JPH0493559A - Reverse stirling refrigeration machine having circulating oil - Google Patents
Reverse stirling refrigeration machine having circulating oilInfo
- Publication number
- JPH0493559A JPH0493559A JP21047190A JP21047190A JPH0493559A JP H0493559 A JPH0493559 A JP H0493559A JP 21047190 A JP21047190 A JP 21047190A JP 21047190 A JP21047190 A JP 21047190A JP H0493559 A JPH0493559 A JP H0493559A
- Authority
- JP
- Japan
- Prior art keywords
- oil
- space
- heat
- working gas
- expansion
- 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
- 239000010724 circulating oil Substances 0.000 title claims abstract description 33
- 238000005057 refrigeration Methods 0.000 title claims abstract description 5
- 238000002347 injection Methods 0.000 claims abstract description 30
- 239000007924 injection Substances 0.000 claims abstract description 30
- 239000003921 oil Substances 0.000 claims abstract description 29
- 230000006835 compression Effects 0.000 claims abstract description 28
- 238000007906 compression Methods 0.000 claims abstract description 28
- 239000007788 liquid Substances 0.000 claims abstract description 11
- 230000001172 regenerating effect Effects 0.000 claims description 5
- 239000012267 brine Substances 0.000 claims description 2
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 claims description 2
- 239000007921 spray Substances 0.000 claims description 2
- 230000008014 freezing Effects 0.000 claims 1
- 238000007710 freezing Methods 0.000 claims 1
- 239000010721 machine oil Substances 0.000 claims 1
- 239000000463 material Substances 0.000 claims 1
- 239000000203 mixture Substances 0.000 claims 1
- 238000000926 separation method Methods 0.000 claims 1
- 239000007789 gas Substances 0.000 abstract description 28
- 239000001307 helium Substances 0.000 abstract description 3
- 229910052734 helium Inorganic materials 0.000 abstract description 3
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 abstract description 3
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 abstract description 2
- 238000000034 method Methods 0.000 abstract 1
- 239000003507 refrigerant Substances 0.000 abstract 1
- 230000005855 radiation Effects 0.000 description 4
- 238000013459 approach Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 239000003595 mist Substances 0.000 description 2
- JTJMJGYZQZDUJJ-UHFFFAOYSA-N phencyclidine Chemical class C1CCCCN1C1(C=2C=CC=CC=2)CCCCC1 JTJMJGYZQZDUJJ-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000003203 everyday effect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 230000032258 transport Effects 0.000 description 1
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明はフロンを使用しないで低温を生ずる逆スターリ
ングサイクル冷凍器の改良に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an improvement in a reverse Stirling cycle refrigerator that produces low temperatures without using fluorocarbons.
［従来の技術］
フロンを使用しない冷凍機として注目を浴びている逆ス
ターリングサイクル冷凍機は本来高い温度降下を生ずる
クライオクーラーとして発達して来たもので、家庭用冷
蔵庫やルームクーラー程度の２０℃〜４０℃くらいの小
温度降下を目的とする場合にはかえってＣＯＰも低くか
つ重量や容積あたりの比出力も小さい欠点があった。[Prior art] The reverse Stirling cycle refrigerator, which is attracting attention as a refrigerator that does not use fluorocarbons, was originally developed as a cryocooler that produces a high temperature drop, and the temperature is about 20℃, which is about the same as that of a home refrigerator or room cooler. When the objective is to lower the temperature by as low as 40° C., the disadvantages are that the COP is low and the specific output per weight and volume is low.
参考として
第１図に従来の代表的な逆スターリングサイクル冷凍機
の側面図を示す。１はクランクケースでその中に外部動
力をうける回転軸２と、それにより矢印３の方向に回転
されるクランク４があり同クランク４はロッド５，６に
よってピストン７゜８を往復運動させて、約９０°のＶ
形をなす二つのシリンダー９，１０の中を動かす。シリ
ンダー９の頭部にあってピストン７の上方となる空間は
膨張空間１１であり、またシリンダーｌＯの中にあって
ピストン８の上方となる空間は圧縮空間１２であって、
該膨張空間１１と該圧縮空間１２との間はそれぞれの出
口管１３．１４．および低温熱交換器１５．再生熱交換
器１６．放熱熱交換器１７が図のように直列に連通され
ている。１８は低温熱交換器１５より冷熱を除去輸送す
る冷凍用ブライン管であり、 １９は放熱熱交換器の放
熱を行う冷却水管である。For reference, FIG. 1 shows a side view of a typical conventional reverse Stirling cycle refrigerator. Reference numeral 1 designates a crankcase, which includes a rotating shaft 2 that receives external power, and a crank 4 that is rotated by the shaft in the direction of arrow 3. The crank 4 causes a piston 7.8 to reciprocate by means of rods 5 and 6. V of about 90°
It moves inside the two cylinders 9 and 10 that form the shape. The space in the head of the cylinder 9 above the piston 7 is an expansion space 11, and the space in the cylinder 1O above the piston 8 is a compression space 12.
Between the expansion space 11 and the compression space 12 are respective outlet pipes 13, 14. and low temperature heat exchanger 15. Regenerative heat exchanger 16. Radiation heat exchangers 17 are connected in series as shown in the figure. 18 is a refrigeration brine pipe that removes and transports cold heat from the low-temperature heat exchanger 15, and 19 is a cooling water pipe that radiates heat from the radiation heat exchanger.
いまクランクケース１．シリンダー９．ＩＱの内部等す
べての内部空間に高圧ヘリウムガス等の作動ガスをみた
し、クランク４を矢印３の方向に回転すると２逆スタ一
リングサイクル機器の原理によって該膨張空間１ｊの中
には低温が発生し、該圧縮空間１２の中には高温が発生
することは公知である。Now crankcase 1. Cylinder 9. When all internal spaces such as the inside of the IQ are filled with working gas such as high-pressure helium gas and the crank 4 is rotated in the direction of the arrow 3, a low temperature is generated in the expansion space 1j due to the principle of a two-way reverse stirring cycle device. It is known that high temperatures occur in the compression space 12.
しかしこのさい、それぞれの空間の中のガスは理論上は
等温変化をすべきではあるが、実際上は断熱変化をする
のでその膨張と圧縮で生ずる温度降下と上昇はかなり大
きくなり、エクセルギ損失が増大するので小温度降下で
はＣＯＰは在来のフロン圧縮冷凍機よりはるかに小さく
なり、とくに日常の冷蔵庫やクーラー等の小さい温度降
下の用途に対して不向きであった。However, in this case, although the gas in each space should change isothermally in theory, it actually changes adiabatically, so the temperature drop and rise caused by expansion and compression become quite large, resulting in exergy loss. As a result, the COP is much smaller than that of conventional fluorocarbon compression refrigerators at small temperature drops, making it particularly unsuitable for applications with small temperature drops such as everyday refrigerators and coolers.
［発明が解決しようとする諌聞コ
以上のように従来の逆スターリングサイクル冷凍機はと
くに膨張空間と圧縮空間内のガスの状態変化が期待され
る等温変化ではなく断熱変化に近く、よって作動ガス自
体の温度変化が要求される温度差より大きくなり過ぎる
ためであるので、その変化を等温変化に近づけるのが最
大の課題である。[Immon to be solved by the invention] As described above, in the conventional reverse Stirling cycle refrigerator, the state change of the gas in the expansion space and the compression space is close to an adiabatic change rather than the expected isothermal change, and therefore the working gas This is because the temperature change itself becomes too large than the required temperature difference, so the biggest challenge is to bring the change closer to isothermal change.
［課耽を解決するための手段］
それに対し本発明は膨張空間と圧縮空間に低粘度の循環
油を十分な量だけ微細な噴霧として噴射してその油滴の
存在によって作動ガスの温度変化を十分小さくして等温
変化に近づけ、かつその循環油は各空間出口で分離して
それぞれ別個のＷＩ環抽油管路流下させ１作動ガスの熱
交換の代りに循１泊を熱交換器に通してその顕熱をもっ
て冷凍及び放熱を行わせるものであり、よって作動ガス
のサイクルは所期の等温サイクルに近づくので小温度降
下でもＣＯＰが理論値に近づき十分大きくなり、また作
動ガスの熱交換器が不要になるので油滴分離装置が十分
小さければ、ガスの死空間が小さくなり全体の比出力も
上昇する。[Means for solving the problem] In contrast, the present invention injects a sufficient amount of low-viscosity circulating oil into the expansion space and the compression space as a fine spray, and the presence of the oil droplets suppresses the temperature change of the working gas. The circulating oil is made sufficiently small to approximate isothermal change, and the circulating oil is separated at the outlet of each space and flows down a separate WI ring oil extraction pipe, and instead of the heat exchange of one working gas, the circulating oil is passed through a heat exchanger. The sensible heat is used to perform refrigeration and heat dissipation, and as a result, the working gas cycle approaches the intended isothermal cycle, so even with a small temperature drop, the COP approaches the theoretical value and becomes sufficiently large, and the working gas heat exchanger Since this becomes unnecessary, if the oil droplet separator is sufficiently small, the dead space for gas will become smaller and the overall specific output will also increase.
よって本発明により、家庭用冷蔵庫やルームクーラーな
どノ」）ｆＩＡ度降下にも使用できるフロン不要の逆ス
ターリング冷凍機が出現し、産業と地球環境上極めて貢
献する所が大きい。Therefore, according to the present invention, an inverted Stirling refrigerator that does not require fluorocarbons and can be used for household refrigerators, room coolers, etc. to reduce fIA degrees has appeared, which will greatly contribute to industry and the global environment.
本発明を説明するため実施例の図面によってその構成と
作用を説明する。In order to explain the present invention, its structure and operation will be explained with reference to drawings of embodiments.
第２図に本発明の一実施例の側面図を示す。FIG. 2 shows a side view of an embodiment of the present invention.
同図において１から１９までの番号の部品の名称作動は
、第１図と全く同じである。In this figure, the names and operations of parts numbered 1 to 19 are exactly the same as in FIG. 1.
第２図の実施例においては、シリンダー９．１０の頂部
附近に循環油を膨張空間１１および圧縮空間１２の中に
微細な霧として吹く噴射ノズル２０．２１を設け、出口
管１３．１４の直後には油滴を分離するサイクロン２２
．２３が設けられ１作動ガス内の循環油の油滴を分離し
て各サイクロンの下部の油だまり２４、２５に流下させ
るように構成しである。In the embodiment of FIG. 2, an injection nozzle 20.21 is provided near the top of the cylinder 9.10 for blowing the circulating oil into the expansion space 11 and the compression space 12 as a fine mist, immediately after the outlet pipe 13.14. A cyclone 22 separates oil droplets.
．． 23 is provided to separate oil droplets of circulating oil in the working gas and allow them to flow down into oil pools 24 and 25 at the bottom of each cyclone.
また液たまり２４．２５内の循環油はそれぞれ別系統と
なって油下降管２１１１．２７でそれぞれ下方に導かれ
、それぞれ冷熱熱交換器１５．放熱熱交換器１７を経由
した後循環液の循環と噴射を司どる噴射ポンプ２８．２
９と油導管３０．３１を経てそれぞれ噴射ノズル２０．
２１へ再循環される。In addition, the circulating oil in the liquid pools 24, 25 are respectively guided downward by oil downcomer pipes 2111, 27 in separate systems, and are respectively guided to the cold heat exchanger 15. Injection pump 28.2 that controls the circulation and injection of the circulating fluid after passing through the radiation heat exchanger 17
9 and oil conduits 30.31 to the injection nozzles 20.31, respectively.
21.
またサイクロン２２．２３の上部出口には作動ガス管路
３２．３３が取りつけられ、中央に作動ガス用再生熱交
換器１６が設けられて両サイクロンと結ばれている。Further, a working gas pipe line 32,33 is attached to the upper outlet of the cyclone 22,23, and a regenerative heat exchanger 16 for the working gas is provided in the center, and is connected to both cyclones.
ここで本発明のもっとも特長とする点として。Here, the most distinctive feature of the present invention.
噴射ポンプ２Ｂ、油導管３０．噴射ノズル２０．サイク
ロン２２．油だまり２４．油下降管路２６．冷熱熱交換
！１１５をもって低温側の循環油が回る低温側循環油ル
ープ３４が形成されて冷熱利用作用が行われ、また一方
で噴射ポンプ２９．噴射ノズル２１．サイクロン２３．
油だまり２５．油下降管路２７．放熱熱交換器！？、油
導管３１をもって高温側の循環油が回る高温側循環油ル
ープ３５がさぎの低温側１！１１ループ３４とは全く別
個で温度の異なるループとして設けられて放熱作用を行
なうことである。Injection pump 2B, oil conduit 30. Injection nozzle 20. Cyclone 22. Oil pool 24. Oil descending pipe line 26. Cold heat heat exchange! 115 forms a low-temperature side circulating oil loop 34 in which the low-temperature side circulating oil circulates to perform cold energy utilization, and on the other hand, the injection pump 29. Injection nozzle 21. Cyclone 23.
Oil puddle 25. Oil descending pipe line 27. Radiation heat exchanger! ? The high-temperature side circulation oil loop 35, in which the high-temperature side circulation oil circulates through the oil conduit 31, is completely separate from the low-temperature side 1!11 loop 34 and is provided as a loop having a different temperature to perform heat dissipation.
いま各噴射ポンプ２８．２９では、それぞれそこに噴射
される循環油の単位時間当りの熱当量が膨張空間１１お
よび圧縮空間１２に出入する高圧ヘリウム等作動ガスの
単位時間当りの熱当量の５倍ないし１０倍程度となるよ
うな流量にて循環油を噴射する。In each of the injection pumps 28 and 29, the heat equivalent per unit time of the circulating oil injected therein is five times the heat equivalent per unit time of the working gas such as high-pressure helium flowing into and out of the expansion space 11 and the compression space 12. Circulating oil is injected at a flow rate that is about 10 times higher.
しかる時は逆スターリングサイクルの原理によって膨張
空間１１および圧縮空間１２の中に生ずる作動ガスの膨
張と圧縮は霧状となった循環油の液滴の存在によってガ
スの温度変化は緩衝されて第１図の実施例におけるよう
な断熱膨張による大きい温度変化を生ずることなく、そ
の６分の１ないし１１分の１という極めて等温変化に近
い膨張及び圧縮を生ずることとなり１作動ガスは逆スタ
ーリングサイクルの理論に近い近似的等温変化をするこ
ととなる。At that time, the expansion and compression of the working gas that occurs in the expansion space 11 and the compression space 12 according to the principle of the reverse Stirling cycle is buffered by the presence of the circulating oil droplets in the form of mist, and the temperature change of the gas is buffered. Without causing large temperature changes due to adiabatic expansion as in the example shown in the figure, expansion and compression occur that are extremely close to isothermal changes of one-sixth to one-eleventh of the temperature changes. This results in an approximately isothermal change close to .
よってまず所期の２０℃ないし４０℃という小温度降下
クーラーに対してもエクセルギ損失は小さくなりかつＣ
ＯＰは極めて大きくなり、また比出力も大きくなる。Therefore, even for a cooler with a small temperature drop of 20°C to 40°C, the exergy loss will be small and the C
OP becomes extremely large, and the specific power also becomes large.
また第１図の在来の逆スターリング冷凍機では熱変換器
１５．１７がガスと液の熱交換であるに反し本発明によ
る第２図の実施例においては、熱はすべて循環油に移さ
れているので熱交換器１５．１７は熱伝達率が高い液・
液熱交換器となるので熱交換器がコンパクトとなる。Furthermore, while in the conventional reverse Stirling refrigerator shown in Fig. 1, the heat converters 15 and 17 exchange heat between gas and liquid, in the embodiment shown in Fig. 2 according to the present invention, all the heat is transferred to the circulating oil. Therefore, the heat exchanger 15.17 uses a liquid with a high heat transfer coefficient.
Since it is a liquid heat exchanger, the heat exchanger becomes compact.
また循環油は潤滑作用があるのでピストンやピストンリ
ングの摩耗も小さい利点もある。Additionally, since the circulating oil has a lubricating effect, it also has the advantage of reducing wear on the piston and piston rings.
第３図には間欠噴射ポンプをもつ場合の本発明の他の一
実施例を示す。FIG. 3 shows another embodiment of the present invention having an intermittent injection pump.
さぎの第２図の実施例が連続作動するポンプ２８２９を
使用しているのにだいし１本実施例はクランク４から副
ロッド３６．３７を出し、小さい径のピストン３８．３
９を油シリンダー４０．４１内で往復させるレシプロ形
の噴射ポンプ４２．４３を用い循環油をシリンダー１．
１．１２内に間欠的に噴射させるものであってとくに図
のような配置をすることによってピストン７．８がシリ
ンダー９．１０内を下降した作動ガスを吸入する行程に
おいて循環油を最も多く噴射することによって各シリン
ダー内へ入る作動ガスと循環油とがよく混合するように
するもので。Although the embodiment shown in FIG. 2 uses a pump 2829 that operates continuously, this embodiment has an auxiliary rod 36.37 extending from the crank 4 and a small diameter piston 38.3.
A reciprocating type injection pump 42.43 that reciprocates oil in the oil cylinder 40.41 circulates oil into the cylinder 1.9.
1.12 is intermittently injected, and by arranging the arrangement as shown in the figure, the maximum amount of circulating oil is injected during the stroke in which the piston 7.8 sucks the working gas that has descended within the cylinder 9.10. This allows the working gas entering each cylinder to mix well with the circulating oil.
また作動ガスが排出される行程においては循環油をそれ
以上噴射しないことによりシリンダー空間内への循環油
の過剰噴射によるオイルハンマー現象を生じさせない効
果がある。なお番号が１ないし３５の部品は第２図の実
施例と全く同一である。Furthermore, by not injecting circulating oil any further during the stroke in which the working gas is discharged, there is an effect of preventing an oil hammer phenomenon caused by excessive injection of circulating oil into the cylinder space. The parts numbered 1 to 35 are exactly the same as those in the embodiment shown in FIG.
また４４．４５．４６．４７は図の方向の循環油逆止弁
である。Further, 44, 45, 46, 47 are circulation oil check valves in the direction shown in the figure.
第４図にはディスプレーサ−形逆スターリングサイクル
冷凍機に対して本発明を適用したさいの一実施例の側面
図を示す。FIG. 4 shows a side view of an embodiment in which the present invention is applied to a displacer type reverse Stirling cycle refrigerator.
本実施例においては４８がデイスプレーサービストンで
あり、４９がパワーピストンであって、それぞれクラン
ク５０．５１の運動によって約９０″の位相差をもって
往復運動し、膨張空間１１と圧縮空間１２を位相差をも
って容積変化させ、それぞれの空間内に入った作動ガス
に冷熱と圧縮熱を発生させる。In this embodiment, 48 is a display service ton, and 49 is a power piston, which reciprocate with a phase difference of about 90'' by the movement of cranks 50 and 51, and position the expansion space 11 and compression space 12. The volume changes based on the phase difference, and cold heat and compression heat are generated in the working gas that enters each space.
本発明はさぎの第２図の実施例と全く同様に低温側と高
温側の油循環ループ３４．３５を有して、冷熱利用と放
熱を行なうのでその作動原理は前と同様である。ただし
本実施例では冷熱側の熱交換器１５は冷蔵庫５２の中に
細いコイル管５３として置かれていて、温度が低くなっ
た循環油が直接に冷蔵庫５２の内部を直接冷却するよう
に構成している。The present invention has cold side and hot side oil circulation loops 34, 35, just like the embodiment of Fig. 2, to utilize cold heat and dissipate heat, so the operating principle is the same as before. However, in this embodiment, the heat exchanger 15 on the cold side is placed in the refrigerator 52 as a thin coiled tube 53, and the circulating oil having a lower temperature is configured to directly cool the inside of the refrigerator 52. ing.
以上が実施例による本発明の原理であるが、なお補言と
して、各機器及び各管路の外部は十分に断熱保温されて
いるものとし、またクランク室に流出した漏洩循環油を
噴射ポンプで再吸引する細管や、二つのサイクロンの液
面のアンバランスを調節するための連通細管のような任
意の形式の補助装置をつけることは自由であり、また逆
スターリングサイクル冷凍機の形式は自由であり、また
循環油の種類９作動ガスの種類、圧力、気液分離装置の
形式、噴射ポンプの形式等は全く自由であって本発明の
原理を損なうものではない。The above is the principle of the present invention according to the embodiments, but as a supplementary note, it is assumed that the outside of each device and each pipe line is sufficiently insulated, and that leaked circulating oil that has leaked into the crank chamber is removed by an injection pump. It is free to attach any type of auxiliary device such as a capillary for re-suction or a communicating capillary for adjusting the unbalance of the liquid level between the two cyclones, and the type of reverse Stirling cycle refrigerator is free. In addition, the type of circulating oil, the type of working gas, the pressure, the type of gas-liquid separator, the type of injection pump, etc. are completely free and do not impair the principles of the present invention.
［効 果］
以上の実施例の説明でわかるように、膨張空間と圧縮空
間内にｆｌ！環油を噴射することによって。[Effect] As can be seen from the explanation of the above embodiments, fl! is present in the expansion space and the compression space. By injecting ring oil.
作動ガスの各空間内状態変化を等温変化に近づけること
によって、小温度降下のクーラーにおいても理論的逆ス
ターリングサイクルに近いＣＯＰを与える逆スターリン
グサイクル冷凍機を得ることができ、フロンを用いない
ことによって地球環境保護に有益であり、コンパクトで
耐久力の高い冷凍機を得ることができる。By bringing the state changes in each space of the working gas closer to isothermal changes, it is possible to obtain a reverse Stirling cycle refrigerator that provides a COP close to the theoretical reverse Stirling cycle even in a cooler with a small temperature drop, and by not using CFCs. A compact and highly durable refrigerator that is beneficial to global environmental protection can be obtained.
第１図には従来の代表的な逆スターリングサイクル冷凍
機の側面図を示す。
第２図には本発明の一実施例の側面図を示す。
第３図には間欠噴射ポンプを持つ場合の本発明の他の一
実施例を示す。
第４図にはディスプレーサ−形逆スターリングサイクル
冷凍機に対して本発明を適用したさいの一実施例の側面
図を示す。
＋１ ＩＩＩ張空間。
】２ 圧縮空間。
２０、２１ 噴射ノズル
２３、２４ サイクロン
２Ｂ、 ２９．４２．４３ 噴射ポンプ１５ Ｗ熟
熱交換器。
１７ 放熱器。
３４ 低温＠循環油ループ
３５ 高温＠循環油ループFIG. 1 shows a side view of a typical conventional reverse Stirling cycle refrigerator. FIG. 2 shows a side view of an embodiment of the present invention. FIG. 3 shows another embodiment of the present invention having an intermittent injection pump. FIG. 4 shows a side view of an embodiment in which the present invention is applied to a displacer type reverse Stirling cycle refrigerator. +1 III Zhang space. ]2 Compressed space. 20, 21 Injection nozzle 23, 24 Cyclone 2B, 29.42.43 Injection pump 15 W mature heat exchanger. 17 Heat sink. 34 Low temperature @ circulating oil loop 35 High temperature @ circulating oil loop
Claims (1)
より作動ガスが膨張してシリンダー内に低温を生ずる膨
張空間と，作動ガスが圧縮されて高温を生ずる圧縮空間
とを有し，両空間の間の管路に再生熱交換器を設けた任
意形式の，逆スターリングサイクル冷凍機において，該
膨張空間と該圧縮空間のそれぞれの出口と該再生熱交換
器の間にサイクロン状の気液分離装置を設け，かつ，該
膨張空間と該圧縮空間のそれぞれの頂部には噴射ノズル
を設けて，適当な低粘度冷凍機油等を主体とする循環油
を，膨張空間内に向けては膨張空間側の噴射ポンプより
，圧縮空間内に向けては圧縮空間側の噴射ポンプより，
それぞれの空間を出入する作動ガスの重量流量に数倍す
る流量にて，該油噴射ノズルを通じて微細な噴霧として
それぞれの空間の内部に噴射し両空間の作動ガス内に十
分な比熱をもつ油滴の存在することによつて，それぞれ
の空間に生ずる作動ガスの膨張と圧縮とを等温変化に近
づけて温度の降下と上昇をかなり小さいものとし，それ
ぞれの空間より流出する作動ガス内の循環油の該油滴を
再生熱交換器にいたる前に前出のサイクロン状の気液分
離装置によって分離捕捉して液状として別個の管路にそ
れぞれ流下させ，膨張空間側よりは噴射時より若干低温
となって出る循環油の冷熱を直接に冷凍に利用するか，
もしくは低温熱交換器にてブラインに移して冷凍利用し
た後該膨張空間側噴射ポンプにもどして再循環させるよ
うに構成し，また圧縮空間側より噴射時より若干高温と
なって出る循環油の熱は適当な放熱器によって外部に放
熱した後，該圧縮空間側の噴射ポンプにもどして再循環
するように構成することにより，作動ガスの発生する冷
熱量と圧縮熱とを作動ガスの顕熱によることなく互いに
混合しない別個の管路の循環油の顕熱によって冷凍利用
及び放熱させるようにした逆スターリングサイクル冷凍
機の原理。 なおこのさい，各機器及び各管路の外側は十分に断熱保
温するものとし，また逆スターリングサイクル冷凍器の
シリンダ配置形式は二気筒形でもディスプレーサー形で
も，リネヤ形でもよい。 また循環油の種類，圧力，作動ガスの種類，気液分離器
や噴射ポンプ等補機の形式材質等は自由である。[Scope of Claims] The cylinder has an expansion space in which working gas is expanded by the movement of two pistons moved by a crank and produces a low temperature in the cylinder, and a compression space in which the working gas is compressed and produces a high temperature; In any type of inverted Stirling cycle refrigerator in which a regenerative heat exchanger is provided in the conduit between both spaces, a cyclone-like air is provided between the respective outlets of the expansion space and the compression space and the regenerative heat exchanger. A liquid separation device is provided, and an injection nozzle is provided at the top of each of the expansion space and the compression space, and circulating oil mainly composed of suitable low-viscosity refrigerating machine oil is directed into the expansion space for expansion. From the injection pump on the space side, towards the compression space, from the injection pump on the compression space side,
Oil droplets with sufficient specific heat are injected into each space as a fine spray through the oil injection nozzle at a flow rate several times the weight flow rate of the working gas entering and exiting each space. Due to the existence of the working gas, the expansion and compression of the working gas occurring in each space are brought closer to isothermal changes, and the drop and rise in temperature are made considerably small, and the circulating oil in the working gas flowing out from each space is reduced. Before reaching the regenerative heat exchanger, the oil droplets are separated and captured by the aforementioned cyclone-like gas-liquid separator and flowed down as liquid into separate pipes, so that the temperature on the expansion space side is slightly lower than that at the time of injection. Is the cold energy of the circulating oil directly used for freezing?
Alternatively, the structure is such that the oil is transferred to brine in a low-temperature heat exchanger, frozen, and then returned to the injection pump on the expansion space side for recirculation. By radiating heat to the outside by a suitable radiator and then returning it to the injection pump on the compression space side for recirculation, the amount of cold heat generated by the working gas and the heat of compression can be converted to the sensible heat of the working gas. The principle of an inverted Stirling cycle refrigerator is that the sensible heat of circulating oil in separate pipes that do not mix with each other is used for refrigeration and heat is radiated. In this case, the outside of each device and each conduit shall be sufficiently insulated and the cylinder arrangement type of the reverse Stirling cycle refrigerator may be a two-cylinder type, a displacer type, or a linear type. In addition, the type and pressure of circulating oil, the type of working gas, the type and material of auxiliary equipment such as gas-liquid separators and injection pumps, etc. are free.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21047190A JPH0493559A (en) | 1990-08-10 | 1990-08-10 | Reverse stirling refrigeration machine having circulating oil |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21047190A JPH0493559A (en) | 1990-08-10 | 1990-08-10 | Reverse stirling refrigeration machine having circulating oil |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0493559A true JPH0493559A (en) | 1992-03-26 |
Family
ID=16589890
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21047190A Pending JPH0493559A (en) | 1990-08-10 | 1990-08-10 | Reverse stirling refrigeration machine having circulating oil |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0493559A (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5638684A (en) * | 1995-01-16 | 1997-06-17 | Bayer Aktiengesellschaft | Stirling engine with injection of heat transfer medium |
| WO2007025027A2 (en) * | 2005-08-24 | 2007-03-01 | Purdue Research Foundation | Thermodynamic systems operating with near-isothermal compression and expansion cycles |
| US7617680B1 (en) | 2006-08-28 | 2009-11-17 | Cool Energy, Inc. | Power generation using low-temperature liquids |
| US7694514B2 (en) | 2007-08-08 | 2010-04-13 | Cool Energy, Inc. | Direct contact thermal exchange heat engine or heat pump |
| US7805934B1 (en) | 2007-04-13 | 2010-10-05 | Cool Energy, Inc. | Displacer motion control within air engines |
| US7810330B1 (en) | 2006-08-28 | 2010-10-12 | Cool Energy, Inc. | Power generation using thermal gradients maintained by phase transitions |
| US7877999B2 (en) | 2007-04-13 | 2011-02-01 | Cool Energy, Inc. | Power generation and space conditioning using a thermodynamic engine driven through environmental heating and cooling |
| US8061132B2 (en) | 2009-06-29 | 2011-11-22 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8247915B2 (en) | 2010-03-24 | 2012-08-21 | Lightsail Energy, Inc. | Energy storage system utilizing compressed gas |
| US8353156B2 (en) | 2009-06-29 | 2013-01-15 | Lightsail Energy Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8436489B2 (en) | 2009-06-29 | 2013-05-07 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| WO2022198246A1 (en) * | 2021-03-26 | 2022-09-29 | Hofbauer Fritz | Hot-fluid machine |
-
1990
- 1990-08-10 JP JP21047190A patent/JPH0493559A/en active Pending
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5638684A (en) * | 1995-01-16 | 1997-06-17 | Bayer Aktiengesellschaft | Stirling engine with injection of heat transfer medium |
| WO2007025027A2 (en) * | 2005-08-24 | 2007-03-01 | Purdue Research Foundation | Thermodynamic systems operating with near-isothermal compression and expansion cycles |
| WO2007025027A3 (en) * | 2005-08-24 | 2007-05-03 | Purdue Research Foundation | Thermodynamic systems operating with near-isothermal compression and expansion cycles |
| US7617680B1 (en) | 2006-08-28 | 2009-11-17 | Cool Energy, Inc. | Power generation using low-temperature liquids |
| US7810330B1 (en) | 2006-08-28 | 2010-10-12 | Cool Energy, Inc. | Power generation using thermal gradients maintained by phase transitions |
| US7805934B1 (en) | 2007-04-13 | 2010-10-05 | Cool Energy, Inc. | Displacer motion control within air engines |
| US7877999B2 (en) | 2007-04-13 | 2011-02-01 | Cool Energy, Inc. | Power generation and space conditioning using a thermodynamic engine driven through environmental heating and cooling |
| US7694514B2 (en) | 2007-08-08 | 2010-04-13 | Cool Energy, Inc. | Direct contact thermal exchange heat engine or heat pump |
| US8061132B2 (en) | 2009-06-29 | 2011-11-22 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8065874B2 (en) | 2009-06-29 | 2011-11-29 | Lightsale Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8191360B2 (en) | 2009-06-29 | 2012-06-05 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8196395B2 (en) | 2009-06-29 | 2012-06-12 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8240142B2 (en) | 2009-06-29 | 2012-08-14 | Lightsail Energy Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8353156B2 (en) | 2009-06-29 | 2013-01-15 | Lightsail Energy Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8436489B2 (en) | 2009-06-29 | 2013-05-07 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
| US8247915B2 (en) | 2010-03-24 | 2012-08-21 | Lightsail Energy, Inc. | Energy storage system utilizing compressed gas |
| WO2022198246A1 (en) * | 2021-03-26 | 2022-09-29 | Hofbauer Fritz | Hot-fluid machine |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4873831A (en) | Cryogenic refrigerator employing counterflow passageways | |
| CN105485953B (en) | Ultra-low temperature refrigerating device | |
| JPH0493559A (en) | Reverse stirling refrigeration machine having circulating oil | |
| US3221509A (en) | Refrigeration method and apparatus | |
| KR101239846B1 (en) | Stirling engine of which the heat-exchange parts are improved | |
| US5609034A (en) | Cooling system | |
| JP5714461B2 (en) | Cryogenic refrigerator | |
| US3673809A (en) | In-line multistage cryogenic apparatus | |
| CN106247661B (en) | A kind of multi-stage pulse tube refrigeration machine | |
| JP6188619B2 (en) | Cryogenic refrigerator | |
| JP6109057B2 (en) | Regenerator type refrigerator | |
| JP3751613B2 (en) | Heat exchange system and Stirling refrigerator | |
| CN110849055A (en) | Low-temperature refrigerator | |
| CN107036320A (en) | Cold compression formula vascular refrigerator and pre-cooling type refrigerator system | |
| JP2941558B2 (en) | Stirling refrigeration equipment | |
| CN100427848C (en) | Heat sound driving pulse pipe refrigeration machine system | |
| Hachem et al. | Impact of operating parameters on beta type regenerative Stirling machine performances | |
| US3365896A (en) | Low temperature refrigerating arrangement | |
| CN209041062U (en) | A kind of air compressor machine water-cooled cylinder structure | |
| CN109990496A (en) | A kind of tandem vascular refrigerator | |
| CN1271833A (en) | Supercritical backheat heated heat pump unit driven thermodynamically | |
| CN2510796Y (en) | Inertial energy-saving pneumatic returning-type refrigerating compressor | |
| KR940010579B1 (en) | Stirring cycle | |
| TWI512190B (en) | Cooling and heating hybrid device having thermal-lag stirling engine and control method thereof | |
| JP3363697B2 (en) | Refrigeration equipment |