JP5958783B1 - Rotary dryer with improved drying capacity and safety - Google Patents
Rotary dryer with improved drying capacity and safety Download PDFInfo
- Publication number
- JP5958783B1 JP5958783B1 JP2015141725A JP2015141725A JP5958783B1 JP 5958783 B1 JP5958783 B1 JP 5958783B1 JP 2015141725 A JP2015141725 A JP 2015141725A JP 2015141725 A JP2015141725 A JP 2015141725A JP 5958783 B1 JP5958783 B1 JP 5958783B1
- Authority
- JP
- Japan
- Prior art keywords
- heating fluid
- heat transfer
- small
- transfer tube
- pipe
- 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.)
- Active
Links
Landscapes
- Drying Of Solid Materials (AREA)
Abstract
【課題】加熱流体往き配管と加熱流体戻り配管の径は、フランジ形状により小さく限定されてしまい、配管の径が小さく限定されると、圧力損失が高くなり加熱流体の流量が制限され、伝熱管内における熱伝達係数が低くなるため乾燥能力が向上しない。加熱流体の循環に対して配管抵抗小さく、加熱流体の循環量が多く取れ、加熱流体が漏れにくい乾燥機を提供することが課題である。【解決手段】加熱流体供給口と加熱流体戻り口を配管接続部の同一面でなく別の面に設けたことを特徴とし、複数の配管接続部を１つにまとめ、加熱流体供給口または加熱流体戻り口を１つに集約したことを特徴として、配管抵抗を小さく外部漏れの危険性を低下させ、加熱流体の循環量を多くして、熱伝達係数を高めた回転式乾燥機。【選択図】図１The diameter of the heating fluid return pipe and the heating fluid return pipe is limited by the flange shape, and if the diameter of the piping is limited, the pressure loss increases and the flow rate of the heating fluid is limited, and heat transfer Since the heat transfer coefficient in the tube is low, the drying capacity is not improved. It is an object to provide a dryer that has a small piping resistance with respect to the circulation of the heating fluid, a large circulation amount of the heating fluid, and the heating fluid does not easily leak. A heating fluid supply port and a heating fluid return port are provided not on the same surface of a pipe connection portion but on different surfaces, and a plurality of pipe connection portions are integrated into one heating fluid supply port or heating. A rotary dryer that features a single fluid return port, reduces piping resistance, reduces the risk of external leakage, increases the circulation of heated fluid, and increases the heat transfer coefficient. [Selection] Figure 1
Description
本発明は、プラントや装置産業に用いる横型胴長の間接加熱による回転式乾燥機に関するものであり、乾燥能力と安全性を向上させたものである。 The present invention relates to a rotary dryer by indirect heating of a horizontal body length used in a plant or equipment industry, and improves drying capacity and safety.
従来、プラントや装置産業において湿潤製品等の乾燥対象物を乾燥させるために、ロータリーキルンと呼ばれる横型胴長の間接加熱による回転式乾燥機が用いられている。 2. Description of the Related Art Conventionally, in order to dry an object to be dried such as a wet product in the plant or equipment industry, a rotary dryer called indirect heating of a horizontal body length called a rotary kiln has been used.
横型胴長の間接加熱による回転式乾燥機の具体的な構造としては、例えば、乾燥機内部に伝熱管を設け、伝熱管に外部から熱を供給して湿潤製品等を乾燥させるものが知られている。このような伝熱管を用いる回転式乾燥機は、単位容積当たりの加熱面積が大きいため乾燥能力も大きく、かつ運転操作が容易等の利点が多いこともあり多用されている。 As a specific structure of the rotary dryer by indirect heating of the horizontal body length, for example, a heat transfer tube is provided inside the dryer, and heat is supplied to the heat transfer tube from the outside to dry wet products and the like. ing. A rotary dryer using such a heat transfer tube is frequently used because it has a large heating area per unit volume and thus has a large drying capacity and has many advantages such as easy operation.
伝熱管を用いる回転式乾燥機の構成及びこの回転式乾燥機を用いた乾燥対象物の乾燥処理方法は、一般的に以下のようになる。 The structure of a rotary dryer using a heat transfer tube and the drying treatment method of an object to be dried using this rotary dryer are generally as follows.
回転式乾燥機は長さが１０〜３０ｍ程の回転胴と呼ばれる本体からなり、回転胴にはフランジを介して内部に伝熱管が設けられる。
伝熱管は外部の加熱流体往きヘッダーから加熱流体を供給するための加熱流体往き配管と外部の加熱流体戻りヘッダーに加熱流体を戻すための加熱流体戻り配管が挿入され、加熱流体往き配管と加熱流体戻り配管の間には仕切るための仕切り板が設けられる。
The rotary dryer is composed of a main body called a rotary drum having a length of about 10 to 30 m, and the rotary drum is provided with a heat transfer tube inside through a flange.
The heat transfer pipe is inserted with a heating fluid return pipe for supplying heating fluid from an external heating fluid return header and a heating fluid return pipe for returning the heating fluid to an external heating fluid return header. A partition plate for partitioning is provided between the return pipes.
入口コンベヤーまで搬送されてきた乾燥対象物は回転式乾燥機に投入され、加熱流体により加熱された伝熱管に接触し、回転胴の緩やかな回転により徐々に乾燥しながら乾燥製品となり出口コンベヤーまで搬送される。
出口コンベヤーの外周には摺動部を有したマニホールドが設けられ、マニホールドには乾燥キャリアガスが供給され、供給された乾燥キャリアガスは入口コンベヤーに向かい、搬送されてきた乾燥製品は乾燥キャリアガスにより更に乾燥される。
出口コンベヤーまで搬送されてきた乾燥製品は移送ガスにより次の処理工程へ搬送される。
The object to be dried, which has been transported to the entrance conveyor, is put into a rotary dryer, contacts the heat transfer tube heated by the heated fluid, and is gradually dried by the rotating drum to be dried and transported to the exit conveyor. Is done.
A manifold having a sliding portion is provided on the outer periphery of the outlet conveyor, and a dry carrier gas is supplied to the manifold. The supplied dry carrier gas is directed to the inlet conveyor, and the dried product conveyed is dried by the dry carrier gas. It is further dried.
The dried product that has been transported to the outlet conveyor is transported to the next processing step by the transfer gas.
マニホールドには回転式乾燥機の外部に設けた加熱流体循環ポンプから加熱流体が供給され、供給された加熱流体は加熱流体往きヘッダーに供給される。かつマニホールドには加熱流体戻りヘッダーから加熱流体が戻り、戻った加熱流体は回転式乾燥機の外部に設けた加熱流体受け槽に戻る。
このように、加熱流体は加熱流体循環ポンプ、マニホールド、加熱流体往きヘッダー、伝熱管、加熱流体戻りヘッダー、マニホールド、加熱流体受け槽の間で循環される。
マニホールドは、乾燥キャリアガス、加熱流体往きヘッダーに供給される加熱流体及び加熱流体戻りヘッダーから戻る加熱流体のシール構造を有する。
A heating fluid is supplied to the manifold from a heating fluid circulation pump provided outside the rotary dryer, and the supplied heating fluid is supplied to a heating fluid going header. The heating fluid returns from the heating fluid return header to the manifold, and the returned heating fluid returns to the heating fluid receiving tank provided outside the rotary dryer.
Thus, the heating fluid is circulated between the heating fluid circulation pump, the manifold, the heating fluid forward header, the heat transfer pipe, the heating fluid return header, the manifold, and the heating fluid receiving tank.
The manifold has a sealing structure for dry carrier gas, heated fluid supplied to the heated fluid forward header, and heated fluid returning from the heated fluid return header.
伝熱管を用いる回転式乾燥機は、伝熱管を回転胴の内周に環状に設け、かつ回転胴の外周から中心に向けて徐々に径が小さくなるように同心円状に設けている（例えば、特許文献１参照）。 A rotary dryer using a heat transfer tube is provided with a heat transfer tube in an annular shape on the inner periphery of the rotary drum, and concentrically so that the diameter gradually decreases from the outer periphery of the rotary drum toward the center (for example, Patent Document 1).
前述のような従来の横型胴長の間接加熱による回転式乾燥機は以下の課題を有する。 The conventional rotary dryer by indirect heating of the horizontal body length as described above has the following problems.
加熱流体往き配管と加熱流体戻り配管の径は、それぞれの配管とフランジとの隅肉溶接の重なりを避けること、加熱流体往き配管と加熱流体戻り配管の間の仕切り板の寸法により、伝熱管の径の１／３相当になってしまう。
このため加熱流体往き配管と加熱流体戻り配管の径は、例えば公称１００Ａの伝熱管であれば公称２５Ａ、公称６５Ａまたは５０Ａの伝熱管であれば公称１５Ａのようになる。
これは、回転胴の外周から中心に向けて徐々に径が小さくなるように同心円状に設けたすべての伝熱管の加熱流体往き配管と加熱流体戻り配管に該当する。
加熱流体往き配管と加熱流体戻り配管の径が小さく限定されると、圧力損失が高くなり加熱流体の流量が制限される。
これにより伝熱管内の加熱流体の流動状況が層流に近い状態になり、伝熱管内における熱伝達係数が低くなるため乾燥能力が向上しない。
The diameter of the heating fluid return pipe and the heating fluid return pipe should be such that the overlap of fillet welds between the respective pipes and the flange should be avoided, and the size of the partition plate between the heating fluid return pipe and the heating fluid return pipe, It will be equivalent to 1/3 of the diameter.
For this reason, the diameters of the heating fluid return pipe and the heating fluid return pipe are, for example, nominally 25A for a nominal 100A heat transfer tube and nominally 15A for a nominal 65A or 50A heat transfer tube.
This corresponds to the heating fluid return piping and the heating fluid return piping of all the heat transfer tubes provided concentrically so that the diameter gradually decreases from the outer periphery to the center of the rotating drum.
When the diameters of the heating fluid return pipe and the heating fluid return pipe are limited to be small, the pressure loss increases and the flow rate of the heating fluid is limited.
As a result, the flow state of the heated fluid in the heat transfer tube becomes close to a laminar flow, and the heat transfer coefficient in the heat transfer tube is lowered, so that the drying capacity is not improved.
乾燥性能を向上させるために圧力損失分を見込んで圧力を高くすることも考えられるが、経済的な運用でないことに加え、マニホールドにおける乾燥キャリアガス、加熱流体往きヘッダーに供給される加熱流体及び加熱流体戻りヘッダーから戻る加熱流体の漏れが大きくなる可能性があるため危険を伴うことになる。
以上から、乾燥能力と安全性を向上させた回転式乾燥機を提供することが課題である。
In order to improve the drying performance, it is possible to increase the pressure in anticipation of the pressure loss, but in addition to not being economically operated, the drying carrier gas in the manifold, the heating fluid supplied to the heating fluid forward header and the heating This can be dangerous because the heated fluid return from the fluid return header can be leaking.
From the above, it is an object to provide a rotary dryer with improved drying capacity and safety.
前述の課題を解決するために、本発明に係る回転式乾燥機は以下の手段を有する。 In order to solve the above-described problems, the rotary dryer according to the present invention has the following means.
第１の手段として、内部に加熱流体配管を有した伝熱管と、加熱流体供給口及び加熱流体戻り口を有し伝熱管に連通される柱形状の配管接続部と、連通孔を有し伝熱管及び配管接続部に接続される隔壁から構成される加熱流体による回転式乾燥機において、加熱流体供給口と加熱流体戻り口を配管接続部の別の面に設けたことを特徴とする。 As a first means, a heat transfer pipe having a heating fluid pipe inside, a columnar pipe connection part having a heating fluid supply port and a heating fluid return port and communicating with the heat transfer pipe, and a communication hole are provided. In a rotary drier using a heating fluid composed of a heat pipe and a partition connected to a pipe connection portion, a heating fluid supply port and a heating fluid return port are provided on different surfaces of the pipe connection portion.
第２の手段として、複数の配管接続部を１つにまとめ、加熱流体供給口または加熱流体戻り口を１つに集約したことを特徴とする。 As a second means, a plurality of pipe connection portions are combined into one, and the heating fluid supply port or the heating fluid return port is integrated into one.
第３の手段として、伝熱管の内部に断面外側から中心に向かうまたは中心から断面外側に向かう加熱流体流量調整板を設けたことを特徴とする。 As a third means, a heating fluid flow rate adjustment plate is provided inside the heat transfer tube from the outer side of the cross section toward the center or from the center toward the outer side of the cross section.
本発明の請求項１に係る回転式乾燥機によれば、加熱流体往き配管と加熱流体戻り配管をフランジの同じ面でなく別の面に設けられるため、それぞれの配管の径を伝熱管の径の１／３相当から公称で１から２サイズ大きくすることができ、加熱流体往き配管と加熱流体戻り配管での圧力損失を低くすることが可能となる。
これにより伝熱管内の加熱流体の流動状況が乱流に近い状態になり、伝熱管内における熱伝達係数が高くなるため乾燥能力を向上させることが可能となる。かつマニホールドにおける乾燥キャリアガス、加熱流体往きヘッダーに供給される加熱流体及び加熱流体戻りヘッダーから戻る加熱流体の漏れを低くすることができ、安全性を向上させることが可能となる。
According to the rotary dryer according to claim 1 of the present invention, since the heating fluid forward piping and the heating fluid return piping are provided on different surfaces instead of the same surface of the flange, the diameter of each piping is set to the diameter of the heat transfer tube. Therefore, it is possible to reduce the pressure loss in the heated fluid forward piping and the heated fluid return piping.
As a result, the flow state of the heating fluid in the heat transfer tube becomes a state close to turbulent flow, and the heat transfer coefficient in the heat transfer tube becomes high, so that the drying capacity can be improved. In addition, it is possible to reduce the leakage of the dry carrier gas in the manifold, the heating fluid supplied to the heating fluid forward header, and the heating fluid returning from the heating fluid return header, and the safety can be improved.
本発明の請求項２に係る回転式乾燥機によれば、加熱流体往き配管または加熱流体戻り配管が不要となるため、マニホールド以外でも加熱流体往き配管または加熱流体戻り配管の接続箇所における加熱流体の漏れを低くすることができ、請求項１に係る回転式乾燥機の効果に加えて更に安全性を向上させることが可能となる。かつ構造がシンプルとなり運用や維持が容易となる。 According to the rotary dryer according to claim 2 of the present invention, since the heating fluid forward piping or the heating fluid return piping is not necessary, the heating fluid at the connection portion of the heating fluid forward piping or the heating fluid return piping other than the manifold is not provided. Leakage can be reduced, and the safety can be further improved in addition to the effect of the rotary dryer according to claim 1. In addition, the structure is simple and easy to operate and maintain.
本発明の請求項３に係る回転式乾燥機によれば、伝熱管の内部に設けた加熱流体流量調整板により、回転胴の外周から中心に向けて徐々に径が小さくなるように同心円状に設けた伝熱管のそれぞれの径に応じて加熱流体の流量を調節することができ、請求項２に係る回転式乾燥機の効果に加えて更に乾燥能力を向上させることが可能となる。かつ運用が容易となる。 According to the rotary dryer according to claim 3 of the present invention, the heating fluid flow rate adjusting plate provided inside the heat transfer tube is concentrically formed so that the diameter gradually decreases from the outer periphery to the center of the rotating drum. The flow rate of the heating fluid can be adjusted according to the diameter of each of the provided heat transfer tubes, and in addition to the effect of the rotary dryer according to claim 2, it is possible to further improve the drying capacity. And operation becomes easy.
以下、本発明に係る回転式乾燥機の実施形態を図１〜１１に基づいて説明する。 Hereinafter, an embodiment of a rotary dryer according to the present invention will be described with reference to FIGS.
尚、本記載は特許請求の範囲を示した例であり、特許請求の範囲を本記載に限定することを意味するものではない。 In addition, this description is an example which showed the claim, and does not mean limiting a claim to this description.
最初に、従来技術における回転式乾燥機を図６〜１１に基づいて説明する。
図６は従来技術における回転式乾燥機の断面図を含む湿潤製品の乾燥処理系統図である。
Initially, the rotary dryer in a prior art is demonstrated based on FIGS.
FIG. 6 is a schematic diagram of a wet product drying process including a sectional view of a rotary dryer according to the prior art.
本発明に係る回転式乾燥機１の乾燥対象物である湿潤製品２００は、湿潤製品供給源１００Ａから湿潤製品供給配管１００Ｂにより入口コンベヤー１００に搬送されて、回転式乾燥機１に投入される。
湿潤製品２００から分離された湿潤キャリアガス２０１は、湿潤キャリアガス配管１１０Ｂによりスクラバーポンプ１１０Ａで駆動するスクラバー１１０に供給される。
The wet product 200 that is the object to be dried by the rotary dryer 1 according to the present invention is conveyed from the wet product supply source 100A to the inlet conveyor 100 through the wet product supply pipe 100B, and is put into the rotary dryer 1.
The wet carrier gas 201 separated from the wet product 200 is supplied to the scrubber 110 driven by the scrubber pump 110A through the wet carrier gas pipe 110B.
回転式乾燥機１は長さが１０〜３０ｍ程で円筒形状の回転胴２と呼ばれる本体からなり、回転胴２には内部に伝熱管（大）３が設けられる。
回転胴２は、入口コンベヤー１００から出口コンベヤー１２０に向けて緩やかな下り勾配を有する。
伝熱管（大）３は後述する外部の加熱流体往きヘッダー８からの加熱流体の供給により加熱され、伝熱管（大）３に接触した湿潤製品２００は徐々に乾燥する。
加熱流体は伝熱管（大）３に挿入された加熱流体配管３Ａにより、後述する外部の加熱流体戻りヘッダー９に戻る。
回転胴２は、モーター１０の力が減速機１０Ａ、ピニオンギヤー１０Ｂ及びガウスギヤー１０Ｃにより伝えられることで緩やかに回転する。なお回転胴２の外周には回転胴２の自重を支え回転がスムーズになるように、タイヤローラー１０Ｄ及び受けローラー１０Ｅが設けられる。
湿潤製品２００は加熱流体及び回転胴２の緩やかな回転により、徐々に乾燥しながら乾燥製品２０４となり出口コンベヤー１２０まで搬送される。
The rotary dryer 1 has a length of about 10 to 30 m and includes a main body called a cylindrical rotary drum 2, and the rotary drum 2 is provided with a heat transfer tube (large) 3 therein.
The rotary drum 2 has a gentle downward slope from the entrance conveyor 100 toward the exit conveyor 120.
The heat transfer tube (large) 3 is heated by the supply of a heating fluid from an external heating fluid forward header 8 to be described later, and the wet product 200 in contact with the heat transfer tube (large) 3 is gradually dried.
The heating fluid is returned to an external heating fluid return header 9 described later by a heating fluid pipe 3 </ b> A inserted in the heat transfer pipe (large) 3.
The rotating drum 2 rotates gently when the force of the motor 10 is transmitted by the speed reducer 10A, the pinion gear 10B, and the Gauss gear 10C. A tire roller 10D and a receiving roller 10E are provided on the outer periphery of the rotating drum 2 so as to support the weight of the rotating drum 2 and to make the rotation smooth.
The wet product 200 becomes a dry product 204 while being gradually dried by the heated fluid and the gentle rotation of the rotary drum 2, and is conveyed to the outlet conveyor 120.
スクラバー１１０に供給された湿潤キャリアガス２０１は乾燥キャリアガス２０２と回収液２０３に分離される。
乾燥キャリアガス２０２は乾燥キャリアガス配管１１０Ｃにより出口コンベヤー１２０の外周に設けたマニホールド１３０に供給され、回収液２０３は回収液配管１１０Ｄにより図示しないタンク等の回収設備へ移送される。
The wet carrier gas 201 supplied to the scrubber 110 is separated into a dry carrier gas 202 and a recovered liquid 203.
The dry carrier gas 202 is supplied to the manifold 130 provided on the outer periphery of the outlet conveyor 120 through the dry carrier gas pipe 110C, and the recovered liquid 203 is transferred to a recovery facility such as a tank (not shown) through the recovered liquid pipe 110D.
マニホールド１３０に供給された乾燥キャリアガス２０２は、回転胴２の内部を入口コンベヤー１００に向かい流れる。これにより湿潤製品２００は更に乾燥しながら乾燥製品２０４となり出口コンベヤー１２０まで搬送される。
このため乾燥キャリアガス２０２は回転胴２の内部を入口コンベヤー１００に向かい流れるにつれて湿潤製品２００が有する湿分を徐々に含むようになり、湿潤キャリアガス２０１となる。回転胴２の内部を流れる湿潤キャリアガス２０１は湿潤キャリアガス配管１１０Ｂによりスクラバー１１０に供給される。
このように、湿潤キャリアガス２０１及び乾燥キャリアガス２０２はスクラバー１１０、マニホールド１３０及び伝熱管（大）３の間で循環される。
The dry carrier gas 202 supplied to the manifold 130 flows toward the inlet conveyor 100 inside the rotary drum 2. As a result, the wet product 200 becomes a dry product 204 while being further dried, and is conveyed to the outlet conveyor 120.
For this reason, the dry carrier gas 202 gradually contains moisture contained in the wet product 200 as it flows toward the inlet conveyor 100 through the rotary drum 2, and becomes the wet carrier gas 201. The wet carrier gas 201 flowing inside the rotary drum 2 is supplied to the scrubber 110 through the wet carrier gas pipe 110B.
As described above, the wet carrier gas 201 and the dry carrier gas 202 are circulated between the scrubber 110, the manifold 130 and the heat transfer tube (large) 3.
出口コンベヤー１２０まで搬送されてきた乾燥製品２０４は、ロータリーバルブ１２０Ａを介してニューマ配管１２０Ｂに供給され、移送ガス２０５により図示しない次の処理工程へ搬送される。 The dried product 204 that has been transported to the outlet conveyor 120 is supplied to the pneumatic piping 120B via the rotary valve 120A, and is transported to the next processing step (not shown) by the transfer gas 205.
マニホールド１３０は外部の加熱流体循環ポンプ１４０から加熱流体往き配管１４０Ｂにより加熱流体往き２０６が供給され、加熱流体往き２０６は加熱流体往き配管１３０Ａにより後述する加熱流体往きヘッダー８に供給される。かつマニホールド１３０には後述する加熱流体戻りヘッダー９から加熱流体戻り配管１３０Ｂにより加熱流体戻り２０７が戻り、加熱流体戻り２０７は加熱流体戻り配管１４０Ｃにより外部の加熱流体受け槽１４０Ａに戻る。
このように、加熱流体は加熱流体循環ポンプ１４０、マニホールド１３０、加熱流体往きヘッダー８、伝熱管（大）３、加熱流体戻りヘッダー９、マニホールド１３０及び加熱流体受け槽１４０Ａの間で循環される。
The manifold 130 is supplied with a heating fluid forward 206 from an external heating fluid circulation pump 140 through a heating fluid forward piping 140B, and the heating fluid forward 206 is supplied through a heating fluid forward piping 130A to a heating fluid forward header 8 described later. And the heating fluid return 207 is returned to the manifold 130 by the heating fluid return pipe 130B from the heating fluid return header 9 described later, and the heating fluid return 207 is returned to the external heating fluid receiving tank 140A by the heating fluid return pipe 140C.
Thus, the heating fluid is circulated among the heating fluid circulation pump 140, the manifold 130, the heating fluid forward header 8, the heat transfer pipe (large) 3, the heating fluid return header 9, the manifold 130, and the heating fluid receiving tank 140A.
マニホールド１３０は摺動部を有しており、乾燥キャリアガス２０２、加熱流体循環ポンプ１４０から供給される加熱流体往き２０６、加熱流体往きヘッダー８に供給される加熱流体往き２０６、加熱流体戻りヘッダー９から戻る加熱流体戻り２０７及び加熱流体受け槽１４０Ａに戻る加熱流体戻り２０７のシール構造を有する。 The manifold 130 has a sliding portion, and includes a dry carrier gas 202, a heated fluid feed 206 supplied from the heated fluid circulation pump 140, a heated fluid feed 206 supplied to the heated fluid feed header 8, and a heated fluid return header 9. A heating fluid return 207 returning from the heating fluid and a heating fluid return 207 returning to the heating fluid receiving tank 140A are provided.
回転胴２の内部には伝熱管（大）３の他に、伝熱管（大）３よりも径が小さい伝熱管（小）３１が設けられる。
伝熱管（小）３１の構造及び作用は伝熱管（大）３と同じであり、加熱流体配管３Ａに相当する加熱流体配管３１Ａが挿入される。
伝熱管（大）３が回転胴２の内周に環状に設けられ、かつ回転胴２の外周から中心に向けて徐々に径が小さくなるように伝熱管（小）３１が同心円状に設けられる。
なお、伝熱管（大）３及び伝熱管（小）３１の配置については後述する。
In addition to the heat transfer tube (large) 3, a heat transfer tube (small) 31 having a smaller diameter than the heat transfer tube (large) 3 is provided inside the rotary drum 2.
The structure and action of the heat transfer tube (small) 31 are the same as those of the heat transfer tube (large) 3, and a heating fluid pipe 31A corresponding to the heating fluid pipe 3A is inserted.
A heat transfer tube (large) 3 is provided in an annular shape on the inner periphery of the rotating drum 2, and a heat transfer tube (small) 31 is provided concentrically so that the diameter gradually decreases from the outer periphery to the center of the rotating drum 2. .
In addition, arrangement | positioning of the heat exchanger tube (large) 3 and the heat exchanger tube (small) 31 is mentioned later.
図７は図６におけるＡ部拡大図である。
回転胴２には回転胴フランジ４Ａ、ガスケット４Ｂにより管板４が接続される。
管板４には伝熱管フランジ（大）５、ガスケット（大）５Ｄにより、前述のように内部に加熱流体配管３Ａが挿入された伝熱管（大）３が接続され、伝熱管フランジ（小）５１、ガスケット（小）５１Ｄにより、前述のように内部に加熱流体配管３１Ａが挿入された伝熱管（小）３１が設けられる。
FIG. 7 is an enlarged view of part A in FIG.
The tube plate 4 is connected to the rotary drum 2 by a rotary drum flange 4A and a gasket 4B.
The heat transfer tube flange (large) 5 and the gasket (large) 5D are connected to the tube plate 4 with the heat transfer tube (large) 3 into which the heating fluid pipe 3A is inserted as described above, and the heat transfer tube flange (small) is connected. 51, the gasket (small) 51D provides the heat transfer pipe (small) 31 into which the heating fluid pipe 31A is inserted as described above.
図８は図７における伝熱管フランジ（大）５・（小）５１の詳細図であり、内部構造を理解しやすくするために、図７における伝熱管フランジ（大）５・（小）５１の鉛直方向の上下を約９０度回転させて記載している。 FIG. 8 is a detailed view of the heat transfer tube flange (large) 5 (small) 51 in FIG. 7. In order to facilitate understanding of the internal structure, FIG. The vertical direction is described by rotating about 90 degrees.
図７及び８に示すように伝熱管フランジ（大）５は、伝熱管（大）３側と加熱流体往きヘッダー８、加熱流体戻りヘッダー９側とを仕切るために、鉛直方向の内部の上下にわたる仕切り板Ａ（大）５Ｂと水平方向の内部に装置手前から奥にわたる仕切り板Ｂ（大）５Ｃを有する。
仕切り板Ａ（大）５Ｂは、加熱流体往きヘッダー８から伝熱管（大）３に加熱流体往き２０６が供給される加熱流体往き配管（大）８Ａが接続され、かつ伝熱管（大）３から加熱流体戻りヘッダー９へ加熱流体戻り２０７が戻る加熱流体戻り配管（大）９Ａが接続される２つの連通孔５Ａを有する。
２つの連通孔５Ａは鉛直方向の上と下に設けられ、上に設けたものと下に設けたものの間に仕切り板Ｂ（大）５Ｃが設けられる。上に設けたものは加熱流体配管３Ａに接続される。
As shown in FIGS. 7 and 8, the heat transfer tube flange (large) 5 extends vertically inside the vertical direction in order to partition the heat transfer tube (large) 3 side from the heating fluid forward header 8 and the heating fluid return header 9 side. A partition plate A (large) 5B and a partition plate B (large) 5C extending from the front of the apparatus to the back are provided in the horizontal direction.
The partition plate A (large) 5B is connected to the heated fluid forward pipe (large) 8A to which the heated fluid forward pipe 206 is supplied from the heated fluid forward header 8 to the heat transfer pipe (large) 3, and from the heat transfer pipe (large) 3 A heating fluid return pipe (large) 9A for returning the heating fluid return 207 to the heating fluid return header 9 is provided with two communication holes 5A.
The two communication holes 5A are provided above and below in the vertical direction, and a partition plate B (large) 5C is provided between what is provided above and what is provided below. What was provided above is connected to the heated fluid piping 3A.
伝熱管フランジ（小）５１の構造は伝熱管フランジ（大）５と同じであり、連通孔５１Ａは連通孔５Ａに、仕切り板Ａ（小）５１Ｂは仕切り板Ａ（大）５Ｂに、仕切り板Ｂ（小）５１Ｃは仕切り板Ｂ（大）５Ｃに相当する。 The structure of the heat transfer tube flange (small) 51 is the same as that of the heat transfer tube flange (large) 5. The communication hole 51A is the communication hole 5A, the partition plate A (small) 51B is the partition plate A (large) 5B, and the partition plate. B (small) 51C corresponds to the partition plate B (large) 5C.
これにより、加熱流体往きヘッダー８から加熱流体往き配管（大）８Ａ・（小）８１Ａ、連通孔５Ａ・５１Ａを介して伝熱管（大）３・（小）３１の内部に加熱流体往き２０６が供給され、伝熱管（大）３・（小）３１から加熱流体配管３Ａ・３１Ａ、連通孔５Ａ・５１Ａ、加熱流体戻り配管（大）９Ａ・（小）９１Ａを介して加熱流体戻りヘッダー９へ加熱流体戻り２０７が戻る。 As a result, the heating fluid outlet 206 is transferred from the heating fluid outlet header 8 to the inside of the heat transfer pipe (large) 3 (small) 31 through the heating fluid outlet pipe (large) 8A / (small) 81A and the communication holes 5A / 51A. Supplied to the heating fluid return header 9 from the heat transfer tubes (large) 3 and (small) 31 through the heating fluid pipings 3A and 31A, communication holes 5A and 51A, heating fluid return piping (large) 9A and (small) 91A The heated fluid return 207 returns.
以上の説明から、連通孔５Ａ・５１Ａ、仕切り板Ａ（大）５Ｂ・（小）５１Ｂ、仕切り板Ｂ（大）５Ｃ・（小）５１Ｃを有した伝熱管フランジ（大）５・（小）５１及びガスケット(大)５Ｄ・（小）５１Ｄは伝熱管（大）３・（小）３１に接続され、伝熱管（大）３・（小）３１と外部との間に設ける隔壁に相当する。 From the above description, the heat transfer tube flange (large) 5 (small) having the communication holes 5A and 51A, the partition plates A (large) 5B and (small) 51B, and the partition plates B (large) 5C and (small) 51C. 51 and gasket (large) 5D (small) 51D are connected to the heat transfer tube (large) 3 (small) 31 and correspond to a partition provided between the heat transfer tube (large) 3 (small) 31 and the outside. .
図７に示すように加熱流体往き配管（大）８Ａ、加熱流体戻り配管（大）９Ａは伝熱管フランジ（大）５の相フランジである伝熱管エンドフランジ（大）６に接続され、仕切り板Ｂ（大）５Ｃを有した伝熱管フランジ（大）５と伝熱管エンドフランジ（大）６がガスケット（大）６Ｃを介して接続されることで、前述のように加熱流体往き配管（大）８Ａ、加熱流体戻り配管（大）９Ａが伝熱管フランジ（大）５の２つの連通孔５Ａに接続される。
加熱流体往き配管（小）８１Ａ、加熱流体戻り配管（小）９１Ａの伝熱管フランジ（小）５１の２つの連通孔５１Ａへの接続も同じであり、伝熱管エンドフランジ（小）６１は伝熱管エンドフランジ（大）６に、ガスケット（小）６１Ｃはガスケット（大）６Ｃに相当する。
As shown in FIG. 7, the heating fluid return pipe (large) 8A and the heating fluid return pipe (large) 9A are connected to the heat transfer pipe end flange (large) 6 which is a companion flange of the heat transfer pipe flange (large) 5, and the partition plate Heat transfer pipe flange (large) 5 having B (large) 5C and heat transfer pipe end flange (large) 6 are connected via a gasket (large) 6C, so that the heating fluid outlet pipe (large) as described above The heating fluid return pipe (large) 9 </ b> A is connected to the two communication holes 5 </ b> A of the heat transfer pipe flange (large) 5.
The connection of the heating fluid return pipe (small) 81A and the heating fluid return pipe (small) 91A to the two communication holes 51A of the heat transfer pipe flange (small) 51 is the same, and the heat transfer pipe end flange (small) 61 is the heat transfer pipe. The end flange (large) 6 and the gasket (small) 61C correspond to the gasket (large) 6C.
図９は図７における伝熱管エンドフランジ（大）６・（小）６１の詳細図であり、内部構造を理解しやすくするために、図８と同様に図７における伝熱管エンドフランジ（大）６・（小）６１の鉛直方向の上下を約９０度回転させて記載している。 FIG. 9 is a detailed view of the heat transfer tube end flange (large) 6 (small) 61 in FIG. 7. In order to facilitate understanding of the internal structure, the heat transfer tube end flange (large) in FIG. 6 (Small) 61 is vertically rotated up and down about 90 degrees.
図９に示すように伝熱管エンドフランジ（大）６は、加熱流体往き配管（大）８Ａが接続される加熱流体供給口６Ａ及び加熱流体戻り配管（大）９Ａが接続される加熱流体戻り口６Ｂを有する。
図７から９に示すように、加熱流体供給口６Ａは鉛直方向の下に設けた連通孔５Ａを介して、加熱流体戻り口６Ｂは鉛直方向の上に設けた連通孔５Ａを介して伝熱管３に連通される。
As shown in FIG. 9, the heat transfer pipe end flange (large) 6 includes a heating fluid supply port 6A to which a heating fluid outgoing pipe (large) 8A is connected and a heating fluid return port to which a heating fluid return pipe (large) 9A is connected. 6B.
As shown in FIGS. 7 to 9, the heating fluid supply port 6A is connected through a communication hole 5A provided below the vertical direction, and the heating fluid return port 6B is connected via a communication hole 5A provided above the vertical direction. 3 communicates.
前述のように伝熱管エンドフランジ（小）６１の構造は伝熱管エンドフランジ（大）６と同じであり、図９に示すように加熱流体供給口６１Ａは加熱流体供給口６Ａに、加熱流体戻り口６１Ｂは加熱流体戻り口６Ｂに相当する。 As described above, the structure of the heat transfer tube end flange (small) 61 is the same as that of the heat transfer tube end flange (large) 6, and as shown in FIG. 9, the heating fluid supply port 61A is connected to the heating fluid supply port 6A, and the heating fluid returns. The port 61B corresponds to the heating fluid return port 6B.
これにより、加熱流体往きヘッダー８から加熱流体往き配管（大）８Ａ・（小）８１Ａ、加熱流体供給口６Ａ・６１Ａ、連通孔５Ａ・５１Ａを介して伝熱管（大）３・（小）３１の内部に加熱流体往き２０６が供給され、伝熱管（大）３・（小）３１から加熱流体配管３Ａ・３１Ａ、連通孔５Ａ・５１Ａ、加熱流体戻り口６Ｂ・６１Ｂ、加熱流体戻り配管（大）９Ａ・（小）９１Ａを介して加熱流体戻りヘッダー９へ加熱流体戻り２０７が戻る。
加熱流体往き配管（大）８Ａ・（小）８１Ａと加熱流体戻り配管（大）９Ａ・（小）９１Ａは、仕切り板Ｂ（大）５Ｃ・（小）５１Ｃにより仕切られる。
As a result, the heat transfer pipe (large) 3 (small) 31 is routed from the heating fluid forward header 8 through the heating fluid forward pipe (large) 8A / (small) 81A, the heating fluid supply ports 6A / 61A, and the communication holes 5A / 51A. The heating fluid outlet 206 is supplied to the inside of the heating pipes 3A and 31A, the communication holes 5A and 51A, the heating fluid return ports 6B and 61B, and the heating fluid return piping (large) from the heat transfer tubes (large) 3 and (small) 31 ) Heated fluid return 207 returns to the heated fluid return header 9 via 9A / (small) 91A.
The heated fluid forward piping (large) 8A / (small) 81A and the heated fluid return piping (large) 9A / (small) 91A are partitioned by a partition plate B (large) 5C / (small) 51C.
以上の説明から、加熱流体供給口６Ａ・６１Ａ、加熱流体戻り口６Ｂ・６１Ｂを有した伝熱管エンドフランジ（大）６・（小）６１及びガスケット(大)６Ｃ・（小）６１Ｃは、伝熱管（大）３・（小）３１に連通し、伝熱管フランジ（大）５・（小）５１及びガスケット(大)５Ｄ・（小）５１Ｄで構成される隔壁に接続される配管接続部に相当する。
伝熱管フランジ（大）５・（小）５１及びガスケット(大)５Ｄ・（小）５１Ｄで構成される隔壁は、前述のように伝熱管（大）３・（小）３１に接続されるだけでなく、伝熱管エンドフランジ（大）６・（小）６１及びガスケット(大)６Ｃ・（小）６１Ｃで構成される配管接続部にも接続される。
From the above description, the heat transfer pipe end flange (large) 6 (small) 61 and the gasket (large) 6C / (small) 61C having the heating fluid supply ports 6A and 61A and the heating fluid return ports 6B and 61B are Connected to the heat pipe (large) 3 ・ (small) 31 and connected to the pipe connection part connected to the partition wall consisting of the heat transfer tube flange (large) 5 ・ (small) 51 and gasket (large) 5D ・ (small) 51D Equivalent to.
The partition composed of the heat transfer tube flange (large) 5 · (small) 51 and the gasket (large) 5D · (small) 51D is only connected to the heat transfer tube (large) 3 · (small) 31 as described above. In addition, it is also connected to a pipe connection portion composed of a heat transfer tube end flange (large) 6 · (small) 61 and a gasket (large) 6C · (small) 61C.
なお図７及び８では連通孔５Ａ・５１Ａとも、それぞれ鉛直方向の上に設けたものが加熱流体配管３Ａ・３１Ａに接続されているが、鉛直方向の下に設けたものを加熱流体配管３Ａ・３１Ａに接続してもよい。 7 and 8, both the communication holes 5A and 51A provided above the vertical direction are connected to the heating fluid pipes 3A and 31A, respectively, but those provided below the vertical direction are connected to the heating fluid pipes 3A and 31A. You may connect to 31A.
図７から９に示すように伝熱管フランジ（大）５・（小）５１は伝熱管（大）３・（小）３１の径よりも大きい径の柱形状であり、これらの相フランジである伝熱管エンドフランジ（大）６・（小）６１も伝熱管（大）３・（小）３１の径よりも大きい径の柱形状である。図８及び９において伝熱管フランジ（大）５・（小）５１及び伝熱管エンドフランジ（大）６・（小）６１はともに平板状の柱形状であるが円柱形状であってもよい。 As shown in FIGS. 7 to 9, the heat transfer tube flange (large) 5 · (small) 51 is a column shape having a diameter larger than the diameter of the heat transfer tube (large) 3 · (small) 31 and is a companion flange of these. The heat transfer tube end flange (large) 6 (small) 61 also has a column shape with a diameter larger than the diameter of the heat transfer tube (large) 3 (small) 31. 8 and 9, the heat transfer tube flanges (large) 5 and (small) 51 and the heat transfer tube end flanges (large) 6 and (small) 61 are both plate-like columnar shapes, but may be cylindrical.
図７から９において、伝熱管フランジ（大）５・（小）５１及び伝熱管エンドフランジ（大）６・（小）６１の管板４への接続は、図示しないボルトを隅に設けた孔（符号は設けず）に通すことにより行われる。 7 to 9, the heat transfer tube flanges (large) 5 and (small) 51 and the heat transfer tube end flanges (large) 6 and (small) 61 are connected to the tube plate 4 by holes provided with bolts (not shown) at the corners. This is done by passing it through (without the reference sign).
加熱流体往き配管（大）８Ａ・（小）８１Ａ、加熱流体戻り配管（大）９Ａ・（小）９１Ａの伝熱管エンドフランジ（大）６・（小）６１への接続は、それぞれの配管の外周と伝熱管エンドフランジ（大）６・（小）６１の隅肉溶接により行われる。 The connection of the heated fluid return pipe (large) 8A / (small) 81A and the heated fluid return pipe (large) 9A / (small) 91A to the heat transfer pipe end flange (large) 6 / (small) 61 This is performed by fillet welding of the outer periphery and the heat transfer tube end flange (large) 6 (small) 61.
そのため、加熱流体往き配管（大）８Ａと加熱流体戻り配管（大）９Ａの径は、それぞれの配管の外周と伝熱管エンドフランジ（大）６の隅肉溶接の重なりを避けること、２つの連通孔５Ａの鉛直方向の間に設けられた仕切り板Ｂ（大）５Ｃの鉛直方向の厚さにより、伝熱管（大）３の径の１／３相当になってしまう。
加熱流体往き配管（小）８１Ａ、加熱流体戻り配管（小）９１Ａの径も同じであり、伝熱管（小）３１の径の１／３相当になってしまう。
このため加熱流体往き配管（大）８Ａ・（小）８１Ａと加熱流体戻り配管（大）９Ａ・（小）９１Ａの径は、例えば公称１００Ａの伝熱管（大）３・（小）３１であれば公称２５Ａ、公称６５Ａまたは５０Ａの伝熱管（大）３・（小）３１であれば公称１５Ａのようになる。
加熱流体往き配管（大）８Ａ・（小）８１Ａと加熱流体戻り配管（大）９Ａ・（小）９１Ａの径が小さく限定されると、圧力損失が高くなり加熱流体往き２０６、加熱流体戻り２０７の流量が制限される。
これにより伝熱管（大）３・（小）３１内の加熱流体の流動状況が層流に近い状態になり、伝熱管（大）３・（小）３１内における熱伝達係数が低くなるため乾燥能力が向上しない。
Therefore, the diameter of the heated fluid forward pipe (large) 8A and the heated fluid return pipe (large) 9A is set so that the outer circumference of each pipe and the fillet weld of the heat transfer pipe end flange (large) 6 are avoided. Due to the vertical thickness of the partition plate B (large) 5C provided between the vertical directions of the holes 5A, it becomes equivalent to 1/3 of the diameter of the heat transfer tube (large) 3.
The diameters of the heated fluid return pipe (small) 81A and the heated fluid return pipe (small) 91A are also the same, which is equivalent to 1/3 of the diameter of the heat transfer pipe (small) 31.
For this reason, the diameter of the heating fluid return pipe (large) 8A / (small) 81A and the heating fluid return pipe (large) 9A / (small) 91A may be, for example, the nominal heat transfer pipe (large) 3 / (small) 31 of 100A. For example, if the heat transfer tube (large) 3 · (small) 31 of nominal 25A, nominal 65A or 50A is used, the nominal value will be 15A.
When the diameters of the heating fluid return pipe (large) 8A / (small) 81A and the heating fluid return pipe (large) 9A / (small) 91A are limited to small diameters, the pressure loss increases, and the heating fluid return 206 and heating fluid return 207 The flow rate is limited.
As a result, the flow state of the heating fluid in the heat transfer tubes (large) 3 (small) 31 becomes close to a laminar flow, and the heat transfer coefficient in the heat transfer tubes (large) 3 (small) 31 becomes low, so that the drying is performed. Ability does not improve.
乾燥性能を向上させるために圧力損失分を見込んで圧力を高くすることも考えられるが、経済的な運用でないことに加え、図６及び７に示すようにマニホールド１３０における乾燥キャリアガス２０２、加熱流体往きヘッダー８に供給される加熱流体往き２０６及び加熱流体戻りヘッダー９から戻る加熱流体戻り２０７の漏れが大きくなる可能性があるため危険を伴うことになる。
以上から、乾燥能力と安全性を向上させた回転式乾燥機を提供することが課題である。
Although it is conceivable to increase the pressure in anticipation of pressure loss in order to improve the drying performance, in addition to not being economically operated, as shown in FIGS. 6 and 7, the drying carrier gas 202 and the heating fluid in the manifold 130 Since the leakage of the heated fluid return 206 supplied to the forward header 8 and the heated fluid return 207 returning from the heated fluid return header 9 may increase, there is a risk.
From the above, it is an object to provide a rotary dryer with improved drying capacity and safety.
図１０は図７におけるＢ−Ｂ断面図である。
加熱流体配管３Ａが挿入された伝熱管（大）３が回転胴２の内周に環状に設けられ、かつ回転胴２の外周から中心に向けて徐々に径が小さくなるように加熱流体配管３１Ａが挿入された伝熱管（小）３１が同心円状に設けられる。
10 is a cross-sectional view taken along the line BB in FIG.
A heating fluid pipe 31A into which the heat transfer pipe (large) 3 into which the heating fluid pipe 3A has been inserted is annularly provided on the inner periphery of the rotating drum 2 and the diameter gradually decreases from the outer periphery of the rotating drum 2 toward the center. The heat transfer tube (small) 31 into which is inserted is provided concentrically.
図１１は図７におけるＣ−Ｃ断面図であり、各部位の接続関係を理解しやすくするために、伝熱管フランジ（大）５・（小）５１、伝熱管エンドフランジ（大）６・（小）６１は省略している。
加熱流体往きヘッダー８から加熱流体往き配管（大）８Ａ・（小）８１Ａにより伝熱管（大）３・（小）３１の内部に加熱流体往き２０６が供給され、伝熱管（大）３・（小）３１から加熱流体戻り配管（大）９Ａ・（小）９１Ａにより加熱流体戻りヘッダー９へ加熱流体戻り２０７が戻る。
なお、加熱流体供給口６Ａと加熱流体戻り口６Ｂの鉛直方向の上下関係についてどちらが上であるか明確に示されていないが、図７〜９及び前述のように加熱流体戻り口６Ｂが上方向である。加熱流体供給口６１Ａと加熱流体戻り口６１Ｂの鉛直方向の上下関係についても同じであり、加熱流体戻り口６１Ｂが上方向である。
FIG. 11 is a cross-sectional view taken along the line CC in FIG. 7. In order to facilitate understanding of the connection relationship of each part, the heat transfer tube flange (large) 5 (small) 51, the heat transfer tube end flange (large) 6 ( (Small) 61 is omitted.
Heated fluid forward 206 is supplied from the heated fluid forward header 8 to the inside of the heat transfer pipe (large) 3 (small) 31 by the heated fluid forward pipe (large) 8A (small) 81A, and the heat transfer pipe (large) 3 ( The heating fluid return 207 is returned from the (small) 31 to the heating fluid return header 9 by the heating fluid return pipe (large) 9A / (small) 91A.
In addition, although it is not clearly shown which is the upper or lower relationship in the vertical direction of the heating fluid supply port 6A and the heating fluid return port 6B, the heating fluid return port 6B is upward as shown in FIGS. It is. The same applies to the vertical relationship between the heating fluid supply port 61A and the heating fluid return port 61B in the vertical direction, and the heating fluid return port 61B is in the upward direction.
次に、本発明の請求項１に係る回転式乾燥機を図１〜３に基づいて説明する。 Next, the rotary dryer according to claim 1 of the present invention will be described with reference to FIGS.
図１は本発明の請求項１に係る回転式乾燥機の要部の拡大断面図である。
請求項１に係る回転式乾燥機における配管接続部は、伝熱管エンドフランジ（大）６Ｉ、ガスケット(大)６Ｊに加えて、伝熱管エンドキャップ（大）６Ｄ、伝熱管エンドプレート（大）６Ｈから構成される。
FIG. 1 is an enlarged cross-sectional view of a main part of a rotary dryer according to claim 1 of the present invention.
In addition to the heat transfer tube end flange (large) 6I and the gasket (large) 6J, the pipe connection portion in the rotary dryer according to claim 1 includes a heat transfer tube end cap (large) 6D and a heat transfer tube end plate (large) 6H. Consists of
図２は図１における伝熱管エンドキャップ（大）６Ｄ、伝熱管エンドプレート（大）６Ｈ及び伝熱管エンドフランジ（大）６Ｉの詳細図である。
伝熱管エンドキャップ（大）６Ｄは中空部６Ｅを有した円柱形状であり、一方の端面が伝熱管エンドフランジ（大）６Ｉに接続され、反対の端面は伝熱管エンドプレート（大）６Ｈに接続される。
伝熱管エンドプレート（大）６Ｈは中空部（符号なし）を有した薄い円板形状であり、伝熱管エンドキャップ（大）６Ｄに接続される端面と反対の端面に加熱流体戻り口６Ｇを有する。
2 is a detailed view of the heat transfer tube end cap (large) 6D, the heat transfer tube end plate (large) 6H, and the heat transfer tube end flange (large) 6I in FIG.
The heat transfer tube end cap (large) 6D has a cylindrical shape with a hollow portion 6E. One end surface is connected to the heat transfer tube end flange (large) 6I and the opposite end surface is connected to the heat transfer tube end plate (large) 6H. Is done.
The heat transfer tube end plate (large) 6H has a thin disk shape having a hollow portion (not indicated), and has a heating fluid return port 6G on the end surface opposite to the end surface connected to the heat transfer tube end cap (large) 6D. .
図８に示すように従来技術における伝熱管フランジ（大）５は２つの連通孔５Ａ、仕切り板Ａ（大）５Ｂ及び仕切り板Ｂ（大）５Ｃを有していたが、図１に示すように請求項１における伝熱管フランジ（大）５Ｅは、伝熱管エンドフランジ（大）６Ｉに接続される側を開口して１つの連通孔（符号なし）としている。
連通孔の径は最大で伝熱管（大）３の外径とすることが可能であり、必要に応じてこれより小さくしてもよい。
As shown in FIG. 8, the heat transfer tube flange (large) 5 in the prior art has two communication holes 5A, a partition plate A (large) 5B, and a partition plate B (large) 5C, but as shown in FIG. In addition, the heat transfer tube flange (large) 5E according to claim 1 is open to the side connected to the heat transfer tube end flange (large) 6I to form one communication hole (not indicated).
The diameter of the communication hole can be the maximum outer diameter of the heat transfer tube (large) 3, and may be smaller than this if necessary.
図１及び２に示すように伝熱管（大）３に挿入された加熱流体配管３Ｂは、連通孔、中空部６Ｅ、伝熱管エンドプレート（大）６Ｈの中空部を介して、加熱流体戻り口６Ｇに接続される。
加熱流体戻り口６Ｇには加熱流体戻りヘッダー９へ加熱流体戻り２０７が戻る加熱流体戻り配管（大）９Ｂが接続され、加熱流体戻り２０７は連通孔、中空部６Ｅを介して加熱流体戻りヘッダー９へ戻る。
As shown in FIGS. 1 and 2, the heating fluid pipe 3B inserted into the heat transfer tube (large) 3 is connected to the heating fluid return port through the communication hole, the hollow portion 6E, and the hollow portion of the heat transfer tube end plate (large) 6H. Connected to 6G.
A heating fluid return pipe (large) 9B for returning the heating fluid return 207 to the heating fluid return header 9 is connected to the heating fluid return port 6G. The heating fluid return 207 is connected to the heating fluid return header 9 via the communication hole and the hollow portion 6E. Return to.
伝熱管エンドキャップ（大）６Ｄの外周には加熱流体供給口６Ｆが設けられる。
すなわち加熱流体供給口６Ｆと加熱流体戻り口６Ｇが配管接続部である伝熱管エンドキャップ（大）６Ｄの別の面に設けられる。
加熱流体供給口６Ｆには加熱流体往きヘッダー８から加熱流体往き２０６が供給される加熱流体往き配管（大）８Ｂが接続され、加熱流体往き２０６は中空部６Ｅ、連通孔を介して伝熱管（大）３に供給される。
A heating fluid supply port 6F is provided on the outer periphery of the heat transfer tube end cap (large) 6D.
That is, the heating fluid supply port 6F and the heating fluid return port 6G are provided on another surface of the heat transfer tube end cap (large) 6D which is a pipe connection portion.
The heating fluid supply port 6F is connected to a heating fluid delivery pipe (large) 8B to which the heating fluid delivery 206 is supplied from the heating fluid delivery header 8, and the heating fluid delivery 206 is connected to the heat transfer pipe (through the hollow portion 6E and the communication hole ( Large) is supplied to 3.
前述のように伝熱管フランジ（大）５Ｅの伝熱管エンドフランジ（大）６Ｉに接続される側を開口して１つの連通孔とし、伝熱管エンドキャップ（大）６Ｄの外周に加熱流体供給口６Ｆを設けることで、中空部６Ｅの内部及び連通孔に加熱流体往き配管（大）８Ｂと加熱流体戻り配管（大）９Ｂ（加熱流体配管３Ｂ）の両方を設ける必要がなくなるため、図１に示すように伝熱管フランジ（大）５Ｅは従来技術における仕切り板Ａ（大）５Ｂ及び仕切り板Ｂ（大）５Ｃが不要となる。 As described above, the side connected to the heat transfer tube end flange (large) 6I of the heat transfer tube flange (large) 5E is opened as one communication hole, and the heating fluid supply port is provided on the outer periphery of the heat transfer tube end cap (large) 6D. By providing 6F, it is not necessary to provide both the heating fluid forward piping (large) 8B and the heating fluid return piping (large) 9B (heating fluid piping 3B) in the hollow portion 6E and in the communication hole. As shown, the heat transfer tube flange (large) 5E does not require the partition plate A (large) 5B and the partition plate B (large) 5C in the prior art.
図３は図１におけるＤ−Ｄ断図面である。
前述のように伝熱管エンドキャップ（大）６Ｄには、加熱流体供給口６Ｆと加熱流体戻り口６Ｇが別の面に設けられる。
なお図１〜３において伝熱管エンドキャップ（大）６Ｄの外周における加熱流体供給口６Ｆの位置が異なるが、外周のどこであってもよい。加熱流体往き配管（大）８Ｂの加熱流体往きヘッダー８と伝熱管エンドキャップ（大）６Ｄ間の引き回しに応じて設ければよい。
3 is a sectional view taken along the line DD in FIG.
As described above, the heat transfer tube end cap (large) 6D is provided with the heating fluid supply port 6F and the heating fluid return port 6G on different surfaces.
1 to 3, the position of the heating fluid supply port 6F on the outer periphery of the heat transfer tube end cap (large) 6D is different, but it may be anywhere on the outer periphery. What is necessary is just to provide according to the routing between the heating fluid going header 8 and the heat transfer pipe end cap (large) 6D of the heating fluid going piping (large) 8B.
伝熱管フランジ（小）５１Ｅ、伝熱管エンドフランジ（小）６１Ｉ、ガスケット（小）６１Ｊ、伝熱管エンドキャップ（小）６１Ｄ、中空部６１Ｅ、伝熱管エンドプレート（小）６１Ｈ、加熱流体供給口６１Ｆ、加熱流体戻り口６１Ｇの構造も同様であり、それぞれ伝熱管フランジ（大）５Ｅ、伝熱管エンドフランジ（大）６Ｉ、ガスケット(大)６Ｊ、伝熱管エンドキャップ（大）６Ｄ、中空部６Ｅ、伝熱管エンドプレート（大）６Ｈ、加熱流体供給口６Ｆ、加熱流体戻り口６Ｇに相当する。
これにより、加熱流体往きヘッダー８から加熱流体供給口６Ｆ・６１Ｆ、加熱流体往き配管（大）８Ｂ・（小）８１Ｂ、伝熱管エンドキャップ（大）６Ｄ（中空部６Ｅ）・（小）６１Ｄ（中空部６１Ｅ）、連通孔を介して伝熱管（大）３・（小）３１の内部に加熱流体往き２０６が供給され、伝熱管（大）３・（小）３１から加熱流体配管３Ｂ・３１Ｂ、連通孔、伝熱管エンドキャップ（大）６Ｄ（中空部６Ｅ）・（小）６１Ｄ（中空部６１Ｅ）、伝熱管エンドプレート（大）６Ｈ（中空部）・（小）６１Ｈ（中空部）、加熱流体戻り口６Ｇ・６１Ｇ、加熱流体戻り配管（大）９Ｂ・（小）９１Ｂを介して加熱流体戻りヘッダー９へ加熱流体戻り２０７が戻る。
Heat transfer tube flange (small) 51E, heat transfer tube end flange (small) 61I, gasket (small) 61J, heat transfer tube end cap (small) 61D, hollow portion 61E, heat transfer tube end plate (small) 61H, heating fluid supply port 61F , The structure of the heating fluid return port 61G is the same, and the heat transfer tube flange (large) 5E, the heat transfer tube end flange (large) 6I, the gasket (large) 6J, the heat transfer tube end cap (large) 6D, the hollow portion 6E, It corresponds to the heat transfer tube end plate (large) 6H, the heating fluid supply port 6F, and the heating fluid return port 6G.
Thereby, the heating fluid supply header 6F / 61F, the heating fluid supply piping (large) 8B / (small) 81B, the heat transfer tube end cap (large) 6D (hollow part 6E) / (small) 61D ( The heating fluid outlet 206 is supplied into the heat transfer pipe (large) 3 (small) 31 through the hollow portion 61E) and the communication hole, and the heating fluid pipes 3B and 31B are supplied from the heat transfer pipe (large) 3 (small) 31. , Communication hole, heat transfer tube end cap (large) 6D (hollow part 6E) · (small) 61D (hollow part 61E), heat transfer tube end plate (large) 6H (hollow part) · (small) 61H (hollow part), The heating fluid return 207 returns to the heating fluid return header 9 via the heating fluid return ports 6G and 61G and the heating fluid return pipe (large) 9B and (small) 91B.
なお図１〜３では伝熱管エンドプレート（大）６Ｈ・（小）６１Ｈに加熱流体戻り口６Ｇ・６１Ｇを、伝熱管エンドキャップ（大）６Ｄ・（小）６１Ｄに加熱流体供給口６Ｆ・６１Ｆを設けているが、伝熱管エンドプレート（大）６Ｈ・（小）６１Ｈに加熱流体供給口６Ｆ・６１Ｆを、伝熱管エンドキャップ（大）６Ｄ・（小）６１Ｄに加熱流体戻り口６Ｇ・６１Ｇを設けて、加熱流体供給口６Ｆ・６１Ｆに加熱流体往き配管（大）８Ｂ・（小）８１Ｂを、加熱流体戻り口６Ｇ・６１Ｇに加熱流体配管３Ｂ・３１Ｂ、加熱流体戻り配管（大）９Ｂ・（小）９１Ｂを接続してもよい。 1 to 3, heating fluid return ports 6G and 61G are provided in the heat transfer tube end plates (large) 6H and (small) 61H, and heating fluid supply ports 6F and 61F are provided in the heat transfer tube end caps (large) 6D and (small) 61D. The heating fluid supply ports 6F and 61F are provided in the heat transfer tube end plates (large) 6H and (small) 61H, and the heating fluid return ports 6G and 61G are provided in the heat transfer tube end caps (large) 6D and (small) 61D. Heating fluid supply pipes 6F and 61F are provided with heating fluid outgoing piping (large) 8B and (small) 81B, heating fluid return ports 6G and 61G are provided with heating fluid piping 3B and 31B, and heating fluid return piping (large) 9B. -(Small) 91B may be connected.
前述のように中空部６Ｅ・６１Ｅの内部及び連通孔に加熱流体往き配管（大）８Ｂ・（小）８１Ｂと加熱流体戻り配管（大）９Ｂ（加熱流体配管３Ｂ）・（小）９１Ｂ（加熱流体配管３１Ｂ）の両方を設ける必要がないこと、仕切り板Ｂ（大）５Ｃ・（小）５１Ｃが不要となることから、加熱流体往き配管（大）８Ｂ・（小）８１Ｂと加熱流体戻り配管（大）９Ｂ・（小）９１Ｂの径を伝熱管（大）３・（小）３１の径の１／３相当から公称で１から２サイズ大きくすることができ、加熱流体往き配管（大）８Ｂ・（小）８１Ｂと加熱流体戻り配管９Ｂ・（小）９１Ｂでの圧力損失を低くすることが可能となる。
これにより伝熱管（大）３・（小）３１内の加熱流体の流動状況が乱流に近い状態になり、伝熱管（大）３・（小）３１内における熱伝達係数が高くなるため乾燥能力を向上させることが可能となる。かつマニホールド１３０における乾燥キャリアガス２０２、加熱流体往きヘッダー８に供給される加熱流体往き２０６及び加熱流体戻りヘッダー９から戻る加熱流体戻り２０７の漏れを低くすることができ、安全性を向上させることが可能となる。
As described above, the heating fluid forward piping (large) 8B / (small) 81B and the heating fluid return piping (large) 9B (heating fluid piping 3B) / (small) 91B (heating) are provided in the hollow portions 6E and 61E and in the communication holes. Since it is not necessary to provide both of the fluid pipes 31B) and the partition plates B (large) 5C / (small) 51C are not required, the heated fluid forward pipe (large) 8B / (small) 81B and the heated fluid return pipe (Large) 9B · (Small) 91B diameter can be increased from 1/3 of the diameter of heat transfer tube (Large) 3 · (Small) 31 to 1 or 2 size nominally, heating fluid going piping (Large) It is possible to reduce the pressure loss at 8B · (small) 81B and the heated fluid return pipe 9B · (small) 91B.
As a result, the flow state of the heating fluid in the heat transfer tubes (large) 3 (small) 31 becomes close to turbulent flow, and the heat transfer coefficient in the heat transfer tubes (large) 3 (small) 31 becomes high, so that the drying is performed. Capability can be improved. Further, the leakage of the dried carrier gas 202 in the manifold 130, the heated fluid return 206 supplied to the heated fluid return header 8 and the heated fluid return 207 returned from the heated fluid return header 9 can be reduced, and safety can be improved. It becomes possible.
次に、本発明の請求項２及び３に係る回転式乾燥機を図４及び５に基づいて説明する。 Next, a rotary dryer according to claims 2 and 3 of the present invention will be described with reference to FIGS.
図４は本発明の請求項２及び３に係る回転式乾燥機の要部の拡大断面図であり、図５は図４におけるＥ−Ｅ断図面である。
請求項２に係る回転式乾燥機は、図１に示す請求項１に係る回転式乾燥機の伝熱管（大）３の配管接続部である伝熱管エンドフランジ（大）６Ｉ、ガスケット(大)６Ｊ、伝熱管エンドキャップ（大）６Ｄ、伝熱管エンドプレート（大）６Ｈと、伝熱管（小）３１の配管接続部である伝熱管エンドフランジ（小）６１Ｉ、ガスケット(小)６１Ｊ、伝熱管エンドキャップ（小）６１Ｄ、伝熱管エンドプレート（小）６１Ｈを、加熱流体往きヘッダー環柱７として１つの配管接続部にまとめている。
4 is an enlarged cross-sectional view of a main part of the rotary dryer according to claims 2 and 3 of the present invention, and FIG. 5 is a sectional view taken along line EE in FIG.
The rotary dryer according to claim 2 includes a heat transfer tube end flange (large) 6I which is a pipe connection portion of the heat transfer tube (large) 3 of the rotary dryer according to claim 1 shown in FIG. 6J, Heat Transfer Tube End Cap (Large) 6D, Heat Transfer Tube End Plate (Large) 6H, and Heat Transfer Tube End Flange (Small) 61I, Pipe Connection Portion of Heat Transfer Tube (Small) 31, Gasket (Small) 61J, Heat Transfer Tube The end cap (small) 61D and the heat transfer tube end plate (small) 61H are combined into one pipe connection portion as the heated fluid forward header ring column 7.
加熱流体往きヘッダー環柱７は中空部（符号なし）を有した円柱形状であり、加熱流体戻りヘッダー９側の端面に、伝熱管（大）３に挿入された加熱流体配管３Ｃに対応する加熱流体戻り口（大）６Ｋ、伝熱管（小）３１に挿入された加熱流体配管３１Ｃに対応する加熱流体戻り口（大）６１Ｋを有する。
加熱流体戻り口（大）６Ｋ・（小）６１Ｋを有した端面と反対の端面は伝熱管（大）３・（小）３１が接続された管板４Ｃが接続され、接続される側を開口して１つの連通孔（符号なし）としている。
加熱流体戻り口（大）６Ｋ・（小）６１Ｋには、それぞれに対応する加熱流体配管３Ｃ・３１Ｃ、加熱流体戻り配管（大）９Ｃ（小）９１Ｃが接続され、加熱流体戻り２０７は連通孔、中空部を介して加熱流体戻りヘッダー９へ戻る。
The heating fluid forward header ring column 7 has a cylindrical shape having a hollow portion (not indicated), and the heating fluid corresponding to the heating fluid pipe 3 </ b> C inserted into the heat transfer tube (large) 3 on the end surface on the heating fluid return header 9 side. A fluid return port (large) 6K and a heating fluid return port (large) 61K corresponding to the heating fluid pipe 31C inserted in the heat transfer tube (small) 31 are provided.
The end face opposite to the end face having the heating fluid return port (large) 6K · (small) 61K is connected to the tube plate 4C to which the heat transfer tubes (large) 3 · (small) 31 are connected, and the connected side is opened. Thus, one communication hole (no symbol) is provided.
The corresponding heating fluid pipes 3C and 31C and heating fluid return pipe (large) 9C (small) 91C are connected to the heating fluid return port (large) 6K / (small) 61K, and the heating fluid return 207 is a communication hole. Return to the heated fluid return header 9 through the hollow portion.
加熱流体往きヘッダー環柱７は外周に加熱流体往きヘッダー環柱連結ノズル７Ａを有する。加熱流体往きヘッダー環柱連結ノズル７Ａは中空部（符号なし）を有し、加熱流体往きヘッダー環柱７の中心に向かう方向と外周に向かう方向にそれぞれ開口部（符号なし）を有する。
加熱流体往きヘッダー環柱連結ノズル７Ａは請求項１に係る回転式乾燥機の加熱流体供給口６Ｆ・６１Ｆを１つに集約したものであり、加熱流体往きヘッダー環柱７の外周に向かう方向の開口部に図示しない加熱流体往きヘッダー８を接続することで、請求項１に係る回転式乾燥機の加熱流体往き配管（大）８Ｂ・（小）８１Ｂを接続しなくても、加熱流体２０６を中空部、連通孔を介して伝熱管（大）３・（小）３１に供給することが可能となる。
なお図４及び５において加熱流体往きヘッダー環柱連結ノズル７Ａは、加熱流体往きヘッダー環柱７の外周のうち鉛直方向の最上部近傍に設けているが、外周のどこであってもよい。加熱流体往きヘッダー８との位置関係（距離）に応じて設ければよい。
The heated fluid forward header ring column 7 has a heated fluid forward header ring column connecting nozzle 7A on the outer periphery. The heating fluid forward header ring column connecting nozzle 7A has a hollow portion (not indicated by a symbol), and has openings (not indicated by symbols) in a direction toward the center of the heating fluid forward header ring column 7 and a direction toward the outer periphery.
The heating fluid forward header ring column connection nozzle 7A is a collection of the heating fluid supply ports 6F and 61F of the rotary drier according to claim 1 in one, and is arranged in a direction toward the outer periphery of the heating fluid forward header ring column 7. By connecting the heating fluid going header 8 (not shown) to the opening, the heating fluid 206 can be supplied without connecting the heating fluid going piping (large) 8B / (small) 81B of the rotary dryer according to claim 1. It becomes possible to supply to the heat transfer tubes (large) 3 and (small) 31 through the hollow portion and the communication hole.
4 and 5, the heating fluid forward header ring column connection nozzle 7A is provided in the vicinity of the uppermost portion in the vertical direction of the outer periphery of the heating fluid forward header ring column 7, but may be anywhere on the outer periphery. What is necessary is just to provide according to the positional relationship (distance) with the heating fluid going-out header 8. FIG.
また図４及び５では請求項１に係る回転式乾燥機の加熱流体供給口６Ｆ・６１Ｆを１つに集約して加熱流体往きヘッダー環柱連結ノズル７Ａを設けたが、加熱流体戻り口６Ｇ・６１Ｇを１つに集約して加熱流体戻りヘッダー環柱連結ノズル（符号なし）を設けてもよい。 4 and 5, the heating fluid supply ports 6F and 61F of the rotary dryer according to claim 1 are combined into one to provide the heating fluid forward header ring column connection nozzle 7A. 61G may be gathered into one and a heating fluid return header ring column connection nozzle (no code) may be provided.
以上から請求項１に係る回転式乾燥機の加熱流体往き配管（大）８Ｂ・（小）８１Ｂまたは加熱流体戻り配管（大）９Ｂ・（小）９１Ｂが不要となるため、マニホールド１３０以外でも加熱流体往き配管（大）８Ｂ・（小）８１Ｂまたは加熱流体戻り配管（大）９Ｂ・（小）９１Ｂの接続箇所における加熱流体の漏れを低くすることができ、請求項１に係る回転式乾燥機の効果に加えて更に安全性を向上させることが可能となる。かつ構造がシンプルとなり運用や維持が容易となる。 As described above, the heating fluid forward piping (large) 8B / (small) 81B or the heating fluid return piping (large) 9B / (small) 91B of the rotary drier according to claim 1 is not necessary, and heating is performed in places other than the manifold 130. The rotary dryer according to claim 1, wherein leakage of the heated fluid at the connection point of the fluid forward pipe (large) 8B / (small) 81B or the heated fluid return pipe (large) 9B / (small) 91B can be reduced. In addition to the effects, it is possible to further improve safety. In addition, the structure is simple and easy to operate and maintain.
請求項３に係る回転式乾燥機は図４に示すように、伝熱管（大）３の内部に鉛直方向の断面における外側から中心に向かう加熱流体流量調整板７Ｂを設けている。
加熱流体流量調整板７Ｂの例としては薄い平板形状の突起があるが、鉛直方向の断面における外側から中心に向かう形状であれば、これ以外でもかまわない。
図４において加熱流体流量調整板７Ｂの伝熱管（大）３に設ける位置は、加熱流体往きヘッダー環柱７の管板４Ｃと接続された端面を開口した連通孔（符号なし）に接する箇所としているが、内部であれば水平方向（図における左右方向）のどこであっても良い。
図４において加熱流体流量調整板７Ｂは伝熱管（大）３にしか設けられていないが、伝熱管（小）３１に設けても良い。
As shown in FIG. 4, the rotary dryer according to a third aspect is provided with a heating fluid flow rate adjusting plate 7 </ b> B from the outside to the center in the vertical cross section inside the heat transfer tube (large) 3.
As an example of the heating fluid flow rate adjusting plate 7B, there is a thin flat plate-shaped protrusion, but other shapes may be used as long as the shape is directed from the outside to the center in the cross section in the vertical direction.
In FIG. 4, the position of the heating fluid flow rate adjusting plate 7 </ b> B provided in the heat transfer tube (large) 3 is a location where the end face connected to the tube plate 4 </ b> C of the heating fluid forward header ring column 7 is in contact with the communication hole (not indicated). However, as long as it is inside, it may be anywhere in the horizontal direction (left-right direction in the figure).
In FIG. 4, the heating fluid flow rate adjusting plate 7 </ b> B is provided only on the heat transfer tube (large) 3, but may be provided on the heat transfer tube (small) 31.
加熱流体流量調整板７Ｂを設けることで、伝熱管（大）３・（小）３１に供給される加熱流体往き２０６または伝熱管（大）３・（小）３１から戻る加熱流体戻り２０７の流量を調整することができ、回転式乾燥機の乾燥能力を向上させることが可能となる。 By providing the heating fluid flow rate adjusting plate 7B, the flow rate of the heating fluid return 206 returned from the heating fluid return 206 or the heat transfer tube (large) 3 (small) 31 supplied to the heat transfer tube (large) 3 (small) 31 Thus, it becomes possible to improve the drying capacity of the rotary dryer.
前述のように、伝熱管（大）３は回転胴２の内周に環状に設けられ、かつ回転胴２の外周から中心に向けて徐々に径が小さくなるように伝熱管（小）３１が同心円状に設けられるので、任意の伝熱管に加熱流体流量調整板７Ｂを設けることで、伝熱管の環状に設けられた数、径の種類に応じて、回転式乾燥機の乾燥能力を向上させることが可能となる。 As described above, the heat transfer tube (large) 3 is provided annularly on the inner periphery of the rotating drum 2, and the heat transfer tube (small) 31 is formed so that the diameter gradually decreases from the outer periphery of the rotating drum 2 toward the center. Since it is provided concentrically, by providing the heating fluid flow rate adjusting plate 7B in an arbitrary heat transfer tube, the drying capacity of the rotary dryer is improved according to the number and diameter of the heat transfer tubes provided in an annular shape. It becomes possible.
回転式乾燥機の乾燥能力を最も向上させるには、伝熱管（大）３には回転胴２の内周に環状に設けられたすべてに加熱流体流量調整板７Ｂを設け、伝熱管の径が小さくなるにつれて加熱流体流量調整板７Ｂを設ける数を少なくし、伝熱管の径が小さくなるにつれて鉛直方向の断面における外側から中心に向かう長さを小さくして加熱流体流量調整板７Ｂを設けると良い。 In order to improve the drying capacity of the rotary drier most, the heat transfer pipe (large) 3 is provided with a heating fluid flow rate adjusting plate 7B on the inner circumference of the rotary drum 2 and the diameter of the heat transfer pipe is increased. The number of the heating fluid flow rate adjustment plates 7B is reduced as it becomes smaller, and the length from the outer side to the center in the vertical cross section is made smaller as the diameter of the heat transfer tube becomes smaller, so that the heating fluid flow rate adjustment plate 7B is provided. .
また加熱流体流量調整板７Ｂは、伝熱管（大）３・（小）３１の鉛直方向の断面における中心から外側に向かうものであっても良い。
例えば加熱流体配管３Ｃ・３１Ｃの外周に、伝熱管（大）３・（小）３１の内部の外側に向かうように設けても良い。
Moreover, the heating fluid flow rate adjusting plate 7B may be directed outward from the center of the cross section in the vertical direction of the heat transfer tubes (large) 3 (small) 31.
For example, you may provide in the outer periphery of heating fluid piping 3C * 31C so that it may go to the outer side of the inside of the heat exchanger tube (large) 3 * (small).
以上から伝熱管（大）３・（小）３１の内部に設けた加熱流体流量調整板７Ｂにより、回転胴２の外周から中心に向けて徐々に径が小さくなるように同心円状に設けた伝熱管（大）３・（小）３１のそれぞれの径に応じて、加熱流体往き２０６または加熱流体戻り２０７の流量を調節することができ、請求項２に係る回転式乾燥機の効果に加えて更に乾燥能力を向上させることが可能となる。かつ運用が容易となる。 From the above, the heating fluid flow rate adjusting plate 7B provided in the heat transfer tubes (large) 3 (small) 31 is provided in a concentric manner so that the diameter gradually decreases from the outer periphery to the center of the rotating drum 2. According to the diameters of the heat pipes (large) 3 and (small) 31, the flow rate of the heating fluid return 206 or heating fluid return 207 can be adjusted, in addition to the effect of the rotary dryer according to claim 2. Furthermore, it becomes possible to improve a drying capacity. And operation becomes easy.
１ 回転式乾燥機
２ 回転胴
３ 伝熱管（大）
３Ａ 加熱流体配管
３Ｂ 加熱流体配管
３Ｃ 加熱流体配管
３１ 伝熱管（小）
３１Ａ 加熱流体配管
３１Ｂ 加熱流体配管
３１Ｃ 加熱流体配管
４ 管板
４Ａ 回転胴フランジ
４Ｂ ガスケット
４Ｃ 管板
５ 伝熱管フランジ（大）
５Ａ 連通孔
５Ｂ 仕切り板Ａ（大）
５Ｃ 仕切り板Ｂ（大）
５Ｄ ガスケット（大）
５Ｅ 伝熱管フランジ（大）
５１ 伝熱管フランジ（小）
５１Ａ 連通孔
５１Ｂ 仕切り板Ａ（小）
５１Ｃ 仕切り板Ｂ（小）
５１Ｄ ガスケット（小）
５１Ｅ 伝熱管フランジ（小）
６ 伝熱管エンドフランジ（大）
６Ａ 加熱流体供給口
６Ｂ 加熱流体戻り口
６Ｃ ガスケット（大）
６Ｄ 伝熱管エンドキャップ（大）
６Ｅ 中空部
６Ｆ 加熱流体供給口
６Ｇ 加熱流体戻り口
６Ｈ 伝熱管エンドプレート（大）
６Ｉ 伝熱管エンドフランジ（大）
６Ｊ ガスケット（大）
６Ｋ 加熱流体戻り口
６１ 伝熱管エンドフランジ（小）
６１Ａ 加熱流体供給口
６１Ｂ 加熱流体戻り口
６１Ｃ ガスケット（小）
６１Ｄ 伝熱管エンドキャップ（小）
６１Ｅ 中空部
６１Ｆ 加熱流体供給口
６１Ｇ 加熱流体戻り口
６１Ｈ 伝熱管エンドプレート（小）
６１Ｉ 伝熱管エンドフランジ（小）
６１Ｊ ガスケット（小）
６１Ｋ 加熱流体戻り口
７ 加熱流体往きヘッダー環柱
７Ａ 加熱流体往きヘッダー環柱連結ノズル
７Ｂ 加熱流体流量調整板
８ 加熱流体往きヘッダー
８Ａ 加熱流体往き配管（大）
８Ｂ 加熱流体往き配管（大）
８１Ａ 加熱流体往き配管（小）
８１Ｂ 加熱流体往き配管（小）
９ 加熱流体戻りヘッダー
９Ａ 加熱流体戻り配管（大）
９Ｂ 加熱流体戻り配管（大）
９Ｃ 加熱流体戻り配管（大）
９１Ａ 加熱流体戻り配管（小）
９１Ｂ 加熱流体戻り配管（小）
９１Ｃ 加熱流体戻り配管（小）
１０ モーター
１０Ａ 減速機
１０Ｂ ピニオンギヤ―
１０Ｃ ガウスギヤー
１０Ｄ タイヤローラー
１０Ｅ 受けローラー
１００ 入口コンベヤー
１００Ａ 湿潤製品供給源
１００Ｂ 湿潤製品供給配管
１１０ スクラバー
１１０Ａ スクラバーポンプ
１１０Ｂ 湿潤キャリアガス配管
１１０Ｃ 乾燥キャリアガス配管
１１０Ｄ 回収液配管
１２０ 出口コンベヤー
１２０Ａ ロータリーバルブ
１２０Ｂ ニューマ配管
１３０ マニホールド
１３０Ａ 加熱流体往き配管
１３０Ｂ 加熱流体戻り配管
１４０ 加熱流体循環ポンプ
１４０Ａ 加熱流体受け槽
１４０Ｂ 加熱流体往き配管
１４０Ｃ 加熱流体戻り配管
２００ 湿潤製品
２０１ 湿潤キャリアガス
２０２ 乾燥キャリアガス
２０３ 回収液
２０４ 乾燥製品
２０５ 移送ガス
２０６ 加熱流体往き
２０７ 加熱流体戻り
1 Rotary dryer 2 Rotating drum 3 Heat transfer tube (large)
3A Heating fluid piping 3B Heating fluid piping 3C Heating fluid piping 31 Heat transfer tube (small)
31A Heating fluid piping 31B Heating fluid piping 31C Heating fluid piping 4 Tube plate 4A Rotary barrel flange 4B Gasket 4C Tube plate 5 Heat transfer tube flange (large)
5A Communication hole 5B Partition plate A (Large)
5C Partition plate B (large)
5D gasket (large)
5E Heat transfer tube flange (large)
51 Heat transfer tube flange (small)
51A Communication hole 51B Partition plate A (small)
51C Partition plate B (small)
51D gasket (small)
51E Heat transfer tube flange (small)
6 Heat transfer tube end flange (large)
6A Heating fluid supply port 6B Heating fluid return port 6C Gasket (large)
6D heat transfer tube end cap (large)
6E Hollow part 6F Heating fluid supply port 6G Heating fluid return port 6H Heat transfer tube end plate (large)
6I Heat transfer tube end flange (large)
6J Gasket (Large)
6K Heating fluid return port 61 Heat transfer tube end flange (small)
61A Heating fluid supply port 61B Heating fluid return port 61C Gasket (small)
61D Heat transfer tube end cap (small)
61E Hollow part 61F Heating fluid supply port 61G Heating fluid return port 61H Heat transfer tube end plate (small)
61I Heat transfer tube end flange (small)
61J Gasket (small)
61K Heating fluid return port 7 Heating fluid forward header ring column 7A Heating fluid forward header ring column connection nozzle 7B Heating fluid flow rate adjustment plate 8 Heating fluid forward header 8A Heating fluid outbound pipe (large)
8B Heating fluid piping (large)
81A Heating fluid forward piping (small)
81B Heating fluid forward piping (small)
9 Heating fluid return header 9A Heating fluid return piping (large)
9B Heated fluid return pipe (large)
9C Heating fluid return pipe (large)
91A Heating fluid return pipe (small)
91B Heating fluid return pipe (small)
91C Heating fluid return pipe (small)
10 Motor 10A Reducer 10B Pinion gear
10C Gaussian gear 10D Tire roller 10E Receiving roller 100 Inlet conveyor 100A Wet product supply source 100B Wet product supply piping 110 Scrubber 110A Scrubber pump 110B Wet carrier gas piping 110C Dry carrier gas piping 110D Recovery liquid piping 120 Outlet conveyor 120A Rotary valve 120B Pneumatic piping 130 Manifold 130A Heated fluid return pipe 130B Heated fluid return pipe 140 Heated fluid circulation pump 140A Heated fluid receiving tank 140B Heated fluid return pipe 140C Heated fluid return pipe 200 Wet product 201 Wet carrier gas 202 Dry carrier gas 203 Recovery liquid 204 Dry product 205 Transfer Gas 206 Heating fluid return 207 Heating fluid return
Claims (1)
加熱流体供給口と加熱流体戻り口を配管接続部の別の面に設け、
複数の配管接続部を１つにまとめ、加熱流体供給口または加熱流体戻り口を１つに集約し、
伝熱管の内部に断面外側から中心に向かうまたは中心から断面外側に向かう加熱流体流量調整板を設けたことを特徴とする加熱流体による回転式乾燥機。 A heat transfer pipe having a heating fluid pipe inside, a columnar pipe connection part having a heating fluid supply port and a heating fluid return port and communicating with the heat transfer pipe, and a heat transfer pipe and pipe connection part having a communication hole. In the rotary dryer with heated fluid composed of connected partition walls,
Provide a heating fluid supply port and a heating fluid return port on the other side of the pipe connection,
Combine multiple piping connections into one, consolidate heating fluid supply ports or heating fluid return ports into one,
A rotary drier using a heating fluid, characterized in that a heating fluid flow rate adjusting plate is provided inside the heat transfer tube from the outside of the cross section toward the center or from the center toward the outside of the cross section .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015141725A JP5958783B1 (en) | 2015-07-16 | 2015-07-16 | Rotary dryer with improved drying capacity and safety |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015141725A JP5958783B1 (en) | 2015-07-16 | 2015-07-16 | Rotary dryer with improved drying capacity and safety |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP5958783B1 true JP5958783B1 (en) | 2016-08-02 |
| JP2017026166A JP2017026166A (en) | 2017-02-02 |
Family
ID=56550495
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2015141725A Active JP5958783B1 (en) | 2015-07-16 | 2015-07-16 | Rotary dryer with improved drying capacity and safety |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP5958783B1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1467038A (en) * | 1919-05-31 | 1923-09-04 | Huhn Mfg Company A | Drier |
| JPS6310474Y2 (en) * | 1983-11-15 | 1988-03-28 | ||
| JPH04345686A (en) * | 1991-05-22 | 1992-12-01 | Kawasaki Steel Corp | Indirect heating rotary dryer for powder and method of using same |
| JPH04359790A (en) * | 1991-06-07 | 1992-12-14 | Kawasaki Steel Corp | Powder indirect heating type rotary dryer and its service method |
| JPH0650532Y2 (en) * | 1988-09-14 | 1994-12-21 | 川崎重工業株式会社 | Tube dryer condensate discharge device |
| JP2009243721A (en) * | 2008-03-28 | 2009-10-22 | Mitsui Eng & Shipbuild Co Ltd | Indirect heating type rotary dryer |
-
2015
- 2015-07-16 JP JP2015141725A patent/JP5958783B1/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1467038A (en) * | 1919-05-31 | 1923-09-04 | Huhn Mfg Company A | Drier |
| JPS6310474Y2 (en) * | 1983-11-15 | 1988-03-28 | ||
| JPH0650532Y2 (en) * | 1988-09-14 | 1994-12-21 | 川崎重工業株式会社 | Tube dryer condensate discharge device |
| JPH04345686A (en) * | 1991-05-22 | 1992-12-01 | Kawasaki Steel Corp | Indirect heating rotary dryer for powder and method of using same |
| JPH04359790A (en) * | 1991-06-07 | 1992-12-14 | Kawasaki Steel Corp | Powder indirect heating type rotary dryer and its service method |
| JP2009243721A (en) * | 2008-03-28 | 2009-10-22 | Mitsui Eng & Shipbuild Co Ltd | Indirect heating type rotary dryer |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017026166A (en) | 2017-02-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP3382310B1 (en) | Rotary furnace | |
| CN205954106U (en) | A processing system for semiconductor is handled | |
| JP5998174B2 (en) | Device for sealing a propeller shaft of a ship and method for manufacturing such a device | |
| JP2015502516A (en) | Coil type heat exchanger | |
| JP2015098361A5 (en) | ||
| JP5958783B1 (en) | Rotary dryer with improved drying capacity and safety | |
| EP1811256B1 (en) | Heat exchange installation | |
| KR101631578B1 (en) | Rotary distribution apparatus | |
| JP2008088557A (en) | Rotary pressure distributor and carousel-type hollow body treatment machine equipped therewith | |
| CN102853637A (en) | Flat round pipe inner heating double-cone vacuum dryer | |
| CN207649426U (en) | A kind of heat exchanger | |
| CN204535492U (en) | A kind of delivery heat transfer device | |
| CN209512590U (en) | A kind of " 0 " leakage type cooler | |
| WO2018000842A1 (en) | Two-channel rotary type filling device | |
| CN109539833A (en) | One kind " 0 " leakage type cooler and its working method | |
| CN200993537Y (en) | Coiled-pipe heat exchanger | |
| CN214139863U (en) | Storage device for biological medicine intermediate preparation process | |
| EP2976948B1 (en) | Module for thermal conditioning and tempering machine employing such a module | |
| CN201672784U (en) | Multiple circular pipes gas distribution chamber | |
| CN102602600B (en) | Jacket applicable to horizontal glass lining equipment | |
| CN202277694U (en) | Vacuum flash tank | |
| CN109612304A (en) | A kind of New round block graphite heat exchanger and method | |
| CN103836030B (en) | A kind of current velocity controller | |
| US9038867B2 (en) | Degasser snorkel with serpentine flow path cooling | |
| CN212839633U (en) | Rotary high-pressure butterfly valve with heat-insulating anti-crystallization structure |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A521 | Request for written amendment filed |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20160510 |
|
| 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: 20160531 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20160608 |
|
| R150 | Certificate of patent or registration of utility model |
Ref document number: 5958783 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |