JP2995883B2 - Stirling cycle device - Google Patents
Stirling cycle deviceInfo
- Publication number
- JP2995883B2 JP2995883B2 JP3038485A JP3848591A JP2995883B2 JP 2995883 B2 JP2995883 B2 JP 2995883B2 JP 3038485 A JP3038485 A JP 3038485A JP 3848591 A JP3848591 A JP 3848591A JP 2995883 B2 JP2995883 B2 JP 2995883B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- compression
- chamber
- side space
- compression chamber
- 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.)
- Expired - Fee Related
Links
Description
【０００１】[0001]
【産業上の利用分野】本発明はスターリングサイクル装
置に関する。このスターリングサイクル装置は、逆スタ
ーリングサイクル冷凍機に利用できる。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a Stirling cycle device. This Stirling cycle device can be used for a reverse Stirling cycle refrigerator.
【０００２】[0002]
【従来の技術】スターリングサイクル装置例えば逆スタ
ーリングサイクル冷凍機として、図２に示す構造のもの
が知られている。この冷凍機は、図２に示す様に、シリ
ンダ室１００を持つ圧縮シリンダ部１０１と、シリンダ
室１００に往復移動可能に配置されシリンダ室１００を
圧縮室１０２と第１背圧側空間１０３に区画する圧縮ピ
ストン１０４と、シリンダ室１０６を持つ膨張シリンダ
部１０７と、シリンダ室１０６に往復移動可能に配置さ
れシリンダ室１０６を膨張室１０８と第２背圧側空間１
０９とに区画する膨張ピストン１１０と、圧縮ピストン
１０４及び膨張ピストン１１０に連結された駆動軸１１
２と、駆動軸１１２が配設された機械室１１３を持つハ
ウジング１１４と、機械室１１３と第１背圧側空間１０
３とを仕切る第１ダイヤフラム１１６と、機械室１１３
と第２背圧側空間１０９とを仕切る第２ダイヤフラム１
１７を具備する。2. Description of the Related Art As a Stirling cycle apparatus, for example, a reverse Stirling cycle refrigerator, one having a structure shown in FIG. 2 is known. As shown in FIG. 2, the refrigerator has a compression cylinder portion 101 having a cylinder chamber 100 and a reciprocatingly arranged cylinder chamber 100 which divides the cylinder chamber 100 into a compression chamber 102 and a first back pressure side space 103. A compression piston 104, an expansion cylinder portion 107 having a cylinder chamber 106, and a reciprocatingly arranged cylinder chamber 106, wherein the cylinder chamber 106 is connected to the expansion chamber 108 and the second back pressure side space 1.
09 and a drive shaft 11 connected to the compression piston 104 and the expansion piston 110.
2, a housing 114 having a machine room 113 in which the drive shaft 112 is disposed, the machine room 113 and the first back pressure side space 10.
3 and a machine room 113.
Diaphragm 1 that separates the second back pressure side space 109 from the second back pressure side space 109
17 is provided.
【０００３】ここでこの冷凍機では、機械室１１３の潤
滑油がシリンダ室１００、１０６に侵入すると、圧縮室
１０２及び膨張室１０８の作動流体が潤滑油で汚染さ
れ、冷凍性能が低下する。かかる問題を解消すべく、油
封止のための柔軟な第１ダイヤフラム１１６、第２ダイ
ヤフラム１１７が設けられている。第１背圧側空間１０
３、シリンダ室１０６は連通しており、さらに機械室１
１３と第１背圧側空間１０３はフィルタ６０を介して通
路６１により連通し同圧となる。[0003] In this refrigerator, when the lubricating oil in the machine chamber 113 enters the cylinder chambers 100 and 106, the working fluid in the compression chamber 102 and the expansion chamber 108 is contaminated with the lubricating oil, and the refrigerating performance deteriorates. In order to solve such a problem, a flexible first diaphragm 116 and a second diaphragm 117 for oil sealing are provided. First back pressure side space 10
3. The cylinder chamber 106 communicates with the machine room 1
13 and the first back pressure side space 103 communicate with each other through a passage 61 via a filter 60 to have the same pressure.
【０００４】ところで従来からの冷凍機では、例えば第
１背圧側空間１０３の圧力Ｐを１５ｋｇ／ｃｍ2 程度に
て制御する場合には、圧縮ピストン１０４の往復移動に
伴い、圧縮室１０２の圧力は最低設定圧Ｐｍｉｎ１５ｋ
ｇ／ｃｍ2 、最高設定圧ｍａｘ３０ｋｇ／ｃｍ2 の間で
サインカーブの様に変動するものである。しかして従来
からの冷凍機では、いわゆる最低圧制御方式、つまり第
１背圧側空間１０３と圧縮室１０２とを逆止弁を介して
連通させ、第１背圧側空間１０３の圧力を圧縮室１０２
の最低設定圧Ｐｍｉｎ１５ｋｇ／ｃｍ2 に設定する方式
を採用していた。In a conventional refrigerator, for example, when the pressure P in the first back pressure side space 103 is controlled at about 15 kg / cm 2 , the pressure in the compression chamber 102 increases as the compression piston 104 reciprocates. Minimum set pressure Pmin15k
g / cm 2 , and fluctuates like a sine curve between the maximum set pressure max of 30 kg / cm 2 . Thus, in a conventional refrigerator, a so-called minimum pressure control system, that is, the first back pressure side space 103 and the compression chamber 102 are communicated via a check valve, and the pressure in the first back pressure side space 103 is reduced.
Of the minimum set pressure Pmin of 15 kg / cm 2 .
【０００５】しかし、かかる最低圧制御方式では第１背
圧側空間１０３の圧力と圧縮室１０２の圧力との差圧は
１５ｋｇ／ｃｍ2 とかなり大きい。そのため冷凍運転時
には、圧縮ピストン１０４には、圧縮室１０２から第１
背圧側空間１０３の方向に押えつける力が作用する。故
にロッド１０４ａ、駆動軸１１２に作用する負荷も大き
くなり、耐久性、騒音、振動の面で不利である。更にロ
ッド１０４ａ、駆動軸１１２も大型化するために、装置
のコンパクト化には不利であった。However, in such a minimum pressure control method, the differential pressure between the pressure in the first back pressure side space 103 and the pressure in the compression chamber 102 is as large as 15 kg / cm 2 . Therefore, during the refrigeration operation, the compression piston 104
A pressing force acts in the direction of the back pressure side space 103. Therefore, the load acting on the rod 104a and the drive shaft 112 also increases, which is disadvantageous in terms of durability, noise, and vibration. Further, the size of the rod 104a and the drive shaft 112 is also increased, which is disadvantageous for downsizing the apparatus.
【０００６】そこで、図２に示す冷凍機では最低圧制御
方式に代えて中間圧制御方式を採用している。つまり、
第１背圧側空間１０３の圧力と圧縮室１０２の圧力との
差圧を極力抑えるべく、図２に示す様に、圧縮ピストン
１０４に、絞り孔として機能するオリフィス孔をもつオ
リフィス式弁１２０が圧縮ピストン１０４の内部に装備
されている。オリフィス式弁１２０は、圧縮室１０２の
余剰の作動流体を背圧側空間１０３に逃がし、また、背
圧側空間１０３の余剰の作動流体を圧縮室１０２に逃が
すものである。かかる中間圧制御方式では、例えば背圧
側空間１０３の圧は最低設定圧Ｐｍｉｎ１５ｋｇ／ｃｍ
2 と最高設定圧Ｐｍａｘ３０ｋｇ／ｃｍ 2 との間の中間
の圧に維持され、そのため、第１背圧側空間１０３の圧
力と圧縮室１０２の圧力との差圧は小さくなる．故にロ
ッド１０４ａ、駆動軸１１２に作用する負荷も軽減され
る。Therefore, in the refrigerator shown in FIG.
An intermediate pressure control system is adopted instead of the system. That is,
Of the pressure in the first back pressure side space 103 and the pressure in the compression chamber 102
To minimize the differential pressure, as shown in Fig. 2, the compression piston
104 has an orifice hole that functions as a throttle hole.
The orifice valve 120 is installed inside the compression piston 104
Have been. The orifice type valve 120 is provided in the compression chamber 102.
Excess working fluid is released to the back pressure side space 103,
Excess working fluid in the compression side space 103 is released to the compression chamber 102.
It is something. In such an intermediate pressure control method, for example,
The pressure in the side space 103 is the minimum set pressure Pmin15kg / cm.
TwoAnd the maximum set pressure Pmax30kg / cm TwoIn between
At the pressure of the first back pressure side space 103.
The pressure difference between the force and the pressure in the compression chamber 102 becomes smaller. Therefore b
Load acting on the head 104a and the drive shaft 112 is also reduced.
You.
【０００７】また中間圧制御方式として、図３に示す様
に、圧縮室１０２と背圧側空間１０３とを通路１３０で
接続し、通路１３０に手動開閉式の開閉弁１３２を設け
たものも知られている。このものでも、開閉弁１３２の
開閉により圧縮室１０２と背圧側空間１０３との差圧は
小さくなり、ロッド１０４ａ、駆動軸１１２に作用する
負荷も軽減される。As an intermediate pressure control system, there is also known an intermediate pressure control system in which a compression chamber 102 and a back pressure side space 103 are connected by a passage 130, and a manual opening / closing valve 132 is provided in the passage 130, as shown in FIG. ing. Also in this case, the differential pressure between the compression chamber 102 and the back pressure side space 103 is reduced by opening and closing the on-off valve 132, and the load acting on the rod 104a and the drive shaft 112 is also reduced.
【０００８】[0008]
【発明が解決しようとする課題】ところで図２に示す冷
凍機では、中間圧制御のために、オリフィス式弁１２０
のオリフィス孔は絞り孔として機能するために常時、開
口している。そのため、圧縮ピストン１０４が圧縮作動
のために僅かでも上動すれば、圧縮室１０２の作動流体
はオリフィス孔から流出する。そのため圧縮室１０２に
おいてはオリフィス孔の流量やピストンリングからの洩
れ量に対する圧力の変動により中間圧力の安定性には限
界があり、ひいては冷凍性能の向上に不利である。また
ピストンリング摩耗粉等の異物が狭小のオリフィス孔に
詰まり冷凍性能を悪化させるという問題がある。In the refrigerator shown in FIG. 2, the orifice valve 120 is used for controlling the intermediate pressure.
Orifice hole is always open to function as a throttle hole. Therefore, if the compression piston 104 slightly moves upward for the compression operation, the working fluid in the compression chamber 102 flows out of the orifice hole. Therefore, in the compression chamber 102, there is a limit to the stability of the intermediate pressure due to the fluctuation of the pressure with respect to the flow rate of the orifice hole and the amount of leakage from the piston ring, which is disadvantageous in improving the refrigeration performance. There is also a problem that foreign matter such as abrasion powder of the piston ring is clogged in the narrow orifice hole and deteriorates refrigerating performance.
【０００９】また図３に示す冷凍機では、オリフィス式
弁を廃止し得るものの、中間圧制御のために、圧縮シリ
ンダ部１０１の外部に突き出る通路１３０を作動流体が
通るためにそのぶん圧損が生じる問題がある。更に通路
１３０が外部に突き出るので、配管スペース等の面で不
利である。本発明は上記した実情に鑑みなされたもので
あり、その目的は、通路を外部に突き出させる構造及び
オリフィス式弁を廃止し、中間圧力の安定を図り、シー
ル粉塵等の異物がオリフィス孔に詰まり易いという問題
を改善した中間圧制御方式のスターリングサイクル装置
を提供することにある。Further, in the refrigerator shown in FIG. 3, although the orifice type valve can be omitted, the working fluid passes through the passage 130 protruding outside the compression cylinder portion 101 due to the intermediate pressure control, so that a pressure loss occurs. There's a problem. Further, since the passage 130 protrudes to the outside, it is disadvantageous in terms of piping space and the like. SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to eliminate the structure for protruding the passage to the outside and the orifice type valve, to stabilize the intermediate pressure, and to prevent foreign matter such as seal dust from clogging the orifice hole. It is an object of the present invention to provide a Stirling cycle device of an intermediate pressure control system which has improved the problem of easiness.
【００１０】[0010]
【課題を解決するための手段】本発明のスターリングサ
イクル装置は、シリンダ室を持つ圧縮シリンダ部と、シ
リンダ室に往復移動可能に配置されシリンダ室を圧縮室
と背圧側空間とに区画する圧縮ピストンと、圧縮ピスト
ンに連結された駆動軸と、駆動軸が配設された機械室と
を具備するスターリングサイクル装置において、圧縮ピ
ストンは、ピストン本体と、ピストン本体に内蔵され常
時閉状態であり圧縮室の圧が最高設定圧よりも高いとき
には開放作動して圧縮室の作動流体を背圧側空間に逃が
す第１圧力応答式リリーフ弁と、ピストン本体に内蔵さ
れ常時閉状態であり圧縮室の圧が最低設定圧よりも低い
ときには開放作動して背圧側空間の作動流体を圧縮室に
補給する第２圧力応答式リリーフ弁とをもち、背圧側空
間の圧力は圧縮室の最高設定圧と最低設定圧との間の中
間圧に規定されていることを特徴とするものである。SUMMARY OF THE INVENTION A Stirling cycle apparatus according to the present invention comprises a compression cylinder portion having a cylinder chamber, and a compression piston arranged reciprocally in the cylinder chamber to partition the cylinder chamber into a compression chamber and a back pressure side space. And a drive shaft connected to the compression piston, and a mechanical chamber provided with the drive shaft, wherein the compression piston includes a piston body, a normally closed state built in the piston body, and a compression chamber. When the pressure is higher than the maximum set pressure, a first pressure-responsive relief valve that opens to allow the working fluid in the compression chamber to escape to the back pressure side space, and is built into the piston body and is always closed, and the pressure in the compression chamber is the lowest. set pressure Chi also a second pressure-responsive relief valve to replenish the working fluid of the back pressure side space into the compression chamber and opening operation when lower than the back pressure side sky
Pressure between the highest and lowest set pressure in the compression chamber.
It is characterized by being defined by the inter-pressure .
【００１１】[0011]
【作用】圧縮室の圧が最高設定圧よりも高いときには、
第１圧力応答式リリーフ弁は開放作動し圧縮室の余剰の
作動流体を背圧側空間に逃がす。また、圧縮室の圧が最
低設定圧よりも低いときには、第２圧力応答式リリーフ
弁は開放作動し、背圧側空間の余剰の作動流体を圧縮室
に補給する。[Function] When the pressure in the compression chamber is higher than the maximum set pressure,
The first pressure-responsive relief valve is opened to release excess working fluid in the compression chamber to the back pressure side space. Further, when the pressure in the compression chamber is lower than the minimum set pressure, the second pressure-responsive relief valve opens to supply excess working fluid in the back pressure side space to the compression chamber.
【００１２】[0012]
【実施例】以下、本発明を逆スターリングサイクル冷凍
機に適用した実施例を、図１を参照しつつ説明する。 （構成）この逆スターリングサイクル冷凍機は、図１に
示す様に、冷凍機構を２個並設した方式である。この冷
凍機は、シリンダ室２０を持つ圧縮シリンダ部２０ａ
と、シリンダ室２０に往復移動可能に配置されシリンダ
室２０を圧縮室２２と第１背圧側空間２１とに区画する
圧縮ピストン２３と、シリンダ室２５を持つ膨張シリン
ダ部２６と、シリンダ室２５に往復移動可能に配置され
シリンダ室２５を膨張室２７と第２背圧側空間２８とに
区画する膨張ピストン２９と、圧縮ピストン２３及び膨
張ピストン２９に連結された駆動軸としてのクランク軸
３１と、クランク軸３１が配設された機械室３２を持つ
ハウジング３３と、クランク軸３１を回転させるモータ
３４と、機械室３２と第１背圧側空間２１とを仕切る第
１ダイヤフラム３６と、機械室３２と第２背圧側空間２
８とを仕切る第２ダイヤフラム３７と、作動流体の圧縮
熱を取り去る放熱器４０と、作動流体を冷却、蓄熱する
蓄冷器４１とを具備する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to a reverse Stirling cycle refrigerator will be described below with reference to FIG. (Structure) This reverse Stirling cycle refrigerator has a configuration in which two refrigeration mechanisms are arranged side by side, as shown in FIG. This refrigerator has a compression cylinder section 20a having a cylinder chamber 20.
A compression piston 23 that is reciprocally movable in the cylinder chamber 20 and divides the cylinder chamber 20 into a compression chamber 22 and a first back pressure side space 21; an expansion cylinder section 26 having a cylinder chamber 25; An expansion piston 29 which is reciprocally movable and partitions the cylinder chamber 25 into an expansion chamber 27 and a second back pressure side space 28; a crankshaft 31 as a drive shaft connected to the compression piston 23 and the expansion piston 29; A housing 33 having a machine room 32 in which the shaft 31 is disposed; a motor 34 for rotating the crankshaft 31; a first diaphragm 36 separating the machine room 32 and the first back pressure side space 21; 2 Back pressure side space 2
8, a radiator 40 for removing the heat of compression of the working fluid, and a regenerator 41 for cooling and storing the working fluid.
【００１３】本実施例では、圧縮シリンダ部２０ａ、膨
張シリンダ部２６、機械室３２には作動流体（ヘリウ
ム）が封入されている。さて、圧縮ピストン２３は、ピ
ストン本体５０と、第１圧力応答式リリーフ弁５１と、
第２圧力応答式リリーフ弁５２とをもつ。第１圧力応答
式リリーフ弁５１は、ピストン本体に５０内蔵され、常
時閉状態であり、圧縮室２２の圧がリリーフ圧（＝約３
０ｋｇ／ｃｍ2 程度）よりも高いときには開放作動し
て、圧縮室２２の余剰の作動流体を背圧側空間２１に逃
がす。また第２圧力応答式リリーフ弁５２は、ピストン
本体５０に内蔵され、常時閉状態であり、圧縮室２３の
圧が約１５ｋｇ／ｃｍ2 程度よりも低いときには開放し
て背圧側空間２１の作動流体を圧縮室２２に送る。この
第１圧力応答式リリーフ弁５１は、作動流体が通過する
開口５１ａと、開口５１ａを閉じる弁５１ｂと、弁５１
ｂを閉弁方向に付勢するバネ５１ｃとで形成されてい
る。同様に、第２圧力応答式リリーフ弁５２は、作動流
体が通過する開口５２ａと、開口５２ａを閉じる弁５２
ｂと、弁５２ｂを閉弁方向に付勢するバネ５２ｃとで形
成されている。In this embodiment, a working fluid (helium) is sealed in the compression cylinder section 20a, the expansion cylinder section 26, and the machine chamber 32. Now, the compression piston 23 includes a piston body 50, a first pressure-responsive relief valve 51,
And a second pressure-responsive relief valve 52. The first pressure-responsive relief valve 51 is built in the piston body 50 and is normally closed, and the pressure in the compression chamber 22 is reduced to a relief pressure (= about 3).
When the pressure is higher than about 0 kg / cm 2 ), the opening operation is performed, and the excess working fluid in the compression chamber 22 is released to the back pressure side space 21. The second pressure responsive relief valve 52 is built in the piston body 50 and is normally closed. When the pressure in the compression chamber 23 is lower than about 15 kg / cm 2, the second pressure responsive relief valve 52 is opened to open the working fluid in the back pressure side space 21. Is sent to the compression chamber 22. The first pressure-responsive relief valve 51, an opening 51a which the working fluid passes, a valve 51b to close the opening 51a, the valve 51
It is formed with a spring 51c which urges in the closing direction b. Similarly, the second pressure-responsive relief valve 52 includes an opening 52a through which the working fluid passes, and a valve 52 that closes the opening 52a.
b and a spring 52c for urging the valve 52b in the valve closing direction.
【００１４】本実施例では、圧縮ピストン２３は膨張ピ
ストン２９よりもほぼ９０度の位相遅れで往復移動す
る。また２個の圧縮ピストン２３の位相差はほぼ９０度
である。同様に、２個の膨張ピストン２９の位相差はほ
ぼ９０度である。圧縮ピストン２３、膨張ピストン２９
の外周部にはシール５５が設けられている。また、膨張
シリンダ部２６の第２背圧側空間２８と圧縮シリンダ部
２０ａの第１背圧側空間２１との間には連通路５６が設
けられており、背圧側空間２１、２５はオイルフィルタ
ー６０を介する連通路６１にて機械室３２と連通されて
いる。なお機械室３２の下部は潤滑油が溜まった油溜め
室とされている。In the present embodiment, the compression piston 23 reciprocates with a phase delay of approximately 90 degrees from the expansion piston 29. The phase difference between the two compression pistons 23 is approximately 90 degrees. Similarly, the phase difference between the two expansion pistons 29 is approximately 90 degrees. Compression piston 23, expansion piston 29
Is provided with a seal 55 on the outer periphery. A communication path 56 is provided between the second back pressure side space 28 of the expansion cylinder part 26 and the first back pressure side space 21 of the compression cylinder part 20a, and the back pressure side spaces 21 and 25 are provided with an oil filter 60. It communicates with the machine room 32 through a communication passage 61 interposed therebetween. The lower part of the machine room 32 is an oil reservoir in which lubricating oil is stored.
【００１５】第１ダイヤフラム３６、第２ダイヤフラム
３７はゴム製であり、従来と同様に機械室３２の潤滑油
及び油雰囲気の作動流体（ヘリウムガス）が背圧側空間
２０、２５に漏れることを防止している。ここで、第１
ダイヤフラム３６の中央部３６ａは圧縮ピストン２３の
ロッド２３ａにシール固定されている。また第１ダイヤ
フラム３６の周縁部３６ｂは機械室３２の留め部に保持
されている。第２ダイヤフラム３７の中央部３７ａは膨
張ピストン２９のロッド２９ａにシール固定されてい
る。また第２ダイヤフラム３７の周縁部３７ｂは機械室
３２の留め部に保持されている。 （作用）本実施例では、従来の冷凍機と同様に、モータ
３４の駆動に伴い、圧縮ピストン２３が上昇すると、圧
縮室２２内の作動流体は圧縮され、放熱部４０、蓄冷器
４１を経て膨張室２７に送られる。このとき作動流体の
圧縮熱は放熱部４０で取り去られ、蓄冷器４１を経て膨
張室２７に至る。そして、膨張ピストン２９の下降に伴
い、膨張室２７で作動流体は実質的に断熱膨張し、膨張
室２７が低温となる。また膨張ピストン２９が上昇する
と、膨張室２７の作動流体は蓄冷器４１、放熱部４０を
経て圧縮室２２に戻る。かかる断熱圧縮工程、等容工
程、断熱膨張工程、等容工程を繰り返すことにより、コ
ールドヘッド５７から１０〜２０Ｋの極低温が取り出さ
れる。The first diaphragm 36 and the second diaphragm 37 are made of rubber, and prevent the lubricating oil in the machine chamber 32 and the working fluid (helium gas) in the oil atmosphere from leaking into the back pressure side spaces 20 and 25 as in the prior art. doing. Here, the first
The central portion 36a of the diaphragm 36 is sealed and fixed to the rod 23a of the compression piston 23. Further, a peripheral portion 36 b of the first diaphragm 36 is held by a retaining portion of the machine room 32. The central portion 37a of the second diaphragm 37 is sealed and fixed to the rod 29a of the expansion piston 29. Further, a peripheral portion 37 b of the second diaphragm 37 is held by a retaining portion of the machine room 32. (Operation) In the present embodiment, as in the conventional refrigerator, when the compression piston 23 rises with the driving of the motor 34, the working fluid in the compression chamber 22 is compressed and passes through the radiator 40 and the regenerator 41. It is sent to the expansion chamber 27. At this time, the heat of compression of the working fluid is removed by the radiator 40 and reaches the expansion chamber 27 via the regenerator 41. As the expansion piston 29 descends, the working fluid substantially adiabatically expands in the expansion chamber 27, and the temperature of the expansion chamber 27 becomes low. When the expansion piston 29 rises, the working fluid in the expansion chamber 27 returns to the compression chamber 22 via the regenerator 41 and the radiator 40. By repeating the adiabatic compression step, the equal volume step, the adiabatic expansion step, and the equal volume step, an extremely low temperature of 10 to 20 K is taken out from the cold head 57.
【００１６】ところで本実施例では、作動時には、膨張
ピストン２９、圧縮ピストン２３の駆動に伴ない膨張室
２７の圧は予め設計された最高設定圧Ｐ１、最低設定圧
Ｐ２間をあたかもサインカーブのように変動する。また
同様に、圧縮室２２の圧は膨張室２７と位相が約９０度
ずれて最高設定圧Ｐｍａｘ、最低設定圧Ｐｍｉｎ間をあ
たかもサインカーブのように変動する。ここで、本実施
例では所望の極低温が得られる様に、圧縮室２２の圧は
最高設定圧Ｐｍａｘは約３０ｋｇ／ｃｍ2 程度、最低設
定圧Ｐｍｉｎは約１５ｋｇ／ｃｍ2 程度に設定されてい
る。なお、機械室３２の圧は約１５ｋｇ／ｃｍ2 程度と
されている。In the present embodiment, during operation, the pressure of the expansion chamber 27 accompanying the driving of the expansion piston 29 and the compression piston 23 is between a previously designed maximum set pressure P1 and a minimum set pressure P2 as if a sine curve. To fluctuate. Similarly, the pressure of the compression chamber 22 fluctuates in a manner similar to a sine curve between the maximum set pressure Pmax and the minimum set pressure Pmin with a phase shift of about 90 degrees from the expansion chamber 27. In this embodiment, the pressure in the compression chamber 22 is set to a maximum set pressure Pmax of about 30 kg / cm 2 and a minimum set pressure Pmin of about 15 kg / cm 2 so as to obtain a desired cryogenic temperature. I have. The pressure in the machine room 32 is about 15 kg / cm 2 .
【００１７】さて、圧縮室２２の実際の最高圧が最高設
定圧Ｐｍａｘ（約３０ｋｇ／ｃｍ2 ）を越え、第１圧力
応答式リリーフ弁５１のリリーフ圧（＝約３０ｋｇ／ｃ
ｍ2 程度）よりも高くなったときには、第１圧力応答式
リリーフ弁５１は開放作動し、圧力室２２の余剰の圧を
背圧側空間２１に逃がす。また、圧縮室２２の実際の最
低圧が最低設定圧Ｐｍｉｎ（約１５ｋｇ／ｃｍ2 ）より
も下がると、第２圧力応答式リリーフ弁５２は開放作動
し、背圧側空間２１の作動流体を圧縮室２２に補給す
る。これにより圧縮室２２の実際の最高圧、最低圧は予
め設計された設定値通りに維持される。また、背圧側空
間２１は、圧縮室２２の最高設定圧Ｐｍａｘ（約３０ｋ
ｇ／ｃｍ2 ）と最低設定圧Ｐｍｉｎ（約１５ｋｇ／ｃｍ
2 ）との中間圧（２２．５ｋｇ／ｃｍ2 程度）に維持さ
れる。従って圧縮室２２と背圧側空間２１との差圧は従
来の差圧約１５ｋｇ／ｃｍ2 に比較して小さくなる。か
かる中間圧制御方式では、ロッド２３ａ、２９ａ、クラ
ンク軸３１に作用する負荷を大いに軽減できる。Now, when the actual maximum pressure of the compression chamber 22 exceeds the maximum set pressure Pmax (about 30 kg / cm 2 ), the relief pressure of the first pressure-responsive relief valve 51 (= about 30 kg / c)
m 2 ), the first pressure-responsive relief valve 51 opens to release the excess pressure in the pressure chamber 22 to the back pressure side space 21. When the actual minimum pressure of the compression chamber 22 falls below the minimum set pressure Pmin (about 15 kg / cm 2 ), the second pressure-responsive relief valve 52 opens and the working fluid in the back pressure side space 21 is released. Refill 22. As a result, the actual maximum pressure and the minimum pressure of the compression chamber 22 are maintained as set values set in advance. Further, the back pressure side space 21 has a maximum set pressure Pmax (about 30 k) of the compression chamber 22.
g / cm 2 ) and the minimum set pressure Pmin (about 15 kg / cm
2 ) and an intermediate pressure (about 22.5 kg / cm 2 ). Therefore, the pressure difference between the compression chamber 22 and the back pressure side space 21 is smaller than the conventional pressure difference of about 15 kg / cm 2 . With such an intermediate pressure control method, the load acting on the rods 23a, 29a and the crankshaft 31 can be greatly reduced.
【００１８】またこのような中間圧制御方式を採用すれ
ば、圧縮室２２の圧は約１５ｋｇ／ｃｍ2 〜約３０ｋｇ
／ｃｍ2 間をサインカーブの様に変動するものの、背圧
側空間２１はその中間圧に維持されるため、圧縮ピスト
ン２３が圧縮室２２から背圧側空間２１の方向へ押さえ
つけられる力ばかりか、逆方向の力、つまり、圧縮ピス
トン２３が圧縮室２２から引っ張られる力も発生する。
そのため圧縮膨脹に伴うロッド２３ａ、２９ａにかかる
負荷の均一化により、クランク軸３１とロッド２３ａ、
２９ａとを係合している軸受メタル３１ｆの潤滑性能も
向上し、軸受メタル３１ｆの耐久性が向上するという利
点も得られる。If such an intermediate pressure control method is adopted, the pressure in the compression chamber 22 is about 15 kg / cm 2 to about 30 kg.
/ Cm 2 varies like a sine curve, but the back pressure side space 21 is maintained at the intermediate pressure. Therefore, not only the force of pressing the compression piston 23 from the compression chamber 22 toward the back pressure side space 21 but also the reverse pressure. A directional force, that is, a force that pulls the compression piston 23 from the compression chamber 22 is also generated.
Therefore, by equalizing the load applied to the rods 23a, 29a due to the compression and expansion, the crankshaft 31 and the rods 23a,
The lubrication performance of the bearing metal 31f engaged with the bearing metal 29a is also improved, and the advantage that the durability of the bearing metal 31f is improved is also obtained.
【００１９】なお、圧縮室２２が適圧となれば第１圧力
応答式リリーフ弁５１、第２圧力応答式リリーフ弁５２
は自然に閉じる。 （効果）以上説明した様に本実施例によれば、図２に示
す従来とは異なり、詰まりが生じかつ圧縮比の向上に限
界があるオリフィス孔をもつオリフィス式弁１２０を用
いることなく中間圧制御方式を達成できる。このように
本実施例ではオリフィス式弁１２０を廃止できるので、
詰まりの問題、圧力の安定性の問題を改善できる。When the pressure in the compression chamber 22 becomes appropriate, the first pressure-responsive relief valve 51, the second pressure-responsive relief valve 52
Closes naturally. (Effects) As described above, according to the present embodiment, unlike the prior art shown in FIG. 2, the intermediate pressure can be reduced without using the orifice type valve 120 having the orifice hole in which the clogging occurs and the improvement of the compression ratio is limited. A control scheme can be achieved. Thus, in this embodiment, the orifice valve 120 can be eliminated,
The problem of clogging and the problem of pressure stability can be improved.
【００２０】ところで圧縮ピストン２３と圧縮シリンダ
部２０ａとの間、膨張ピストン２９と膨張シリンダ部２
６との間にはシール５５が設けられ気密的にシールされ
ているが、シールされているといえども、ピストン２
３、２９は摺動するためシール５５からの作動流体の漏
れが不可避的に生じる。そして、漏れにより圧縮室２２
の実際の最高圧が最高設定圧Ｐｍａｘよりも低下し、ま
た、圧縮室２２の実際の最低圧が最低設定圧Ｐｍｉｎを
越えてしまい、所望の冷凍性能を発揮できないことがあ
る。この点本実施例ではシール５５からの作動流体の漏
れがあっても、前述した様に、圧縮室２２の圧がリリー
フ圧よりも高くなれば、第１圧力応答式リリーフ弁５１
は開放作動し、背圧側空間２１の圧がリリーフ圧よりも
高くなれば、第２圧力応答式リリーフ弁５２は開放作動
し、これにより圧縮室２２の実際の最高圧を最高設定圧
Ｐｍａｘに維持でき、また、圧縮室２２の実際の最低圧
を最低設定圧Ｐｍｉｎに維持でき、所望の冷凍性能を維
持できる。By the way, between the compression piston 23 and the compression cylinder 20a, the expansion piston 29 and the expansion cylinder 2
6, a seal 55 is provided and air-tightly sealed.
Since the components 3 and 29 slide, leakage of the working fluid from the seal 55 inevitably occurs. Then, due to leakage, the compression chamber 22
May lower than the maximum set pressure Pmax, and the actual minimum pressure of the compression chamber 22 may exceed the minimum set pressure Pmin, so that desired refrigeration performance may not be exhibited. In this regard, in this embodiment, even if the working fluid leaks from the seal 55, as described above, if the pressure in the compression chamber 22 becomes higher than the relief pressure, the first pressure-responsive relief valve 51
When the pressure in the back pressure side space 21 becomes higher than the relief pressure, the second pressure responsive relief valve 52 opens, thereby maintaining the actual maximum pressure of the compression chamber 22 at the maximum set pressure Pmax. In addition, the actual minimum pressure in the compression chamber 22 can be maintained at the minimum set pressure Pmin, and desired refrigeration performance can be maintained.
【００２１】[0021]
【発明の効果】本発明のスターリングサイクル装置によ
れば、従来とは異なり、常時に開口しているオリフィス
孔を設けずとも良いので、圧力の安定性、冷凍性能の向
上に有利である。更に、微小孔であるオリフィス孔を設
けずとも良いので、詰まりの問題を改善できる。また本
発明のスターリングサイクル装置によれば、第１圧力応
答式リリーフ弁及び第１圧力応答式リリーフ弁は圧縮ピ
ストンに内蔵されているので、図３に示す従来とは異な
り、通路が外部に突き出ない利点、圧損を極力回避でき
る利点がある。According to the Stirling cycle apparatus of the present invention, unlike the prior art, it is not necessary to provide an orifice hole which is always open, which is advantageous for improving pressure stability and refrigerating performance. Further, since there is no need to provide an orifice hole which is a minute hole, the problem of clogging can be improved. Further, according to the Stirling cycle device of the present invention, since the first pressure-responsive relief valve and the first pressure-responsive relief valve are built in the compression piston, the passage protrudes outside unlike the conventional case shown in FIG. There is no advantage and the advantage that pressure loss can be avoided as much as possible.
【図１】冷凍機の全体の構成図である。FIG. 1 is an overall configuration diagram of a refrigerator.
【図２】従来の冷凍機の全体の構成図である。FIG. 2 is an overall configuration diagram of a conventional refrigerator.
【図３】従来の冷凍機の要部の構成図である。FIG. 3 is a configuration diagram of a main part of a conventional refrigerator.
図中、２２は圧縮室、２１は第１背圧側空間、２３は圧
縮ピストン、３１はクランク軸、３２は機械室、３６は
第１ダイヤフラム、３７は第２ダイヤフラム、５１は第
１圧力応答式リリーフ弁、５２は第２圧力応答式リリー
フ弁を示す。In the drawing, 22 is a compression chamber, 21 is a first back pressure side space, 23 is a compression piston, 31 is a crankshaft, 32 is a machine chamber, 36 is a first diaphragm, 37 is a second diaphragm, and 51 is a first pressure response type. A relief valve 52 indicates a second pressure-responsive relief valve.
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.6，ＤＢ名) F25B 9/14 510 F25B 9/14 520 ──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. 6 , DB name) F25B 9/14 510 F25B 9/14 520
Claims (1)
シリンダ室に往復移動可能に配置され該シリンダ室を圧
縮室と背圧側空間とに区画する圧縮ピストンと、該圧縮
ピストンに連結された駆動軸と、該駆動軸が配設された
機械室とを具備するスターリングサイクル装置におい
て、 該圧縮ピストンは、 ピストン本体と、該ピストン本体に内蔵され常時閉状態
であり該圧縮室の圧が最高設定圧よりも高いときには開
放作動して圧縮室の作動流体を該背圧側空間に逃がす第
１圧力応答式リリーフ弁と、該ピストン本体に内蔵され
常時閉状態であり該圧縮室の圧が最低設定圧よりも低い
ときには開放作動して該背圧側空間の作動流体を圧縮室
に補給する第２圧力応答式リリーフ弁とをもち、 該背圧側空間の圧力は該圧縮室の最高設定圧と最低設定
圧との間の中間圧に規定されている ことを特徴とするス
ターリングサイクル装置。A compression cylinder portion having a cylinder chamber; a compression piston disposed reciprocally in the cylinder chamber to partition the cylinder chamber into a compression chamber and a back pressure side space; and a drive connected to the compression piston. In a Stirling cycle device comprising a shaft and a machine room in which the drive shaft is disposed, the compression piston is built in the piston body and is always closed so that the pressure in the compression chamber is set to a maximum. When the pressure is higher than the pressure, a first pressure-responsive relief valve that opens to allow the working fluid in the compression chamber to escape to the back pressure side space, and is built in the piston body and is always closed, and the pressure in the compression chamber is the minimum set pressure. second Chi also a pressure-responsive relief valve, the pressure of the back pressure side space maximum set pressure and the lowest setting of the compression chamber to replenish the compression chamber the working fluid of the opening operation to the back pressure side space when less than
A Stirling cycle device characterized by being defined at an intermediate pressure between the pressure and the pressure .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3038485A JP2995883B2 (en) | 1991-03-05 | 1991-03-05 | Stirling cycle device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3038485A JP2995883B2 (en) | 1991-03-05 | 1991-03-05 | Stirling cycle device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04278147A JPH04278147A (en) | 1992-10-02 |
| JP2995883B2 true JP2995883B2 (en) | 1999-12-27 |
Family
ID=12526564
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3038485A Expired - Fee Related JP2995883B2 (en) | 1991-03-05 | 1991-03-05 | Stirling cycle device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2995883B2 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TW521121B (en) * | 2001-03-30 | 2003-02-21 | Sanyo Electric Co | Stirling refrigerating device |
| JP2015098844A (en) * | 2013-11-20 | 2015-05-28 | 住友重機械工業株式会社 | Cryopump system, and operation method of cryopump system |
| JP2017214936A (en) * | 2017-09-11 | 2017-12-07 | 住友重機械工業株式会社 | Cryopump system, and operation method of cryopump system |
-
1991
- 1991-03-05 JP JP3038485A patent/JP2995883B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04278147A (en) | 1992-10-02 |
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