JPH05981U - Reciprocating compressor valve device - Google Patents
Reciprocating compressor valve deviceInfo
- Publication number
- JPH05981U JPH05981U JP4814591U JP4814591U JPH05981U JP H05981 U JPH05981 U JP H05981U JP 4814591 U JP4814591 U JP 4814591U JP 4814591 U JP4814591 U JP 4814591U JP H05981 U JPH05981 U JP H05981U
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- Prior art keywords
- valve
- valve body
- retainer
- port
- 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.)
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
(57)【要約】
【目的】 動力損失を極力低減しつつ、弁体の戻り遅れ
に起因する体積効率の低下を極力防止する。
【構成】 吸入ポート６ａが開口された平坦な弁座面６
ｂと、弁座面に離隔対向するリテーナ２６とを含んだ弁
室６ｃ内に、平板状弁体２７を遊装する。リテーナは、
リング部２６ａと弁室の外周にそってほぼ等間隔に４個
形成された舌片部２６ｂとからなり、各舌片部の弁体側
の面には弁体との接触面積を縮小させる小突子２６ｃが
形成されている。弁体は、ポートを挟む領域の差圧のみ
に応じてポートを開閉する。弁体とリテーナとの接触面
積が小さく、弁体の戻り遅れが抑えられる。
(57) [Abstract] [Purpose] To reduce the power loss as much as possible and prevent the volume efficiency from being lowered due to the delay in the return of the valve body. [Structure] Flat valve seat surface 6 with an intake port 6a opened
A flat plate-shaped valve element 27 is mounted in a valve chamber 6c that includes b and a retainer 26 that faces the valve seat surface. Retainer
It is composed of a ring portion 26a and four tongue pieces 26b formed at substantially equal intervals along the outer circumference of the valve chamber, and a small protrusion that reduces the contact area with the valve body on the valve body side surface of each tongue piece. The child 26c is formed. The valve body opens and closes the port only in accordance with the pressure difference between the regions sandwiching the port. The contact area between the valve body and the retainer is small, and the return delay of the valve body is suppressed.
Description
【０００１】[0001]
本考案は、車両空調用に供して好適な往復動式圧縮機の弁装置に関する。 The present invention relates to a valve device for a reciprocating compressor suitable for air conditioning of a vehicle.
【０００２】[0002]
従来の往復動式圧縮機の弁装置としてリード弁が用いられており、図９に示す ように、吐出弁においては冷媒が圧縮されるボア１００と吐出室１０３とを仕切 る弁板１０５にポート１０６を形成するとともに、弁板１０５に板ばね状の弁１ ０７およびリテーナ１０９を共締めしたものが知られている。このようなリード 弁形式の弁装置では、常時閉弁状態であり、ボア１００と吐出室１０３との差圧 が開弁圧以上になると、弁１０７はポート１０６から離れて開弁するように設定 されている。開弁すると、ボア１００内で圧縮された冷媒はポート１０６を通り 吐出室１０３に吐出される。なお、弁１０７の開弁度はリテーナ１０９により規 制される。 A reed valve is used as a valve device of a conventional reciprocating compressor, and as shown in FIG. 9, in a discharge valve, a port is provided on a valve plate 105 that separates a bore 100 in which a refrigerant is compressed from a discharge chamber 103. It is known that a valve spring 105 and a retainer 109 are fastened together with the valve plate 105 while forming the valve 106. In such a reed valve type valve device, the valve is normally closed, and when the pressure difference between the bore 100 and the discharge chamber 103 becomes equal to or higher than the valve opening pressure, the valve 107 is set to open apart from the port 106. Has been done. When the valve is opened, the refrigerant compressed in the bore 100 is discharged into the discharge chamber 103 through the port 106. The opening degree of the valve 107 is regulated by the retainer 109.
【０００３】[0003]
ところで、上記リード弁形式の弁装置は、前述したように、常時閉弁状態であ り、ボア１００と吐出室１０３との差圧が弁１０７の所定の開弁圧を越えると、 弁１０７は始めて開弁する。すなわち、弁１０７は、ボア１００と吐出室１０３ との差圧による弁１０７を開けようとする力が、弁１０７の弾性力よりも大きく なったとき始めて開弁する。このため、吐出の際に上記弾性力による抵抗が大き いことから、冷媒は過圧縮となり動力損失を許容しなければならなかった。 As described above, the reed valve type valve device is always closed, and when the pressure difference between the bore 100 and the discharge chamber 103 exceeds the predetermined valve opening pressure of the valve 107, the valve 107 is opened. Open the valve for the first time. That is, the valve 107 opens only when the force to open the valve 107 due to the pressure difference between the bore 100 and the discharge chamber 103 becomes larger than the elastic force of the valve 107. For this reason, since the resistance due to the elastic force is large at the time of discharge, the refrigerant must be over-compressed and power loss must be allowed.
【０００４】 また、弁１０７は上述のように開弁の際の応答性が悪く、吐出圧の脈動が生じ やすい。 これらの不具合を避けるべく、ポートが開口された平坦な弁座面と、弁座面に 離隔対向するリテーナとを含んで囲包された弁室を形成し、この弁室内にポート を挟む領域の差圧に応じて該ポートを開閉する平板状弁体を遊装する手段を採用 することもできる。しかし、このようなフロート弁形式の弁装置では、上記従来 のリード弁形式の弁装置と比べて、吐出弁における弁体の吸入時の戻り遅れや、 吸入弁における弁体の吐出時の戻り遅れが発生しやすい。これは、冷媒中に含ま れる潤滑油などにより、弁体がリテーナ面に密着して剥がれ難くなるためである 。したがって、このような弁体の戻り遅れにより圧縮機の体積効率が低下すると いう不都合が生じる場合がある。Further, the valve 107 has poor responsiveness when opened as described above, and pulsation of the discharge pressure is likely to occur. In order to avoid these problems, a valve chamber surrounded by a flat valve seat surface with an open port and a retainer facing the valve seat surface is formed, and a region sandwiching the port is formed in the valve chamber. It is also possible to employ means for loosely mounting a flat plate-shaped valve element that opens and closes the port according to the differential pressure. However, in such a float valve type valve device, as compared with the above-mentioned conventional reed valve type valve device, the return delay when the valve body is sucking in the discharge valve and the return delay when the valve body is discharging in the suction valve are delayed. Is likely to occur. This is because the lubricating oil contained in the refrigerant causes the valve element to come into close contact with the retainer surface and become difficult to peel off. Therefore, such a delay in return of the valve element may cause a disadvantage that the volumetric efficiency of the compressor is reduced.
【０００５】 本考案は、動力損失及び吐出脈動を極力低減し、しかも上記フロート弁形式の 弁装置における弁体の戻り遅れに起因する体積効率の低下を極力防止することを 解決すべき技術課題とするものである。The present invention aims to reduce the power loss and the discharge pulsation as much as possible, and further, to prevent the volume efficiency from being lowered due to the return delay of the valve body in the float valve type valve device. To do.
【０００６】[0006]
本考案の往復動式圧縮機の弁装置は、ポートが開口された平坦な弁座面と、該 弁座面に離隔対向するリテーナとを含んで囲包された弁室を形成し、該弁室内に 該ポートを挟む領域の差圧に応じて該ポートを開閉する平板状弁体を遊装してな り、前記リテーナと前記平板状弁体との接触が、両者の接触面積を縮小させる突 状部によりなされることを特徴とする。 The reciprocating compressor valve device of the present invention forms a valve chamber surrounded by a flat valve seat surface having an open port and a retainer facing the valve seat surface. A flat plate valve element that opens and closes the port is loosely mounted in the chamber according to the pressure difference between the areas sandwiching the port, and the contact between the retainer and the flat plate valve element reduces the contact area between them. It is characterized in that it is made by a protrusion.
【０００７】 上記突状部は、リテーナと平板状弁体とを、巨視的にみて点接触又は線接触さ せるものであり、両者の接触面積が極小となるように面接触させるものも含む。[0007] The above-mentioned projecting portion makes the retainer and the plate-shaped valve body macroscopically in point contact or in line contact, and also includes those in surface contact so that the contact area between them is minimized.
【０００８】[0008]
本考案の弁装置においては、ポートを挟む領域において差圧が生じると、その 差圧に応じて平板状弁体は弁室内で移動し、これにより弁体が弁座面に着座して ポートを閉じたり、弁体が弁座面から離れてポートを開き、リテーナに当たった りする。 In the valve device of the present invention, when a differential pressure is generated in the area sandwiching the port, the flat valve body moves in the valve chamber according to the differential pressure, whereby the valve body is seated on the valve seat surface and the port is closed. The valve may close or the valve may move away from the valve seat surface, open the port, and hit the retainer.
【０００９】 このように、弁体がポートを挟む領域の差圧のみに応じて弁体が該ポートを開 閉するので、開弁の際の応答性が向上し、冷媒の過圧縮による動力損失や吐出脈 動を低減できる。 また、リテーナと平板状弁体との接触が突状部によりなさるので、両者の接触 面積が縮小される。このため、冷媒中に含まれる潤滑油などにより平板状弁体が リテーナに密着して剥がれ難くなることを防止でき、平板状弁体の戻り遅れに起 因して圧縮機の体積効率が低下することを防止できる。As described above, since the valve body opens and closes the port only in accordance with the pressure difference in the region where the valve body sandwiches the port, the responsiveness at the time of opening the valve is improved and the power loss due to the overcompression of the refrigerant is lost. And discharge pulsation can be reduced. Further, since the retainer and the flat plate-shaped valve body are brought into contact with each other by the projecting portion, the contact area between them is reduced. For this reason, it is possible to prevent the flat valve element from coming into close contact with the retainer and becoming difficult to peel off due to the lubricating oil contained in the refrigerant, and the volume efficiency of the compressor decreases due to the delay in the return of the flat valve element. Can be prevented.
【００１０】[0010]
以下、本考案を具体化した実施例を図面を参照しつつ説明する。 この斜板式圧縮機は、図１に示すように、一対のシリンダブロック１、２が前 後に対設されて結合部分に帰還冷媒の吸入口３と連通する斜板室４を形成してい る。各シリンダブロック１、２はその両端をそれぞれアルミ合金系の弁板５、６ を介してフロントハウジング７及びリアハウジング８により閉塞されている。フ ロントハウジング７及びリアハウジング８には、径内側に吸入室９、１０が形成 され、径外側にリング状の吐出室１１、１２が形成されている。なお、吸入室９ 、１０はそれぞれ吸入通路１６、１７により斜板室４と連通している。 Embodiments embodying the present invention will be described below with reference to the drawings. In this swash plate compressor, as shown in FIG. 1, a pair of cylinder blocks 1 and 2 are provided in front of and behind each other to form a swash plate chamber 4 communicating with a return refrigerant suction port 3 at a connecting portion. Both ends of each of the cylinder blocks 1 and 2 are closed by a front housing 7 and a rear housing 8 via aluminum alloy valve plates 5 and 6, respectively. In the front housing 7 and the rear housing 8, suction chambers 9 and 10 are formed on the radially inner side, and ring-shaped discharge chambers 11 and 12 are formed on the radially outer side. The suction chambers 9 and 10 communicate with the swash plate chamber 4 through suction passages 16 and 17, respectively.
【００１１】 各シリンダブロック１、２の共通中心軸孔には各シリンダブロック１、２との 間にラジアル軸受１４、１５を介して駆動軸１８が挿嵌されており、この駆動軸 １８はフロント側の弁板５の中心孔５ａを貫通しラジアル軸受１９及び軸封装置 ２０を介してフロントハウジング７に支承されている。駆動軸１８には斜板室４ 内を回転可能に斜板２３が固着されており、この斜板２３はスラスト軸受２１、 ２２を介して各シリンダブロック１、２に支承されている。また、各シリンダブ ロック１、２には駆動軸１８周りに平行状に配列した前後複数対のボア１ａ、２ ａが形成され、各ボア１ａ、２ａには斜板２３に一対のシュー２４、２４を介し て係留された両頭形のピストン２５が直動自在に嵌入されている。A drive shaft 18 is inserted into the common central shaft hole of each cylinder block 1 and 2 via radial bearings 14 and 15 between each cylinder block 1 and 2, and the drive shaft 18 is a front shaft. It penetrates through the central hole 5a of the valve plate 5 on the side and is supported by the front housing 7 via a radial bearing 19 and a shaft sealing device 20. A swash plate 23 is fixed to the drive shaft 18 so as to be rotatable in the swash plate chamber 4. The swash plate 23 is supported by the cylinder blocks 1 and 2 via thrust bearings 21 and 22, respectively. Further, a plurality of pairs of front and rear bores 1a, 2a arranged in parallel around the drive shaft 18 are formed in each cylinder block 1, 2, and each bore 1a, 2a has a pair of shoes 24, 24 on a swash plate 23. A double-headed piston 25 moored via is inserted in a freely movable manner.
【００１２】 フロント側の弁板５、及びリヤ側の弁板６は同じ構成をもっているので、リヤ 側の弁板６の構成について説明する。図２の部分断面図に示すように、リヤ側の 弁板６には、吸入ポート６ａが開口されたリング状の平坦な弁座面６ｂと、弁座 面６ｂに離隔対向するリテーナ２６とを含んで囲包された弁室６ｃが形成されて いる。弁室６ｃには平板状弁体２７が遊装されている。吸入ポート６ａは弁室６ ｃを介してボア２ａと吸入室１０とを連通している。また、リヤ側の弁板６には 、吐出ポート６ｈが開口されたリング状の平坦な弁座面６ｉと、弁座面６ｉに離 隔対向するリテーナ２６とを含んで囲包された弁室６ｊが形成されている。弁室 ６ｊには平板状弁体２８が遊装されている。吐出ポート６ｈは弁室６ｊを介して ボア２ａと吐出室１２とを連通している。Since the front side valve plate 5 and the rear side valve plate 6 have the same structure, the structure of the rear side valve plate 6 will be described. As shown in the partial cross-sectional view of FIG. 2, the rear valve plate 6 is provided with a ring-shaped flat valve seat surface 6b in which the suction port 6a is opened, and a retainer 26 facing away from the valve seat surface 6b. A valve chamber 6c is formed so as to be enclosed. A flat plate-shaped valve element 27 is mounted in the valve chamber 6c. The suction port 6a connects the bore 2a and the suction chamber 10 via the valve chamber 6c. Further, the valve plate 6 on the rear side is surrounded by a ring-shaped flat valve seat surface 6i having an opening for the discharge port 6h and a retainer 26 spaced apart from and facing the valve seat surface 6i. 6j is formed. A flat plate-shaped valve body 28 is mounted in the valve chamber 6j. The discharge port 6h connects the bore 2a and the discharge chamber 12 via the valve chamber 6j.
【００１３】 図３に図２のＡ矢視図を示すように、リテーナ２６は、リング部２６ａと、弁 室６ｊの外周にそってほぼ等間隔で４個形成された舌片部２６ｂとから構成され ている。そして、各舌片部２６ｂの先端には、平板状弁板２８と当接する側の面 にそれぞれ本考案の突状部をなす小突子２６ｃが設けられている。なお、リテー ナ２６は弁板６に形成された凹部６ｄに圧入又は溶接により固定されている。As shown in the view from the arrow A in FIG. 3, the retainer 26 includes a ring portion 26a and four tongue pieces 26b formed along the outer circumference of the valve chamber 6j at substantially equal intervals. It is configured. The tip of each tongue piece 26b is provided with a small protrusion 26c, which forms the projection of the present invention, on the surface that contacts the flat valve plate 28. The retainer 26 is fixed to the recess 6d formed in the valve plate 6 by press fitting or welding.
【００１４】 この斜板式圧縮機では、駆動軸１８が回転して斜板２３が回転すると、ピスト ン２５が各ボア１ａ、２ａ内を往復動し、ボア１ａ、２ａの容積拡大による吸入 行程、ボア１ａ、２ａの容積縮小による圧縮行程が交互に行われる。 上記吸入行程の際には、図示しない冷凍回路より吸入口３を介して斜板室４内 に帰還した帰還冷媒は、吸入通路１６、１７を通り、フロント側では吸入室９に 導出され、リヤ側では吸入室１０に導出される。ここで、ボア２ａが容積拡大し て吸入行程に至ったときを説明する。このときには、ボア２ａ内が減圧されるの で、差圧が生じ、リヤ側の弁体２７、２８はボア２ａ側に寄せられる。そのため 、吐出用の弁体２８は弁座面６ｉに着座し吐出ポート６ｈを閉じるとともに、吸 入用の弁体２７はリテーナ２６に当たり吸入ポート６ａを開口する。したがって 、吸入室１０の冷媒は吸入ポート６ａ、弁室６ｃを介して容積拡大途上のボア２ ａ内に吸入される。In this swash plate compressor, when the drive shaft 18 rotates and the swash plate 23 rotates, the piston 25 reciprocates in each of the bores 1a and 2a, and the suction stroke due to the expansion of the volume of the bores 1a and 2a. The compression strokes due to the volume reduction of the bores 1a, 2a are performed alternately. During the suction stroke, the return refrigerant that has returned from the refrigeration circuit (not shown) into the swash plate chamber 4 through the suction port 3 passes through the suction passages 16 and 17 and is led to the suction chamber 9 on the front side and the rear side. Is led to the suction chamber 10. Here, the case where the bore 2a expands in volume and reaches the suction stroke will be described. At this time, since the inside of the bore 2a is depressurized, a differential pressure is generated, and the valve elements 27, 28 on the rear side are brought close to the bore 2a side. Therefore, the discharge valve body 28 is seated on the valve seat surface 6i to close the discharge port 6h, and the suction valve body 27 hits the retainer 26 to open the suction port 6a. Therefore, the refrigerant in the suction chamber 10 is sucked into the bore 2a whose volume is being increased through the suction port 6a and the valve chamber 6c.
【００１５】 この後、ボア２ａが容積縮小するため、ボア２ａ内が増圧され、吐出用の弁体 ２８は吐出室１２側に、吸入用の弁体２７は吸入室１０側に寄せられる。そのた め、吸入用の弁体２７は弁座面６ｂに着座し吸入ポート６ａを閉じるとともに、 吐出用の弁体２８はリテーナ２６に当たり吐出ポート６ｈを開口する。したがっ て、ボア２ａ内の圧縮冷媒は吐出ポート６ｈ、弁室６ｊを介して吐出室１２に吐 出される。After that, since the volume of the bore 2a is reduced, the pressure inside the bore 2a is increased, and the valve body 28 for discharge is moved to the discharge chamber 12 side, and the valve body 27 for suction is moved to the suction chamber 10 side. Therefore, the suction valve element 27 is seated on the valve seat surface 6b to close the suction port 6a, and the discharge valve element 28 hits the retainer 26 to open the discharge port 6h. Therefore, the compressed refrigerant in the bore 2a is discharged to the discharge chamber 12 via the discharge port 6h and the valve chamber 6j.
【００１６】 なお、フロント側の弁板５についてもリヤ側の弁板６と同様に作用する。 そして、フロント側の吐出室１１内の圧縮冷媒は図示しない吐出通路を経てリ ア側の吐出室１２に集められ、リア側の吐出室１２内の圧縮冷媒は図示しない吐 出口から再び冷凍回路に循環される。 ここで、この斜板式圧縮機では、リテーナ２６と吸入用の弁体２７、吐出用の 弁体２８との接触がリテーナ２６の小突子２６ｃによりなさるので、両者の接触 面積が縮小される。このため、冷媒中に含まれる潤滑油などにより吸入用の弁体 ２７、吐出用の弁体２８がリテーナに密着して剥がれ難くなることを防止できる 。したがって、吸入用の弁体２７における吐出時の戻り遅れや、吐出用の弁体２ ８における吸入時の戻り遅れに起因して発生する圧縮機の体積効率の低下を防止 できる。The valve plate 5 on the front side operates in the same manner as the valve plate 6 on the rear side. Then, the compressed refrigerant in the front-side discharge chamber 11 is collected in the rear-side discharge chamber 12 through the discharge passage (not shown), and the compressed refrigerant in the rear-side discharge chamber 12 is returned to the refrigeration circuit from the discharge outlet (not shown). Circulated. Here, in this swash plate compressor, the retainer 26, the suction valve body 27, and the discharge valve body 28 are brought into contact with each other by the small protrusion 26c of the retainer 26, so that the contact area between them is reduced. For this reason, it is possible to prevent the valve element 27 for suction and the valve element 28 for discharge from coming into close contact with the retainer and being difficult to be peeled off due to the lubricating oil contained in the refrigerant. Therefore, it is possible to prevent a decrease in the volumetric efficiency of the compressor that is caused by the return delay of the suction valve body 27 at the time of discharge and the return delay of the discharge valve body 28 at the time of suction.
【００１７】 また、上述したように、リヤ側の弁板６（フロント側の弁板５も同様）の吸入 用の弁体２７、吐出用の弁体２８はボア２ａと吸入室１０、吐出室１２との差圧 のみに応じて往復動してリヤ側の吸入ポート６ａ、吐出ポート６ｈを開閉するの で、開弁の際の応答性が向上する。したがって、冷媒の過圧縮を低減又は回避す るのに有利であり、圧縮効率の向上を図ることが可能となる。また、吐出圧の脈 動を低減するのにも有利となる。Further, as described above, the valve element 27 for suction of the valve plate 6 on the rear side (the same applies to the valve plate 5 on the front side) and the valve element 28 for discharge are the bore 2a, the suction chamber 10, and the discharge chamber. Since the rear suction port 6a and the discharge port 6h are opened / closed by reciprocating only in accordance with the pressure difference between the valve 12 and 12, the responsiveness at the time of valve opening is improved. Therefore, it is advantageous to reduce or avoid overcompression of the refrigerant, and it is possible to improve the compression efficiency. It is also advantageous in reducing the pulsation of the discharge pressure.
【００１８】 なお、上記リテーナ２６として、図４〜図６に示すものを採用することも可能 である。図４に示すリテーナ２６は、各舌片部２６ｂの先端を弁体側に屈曲させ たもので、その屈曲先端部２６ｄが本考案の突状部をなす。図５に示すリテーナ ２６は、各舌片部２６ｂの先端側を弁体側に向けて傾けたもので、その先端部２ ６ｅが本考案の突状部をなす。図６に示すリテーナ２６は、各舌片部２６ｂの弁 体側の面を粗したもので、粗面化されることにより設けられる微小突部２６ｆが 本考案の突状部をなす。It is also possible to employ the retainer 26 shown in FIGS. 4 to 6. In the retainer 26 shown in FIG. 4, the tip of each tongue piece portion 26b is bent toward the valve body side, and the bent tip end portion 26d forms the projecting portion of the present invention. The retainer 26 shown in FIG. 5 is one in which the tip end side of each tongue piece portion 26b is inclined toward the valve body side, and the tip end portion 26e forms the projecting portion of the present invention. The retainer 26 shown in FIG. 6 has a roughened surface on the valve body side of each tongue piece 26b, and the minute projections 26f provided by roughening the projections form the projections of the present invention.
【００１９】 また、本考案の突状部を上記実施例のようにリテーナ２６側に設ける代わりに 、弁体側に設けることもできる。例えば、図７及び図８に示すように、弁体２８ のリテーナ２６側の面の周縁部に環状突部２８ａを設けることができる。Further, instead of providing the protruding portion of the present invention on the retainer 26 side as in the above embodiment, it may be provided on the valve body side. For example, as shown in FIGS. 7 and 8, an annular protrusion 28a can be provided on the peripheral edge of the surface of the valve body 28 on the retainer 26 side.
【００２０】[0020]
以上詳述したように、本考案の往復動式圧縮機の弁装置によれば、平板状弁体 の開弁の際の応答性が向上するので、冷媒の過圧縮、吐出圧の脈動を低減するこ とができる。また、平板状弁体がリテーナに密着して剥がれ難くなることが防止 できるので、弁体の戻り遅れに起因する圧縮機の体積効率の低下を防止すること が可能となる。 As described above in detail, according to the valve device of the reciprocating compressor of the present invention, the responsiveness at the time of opening the flat valve element is improved, so that the overcompression of the refrigerant and the pulsation of the discharge pressure are reduced. can do. In addition, since it is possible to prevent the flat valve element from coming into close contact with the retainer and becoming difficult to peel off, it is possible to prevent the volumetric efficiency of the compressor from being lowered due to the delay in return of the valve element.
【図１】実施例にかかる斜板式圧縮機の縦断面図であ
る。FIG. 1 is a vertical sectional view of a swash plate compressor according to an embodiment.
【図２】実施例にかかる弁板部分の部分断面図である。FIG. 2 is a partial cross-sectional view of a valve plate portion according to the embodiment.
【図３】図２のＡ矢視図である。FIG. 3 is a view on arrow A in FIG.
【図４】リテーナの他の態様を示す部分断面図である。FIG. 4 is a partial cross-sectional view showing another aspect of the retainer.
【図５】リテーナの他の態様を示す部分断面図である。FIG. 5 is a partial cross-sectional view showing another aspect of the retainer.
【図６】リテーナの他の態様を示す部分断面図である。FIG. 6 is a partial cross-sectional view showing another aspect of the retainer.
【図７】平板状弁体の他の態様を示す部分平面図であ
る。FIG. 7 is a partial plan view showing another aspect of the flat valve body.
【図８】平板状弁体の他の態様を示す部分断面図であ
る。FIG. 8 is a partial cross-sectional view showing another aspect of the flat valve body.
【図９】従来装置にかかる断面図である。FIG. 9 is a cross-sectional view of a conventional device.
６ａは吸入ポート、６ｈは吐出ポート、６ｂ、６ｉは弁
座面、６ｃ、６ｊは弁室、２６はリテーナ、２７、２８
は平板状弁体、２６ｃ、２６ｄ ２６ｅ、２６ｆ、２８
ａはそれぞれ突状部をなす小突子、屈曲先端部、先端
部、微小突部、環状突部である。6a is an intake port, 6h is a discharge port, 6b and 6i are valve seat surfaces, 6c and 6j are valve chambers, 26 is a retainer, 27 and 28.
Is a flat plate type valve body, 26c, 26d 26e, 26f, 28
Reference symbol a denotes a small protrusion, a bent tip, a tip, a minute protrusion, and an annular protrusion, each of which forms a protrusion.
───────────────────────────────────────────────────── フロントページの続き (72)考案者 樽谷 知二 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 Tomoji Tarutani 2-chome, Toyota-cho, Kariya City, Aichi Stock Company Toyota Industries Corp.
Claims (1)
弁座面に離隔対向するリテーナとを含んで囲包された弁
室を形成し、該弁室内に該ポートを挟む領域の差圧に応
じて該ポートを開閉する平板状弁体を遊装してなり、前
記リテーナと前記平板状弁体との接触は、両者の接触面
積を縮小させる突状部によりなされることを特徴とする
往復動式圧縮機の弁装置。Claims for utility model registration: 1. A valve chamber is formed, which includes a flat valve seat surface having a port opened and a retainer facing the valve seat surface with a space therebetween. A plate-shaped valve body that opens and closes the port is loosely mounted in the chamber according to the pressure difference between the regions sandwiching the port, and the retainer and the plate-shaped valve body come into contact with each other to reduce the contact area between them. A valve device for a reciprocating compressor, characterized in that the valve device is formed by a cylindrical portion.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4814591U JPH05981U (en) | 1991-06-25 | 1991-06-25 | Reciprocating compressor valve device |
| KR1019920007766A KR920021873A (en) | 1991-05-10 | 1992-05-08 | Discharge valve device of reciprocating compressor |
| EP92909986A EP0538493A1 (en) | 1991-05-10 | 1992-05-11 | Reciprocatory piston type compressor with valve assemblies having enhanced pressure response characteristics |
| PCT/JP1992/000600 WO1992020919A1 (en) | 1991-05-10 | 1992-05-11 | Reciprocatory piston type compressor with valve assemblies having enhanced pressure response characteristics |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4814591U JPH05981U (en) | 1991-06-25 | 1991-06-25 | Reciprocating compressor valve device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH05981U true JPH05981U (en) | 1993-01-08 |
Family
ID=12795192
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4814591U Pending JPH05981U (en) | 1991-05-10 | 1991-06-25 | Reciprocating compressor valve device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH05981U (en) |
-
1991
- 1991-06-25 JP JP4814591U patent/JPH05981U/en active Pending
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