
ES2234414A1 (en) * | 2003-09-24 | 2005-06-16 | Valeo Termico, S.A. | Heat exchanger, has multiple piled up plates arranged between two independent circuits, and contractions parts attached with entrance orifices and exit orifices, and sealing units equipped with reinforcement units |
WO2010106717A1 (en) | 2009-03-18 | 2010-09-23 | 三菱電機株式会社 | Plate-type heat exchanger and refrigerating air-conditioning device |
US8061416B2 (en) | 2003-08-01 | 2011-11-22 | Behr Gmbh & Co. Kg | Heat exchanger and method for the production thereof |
CN102261861A (en) * | 2011-07-16 | 2011-11-30 | 蓬莱市安源水产有限公司 | Plate-type heat exchanger and application thereof to mariculture |
CN103791760A (en) * | 2012-10-30 | 2014-05-14 | 阿尔法拉瓦尔股份有限公司 | Gasket and assembly |
CN103791756A (en) * | 2012-10-30 | 2014-05-14 | 阿尔法拉瓦尔股份有限公司 | Heat transfer plate and plate heat exchanger comprising such a heat transfer plate |
-
1995
- 1995-09-06 JP JP22938595A patent/JP3670725B2/en not_active Expired - Fee Related
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2000022364A1 (en) * | 1998-10-15 | 2000-04-20 | Ebara Corporation | Plate type heat exchanger |
US6681844B1 (en) | 1998-10-15 | 2004-01-27 | Ebara Corporation | Plate type heat exchanger |
US8061416B2 (en) | 2003-08-01 | 2011-11-22 | Behr Gmbh & Co. Kg | Heat exchanger and method for the production thereof |
ES2234414A1 (en) * | 2003-09-24 | 2005-06-16 | Valeo Termico, S.A. | Heat exchanger, has multiple piled up plates arranged between two independent circuits, and contractions parts attached with entrance orifices and exit orifices, and sealing units equipped with reinforcement units |
WO2010106717A1 (en) | 2009-03-18 | 2010-09-23 | 三菱電機株式会社 | Plate-type heat exchanger and refrigerating air-conditioning device |
CN102261861A (en) * | 2011-07-16 | 2011-11-30 | 蓬莱市安源水产有限公司 | Plate-type heat exchanger and application thereof to mariculture |
CN103791760A (en) * | 2012-10-30 | 2014-05-14 | 阿尔法拉瓦尔股份有限公司 | Gasket and assembly |
CN103791756A (en) * | 2012-10-30 | 2014-05-14 | 阿尔法拉瓦尔股份有限公司 | Heat transfer plate and plate heat exchanger comprising such a heat transfer plate |
JP2015532972A (en) * | 2012-10-30 | 2015-11-16 | アルファ−ラヴァル・コーポレート・アーベー | Heat exchanger flat plate and flat plate heat exchanger comprising such a heat exchanger flat plate |
KR20170000403A (en) * | 2012-10-30 | 2017-01-02 | 알파 라발 코포레이트 에이비 | Gasket and assembly |
US9759494B2 (en) | 2012-10-30 | 2017-09-12 | Alfa Laval Corporate Ab | Heat exchanger plate and plate heat exchanger comprising such a heat exchanger plate |
US9903668B2 (en) | 2012-10-30 | 2018-02-27 | Alfa Laval Corporate Ab | Gasket and assembly |
Also Published As
Publication number | Publication date |
---|---|
JP3670725B2 (en) | 2005-07-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8646517B2 (en) | Plate and gasket for plate heat exchanger | |
JP4981063B2 (en) | Means for plate heat exchangers | |
JP2003526070A (en) | Plate packing for heat transfer plates and plate heat exchangers | |
JP3654669B2 (en) | Plate heat exchanger | |
JPH0972685A (en) | Plate type heat exchanger | |
JPH04227480A (en) | Plate heat exchanger | |
JP3212350B2 (en) | Plate heat exchanger | |
JP3285243B2 (en) | Plate heat exchanger | |
JP3543992B2 (en) | Plate heat exchanger | |
JP3328329B2 (en) | Plate heat exchanger plate | |
JPH0989482A (en) | Plate-type heat exchanger | |
JPH07260385A (en) | Plate type heat exchanger | |
JP3751331B2 (en) | Plate structure of plate heat exchanger | |
JP2952261B2 (en) | Plate heat exchanger | |
EP1813901A2 (en) | Heat exchange plate | |
JP7278489B2 (en) | Gaskets and assemblies for plate heat exchangers | |
JPH0979782A (en) | Plate type heat exchanger | |
CN112146484B (en) | Plate heat exchanger | |
JP3543993B2 (en) | Plate heat exchanger | |
JPH07260384A (en) | Plate type heat exchanger | |
JP2001099583A (en) | Plate type heat exchanger | |
CN217504442U (en) | Heat exchanger | |
EP4290168A1 (en) | Heat exchanger | |
JP7432742B2 (en) | Heat exchanger | |
JPH01174895A (en) | Plate type heat exchanger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20050311 |
|
TRDD | Decision of grant or rejection written | ||
A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20050318 |
|
A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20050415 |
|
R150 | Certificate of patent (=grant) or registration of utility model |
Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080422 Year of fee payment: 3 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090422 Year of fee payment: 4 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090422 Year of fee payment: 4 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100422 Year of fee payment: 5 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100422 Year of fee payment: 5 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110422 Year of fee payment: 6 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120422 Year of fee payment: 7 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130422 Year of fee payment: 8 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130422 Year of fee payment: 8 |
|
FPAY | Renewal fee payment (prs date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20140422 Year of fee payment: 9 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
LAPS | Cancellation because of no payment of annual fees |