JPH04260783A - Cooling controller for hot isotropic pressurizer - Google Patents
Cooling controller for hot isotropic pressurizerInfo
- Publication number
- JPH04260783A JPH04260783A JP3020147A JP2014791A JPH04260783A JP H04260783 A JPH04260783 A JP H04260783A JP 3020147 A JP3020147 A JP 3020147A JP 2014791 A JP2014791 A JP 2014791A JP H04260783 A JPH04260783 A JP H04260783A
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- furnace
- cooling
- gas
- insulating layer
- 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.)
- Pending
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 68
- 238000010438 heat treatment Methods 0.000 claims description 2
- 230000004907 flux Effects 0.000 abstract description 9
- 239000000463 material Substances 0.000 abstract description 2
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 238000000034 method Methods 0.000 description 15
- 238000010586 diagram Methods 0.000 description 5
- 238000005338 heat storage Methods 0.000 description 3
- 230000005855 radiation Effects 0.000 description 3
- 230000017525 heat dissipation Effects 0.000 description 2
- 238000001513 hot isostatic pressing Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 239000000843 powder Substances 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B11/00—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses
- B30B11/001—Presses specially adapted for forming shaped articles from material in particulate or plastic state, e.g. briquetting presses, tabletting presses using a flexible element, e.g. diaphragm, urged by fluid pressure; Isostatic presses
- B30B11/002—Isostatic press chambers; Press stands therefor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22F—WORKING METALLIC POWDER; MANUFACTURE OF ARTICLES FROM METALLIC POWDER; MAKING METALLIC POWDER; APPARATUS OR DEVICES SPECIALLY ADAPTED FOR METALLIC POWDER
- B22F3/00—Manufacture of workpieces or articles from metallic powder characterised by the manner of compacting or sintering; Apparatus specially adapted therefor ; Presses and furnaces
- B22F3/12—Both compacting and sintering
- B22F3/14—Both compacting and sintering simultaneously
- B22F3/15—Hot isostatic pressing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F27—FURNACES; KILNS; OVENS; RETORTS
- F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
- F27D9/00—Cooling of furnaces or of charges therein
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Furnace Details (AREA)
- Powder Metallurgy (AREA)
- Heat Treatments In General, Especially Conveying And Cooling (AREA)
Abstract
Description
【０００１】0001
【産業上の利用分野】本発明は、熱間等方圧加圧装置の
冷却制御装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cooling control device for a hot isostatic pressurizing device.
【０００２】0002
【従来の技術】各種粉末の高密度焼結体等の製造に用い
る熱間等方圧加圧装置としては、従来、図７に示すよう
なものがある。即ち、図７において、上・下蓋１，２
を有する高圧容器３ に、これとの間に間隙４ をおい
て断熱層５ を配設すると共に、断熱層５ の内側にヒ
ータ６ を配設して炉室７ が構成されている。2. Description of the Related Art Conventionally, there is a hot isostatic pressing apparatus shown in FIG. 7 used for producing high-density sintered bodies of various powders. That is, in FIG. 7, the upper and lower lids 1 and 2
A furnace chamber 7 is constructed by disposing a heat insulating layer 5 in a high-pressure vessel 3 having a high-pressure container 3 with a gap 4 therebetween, and a heater 6 disposed inside the heat insulating layer 5.
【０００３】この装置で被処理体８ を処理する場合に
は、炉室７ 内に被処理体８ を配し、高圧容器３ 内
に高圧の圧媒ガスを導入すると共に、ヒータ６ で加熱
することにより、被処理体８ に高温高圧の圧媒ガスを
作用させて熱間等方圧加圧処理を行う。そして、処理後
、炉内を冷却した後、被処理体８ を取出す。この処理
後の炉内の冷却は、従来、断熱層５ を介した放熱作用
のみで行われていたため、冷却に長時間を要し、生産性
向上のネックとなっていた。When processing an object to be processed 8 with this apparatus, the object to be processed 8 is placed in a furnace chamber 7 , high-pressure pressure medium gas is introduced into a high-pressure container 3 , and the object is heated by a heater 6 . As a result, a hot isostatic pressurization process is performed by applying a high temperature and high pressure pressure medium gas to the object to be processed 8 . After the treatment, the inside of the furnace is cooled, and then the object to be treated 8 is taken out. Conventionally, the inside of the furnace after this treatment was cooled only by the heat dissipation effect through the heat insulating layer 5, which took a long time and became a bottleneck in improving productivity.
【０００４】冷却時間の短縮の一手段としては、冷却時
に高圧容器３ 内のガスを循環させる方法があり、例え
ば実開昭６０−３３１９５ 号公報で開示されたような
間接冷却の方法があるが、ガス循環により冷却過程を促
進する方法の内、究極的なものは図７に示すような直接
冷却方式である。この直接冷却方式は、循環ガスの流れ
を点線で示すように、炉内（断熱層５ 内） の高温ガ
スを炉外へ流出させて、上蓋１ 、高圧容器３ の内壁
等で熱交換させ、低温になったガスを断熱層５ の下部
から再び炉内に循環させて冷却する。この直接冷却方式
によれば、冷却速度を大幅に促進できる。[0004] One means of shortening the cooling time is to circulate the gas in the high-pressure vessel 3 during cooling; for example, there is an indirect cooling method as disclosed in Japanese Utility Model Application No. 60-33195. Among the methods of promoting the cooling process by gas circulation, the ultimate method is a direct cooling method as shown in FIG. In this direct cooling method, as the flow of circulating gas is shown by the dotted line, high-temperature gas inside the furnace (inside the heat insulating layer 5) flows out of the furnace, and heat is exchanged with the upper lid 1, the inner wall of the high-pressure vessel 3, etc. The low-temperature gas is circulated again into the furnace from the lower part of the heat insulating layer 5 to be cooled. According to this direct cooling method, the cooling rate can be greatly accelerated.
【０００５】[0005]
【発明が解決しようとする課題】従来の直接冷却方式で
は、循環ガス量を増やせば冷却速度が大きくなるが、容
器内面温度の上昇も比例して大きくなる。高圧容器３
には材料強度上の観点から許容最高温度が決まっており
、これを超えてはならない。従って、トータル放熱量を
大きくして高圧容器３ の温度上昇を低く抑えるために
は、炉内からの単位時間当りの放熱量を一定に保つのが
理想である。[Problems to be Solved by the Invention] In the conventional direct cooling system, increasing the amount of circulating gas increases the cooling rate, but the increase in the internal temperature of the container also increases proportionally. High pressure container 3
The maximum allowable temperature is determined from the viewpoint of material strength, and this must not be exceeded. Therefore, in order to increase the total amount of heat radiation and suppress the temperature rise in the high-pressure vessel 3, it is ideal to keep the amount of heat radiation from the inside of the furnace constant per unit time.
【０００６】しかしながら、従来の冷却法では、この目
的に沿った風量制御を行わないため、冷却初期の炉内か
らの放熱量と冷却過程最後の放熱量は１０倍近い差があ
り（初期が大きい） 、徒らに高圧容器３ の内面温度
の上昇を招く結果となっていた。図８は或る容器サイズ
（内径 ９００ｍｍ）の高圧容器３ において、特定の
炉内熱容量を仮定した場合の容器内面への平均熱流束と
容器最高温度との関係を示す。この図８よりも明らかな
ように、平均熱流束が同じでも、その最大値／最小値の
比Ｒが大きい場合には、高圧容器３ の温度上昇が大き
くなる。従って、理想的には熱流束を一定にし、前記比
Ｒを１にすべきであるが、従来の冷却法では比Ｒが１０
近い値となっている。However, in conventional cooling methods, the air volume is not controlled in accordance with this purpose, so there is a difference of nearly 10 times between the amount of heat released from the inside of the furnace at the initial stage of cooling and the amount of heat released at the end of the cooling process (larger in the initial stage). ), which resulted in an unnecessary increase in the internal temperature of the high-pressure vessel 3. FIG. 8 shows the relationship between the average heat flux to the inner surface of the container and the maximum temperature of the high-pressure container 3 having a certain container size (inner diameter 900 mm) assuming a specific heat capacity in the furnace. As is clear from FIG. 8, even if the average heat flux is the same, when the ratio R of the maximum value/minimum value is large, the temperature rise in the high pressure vessel 3 becomes large. Therefore, ideally the heat flux should be constant and the ratio R should be 1, but in conventional cooling methods the ratio R should be 10.
The values are close.
【０００７】本発明は、かかる点に鑑み、冷却過程中の
ガスから容器内面への熱流束を略一定に保ち、容器温度
上昇を最小限に抑えた放熱を可能にすることを目的とす
る。[0007] In view of the above, an object of the present invention is to keep the heat flux from the gas to the inner surface of the container substantially constant during the cooling process, thereby making it possible to dissipate heat while minimizing the rise in the temperature of the container.
【０００８】[0008]
【課題を解決するための手段】本発明は、高圧容器３
内に、該高圧容器３ との間に間隙４ をおいて断熱層
５ を配設すると共に、断熱層５ 内にヒータ６ を配
設して炉室７ を構成し、炉室７ 内に高圧の圧媒ガス
を導入しヒータ６ で加熱することにより、炉室７内の
被処理体８ に高温高圧の圧媒ガスを作用させて熱間等
方圧加圧処理を行う熱間等方圧加圧装置において、炉室
７ 内の高温の圧媒ガスを断熱層５ の上部から外部に
導き、高圧容器３ の内壁に沿って流下させて断熱層５
の下部から炉室７ 内に導く圧媒ガス循環路１２の途
中に循環ガス流量調節機構１０を設け、被処理体温度又
は炉内ガス温度を測定する温度センサ１３と、温度セン
サ１３の温度信号より時間変化率を演算する時間変化率
演算部１４と、被処理体８ の比表面積及び熱容量及び
冷却開始時の炉内ガス温度、圧力より算出される規定冷
却速度に時間変化率が一致するように循環ガス流量調節
機構１０を作動させる制御部１８とを備えたものである
。[Means for Solving the Problems] The present invention provides a high pressure vessel 3
A heat insulating layer 5 is disposed within the high pressure vessel 3 with a gap 4 therebetween, and a heater 6 is disposed within the heat insulating layer 5 to form a furnace chamber 7. Hot isostatic pressure treatment is performed by introducing high temperature and high pressure pressure medium gas onto the object to be processed 8 in the furnace chamber 7 and heating it with the heater 6. In the pressurizing device, high-temperature pressurized gas in the furnace chamber 7 is guided to the outside from the upper part of the heat insulating layer 5 , and is caused to flow down along the inner wall of the high pressure vessel 3 to form the heat insulating layer 5 .
A circulating gas flow rate adjustment mechanism 10 is provided in the middle of a pressure medium gas circulation path 12 leading from the lower part of the chamber into the furnace chamber 7, and a temperature sensor 13 for measuring the temperature of the object to be treated or the temperature of the gas in the furnace and a temperature signal of the temperature sensor 13 are provided. The time change rate calculation unit 14 calculates the time change rate, and the time change rate is calculated so that the time change rate matches the specified cooling rate calculated from the specific surface area and heat capacity of the object to be processed 8 and the furnace gas temperature and pressure at the time of starting cooling. and a control section 18 that operates the circulating gas flow rate adjustment mechanism 10.
【０００９】[0009]
【作用】冷却期間中、温度センサ１３により被処理体温
度又は炉内ガス温度を測定し、演算部１４により温度の
時間変化率を求める。そして、この時間変化率が、比表
面積及び熱容量及び冷却開始時の炉内ガス温度、圧力よ
り算出される規定冷却速度に一致するように、制御部１
８により循環ガス流量調節機構１０を作動させ、循環ガ
ス流量を調節する。[Operation] During the cooling period, the temperature sensor 13 measures the temperature of the object to be processed or the temperature of the gas in the furnace, and the calculating section 14 calculates the rate of change in temperature over time. Then, the controller 1 controls the rate of change over time to match the specified cooling rate calculated from the specific surface area, heat capacity, and furnace gas temperature and pressure at the start of cooling.
8 operates the circulating gas flow rate adjustment mechanism 10 to adjust the circulating gas flow rate.
【００１０】0010
【実施例】以下、本発明の実施例を図面に基づいて詳述
する。図１において、９は循環ガス流量調節機構１０を
構成する電動アクチュエータ付きのバルブで、炉室７
内の高温の圧媒ガスを断熱層５ の上部から蓄熱器１１
を経て外部に導き、高圧容器３ の内壁に沿って間隙４
を下方に流下させて断熱層５ の下部から炉室７ 内
に導く圧媒ガス循環路１２の途中、即ち断熱層５ の下
部に複数個設けられている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Examples of the present invention will be described below in detail with reference to the drawings. In FIG. 1, reference numeral 9 denotes a valve with an electric actuator that constitutes the circulating gas flow rate adjustment mechanism 10.
The high temperature pressurized gas inside the heat storage layer 11 is transferred from the top of the heat insulating layer 5
is guided to the outside through the gap 4 along the inner wall of the high pressure vessel 3.
A plurality of pressurized gas circulation paths 12 are provided in the middle of the pressurized gas circulation path 12 that flows downward into the furnace chamber 7 from the lower part of the heat insulating layer 5, that is, in the lower part of the heat insulating layer 5.
【００１１】１３は炉室７ 内のガス温度を測定する温
度センサ、１４は時間変化率演算部で、温度センサ１３
で測定された炉内ガス温度Ｔの温度信号より、その時間
変化率ｄＴ／ｄｔを演算するようになっている。１５は
規定冷却速度演算部で、容器及び炉体サイズ、容器許容
温度、被処理体８の比表面積（表面積／重量）及び被処
理体８ の熱容量及び冷却開始時の炉内ガス温度、圧力
より、各装置毎に予め規定冷却速度Ｖを演算し算出する
ためのものである。例えば、冷却速度として炉内のガス
温度降下速度をとった場合、これに対する影響因子は、
表１に示す通りである。従って、容器サイズ、容器許容
温度、炉内熱容量及び被処理物比表面積を条件にして規
定冷却速度Ｖが演算される。但し、容器許容温度と容器
，炉体サイズは定数である。13 is a temperature sensor that measures the gas temperature in the furnace chamber 7; 14 is a time change rate calculating section;
From the temperature signal of the furnace gas temperature T measured at , the time rate of change dT/dt is calculated. Reference numeral 15 denotes a specified cooling rate calculation unit, which calculates the temperature based on the container and furnace body size, the allowable temperature of the container, the specific surface area (surface area/weight) of the object to be processed 8, the heat capacity of the object to be processed 8, and the gas temperature and pressure in the furnace at the start of cooling. , for calculating the specified cooling rate V for each device in advance. For example, if we take the gas temperature drop rate in the furnace as the cooling rate, the influencing factors for this are:
As shown in Table 1. Therefore, the specified cooling rate V is calculated based on the container size, the allowable temperature of the container, the heat capacity in the furnace, and the specific surface area of the object to be treated. However, the allowable temperature of the container and the size of the container and furnace body are constants.
【００１２】0012
【表１】[Table 1]
【００１３】１６は規定冷却速度Ｖと時間変化率とを比
較する比較部、１７は比較部１６の出力により働く調節
器であり、これらにより規定冷却速度Ｖに時間変化率が
一致するようにバルブ９ を作動させる制御部１８が構
成されている。次に規定冷却速度Ｖの導出方法を説明す
る。被処理体８ を処理した後、冷却するに際しては、
冷却開始から終了までの間を微小時間に区切り、その微
小時間内にガス循環によって蓄熱器１１、上蓋１ 、高
圧容器３ へ放出される放熱量は、計算によって求める
ことができる。また、この放熱量がその時間内に炉内の
被処理体８ 、ヒータ６ 等の炉内構造物、炉内ガスか
ら奪われる熱量と等しいとして、炉内の被処理体８ 、
ヒータ６ 、炉内ガスの温度降下を計算できる。そして
、このようにして求めた微小時間後の炉内の被処理体８
、ヒータ６ 、炉内ガスの温度を元に、次の微小時間
での各部の放熱量を再び求めることができる。Reference numeral 16 denotes a comparator for comparing the prescribed cooling rate V and the time rate of change, and 17 denotes a regulator that operates based on the output of the comparator 16, which adjusts the valve so that the rate of change over time matches the prescribed cooling rate V. A control section 18 is configured to operate 9. Next, a method for deriving the specified cooling rate V will be explained. When cooling the object 8 after processing,
The time period from the start to the end of cooling can be divided into minute periods of time, and the amount of heat released to the heat storage device 11, the upper lid 1, and the high-pressure vessel 3 through gas circulation within each minute period can be determined by calculation. Furthermore, assuming that this amount of heat radiation is equal to the amount of heat removed from the object to be processed 8 in the furnace, the structures in the furnace such as the heater 6, and the gas in the furnace within that time, the object to be processed in the furnace 8,
Heater 6 can calculate the temperature drop of the gas in the furnace. Then, the object to be processed 8 in the furnace after the minute time determined in this way
, heater 6, and the temperature of the gas in the furnace, the amount of heat dissipated from each part in the next minute time can be determined again.
【００１４】上記のような計算を繰返すことにより、炉
内温度の冷却過程をトレースできることになり、冷却速
度も求まる。図２は上記過程を示すフローチャートであ
る。図２において、容器サイズ、炉内熱容量、被処理体
比表面積の入力データがあり（ステップＳ１）、更に或
る冷却速度に対応すると考えられる循環風量を仮初期値
として入力する（ステップ３）。なお、炉内熱容量は、
被処理体熱容量、冷却開始時炉内ガス温度、圧力から求
められるので、実際にはこれらを入力する。そして、微
小時間Δｔ秒間の放熱及び容器内面温度を計算し（ステ
ップＳ４）、Δｔ秒後の被処理体温度を計算した後（ス
テップＳ５）、炉内ガス温度の低下速度と冷却速度設定
値とを比較する（ステップＳ６）。この比較を行った結
果、両者が等しくなければ、循環風量を設定し直して（
ステップＳ７）、ステップＳ４に戻り、また等しければ
Δｔ秒後の状態にデータを置き換える（ステップＳ８）
。そして、次に炉内温度と冷却終了温度との大小関係を
求め（ステップＳ９）、炉内温度が大であればステップ
Ｓ４に戻り、また小であれば終わる。このような計算に
より設定冷却速度に対する循環風景が求まる。By repeating the above calculations, the cooling process of the furnace temperature can be traced, and the cooling rate can also be determined. FIG. 2 is a flowchart showing the above process. In FIG. 2, there is input data such as the container size, the heat capacity in the furnace, and the specific surface area of the object to be treated (step S1), and furthermore, the circulating air volume that is considered to correspond to a certain cooling rate is input as a temporary initial value (step 3). In addition, the heat capacity inside the furnace is
It is determined from the heat capacity of the object to be processed, the gas temperature in the furnace at the start of cooling, and the pressure, so these are actually input. Then, after calculating the heat dissipation and the inner surface temperature of the container for a minute time of Δt seconds (step S4), and calculating the temperature of the object to be processed after Δt seconds (step S5), the decreasing rate of the furnace gas temperature and the cooling rate set value are calculated. are compared (step S6). As a result of this comparison, if the two are not equal, reset the circulating air volume (
Step S7), return to step S4, and if they are equal, replace the data with the state after Δt seconds (step S8)
. Then, the magnitude relationship between the furnace temperature and the cooling end temperature is determined (step S9), and if the furnace temperature is high, the process returns to step S4, and if it is low, the process ends. Through such calculations, the circulation landscape for the set cooling rate can be determined.
【００１５】設定冷却速度の値及び炉内の熱容量、比表
面積を色々変えて計算すると、容器サイズ毎に図３に示
すようなグラフが得られる。容器については、金属材料
の強度面から許容最高温度Ｔ℃が設計面から決定される
（ 通常 １５０℃〜 ２００℃） 、許容最高温度Ｔ
℃が決まれば図３より炉内熱容量と最高冷却速度の関係
が求まる。こうして得られるのが図４である。即ち最高
冷却速度は容器温度が許容値を超えない範囲の最高冷却
速度である。When calculations are made by varying the set cooling rate, the heat capacity in the furnace, and the specific surface area, a graph as shown in FIG. 3 is obtained for each container size. For containers, the maximum allowable temperature T°C is determined from the design aspect based on the strength of the metal material (usually 150°C to 200°C).
Once the temperature is determined, the relationship between the heat capacity inside the furnace and the maximum cooling rate can be determined from Figure 3. FIG. 4 is thus obtained. That is, the maximum cooling rate is the highest cooling rate within a range where the container temperature does not exceed the permissible value.
【００１６】図４で求まる最高速度が規定冷却速度であ
る。図４は容器サイズや容器の許容温度が変われば異な
る。逆に一つの装置について、図４のグラフが一つ決ま
ることになる。上記では理解の助けのためグラフ等を用
いたが、実際にはこの過程は計算機内で演算される。冷
却時の制御は、図５に示すフローチャートのように行わ
れる。各チャージ毎に熱容量、比表面積冷却開始ガス温
度、圧力を入力し（ステップＳ１０） 、これより冷却
開始時の炉内熱容量が求まる（Ｓ１０ ，） 。これよ
り予め計算されたガス規定冷却速度のデータから入力値
に見合う冷却速度Ｖｓ （＝一定） が選定される（ス
テップＳ１１） 。
一方、温度センサ１３により炉内のガス温度Ｔｇを測定
し（ステップＳ１２） 、演算部１４でＴｇの時間変化
率Ｖｍを計算する（ステップＳ１３）。そして、比較部
１６で冷却速度Ｖｓと時間変化率Ｖｍとを比較し（ステ
ップＳ１４） 、規定冷却速度Ｖｓが時間変化率Ｖｍよ
り大であれば、調節器１７によりバルブ９ を一定量だ
け開け、また逆であればバルブ９ を一定量だけ閉じる
。なお、実際の制御に当っては、｜Ｖｓ−Ｖｍ｜の値に
比例してバルブ９ を動作させたり、冷却初期の過渡期
間は別の制御方法をとる等の状況に応じた処置をとるの
は勿論である。The maximum speed found in FIG. 4 is the specified cooling rate. Figure 4 differs depending on the container size and allowable temperature of the container. Conversely, one graph in FIG. 4 is determined for one device. In the above, graphs and the like are used to aid understanding, but in reality, this process is calculated within a computer. Control during cooling is performed as shown in the flowchart shown in FIG. The heat capacity, specific surface area, cooling start gas temperature, and pressure are input for each charge (step S10), and from these, the furnace heat capacity at the start of cooling is determined (S10,). From this, a cooling rate Vs (=constant) corresponding to the input value is selected from data on the gas prescribed cooling rate calculated in advance (step S11). On the other hand, the temperature sensor 13 measures the gas temperature Tg in the furnace (step S12), and the calculation unit 14 calculates the temporal change rate Vm of Tg (step S13). Then, the comparison section 16 compares the cooling rate Vs and the time rate of change Vm (step S14), and if the prescribed cooling rate Vs is greater than the time rate of change Vm, the regulator 17 opens the valve 9 by a certain amount. If the opposite is true, valve 9 is closed by a certain amount. In actual control, measures may be taken depending on the situation, such as operating the valve 9 in proportion to the value of |Vs-Vm| or using a different control method during the initial transient period of cooling. Of course.
【００１７】このようにすれば、ガスから容器内面への
熱流束を略一定にして最も効率の良い冷却を行うことが
可能である。炉内の冷却速度を一定に保ち得ることは、
炉内からの放熱量が略一定になることを意味している。
炉内からの放熱量は蓄熱器１１や炉外の低温ガスとの熱
交換があり、厳密な意味で容器系外への放熱量と全く同
じではないが、冷却過程のトータルで見れば同じとみな
しても良く、即ち容器への熱流束を略一定値に保つこと
につながり、容器温度上昇を最小限に抑えた放熱が可能
となる。[0017] In this way, it is possible to keep the heat flux from the gas to the inner surface of the container substantially constant, thereby achieving the most efficient cooling. Being able to maintain a constant cooling rate in the furnace means that
This means that the amount of heat released from inside the furnace is approximately constant. The amount of heat released from inside the furnace involves heat exchange with the heat storage device 11 and the low-temperature gas outside the furnace, so in a strict sense it is not exactly the same as the amount of heat released outside the container system, but if you look at the total cooling process, it is the same. In other words, it leads to keeping the heat flux to the container at a substantially constant value, and it becomes possible to dissipate heat while minimizing the rise in the temperature of the container.
【００１８】図６は本発明の別の実施例を示す。この図
６に示すように、炉室７ 内の下部に、インバータ２１
制御型のモータ１９により駆動されるファン２０を設け
、循環ガス流をファン２０によって強制対流させるよう
にしてもよい。この場合、循環ガス流量の調節は、ファ
ン２０の回転数を変化させて行うこともできる。従って
、断熱層５ の下部のバルブ９ は開閉機能のみを有す
るものにできる。FIG. 6 shows another embodiment of the invention. As shown in FIG. 6, an inverter 21 is installed at the bottom of the furnace chamber 7.
A fan 20 driven by a controlled motor 19 may be provided, with forced convection of the circulating gas flow. In this case, the circulating gas flow rate can also be adjusted by changing the rotation speed of the fan 20. Therefore, the valve 9 under the heat insulating layer 5 can be made to have only an opening/closing function.
【００１９】また開度調節可能なバルブ９ の代わりに
、開閉バルブを複数個設けて、開と閉のバルブ個数の配
分を変化させて循環ガス流量を制御するようにしても良
い。さらに、本実施例では、炉内ガス温度を測定してい
るが、被処理体の温度を測定し、これにより時間変化率
を演算するようにしてもよい。Furthermore, instead of the valve 9 whose opening degree can be adjusted, a plurality of open/close valves may be provided, and the distribution of the number of open and closed valves may be changed to control the circulating gas flow rate. Further, in this embodiment, the temperature of the gas in the furnace is measured, but the temperature of the object to be processed may be measured and the time rate of change may be calculated based on this.
【００２０】[0020]
【発明の効果】本発明によれば、炉室７ 内の高温の圧
媒ガスを断熱層５ の上部から外部に導き、高圧容器３
の内壁に沿って流下させて断熱層５ の下部から炉室
７ 内に導く圧媒ガス循環路１２の途中に循環ガス流量
調節機構１０を設け、被処理体温度又は炉内ガス温度を
測定する温度センサ１３と、温度センサ１３の温度信号
より時間変化率を演算する時間変化率演算部１４と、被
処理体８ の比表面積及び熱容量及び冷却開始時の炉内
ガス温度、圧力より算出される規定冷却速度に時間変化
率が一致するように循環ガス流量調節機構１０を作動さ
せる制御部１８とを備えているので、冷却過程中のガス
から容器内壁への熱流束を略一定にでき、容器温度上昇
を最小限に抑えた放熱が可能となる。According to the present invention, the high-temperature pressure medium gas in the furnace chamber 7 is guided to the outside from the upper part of the heat insulating layer 5, and the high-pressure vessel 3
A circulating gas flow rate adjustment mechanism 10 is provided in the middle of a pressure gas circulation path 12 that flows down along the inner wall of the heat insulating layer 5 and leads into the furnace chamber 7, and measures the temperature of the object to be treated or the temperature of the gas in the furnace. Calculated from the temperature sensor 13, the time change rate calculation unit 14 that calculates the time change rate from the temperature signal of the temperature sensor 13, the specific surface area and heat capacity of the object to be processed 8, and the furnace gas temperature and pressure at the start of cooling. Since it is equipped with a control unit 18 that operates the circulating gas flow rate adjustment mechanism 10 so that the time rate of change matches the prescribed cooling rate, the heat flux from the gas to the inner wall of the container during the cooling process can be kept approximately constant, and the It is possible to dissipate heat while minimizing temperature rise.
【図１】本発明に係る冷却制御装置を示す構成図である
。FIG. 1 is a configuration diagram showing a cooling control device according to the present invention.
【図２】規定冷却速度を求めるフローチャートである。FIG. 2 is a flowchart for determining a prescribed cooling rate.
【図３】容器内面最高上昇温度と冷却速度との関係を示
す図である。FIG. 3 is a diagram showing the relationship between the maximum temperature rise inside the container and the cooling rate.
【図４】炉内熱容量と規定冷却速度との関係を示す図で
ある。FIG. 4 is a diagram showing the relationship between furnace heat capacity and specified cooling rate.
【図５】制御動作のフローチャートである。FIG. 5 is a flowchart of control operation.
【図６】本発明に係る冷却制御装置の別の実施例を示す
構成図である。FIG. 6 is a configuration diagram showing another embodiment of the cooling control device according to the present invention.
【図７】熱間等方圧加圧装置の断面図である。FIG. 7 is a sectional view of a hot isostatic pressing device.
【図８】容器最高温度と平均熱流束との関係を示す図で
ある。FIG. 8 is a diagram showing the relationship between container maximum temperature and average heat flux.
３ 高圧容器 ５ 断熱層 ６ ヒータ ８ 被処理体 １０ 循環ガス流量調節機構 １２ 圧媒ガス循環路 １３ 温度センサ １４ 時間変化率演算部 １８ 制御部 3 High pressure container 5 Heat insulation layer 6 Heater 8 Object to be processed 10 Circulating gas flow rate adjustment mechanism 12 Pressure gas circulation path 13 Temperature sensor 14 Time change rate calculation section 18 Control section
Claims (1)
３） との間に間隙（４） をおいて断熱層（５） を
配設すると共に、断熱層（５）内にヒータ（６） を配
設して炉室（７） を構成し、炉室（７）内に高圧の圧
媒ガスを導入しヒータ（６） で加熱することにより、
炉室（７） 内の被処理体（８） に高温高圧の圧媒ガ
スを作用させて熱間等方圧加圧処理を行う熱間等方圧加
圧装置において、炉室（７） 内の高温の圧媒ガスを断
熱層（５） の上部から外部に導き、高圧容器（３）
の内壁に沿って流下させて断熱層（５） の下部から炉
室（７） 内に導く圧媒ガス循環路（１２）の途中に循
環ガス流量調節機構（１０）を設け、被処理体温度又は
炉内ガス温度を測定する温度センサ（１３）と、温度セ
ンサ（１３）の温度信号より時間変化率を演算する時間
変化率演算部（１４）と、被処理体（８） の比表面積
及び熱容量及び冷却開始時の炉内ガス温度、圧力より算
出される規定冷却速度に時間変化率が一致するように循
環ガス流量調節機構（１０）を作動させる制御部（１８
）とを備えたことを特徴とする熱間等方圧加圧装置の冷
却制御装置。Claim 1: Inside the high pressure vessel (3), the high pressure vessel (
3) A heat insulating layer (5) is provided with a gap (4) between the heat insulating layer (5) and a heater (6) is provided within the heat insulating layer (5) to form a furnace chamber (7). By introducing high-pressure pressure medium gas into the chamber (7) and heating it with the heater (6),
In a hot isostatic pressurizing device that performs hot isostatic pressurization treatment by applying high temperature and high pressure pressure medium gas to a workpiece (8) in the furnace chamber (7), The high-temperature pressure medium gas is led to the outside from the top of the heat insulating layer (5), and
A circulating gas flow rate adjustment mechanism (10) is provided in the middle of a pressure gas circulation path (12) that flows down along the inner wall of the heat insulating layer (5) and leads into the furnace chamber (7). or a temperature sensor (13) that measures the furnace gas temperature, a time rate of change calculation unit (14) that calculates the rate of change over time from the temperature signal of the temperature sensor (13), and a specific surface area of the object to be processed (8). A control unit (18) that operates the circulating gas flow rate adjustment mechanism (10) so that the rate of change over time matches the prescribed cooling rate calculated from the heat capacity and the furnace gas temperature and pressure at the start of cooling.
) A cooling control device for a hot isostatic pressurizing device.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3020147A JPH04260783A (en) | 1991-02-13 | 1991-02-13 | Cooling controller for hot isotropic pressurizer |
| DE19924203959 DE4203959A1 (en) | 1991-02-13 | 1992-02-11 | Gas flow regulator to limit temperature rise in isostatic hot pressing system |
| FR9201619A FR2672669A1 (en) | 1991-02-13 | 1992-02-13 | Cooling control device for a hot isostatic-compression installation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3020147A JPH04260783A (en) | 1991-02-13 | 1991-02-13 | Cooling controller for hot isotropic pressurizer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH04260783A true JPH04260783A (en) | 1992-09-16 |
Family
ID=12019043
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3020147A Pending JPH04260783A (en) | 1991-02-13 | 1991-02-13 | Cooling controller for hot isotropic pressurizer |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH04260783A (en) |
| DE (1) | DE4203959A1 (en) |
| FR (1) | FR2672669A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11298905B2 (en) | 2017-03-23 | 2022-04-12 | Quintus Technologies Ab | Pressing arrangement |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3914442A1 (en) * | 2019-01-25 | 2021-12-01 | Quintus Technologies AB | A method in a pressing arrangement |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE398984B (en) * | 1976-05-25 | 1978-01-30 | Asea Ab | OVEN FOR TREATMENT OF MATERIAL AT HIGH TEMPERATURE IN A GAS ATMOSPHERE HIGH |
| JPS6033195U (en) * | 1983-08-11 | 1985-03-06 | 株式会社神戸製鋼所 | Hot isostatic pressurization device |
| US4532984A (en) * | 1984-06-11 | 1985-08-06 | Autoclave Engineers, Inc. | Rapid cool autoclave furnace |
| DE3833337A1 (en) * | 1988-09-30 | 1990-04-05 | Dieffenbacher Gmbh Maschf | Apparatus for rapid cooling of workpieces and of the pressure container in an HIP plant |
-
1991
- 1991-02-13 JP JP3020147A patent/JPH04260783A/en active Pending
-
1992
- 1992-02-11 DE DE19924203959 patent/DE4203959A1/en not_active Withdrawn
- 1992-02-13 FR FR9201619A patent/FR2672669A1/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11298905B2 (en) | 2017-03-23 | 2022-04-12 | Quintus Technologies Ab | Pressing arrangement |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2672669A1 (en) | 1992-08-14 |
| DE4203959A1 (en) | 1992-09-03 |
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