JP2538505Y2 - Pump structure - Google Patents
Pump structureInfo
- Publication number
- JP2538505Y2 JP2538505Y2 JP1990099236U JP9923690U JP2538505Y2 JP 2538505 Y2 JP2538505 Y2 JP 2538505Y2 JP 1990099236 U JP1990099236 U JP 1990099236U JP 9923690 U JP9923690 U JP 9923690U JP 2538505 Y2 JP2538505 Y2 JP 2538505Y2
- Authority
- JP
- Japan
- Prior art keywords
- housing
- pump
- annular
- cover member
- rotor
- 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
Landscapes
- Rotary Pumps (AREA)
Description
【考案の詳細な説明】 〔産業上の利用分野〕 本考案は、ハウジング及びカバー部材が軽合金で構成
されたポンプ構造に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a pump structure in which a housing and a cover member are made of a light alloy.
一般に、作動油や潤滑油などを圧送するためのポンプ
として、内接式の歯車ポンプやトロコイドポンプが広く
採用されている。Generally, an internal gear pump or a trochoid pump is widely used as a pump for pumping hydraulic oil, lubricating oil, and the like.
上記内接式のポンプは、ロータを収容する為の収容部
を有するハウジングと、ハウジングに締結されたカバー
部材と、収容部内に回転自在に収容された外部ロータ
と、外部ロータ内に偏心状に装着された内部ロータとを
備え、例えばトロコイドポンプは、実開昭61−171885号
公報に記載されているように、内部ロータの歯数を外部
ロータよりも１枚少なく構成し、内部ロータの歯先を外
部ロータの歯面に常に滑り接触させつつ内部ロータを回
転駆動することにより吸入と吐出を行うようになってい
る。The inscribed pump includes a housing having an accommodating portion for accommodating the rotor, a cover member fastened to the housing, an external rotor rotatably accommodated in the accommodating portion, and an eccentric shape in the external rotor. For example, the trochoid pump is provided with an inner rotor mounted thereon, and as described in Japanese Utility Model Laid-Open Publication No. 61-171885, the number of teeth of the inner rotor is made one less than that of the outer rotor. The suction and discharge are performed by rotating the internal rotor while always keeping the tip in sliding contact with the tooth surface of the external rotor.
通常、上記ポンプのハウジングとカバー部材と両ロー
タとは鉄系金属で構成されているが、近年の軽量化のニ
ーズによりカバー部材をアルミニウム合金で構成したも
のも実用化されている。Normally, the housing, cover member, and both rotors of the pump are made of an iron-based metal. However, in recent years, a cover member made of an aluminum alloy has been put into practical use due to the need for weight reduction.
ところで、上記ポンプを更に軽量化するため、ハウジ
ングもアルミニウム合金などの軽合金で構成した場合、
ハウジングの熱膨張率が外部ロータの熱膨張率よりも大
きくなるので、高温作動時にハウジングの内周面と外部
ロータの外周面間のクリアランスが大きくなってポンプ
機械効率が低下し、吐出量が減少するという問題が発生
する。By the way, in order to further reduce the weight of the pump, when the housing is also made of a light alloy such as an aluminum alloy,
Since the coefficient of thermal expansion of the housing is greater than the coefficient of thermal expansion of the external rotor, the clearance between the inner peripheral surface of the housing and the outer peripheral surface of the external rotor increases during high-temperature operation, reducing pump machine efficiency and reducing discharge. Problem arises.
本考案の目的は、ポンプを軽量に構成し且つ高温作動
時におけるポンプ機械効率の低下を防止し得るポンプ構
造を提供することである。SUMMARY OF THE INVENTION It is an object of the present invention to provide a pump structure that can reduce the weight of a pump and prevent a decrease in pump mechanical efficiency during high-temperature operation.
請求項１のポンプ構造は、ハウジングと、このハウジ
ングにその一側面側から凹設された凹部と、この凹部内
に収容されたロータと、ハウジングの上記一側面に固定
されて凹部を塞ぐカバー部材とを備え、ロータを回転さ
せることにより流体圧を発生させるポンプにおいて、上
記ハウジング及びカバー部材が軽合金で構成されるとと
もに、ロータは鉄系金属で構成され、上記ロータの外周
面に対向するハウジングの環状の内周壁部の半径方向外
側にはカバー部材側へ開口し且つ凹部と略同深さの環状
溝がハウジングの上記一側面側から凹設され、上記環状
溝内には内周壁部の半径方向への熱膨張を抑制する環状
部材が装着されていることを特徴とするものである。The pump structure according to claim 1, wherein the housing, a recess formed in the housing from one side thereof, a rotor housed in the recess, and a cover member fixed to the one side of the housing to cover the recess. Wherein the housing and the cover member are made of a light alloy, the rotor is made of an iron-based metal, and the housing faces the outer peripheral surface of the rotor. An annular groove which is open to the cover member side and has substantially the same depth as the concave portion is recessed from the one side surface of the housing on the radially outer side of the annular inner peripheral wall portion. An annular member for suppressing thermal expansion in the radial direction is mounted.
請求項２のポンプ構造は、請求項１の考案において、
上記環状溝の奥端面と環状溝に対向するカバー部材の端
面との少なくとも一方と環状部材の端面間に環状隙間が
形成されていることを特徴とするものである。The pump structure according to claim 2 is the pump structure according to claim 1,
An annular gap is formed between at least one of the inner end surface of the annular groove and the end surface of the cover member facing the annular groove and the end surface of the annular member.
請求項１に係るポンプ構造においては、ハウジング及
びカバー部材が軽合金で構成されているので、ポンプを
大幅に軽量に構成出来る。一方、ロータはハウジング及
びカバー部材よりも熱膨張率の小さい鉄系金属で構成さ
れているので、高温作動時にはハウジングの内周壁部が
ロータの外周壁部よりも半径方向に大きく熱膨張し、ハ
ウジングの内周面とロータの外周面間のクリアランスが
大きくなろうとするが、環状溝に装着された環状部材に
より内周壁部の半径方向への熱膨張が抑制されるので、
高温作動時におけるポンプ機械効率の低下を効果的に防
止して吐出量の減少を防止出来る。In the pump structure according to the first aspect, since the housing and the cover member are made of a light alloy, the pump can be made significantly lighter. On the other hand, since the rotor is made of an iron-based metal having a lower coefficient of thermal expansion than the housing and the cover member, the inner peripheral wall of the housing expands more in the radial direction than the outer peripheral wall of the rotor during high-temperature operation, and Although the clearance between the inner peripheral surface of the rotor and the outer peripheral surface of the rotor tends to increase, thermal expansion in the radial direction of the inner peripheral wall portion is suppressed by the annular member attached to the annular groove.
It is possible to effectively prevent a decrease in pump mechanical efficiency at the time of high-temperature operation and prevent a decrease in the discharge amount.
請求項２に係るポンプ構造においては、請求項１に記
載のポンプ構造と同様の効果が得られる。加えて、環状
溝の奥端面と環状溝に対向するカバー部材の端面との少
なくとも一方と環状部材の端面間に環状隙間が形成され
ているので、ハウジング及びカバー部材が半径方向に熱
膨張しても、環状部材とハウジング及びカバー部材との
端面同士の接触による環状部材の半径方向への拡大を防
止出来、高温作動時におけるポンプ機械効率の低下を更
に効果的に防止して吐出量の減少を防止出来る。In the pump structure according to the second aspect, the same effect as the pump structure according to the first aspect is obtained. In addition, since the annular gap is formed between at least one of the inner end surface of the annular groove and the end surface of the cover member facing the annular groove and the end surface of the annular member, the housing and the cover member thermally expand in the radial direction. Also, it is possible to prevent the annular member from expanding in the radial direction due to the contact between the end surfaces of the annular member, the housing, and the cover member, and to more effectively prevent a decrease in pump mechanical efficiency at the time of high-temperature operation, thereby reducing a discharge amount. Can be prevented.
請求項１のポンプ構造によれば、上記のように、軽合
金製のハウジングの内周壁部の半径方向外側に、カバー
部材側へ開口し且つロータを収容する凹部と略同深さの
環状溝を形成し、この環状溝内に内周壁部の半径方向へ
の熱膨張を抑制する環状部材を装着したので、この環状
部材により高温作動時における内周壁部の半径方向への
熱膨張を抑制して、ハウジングの凹部の内周面とロータ
間のクリアランスが拡大するのを確実に抑制することが
できるから、ポンプ機械効率の低下を効果的に防止して
吐出量の減少を防止できる。According to the pump structure of the first aspect, as described above, the annular groove which is opened to the cover member side and has substantially the same depth as the concave portion which accommodates the rotor is provided radially outside the inner peripheral wall portion of the light alloy housing. Is formed, and an annular member for suppressing the thermal expansion of the inner peripheral wall in the radial direction is mounted in the annular groove, so that the annular member suppresses the thermal expansion of the inner peripheral wall in the radial direction during high-temperature operation. As a result, it is possible to reliably prevent the clearance between the inner peripheral surface of the recess of the housing and the rotor from increasing, so that it is possible to effectively prevent a decrease in pump mechanical efficiency and a discharge amount.
しかも、環状の内周壁部が熱膨張する際の熱膨張力は
さほど強力ではないから、比較的小型の環状部材により
環状の内周壁部の熱膨張を抑制できる。つまり、環状溝
や環状部材を小型化でき、ポンプ構造が殆ど大型化する
こともない。In addition, since the thermal expansion force when the annular inner peripheral wall is thermally expanded is not so strong, the thermal expansion of the annular inner peripheral wall can be suppressed by a relatively small annular member. That is, the annular groove and the annular member can be reduced in size, and the pump structure does not almost increase in size.
請求項２のポンプ構造においては、請求項１の考案と
同様の効果を奏する。加えて、環状隙間を設けることに
より環状部材とハウジング及びカバー部材との端面同士
の接触による環状部材の半径方向への拡大を防止出来る
ので、高温作動時におけるポンプ機械効率の低下を更に
効果的に防止出来る。According to the pump structure of the second aspect, the same effect as the invention of the first aspect is obtained. In addition, by providing the annular gap, it is possible to prevent the annular member from expanding in the radial direction due to the contact between the end surfaces of the annular member, the housing, and the cover member. Can be prevented.
以下、本考案の実施例を図面に基いて説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
本実施例は、FF車用の自動変速機に設けられた内接歯
車式のオイルポンプに本考案を適用した場合のものであ
る。In this embodiment, the present invention is applied to an internal gear type oil pump provided in an automatic transmission for a front-wheel drive vehicle.
第１図に示すように、自動変速機１の左端部にはオイ
ルポンプ２が設けられ、このオイルポンプ２によりトル
クコンバータ（図示略）への送油、パワートレーン系の
潤滑、油圧制御系への作動圧の確保が行われる。As shown in FIG. 1, an oil pump 2 is provided at a left end portion of the automatic transmission 1. The oil pump 2 supplies oil to a torque converter (not shown), lubrication of a power train system, and a hydraulic control system. Is ensured.
上記オイルポンプ２について説明すると、第１図〜第
４図に示すように、自動変速機１のケーシング３の左端
部にはハウジング４が固着され、ハウジング４の右端面
にはカバー部材５がハウジング４及びカバー部材５を貫
通するボルト６で締結され、ハウジング４内にはカバー
部材５側に開口する収容部７が形成されている。The oil pump 2 will be described. As shown in FIGS. 1 to 4, a housing 4 is fixed to a left end portion of a casing 3 of the automatic transmission 1, and a cover member 5 is provided on a right end surface of the housing 4. The housing 4 is fastened by bolts 6 penetrating through the cover member 5, and a housing 7 is formed in the housing 4 and opens toward the cover member 5.
上記収容部７内には略環状の内歯歯車８がハウジング
４の内周壁部4aに僅かなクリアランス９をあけて回転自
在に装着され、内歯歯車８の内側には下半部が内歯歯車
８に噛合する外歯歯車10が内歯歯車８と偏心状に配設さ
れ、外歯歯車10は収容部７内に延びる自動変速機１のタ
ービン軸11の左端部に連結部材12を介して連結され、内
歯歯車８及び外歯歯車10の右端面とカバー部材５の左端
面間に僅かなクリアランス13が形成され、ハウジング４
には内歯歯車８と外歯歯車10間へ延びる三日月状の仕切
部4bが突出状に形成され、仕切部4bの左端面はカバー部
材５の右端面に略油密状に当接されている。A substantially annular internal gear 8 is rotatably mounted in the housing 7 with a slight clearance 9 provided on an inner peripheral wall 4 a of the housing 4, and a lower half inside the internal gear 8 has internal teeth. An external gear 10 meshing with the gear 8 is disposed eccentrically with the internal gear 8, and the external gear 10 is connected via a connecting member 12 to a left end of a turbine shaft 11 of the automatic transmission 1 extending into the housing 7. And a slight clearance 13 is formed between the right end face of the internal gear 8 and the external gear 10 and the left end face of the cover member 5.
A crescent-shaped partition portion 4b extending between the internal gear 8 and the external gear 10 is formed in a protruding shape, and the left end surface of the partition portion 4b is brought into substantially oil-tight contact with the right end surface of the cover member 5. I have.
上記ハウジング４の左壁部には内歯歯車８と外歯歯車
10との噛合開始部位14付近と噛合終了部位15付近に開口
する吐出通路16と吸入通路17が夫々形成され、第３図に
示すように、タービン軸11が矢印の方向に回転駆動され
ると、吸入通路17からオイルポンプ２内に作動油が流入
し、オイルポンプ２から吐出通路16へ加圧された作動油
が排出される。An internal gear 8 and an external gear are provided on the left wall of the housing 4.
A discharge passage 16 and a suction passage 17 are formed in the vicinity of the meshing start portion 14 and the meshing end portion 15 with the turbine 10, respectively, and when the turbine shaft 11 is driven to rotate in the direction of the arrow as shown in FIG. The hydraulic oil flows into the oil pump 2 from the suction passage 17, and the pressurized hydraulic oil is discharged from the oil pump 2 to the discharge passage 16.
上記オイルポンプ２を軽量に構成するため、内歯歯車
８及び外歯歯車10は熱膨張率が12〜14×10degの鉄系焼
結合金で構成されているが、ハウジング４及びカバー部
材５は熱膨張率が19×10degのアルミニウム合金で構成
されている。In order to make the oil pump 2 lightweight, the internal gear 8 and the external gear 10 are made of an iron-based sintered alloy having a coefficient of thermal expansion of 12 to 14 × 10 deg. It is composed of an aluminum alloy having a coefficient of thermal expansion of 19 × 10 deg.
上記内歯歯車８とハウジング４との熱膨張率の差によ
り、オイルポンプ２の高温作動時においてクリアランス
９が大きくならないようにするため、ハウジング４の内
周壁部4aの外側にはカバー部材５側に開口する環状溝18
が形成され、環状溝18は収容部７と略同じ深さに形成さ
れ、環状溝18内には内周壁部4aの半径方向への熱膨張を
抑制する環状部材19が圧入状に装着され、環状部材19は
その熱膨張率が内歯歯車８と略同じ12〜14×10degの鋼
で構成され、環状部材19はその左右両端面と環状溝18の
奥端面及び環状溝18に対向するカバー部材５の左端面間
に環状隙間20が夫々形成されるように装着されている。Due to the difference in the coefficient of thermal expansion between the internal gear 8 and the housing 4, the clearance 9 does not increase when the oil pump 2 is operated at a high temperature. Annular groove 18 opening in
Is formed, the annular groove 18 is formed at substantially the same depth as the housing portion 7, and an annular member 19 that suppresses thermal expansion of the inner peripheral wall portion 4a in the radial direction is mounted in the annular groove 18 in a press-fit manner. The annular member 19 is made of steel having a coefficient of thermal expansion of 12 to 14 × 10 deg, which is substantially the same as that of the internal gear 8. The annular member 19 has a cover facing the left and right end surfaces, the inner end surface of the annular groove 18 and the annular groove 18. The members 5 are mounted such that annular gaps 20 are formed between the left end surfaces thereof.
次に、上記オイルポンプ２の作用について説明する。 Next, the operation of the oil pump 2 will be described.
ハウジング４及びカバー部材５がアルミニウム合金で
構成されているので、オイルポンプ２を大幅に軽量に構
成出来る。Since the housing 4 and the cover member 5 are made of an aluminum alloy, the oil pump 2 can be made significantly lighter.
一方、上記のようにハウジング４をアルミニウム合金
で構成した場合、内歯歯車８の熱膨張率がハウジング４
との熱膨張率よりも小さくなるので、トルクコンバータ
内における摩擦熱やエンジンからの伝熱による作動油の
温度上昇によりオイルポンプ２の温度が高くなると、内
歯歯車８の外周面と内周壁部4a間のクリアランス９が大
きくなろうとするが、内周壁部4aの外側の環状溝18内に
内歯歯車８と略同じ熱膨張率の環状部材19が圧入状に装
着されているので、内周壁部4aの半径方向への大幅な熱
膨張が抑制されてクリアランス９が正規の値に保持さ
れ、高温作動時におけるポンプ機械効率の低下が防止さ
れて吐出量の減少が防止される。しかも、環状部材19の
左右両端面と環状溝18の奥端面及び環状溝18に対向する
カバー部材５の端面間に環状隙間20が形成されているの
で、ハウジング４及カバー部材４が半径方向に熱膨張し
ても、環状部材19とハウジング４及カバー部材４との端
面同士の接触による環状部材19の半径方向への拡大が防
止され、高温作動時におけるポンプ機械効率の低下が更
に効果的に防止される。On the other hand, when the housing 4 is made of an aluminum alloy as described above, the coefficient of thermal expansion of the
When the temperature of the oil pump 2 rises due to a rise in the temperature of the hydraulic oil due to frictional heat in the torque converter and heat transfer from the engine, the outer peripheral surface and the inner peripheral wall of the internal gear 8 are reduced. Although the clearance 9 between the inner peripheral gears 4a tends to increase, the annular member 19 having the same thermal expansion coefficient as the internal gear 8 is press-fitted in the annular groove 18 outside the inner peripheral wall 4a. Significant thermal expansion of the portion 4a in the radial direction is suppressed, the clearance 9 is maintained at a regular value, and a decrease in pump mechanical efficiency at the time of high-temperature operation is prevented, and a decrease in the discharge amount is prevented. In addition, since the annular gap 20 is formed between the left and right end surfaces of the annular member 19, the rear end surface of the annular groove 18 and the end surface of the cover member 5 facing the annular groove 18, the housing 4 and the cover member 4 can be moved in the radial direction. Even if it is thermally expanded, the radial expansion of the annular member 19 due to the contact between the end faces of the annular member 19 and the housing 4 and the cover member 4 is prevented, and the pump mechanical efficiency at the time of high-temperature operation is more effectively reduced. Is prevented.
更に、ハウジング４とカバー部材５とが両者を貫通す
るボルト６で締結されているので、ボルト６の熱膨張率
を内歯歯車８と略同じにすることにより、ハウジング４
及びカバー部材５の左右方向への熱膨張によるクリアラ
ンス13の拡大を防止出来、高温作動時におてもクリアラ
ンス13を正規の値に保持してポンプ機械効率の低下を防
止出来る。Further, since the housing 4 and the cover member 5 are fastened by the bolts 6 penetrating both, the thermal expansion coefficient of the bolts 6 is made substantially the same as that of the internal gear 8 so that the housing 4
Further, the expansion of the clearance 13 due to the thermal expansion of the cover member 5 in the left-right direction can be prevented, and the clearance 13 can be maintained at a regular value even at the time of high-temperature operation, so that the efficiency of the pump can be prevented from lowering.
以上のように、ハウジング４及びカバー部材５をアル
ミニウム合金で構成してオイルポンプ２を大幅に軽量に
構成出来、且つ比較的簡単な構成で高温作動時における
クリアランス９・13の拡大を防止してポンプ機械効率の
低下を効果的に防止出来る。As described above, the oil pump 2 can be made significantly lighter by forming the housing 4 and the cover member 5 from an aluminum alloy, and the expansion of the clearances 9 and 13 during high-temperature operation can be prevented with a relatively simple structure. A decrease in pump machine efficiency can be effectively prevented.
尚、ハウジング４及びカバー部材５はアルミニウム合
金以外の軽合金で構成してもよい。また、歯車８・10は
鋳鉄や鋼などの鉄系金属で構成してもよい。The housing 4 and the cover member 5 may be made of a light alloy other than the aluminum alloy. Further, the gears 8 and 10 may be made of an iron-based metal such as cast iron or steel.
尚、本実施例では、自動変速機１の内接歯車式のオイ
ルポンプ２に本考案を適用したが、自動変速機１以外の
機器に用いられるポンプに対しても適用出来るし、内接
式のトロコイドポンプなどその他の形式のポンプに対し
ても同様に適用することが出来る。In the present embodiment, the present invention is applied to the internal gear type oil pump 2 of the automatic transmission 1, but the present invention can be applied to a pump used for equipment other than the automatic transmission 1. The same can be applied to other types of pumps such as the trochoid pump.
図面は本考案の実施例を示すもので、第１図は自動変速
機の要部切欠き正面図、第２図はオイルポンプの分解斜
視図、第３図はカバー部材を取り除いた状態におけるオ
イルポンプの側面図、第４図はオイルポンプの縦断面図
である。 ２……オイルポンプ、４……ハウジング、4a……内周壁
部、５……カバー部材、８……内歯歯車、10……外歯歯
車、18……環状溝、19……環状部材、20……環状隙間。FIG. 1 shows an embodiment of the present invention. FIG. 1 is a front view of a cutaway portion of an automatic transmission, FIG. 2 is an exploded perspective view of an oil pump, and FIG. 3 is an oil pump with a cover member removed. FIG. 4 is a side view of the pump, and FIG. 4 is a longitudinal sectional view of the oil pump. 2 ... oil pump, 4 ... housing, 4a ... inner peripheral wall, 5 ... cover member, 8 ... internal gear, 10 ... external gear, 18 ... annular groove, 19 ... annular member, 20 ... An annular gap.
Claims (2)
面側から凹設された凹部と、この凹部内に収容されたロ
ータと、ハウジングの上記一側面に固定されて凹部を塞
ぐカバー部材とを備え、ロータを回転させることにより
流体圧を発生させるポンプにおいて、 上記ハウジング及びカバー部材が軽合金で構成されると
ともに、ロータは鉄系金属で構成され、 上記ロータの外周面に対向するハウジングの環状の内周
壁部の半径方向外側にはカバー部材側へ開口し且つ凹部
と略同深さの環状溝がハウジングの上記一側面側から凹
設され、 上記環状溝内には内周壁部の半径方向への熱膨張を抑制
する環状部材が装着されていることを特徴とするポンプ
構造。1. A housing, a recess formed in the housing from one side thereof, a rotor housed in the recess, and a cover member fixed to the one side of the housing to cover the recess. A pump that generates fluid pressure by rotating a rotor, wherein the housing and the cover member are made of a light alloy, the rotor is made of an iron-based metal, and an annular shape of the housing facing the outer peripheral surface of the rotor is provided. An annular groove which is open to the cover member side and has substantially the same depth as the concave portion is formed on the outer side of the inner peripheral wall in the radial direction, and is recessed from the one side surface of the housing. A pump structure comprising an annular member for suppressing thermal expansion of the pump.
バー部材の端面との少なくとも一方と環状部材の端面間
に環状隙間が形成されていることを特徴とする請求項１
に記載のポンプ構造。2. An annular gap is formed between at least one of a back end face of the annular groove and an end face of a cover member facing the annular groove and an end face of the annular member.
3. The pump structure according to 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1990099236U JP2538505Y2 (en) | 1990-09-20 | 1990-09-20 | Pump structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1990099236U JP2538505Y2 (en) | 1990-09-20 | 1990-09-20 | Pump structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0457686U JPH0457686U (en) | 1992-05-18 |
| JP2538505Y2 true JP2538505Y2 (en) | 1997-06-18 |
Family
ID=31841021
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1990099236U Expired - Fee Related JP2538505Y2 (en) | 1990-09-20 | 1990-09-20 | Pump structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2538505Y2 (en) |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5550384Y2 (en) * | 1974-08-20 | 1980-11-22 | ||
| JPS57136801U (en) * | 1981-02-20 | 1982-08-26 |
-
1990
- 1990-09-20 JP JP1990099236U patent/JP2538505Y2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0457686U (en) | 1992-05-18 |
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|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |