JPH1194382A - Pulse tube refrigerator - Google Patents
Pulse tube refrigeratorInfo
- Publication number
- JPH1194382A JPH1194382A JP27188897A JP27188897A JPH1194382A JP H1194382 A JPH1194382 A JP H1194382A JP 27188897 A JP27188897 A JP 27188897A JP 27188897 A JP27188897 A JP 27188897A JP H1194382 A JPH1194382 A JP H1194382A
- Authority
- JP
- Japan
- Prior art keywords
- refrigeration unit
- pulse tube
- heat exchanger
- temperature heat
- working gas
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
- F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1407—Pulse-tube cycles with pulse tube having in-line geometrical arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
- F25B2309/14241—Pulse tubes with basic schematic including an orifice reservoir multiple inlet pulse tube
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1425—Pulse tubes with basic schematic including several pulse tubes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/13—Vibrations
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は，往復運動するピス
トンによる振動を抑制すると共に，寒冷発生量を増大さ
せたパルスチューブ冷凍機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pulse tube refrigerator which suppresses vibration caused by a reciprocating piston and increases the amount of generated cold.
【０００２】[0002]
【従来の技術】従来，冷凍機としては種々の構造が提案
され，なかでも構成が簡単で極低温が達成できる可能性
を秘めたものとしてパルスチューブを用いた冷凍機が提
案されている。当該冷凍機には，ベーシック型，オリフ
ィス型，ダブルインレット型等種々の構造がある。2. Description of the Related Art Conventionally, various types of refrigerators have been proposed. Among them, a refrigerator using a pulse tube has been proposed as having a simple structure and a possibility of achieving extremely low temperatures. The refrigerator has various structures such as a basic type, an orifice type and a double inlet type.
【０００３】図４は，オリフィス型パルスチューブ冷凍
機の断面図で，クランク機構を備えた駆動部１，該駆動
部１から駆動力を受けて往復運動するピストン２，熱伝
導率の高い銅等からなる放熱用熱交換器３，内部に銅や
鉛等の蓄冷材が充填された蓄冷器４，銅などの熱伝導性
の高い材料からなり１００Ｋ以下の極低温を取り出すた
めの低温熱交換器５，ステンレス鋼により形成されたパ
ルスチューブ６，熱伝導率の高い銅等からなる水冷式又
は空冷式の放熱フィンを備えた高温熱交換器７，ニード
ル弁等のオリフィス８及びバッファタンク９５等を主要
構成要素として，これらが順次配管接続された構成とな
っている。FIG. 4 is a cross-sectional view of an orifice type pulse tube refrigerator. A drive unit having a crank mechanism, a piston reciprocating by receiving a driving force from the drive unit 2, copper having a high thermal conductivity, etc. A heat exchanger for heat radiation consisting of a heat exchanger 3, a regenerator filled with a regenerator material such as copper or lead 4, and a low-temperature heat exchanger made of a material having high thermal conductivity such as copper for extracting an extremely low temperature of 100K or less. 5, a pulse tube 6 made of stainless steel, a high-temperature heat exchanger 7 having a water-cooled or air-cooled radiating fin made of copper or the like having a high thermal conductivity, an orifice 8 such as a needle valve, and a buffer tank 95. As main components, these are sequentially connected by piping.
【０００４】なお，オリフィス８は，高温熱交換器７と
バッファタンク９とを連結する配管１０の途中に設けら
れている。The orifice 8 is provided in the middle of a pipe 10 connecting the high-temperature heat exchanger 7 and the buffer tank 9.
【０００５】上記の構成において，ピストン２が，駆動
部１から駆動力を受けて往復運動し，これによりヘリウ
ム等の作動ガスを圧縮／膨張している。In the above configuration, the piston 2 reciprocates upon receiving a driving force from the driving section 1, thereby compressing / expanding a working gas such as helium.
【０００６】即ち，ピストン２が上動（図８において上
方向）する圧縮過程により，作動ガスは圧縮されて，放
熱用熱交換器３及び蓄冷器４側に押込まれる。そして，
当該放熱用熱交換器３で作動ガスは外気に放熱し，その
後蓄冷器４と熱交換して冷却され，パルスチューブ６に
流入する。That is, in the compression process in which the piston 2 moves upward (upward in FIG. 8), the working gas is compressed and pushed into the heat-radiating heat exchanger 3 and the regenerator 4. And
The working gas radiates heat to the outside air in the heat radiating heat exchanger 3, is then cooled by exchanging heat with the regenerator 4, and flows into the pulse tube 6.
【０００７】当該作動ガスの流入に伴い，パルスチュー
ブ６内の作動ガスはオリフィス８を介してバッファタン
ク９に流入する。その膨張に伴い寒冷が発生する。[0007] With the inflow of the working gas, the working gas in the pulse tube 6 flows into the buffer tank 9 through the orifice 8. Cold occurs with the expansion.
【０００８】一方，ピストン２が下動（図３に於いて下
方向）する膨張過程により，パルスチューブ６内の作動
ガスは吸引されて更に膨張し，寒冷を発生する。On the other hand, due to the expansion process in which the piston 2 moves downward (downward in FIG. 3), the working gas in the pulse tube 6 is sucked and further expanded to generate cold.
【０００９】発生した寒冷により，低温熱交換器５に負
荷が設けられている場合には，当該負荷を冷すことが可
能になる。また，オリフィス８からの作動ガスの戻りに
より冷凍サイクルが形成される。When a load is provided in the low-temperature heat exchanger 5 due to the generated cold, the load can be cooled. The return of the working gas from the orifice 8 forms a refrigeration cycle.
【００１０】そこで，パルスチューブ冷凍機において，
寒冷の発生量を増加させるためには，パルスチューブ６
内の作動ガスの圧力変動とバッファタンク９の作動ガス
の変位とに位相差を持たせる必要がある。Therefore, in a pulse tube refrigerator,
To increase the amount of cold generated, use a pulse tube 6
It is necessary to provide a phase difference between the pressure fluctuation of the working gas in the inside and the displacement of the working gas in the buffer tank 9.
【００１１】このようなことから，図８において点線で
示すダブルインレット用配管１１によりピストン２側の
圧縮空間Ｓと高温熱交換器７とを連結し，当該ダブルイ
ンレット用配管１１にオリフィス１２を設けたダブルイ
ンレット型パルスチューブ冷凍機が提案されている。For this reason, the compression space S on the piston 2 side and the high-temperature heat exchanger 7 are connected by the double inlet pipe 11 shown by the dotted line in FIG. 8, and the orifice 12 is provided in the double inlet pipe 11. In addition, a double inlet type pulse tube refrigerator has been proposed.
【００１２】当該パルスチューブ冷凍機では，ピストン
２が上動すると圧縮された作動ガスは，蓄冷器３内を通
ってパルスチューブ６内へ流れ込むと共に，ダブルイン
レット用配管１１を介してパルスチューブ６及びバッフ
ァタンク９に流入する。In the pulse tube refrigerator, when the piston 2 moves upward, the compressed working gas flows into the pulse tube 6 through the regenerator 3 and at the same time, the pulse tube 6 and the It flows into the buffer tank 9.
【００１３】また，ピストン２が下動すると，パルスチ
ューブ６内の作動ガスは，蓄冷器３及びダブルインレッ
ト用配管１１を通って流出する。When the piston 2 moves down, the working gas in the pulse tube 6 flows out through the regenerator 3 and the pipe 11 for the double inlet.
【００１４】これにより，前述した位相差を大きくする
ことができて，パルスチューブ６内を流動する作動ガス
の流量を増大させることが可能になる。そして，オリフ
ィス８，１２の開度を調節することによって，作動ガス
の流量を最適に調整すれば寒冷の発生量を多することが
できる。As a result, the above-described phase difference can be increased, and the flow rate of the working gas flowing in the pulse tube 6 can be increased. By adjusting the opening of the orifices 8 and 12 to optimize the flow rate of the working gas, the amount of cold generated can be increased.
【００１５】このような作動ガスの流れにより，寒冷の
一部は低温熱交換器４を介して負荷を冷却し，残りは作
動ガスが逆の経路で戻るときに蓄冷材７を冷却するのに
供される。Due to such a flow of the working gas, a part of the refrigeration cools the load through the low-temperature heat exchanger 4 and the rest cools the cold storage material 7 when the working gas returns in the reverse route. Provided.
【００１６】[0016]
【発明が解決しようとする課題】しかしながら，上記構
成ではピストンの往復運動に伴う振動が発生する問題が
あった。However, the above configuration has a problem that vibrations are generated due to the reciprocating motion of the piston.
【００１７】また，蓄冷器等を通過する作動ガスの流量
は，ピストン２の移動量によって制限されるため，これ
を十分に大きくすることが困難となる問題がある。Further, since the flow rate of the working gas passing through the regenerator or the like is limited by the moving amount of the piston 2, there is a problem that it is difficult to sufficiently increase the flow rate.
【００１８】そこで，本発明は，ピストンの往復運動に
伴う振動を抑えると共に，寒冷発生量を大きくことがで
きるパルスチューブ冷凍機を提供することを目的とす
る。Accordingly, an object of the present invention is to provide a pulse tube refrigerator capable of suppressing vibration caused by reciprocation of a piston and increasing the amount of cold generated.
【００１９】[0019]
【課題を解決するための手段】本発明は，上記課題を解
決するため，請求項１にかかる発明は，第１冷凍部及び
第２冷凍部を，駆動力を受けて往復運動するピストン
と，該ピストンの往復運動により圧縮／膨張した作動ガ
スと熱交換する蓄冷器と，寒冷を取出す低温熱交換器
と，作動ガスが圧縮／膨張するパルスチューブと，作動
ガスと熱交換して外部に放熱する高温熱交換器とを直列
接続して形成する。そして，当該第１冷凍部及び第２冷
凍部を１対として冷凍部を構成し，当該冷凍部をＮ対
（Ｎ＝１，２…）設ける。さらに，第１冷凍部と第２冷
凍部とのピストンの位相を１８０度ずらす。これによ
り，第１冷凍部及び第２冷凍部の各ピストンが往復運動
した際の振動を相互に打消すように作用させて静音化を
図ったことを特徴とする。According to the present invention, in order to solve the above-mentioned problems, a first aspect of the present invention provides a first refrigeration unit and a second refrigeration unit, which reciprocate by receiving a driving force; A regenerator that exchanges heat with the working gas that has been compressed / expanded by the reciprocating motion of the piston, a low-temperature heat exchanger that extracts cold, a pulse tube that compresses / expands the working gas, and exchanges heat with the working gas to release heat to the outside. And a high temperature heat exchanger to be connected in series. The first freezing section and the second freezing section constitute a pair to form a freezing section, and the freezing sections are provided in N pairs (N = 1, 2,...). Further, the phases of the pistons of the first freezing section and the second freezing section are shifted by 180 degrees. Thus, the first and second refrigerating sections are characterized in that the pistons of the reciprocating section act so as to cancel each other out of vibration, thereby reducing noise.
【００２０】請求項２にかかる発明は，第１冷凍部の高
温熱交換器と第２冷凍部の高温熱交換器とを相互に連通
する冷凍部連結用配管を設けて，当該第１冷凍部と第２
冷凍部との大きな圧力差を利用して作動ガスの移動量の
増大を図り，これにより寒冷発生量を増大させたことを
特徴とする。According to a second aspect of the present invention, there is provided a refrigeration unit connecting pipe for interconnecting the high temperature heat exchanger of the first refrigeration unit and the high temperature heat exchanger of the second refrigeration unit. And the second
The present invention is characterized in that the amount of movement of the working gas is increased by utilizing a large pressure difference from the refrigeration unit, thereby increasing the amount of cold generated.
【００２１】請求項３にかかる発明は，冷凍部連結用配
管の配管途中に，当該配管を流動する作動ガスの流量を
調整するオリフィスを設けて，寒冷発生量が最大になる
ように流量調整を可能にしたことを特徴とする。According to a third aspect of the present invention, an orifice for adjusting the flow rate of the working gas flowing through the pipe is provided in the middle of the pipe for connecting the refrigeration section, and the flow rate is adjusted so that the amount of generated cold is maximized. It is made possible.
【００２２】請求項４にかかる発明は，第１冷凍部の高
温熱交換器と第２冷凍部の高温熱交換器とを１つのバッ
ファタンクを介して連通したことを特徴とする。The invention according to claim 4 is characterized in that the high-temperature heat exchanger of the first refrigeration unit and the high-temperature heat exchanger of the second refrigeration unit are connected via one buffer tank.
【００２３】請求項５にかかる発明は，第１冷凍部及び
第２冷凍部におけるそれぞれの高温熱交換器と圧縮空間
とがダブルインレット用配管により連結したことを特徴
とする。The invention according to claim 5 is characterized in that the respective high-temperature heat exchangers and the compression space in the first refrigeration section and the second refrigeration section are connected by a double inlet pipe.
【００２４】[0024]
【発明の実施の形態】本発明の実施の形態を図を参照し
て説明する。本発明にかかるパルスチューブ冷凍機は，
ベーシック型，オリフェス型及びダブルインレット型の
パルスチューブのいずれであっても適用可能であり，以
下の説明においては，オリフェス型パルスチューブ冷凍
機を例に説明する。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings. The pulse tube refrigerator according to the present invention comprises:
The present invention can be applied to any of a basic type, an orifice type, and a double inlet type pulse tube. In the following description, an orifice type pulse tube refrigerator will be described as an example.
【００２５】図１は第１の実施の形態にかかるオリフェ
ス型パルス冷凍機の構成図で，同じ構成の第１及び２冷
凍部Ａ，Ｂ，該第１，２冷凍部Ａ，Ｂのピストン２ａ，
２ｂの位相が１８０度異なるクランク機構を備えた駆動
部３０等を有している。FIG. 1 is a block diagram of an orifice-type pulse refrigerator according to a first embodiment. First and second refrigerators A and B having the same structure, and pistons 2a of the first and second refrigerators A and B are shown. ,
The drive unit 30 includes a crank mechanism having a phase difference of 2b by 180 degrees.
【００２６】なお，第１，第２冷凍部Ａ，Ｂの構成の
内，従来の構成と同一構成に関しては同一符号に添字
「a」又は「ｂ」を付して説明を適宜省略する。このと
き，添字「ａ」は第１冷凍部Ａの構成要素を示し，添字
「ｂ」は第２冷凍部Ｂの構成要素であることを示すもの
とする。In the first and second refrigeration units A and B, the same reference numerals as those of the conventional refrigeration units A and B are given the same reference numerals with the suffix "a" or "b", and the description is omitted as appropriate. At this time, the subscript “a” indicates a component of the first freezing section A, and the subscript “b” indicates a component of the second freezing section B.
【００２７】駆動部３０は，クランク機構３１に回転駆
動力を与えるロータ３２，クランク機構３１を潤滑する
ためのオイルを貯留するオイル槽３３，シャフト３４に
取付けられたクランク３５ａ，３５ｂ等を有している。The drive section 30 has a rotor 32 for applying a rotational driving force to the crank mechanism 31, an oil tank 33 for storing oil for lubricating the crank mechanism 31, and cranks 35a and 35b attached to the shaft 34. ing.
【００２８】なお，クランク３５ａ，３５ｂは，シャフ
ト３４に偏心して連結され，かつ，ピストン２ａとピス
トン２ｂとの位相が略１８０度異なるように設定されて
いる。The cranks 35a and 35b are eccentrically connected to the shaft 34, and are set so that the phases of the pistons 2a and 2b are different by approximately 180 degrees.
【００２９】このような構成にすることにより，ピスト
ン２ａ，２ｂによる振動は相互に打消し合うようにな
り，振動を効果的に抑制することが可能になる。With this configuration, the vibrations caused by the pistons 2a and 2b cancel each other, and the vibrations can be effectively suppressed.
【００３０】また，ピストン２ａ，２ｂの背面側は連通
し，各ピストン２ａ，２ｂの位相が１８０度ずれている
ので当該背面側の空間には圧力変動が生じない。このた
め，ピストン２ａ，２ｂとクランク３５ａ，３５ｂとの
間のロッドにオイルシールを設けて，オイルが圧縮空間
Ｓａ，Ｓｂに侵入しないようにした場合には，当該オイ
ルシールとピストン２ａ，２ｂで形成される空間を相互
に連通すれば，オイル槽３３との圧力差を無くすことが
可能になって，効果的にオイルシールを作用させること
が可能になる。Further, the rear sides of the pistons 2a and 2b communicate with each other and the phases of the pistons 2a and 2b are shifted by 180 degrees, so that no pressure fluctuation occurs in the space on the rear side. For this reason, when an oil seal is provided on the rod between the pistons 2a, 2b and the cranks 35a, 35b to prevent oil from entering the compression spaces Sa, Sb, the oil seal and the pistons 2a, 2b are used. If the formed spaces communicate with each other, it is possible to eliminate the pressure difference between the space and the oil tank 33, and it is possible to effectively operate the oil seal.
【００３１】なお，上記説明では，第１，２冷凍部Ａ，
Ｂを持つ場合について説明したが，本発明はこれに限定
されるものではなく，これらを１対としてＮ対（Ｎは正
数）設けても良いことは付言するまでもない。In the above description, the first and second refrigeration units A,
Although the case where B is provided has been described, the present invention is not limited to this, and it goes without saying that N pairs (N is a positive number) may be provided as one pair.
【００３２】次に本発明の第２の実施の形態について説
明する。図２は本実施の形態に係るパルスチューブ冷凍
機の構成図である。なお，第１の実施の形態と同一構成
については同一符号を用いて説明を適宜省略する。Next, a second embodiment of the present invention will be described. FIG. 2 is a configuration diagram of the pulse tube refrigerator according to the present embodiment. Note that the same components as those of the first embodiment are denoted by the same reference numerals, and description thereof will be omitted as appropriate.
【００３３】本実施の形態に係るパルスチューブ型冷凍
機は，バッファタンク等が省略されて，高温熱交換器７
ａ，７ｂを冷凍部連結用配管２１により相互に連結され
た構成となっている。当該冷凍部連結用配管２１の途中
には，オリフィス２２が設けられている。In the pulse tube type refrigerator according to this embodiment, the buffer tank and the like are omitted, and the high-temperature heat exchanger 7 is used.
a and 7b are connected to each other by a refrigeration unit connection pipe 21. An orifice 22 is provided in the middle of the refrigeration unit connection pipe 21.
【００３４】次に，上記構成の作用について説明する
が，第１冷凍部Ａと第２冷凍部Ｂとは，同じ作用を行う
ので，第１冷凍部に注目して説明を行い，第２冷凍部に
ついては説明を省略する。Next, the operation of the above configuration will be described. Since the first refrigeration unit A and the second refrigeration unit B perform the same operation, the description will focus on the first refrigeration unit, and the second refrigeration unit will be described. Description of the parts will be omitted.
【００３５】ピストン２ａが上動して第１冷凍機Ａ内の
作動ガスを圧縮すると，当該作動ガスは蓄冷器４ａ等を
介してパルスチューブ６ａに流入する。このとき，当該
パルスチューブ６ａ内の作動ガスの一部は，オリフィス
２２を介して第２冷凍部Ｂの高温熱交換器７ｂに流入す
る。When the piston 2a moves upward to compress the working gas in the first refrigerator A, the working gas flows into the pulse tube 6a via the regenerator 4a and the like. At this time, a part of the working gas in the pulse tube 6a flows into the high-temperature heat exchanger 7b of the second refrigeration section B via the orifice 22.
【００３６】他方，ピストン２ａが下動して第１冷凍機
Ａ内の作動ガスを膨張させると，当該作動ガスは蓄冷器
４ａ等を介してピストン２ａ側に流動する。このとき，
圧縮過程で第２冷凍部Ｂに流出した作動ガスは第１冷凍
部Ａ側に戻るようになる。On the other hand, when the piston 2a moves down to expand the working gas in the first refrigerator A, the working gas flows toward the piston 2a via the regenerator 4a and the like. At this time,
The working gas flowing out to the second refrigeration section B during the compression process returns to the first refrigeration section A side.
【００３７】ピストン２ａとピストン２ｂとは，位相が
１８０度ずれているので，第１冷凍部Ａが圧縮過程の時
は，第２冷凍部Ｂは膨張過程である。同時に，第２冷凍
部Ｂが圧縮過程の時は，第１冷凍部Ａは膨張過程であ
る。Since the phases of the pistons 2a and 2b are shifted by 180 degrees, when the first refrigeration unit A is in the compression process, the second refrigeration unit B is in the expansion process. At the same time, when the second refrigeration unit B is in the compression process, the first refrigeration unit A is in the expansion process.
【００３８】従って，第１冷凍部Ａから第２冷凍部Ｂに
流動する際の圧力差が大きくなり，第１冷凍部Ａ及び第
２冷凍部Ｂにそれぞれ独立にバッファタンクを設けた場
合に比べ，作動ガスの流量を増大させることができる。
因ってオリフィス２２の開閉度を最適化すれば，低温熱
交換器５ａでの寒冷量を増大させることが可能になる。Therefore, the pressure difference when flowing from the first freezing section A to the second freezing section B becomes large, and compared with the case where the first freezing section A and the second freezing section B are each provided with a buffer tank independently. , The flow rate of the working gas can be increased.
Therefore, by optimizing the degree of opening and closing of the orifice 22, it is possible to increase the amount of cold in the low-temperature heat exchanger 5a.
【００３９】なお，上記説明においては，冷凍部連結用
配管２１を流動する作動ガスの流量をオリフィス２２に
より調整する場合について説明したが，本発明はこれに
限定されるものではない。In the above description, the case where the flow rate of the working gas flowing through the refrigeration unit connecting pipe 21 is adjusted by the orifice 22 has been described, but the present invention is not limited to this.
【００４０】即ち，冷凍部連結用配管２１を流動する作
動ガスの流量は，当該冷凍部連結用配管２１のコンダク
タンスにより規定されると共に，第１冷凍部と第２冷凍
部との圧力関係により依存する。従って，これらのパラ
メータを考慮して冷凍部連結用配管２１の管径や長さ等
が予め最適設計された場合には，当該オリフィス２２は
不用になる。That is, the flow rate of the working gas flowing through the refrigeration unit connection pipe 21 is determined by the conductance of the refrigeration unit connection pipe 21 and depends on the pressure relationship between the first refrigeration unit and the second refrigeration unit. I do. Therefore, when the pipe diameter and length of the refrigeration unit connection pipe 21 are optimally designed in advance in consideration of these parameters, the orifice 22 becomes unnecessary.
【００４１】また，上記説明においてはバッファタンク
を用いない場合について説明した。これによりパルスチ
ューブ冷凍機のコンパクト化が可能になる利点がある
が，本発明はこれに限定されるものではなく，図１に示
すように第１冷凍部と第２冷凍部とにそれぞれ独立した
バッファタンク及びオリフィスを設けることも可能であ
り，また図３に示すように，第１冷凍部と第２冷凍部と
に共通のバッファタンク２０を設けることも可能であ
る。In the above description, the case where the buffer tank is not used has been described. This has the advantage that the pulse tube refrigerator can be made more compact, but the present invention is not limited to this, and the first refrigerator and the second refrigerator are independent as shown in FIG. It is also possible to provide a buffer tank and an orifice, and as shown in FIG. 3, it is also possible to provide a common buffer tank 20 for the first freezing unit and the second freezing unit.
【００４２】図３に示すバッファタンク２０は，オリフ
ィス８ａ，８ｂにより高温熱交換器７ａ，７ｂと連結さ
れている。従って，第１冷凍部Ａ及び第２冷凍部Ｂの低
温熱交換器５ａ，５ｂを流動する作動ガスの位相をその
サイズにより最適な点に調整できて，流量を増大させる
ことができて寒冷量を増大させることができる。The buffer tank 20 shown in FIG. 3 is connected to the high-temperature heat exchangers 7a and 7b by orifices 8a and 8b. Therefore, the phase of the working gas flowing through the low-temperature heat exchangers 5a and 5b of the first freezing section A and the second freezing section B can be adjusted to an optimum point depending on the size, the flow rate can be increased, and the amount of refrigeration can be increased. Can be increased.
【００４３】無論，図４に示すように，冷凍部連結用配
管２１等とバッファタンク２０等とを共に備えて，図２
と図３とを合成した構成とすることも可能である。Of course, as shown in FIG. 4, both the refrigeration section connection pipe 21 and the like and the buffer tank 20 and the like are provided, and FIG.
3 and FIG. 3 can be combined.
【００４４】次に本発明の第３の実施の形態について説
明する。図５は本実施の形態に係るパルスチューブ冷凍
機の構成図である。なお，第１の実施の形態と同一構成
については同一符号を用いて説明を適宜省略する。Next, a third embodiment of the present invention will be described. FIG. 5 is a configuration diagram of the pulse tube refrigerator according to the present embodiment. Note that the same components as those of the first embodiment are denoted by the same reference numerals, and description thereof will be omitted as appropriate.
【００４５】本実施の形態にかかるパルスチューブ冷凍
機は，高温熱交換器７ａ，７ｂと圧縮空間Ｓａ，Ｓｂと
をダブルインレット用配管１１ｂ，１１ｂにより連結し
てダブルインレット型パルスチューブ冷凍機とした場合
を示している。In the pulse tube refrigerator according to the present embodiment, the high-temperature heat exchangers 7a and 7b and the compression spaces Sa and Sb are connected by double inlet pipes 11b and 11b to form a double inlet type pulse tube refrigerator. Shows the case.
【００４６】このような構成にすることにより，本来の
ダブルインレット構成による作用効果に加えて，第２の
実施の形態において説明した作用効果が同時に達成でき
て寒冷発生量を増大させることができるようになる。With this configuration, in addition to the function and effect of the original double inlet structure, the function and effect described in the second embodiment can be simultaneously achieved, and the amount of cold generated can be increased. become.
【００４７】なお，本実施の形態においても，図６に示
すように，共通したバッファタンクを相互に連結した構
成とすることも可能であり，また図７に示すようにこれ
らを共に備えた構成にしても良いことは付言するまでも
ない。In this embodiment, as shown in FIG. 6, a common buffer tank may be connected to each other, and as shown in FIG. Needless to say, it is possible to do so.
【００４８】[0048]
【発明の効果】以上説明したように，請求項１にかかる
発明によれば，第１冷凍部と第２冷凍部とのピストンの
位相を１８０度ずらして設けたので，各ピストンが往復
運動した際の振動を相互に打消すように作用させること
が可能になって静音化が図れる。As described above, according to the first aspect of the present invention, the phases of the pistons of the first refrigeration unit and the second refrigeration unit are shifted by 180 degrees, so that each piston reciprocates. In this case, the vibrations at the time can be made to cancel each other, so that the noise can be reduced.
【００４９】また，第１冷凍部と第２冷凍部とのピスト
ンの背面空間を連結できるので，当該背面空間の圧力変
動を防止することができる。Further, since the space behind the piston of the first freezing section and the second freezing section can be connected to each other, it is possible to prevent pressure fluctuation in the back space.
【００５０】請求項２にかかる発明は，第１冷凍部の高
温熱交換器と第２冷凍部の高温熱交換器とを相互に連通
する冷凍部連結用配管を設けたので，第１冷凍部と第２
冷凍部との大きな圧力差を利用して，これらの間を流動
する作動ガスの流量を増大させて寒冷発生量を増大させ
ることが可能になる。According to the second aspect of the present invention, since the refrigeration unit connecting pipe for connecting the high temperature heat exchanger of the first refrigeration unit and the high temperature heat exchanger of the second refrigeration unit to each other is provided, the first refrigeration unit is provided. And the second
By utilizing a large pressure difference with the refrigeration unit, the flow rate of the working gas flowing between them can be increased to increase the amount of cold generated.
【００５１】また，バッファタンクを用いない場合に
は，装置の小型化を図ることが可能になる。When no buffer tank is used, the size of the apparatus can be reduced.
【００５２】請求項３にかかる発明は，冷凍部連結用配
管の配管途中に，当該配管を流動する作動ガスの流量を
調整するオリフィスを設けたので，寒冷発生量が最大に
なるように流量が調整できるようになる。According to the third aspect of the present invention, since the orifice for adjusting the flow rate of the working gas flowing through the pipe is provided in the middle of the pipe for connecting the refrigeration section, the flow rate is controlled so as to maximize the amount of cold generated. Be able to adjust.
【００５３】請求項４にかかる発明は，第１冷凍部の高
温熱交換器と第２冷凍部の高温熱交換器とを１つのバッ
ファタンクを介して連通したので，部品点数が少なくな
り装置の小型化が図れると共に，位相の最適化が可能に
なる。In the invention according to claim 4, the high-temperature heat exchanger of the first refrigeration unit and the high-temperature heat exchanger of the second refrigeration unit are communicated via one buffer tank, so that the number of parts is reduced, and The size can be reduced, and the phase can be optimized.
【００５４】請求項５にかかる発明は，第１冷凍部及び
第２冷凍部における高温熱交換器と圧縮空間とがダブル
インレット用配管により連結したので，寒冷発生量を増
大させることが可能になる。In the invention according to claim 5, since the high-temperature heat exchanger and the compression space in the first refrigeration section and the second refrigeration section are connected by the double inlet pipe, it is possible to increase the amount of cold generated. .
【図１】本発明の第１の実施の形態の説明に適用される
パルスチューブ冷凍機の断面図である。FIG. 1 is a sectional view of a pulse tube refrigerator applied to the description of a first embodiment of the present invention.
【図２】本発明の第２の実施の形態の説明に適用される
パルスチューブ冷凍機の断面図である。FIG. 2 is a sectional view of a pulse tube refrigerator applied to a description of a second embodiment of the present invention.
【図３】本発明の第２の実施の形態の説明に適用され
る，他の構成のパルスチューブ冷凍機の断面図である。FIG. 3 is a cross-sectional view of a pulse tube refrigerator having another configuration applied to the description of the second embodiment of the present invention.
【図４】本発明の第２の実施の形態の説明に適用され
る，他の構成のパルスチューブ冷凍機の断面図である。FIG. 4 is a sectional view of a pulse tube refrigerator having another configuration applied to the description of the second embodiment of the present invention.
【図５】本発明の第３の実施の形態の説明に適用される
パルスチューブ冷凍機の断面図である。FIG. 5 is a sectional view of a pulse tube refrigerator applied to the description of a third embodiment of the present invention.
【図６】本発明の第３の実施の形態の説明に適用され
る，他の構成のパルスチューブ冷凍機の断面図である。FIG. 6 is a sectional view of a pulse tube refrigerator having another configuration applied to the description of the third embodiment of the present invention.
【図７】本発明の第３の実施の形態の説明に適用され
る，他の構成のパルスチューブ冷凍機の断面図である。FIG. 7 is a cross-sectional view of a pulse tube refrigerator having another configuration applied to the description of the third embodiment of the present invention.
【図８】従来の技術の説明に適用されるパルスチューブ
冷凍機の断面図である。FIG. 8 is a cross-sectional view of a pulse tube refrigerator applied to the description of the related art.
３０ 駆動部 ３５ａ，３５ｂ クランク ２ａ，２ｂ ピストン ３ａ，３ｂ 放熱用熱交換器 ４ａ，４ｂ 蓄冷器 ５ａ，５ｂ 低温熱交換器 ６ａ，６ｂ パルスチューブ ７ａ，７ｂ 高温熱交換器 ８ａ，８ｂ，１２ａ，１２ｂ，２２ オリフィス ９ａ，９ｂ，２０ バッファタンク １０ａ，１０ｂ 配管 １１ａ，１１ｂ ダブルインレット用配管 ２１ 冷凍部連結用配管 30 Drive unit 35a, 35b Crank 2a, 2b Piston 3a, 3b Heat radiating heat exchanger 4a, 4b Cold storage 5a, 5b Low temperature heat exchanger 6a, 6b Pulse tube 7a, 7b High temperature heat exchanger 8a, 8b, 12a, 12b , 22 Orifice 9a, 9b, 20 Buffer tank 10a, 10b Piping 11a, 11b Double inlet piping 21 Piping for connecting refrigeration unit
Claims (5)
と，該ピストンの往復運動により圧縮／膨張した作動ガ
スと熱交換する蓄冷器と，寒冷を取出す低温熱交換器
と，作動ガスが圧縮／膨張するパルスチューブと，作動
ガスと熱交換して外部に放熱する高温熱交換器とが直列
接続されてなる第１冷凍部及び第２冷凍部を１対とした
冷凍部がＮ対（Ｎ＝１，２…）設けられ，かつ，前記第
１冷凍部と第２冷凍部との前記ピストンの位相が１８０
度ずれるように設けられてなることを特徴とするパルス
チューブ冷凍機。A piston that reciprocates by receiving a driving force; a regenerator that exchanges heat with working gas that is compressed / expanded by the reciprocating motion of the piston; a low-temperature heat exchanger that extracts cold; N pairs of refrigeration units (N = N = 1) having a pair of a first refrigeration unit and a second refrigeration unit in which an expanding pulse tube and a high-temperature heat exchanger for exchanging heat with the working gas and radiating heat to the outside are connected in series. 1, 2...) And the phases of the pistons of the first freezing section and the second freezing section are 180
A pulse tube refrigerator characterized by being provided so as to be shifted from one another.
２冷凍部の前記高温熱交換器とを相互に連通する冷凍部
連結用配管を設けたことを特徴とする請求項１記載のパ
ルスチューブ冷凍機。2. A refrigeration unit connection pipe for interconnecting the high-temperature heat exchanger of the first refrigeration unit and the high-temperature heat exchanger of the second refrigeration unit. Pulse tube refrigerator.
該配管を流動する作動ガスの流量を調整するオリフィス
を設けたことを特徴とする請求項２記載のパルスチュー
ブ冷凍機。3. The pulse tube refrigerator according to claim 2, wherein an orifice for adjusting a flow rate of the working gas flowing through the piping is provided in the middle of the piping for connecting the refrigeration unit.
２冷凍部の前記高温熱交換器とが１つのバッファタンク
を介して連通してなることを特徴とする請求項１乃至３
いずれか１項記載のパルスチューブ冷凍機。4. The high-temperature heat exchanger of the first refrigeration unit and the high-temperature heat exchanger of the second refrigeration unit communicate with each other via one buffer tank.
A pulse tube refrigerator according to any one of the preceding claims.
前記高温熱交換器と圧縮空間とがダブルインレット用配
管により連結されてなることを特徴とする請求項１乃至
４いずれか１項記載のパルスチューブ冷凍機。5. The high-temperature heat exchanger and a compression space in the first refrigeration unit and the second refrigeration unit are connected by a double inlet pipe. Pulse tube refrigerator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27188897A JPH1194382A (en) | 1997-09-19 | 1997-09-19 | Pulse tube refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP27188897A JPH1194382A (en) | 1997-09-19 | 1997-09-19 | Pulse tube refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH1194382A true JPH1194382A (en) | 1999-04-09 |
Family
ID=17506303
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP27188897A Pending JPH1194382A (en) | 1997-09-19 | 1997-09-19 | Pulse tube refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH1194382A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100393790B1 (en) * | 2001-02-13 | 2003-08-02 | 엘지전자 주식회사 | Pulstube refrigerator |
| DE10105489B4 (en) * | 2000-02-17 | 2005-03-17 | Lg Electronics Inc. | Pulse tube refrigerator |
| JP2006112260A (en) * | 2004-10-13 | 2006-04-27 | Daikin Ind Ltd | Thermoacoustic engine |
| KR101395285B1 (en) * | 2012-08-30 | 2014-05-15 | 한국과학기술원 | Tandem pulse tube refrigerator to automatically reduce vibration |
| JP2019190678A (en) * | 2018-04-19 | 2019-10-31 | 住友重機械工業株式会社 | Active buffer pulse tube refrigerator |
-
1997
- 1997-09-19 JP JP27188897A patent/JPH1194382A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10105489B4 (en) * | 2000-02-17 | 2005-03-17 | Lg Electronics Inc. | Pulse tube refrigerator |
| KR100393790B1 (en) * | 2001-02-13 | 2003-08-02 | 엘지전자 주식회사 | Pulstube refrigerator |
| JP2006112260A (en) * | 2004-10-13 | 2006-04-27 | Daikin Ind Ltd | Thermoacoustic engine |
| KR101395285B1 (en) * | 2012-08-30 | 2014-05-15 | 한국과학기술원 | Tandem pulse tube refrigerator to automatically reduce vibration |
| JP2019190678A (en) * | 2018-04-19 | 2019-10-31 | 住友重機械工業株式会社 | Active buffer pulse tube refrigerator |
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