JP3301567B2 - Reciprocating compressor - Google Patents
Reciprocating compressorInfo
- Publication number
- JP3301567B2 JP3301567B2 JP22478293A JP22478293A JP3301567B2 JP 3301567 B2 JP3301567 B2 JP 3301567B2 JP 22478293 A JP22478293 A JP 22478293A JP 22478293 A JP22478293 A JP 22478293A JP 3301567 B2 JP3301567 B2 JP 3301567B2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- valve
- discharge
- cylinder block
- pressure
- 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
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両空調用に供して好
適な圧縮機に係り、詳しくは単頭ピストンを内装した多
気筒往復動型圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor suitable for use in vehicle air conditioning, and more particularly to a multi-cylinder reciprocating compressor having a single-headed piston.
【０００２】[0002]
【従来の技術】従来この種の圧縮機として、回転斜板が
シユーを介して単頭ピストンに係留されるか、又は自転
を拘束された揺動板がコンロッドを介して単頭ピストン
と連係されるといった形態の圧縮機が知られている。こ
れら固定容量型の圧縮機においては、熱負荷が小さくな
ると蒸発器のフロストを防止するためにクラッチがオフ
され、熱負荷の復活に伴って再びクラッチがオンされる
といった断続運転が行われる。2. Description of the Related Art Conventionally, as a compressor of this type, a rotating swash plate is moored to a single-headed piston via a shoe, or a swinging plate whose rotation is restricted is connected to a single-headed piston via a connecting rod. A known type of compressor is known. In these fixed displacement compressors, an intermittent operation is performed in which the clutch is turned off to prevent frost of the evaporator when the heat load is reduced, and the clutch is turned on again when the heat load is restored.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、圧縮機
の起動時には急激なトルク上昇によってクラッチを含む
構成要素の耐久性が低下するほか、減速加速度に起因し
て運転フイーリングが極端に損なわれる。また、エンジ
ンのアイドリング状態においては、負荷変動に基づくア
イドリング回転の不安定化、ひいてはエンジンストール
を惹起するといった虞れもある。However, when the compressor is started, the durability of components including the clutch is reduced due to a sudden increase in torque, and the driving feeling is extremely impaired due to the deceleration. Further, in the idling state of the engine, there is a possibility that the idling rotation may be destabilized due to the load fluctuation, and the engine may be stalled.
【０００４】本発明は、圧縮機起動時の過激なトルク変
動を抑制し、エンジンの負担軽減と運転操作性の向上を
図ることを解決すべき技術課題とするものである。An object of the present invention is to suppress radical torque fluctuation at the time of starting a compressor, to reduce the load on the engine and to improve the driving operability.
【０００５】[0005]
【課題を解決するための手段】本発明は上記課題解決の
ため、複数のボアを並設したシリンダブロックと、クラ
ンク室を形成して該シリンダブロックの一端を閉塞する
フロントハウジングと、内方域に吐出室、外方域には吸
入室を形成し、かつ吸入弁及び吐出弁を有する弁板を介
して該シリンダブロックの他端を閉塞するリヤハウジン
グと、上記クランク室内に延在する駆動軸に固着された
斜板要素と、該斜板要素と連係して上記ボア内を直動す
る単頭ピストンとを備えた往復動型圧縮機において、上
記シリンダブロックの中心部に有底状のチヤンバを設け
てその底部を低圧域と連通し、かつ各ボア内圧縮室の中
間領域と該チヤンバとを通孔により連通するとともに、
該チヤンバ内にはばねの付勢力と吐出圧力との対抗によ
り該通孔を開閉する制御弁を嵌挿し、上記吐出弁の開弁
時にのみ該チヤンバ内へ吐出圧力を導入して上記制御弁
で上記通孔３１を閉鎖する導圧路を上記弁板に穿設した
新規な構成を採用している。According to the present invention, there is provided a cylinder block having a plurality of bores, a front housing for forming a crank chamber and closing one end of the cylinder block, and an inner region. A rear housing that forms a suction chamber in an outer region, and closes the other end of the cylinder block via a valve plate having a suction valve and a discharge valve; and a drive shaft that extends into the crank chamber. A reciprocating compressor including a swash plate element fixed to the swash plate element and a single-headed piston that moves directly in the bore in cooperation with the swash plate element. And the bottom thereof is communicated with the low-pressure area, and the intermediate areas of the respective compression chambers in the bore and the chamber are communicated with each other through holes,
The then fitted control valve for opening and closing the vent hole by opposing the urging force of the spring and discharge pressure in Chiyanba, above with a discharge pressure into the Chiyanba only when opening the upper Symbol discharge valve Type guide Control valve
In which the guide passage close the through hole 31 employs a novel structure that is formed in the valve plate.
【０００６】[0006]
【作用】圧縮機の通常運転時には、吐出室から導圧路を
介してチヤンバ内へ吐出圧力が導入され、該吐出圧力の
付勢によりばねに抗して進動した制御弁が通孔を閉鎖
し、圧縮機は正規の全容量状態で運転されている。そし
て圧縮機が停止されると、吐出弁によって自動的に導圧
路が閉止される一方、チヤンバ内の残存冷媒は制御弁の
微小な嵌合遊隙を潜通して低圧域へと漏出し、制御弁の
前後に作用する圧力が平衡状態に近づくにつれ、制御弁
はばねの付勢力により退動して通孔を開放するので、圧
縮機は各ボアの有効ストロークが半減される半容量状態
へと変移される。その後圧縮機が再起動されると、当初
は通孔の開放により半容量状態のままに運転が開始され
るが、吐出弁の反復開弁動作に付随してチヤンバへの吐
出圧力の導入も復活されるため、ばねの付勢力が吐出圧
力に屈することによって制御弁は徐々に進動し、通孔が
完全に閉鎖されるに至って圧縮機は再び全容量状態の運
転に復帰する。During normal operation of the compressor, a discharge pressure is introduced from the discharge chamber into the chamber via the pressure guiding passage, and the control valve, which is advanced against the spring by the urging of the discharge pressure, closes the through hole. However, the compressor is operating at full capacity. When the compressor is stopped, the discharge valve automatically closes the pressure guide path, while the residual refrigerant in the chamber leaks through the small fitting play gap of the control valve to the low pressure area, As the pressure acting before and after the control valve approaches the equilibrium state, the control valve retreats by the urging force of the spring and opens the through hole, so that the compressor enters a half capacity state where the effective stroke of each bore is reduced by half. It is transferred. After that, when the compressor is restarted, the operation is initially started in the half capacity state by opening the through hole, but the introduction of the discharge pressure to the chamber is also restored with the repeated opening of the discharge valve As a result, the control valve gradually advances due to the biasing force of the spring buckling to the discharge pressure, the through hole is completely closed, and the compressor returns to the full capacity operation again.
【０００７】[0007]
【実施例】以下、図に基づいて本発明の実施例を具体的
に説明する。図１において、圧縮機の外郭の一部を構成
するシリンダブロック１の前端にはフロントハウジング
２が結合され、同後端には外方域に吸入室５、内方域に
吐出室６が形成されたリヤハウジング３が弁板４を介し
て結合されている。そしてフロントハウジング２内に形
成されたクランク室７には、動力源に連結された駆動軸
８が挿通され、該駆動軸８はシリンダブロック１及びフ
ロントハウジング２にそれぞれラジアル軸受２０及び２
１を介して回転自在に支承されている。クランク室７内
の駆動軸８上には回転斜板９が固着され、該回転斜板９
の後面側には揺動板１０が相対回転可能に支持され、か
つ外縁部に設けた案内部１０ａが通しボルト１１と係合
することにより自転が拘束されるとともに、シリンダブ
ロック１に貫設されたボア１２内の単頭ピストン１３と
該揺動板１０とはコンロッド１４により連節されてい
る。したがって、駆動軸８の回転運動が回転斜板９を介
して揺動板１０の前後揺動に変換され、単頭ピストン１
３がボア１２内を往復動することにより、吸入弁１５を
介して吸入室５からボア１２内へ吸入された冷媒ガス
が、圧縮されつつ後述する吐出弁１６を介して吐出室６
へ吐出される。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be specifically described below with reference to the drawings. In FIG. 1, a front housing 2 is connected to a front end of a cylinder block 1 which forms a part of an outer shell of the compressor, and a suction chamber 5 is formed in an outer area and a discharge chamber 6 is formed in an inner area at the rear end. The rear housing 3 is connected via a valve plate 4. A drive shaft 8 connected to a power source is inserted through a crank chamber 7 formed in the front housing 2, and the drive shaft 8 is connected to the cylinder block 1 and the front housing 2 by radial bearings 20 and 2, respectively.
It is rotatably supported via 1. A rotary swash plate 9 is fixed on a drive shaft 8 in the crank chamber 7.
A rocking plate 10 is supported on the rear surface side so as to be relatively rotatable, and a guide portion 10 a provided on an outer edge portion is engaged with a through bolt 11 to restrict rotation and penetrate the cylinder block 1. The single-headed piston 13 in the bore 12 and the swing plate 10 are connected by a connecting rod 14. Therefore, the rotational motion of the drive shaft 8 is converted into the forward and backward swing of the swing plate 10 via the rotary swash plate 9, and the single-head piston 1
When the refrigerant gas 3 is reciprocated in the bore 12, the refrigerant gas sucked into the bore 12 from the suction chamber 5 through the suction valve 15 is compressed and discharged into the discharge chamber 6 through the discharge valve 16 described later.
Is discharged to
【０００８】また、シリンダブロック１の軸心部分には
クランク室７内へ突出したボス部１ａが形成されて、該
ボス部１ａに穿設された中心軸孔には上記ラジアル軸受
２０が内装圧入されており、該ラジアル軸受２０に支承
された駆動軸８の後端は、中心軸孔内に収納されたスラ
ストレース２２及び皿ばね２３によって支持されてお
り、該皿ばね２３の付勢力は、該駆動軸８に固着された
回転斜板９とフロントハウジング２との間に介装された
スラスト軸受２４により受承されている。なお、１７は
クランク室７と吸入室５とを連通する抽気通路である。A boss 1a projecting into the crank chamber 7 is formed in the axial center of the cylinder block 1, and the radial bearing 20 is press-fitted into a central shaft hole formed in the boss 1a. The rear end of the drive shaft 8 supported by the radial bearing 20 is supported by a thrust trace 22 and a disc spring 23 housed in a center shaft hole, and the urging force of the disc spring 23 is It is received by a thrust bearing 24 interposed between the rotating housing 9 fixed to the drive shaft 8 and the front housing 2. Reference numeral 17 denotes a bleed passage that connects the crank chamber 7 and the suction chamber 5.
【０００９】次いで本発明のもっとも特徴とする容量制
御機構について説明する。図１〜３において、シリンダ
ブロック１の中心部には有底円孔状のチヤンバ３０が穿
設され、該チヤンバ３０内には各ボア１２内圧縮室のほ
ぼ中間領域と連通する通孔３１が放射方向に開口されて
おり、さらに該チヤンバ３０の底部には段差状をなすば
ね受室３２が形成され、該ばね受室３２は逃孔３３を介
してクランク室７と連通されている。そして該チヤンバ
３０に嵌挿された有底円筒状の制御弁３４は、上記ばね
受室３２と該制御弁３４の内底壁との間に介装されたコ
イルばね３５によって常に弁板４に向け付勢され、圧縮
機の停止時を示す図２の状態では、該制御弁３４の後端
が弁板４と衝合し、かつチヤンバ３０内に開口する各通
孔３１はいずれも開放されて上記逃孔３３と導通されて
いる。Next, a capacity control mechanism which is the most characteristic of the present invention will be described. In FIGS. 1 to 3, a bottomed circular chamber 30 is drilled at the center of the cylinder block 1, and a through hole 31 communicating with a substantially intermediate area of the compression chamber in each bore 12 is formed in the chamber 30. The chamber 30 is opened in the radial direction, and a stepped spring receiving chamber 32 is formed at the bottom of the chamber 30. The spring receiving chamber 32 communicates with the crank chamber 7 through a relief hole 33. The bottomed cylindrical control valve 34 fitted into the chamber 30 is always attached to the valve plate 4 by a coil spring 35 interposed between the spring receiving chamber 32 and the inner bottom wall of the control valve 34. When the compressor is stopped, the rear end of the control valve 34 abuts with the valve plate 4 and all the through holes 31 opened in the chamber 30 are opened. And is electrically connected to the escape hole 33.
【００１０】図３からも明らかなように、弁板４には吐
出弁１６の少なくとも１個のリード部の開弁動作時にの
み、吐出室６と上記チヤンバ３０とを導通する導圧路３
６が形成されており、圧縮機の正常運転時を示す図１の
状態では、該導圧路３６を介してチヤンバ３０内に導入
された吐出圧力の付勢により、上記制御弁３４の前端が
段差部３０ａに衝合するまで進動し、上記各通孔３１は
制御弁３４の干渉によって閉鎖されている。As is apparent from FIG. 3, the valve plate 4 has a pressure guiding passage 3 that connects the discharge chamber 6 and the chamber 30 only when at least one lead of the discharge valve 16 is opened.
In the state shown in FIG. 1 showing the normal operation of the compressor, the front end of the control valve 34 is formed by the urging of the discharge pressure introduced into the chamber 30 through the pressure introducing passage 36. It moves until it abuts on the step portion 30 a, and the through holes 31 are closed by the interference of the control valve 34.
【００１１】本実施例は上述のように構成されており、
圧縮機の通常運転時における制御弁３４には、反復継続
される吐出弁１６の開弁動作によって、吐出室６から導
圧路３６を介してチヤンバ３０内へ導入された吐出圧力
がその進動方向（図示左方向）に向けて作用し、一方、
退動方向（図示右方向）に向けてはクランク室圧力及び
コイルばね３５の付勢力が作用している。かかる状態で
は、該吐出圧力の付勢により対抗圧力に打勝って進動し
た制御弁３４が各通孔３１を閉鎖し、圧縮機は正規の全
容量状態で運転されている（図１）。This embodiment is configured as described above.
During the normal operation of the compressor, the discharge pressure introduced into the chamber 30 from the discharge chamber 6 through the pressure guide path 36 by the repetitively continued opening operation of the discharge valve 16 causes the control valve 34 to advance. In the direction (left direction in the figure),
The crank chamber pressure and the urging force of the coil spring 35 act in the retreating direction (rightward in the figure). In such a state, the control valve 34 which has advanced by overcoming the opposing pressure by the urging of the discharge pressure closes each through hole 31, and the compressor is operated in a normal full capacity state (FIG. 1).
【００１２】そして熱負荷の低下などにより圧縮機が停
止されると、弁板４に着座した吐出弁１６によって導圧
路３６が自動的に閉止される一方、チヤンバ３０内の残
存冷媒は制御弁３４の微小な嵌合遊隙を潜通して逃孔３
３からクランク室７へと漏出し、制御弁３４の前後に作
用する圧力が平衡状態に近づくにつれ、制御弁３４はコ
イルばね３５の付勢力によって緩やかに退動せしめられ
る。すなわち制御弁３４の後端が弁板４と衝合した時点
で、チヤンバ３０内に開口する各通孔３１は完全に開放
されて逃孔３３と導通し、圧縮機は各ボア１２の有効ス
トロークが該通孔３１の開放によって半減される半容量
状態へと変移される（図２）。When the compressor is stopped due to a decrease in heat load or the like, the pressure guiding path 36 is automatically closed by the discharge valve 16 seated on the valve plate 4, while the remaining refrigerant in the chamber 30 is removed by the control valve. 34 through the small fitting play gap
As the pressure leaks from 3 to the crank chamber 7 and the pressure acting before and after the control valve 34 approaches an equilibrium state, the control valve 34 is gradually retracted by the urging force of the coil spring 35. That is, when the rear end of the control valve 34 abuts against the valve plate 4, each through hole 31 opening into the chamber 30 is completely opened and communicates with the escape hole 33, and the compressor operates the effective stroke of each bore 12. Is changed to a half capacity state which is reduced by half by opening the through hole 31 (FIG. 2).
【００１３】その後熱負荷の上昇などにより圧縮機が再
起動されると、当初は各通孔３１の開放により半容量状
態のまま運転が開始されるため起動トルクはきわめて小
さく、エンジン負荷も良好に軽減される。そして吐出弁
１６の反復開弁動作に付随して導圧路３６を介したチヤ
ンバ３０への吐出圧力の導入が復活されると、コイルば
ね３５の付勢力が吐出圧力に屈することとなって制御弁
３４は徐々に進動し、各通孔３１が完全に閉鎖されるに
至って圧縮機は再び全容量状態の運転に復帰する。Thereafter, when the compressor is restarted due to an increase in heat load, the operation is initially started in a half-capacity state by opening the through holes 31, so that the starting torque is extremely small and the engine load is good. It is reduced. Then, when the introduction of the discharge pressure to the chamber 30 via the pressure guiding path 36 is restored in association with the repetitive valve opening operation of the discharge valve 16, the urging force of the coil spring 35 buckles to the discharge pressure, and the control is performed. The valve 34 advances gradually, and the compressor returns to the full capacity operation again when the respective through holes 31 are completely closed.
【００１４】なお、上記制御弁３４の前後に作用する冷
媒圧力の差圧変動に基づいて、該制御弁３４の受圧面
積、通孔３１の開設位置、コイルばね３５のばね定数等
を選択的に設定することにより、吐出圧力が格段と低下
した低熱負荷時、該吐出圧力に打勝ったコイルばね３５
の付勢力によって制御弁３４に退動を促し、クラッチ操
作を経ることなく通孔３１を開放に導いて実吐出容量の
半減化制御を具現することもできる。The pressure receiving area of the control valve 34, the opening position of the through hole 31, the spring constant of the coil spring 35 and the like are selectively determined based on the differential pressure fluctuation of the refrigerant pressure acting before and after the control valve 34. By setting, the coil spring 35 which has overcome the discharge pressure when the discharge pressure is significantly reduced and the heat load is low.
By urging the control valve 34 to retreat by the urging force described above, the through-hole 31 can be opened without passing through the clutch operation, thereby realizing control for halving the actual discharge capacity.
【００１５】[0015]
【発明の効果】以上、詳述したように本発明に係る圧縮
機は、その起動時に半容量状態で運転が開始されるため
立上りトルクはきわめて小さく、起動衝撃に基づく圧縮
機及びクラッチの疲労劣化を有効に防止しうるととも
に、圧縮機の起動に伴うエンジン負荷も必然的に軽減さ
れるので、運転フィーリングを損なうことなく、良好な
操作性を維持することができる。As described in detail above, the compressor according to the present invention starts operation in a half-capacity state at the time of start-up, so that the start-up torque is extremely small, and the compressor and clutch are fatigued and deteriorated due to start-up impact. Can be effectively prevented, and the engine load involved in starting the compressor is necessarily reduced, so that good operability can be maintained without impairing the driving feeling.
【００１６】また、圧縮機の稼動中、吐出圧力の変化に
応動して制御弁が通孔を開閉すべく媒介変数を選択した
ものでは、クラッチ操作回数の減少を通じてその延命に
貢献することができる。Further, when the control valve selects a parameter to open and close the through hole in response to a change in the discharge pressure during operation of the compressor, the life of the compressor can be extended by reducing the number of clutch operations. .
【図１】本発明の実施例に係る圧縮機の通常運転状態を
示す断面図。FIG. 1 is a sectional view showing a normal operation state of a compressor according to an embodiment of the present invention.
【図２】同圧縮機の起動前の状態を示す断面図。FIG. 2 is a sectional view showing a state before starting the compressor.
【図３】同圧縮機の吐出弁及び導圧路の形態を示す図１
のＡ−Ａ線断面図。FIG. 3 is a view showing a configuration of a discharge valve and a pressure guide path of the compressor.
Sectional view on the AA line of FIG.
１はシリンダブロック、２はフロントハウジング、３は
リヤハウジング、４は弁板、５は吸入室、６は吐出室、
７はクランク室、８は駆動軸、１２はボア、１３は単頭
ピストン、１６は吐出弁、３０はチャンバ、３１は通
孔、３３は逃孔、３４は制御弁、３５はコイルばね、３
６は導圧路1 is a cylinder block, 2 is a front housing, 3 is a rear housing, 4 is a valve plate, 5 is a suction chamber, 6 is a discharge chamber,
7 is a crank chamber, 8 is a drive shaft, 12 is a bore, 13 is a single-headed piston, 16 is a discharge valve, 30 is a chamber, 31 is a through hole, 33 is a vent, 34 is a control valve, 35 is a coil spring, 3
6 is an impulse line
───────────────────────────────────────────────────── フロントページの続き (72)発明者 濱岡 貴裕 愛知県刈谷市豊田町２丁目１番地 株式 会社豊田自動織機製作所内 (58)調査した分野(Int.Cl.7，ＤＢ名) F04B 27/14 F04B 49/00 361 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Takahiro Hamaoka 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation (58) Field surveyed (Int. Cl. 7 , DB name) F04B 27 / 14 F04B 49/00 361
Claims (1)
と、クランク室を形成して該シリンダブロックの一端を
閉塞するフロントハウジングと、内方域に吐出室、外方
域には吸入室を形成し、かつ吸入弁及び吐出弁を有する
弁板を介して該シリンダブロックの他端を閉塞するリヤ
ハウジングと、上記クランク室内に延在する駆動軸に固
着された斜板要素と、該斜板要素と連係して上記ボア内
を直動する単頭ピストンとを備えた往復動型圧縮機にお
いて、上記シリンダブロックの中心部に有底状のチヤン
バを設けてその底部を低圧域と連通し、かつ各ボア内圧
縮室の中間領域と該チヤンバとを通孔により連通すると
ともに、該チヤンバ内にはばねの付勢力と吐出圧力との
対抗により該通孔を開閉する制御弁を嵌挿し、上記吐出
弁の開弁時にのみ該チヤンバ内へ吐出圧力を導入して上
記制御弁で上記通孔３１を閉鎖する導圧路を上記弁板に
穿設したことを特徴とする往復動型圧縮機。1. A cylinder block having a plurality of bores arranged side by side, a front housing forming a crank chamber and closing one end of the cylinder block, a discharge chamber in an inner area, and a suction chamber in an outer area. A rear housing for closing the other end of the cylinder block via a valve plate having a suction valve and a discharge valve, a swash plate element fixed to a drive shaft extending into the crank chamber, and the swash plate element A reciprocating compressor having a single-headed piston that linearly moves in the bore in conjunction with a cylinder block, a bottomed chamber is provided at the center of the cylinder block, and the bottom communicates with the low-pressure region, and with an intermediate region and said Chiyanba of each bore in the compression chamber communicating with the hole, is within the Chiyanba and fitted control valve for opening and closing the vent hole by opposing the urging force of the spring between the discharge pressure, the upper Only when the discharge valve is open. On the discharge pressure by entering guide into Yamba
Reciprocating compressor the pressure introduction passage close the through hole 31, characterized in that bored in the valve plate in serial control valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22478293A JP3301567B2 (en) | 1993-09-09 | 1993-09-09 | Reciprocating compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22478293A JP3301567B2 (en) | 1993-09-09 | 1993-09-09 | Reciprocating compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0777158A JPH0777158A (en) | 1995-03-20 |
| JP3301567B2 true JP3301567B2 (en) | 2002-07-15 |
Family
ID=16819128
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22478293A Expired - Fee Related JP3301567B2 (en) | 1993-09-09 | 1993-09-09 | Reciprocating compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3301567B2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10196529A (en) * | 1997-01-10 | 1998-07-31 | Sanden Corp | Reciprocating compressor |
-
1993
- 1993-09-09 JP JP22478293A patent/JP3301567B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0777158A (en) | 1995-03-20 |
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