JPH0549910B2 - - Google Patents
Info
- Publication number
- JPH0549910B2 JPH0549910B2 JP60224945A JP22494585A JPH0549910B2 JP H0549910 B2 JPH0549910 B2 JP H0549910B2 JP 60224945 A JP60224945 A JP 60224945A JP 22494585 A JP22494585 A JP 22494585A JP H0549910 B2 JPH0549910 B2 JP H0549910B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- port
- differential pressure
- valve body
- sliding guide
- 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 - Lifetime
Links
- 238000005192 partition Methods 0.000 claims description 23
- 238000004891 communication Methods 0.000 claims description 6
- 239000012530 fluid Substances 0.000 claims description 6
- 230000002441 reversible effect Effects 0.000 claims description 5
- 238000005057 refrigeration Methods 0.000 claims description 4
- 238000012856 packing Methods 0.000 description 11
- 239000003507 refrigerant Substances 0.000 description 5
- 230000008030 elimination Effects 0.000 description 3
- 238000003379 elimination reaction Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 2
- 239000000696 magnetic material Substances 0.000 description 2
- 239000004809 Teflon Substances 0.000 description 1
- 229920006362 Teflon® Polymers 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000002452 interceptive effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Landscapes
- Magnetically Actuated Valves (AREA)
- Temperature-Responsive Valves (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は冷暖兼用空調装置に用いられる可逆冷
凍サイクル用膨張弁に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to an expansion valve for a reversible refrigeration cycle used in a dual purpose air conditioner.
従来の膨張弁はいずれも、弁の開度を制御する
ことにより冷媒の流量を制御するようになつてい
るため、例えば冷蔵庫のように小容量の冷媒制御
を必要とし、レイノルズ数の小さな所での流体制
御を行わなければならないものにあつては、たと
え弁の位置を或所に保つていても流体の粘度変化
などによる流量が変化してしまい制御ができない
という問題がある。
Conventional expansion valves all control the flow rate of refrigerant by controlling the opening degree of the valve, so they require small capacity refrigerant control, such as in refrigerators, and are difficult to operate in places with small Reynolds numbers. For devices that require fluid control, there is a problem in that even if the valve is kept at a certain position, the flow rate changes due to changes in the viscosity of the fluid and cannot be controlled.
そこで、出願人においては、弁の開度により流
量を制御するのでなく、弁の開時間により流量を
制御するため、パルスによりオン・オフ動作する
電磁弁に一定の繰返周期のパルスを印加し、この
パルスの幅を変えて上記電磁弁のオン時間を変化
させるデユーテイサイクル制御により電磁弁を通
る流体の流量を制御する技術を開発している（特
開昭57−204381号）。 Therefore, in order to control the flow rate not by the opening degree of the valve but by the opening time of the valve, the applicant applies pulses with a constant repetition period to a solenoid valve that operates on and off by pulses. have developed a technology for controlling the flow rate of fluid through a solenoid valve by duty cycle control that changes the on-time of the solenoid valve by changing the width of this pulse (Japanese Patent Application Laid-open No. 204381/1983).
ところで、上記の流量制御技術を自動車用空調
装置等の可逆冷凍サイクルにおける膨張弁に採り
入れようとすると、冷媒の逆流時において高圧側
の圧力変動が弁の開閉力に影響を及ぼして正確な
制御が不可能となる。
By the way, if we try to apply the above flow rate control technology to the expansion valve in a reversible refrigeration cycle of an automobile air conditioner, etc., when the refrigerant flows back, pressure fluctuations on the high pressure side will affect the opening and closing force of the valve, making accurate control impossible. It becomes impossible.
本発明は上記した点に着目して為されたもので
あり、高圧の圧力変動が弁の開閉制御に及ぼす影
響を除去しつつ弁の開閉をデユーテイサイクルで
制御し得ることを可能とした可逆冷凍サイクル用
膨張弁を提供するものである。 The present invention has been made with attention to the above-mentioned points, and has made it possible to control the opening and closing of the valve in accordance with the duty cycle while eliminating the influence of high pressure fluctuations on the opening and closing control of the valve. An expansion valve for a reversible refrigeration cycle is provided.
本発明は上記した点に着目して為されたもので
あり、パルスによりオン・オフ動作する電磁弁に
一定の繰返周期のパルスを印加し、該パルスの幅
を変えて前記電磁弁のオン時間を変えることによ
り流体の流量を制御する膨張弁において、流通口
の一方において該流通口と弁室を区画する隔壁と
該流通口と他方の流通口を区画する隔壁とを相対
向して設けて一方の隔壁に弁口を形成すると共に
他方の隔壁に弁口径と同径の摺動案内孔を形成
し、電磁石の吸引子と該弁口との間で往復動する
筒状のプランジヤの端部において該弁口を開閉す
る弁体を軸方向に移動自在にして該弁体の一部を
該弁口方向へ突出させた状態で支持し、該吸引子
との間に設けた第１のスプリング１８により該弁
体を閉弁方向に付勢し、該摺動案内孔において該
弁口と略同径であつて一端が該他方の流通孔に臨
んでいる差圧消去用ロツドを摺動自在に支持する
と共に該差圧消去用ロツドを他端の細径部をもつ
て該弁体に連結し、該差圧消去用ロツドの周囲に
設けたシールパツキンを第２のスプリング８によ
り加圧して該シールパツキンの尖頭部により該摺
動案内孔を閉じ、前記他方の流通口と該弁室内に
通路を形成する構成を採用した。
The present invention has been made by focusing on the above-mentioned points, and it applies a pulse with a constant repetition period to a solenoid valve that is turned on and off by pulses, and changes the width of the pulse to turn on and off the solenoid valve. In an expansion valve that controls the flow rate of fluid by changing time, a partition wall that partitions the flow port and the valve chamber from one of the flow ports and a partition wall that partitions the flow port and the other flow port are provided facing each other. A valve port is formed in one partition wall, and a sliding guide hole having the same diameter as the valve port is formed in the other partition wall, and the end of a cylindrical plunger that reciprocates between the attractor of the electromagnet and the valve port. The valve element for opening and closing the valve opening is supported in a state in which it is movable in the axial direction and a part of the valve element projects toward the valve opening, and a first The valve body is urged in the valve closing direction by a spring 18, and a differential pressure eliminating rod, which has approximately the same diameter as the valve opening and has one end facing the other communication hole, is slid in the sliding guide hole. While freely supporting the differential pressure eliminating rod, the narrow diameter portion at the other end is connected to the valve body, and a seal packing provided around the differential pressure eliminating rod is pressurized by a second spring 8. The sliding guide hole is closed by the pointed head of the seal packing, and a passage is formed in the other communication port and the valve chamber.
第１図において、１は略Ｌ字状の膨張弁本体で
あり、流通口Ａと流通口Ｂが形成されている。流
通口Ａの内端部において、弁室Ｃとの間に弁口２
ａを有する隔壁２と流通口Ｂとの間に摺動案内孔
３ａを有する隔壁３が対抗して設けられる。弁口
２ａと摺動案内孔３ａは同径にして中心が一致す
るように配置され、弁室Ｃにおいてボール弁体４
が弁シート２ｂに接離する。摺動案内孔３ａには
弁口２ａと略同径に形成された差圧消去用ロツド
５が摺動自在に支持され、該差圧消去用ロツド５
は細径部５ａをもつて弁口２ａからボール弁体４
に溶接手段により固着され、差圧消去用ロツド５
の他端は流通口Ｂに臨んでいる。
In FIG. 1, reference numeral 1 denotes a substantially L-shaped expansion valve body, in which a flow port A and a flow port B are formed. At the inner end of the flow port A, there is a valve port 2 between the valve chamber C and the valve chamber C.
A partition wall 3 having a sliding guide hole 3a is provided oppositely between the partition wall 2 having a diameter of 1.a and the flow port B. The valve port 2a and the sliding guide hole 3a have the same diameter and are arranged so that their centers coincide.
comes into contact with and separates from the valve seat 2b. A differential pressure eliminating rod 5 formed to have approximately the same diameter as the valve port 2a is slidably supported in the sliding guide hole 3a.
has a narrow diameter portion 5a and extends from the valve port 2a to the ball valve body 4.
is fixed by welding means to the differential pressure eliminating rod 5.
The other end faces distribution port B.
隔壁３内において摺動案内孔３ａにはテーパー
状部３ｂを介して大径のパツキン収容孔３ｃが形
成され、該パツキン収容孔３ｃ内において差圧消
去用ロツド５の周囲には孔６ａを介してテフロン
等の硬質合成樹脂製のシールパツキン６が嵌合さ
れ、該シールパツキン６は流通口Ｂに設けた受金
７との間に架設したスプリング８により摺動案内
孔３ａに対して加圧される。シールパツキン６は
尖頭部６ｂを有し、加圧により該尖頭部６ｂがテ
ーパー状部３ｂの作用を受けて差圧消去用ロツド
５の周囲に圧接し、従つてシールパツキン６は小
範囲の部分において差圧消去用ロツド５に圧接し
て、該差圧消去用ロツド５の円滑な移動を阻害し
ないで摺動案内孔３ａをシールする。 In the partition wall 3, a large-diameter packing receiving hole 3c is formed in the sliding guide hole 3a through a tapered portion 3b, and a hole 6a is formed around the differential pressure eliminating rod 5 in the packing receiving hole 3c. A seal packing 6 made of a hard synthetic resin such as Teflon is fitted, and the seal packing 6 is pressurized against the sliding guide hole 3a by a spring 8 installed between it and a receiver 7 provided in the flow port B. be done. The seal packing 6 has a pointed head 6b, and when pressurized, the pointed head 6b is brought into pressure contact with the periphery of the differential pressure eliminating rod 5 under the action of the tapered part 3b, so that the seal packing 6 is pressed against the periphery of the differential pressure elimination rod 5. It comes into pressure contact with the differential pressure eliminating rod 5 at this portion to seal the sliding guide hole 3a without interfering with the smooth movement of the differential pressure eliminating rod 5.
弁本体１において、流通口Ｂと弁室Ｃ間には通
孔９が形成されている。 In the valve body 1, a through hole 9 is formed between the flow port B and the valve chamber C.
弁室Ｃにはプランジヤチユーブ１０が立設さ
れ、その上端には電磁石Ｄの吸引子１１が固定さ
れる。吸引子１１には磁性材料によりコ字状に形
成された外函１２がボルト１３により固着され、
この外函１２の対向片間には鍔付中空ボビン１４
に巻設された電磁コイル１５が挾持されている。 A plunger tube 10 is erected in the valve chamber C, and an attractor 11 of an electromagnet D is fixed to the upper end of the plunger tube 10. A U-shaped outer case 12 made of magnetic material is fixed to the attractor 11 with bolts 13.
Between the opposing pieces of this outer case 12 is a flanged hollow bobbin 14.
An electromagnetic coil 15 wound around is clamped.
プランジヤチユーブ１０内には磁性材料からな
る管状のプランジヤ１６が摺動可能に収められて
おり、この弁口２ａに対向した端部において下方
に向けて狭小した支持孔１６ａが形成され、該支
持孔１６ａにおいて前記ボール弁体４はプランジ
ヤ１６の内方へは移動可能にして一部外方へ突出
した状態で支持される。プランジヤ１６にはばね
受け１７が移動自在に設けられ、該ばね受け１７
は吸引子１１との間に設けた圧縮スプリング１８
によりボール弁体４をプランジヤ１６の支持孔１
６ａから弁口２ａ方向へ突出するように付勢す
る。 A tubular plunger 16 made of a magnetic material is slidably housed in the plunger tube 10, and a support hole 16a narrowing downward is formed at the end opposite the valve port 2a. At 16a, the ball valve body 4 is supported in a state in which it is movable inwardly of the plunger 16 and partially protrudes outward. A spring receiver 17 is movably provided on the plunger 16.
is the compression spring 18 provided between the suction element 11
The ball valve body 4 is inserted into the support hole 1 of the plunger 16.
6a to project toward the valve port 2a.
なお、１９は電磁コイル１５にパルス電流を供
給するためのリード線である。 Note that 19 is a lead wire for supplying a pulse current to the electromagnetic coil 15.
上記構成において、冷房運転時には冷媒は流通
口Ａから弁口２ａ、弁室Ｃ、通孔９を通つて流通
口Ｂに流れ、暖房運転時においては逆に流通口Ｂ
から流通口Ａに流れる。この際に、リード線１９
にパルス電流が流されて電磁コイル１５が励磁さ
れることにより、プランジヤ１６が吸引子１１に
より吸引されてボール弁体４を弁シート２ｂより
引き離す。 In the above configuration, during the cooling operation, the refrigerant flows from the circulation port A to the circulation port B through the valve port 2a, the valve chamber C, and the through hole 9, and vice versa during the heating operation.
It flows from the flow port A to the flow port A. At this time, the lead wire 19
When a pulse current is passed through and the electromagnetic coil 15 is excited, the plunger 16 is attracted by the attractor 11 and the ball valve body 4 is separated from the valve seat 2b.
第３図に示される如くに、弁口２ａと摺動案内
孔３ａを同径としてその面積をＳとし、流通口Ｂ
の圧力をP1、流通口Ａの圧力をP2とすると、互
いに固着され一体化されたボール弁体４及び差圧
消去用ロツド５に働く力は、同図の上向きの力
F1＝（P2×Ｓ）＋（P1×Ｓ）、下向きの力F2＝（P1×
Ｓ）＋（P2×Ｓ）となり、従つてF1＝F2であるの
で、ボール弁体４に加わる力は上下において消去
されて働かないものであり、圧力が変動してもこ
の関係は変ることなく、ボール弁体４の動作は圧
力変動の影響を受けない。ボール弁体４に加えら
れる力は、第１スプリング１８による下向きの押
圧力のみである。 As shown in FIG. 3, the valve port 2a and the sliding guide hole 3a have the same diameter, and their area is S, and the flow port B
Assuming that the pressure at the flow port A is P 1 and the pressure at the flow port A is P 2 , the force acting on the ball valve body 4 and the differential pressure eliminating rod 5, which are fixed to each other and integrated, is the upward force shown in the figure.
F 1 = (P 2 × S) + (P 1 × S), downward force F 2 = (P 1 ×
S) + (P 2 × S), and therefore F 1 = F 2 , the force applied to the ball valve body 4 is canceled in the upper and lower directions and does not work, and even if the pressure fluctuates, this relationship remains Without change, the operation of the ball valve body 4 is not affected by pressure fluctuations. The only force applied to the ball valve body 4 is the downward pressing force by the first spring 18.
上述した構成の電磁弁の動作を第２図ａ乃至ｃ
を参照して説明する。 The operation of the solenoid valve configured as described above is shown in Figures 2a to 2c.
Explain with reference to.
第２図ａは弁閉の状態を示し、プランジヤ１６
は自重により隔壁２に当節し、ボール弁体４は圧
縮スプリング１８の作用により弁シート２ｂに圧
接している。この状態で電磁コイル１５に通電す
ると、プランジヤ１６が吸引子１１により吸引さ
れるが、第２図ｂに至るl1の間プランジヤ１６に
弁開のための負荷がかからないため、距離l1は弁
開の力を増すための衝撃間隔として作用する。 FIG. 2a shows the valve closed state, and the plunger 16
is pressed against the partition wall 2 by its own weight, and the ball valve body 4 is pressed against the valve seat 2b by the action of the compression spring 18. When the electromagnetic coil 15 is energized in this state, the plunger 16 is attracted by the attractor 11, but since no load is applied to the plunger 16 during l 1 leading to FIG . It acts as a shock interval to increase the opening force.
その後プランジヤ１６はボール弁体４を支持し
て第２図ｃに示される距離l2迄移動し、全開状態
となる。 Thereafter, the plunger 16 supports the ball valve body 4 and moves to a distance l2 shown in FIG. 2c, and becomes fully open.
本発明は上記した如くに、パルスによりオン・
オフ動作する電磁弁に一定の繰返周期のパルスを
印加し、該パルスの幅を変えて前記電磁弁のオン
時間を変えることにより流体の流量を制御する膨
張弁において、流通口の一方において該流通口と
弁室を区画する隔壁と該流通口と他方の流通口を
区画する隔壁とを相対向して設けて一方の隔壁に
弁口を形成すると共に他方の隔壁に弁口径と同径
の摺動案内孔を形成し、電磁石の吸引子と該弁口
との間で往復動する筒状のプランジヤの端部にお
いて該弁口を開閉する弁体を軸方向に移動自在に
して該弁体の一部を該弁口方向へ突出させた状態
で支持し、該吸引子との間に設けた第１のスプリ
ング１８により該弁体を閉弁方向に付勢し、該摺
動案内孔において該弁口と略同径であつて一端が
該他方の流通孔に臨んでいる差圧消去用ロツドを
摺動自在に支持すると共に該差圧消去用ロツドを
他端の細径部をもつて該弁体に連結し、該差圧消
去用ロツドの周囲に設けたシールパツキンを第２
のスプリング８により加圧して該シールパツキン
の尖頭部により該摺動案内孔を閉じ、前記他方の
流通口と該弁室内に通路を形成して成るものであ
るから、弁体に連結した差圧消去用ロツドがボー
ル弁体に加わる流通口の一方の圧力と他方の流通
口の圧力を消去することにより高圧変動が弁の開
閉に影響するのを防いで可逆双方の流通時におい
て正確な制御が為し得られ、この際にシールパツ
キンにより該消去ロツドの周囲における冷媒の漏
れを阻止することができ、ボール弁体をプランジ
ヤに固定しないでプランジヤとの間に衝撃間隔を
設けているので、弁開力を大きくすることができ
る特長を有する。 As described above, the present invention turns on and off by a pulse.
In an expansion valve that controls the flow rate of fluid by applying a pulse with a constant repetition period to a solenoid valve that is turned off and changing the width of the pulse to change the on time of the solenoid valve, one of the flow ports A partition wall that partitions a flow port and a valve chamber, and a partition wall that partitions the flow port and the other flow port are provided facing each other to form a valve port in one partition wall, and a valve port having the same diameter as the valve port diameter in the other partition wall. A sliding guide hole is formed, and a valve element for opening and closing the valve opening is movable in the axial direction at the end of a cylindrical plunger that reciprocates between the attractor of the electromagnet and the valve opening. A first spring 18 provided between the suction element and the suction element urges the valve body in the valve closing direction, and the valve element is supported in a state in which a part of the valve element is protruded toward the valve opening. A differential pressure eliminating rod having approximately the same diameter as the valve port and having one end facing the other communication hole is slidably supported, and the differential pressure eliminating rod is held with a narrow diameter portion at the other end. A second sealing gasket connected to the valve body and provided around the differential pressure eliminating rod is connected to the valve body.
The sliding guide hole is closed by the spring 8 of the seal packing, and a passage is formed between the other communication port and the valve chamber. The pressure elimination rod eliminates the pressure applied to the ball valve body from one side of the flow port and the pressure from the other flow port, thereby preventing high pressure fluctuations from affecting the opening and closing of the valve, allowing for accurate control during reversible flow. At this time, the seal packing can prevent the refrigerant from leaking around the erasing rod, and since the ball valve body is not fixed to the plunger and an impact gap is provided between it and the plunger, It has the feature of increasing the valve opening force.
第１図は本発明の一実施例についての断面図、
第２図ａ，ｂ，ｃは動作を説明するための断面
図、第３図は差圧消去用ロツドの作用を示す説明
図である。
Ａ，Ｂ……流通口、Ｃ……弁室、Ｄ……電磁
石、２，３……相対向する隔壁、２ａ……弁口、
３ａ……摺動案内孔、４……弁体、５……差圧消
去用ロツド、６……シールパツキン、８……スプ
リング、９……通孔、１０……筒状のプランジ
ヤ。
FIG. 1 is a sectional view of an embodiment of the present invention;
FIGS. 2a, b, and c are sectional views for explaining the operation, and FIG. 3 is an explanatory view showing the action of the differential pressure eliminating rod. A, B...flow port, C...valve chamber, D...electromagnet, 2, 3...opposed partition wall, 2a...valve port,
3a...Sliding guide hole, 4...Valve body, 5...Differential pressure elimination rod, 6...Seal packing, 8...Spring, 9...Through hole, 10...Cylindrical plunger.
Claims (1)
定の繰返周期のパルスを印加し、該パルスの幅を
変えて前記電磁弁のオン時間を変えることにより
流体の流量を制御する膨張弁において、流通口の
一方において該流通口と弁室を区画する隔壁と該
流通口と他方の流通口を区画する隔壁とを相対向
して設けて一方の隔壁に弁口を形成すると共に他
方の隔壁に弁口径と同径の摺動案内孔を形成し、
電磁石の吸引子と該弁口との間で往復動する筒状
のプランジヤの端部において該弁口を開閉する弁
体を軸方向に移動自在にして該弁体の一部を該弁
口方向へ突出させた状態で支持し、該吸引子との
間に設けた第１のスプリング１８により該弁体を
閉弁方向に付勢し、該摺動案内孔において該弁口
と略同径であつて一端が該他方の流通孔に臨んで
いる差圧消去用ロツドを摺動自在に支持すると共
に該差圧消去用ロツドを他端の細径部をもつて該
弁体に連結し、該差圧消去用ロツドの周囲に設け
たシールパツキンを第２のスプリング８により加
圧して該シールパツキンの尖頭部により該摺動案
内孔を閉じ、前記他方の流通口と該弁室内に通路
を形成して成ることを特徴とする可逆冷凍サイク
ル用膨張弁。1. In an expansion valve that controls the flow rate of fluid by applying a pulse with a constant repetition period to a solenoid valve that operates on and off by pulses, and changing the width of the pulse and changing the on time of the solenoid valve, A partition that partitions the flow port and the valve chamber on one side of the port and a partition wall that partitions the flow port and the other flow port are provided facing each other to form a valve port in one partition and a valve in the other partition. A sliding guide hole with the same diameter as the bore is formed,
At the end of a cylindrical plunger that reciprocates between an electromagnetic attractor and the valve port, a valve body that opens and closes the valve port is movable in the axial direction, and a part of the valve body is moved in the direction of the valve port. A first spring 18 provided between the suction element and the suction element urges the valve body in the valve closing direction, and a valve element with approximately the same diameter as the valve opening is installed in the sliding guide hole. A differential pressure eliminating rod with one end facing the other communication hole is slidably supported, and the differential pressure eliminating rod is connected to the valve body with a narrow diameter portion at the other end, A seal gasket provided around the differential pressure eliminating rod is pressurized by the second spring 8, and the pointed head of the seal gasket closes the sliding guide hole, creating a passage between the other communication port and the valve chamber. An expansion valve for a reversible refrigeration cycle, characterized by comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60224945A JPS6287775A (en) | 1985-10-11 | 1985-10-11 | Expansion valve for reversible refrigeration cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60224945A JPS6287775A (en) | 1985-10-11 | 1985-10-11 | Expansion valve for reversible refrigeration cycle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6287775A JPS6287775A (en) | 1987-04-22 |
| JPH0549910B2 true JPH0549910B2 (en) | 1993-07-27 |
Family
ID=16821653
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60224945A Granted JPS6287775A (en) | 1985-10-11 | 1985-10-11 | Expansion valve for reversible refrigeration cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6287775A (en) |
-
1985
- 1985-10-11 JP JP60224945A patent/JPS6287775A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6287775A (en) | 1987-04-22 |
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