JPH07103138A - Swash plate type variable displacement compressor - Google Patents
Swash plate type variable displacement compressorInfo
- Publication number
- JPH07103138A JPH07103138A JP5251967A JP25196793A JPH07103138A JP H07103138 A JPH07103138 A JP H07103138A JP 5251967 A JP5251967 A JP 5251967A JP 25196793 A JP25196793 A JP 25196793A JP H07103138 A JPH07103138 A JP H07103138A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- swash plate
- compressor
- suction
- chamber
- 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.)
- Granted
Links
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は例えば車輌用空調装置
における冷媒ガスの圧縮等に使用される斜板式可変容量
圧縮機に関する。より詳細には起動ショックを緩和する
ことによりエンジンへの負荷を低減して耐久性を向上
し、騒音を低減することができる最小容量起動型の斜板
式可変容量圧縮機の改良された構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate type variable displacement compressor used, for example, for compressing refrigerant gas in a vehicle air conditioner. More specifically, the present invention relates to an improved structure of a minimum capacity starting type swash plate type variable capacity compressor capable of reducing load on an engine by improving a starting shock, improving durability, and reducing noise.
【０００２】[0002]
【従来の技術】一般に、車両用空調装置に使用される圧
縮機はエンジンの動力により回転されて、冷媒ガスの圧
縮を行う。圧縮機はその回転数が同じである場合に吐出
容量が同一の固定容量型のものと、同じ回転数でも吐出
容量を変化する可変容量型のものがある。前者の圧縮機
では製造が容易でコスト上有利である反面、冷房負荷が
小さくて吐出容量を低減したい場合にもそれが不可能で
ある。後者の可変容量圧縮機は冷房負荷に応じて適正な
空調動作を行うことができるとともに、エンジンへの負
荷を軽減して動力損失を抑制することができる。又、圧
縮機は車両の走行中に電磁クラッチをオンしてエンジン
の動力により起動される。この起動時のショックを緩和
してエンジンへの急激な負荷増大を抑制することによ
り、電磁クラッチやエンジンの耐久性を向上し、かつ走
行フィーリングを向上するため、停止中に圧縮機が最小
容量で起動されるようにした可変容量圧縮機が提案され
ている。この圧縮機として本願出願人による特開昭６２
−５５４７８号公報に示すものが提案されている。2. Description of the Related Art Generally, a compressor used in a vehicle air conditioner is rotated by the power of an engine to compress a refrigerant gas. There are two types of compressors, a fixed displacement type that has the same discharge capacity when the rotation speed is the same, and a variable displacement type that changes the discharge capacity even at the same rotation speed. The former compressor is easy to manufacture and advantageous in cost, but it is impossible even when the cooling load is small and the discharge capacity is desired to be reduced. The latter variable displacement compressor can perform an appropriate air conditioning operation according to the cooling load, and can reduce the load on the engine to suppress power loss. The compressor is started by the power of the engine by turning on the electromagnetic clutch while the vehicle is traveling. By reducing this shock at startup and suppressing a sudden increase in load on the engine, the durability of the electromagnetic clutch and engine is improved, and the driving feeling is improved. A variable capacity compressor is proposed which is adapted to be started in. This compressor is disclosed in Japanese Patent Application Laid-Open No. 62-62
The one disclosed in Japanese Patent No. 55478 has been proposed.
【０００３】上記圧縮機はハウジング内に吸入室と吐出
室及びクランク室とを備え、回転軸上に回転支持体を同
期回転可能に取り付けている。又、該回転支持体にはピ
ストンを往復動させるための斜板が前後方向の傾動可能
に、かつ回転軸の周りで回動不能に装着されている。そ
して、ピストンの背面に作用するクランク室圧力と前面
に作用するシリンダボア内の作動室の圧力との差圧に応
じて斜板の傾斜角が変化して吐出容量が制御されるよう
になっている。さらに、回転支持体と斜板との間には圧
縮機の停止時において斜板を傾斜角が最小となる方向へ
付勢してピストンのストロークが最小となる最小容量位
置に保持するバネが介在されている。The compressor is provided with a suction chamber, a discharge chamber and a crank chamber in a housing, and a rotary support is mounted on a rotary shaft so as to be synchronously rotatable. Further, a swash plate for reciprocating the piston is mounted on the rotary support so as to be tiltable in the front-rear direction and non-rotatable around the rotation axis. The inclination angle of the swash plate is changed according to the pressure difference between the crank chamber pressure acting on the rear surface of the piston and the working chamber pressure in the cylinder bore acting on the front surface, so that the discharge capacity is controlled. . Further, a spring is interposed between the rotary support and the swash plate to urge the swash plate in the direction in which the inclination angle is minimized when the compressor is stopped and to hold the piston in the minimum capacity position in which the stroke of the piston is minimized. Has been done.
【０００４】[0004]
【発明が解決しようとする課題】上記従来の圧縮機にお
いては、最大容量状態で圧縮機を運転中に電磁クラッチ
をオフすると、斜板は前記バネにより最大傾斜角から最
小傾斜角に向かって移動しようとする。圧縮機の停止直
後は各ピストンと対応するシリンダボア内の圧力はそれ
ぞれ異なる。圧縮行程の途中にあるピストンを収容する
シリンダボア内作動室の圧力Ｐｂと、吐出室内の圧力Ｐ
ｄと、吸入室内の圧力Ｐｓとの間には、Ｐｓ＜Ｐｂ＜Ｐ
ｄの関係が成立する。このため作動室内は完全に独立し
てしまい、その圧力が低下しにくい。従って、バネによ
り斜板が最小傾斜角へ傾動されるまでの時間が長くな
り、完全に最小傾斜角となるまでの間には、吸入圧力Ｐ
ｓと吐出圧力Ｐｄが等しくなるまでの長時間が必要とな
る。このため、圧縮機を停止してから短時間のうちに圧
縮機を再起動する場合には、斜板の傾斜角が最大に近い
状態又は中間傾斜状態で行われるので、起動時のショッ
クを緩和することができないという問題があった。In the above conventional compressor, when the electromagnetic clutch is turned off while the compressor is operating in the maximum capacity state, the swash plate moves from the maximum inclination angle to the minimum inclination angle by the spring. try to. Immediately after the compressor is stopped, the pressure in the cylinder bore corresponding to each piston is different. The pressure Pb in the working chamber in the cylinder bore that houses the piston in the middle of the compression stroke and the pressure P in the discharge chamber
d and the pressure Ps in the suction chamber, Ps <Pb <P
The relationship of d is established. For this reason, the working chamber is completely independent, and its pressure does not easily drop. Therefore, it takes a long time until the swash plate is tilted to the minimum tilt angle by the spring, and the suction pressure P is increased until the tilt angle is completely reached.
It takes a long time until the discharge pressure Pd becomes equal to s. Therefore, when the compressor is restarted within a short time after the compressor is stopped, the tilt angle of the swash plate is close to the maximum or the intermediate tilt state, so the shock at the time of startup is mitigated. There was a problem that I could not do it.
【０００５】この発明の第１の目的は上記従来技術に存
する問題点を解消して、圧縮機が停止された後、斜板の
最小傾斜角への移動を迅速に行い、圧縮機を早期に再起
動した場合のショックを緩和して電磁クラッチの耐久性
を向上し、騒音を低減することができる斜板式可変容量
圧縮機を提供することにある。A first object of the present invention is to solve the problems existing in the above-mentioned prior art, to quickly move the swash plate to the minimum inclination angle after the compressor is stopped, and to quickly start the compressor. It is an object of the present invention to provide a swash plate type variable displacement compressor capable of reducing shock when restarted, improving durability of an electromagnetic clutch, and reducing noise.
【０００６】この発明の第２の目的は上記第１の目的に
加えて、製造を容易に行い安価な斜板式可変容量圧縮機
を提供することにある。この発明の第３の目的は上記第
２の目的に加えて、圧縮機が停止された後、斜板の最小
傾斜角への復帰をさらに迅速に行い、圧縮機を早期に再
起動した場合のショックをさらに緩和して電磁クラッチ
の耐久性を向上し、騒音をより低減することができる斜
板式可変容量圧縮機を提供することにある。A second object of the present invention is to provide a swash plate type variable displacement compressor which is easy to manufacture and inexpensive in addition to the first object. A third object of the present invention is, in addition to the above-mentioned second object, the case where after the compressor is stopped, the swash plate is returned to the minimum inclination angle more quickly, and the compressor is restarted early. An object of the present invention is to provide a swash plate type variable displacement compressor that can further reduce shock and improve the durability of the electromagnetic clutch and further reduce noise.
【０００７】さらに、この発明の第４の目的は、上記第
１の目的に加えて騒音をさらに低減することができる斜
板式可変容量圧縮機を提供することにある。A fourth object of the present invention is to provide a swash plate type variable displacement compressor capable of further reducing noise in addition to the first object.
【０００８】[0008]
【課題を解決するための手段】請求項１記載の発明は上
記第１の目的を達成するため、ハウジング内に吸入室、
吐出室及びクランク室を備え、回転軸に対してシリンダ
ボア内に収容した複数のピストンを往復動させるための
斜板を前記クランク室内で傾動可能に装着し、前記ピス
トンのストロークに比例する前記斜板の傾斜角を容量制
御機構により変化させて冷媒ガスの吐出容量を制御する
とともに、回転軸の停止状態で前記斜板の傾斜角を最小
容量となる最小傾斜角に復帰する付勢手段を備えた斜板
式可変容量圧縮機において、前記吸入室とシリンダボア
を連通する吸入ポートを開閉する弾性材よりなる板状の
吸入弁と、該吸入弁が接触する弁座との間に、圧縮機の
停止状態でシリンダボア内の圧力を吸入室へ逃すための
放圧通路を設けるという手段をとっている。In order to achieve the first object, the invention according to claim 1 has a suction chamber inside a housing,
A swash plate, which has a discharge chamber and a crank chamber, is provided for tilting in the crank chamber for reciprocating a plurality of pistons housed in a cylinder bore with respect to a rotation shaft, and the swash plate proportional to the stroke of the piston And a biasing means for controlling the discharge capacity of the refrigerant gas by changing the tilt angle of the swash plate by the capacity control mechanism and for returning the tilt angle of the swash plate to the minimum tilt angle which is the minimum capacity when the rotating shaft is stopped. In a swash plate type variable displacement compressor, a compressor stop state is provided between a plate-shaped intake valve made of an elastic material that opens and closes an intake port that communicates the intake chamber with a cylinder bore, and a valve seat with which the intake valve contacts. Therefore, a means for providing a pressure release passage for releasing the pressure in the cylinder bore to the suction chamber is adopted.
【０００９】又、請求項２記載の発明は上記第２の目的
を達成するため、請求項１において圧縮機の停止状態で
吸入ポートを形成した弁座から吸入弁を離隔し、弁座と
吸入弁との隙間により前記放圧通路を形成するという手
段をとっている。Further, in order to achieve the above-mentioned second object, the invention according to claim 2 separates the intake valve from the valve seat having the intake port in the stopped state of the compressor, and the intake valve and the intake valve are separated from each other. The means for forming the pressure release passage by the gap with the valve is adopted.
【００１０】又、請求項３記載の発明は上記第２の目的
を達成するため、請求項１において圧縮機の停止状態で
弁座に形成した凹部の底面と吸入弁との隙間により前記
放圧通路を形成するという手段をとっている。Further, in order to achieve the above-mentioned second object, the invention according to claim 3 is characterized in that the pressure is released by the gap between the suction valve and the bottom surface of the recess formed in the valve seat when the compressor is stopped. It takes the means of forming a passage.
【００１１】又、請求項４記載の発明は上記第３の目的
を達成するため、請求項１において弁座又は吸入弁に形
成された粗面によって弁座と吸入弁との間に着座状態で
生ずる隙間により前記放圧通路を形成するという手段を
とっている。Further, in order to achieve the third object, the invention according to claim 4 is characterized in that the rough surface formed on the valve seat or the intake valve in the first aspect allows the valve seat and the intake valve to be seated between the valve seat and the intake valve. The means for forming the pressure release passage by the generated gap is adopted.
【００１２】さらに、請求項５記載の発明は上記第４の
目的を達成するため、請求項２又は３において前記吸入
弁又は該弁と接触する弁座に粗面を形成するという手段
をとっている。Further, in order to achieve the above-mentioned fourth object, the invention according to claim 5 takes the means of forming a rough surface on the intake valve or the valve seat which is in contact with the valve according to claim 2 or 3. There is.
【００１３】さらに、請求項６記載の発明は上記第４の
目的を達成するため、請求項１〜５のいずれか１項にお
いて前記シリンダボア内と吐出室を連通する吐出ポート
を開閉する板状の吐出弁が着座する弁座に粗面を形成
し、吐出室に連通する外部吐出管路に逆止弁を設けると
いう手段をとっている。Further, in order to achieve the fourth object, the invention according to claim 6 has a plate-like shape for opening and closing a discharge port for communicating the inside of the cylinder bore with the discharge chamber in any one of claims 1 to 5. A rough surface is formed on the valve seat on which the discharge valve is seated, and a check valve is provided on the external discharge conduit communicating with the discharge chamber.
【００１４】前記粗面の粗さは、バルブプレート、吸入
弁及び吐出弁の材質、シール面積等を考慮して設定すれ
ば良く、吸入弁側は２０〜３０μｍＲｚ、吐出弁側は１
０〜２０μｍＲｚが望ましい。粗面の加工方法はショッ
トブラスト等である。The roughness of the rough surface may be set in consideration of the material of the valve plate, the suction valve and the discharge valve, the seal area, etc., and the suction valve side is 20 to 30 μmRz, and the discharge valve side is 1 μm.
0 to 20 μmRz is desirable. The rough surface processing method is shot blasting or the like.
【００１５】[0015]
【作用】請求項１記載の発明では、回転軸の回転運動に
より斜板が揺動されてピストンがシリンダボア内で往復
動され、吸入ポートから吸入された冷媒ガスはシリンダ
ボア内作動室で圧縮された後、吐出ポートから吐出室へ
吐出される。圧縮機の運転中は容量制御機構により斜板
の傾斜角が冷房負荷に応じて適宜に変更されてピストン
のストロークが変更され、冷媒ガスの吐出容量が調整さ
れる。According to the first aspect of the invention, the swash plate is swung by the rotary motion of the rotary shaft to reciprocate the piston in the cylinder bore, and the refrigerant gas sucked from the suction port is compressed in the working chamber in the cylinder bore. Then, it is discharged from the discharge port to the discharge chamber. During operation of the compressor, the displacement control mechanism appropriately changes the inclination angle of the swash plate according to the cooling load to change the stroke of the piston and adjusts the discharge capacity of the refrigerant gas.
【００１６】前記斜板の傾斜角が最大状態で圧縮機が停
止されると、各ピストンと対応するシリンダボア内作動
室の圧力は吸入行程中であれば、低いのでこの圧力は斜
板の傾斜角を減少する方向に作用する。しかし、圧縮行
程中にあった作動室内の圧力は吸入圧力よりも高いの
で、この圧力は斜板の傾斜角を大きくする方向への力と
なる。しかし、作動室内の圧力は停止状態で該室内の圧
力を吸入室側に逃がす放圧通路により放圧されるので、
斜板は付勢手段により最小傾斜角となる位置に速やかに
移動される。このため、圧縮機の停止後に早期に最小容
量状態に復帰するので、早期に圧縮機が再起動された場
合のショックが緩和される。When the compressor is stopped when the inclination angle of the swash plate is maximum, the pressure in the working chamber in the cylinder bore corresponding to each piston is low during the intake stroke, so this pressure is low. Acts in the direction of decreasing. However, since the pressure in the working chamber during the compression stroke is higher than the suction pressure, this pressure serves as a force to increase the inclination angle of the swash plate. However, since the pressure in the working chamber is released in the stopped state by the pressure release passage that releases the pressure in the chamber to the suction chamber side,
The swash plate is swiftly moved to a position where the swash plate has the minimum inclination angle by the biasing means. Therefore, after the compressor is stopped, the minimum capacity state is returned to early, so that the shock when the compressor is restarted early is reduced.
【００１７】又、請求項２記載の発明では、圧縮機の停
止後に吸入弁がそれ自身の弾性により弁座から離隔して
弁座との間に放圧通路を形成するので、作動室内の圧力
は吸入室側に放圧され、斜板が最小傾斜角の位置に速や
かに復帰する。又、請求項２記載の発明では圧縮機の停
止状態で吸入弁を単に弁座から離隔する構造のため、製
造が容易となる。According to the second aspect of the present invention, after the compressor is stopped, the suction valve is separated from the valve seat by its own elasticity to form a pressure release passage between the suction valve and the valve seat. Is released to the suction chamber side, and the swash plate quickly returns to the position of the minimum inclination angle. Further, according to the second aspect of the present invention, the structure is such that the intake valve is simply separated from the valve seat when the compressor is stopped, so that the manufacturing is facilitated.
【００１８】又、請求項３記載の発明では請求項１記載
の発明の作用に加えて、圧縮機の運転中は吸入弁が変形
して弁座に接触することにより、作動室内の圧縮ガスの
吸入室側への漏洩が阻止される。又、圧縮機の停止後は
吸入弁と弁座との間に放圧通路が形成され、作動室内の
ガスが吸入室側へ放圧されて、斜板の傾斜角が速やかに
最小傾斜角に復帰される。請求項３記載の発明では弁座
に凹部を形成する構造のため、製造が容易となる。Further, according to the invention described in claim 3, in addition to the operation of the invention described in claim 1, the intake valve is deformed and comes into contact with the valve seat during the operation of the compressor, so that the compressed gas in the working chamber is Leakage to the suction chamber side is prevented. Further, after the compressor is stopped, a pressure release passage is formed between the intake valve and the valve seat, the gas in the working chamber is released to the suction chamber side, and the inclination angle of the swash plate quickly becomes the minimum inclination angle. Will be restored. According to the third aspect of the invention, the structure is such that the recess is formed in the valve seat, so that the manufacturing becomes easy.
【００１９】さらに、請求項４記載の発明では、請求項
１記載の発明の作用に加えて、圧縮機が停止されたとき
吸入弁が弁座に接触している状態で作動室から吸入室へ
の放圧が粗面によって生じる隙間により直ちに開始され
る。このため、斜板の最小傾斜角への復帰がより迅速に
行われ、動作信頼性が向上する。Further, according to the invention of claim 4, in addition to the operation of the invention of claim 1, when the compressor is stopped, the suction valve is in contact with the valve seat from the working chamber to the suction chamber. The release of pressure is immediately initiated by the gap created by the rough surface. Therefore, the swash plate is returned to the minimum inclination angle more quickly, and the operation reliability is improved.
【００２０】さらに、請求項５記載の発明では、請求項
２又は３記載の発明の作用に加えて、圧縮機が停止され
たとき吸入弁が弁座に潤滑油の膜を挟んで接触している
状態から離隔する動作が粗面接触の作用により迅速に行
われるので、放圧通路の開放が早くなり斜板の最小傾斜
角への復帰がより迅速に行われ、動作信頼性が向上す
る。Further, according to the invention of claim 5, in addition to the operation of the invention of claim 2 or 3, when the compressor is stopped, the suction valve comes into contact with the valve seat with the lubricating oil film interposed therebetween. Since the operation of separating from the existing state is performed quickly by the action of the rough surface contact, the pressure release passage is opened faster, the swash plate is returned to the minimum inclination angle more quickly, and the operation reliability is improved.
【００２１】さらに、請求項６記載の発明では請求項１
〜５のいずれか１項の作用に加えて、吐出ポートを開閉
する吐出弁と対応する弁座に粗面が形成されているた
め、吐出弁が潤滑油の膜を挟んで接触している弁座から
離隔し易く、圧縮機の運転中に吐出弁の開閉動作が円滑
に行われ、圧縮動作中の騒音が低減される。又、圧縮機
が停止された場合には、吐出室から粗面による隙間を通
して作動室内に高圧の冷媒ガスが還流される。このガス
流は逆止弁により速やかに停止されるので、作動室内の
圧力は放圧通路を通して吸入室へ速やかに開放される。Further, according to the invention of claim 6, claim 1
In addition to the operation of any one of the items 1 to 5, since the valve seat corresponding to the discharge valve that opens and closes the discharge port has a rough surface, the discharge valve is in contact with the lubricating oil film in between. It is easy to separate from the seat, the discharge valve is smoothly opened and closed during the operation of the compressor, and the noise during the compression operation is reduced. When the compressor is stopped, high-pressure refrigerant gas is recirculated from the discharge chamber through the gap formed by the rough surface into the working chamber. Since this gas flow is quickly stopped by the check valve, the pressure in the working chamber is quickly released to the suction chamber through the pressure release passage.
【００２２】[0022]
【実施例】以下、この発明を具体化した第１実施例を図
１〜図５に基づいて説明する。図３に示すようにシリン
ダブロック１の前端部にはクランク室２ａを形成するフ
ロントハウジング２が固定され、後端面にはバルブプレ
ート３を介してリヤハウジング４が固定されている。こ
のリヤハウジング４内には隔壁４ａによって吸入室５及
び吐出室６が区画形成されている。前記バルブプレート
３の前後両側面には吸入弁形成板７及び吐出弁形成板８
が接合されている。シリンダブロック１には円筒状をな
す複数（この実施例では５）のボア１ａが互いに平行に
かつ同一円周上に位置するように形成されている。この
ボア１ａ内にはそれぞれピストン９が往復動可能に収容
されている。又、前記バルブプレート３は、前記吸入室
５と各シリンダボア１ａ内において吸入と圧縮を繰り返
す作動室１０とをそれぞれ連通するための複数の吸入ポ
ート３ａを有している。同じくバルブプレート３は前記
各作動室１０と吐出室６をそれぞれ連通する複数の吐出
ポート３ｂを有している。さらに、前記吸入弁形成板７
は前記各吸入ポート３ａを開閉する吸入弁７ａを備えて
いる。同様に前記吐出弁形成板８は前記各吐出ポート３
ｂをそれぞれ開閉する吐出弁８ａを備えている。前記各
吐出弁８ａはボルト１２によりバルブプレート３に固定
したリテーナ１１により最大開口位置が規制される。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment embodying the present invention will be described below with reference to FIGS. As shown in FIG. 3, a front housing 2 forming a crank chamber 2a is fixed to a front end portion of a cylinder block 1, and a rear housing 4 is fixed to a rear end surface of the cylinder block 1 via a valve plate 3. A suction chamber 5 and a discharge chamber 6 are defined in the rear housing 4 by a partition wall 4a. A suction valve forming plate 7 and a discharge valve forming plate 8 are provided on both front and rear sides of the valve plate 3.
Are joined. In the cylinder block 1, a plurality of (5 in this embodiment) bores 1a having a cylindrical shape are formed in parallel to each other and on the same circumference. Pistons 9 are reciprocally housed in the bores 1a. Further, the valve plate 3 has a plurality of suction ports 3a for communicating the suction chamber 5 with the working chamber 10 that repeats suction and compression in each cylinder bore 1a. Similarly, the valve plate 3 has a plurality of discharge ports 3b that respectively connect the respective working chambers 10 and the discharge chamber 6 to each other. Further, the suction valve forming plate 7
Is equipped with a suction valve 7a that opens and closes each of the suction ports 3a. Similarly, the discharge valve forming plate 8 is connected to each of the discharge ports 3
The discharge valve 8a which opens and closes each b is provided. The maximum opening position of each discharge valve 8a is regulated by a retainer 11 fixed to the valve plate 3 by a bolt 12.
【００２３】前記シリンダブロック１及びフロントハウ
ジング２の中心部には回転軸１３がラジアルベアリング
１４により支持されている。この回転軸１３の中間部に
は回転駆動体１５が嵌合固定され、該駆動体１５とフロ
ントハウジング２の内壁面との間にはスラストベアリン
グ１６が介在され、圧縮反力をハウジング２に伝達す
る。駆動体１５の外周には支持アーム１７が一体に突出
形成されている。又、該アーム１７に形成した長孔１７
ａには連結ピン１８を介して回転支持体１９が前後方向
の揺動可能に、かつ回転軸１３と同期回転可能に支持さ
れている。この回転支持体１９のボス部１９ａには斜板
２０が相対回転可能に支持されている。この斜板２０と
前記各ピストン９はロッド２１によりそれぞれ連結され
ている。A rotary shaft 13 is supported by a radial bearing 14 at the center of the cylinder block 1 and the front housing 2. A rotary driving body 15 is fitted and fixed to an intermediate portion of the rotary shaft 13, and a thrust bearing 16 is interposed between the driving body 15 and an inner wall surface of the front housing 2 to transmit a compression reaction force to the housing 2. To do. A support arm 17 is integrally formed on the outer periphery of the driving body 15 so as to project therefrom. Also, the long hole 17 formed in the arm 17
A rotary support 19 is supported on a by a connecting pin 18 so as to be swingable in the front-rear direction and rotatable in synchronization with the rotary shaft 13. A swash plate 20 is supported on the boss portion 19a of the rotary support 19 so as to be relatively rotatable. The swash plate 20 and each piston 9 are connected by a rod 21.
【００２４】前記回転軸１３上にはスライダー２２が軸
線方向の往復動可能に支持され、該スライダー２２は連
結ピン２３により前記回転支持体１９に形成したボス部
１９ａに連結されている。前記スライダー２２は回転軸
１３上において駆動体１５との間に介装したバネ２４に
より常には図３において右方に付勢され、回転支持体１
９及び斜板２０をその傾斜角が最小となる位置に付勢し
ている。前記回転軸１３には前記スライダー２２の位置
を規制することにより斜板２０の最小傾斜位置を設定す
るためのストッパー２５が固定されている。又、前記斜
板２０はフロントハウジング２に形成した案内溝２６に
案内されるロッド２７により定位置おいて前後方向への
傾動のみ可能に支持されている。A slider 22 is supported on the rotary shaft 13 so as to be reciprocally movable in the axial direction, and the slider 22 is connected to a boss portion 19a formed on the rotary support 19 by a connecting pin 23. The slider 22 is always urged to the right in FIG. 3 by a spring 24 interposed between the slider 22 and the driving body 15 on the rotary shaft 13, and the rotary support 1
The swash plate 9 and the swash plate 20 are urged to a position where the inclination angle is minimum. A stopper 25 for fixing the minimum tilt position of the swash plate 20 by restricting the position of the slider 22 is fixed to the rotary shaft 13. Further, the swash plate 20 is supported by a rod 27 guided by a guide groove 26 formed in the front housing 2 so as to be tiltable in the front-rear direction at a fixed position.
【００２５】従って、エンジンの動力により回転軸１３
が回転されて回転駆動体１５、連結ピン１８及び回転支
持体１９が一体となって回転されると、斜板２０が非回
転状態で前後方向に揺動され、ロッド２１を介してピス
トン９がシリンダボア１ａ内で往復動される。このため
吸入室５から吸入ポート３ａを通して作動室１０に吸入
した冷媒ガスは、該作動室１０で圧縮された後、吐出ポ
ート３ｂを通して吐出室６へ吐出される。Therefore, the rotary shaft 13 is driven by the power of the engine.
When the rotary drive body 15, the connecting pin 18, and the rotary support body 19 are rotated integrally with each other, the swash plate 20 is swung in the front-back direction in a non-rotating state, and the piston 9 is moved through the rod 21. It is reciprocated in the cylinder bore 1a. Therefore, the refrigerant gas sucked from the suction chamber 5 into the working chamber 10 through the suction port 3a is compressed in the working chamber 10 and then discharged into the discharge chamber 6 through the discharge port 3b.
【００２６】前記リヤハウジング４には容量制御弁２８
が収容されていて、前記吐出室６とクランク室２ａを連
通する給気通路２９と、クランク室２ａと吸入室５を連
通する抽気通路３０の開閉を行う。そして、前記制御弁
２８によりクランク室２ａ内の圧力Ｐｃを制御して該圧
力Ｐｃと作動室１０内の圧力Ｐｂとの差圧を制御するこ
とにより斜板２０の傾斜角を変化させて圧縮機の吐出容
量を制御する。又、前記リヤハウジング４の吸入口４ｂ
には外部吸入管路３１が接続され、吐出口４ｃには外部
吐出管路３２が接続されている。The rear housing 4 has a capacity control valve 28.
The air supply passage 29 that connects the discharge chamber 6 and the crank chamber 2a and the extraction passage 30 that connects the crank chamber 2a and the suction chamber 5 are opened and closed. The pressure Pc in the crank chamber 2a is controlled by the control valve 28 to control the differential pressure between the pressure Pc and the pressure Pb in the working chamber 10 to change the inclination angle of the swash plate 20 and to compress the compressor. Control the discharge capacity of. Further, the suction port 4b of the rear housing 4
Is connected to an external suction pipe line 31, and the discharge port 4c is connected to an external discharge pipe line 32.
【００２７】ここで、この発明の要部である吸入弁機構
について説明する。この実施例では圧縮機の停止状態に
おいて、吸入弁７ａがそれ自身の弾性によりバルブプレ
ート３の弁座Ｓ1 から離隔して、該吸入弁７ａと弁座Ｓ
1 との間に放圧通路３３が形成されるように、吸入弁７
ａを傾斜状態に保持している。この吸入弁７ａの加工方
法としては吸入弁形成板７のプレス成型時に同時に行う
のが望ましいが、吸入弁７ａを傾斜する工程を後行程で
行ってもよい。又、バルブプレート３の弁座Ｓ1 には前
記吸入ポート３ａの周りに例えばショットブラストによ
りリング状の粗面３ｃを形成している。そして、冷媒ガ
ス中に含まれるミスト状の潤滑油が吸入弁７ａと弁座Ｓ
1 との接触界面にあっても弁座Ｓ1 から吸入弁７ａが離
れ易くしている。なお、前記吸入弁７ａの先端縁はシリ
ンダブロック１のボア１ａの外周縁に形成した係合凹部
１ｂ内に進入されていて、その最大開放位置が設定され
ている。Here, the intake valve mechanism which is the main part of the present invention will be described. In this embodiment, when the compressor is stopped, the suction valve 7a is separated from the valve seat S 1 of the valve plate 3 by its own elasticity, so that the suction valve 7a and the valve seat S
1, so that the pressure release passage 33 is formed between
a is held in an inclined state. As a method of processing the suction valve 7a, it is desirable to perform the suction valve formation plate 7 at the same time as the press molding, but the step of inclining the suction valve 7a may be performed in a later process. Further, a ring-shaped rough surface 3c is formed on the valve seat S 1 of the valve plate 3 around the suction port 3a by, for example, shot blasting. Then, the mist-like lubricating oil contained in the refrigerant gas is absorbed by the intake valve 7a and the valve seat S.
The suction valve 7a is easily separated from the valve seat S 1 even at the contact interface with 1 . The leading edge of the suction valve 7a is inserted into the engaging recess 1b formed in the outer peripheral edge of the bore 1a of the cylinder block 1, and its maximum open position is set.
【００２８】次に、前記のように構成した斜板式可変容
量圧縮機についてその作用を説明する。今、圧縮機の停
止状態においては、図４に示すようにバネ２４により斜
板２０が回転支持体１９及びスライダー２２とともに最
小傾斜位置に付勢されている。この状態で車両の走行中
に空調装置のスイッチがオンされると、図示しない電磁
クラッチがオンに切り換えられて、圧縮機の回転軸１３
が回転される。すると、回転駆動体１５、支持アーム１
７及び連結ピン１８等を介して回転支持体１９が回転さ
れる。そして、斜板２０は零容量に等しい最小傾斜角に
保持されたまま前記回転支持体１９の回転運動により非
回転のまま前後方向に揺動され、ロッド２１を介してピ
ストン９が前後に最小ストロークで揺動される。このた
め圧縮機は最小容量で起動され、そのショックが緩和さ
れて騒音が低減されるとともに、電磁クラッチあるいは
エンジンに作用する負荷が軽減されて、それらの耐久性
が向上する。Next, the operation of the swash plate type variable displacement compressor constructed as described above will be described. Now, when the compressor is stopped, as shown in FIG. 4, the swash plate 20 is urged by the spring 24 to the minimum tilt position together with the rotary support 19 and the slider 22. When the switch of the air conditioner is turned on while the vehicle is running in this state, the electromagnetic clutch (not shown) is turned on to turn on the rotary shaft 13 of the compressor.
Is rotated. Then, the rotary driver 15 and the support arm 1
The rotary support 19 is rotated via the connection pins 7 and the like. The swash plate 20 is oscillated in the front-rear direction by the rotational movement of the rotary support 19 while being kept at the minimum inclination angle equal to zero capacity, and the piston 9 is moved forward and backward by the rod 21 through the minimum stroke. Is rocked by. Therefore, the compressor is started with the minimum capacity, the shock is alleviated and the noise is reduced, and the load acting on the electromagnetic clutch or the engine is reduced, and their durability is improved.
【００２９】圧縮機が最小容量で運転を開始するとシリ
ンダボア１ａ内の各作動室１０は吸入行程と圧縮行程を
繰り返す。このため各ピストン９の背面に作用するクラ
ンク室圧力Ｐｃよりも前面に作用する作動室１０の圧力
Ｐｂの方が大きくなり、斜板２０の傾斜角が増大され、
圧縮機の吐出容量が増大し、冷房負荷が高い場合には斜
板２０の傾斜角が図３に示すように最大となって、最大
容量運転となる。なお、この圧縮機の運転中に容量制御
弁２８を開閉して前記クランク室圧力Ｐｃを調整するこ
とにより、冷房負荷に応じて吐出容量を調整することが
できる。When the compressor starts operating with the minimum capacity, each working chamber 10 in the cylinder bore 1a repeats the suction stroke and the compression stroke. Therefore, the pressure Pb of the working chamber 10 acting on the front surface is larger than the crank chamber pressure Pc acting on the back surface of each piston 9, and the inclination angle of the swash plate 20 is increased.
When the discharge capacity of the compressor increases and the cooling load is high, the inclination angle of the swash plate 20 becomes maximum as shown in FIG. 3, and maximum capacity operation is performed. The discharge capacity can be adjusted according to the cooling load by opening and closing the capacity control valve 28 during operation of the compressor to adjust the crank chamber pressure Pc.
【００３０】圧縮機の最大容量運転中に何らかの理由に
より圧縮機の電磁クラッチがオフされると、圧縮機は図
３の最大容量状態で停止される。このとき各吸入弁７ａ
は図１に示すように停止状態で傾斜してバルブプレート
３の弁座Ｓ1 との間に放圧通路３３を形成するので、各
作動室１０内に残留した高圧冷媒ガスが吸入室５側に放
圧通路３３を通して放出される。従って、全てのピスト
ン９の前面に作用する作動室１０内圧力Ｐｂが吸入圧力
Ｐｓに低下されて、バネ２４の付勢力による斜板２０の
最大傾斜位置（図３）から最小傾斜位置（図４）への復
帰が速やかに行われる。この結果、電磁クラッチをオン
して圧縮機を早期に再起動してもそのショックが緩和さ
れて、騒音の発生が低減され、電磁クラッチやエンジン
等の耐久性が向上する。If the electromagnetic clutch of the compressor is turned off for some reason during the maximum capacity operation of the compressor, the compressor is stopped in the maximum capacity state shown in FIG. At this time, each suction valve 7a
1 is inclined in the stopped state to form the pressure release passage 33 between the valve plate 3 and the valve seat S 1 , so that the high pressure refrigerant gas remaining in each working chamber 10 is sucked into the suction chamber 5 side. Is discharged through the pressure release passage 33. Therefore, the pressure Pb in the working chamber 10 acting on the front surface of all the pistons 9 is reduced to the suction pressure Ps, and the swash plate 20 is biased by the spring 24 from the maximum tilt position (FIG. 3) to the minimum tilt position (FIG. 4). ) To return promptly. As a result, even if the electromagnetic clutch is turned on and the compressor is restarted early, the shock is alleviated, noise is reduced, and the durability of the electromagnetic clutch, engine, etc. is improved.
【００３１】さらに、前記実施例ではバルブプレート３
の弁座Ｓ1 に粗面３ｃを形成したが、この場合には圧縮
機の停止と同時に弁座Ｓ1 に潤滑油が付着していても該
弁座Ｓ1 からから吸入弁７ａが離れ易い。このため粗面
３ｃを形成しない場合と比較して作動室１０内の圧力Ｐ
ｂを迅速に低下して、起動ショックを緩和する動作の信
頼性を向上することができる。Further, in the above embodiment, the valve plate 3
The rough surface 3c is formed on the valve seat S 1 of the above , but in this case, even if the lubricating oil adheres to the valve seat S 1 at the same time when the compressor is stopped, the intake valve 7a is easily separated from the valve seat S 1. . Therefore, the pressure P in the working chamber 10 is higher than that in the case where the rough surface 3c is not formed.
It is possible to reduce b rapidly and improve the reliability of the operation for reducing the starting shock.
【００３２】次に、この発明を具体化した第２実施例を
図６に基づいて説明する。この第２実施例においては前
記バルブプレート３に凹部３ｄを形成し、該凹部３ｄの
底面に傾斜状態の弁座Ｓ1 を形成するとともに、吸入弁
７ａを該プレート３と平行になるようにしている。弁座
Ｓ1 には粗面３ｃが形成されている。又、圧縮機の停止
状態では前記弁座Ｓ1 と吸入弁７ａとの間に放圧通路３
３が形成されるようにしている。その他の構成は前述し
た第１実施例と同様である。Next, a second embodiment of the present invention will be described with reference to FIG. In the second embodiment, a concave portion 3d is formed in the valve plate 3, an inclined valve seat S 1 is formed on the bottom surface of the concave portion 3d, and the intake valve 7a is made parallel to the plate 3. There is. A rough surface 3c is formed on the valve seat S 1 . Further, when the compressor is stopped, the pressure release passage 3 is provided between the valve seat S 1 and the suction valve 7a.
3 is formed. The other structure is similar to that of the first embodiment described above.
【００３３】従って、この実施例では圧縮機の運転中は
作動室１０が圧縮行程に入ると、吸入弁７ａが凹部３ｄ
の弁座Ｓ1 に接触してシール性を確保する。圧縮機が停
止されると、吸入弁７ａが弁座Ｓ1 から離隔して放圧通
路３３が形成されて、作動室１０内の高圧の冷媒ガスが
吸入室５へ放出される。このため斜板２０が最小傾斜角
位置に速やかに復帰され、早期に圧縮機を再起動した場
合のショックが緩和される。Therefore, in this embodiment, when the working chamber 10 enters the compression stroke during operation of the compressor, the suction valve 7a is depressed into the recess 3d.
The valve seat S 1 is contacted to secure the sealing property. When the compressor is stopped, the suction valve 7a is separated from the valve seat S 1 to form the pressure release passage 33, and the high pressure refrigerant gas in the working chamber 10 is discharged to the suction chamber 5. Therefore, the swash plate 20 is quickly returned to the minimum tilt angle position, and the shock caused when the compressor is restarted early is reduced.
【００３４】次に、この発明を具体化した第３実施例を
図７に基づいて説明する。この実施例では圧縮機の停止
状態で吸入弁７ａが弁座Ｓ1 に接触されている。弁座Ｓ
1 の表面には粗面３ｃが形成され、この粗面３ｃにより
弁座Ｓ1 と吸入弁７ａとの接触界面に放圧通路３３が形
成されている。前記粗面３ｃは吸入弁７ａ側に形成して
も、両者にそれぞれ形成してもよい。その他の構成は前
記第一実施例と同様である。Next, a third embodiment of the present invention will be described with reference to FIG. In this embodiment, the suction valve 7a is in contact with the valve seat S 1 when the compressor is stopped. Valve seat S
A rough surface 3c is formed on the surface of 1, and a pressure release passage 33 is formed at the contact interface between the valve seat S 1 and the suction valve 7a by the rough surface 3c. The rough surface 3c may be formed on the suction valve 7a side or on both sides. The other structure is the same as that of the first embodiment.
【００３５】この実施例では圧縮機が停止された直後に
作動室１０内の高圧ガスが放圧通路３３を通して吸入室
５へ放出される。このため斜板２０が最小傾斜角位置に
速やかに復帰され、早期に圧縮機を再起動した場合のシ
ョックが緩和される。又、この実施例では吸入弁７ａを
曲げ加工する必要はなく、ショットブラスト等により弁
座Ｓ1 に粗面３ｃを形成するのみで済むため、加工が容
易となる。なお、この実施例における放圧通路３３は圧
縮行程において、作動室１０からガスが吸入室５へ漏洩
するので、シール性を考慮して粗面３ｃの粗さを２０〜
３０μｍＲｚに設定するのが望ましい。In this embodiment, the high-pressure gas in the working chamber 10 is discharged into the suction chamber 5 through the pressure release passage 33 immediately after the compressor is stopped. Therefore, the swash plate 20 is quickly returned to the minimum tilt angle position, and the shock caused when the compressor is restarted early is reduced. Further, in this embodiment, the suction valve 7a does not need to be bent, and only the rough surface 3c is formed on the valve seat S 1 by shot blasting or the like, which facilitates the processing. In the pressure release passage 33 in this embodiment, gas leaks from the working chamber 10 to the suction chamber 5 in the compression stroke, so that the roughness of the rough surface 3c is 20 to 20 in consideration of the sealing property.
It is desirable to set to 30 μmRz.
【００３６】次に、この発明を具体化した第４実施例を
図８及び図９に基づいて説明する。この実施例では図９
に示すように、吐出弁８ａが接触する弁座Ｓ2 に対し該
弁座Ｓ2 からの弁８ａの離隔動作を円滑に行い、騒音を
低減するための粗面３ｅを形成し、バルブプレート３と
吐出弁８ａとの接触界面に前記粗面３ｅによる隙間３４
を形成している。さらに、前記吐出室６に接続された外
部吐出管路３２に逆止弁３５を配設している。前記粗面
３ｅの粗さはシール性を考慮して１０〜２０μｍＲｚに
するのが望ましく、加工方法はショットブラスト等であ
る。この第３実施例において前記第１実施例と同様の機
能を有する部材については、同一の符号を付している。Next, a fourth embodiment embodying the present invention will be described with reference to FIGS. 8 and 9. In this embodiment, FIG.
As shown in FIG. 3, the valve seat S 2 that comes into contact with the discharge valve 8 a smoothly separates the valve 8 a from the valve seat S 2 , forms a rough surface 3 e for reducing noise, and forms the valve plate 3 At the contact interface between the discharge valve 8a and the discharge valve 8a.
Is formed. Further, a check valve 35 is arranged in the external discharge pipe line 32 connected to the discharge chamber 6. The roughness of the rough surface 3e is preferably 10 to 20 μmRz in consideration of the sealing property, and the processing method is shot blasting or the like. In the third embodiment, members having the same functions as those in the first embodiment are designated by the same reference numerals.
【００３７】従って、第４実施例では圧縮機が図８に示
すような最大容量状態で停止されると、吐出室６内の高
圧の冷媒ガスが粗面３ｅにより形成された隙間３４から
作動室１０内に進入する。又、逆止弁３５により外部吐
出管路３２から継続して前記吐出室６内にガスが流入す
ることはない。従って、吐出室６及び作動室１０内のガ
スは放圧通路３３を通して吸入室５へ素早く放出される
ので、斜板２０が最大傾斜角から最小傾斜角に速やかに
傾動される。Therefore, in the fourth embodiment, when the compressor is stopped in the maximum capacity state as shown in FIG. 8, the high pressure refrigerant gas in the discharge chamber 6 flows from the gap 34 formed by the rough surface 3e into the working chamber. Enter within 10. Further, the check valve 35 prevents the gas from continuously flowing into the discharge chamber 6 from the external discharge conduit 32. Therefore, the gas in the discharge chamber 6 and the working chamber 10 is quickly discharged to the suction chamber 5 through the pressure release passage 33, so that the swash plate 20 is swung quickly from the maximum tilt angle to the minimum tilt angle.
【００３８】なお、この発明は前記各実施例に限定され
るものではなく、次のように具体化することもできる。 （１）図１０に示すように、圧縮機の停止中では前記吸
入弁７ａを弁座Ｓ1 に対し傾斜するように形成して放圧
通路３３を形成すること。圧縮動作中では吸入弁７ａが
弾性変形して弁座Ｓ1 に接触し、吸入ポート３ａのシー
ルが行われる。The present invention is not limited to the above embodiments, but can be embodied as follows. (1) As shown in FIG. 10, while the compressor is stopped, the suction valve 7a is formed to incline with respect to the valve seat S 1 to form the pressure release passage 33. Intake valve 7a is in compression operation is in contact with the valve seat S 1 is elastically deformed, the seal of the suction port 3a is performed.
【００３９】（２）図１１に示すように吸入弁７ａをバ
ルブプレート３と平行に形成し、前述した凹部３ｄの底
面に形成した弁座Ｓ1 を傾斜すること。この実施例では
圧縮動作中に吸入弁７ａが傾斜して弁座Ｓ1 に接触して
吸入ポート３ａが閉鎖される。(2) As shown in FIG. 11, the intake valve 7a is formed in parallel with the valve plate 3, and the valve seat S 1 formed on the bottom surface of the recess 3d is inclined. In this embodiment, during the compression operation, the intake valve 7a tilts and comes into contact with the valve seat S 1 to close the intake port 3a.
【００４０】（３）図１２に示すように吸入弁７ａをバ
ルブプレート３の表面に形成した突起３ｆにより傾斜状
態に保持すること。この別例では圧縮機が停止された場
合に、弁座Ｓ1 から吸入弁７ａが傾斜状態となって放圧
通路３３が形成され、作動室１０内のガスが通路３３か
ら吸入室５に排出される。(3) As shown in FIG. 12, the suction valve 7a is held in an inclined state by the projection 3f formed on the surface of the valve plate 3. In this another example, when the compressor is stopped, the suction valve 7a is inclined from the valve seat S 1 to form the pressure release passage 33, and the gas in the working chamber 10 is discharged from the passage 33 to the suction chamber 5. To be done.
【００４１】（４）図１０〜１２において弁座Ｓ1 に粗
面３ｃを形成すること。 （５）図示しないが前述した粗面３ｃ，３ｅに代えて細
い溝を弁座Ｓ1 ，Ｓ2あるい吸入弁７ａ、吐出弁８ａに
例えば放射状に形成すること。(4) To form a rough surface 3c on the valve seat S 1 in FIGS. (5) Although not shown, thin grooves may be formed in the valve seats S 1 and S 2 or the intake valve 7a and the discharge valve 8a, for example, radially instead of the rough surfaces 3c and 3e.
【００４２】（６）図示しないが前述した粗面３ｅを吐
出弁８ａ側に形成すること。 （７）前記実施例では斜板２０が非回転で前後に揺動す
る方式の斜板式可変容量圧縮機に具体化したが、これに
代えて回転斜板にピストン９を係留した方式の斜板式可
変容量圧縮機に具体化すること。(6) Although not shown, the aforementioned rough surface 3e should be formed on the discharge valve 8a side. (7) In the above embodiment, the swash plate 20 is a non-rotating swash plate type variable displacement compressor that swings back and forth. However, instead of this, a swash plate type swash plate type in which the piston 9 is moored to the rotating swash plate is used. Be embodied in a variable capacity compressor.
【００４３】[0043]
【発明の効果】以上詳述したように、請求項１記載の発
明は圧縮機が停止された後、斜板の最小傾斜角への移動
を迅速に行い、圧縮機を早期に再起動した場合のショッ
クを緩和して電磁クラッチの耐久性を向上し、騒音をさ
らに低減することができる。As described above in detail, according to the first aspect of the present invention, after the compressor is stopped, the swash plate is quickly moved to the minimum inclination angle and the compressor is restarted early. It is possible to reduce the shock and improve the durability of the electromagnetic clutch and further reduce the noise.
【００４４】請求項２，３記載の発明は、請求項１記載
の発明に加えて、製造を容易に行いコストダウンを実現
することができる。請求項４，５記載の発明は請求項１
記載の発明の効果に加えて、圧縮機が停止された後、斜
板の最小傾斜角への移動をさらに迅速に行い、圧縮機を
早期に再起動した場合のショックをさらに緩和して電磁
クラッチ等の耐久性を向上し、騒音を一層低減すること
ができる。In addition to the invention described in claim 1, the inventions described in claims 2 and 3 can easily manufacture and realize cost reduction. The invention described in claims 4 and 5 is claim 1
In addition to the effects of the described invention, after the compressor is stopped, the swash plate is moved to the minimum inclination angle more quickly, and the shock in the case of restarting the compressor early is further alleviated and the electromagnetic clutch It is possible to improve durability such as, and further reduce noise.
【００４５】さらに、請求項６記載の発明は請求項１〜
５記載のいずれかの発明の効果に加えて騒音をさらに低
減することができる。Further, the invention according to claim 6 is defined by claims 1 to 1.
In addition to the effect of any one of the inventions described in 5, it is possible to further reduce noise.
【図１】この発明を具体化した第１実施例の斜板式可変
容量圧縮機の要部を示す部分断面図である。FIG. 1 is a partial cross-sectional view showing a main part of a swash plate type variable displacement compressor according to a first embodiment of the present invention.
【図２】要部の分解斜視図である。FIG. 2 is an exploded perspective view of a main part.
【図３】斜板式可変容量圧縮機の最大容量状態の縦断面
図である。FIG. 3 is a longitudinal sectional view of a swash plate type variable displacement compressor in a maximum displacement state.
【図４】斜板式可変容量圧縮機の最小容量状態の縦断面
図である。FIG. 4 is a vertical sectional view of a swash plate type variable displacement compressor in a minimum displacement state.
【図５】図３のＡ−Ａ線断面図である。5 is a cross-sectional view taken along the line AA of FIG.
【図６】この発明の第２実施例を示す要部の断面図であ
る。FIG. 6 is a cross-sectional view of a main part showing a second embodiment of the present invention.
【図７】この発明の第３実施例を示す要部の断面図であ
る。FIG. 7 is a cross-sectional view of a main part showing a third embodiment of the present invention.
【図８】この発明の第４実施例を示す斜板式可変容量圧
縮機の最大容量状態の縦断面図である。FIG. 8 is a vertical sectional view of a swash plate type variable displacement compressor according to a fourth embodiment of the present invention in a maximum displacement state.
【図９】第４実施例の要部の断面図である。FIG. 9 is a sectional view of an essential part of the fourth embodiment.
【図１０】この発明の別例を示す部分断面図である。FIG. 10 is a partial cross-sectional view showing another example of the present invention.
【図１１】この発明の別例を示す部分断面図である。FIG. 11 is a partial cross-sectional view showing another example of the present invention.
【図１２】この発明の別例を示す部分断面図である。FIG. 12 is a partial cross-sectional view showing another example of the present invention.
１…シリンダブロック、１ａ…シリンダボア、２…フロ
ントハウジング、２ａ…クランク室、３…バルブプレー
ト、３ａ…吸入ポート、３ｂ…吐出ポート、３ｃ…粗
面、３ｄ…凹部、３ｅ…粗面、４…リヤハウジング、５
…吸入室、６…吐出室、７…吸入弁形成板、７ａ…吸入
弁、８…吐出弁形成板、８ａ…吐出弁、９…ピストン、
１３…回転軸、１５…回転駆動体、１９…回転支持体、
２０…斜板、２４…付勢手段としてのバネ、３３…放圧
通路、３４…隙間、３５…逆止弁、Ｓ1 …吸入ポート側
の弁座、Ｓ2 …吐出ポート側の弁座。1 ... Cylinder block, 1a ... Cylinder bore, 2 ... Front housing, 2a ... Crank chamber, 3 ... Valve plate, 3a ... Suction port, 3b ... Discharge port, 3c ... Rough surface, 3d ... Recessed part, 3e ... Rough surface, 4 ... Rear housing, 5
... suction chamber, 6 ... discharge chamber, 7 ... suction valve forming plate, 7a ... suction valve, 8 ... discharge valve forming plate, 8a ... discharge valve, 9 ... piston,
13 ... Rotation shaft, 15 ... Rotation drive member, 19 ... Rotation support member,
20 ... swash plate, spring as 24 ... urging means 33 ... pressure release passage, 34 ... clearance, 35 ... check valve, S 1 ... valve seat of the intake port side, S 2 ... discharge port side of the valve seat.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 廣田 英 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 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hideta Hirota 2-1-1 Toyota-cho, Kariya-shi, Aichi Stock Company Toyota Industries Corp.
Claims (6)
ンク室を備え、回転軸に対してシリンダボア内に収容し
た複数のピストンを往復動させるための斜板を前記クラ
ンク室内で傾動可能に装着し、前記ピストンのストロー
クに比例する前記斜板の傾斜角を容量制御機構により変
化させて冷媒ガスの吐出容量を制御するとともに、回転
軸の停止状態で前記斜板の傾斜角を最小容量となる最小
傾斜角に復帰する付勢手段を備えた斜板式可変容量圧縮
機において、 前記吸入室とシリンダボアを連通する吸入ポートを開閉
する弾性材よりなる板状の吸入弁と、該吸入弁が接触す
る弁座との間に、圧縮機の停止状態でシリンダボア内の
圧力を吸入室へ逃すための放圧通路を設けた斜板式可変
容量圧縮機。1. A swash plate for reciprocating a plurality of pistons housed in a cylinder bore with respect to a rotating shaft, the swash plate having a suction chamber, a discharge chamber and a crank chamber in a housing, the tilt plate being tiltably mounted in the crank chamber. The inclination angle of the swash plate, which is proportional to the stroke of the piston, is controlled by a capacity control mechanism to control the discharge capacity of the refrigerant gas, and the inclination angle of the swash plate becomes the minimum capacity when the rotating shaft is stopped. In a swash plate type variable displacement compressor provided with a biasing means for returning to a tilt angle, a plate-shaped suction valve made of an elastic material for opening and closing a suction port communicating the suction chamber and a cylinder bore, and a valve for contacting the suction valve A swash plate type variable displacement compressor having a pressure release passage between the seat and the seat for releasing the pressure in the cylinder bore to the suction chamber when the compressor is stopped.
ポートを形成した弁座から吸入弁を離隔し、弁座と吸入
弁との隙間により形成されたものである斜板式可変容量
圧縮機。2. The swash plate type variable displacement compressor according to claim 1, wherein the pressure release passage is formed by separating a suction valve from a valve seat forming a suction port and forming a gap between the valve seat and the suction valve. .
に形成した凹部の底面と吸入弁との隙間により形成され
ている斜板式可変容量圧縮機。3. The swash plate type variable displacement compressor according to claim 1, wherein the pressure release passage is formed by a gap between a bottom surface of a recess formed in a valve seat and an intake valve.
又は吸入弁に形成された粗面によって弁座と吸入弁との
間に着座状態で生ずる隙間により形成されている斜板式
可変容量圧縮機。4. The swash plate type variable capacity according to claim 1, wherein the pressure release passage is formed by a gap formed in a seated state between the valve seat and the intake valve by a rough surface formed on the valve seat or the intake valve. Compressor.
該弁と接触する弁座には粗面が形成されている斜板式可
変容量圧縮機。5. The swash plate type variable displacement compressor according to claim 2 or 3, wherein a rough surface is formed on the suction valve or a valve seat contacting the valve.
記シリンダボア内と吐出室を連通する吐出ポートを開閉
する板状の吐出弁が着座する弁座に粗面を形成し、吐出
室に連通する外部吐出管路に逆止弁を設けた斜板式可変
容量圧縮機。6. A rough surface is formed on a valve seat on which a plate-shaped discharge valve for opening and closing a discharge port that connects the inside of the cylinder bore and the discharge chamber is formed with a rough surface, and the discharge chamber is provided in the discharge chamber according to claim 1. A swash plate type variable displacement compressor with a check valve installed in the communicating external discharge line.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25196793A JP3326909B2 (en) | 1993-10-07 | 1993-10-07 | Swash plate type variable displacement compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25196793A JP3326909B2 (en) | 1993-10-07 | 1993-10-07 | Swash plate type variable displacement compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07103138A true JPH07103138A (en) | 1995-04-18 |
| JP3326909B2 JP3326909B2 (en) | 2002-09-24 |
Family
ID=17230664
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25196793A Expired - Fee Related JP3326909B2 (en) | 1993-10-07 | 1993-10-07 | Swash plate type variable displacement compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3326909B2 (en) |
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|---|---|---|---|---|
| EP0911522A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Swash plate type compressor |
| EP0911521A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Arrangement of lubrication fluid grooves in a rotating drive plate for a swash plate compressor |
| EP0911518A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Sealing for the housing of a swash plate compressor |
| EP0911520A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Swash plate |
| EP0962655A2 (en) | 1998-06-05 | 1999-12-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston-type compressor inlet valve |
| US6146110A (en) * | 1997-10-21 | 2000-11-14 | Calsonic Corporation | Swash plate type compressor |
| US6162025A (en) * | 1997-10-21 | 2000-12-19 | Calsonic Kansei Corporation | Variable displacement swash plate type compressor |
| WO2005033510A1 (en) * | 2003-09-30 | 2005-04-14 | Calsonic Kansei Corporation | Compressor and suction valve structure |
| KR100625264B1 (en) * | 2003-08-27 | 2006-09-20 | 할덱스 브레이크 코포레이션 | Pump valve assembly |
| KR100676744B1 (en) * | 1999-12-30 | 2007-01-31 | 한라공조주식회사 | Valve unit for compressor |
| WO2011046106A1 (en) | 2009-10-13 | 2011-04-21 | カルソニックカンセイ株式会社 | Compressor |
| KR101452487B1 (en) * | 2008-01-29 | 2014-10-21 | 한라비스테온공조 주식회사 | Compressor |
| WO2017169642A1 (en) * | 2016-03-30 | 2017-10-05 | 株式会社豊田自動織機 | Variable-displacement swash-plate-type compressor |
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| CN102713289B (en) | 2010-01-28 | 2015-01-14 | 株式会社丰田自动织机 | Compressor |
-
1993
- 1993-10-07 JP JP25196793A patent/JP3326909B2/en not_active Expired - Fee Related
Cited By (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6095030A (en) * | 1997-10-21 | 2000-08-01 | Calsonic Corporation | Swash plate variable displacement compressor |
| US6146110A (en) * | 1997-10-21 | 2000-11-14 | Calsonic Corporation | Swash plate type compressor |
| EP0911518A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Sealing for the housing of a swash plate compressor |
| EP0911520A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Swash plate |
| EP0911518A3 (en) * | 1997-10-21 | 1999-07-07 | Calsonic Corporation | Sealing for the housing of a swash plate compressor |
| EP0911522A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Swash plate type compressor |
| EP0911521A2 (en) | 1997-10-21 | 1999-04-28 | Calsonic Corporation | Arrangement of lubrication fluid grooves in a rotating drive plate for a swash plate compressor |
| US6179571B1 (en) | 1997-10-21 | 2001-01-30 | Calsonic Kansei Corporation | Swash plate type compressor |
| US6162025A (en) * | 1997-10-21 | 2000-12-19 | Calsonic Kansei Corporation | Variable displacement swash plate type compressor |
| US6158325A (en) * | 1997-10-21 | 2000-12-12 | Calsonic Corporation | Swash plate type variable displacement compressor |
| US6120259A (en) * | 1997-10-21 | 2000-09-19 | Calsonic Corporation | Swash plate type compressor |
| EP0962655A2 (en) | 1998-06-05 | 1999-12-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston-type compressor inlet valve |
| KR100676744B1 (en) * | 1999-12-30 | 2007-01-31 | 한라공조주식회사 | Valve unit for compressor |
| KR100625264B1 (en) * | 2003-08-27 | 2006-09-20 | 할덱스 브레이크 코포레이션 | Pump valve assembly |
| WO2005033510A1 (en) * | 2003-09-30 | 2005-04-14 | Calsonic Kansei Corporation | Compressor and suction valve structure |
| KR101452487B1 (en) * | 2008-01-29 | 2014-10-21 | 한라비스테온공조 주식회사 | Compressor |
| WO2011046106A1 (en) | 2009-10-13 | 2011-04-21 | カルソニックカンセイ株式会社 | Compressor |
| US10655580B2 (en) | 2014-10-09 | 2020-05-19 | Hitachi Automotive Systems, Ltd. | High pressure fuel supply pump |
| WO2017169642A1 (en) * | 2016-03-30 | 2017-10-05 | 株式会社豊田自動織機 | Variable-displacement swash-plate-type compressor |
| KR20220142350A (en) * | 2021-04-14 | 2022-10-21 | 웬-산 초우 | Piston of air compressor cylinder |
| US11905945B2 (en) | 2021-04-14 | 2024-02-20 | Wen-San Chou | Piston of air compressor |
| KR20220143570A (en) * | 2021-04-16 | 2022-10-25 | 웬-산 초우 | Air compressor device |
| KR20220143571A (en) * | 2021-04-16 | 2022-10-25 | 웬-산 초우 | Air compressor |
| KR20220145266A (en) * | 2021-04-21 | 2022-10-28 | 웬-산 초우 | Porous piston body in air compressor cylinder |
| KR20220145765A (en) * | 2021-04-22 | 2022-10-31 | 웬-산 초우 | Air inlet barrier plate on cylinder piston body |
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|---|---|
| JP3326909B2 (en) | 2002-09-24 |
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