JPH0350955B2 - - Google Patents
Info
- Publication number
- JPH0350955B2 JPH0350955B2 JP13481385A JP13481385A JPH0350955B2 JP H0350955 B2 JPH0350955 B2 JP H0350955B2 JP 13481385 A JP13481385 A JP 13481385A JP 13481385 A JP13481385 A JP 13481385A JP H0350955 B2 JPH0350955 B2 JP H0350955B2
- Authority
- JP
- Japan
- Prior art keywords
- expansion
- variable
- space
- piston
- working refrigerant
- 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
Links
- 230000006835 compression Effects 0.000 claims description 37
- 238000007906 compression Methods 0.000 claims description 37
- 238000005057 refrigeration Methods 0.000 claims description 18
- 230000003111 delayed effect Effects 0.000 claims description 3
- 239000003507 refrigerant Substances 0.000 description 38
- 238000010586 diagram Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000001307 helium Substances 0.000 description 2
- 229910052734 helium Inorganic materials 0.000 description 2
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 239000002826 coolant Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 239000011232 storage material Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
【発明の詳細な説明】
（発明の利用分野）
本発明は、可変圧縮空間、放熱器、蓄冷器及び
複数の可変膨脹空間を互いに連通させたスターリ
ングサイクルし、ブルミエールサイクル、ギホー
ドマクマホンサイクル、ソルベイサイクル等の多
段膨脹型の冷凍機に関する。この種の冷凍機は、
クライオポンプ、スキツド素子、超電導磁石等の
冷却に利用されるが、本発明は、これら冷凍機の
冷凍量を、２個以上の可変膨脹空間の容積の位相
を変えることで増大させるためのものである。Detailed Description of the Invention (Field of Application of the Invention) The present invention relates to a Stirling cycle in which a variable compression space, a radiator, a regenerator, and a plurality of variable expansion spaces are communicated with each other, and includes a Blumière cycle, a Gifford-McMahon cycle, The present invention relates to a multi-stage expansion type refrigerator such as a Solvay cycle. This type of refrigerator is
It is used for cooling cryopumps, skid elements, superconducting magnets, etc., and the present invention is intended to increase the amount of refrigeration in these refrigerators by changing the phase of the volumes of two or more variable expansion spaces. be.
（従来技術とその問題点）
多段膨脹型の冷凍機、そのものは、実公昭43−
17026号公報に開示される如く公知である。同公
報に示される冷凍機の基本構成を、添付第４図に
示す。冷凍機の可変圧縮空間１は、放熱器２、蓄
冷器３及び熱交換部を介して第１の可変膨脹空間
４と連通し、さらに、蓄冷器３、別の蓄冷器５及
び熱交換器６を介して第２の可変膨脹空間７へと
連通する。両膨脹空間４，７を、多段膨脹ピスト
ン８と膨脹シリンダ９，１０とで画定し、又、可
変圧縮空間１を、圧縮ピストン１１と圧縮シリン
ダ１２とで形成する。(Prior art and its problems) The multi-stage expansion type refrigerator itself was developed in 1973-
This is known as disclosed in Japanese Patent No. 17026. The basic configuration of the refrigerator disclosed in the publication is shown in attached FIG. 4. The variable compression space 1 of the refrigerator communicates with the first variable expansion space 4 via a heat radiator 2, a regenerator 3, and a heat exchanger, and is further connected to a regenerator 3, another regenerator 5, and a heat exchanger 6. It communicates with the second variable expansion space 7 via. Both expansion spaces 4 and 7 are defined by a multistage expansion piston 8 and expansion cylinders 9 and 10, and a variable compression space 1 is formed by a compression piston 11 and a compression cylinder 12.
両ピストン８，１１を、コネクテイングロツド
１３，１４を介して、クランク軸１５に接続させ
る。モータに接続されたクランク軸１５は、膨脹
ピストン８の動きを、圧縮ピストン１１の動きよ
り90度（角度）位相が進むよう形成される。尚、
作動空間には、作動冷媒として、たとえば、ヘリ
ウムガスを封入する。 Both pistons 8, 11 are connected to a crankshaft 15 via connecting rods 13, 14. A crankshaft 15 connected to the motor is configured to cause the movement of the expansion piston 8 to lead the movement of the compression piston 11 by 90 degrees (angular) phase. still,
The working space is filled with, for example, helium gas as a working refrigerant.
モータによりクランク軸１５を回転させると、
圧縮ピストン１１が上昇し、可変圧縮空間１内の
作動冷媒は、圧力、温度とを高くなり、放熱器２
内に流入する。作動冷媒は、放熱器２内でその温
度を下げ、さらに、蓄冷器３によつて冷却されて
温度を下げ、第１の可変膨脹空間４と蓄冷器５内
に流入する。蓄冷器５に流入した作動冷媒は、蓄
冷材によつて冷却され、さらに降温し熱交換器６
を通つて第２の可変膨脹空間７内に流入する。両
膨脹空間４，７に流入した作動冷媒は、膨脹ピス
トン８の下方向への移動によつて膨脹し、その温
度をさらに下げ、たとえば、第１の可変膨脹空間
４の作動冷媒を90K、第２の可変膨脹空間７内の
作動冷媒を30Kとさせる。 When the crankshaft 15 is rotated by the motor,
The compression piston 11 rises, and the working refrigerant in the variable compression space 1 increases in pressure and temperature, and the radiator 2
flow inside. The working refrigerant lowers its temperature in the radiator 2, is further cooled by the regenerator 3, lowers its temperature, and flows into the first variable expansion space 4 and the regenerator 5. The working refrigerant that has flowed into the regenerator 5 is cooled by the regenerator material, further lowers its temperature, and passes through the heat exchanger 6.
It flows into the second variable expansion space 7 through. The working refrigerant that has flowed into both expansion spaces 4 and 7 is expanded by the downward movement of the expansion piston 8, and its temperature is further lowered. The working refrigerant in the variable expansion space 7 of No. 2 is set to 30K.
この冷凍機の膨脹ピストン８の一行程の圧力
を、第２図に点線で示す。同図から明らかなよう
に、膨脹ピストン８が、上死点から略37度（クラ
ンク軸１５の回転角に変換した値）の位置で圧力
が最大となつている。一方、第２の可変膨脹空間
７でのPV線図を第３図に点線で示す。この点線
に囲まれた面積は、作動冷媒が可変膨脹空間７内
で、膨脹ピストン８がなした膨脹仕事に相当し、
この膨脹仕事が第２の可変膨脹空間７で発生した
冷凍量となる。 The pressure during one stroke of the expansion piston 8 of this refrigerator is shown by a dotted line in FIG. As is clear from the figure, the pressure of the expansion piston 8 is at its maximum at a position approximately 37 degrees from the top dead center (value converted to the rotation angle of the crankshaft 15). On the other hand, the PV diagram in the second variable expansion space 7 is shown by dotted lines in FIG. The area surrounded by this dotted line corresponds to the expansion work done by the expansion piston 8 of the working refrigerant in the variable expansion space 7,
This expansion work becomes the amount of refrigeration generated in the second variable expansion space 7.
第３図点線で示す如く、従来の冷凍機の可変膨
脹空間７の単位容積当りの冷凍量が少ない。この
原因として考えられることは、作動冷媒の圧縮比
が小さいこと、及び作動冷媒の圧力最大時におけ
る膨脹ピストン８の位置が最適でないことであ
り、このため、第２の可変膨脹空間７でのPV線
図（第３図点線参照）の閉曲線の面積が小さくな
り、可変膨脹空間７の作動冷媒が発生する冷凍が
小さくなるためである。 As shown by the dotted line in FIG. 3, the amount of refrigeration per unit volume of the variable expansion space 7 of the conventional refrigerator is small. Possible causes of this are that the compression ratio of the working refrigerant is small and that the position of the expansion piston 8 at the maximum pressure of the working refrigerant is not optimal, so that the PV in the second variable expansion space 7 This is because the area of the closed curve in the diagram (see the dotted line in Figure 3) becomes smaller, and the amount of refrigeration generated by the working refrigerant in the variable expansion space 7 becomes smaller.
（本発明の技術的課題）
本発明は、可変膨脹空間の単位容積当りの発生
冷凍量を増大することにより、従来技術の欠点を
解消させることを解消すべき技術的課題とする。(Technical Problem of the Present Invention) A technical problem of the present invention is to eliminate the drawbacks of the prior art by increasing the amount of refrigeration generated per unit volume of the variable expansion space.
（本発明の技術的手段とその作用）
前述した技術的課題を解決するために、本発明
は、２個以上の可変膨脹空間のうちの１つの可変
膨脹空間の容積に対して他の少なくとも１個以上
の可変膨脹空間の容積の位相を変える技術的手段
を基本的に採用する。この結果、第１の可変膨脹
空間の容積は、第２の可変膨脹空間の容積の動き
より位相がずれ、第２図の実線で示す如く、作動
冷媒の圧力変化が大きくなる。このため、第３図
の実線で示す如く、第２の可変膨脹空間でのPV
線図の閉曲線に囲まれた面積が大きくなり、第２
の可変膨脹空間での単位容積当りの冷凍量が増大
する。(Technical Means of the Present Invention and its Effects) In order to solve the above-mentioned technical problem, the present invention provides that the volume of one variable expansion space among two or more variable expansion spaces is reduced by at least one other variable expansion space. Basically, a technical means is adopted to change the phase of the volume of more than one variable expansion space. As a result, the volume of the first variable expansion space is out of phase with the movement of the volume of the second variable expansion space, and as shown by the solid line in FIG. 2, the pressure change of the working refrigerant increases. Therefore, as shown by the solid line in Figure 3, the PV in the second variable expansion space
The area surrounded by the closed curve in the diagram increases, and the second
The amount of refrigeration per unit volume in the variable expansion space increases.
（実施例）
第１図を参照する。可変圧縮空間１０１を、圧
縮シリンダ１１５、圧縮ピストン１０９、ピスト
ンリング１１２より形成し、該圧縮空間１０１を
放熱器１０２、蓄冷器１０３，１０４に連通させ
る。(Example) Refer to FIG. 1. A variable compression space 101 is formed by a compression cylinder 115, a compression piston 109, and a piston ring 112, and the compression space 101 is communicated with a radiator 102 and regenerators 103 and 104.
一方、第１の可変膨脹空間１０７を、膨脹シリ
ンダ１１６、膨脹ピストン１１０、ピストンリン
グ１１３より形成し、第２の可変膨脹空間１０８
を、膨脹ピストン１１１、膨脹シリンダ１１７、
ピストンリング１１４より形成する。蓄冷器１０
３の低温端を導管１０５を介して第１の可変膨脹
空間１０７に連通させ且つ蓄冷器１０４の低温端
を導管１０６を介して第２の可変膨脹空間１０８
に連通させる。 On the other hand, a first variable expansion space 107 is formed by an expansion cylinder 116, an expansion piston 110, and a piston ring 113, and a second variable expansion space 108
, an expansion piston 111, an expansion cylinder 117,
It is formed from a piston ring 114. Cool storage device 10
A cold end of the regenerator 104 is connected to a first variable expansion space 107 through a conduit 105, and a cold end of the regenerator 104 is connected to a second variable expansion space 108 through a conduit 106.
communicate with.
圧縮ピストン１０９、両膨脹ピストン１１０，
１１１は、コネクテイングロツド１１８，１１
９，１２０を介して、クランク軸１２１に接続す
る。尚、クランク軸１２１は図示しないモータに
結合される。クランク軸１２１は、圧縮ピストン
１０９の動きが、第２の可変膨脹ピストン１１１
より略90度の位相遅れを作り且つ第１の可変膨脹
ピストン１１０が第２の可変膨脹ピストン１１１
より略30度の位相遅れを作るよう構成される。放
熱器１０２内には、導管１０２ａ，１０２ｂを介
して水等の寒剤が循環する。 compression piston 109, both expansion pistons 110,
111 is a connecting rod 118, 11
It is connected to the crankshaft 121 via 9 and 120. Incidentally, the crankshaft 121 is coupled to a motor (not shown). The crankshaft 121 is arranged so that the movement of the compression piston 109 is connected to the second variable expansion piston 111.
A phase delay of approximately 90 degrees is created, and the first variable expansion piston 110 is connected to the second variable expansion piston 111.
It is configured to create a phase delay of approximately 30 degrees. A coolant such as water is circulated within the radiator 102 via conduits 102a and 102b.
クランク軸１２１の回転により、圧縮ピストン
１０９が上昇すると、可変圧縮空間１０１内のヘ
リウム等の作動冷媒が圧縮、昇温されて放熱器１
０２に流入して冷却され、蓄冷器１０３，１０４
に流入する。蓄冷器１０３に流入した作動冷媒の
一部が、導管１０５を介して、第１の可変膨脹空
間１０７に入り、クランク軸１２１による可変膨
脹ピストン１１０の下向きの移動と共に、膨脹
し、第１の可変膨脹空間１０７に冷凍を発生させ
る。即ち、作動冷媒は第１の膨脹ピストン１１０
を下方向に移動させる膨脹仕事量に相当する冷凍
量を発生する。同様に、蓄冷器１０４に流入した
作動冷媒も導管１０６を通つて第２の可変膨脹空
間１０８に流入する。第２の可変膨脹空間１０８
に流入した作動冷媒が、膨脹ピストン１１１を下
方向に移動せしめる膨脹仕事量に相当する冷凍を
発生させる。第２の可変圧縮空間１０８での冷凍
は、第１の可変圧縮空間１０７での冷凍より低温
となる。 When the compression piston 109 rises due to the rotation of the crankshaft 121, the working refrigerant such as helium in the variable compression space 101 is compressed and heated, and the radiator 1
02 and is cooled, and the cold storage units 103 and 104
flows into. A portion of the working refrigerant that has flowed into the regenerator 103 enters the first variable expansion space 107 via the conduit 105, expands as the variable expansion piston 110 moves downward by the crankshaft 121, and expands into the first variable expansion space 107. Refrigeration is generated in the expansion space 107. That is, the working refrigerant is in the first expansion piston 110.
The amount of refrigeration that is equivalent to the amount of expansion work that moves the Similarly, the working refrigerant that has entered the regenerator 104 also flows into the second variable expansion space 108 through the conduit 106 . Second variable expansion space 108
The working refrigerant flowing into generates refrigeration corresponding to the expansion work that moves the expansion piston 111 downward. Refrigeration in the second variable compression space 108 is at a lower temperature than freezing in the first variable compression space 107.
第２の可変膨脹空間１０８内の作動冷媒は、膨
脹ピストン１１１の上方向への移動により導管１
０６を介して、蓄冷器１０４，１０３に流入し、
蓄冷材から熱をうばい昇温し、放熱器１０２を通
つて可変圧縮空間１０１に流入する。第１の可変
膨脹空間１０７内の作動冷媒も、膨脹ピストン１
１０の上方向への移動によつて、導管１０５を介
して、蓄冷器１０３に流入する。蓄冷器１０３に
流入した作動冷媒は、膨脹ピストン１１１が上方
位置をとる場合には、蓄冷器１０３内の蓄冷材か
ら熱をうばい昇温し、放熱器１０２を通過し、可
変圧縮空間１０１に入り、膨脹ピストン１１１が
下方位置をとる場合には、蓄冷器１０４に流入
し、蓄冷材によつて冷却される。 The working refrigerant in the second variable expansion space 108 is transferred to the conduit 1 by the upward movement of the expansion piston 111.
06, flows into the regenerators 104, 103,
Heat is absorbed from the cold storage material to raise the temperature and flows into the variable compression space 101 through the radiator 102. The working refrigerant in the first variable expansion space 107 also flows through the expansion piston 1
10 flows into the regenerator 103 via the conduit 105. When the expansion piston 111 assumes the upper position, the working refrigerant that has flowed into the regenerator 103 increases its temperature by absorbing heat from the regenerator material in the regenerator 103, passes through the radiator 102, and enters the variable compression space 101. When the expansion piston 111 assumes the lower position, the air flows into the regenerator 104 and is cooled by the regenerator material.
膨張ピストン１１１が略上死点付近（可変膨張
空間１０８の容積が最小）にあるとき、圧縮ピス
トン１０９は、略中立点付近におり、上死点に向
かつて動いているので可変圧縮空間１０１内の作
動冷媒は、放熱器１０２、蓄冷器１０３，１０
４、導管１０６を通つて可変膨張空間１０８に流
入し、又膨張ピストン１０７は、略上死点より手
前の位置におり、上死点に向かつて動いているの
で、可変膨張空間内の作動冷媒は、導管１０５、
蓄冷器１０４、導管１０６を通つて可変膨張空間
１０８に流入する。従来のように、膨張ピストン
１１１と膨張ピストン１０７の動きが同位相の場
合には、膨張ピストン１１１、略上死点付近で
は、可変圧縮空間１０１内の作動冷媒は、放熱器
１０２、蓄冷器１０３，１０４、導管１０５，１
０６を通つて、可変膨張空間１０７，１０８に流
入する。上記の理由により、従来のように膨張ピ
ストン１１１と１０７の動きが同位相の場合にく
らべ本発明では、膨張ピストン１１１の動きが膨
張ピストン１１０の動きより位相が進んでいるの
で可変膨張空間１０８に流入する作動冷媒の量は
従来の場合に比べ多く流れるので膨張ピストン１
０８の膨張仕事量は、従来の場合より多くなる。
膨張ピストン１１１が略下死点付近にいる時は、
圧縮ピストン１０９は、略中立点付近におり、下
死点に向かつて動いているので、可変膨張空間１
０８内の作動冷媒は、導管１０６、蓄冷器１０
４，１０３、放熱器１０２を通つて可変圧縮空間
１０２に流入し、又この時膨張ピストン１０７
は、下死点より手前の位置におり、下死点に向か
つて動いているので、作動冷媒を吸込んでいる。
即可変膨張空間１０８内の作動冷媒が、導管１０
６、蓄冷器１０４、導管１０５を通つて可変膨張
空間１０７に流入する。従来のように膨張ピスト
ン１０７と１０８の動きが同位相の場合には、可
変膨張空間１０８内の作動冷媒は可変膨張空間１
０７には流入しない。即ち、膨張ピストン１１１
が可変膨張空間１０８内の作動冷媒を吐き出して
いる時は膨張ピストン１０７も可変膨張空間１０
７内の作動冷媒を吐き出している。可変膨張空間
１０７，１０８より吐き出された作動冷媒は、可
変圧縮空間１０１に流入する。上記の理由によ
り、従来のように膨張ピストン１１１と１０７の
動きが同位相の場合にくらべ、本発明で膨張ピス
トン１１１の動きが１１０の動きより位相が進ん
でいるので、可変膨張ピストン１０８内より吐き
出される作動冷媒は、可変圧縮空間１０１と可変
膨張空間１０７にも吸い込まれるので、膨張ピス
トン１１１が可変膨張空間１０８内の作動冷媒を
吐出するための仕事量が少なくなる。 When the expansion piston 111 is approximately at the top dead center (the volume of the variable expansion space 108 is the minimum), the compression piston 109 is approximately at the neutral point and is moving toward the top dead center, so there is no space inside the variable compression space 101. The working refrigerant is the radiator 102, the regenerators 103, 10
4. The working refrigerant in the variable expansion space flows through the conduit 106 into the variable expansion space 108, and since the expansion piston 107 is at a position approximately before the top dead center and is moving toward the top dead center, the working refrigerant in the variable expansion space is the conduit 105,
It flows into the variable expansion space 108 through the regenerator 104 and the conduit 106. As in the conventional case, when the expansion piston 111 and the expansion piston 107 move in the same phase, the working refrigerant in the variable compression space 101 is transferred to the radiator 102 and the regenerator 103 when the expansion piston 111 is near the top dead center. , 104, conduit 105, 1
06 and into variable expansion spaces 107 and 108. For the above reasons, compared to the conventional case in which the movements of the expansion pistons 111 and 107 are in the same phase, in the present invention, the movement of the expansion piston 111 is ahead of the movement of the expansion piston 110 in phase, so that the variable expansion space 108 Since the amount of working refrigerant flowing in is larger than in the conventional case, the expansion piston 1
The expansion work of 08 is larger than that of the conventional case.
When the expansion piston 111 is near the bottom dead center,
The compression piston 109 is near the neutral point and is moving toward the bottom dead center, so the variable expansion space 1
The working refrigerant in 08 is transferred to conduit 106, regenerator 10
4,103, flows into the variable compression space 102 through the radiator 102, and at this time, the expansion piston 107
is located before the bottom dead center and is moving toward the bottom dead center, so it is sucking in the working refrigerant.
The working refrigerant in the rapidly variable expansion space 108 is transferred to the conduit 10
6. It flows into the variable expansion space 107 through the regenerator 104 and the conduit 105. When the expansion pistons 107 and 108 move in the same phase as in the conventional case, the working refrigerant in the variable expansion space 108 flows into the variable expansion space 1.
It does not flow into 07. That is, the expansion piston 111
is discharging the working refrigerant in the variable expansion space 108, the expansion piston 107 also discharges the working refrigerant in the variable expansion space 10.
The working refrigerant in 7 is being discharged. The working refrigerant discharged from the variable expansion spaces 107 and 108 flows into the variable compression space 101. For the above reasons, compared to the conventional case where the movements of the expansion pistons 111 and 107 are in the same phase, in the present invention, the movement of the expansion piston 111 is ahead of the movement of the movement of the expansion piston 110. Since the discharged working refrigerant is also sucked into the variable compression space 101 and the variable expansion space 107, the amount of work for the expansion piston 111 to discharge the working refrigerant in the variable expansion space 108 is reduced.
可変膨張空間１０８で発生される冷凍量は膨張
ピストン１１１の膨張仕事量から膨張ピストン１
１１が可変膨張空間１０８内の作動冷媒を吐出す
るのに要する仕事量を差引いたものであるから、
前述した理由により、本発明では従来の場合（２
つの膨張ピストンの動きが同位相の場合）にくら
べ可変膨張空間１０８で発生される冷凍量は多く
なる。 The amount of refrigeration generated in the variable expansion space 108 is calculated from the expansion work of the expansion piston 111.
Since 11 is the amount of work required to discharge the working refrigerant in the variable expansion space 108,
For the reasons mentioned above, in the present invention, the conventional case (2
The amount of refrigeration generated in the variable expansion space 108 is larger than in the case where the movements of the two expansion pistons are in the same phase).
尚、可変圧縮空間１０１の容積VC、可変膨張
空間１０７の容積VE1、可変膨張空間１０８の容
積VE2とすれば、VC、VE1、VE2は、一般に、次式
で示される。 Incidentally, assuming that the volume of the variable compression space 101 is V C , the volume of the variable expansion space 107 is V E1 , and the volume of the variable expansion space 108 is V E2 , V C , V E1 , and V E2 are generally expressed by the following equations. It is indicated by.
VE1はVE2に対してφ2−φ1位相が遅れているこ
とが分る。 It can be seen that V E1 is delayed by φ 2 −φ 1 phase with respect to V E2 .
可変圧縮空間１０１の容積、可変膨張空間１０
７の容積と可変膨張空間１０８の容積の位相を変
えるために前述した如く、本例では各ピストンの
動きの位相を変えている。 Volume of variable compression space 101, variable expansion space 10
7 and the volume of the variable expansion space 108, the phase of the movement of each piston is changed in this example, as described above.
前述した如く、膨脹ピストン１１０の動きを、
膨脹ピストン１１１の動きより位相を遅らせてい
るので、第１の可変膨脹空間１０７の容積は第２
の可変膨脹空間１０８の容積の動きより位相が遅
れる。かくして、第２図の実線で示すように作動
冷媒の圧力変化は大きくなり、又、圧力の最大な
る位置が、膨脹ピストン１１１の上死点から略45
度下死点側に向つた位置に生ずる。この結果、第
３図の実線で示すように、第２の可変膨脹空間１
０８でのPV線図の閉曲線に囲まれた面積は、従
来のもの（第３図の点線）より大きくなる。この
実線で示す閉曲線によつて囲まれた面積は、第２
の可変膨脹空間１０８で作動冷媒が膨脹ピストン
１１１になした膨脹仕事量に相当する。この膨脹
仕事量は、第２の可変膨脹空間１０８で発生した
冷凍量となる。従つて、本実施例の単位容積当り
の冷凍量が従来の冷凍機のそれより大きくなる。 As mentioned above, the movement of the expansion piston 110 is
Since the phase of the movement of the expansion piston 111 is delayed, the volume of the first variable expansion space 107 is equal to that of the second variable expansion space 107.
The phase lags behind the movement of the volume of the variable expansion space 108. As a result, the pressure change of the working refrigerant increases as shown by the solid line in FIG.
Occurs in a position facing toward bottom dead center. As a result, as shown by the solid line in FIG.
The area surrounded by the closed curve of the PV diagram at 08 is larger than that of the conventional one (dotted line in Figure 3). The area surrounded by this closed curve shown by the solid line is the second
This corresponds to the amount of expansion work done by the working refrigerant on the expansion piston 111 in the variable expansion space 108 of . This expansion work amount becomes the amount of refrigeration generated in the second variable expansion space 108. Therefore, the amount of refrigeration per unit volume of this embodiment is larger than that of the conventional refrigerator.
（効果）
本発明によれば、可変膨脹空間での単位容積当
りの冷凍量が増大するため、従来より低い温度が
得られる。たとえば、可変膨脹空間と蓄冷器との
間に凝縮器を設ける場合、圧縮比が低下すること
なくむしろ増大するので凝縮能力を増大させ得
る。(Effects) According to the present invention, since the amount of refrigeration per unit volume in the variable expansion space increases, a lower temperature than before can be obtained. For example, when a condenser is provided between the variable expansion space and the regenerator, the compression ratio increases rather than decreases, thereby increasing the condensing capacity.
ところで、可変圧縮空間の容積を増大させるこ
とで、可変膨脹空間の単位容積当りの冷凍量を増
大させることができるが、しかし、この場合、可
変圧縮空間の増大に比例して圧縮仕事が増大し、
摩擦損失も増大する。この結果、冷凍機の消費動
力が増大し、効率が低下するが、本発明によれ
ば、このような不具合を生じない。 By the way, by increasing the volume of the variable compression space, the amount of refrigeration per unit volume of the variable expansion space can be increased, but in this case, the compression work increases in proportion to the increase in the variable compression space. ,
Friction losses also increase. As a result, the power consumption of the refrigerator increases and the efficiency decreases, but according to the present invention, such problems do not occur.
第１図は本発明の一例の冷凍機の断面図、第２
図は作動冷媒の圧力変動を示すグラフ図、第３図
はPV線図を示すグラフ図、および第４図は従来
例の冷凍機の断面図である。
図中：１０１……可変圧縮空間、１０２……放
熱器、１０３，１０４……蓄冷器、１０７，１０
８……可変膨脹空間、１０９……圧縮ピストン、
１１０，１１１……膨脹ピストン、１２１……ク
ランク軸。
FIG. 1 is a sectional view of a refrigerator as an example of the present invention, and FIG.
FIG. 3 is a graph showing pressure fluctuations of the working refrigerant, FIG. 3 is a graph showing a PV diagram, and FIG. 4 is a sectional view of a conventional refrigerator. In the figure: 101...Variable compression space, 102...Radiator, 103, 104...Regenerator, 107, 10
8...Variable expansion space, 109...Compression piston,
110, 111...expansion piston, 121...crankshaft.
Claims (1)
変膨張空間を互いに連通させる冷凍機において、
前記複数の可変膨張空間のうち温度の低い冷凍を
発生する可変膨張空間の容積に対し、高い温度の
冷凍を発生する可変膨張空間の容積の位相を遅ら
せたことを特徴とする冷凍機。1. In a refrigerator that communicates a variable compression space, a radiator, a regenerator, and a plurality of variable expansion spaces with each other,
A refrigerator characterized in that, among the plurality of variable expansion spaces, the phase of the volume of the variable expansion space that generates high-temperature refrigeration is delayed relative to the volume of the variable expansion space that generates low-temperature refrigeration.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13481385A JPS61291873A (en) | 1985-06-20 | 1985-06-20 | Refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13481385A JPS61291873A (en) | 1985-06-20 | 1985-06-20 | Refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61291873A JPS61291873A (en) | 1986-12-22 |
| JPH0350955B2 true JPH0350955B2 (en) | 1991-08-05 |
Family
ID=15137093
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13481385A Granted JPS61291873A (en) | 1985-06-20 | 1985-06-20 | Refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS61291873A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014006001A (en) * | 2012-06-25 | 2014-01-16 | Aisin Seiki Co Ltd | Gm refrigerator |
-
1985
- 1985-06-20 JP JP13481385A patent/JPS61291873A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014006001A (en) * | 2012-06-25 | 2014-01-16 | Aisin Seiki Co Ltd | Gm refrigerator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61291873A (en) | 1986-12-22 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |