JPH03149361A - Swash plate structure of variable displacement swash plate type compressor - Google Patents
Swash plate structure of variable displacement swash plate type compressorInfo
- Publication number
- JPH03149361A JPH03149361A JP1286626A JP28662689A JPH03149361A JP H03149361 A JPH03149361 A JP H03149361A JP 1286626 A JP1286626 A JP 1286626A JP 28662689 A JP28662689 A JP 28662689A JP H03149361 A JPH03149361 A JP H03149361A
- Authority
- JP
- Japan
- Prior art keywords
- swash plate
- piston
- shoe
- curvature
- center
- 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
- 238000006073 displacement reaction Methods 0.000 title abstract description 10
- 230000006835 compression Effects 0.000 claims description 17
- 238000007906 compression Methods 0.000 claims description 17
- 230000002093 peripheral effect Effects 0.000 claims description 7
- 239000003507 refrigerant Substances 0.000 abstract description 4
- 230000007935 neutral effect Effects 0.000 abstract description 3
- 229910052705 radium Inorganic materials 0.000 abstract 1
- HCWPIIXVSYCSAN-UHFFFAOYSA-N radium atom Chemical compound [Ra] HCWPIIXVSYCSAN-UHFFFAOYSA-N 0.000 abstract 1
- 230000004308 accommodation Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は両頭ピストンを備えた可変容量型斜板式圧縮機
の斜板構造に間するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a swash plate structure of a variable displacement swash plate compressor equipped with a double-ended piston.
［従来の技術］
従来この種の可変容量型斜板式圧縮機としては、例えば
第５図に示ず構成のものが特開平−１３８３８２号公報
に開示されている。この圧ｍｓではシリンダブロック５
１に形成された複数のシリンダボア５２内に両頭ピスト
ン５３が収容されると共に、シリンダボア５２と平行な
軸線上に回転軸５４が配置され、その回転軸５４にはス
ライダ（ガイドプッシュ）５５が摺動可能に嵌挿されて
いる。スライダ５５の球面部５５ａには周縁部がシュー
５６を介して両頭ピストン５３に係合される斜板５７が
回動可能に嵌合され、斜板５７の前面に形成された連結
部５７ａが回転ＩＩＩ ５４のフＩフント軸部５４ａに
対してそのカイト孔５４ｂに嵌挿されるガイドピン５８
を介して連結され、斜板５７がスライダ５５の摺動に伴
って揺動可能となっており、その揺動中心Ｃが斜板５７
の周縁側に設定されている。これによりピストン５３の
一側のシリンダボア５２における圧縮行程上死点が定位
置に規定され、斜板傾角が両側に近い小容量側のＬ１縮
作用領域でも実質的な圧縮及び吐出か行われる。[Prior Art] As a conventional variable displacement swash plate compressor of this type, for example, one having a configuration not shown in FIG. 5 is disclosed in Japanese Patent Application Laid-Open No. 138382. At this pressure ms, cylinder block 5
A double-headed piston 53 is housed in a plurality of cylinder bores 52 formed in the cylinder bore 1, and a rotating shaft 54 is arranged on an axis parallel to the cylinder bore 52, and a slider (guide push) 55 slides on the rotating shaft 54. It can be inserted easily. A swash plate 57 whose peripheral edge is engaged with the double-ended piston 53 via a shoe 56 is rotatably fitted into the spherical portion 55a of the slider 55, and a connecting portion 57a formed on the front surface of the swash plate 57 rotates. A guide pin 58 that is inserted into the kite hole 54b of the shaft portion 54a of the III 54.
The swash plate 57 can swing as the slider 55 slides, and the center of swing C is connected to the swash plate 57.
It is set on the periphery side. As a result, the top dead center of the compression stroke in the cylinder bore 52 on one side of the piston 53 is defined at a fixed position, and substantial compression and discharge are performed even in the L1 compression action region on the small capacity side where the swash plate inclination angle is close to both sides.
斜板傾角は吐出圧領域又は吸入圧領域に切換え接続さ１
１、る制御圧室５９の容積を変える摺動制御体６０及び
斜板５７を介して、前後面シリンダボア５２内の圧力に
よる斜板揺動力と制御圧室５９内の圧力との対抗により
制御されるようになっており一摺動制御体６０は回転軸
５４上に摺動可能に支持されている。この圧力対抗によ
り揺動する斜板５７が回転軸５４に付ｉｊする作用力は
斜板５７間のカイトピン５８を介して回転軸５４側のガ
イド孔５４ｂに受は止められ、カイトピン５８とカイト
孔５４ｂとのカイト関係により斜板傾角が制御されるよ
うになっている。The swash plate inclination is switched and connected to the discharge pressure area or suction pressure area.
1. Controlled by the opposition between the swash plate rocking force caused by the pressure in the front and rear cylinder bores 52 and the pressure in the control pressure chamber 59 via the sliding control body 60 that changes the volume of the control pressure chamber 59 and the swash plate 57. The sliding control body 60 is slidably supported on the rotating shaft 54. The acting force exerted on the rotating shaft 54 by the swash plate 57, which oscillates due to the pressure opposition, is received by the guide hole 54b on the rotating shaft 54 side via the kite pin 58 between the swash plates 57, and the kite pin 58 and the kite hole The swash plate inclination angle is controlled by the kite relationship with 54b.
又、摺動制御休６０の移動に対応Ｉ−で斜板５７を回転
軸５４に沿って移動可能かつ回転可能に支持する構成と
して、斜板５７を回転軸５４に治って摺動可能なスライ
ダ５５にピンで連結支持する構成もある。In addition, the swash plate 57 is movably and rotatably supported along the rotating shaft 54 by the I- corresponding to the movement of the slide control suspension 60, and the swash plate 57 is supported by a slider that can be slid on the rotating shaft 54. There is also a configuration in which it is connected and supported to 55 with a pin.
［発明か解決しようとする課題］
この種の可変容量型斜板式圧縮機では斜板５７の揺動中
心を両頭ピストン５３を収容するシリンダボア５２内に
設定する必要かあり、かつ斜板傾角が変化してもビス１
−ン５３とシュー５６間及びシュー５６と斜板５７間の
隙間が変化しないようにするため、シュー５６は斜板５
７の厚さ方向の中央に中心を持つ球の一部を構成する必
要がある。[Problem to be solved by the invention] In this type of variable capacity swash plate compressor, it is necessary to set the center of swing of the swash plate 57 within the cylinder bore 52 that accommodates the double-ended piston 53, and the swash plate inclination angle changes. Even if screw 1
- In order to prevent the gaps between the horn 53 and the shoe 56 and between the shoe 56 and the swash plate 57 from changing, the shoe 56 is attached to the swash plate 56.
It is necessary to form a part of a sphere whose center is at the center in the thickness direction of 7.
このため−斜板傾角が一定の固定容量型斜板式圧縮機と
比較してビスＩ〜ン５３に形成される球面四部５３ａが
浅くなってシューう６どの引っ掛かりが小さくなり、ル
ｆｆｉ機の運転時、特に圧縮容量か大きい時に、シュー
５６と斜板５７との摺動抵抗等によりシュー５６が迫り
出し、第６図に示すようにピストン５３と斜板５７間に
楔を打ったようにシュー５６が食い込むようになる。そ
の結果、斜板５７の回転運動をビスｌ−ンの往復運動に
円滑に変換できなくなり、動力消費の増大や最悪の場合
は運転不能に至る虞がある。For this reason, compared to a fixed capacity swash plate compressor with a constant swash plate inclination angle, the four spherical parts 53a formed on the screw I~n 53 are shallower, and the catch in the shoe 6 is reduced, making it easier to operate the LeFFI machine. When the compression capacity is large, the shoe 56 protrudes due to the sliding resistance between the shoe 56 and the swash plate 57, and the shoe 56 pushes out as shown in FIG. 56 starts to bite. As a result, the rotational motion of the swash plate 57 cannot be smoothly converted into the reciprocating motion of the screws, leading to an increase in power consumption or, in the worst case, to the inability to operate.
ピストン５３の球面四部５３ａを深く形成することによ
り、シュー５６の迫り出しによる前記不都合を解消する
ことが可能であるが、従来はこのことか非常に困難であ
った。なぜならば、ピストン５３の球面四部５３ａを深
く形成するためには、一対のシュー５６が斜板５７の厚
さ方向の中央に中心を持つ球の一部を構成しなければな
らないという制約があるため、シュー５６が収容される
ピストン５３の収容部５３Ｉ）の第７図における長さＡ
を小さくしなければならない、斜板５７の厚さを薄くす
れば長さＡを小さくできるが、斜板５７の強度か弱くな
り耐久性、信頼性が悪くなるという問題が生じる。By forming the four spherical parts 53a of the piston 53 deeply, it is possible to eliminate the above-mentioned disadvantage caused by the protruding shoe 56, but this has been extremely difficult in the past. This is because, in order to form the four spherical parts 53a of the piston 53 deeply, there is a restriction that the pair of shoes 56 must form part of a sphere whose center is at the center of the swash plate 57 in the thickness direction. , the length A in FIG. 7 of the accommodation portion 53I) of the piston 53 in which the shoe 56 is accommodated.
Although the length A can be reduced by reducing the thickness of the swash plate 57, the strength of the swash plate 57 is weakened, resulting in poor durability and reliability.
又、斜板５７の厚さを変更せずに長さＡを小さくすると
、大容量時〈斜板傾角が大の時）において斜板５７とピ
ストン５３どが干渉するという問題があった。そこで斜
板５７とピストン５３とが干渉する原因を究明した結果
、次のことが判明１〜な。Further, if the length A of the swash plate 57 is reduced without changing the thickness, there is a problem that the swash plate 57 and the piston 53 interfere with each other when the capacity is large (when the swash plate inclination angle is large). As a result of investigating the cause of the interference between the swash plate 57 and the piston 53, the following findings were found.
固定容量型斜板式圧縮機の斜板５７は第８図に示すよう
に、回転軸に嵌合される嵌合孔５７ｃが中心部に形成さ
れると共に、嵌合孔５７ｃの軸心と平行な外周面を有す
るボス部５７ｂに対して所定角度をなす状態で斜板本体
か一体に形成されている。そして、斜板５７の外周面を
加＝［する際には、ボス部５７ｂを把持した状態で軸り
を中心に全体を回転させて切削加工する。従って、斜板
５７の外形は嵌合孔５７ｃの軸心方向から見た場合円ど
なり、斜板本体の軸心方向から見た場合前記円の直径を
短径とした楕円となる。As shown in FIG. 8, the swash plate 57 of the fixed capacity swash plate compressor has a fitting hole 57c formed in the center to fit into the rotating shaft, and a hole parallel to the axis of the fitting hole 57c. The swash plate body is integrally formed at a predetermined angle with respect to a boss portion 57b having an outer circumferential surface. When machining the outer circumferential surface of the swash plate 57, cutting is performed by rotating the entire body around the axis while holding the boss portion 57b. Therefore, the outer shape of the swash plate 57 is a circle when viewed from the axial direction of the fitting hole 57c, and an ellipse whose short axis is the diameter of the circle when viewed from the axial direction of the swash plate body.
一方、容量可変型斜板式圧縮機の場合は、斜板５７が回
転軸５４どなず角度は一定ではないため斜板５７の外周
面を加工する際には、第９しに示すように斜板５７の側
面に対して直角に突設されたボス部５７ｂを把持した状
態で軸りを中心に全体を回転させて切削加工する。従っ
て、斜板５７の外形は斜板本体の軸心方向から見た場合
円となる。そして、この形状の斜板５７を形成する場合
、第５図に示すように最大容量においてピストン５３が
リヤ側の圧縮行程上死点に配置された状態で、斜板５７
がピストン５３の収容部５３ｂと干渉しないように〜か
つ斜板５７とシュー５６とが十分係合するように斜板５
７の直径が設定される。この状態で斜板５７を回転軸５
４の軸線方向から見−た外形は、第１０図に示ずように
揺動軸方向を長〜径とする楕円となる。そして、斜板５
７の回転に伴うシュー５６の移動軌跡は鎖線で示すよう
にほぼ軸中心０を中心とする円となる。従って、第５図
の状態から斜板５７が９０度あるいは２７０度回転して
ピストン５３が中間位置に移動した状態になると、第１
０図の斜線部分がピストン５３の収容部５３ｂ内にはみ
出しｔピストン５３と干渉し易くなる。この状態を上か
ら見た場合第１１図に示すように、斜板５７はピストン
５３の長平方向に対して傾いた状態となるので、斜板５
７はピストン５３に対して第１２図の斜線部分で干渉し
易くなる。前記斜板５７のピストン５３に対する傾きは
斜板傾角と対応し、最大容量時に最大となり容量の減少
に伴い小さくなる。収容部５３ｂの深さを大きくすれば
、斜板５７と収容部５３ｂとの干渉を回避することが可
能となるが、ピストン５３の強度が低下する。従って、
従来の強度を確保したまま収容部５３ｂの長さＡを小さ
くすることは難しい。On the other hand, in the case of a variable capacity swash plate type compressor, since the angle of the swash plate 57 is not constant due to the rotating shaft 54, when machining the outer peripheral surface of the swash plate 57, it is necessary to While gripping the boss portion 57b that protrudes perpendicularly to the side surface of the plate 57, cutting is performed by rotating the entire plate 57 around its axis. Therefore, the outer shape of the swash plate 57 is a circle when viewed from the axial direction of the swash plate main body. When forming the swash plate 57 in this shape, as shown in FIG. 5, the swash plate 57 is
The swash plate 5 is arranged so that the swash plate 57 does not interfere with the accommodation portion 53b of the piston 53 and the swash plate 57 and the shoes 56 are sufficiently engaged.
A diameter of 7 is set. In this state, the swash plate 57 is
4, the outer shape as seen from the axial direction is an ellipse whose length and diameter are in the direction of the swing axis, as shown in FIG. And swash plate 5
The locus of movement of the shoe 56 as the shoe 7 rotates becomes a circle centered approximately at the axis center 0, as shown by the chain line. Therefore, when the swash plate 57 rotates 90 degrees or 270 degrees from the state shown in FIG. 5 and the piston 53 moves to the intermediate position, the first
The shaded portion in Figure 0 protrudes into the housing portion 53b of the piston 53 and tends to interfere with the piston 53. When this state is viewed from above, as shown in FIG. 11, the swash plate 57 is inclined with respect to the longitudinal direction of the piston 53.
7 tends to interfere with the piston 53 in the shaded area in FIG. The inclination of the swash plate 57 with respect to the piston 53 corresponds to the inclination angle of the swash plate, and is maximum at the maximum capacity and becomes smaller as the capacity decreases. If the depth of the housing portion 53b is increased, interference between the swash plate 57 and the housing portion 53b can be avoided, but the strength of the piston 53 will be reduced. Therefore,
It is difficult to reduce the length A of the accommodating portion 53b while maintaining the conventional strength.
本発明は前記の問題点に鑑みてなされたものであって、
その目的はシューを支承するためピストンに形成される
球面四部を深くすることができ、斜板の回転運動が安定
した状態で円滑にピストンの往復運動に変換されて動力
消費の低減及び信頼性の向上を図ることができる可変容
量型斜板式圧ｓＩｌの斜板梢造を提供することにある。The present invention has been made in view of the above problems, and includes:
The purpose of this is to deepen the four spherical parts formed on the piston to support the shoes, and the rotating motion of the swash plate is smoothly converted into reciprocating motion of the piston in a stable state, reducing power consumption and improving reliability. It is an object of the present invention to provide a swash plate structure of a variable capacity type swash plate type pressure sIl that can improve the pressure.
［課題を解決ずるための手段］
前記の目的を達成するため本発明においては、両頭ピス
トンを往復動可能に収容するシリンダブロック内に回転
軸を回転可能に収容支持すると共に、該回転軸には両頭
ピストンを往復駆動する斜板を相対回転不能かつその周
縁側を中心として前後に揺動可能に支持し、その揺動中
心位置をリヤ側シリンダボア寄りに設定すると共に、回
転軸の回転に伴うｍｙｔｈ中心の回転領域上に前記両頭
ピストンの往復動領域を設定し、前記斜板の傾角変更に
よりピストンストロークを変更して容量を調節できるよ
うにした可変容量型斜板式圧ａｍにおいて、斜板の外形
を斜板揺動の軸方向を短径とする楕円とし、短径を回転
軸の軸線とシューの曲率中心との距離と、シューの曲率
半径との和とほぼ等しい長さに、長径を最大容量時にピ
ストンが圧縮行程上死点位置に配置された状態で回転軸
とシューの曲率中心を含む断面において斜板の外周が当
該ピストンのシューの外側にはみ出さない長さにそれぞ
れ設定した。[Means for Solving the Problems] In order to achieve the above object, in the present invention, a rotary shaft is rotatably housed and supported in a cylinder block that accommodates a double-ended piston so as to be able to reciprocate, and the rotary shaft has a A swash plate that reciprocates a double-headed piston is supported so that it cannot rotate relatively but can swing back and forth around its peripheral edge.The center of the swing is set near the rear cylinder bore, and the myth In a variable capacity swash plate type pressure am, in which a reciprocating area of the double-headed piston is set above a central rotation area, and the displacement can be adjusted by changing the piston stroke by changing the inclination of the swash plate, the outer shape of the swash plate is is an ellipse whose minor axis is in the axial direction of the swash plate, the minor axis is approximately equal to the sum of the distance between the axis of the rotating shaft and the center of curvature of the shoe, and the radius of curvature of the shoe, and the major axis is the maximum. The length was set so that the outer periphery of the swash plate would not protrude outside the shoe of the piston in a cross section including the rotating shaft and the center of curvature of the shoe when the piston was placed at the top dead center position of the compression stroke during displacement.
［作用］
前記のように梢成された可変容量型斜板式圧縮機におい
て回転軸が回転されると−斜板の傾角に ９ 一
応じて両頭ピストンが往復動されて冷媒ガスの圧縮が行
われる。斜板はその外形が斜板揺動の軸方向を短径とす
る楕円形に形成され、その短径が回転軸の軸線とシュー
の曲率中心との距離と、シューの曲率半径との和とほぼ
等しい長さに形成されているので、ピストンに形成され
た球面四部を深くしても、斜板とピストンとが干渉し易
い中立位置にピストンが移動配置された際に−斜板とピ
ストンとは干渉しない。[Operation] When the rotary shaft of the variable capacity swash plate compressor constructed as above is rotated, the double-headed piston is reciprocated in accordance with the inclination angle of the swash plate, thereby compressing the refrigerant gas. . The swash plate has an elliptical outer shape with its short axis in the axial direction of the swash plate's swing, and its short axis is the sum of the distance between the axis of the rotating shaft and the center of curvature of the shoe, and the radius of curvature of the shoe. Since they are formed to have approximately equal lengths, even if the four spherical surfaces formed on the piston are deepened, when the piston is moved to a neutral position where the swash plate and piston are likely to interfere, the swash plate and piston will does not interfere.
［実施例］
以下、本発明を具体化したー実施例を第１〜４図に従っ
て説明する。[Examples] Examples that embody the present invention will be described below with reference to FIGS. 1 to 4.
第２．３図に示すように、シリンダブロック１は前後一
対のプロ・シフ体１ａ、１ｂを互いに接合して構成され
、その内部中央には斜板室２が形成されると共に−前後
両端面にはフロントハウジング３及びリヤハウジング４
が接合固定されている。As shown in Fig. 2.3, the cylinder block 1 is constructed by joining a pair of front and rear pro-shift bodies 1a and 1b to each other, and a swash plate chamber 2 is formed in the center of the interior thereof. are front housing 3 and rear housing 4
is bonded and fixed.
シリンダブロック１には斜板室２のフロント側及びリヤ
側の対向する位置に複数組のシリンダボア５ａ、５ｂ−
が形成され、両シリンダボア５ａ、５ｂ内には両頭ピス
トン６か往復動可能に収容されているアシリンタブロッ
ク１にはフロント軸部７ａと、リヤ軸部７ｂと、両者の
間に形成された偏平な連結部７Ｃとからなる回転軸７か
シリンダボア５ａ、５ｂと平行に延びるように回転可能
に支持され、連結部７Ｃにはガイド孔７ｄが形成されて
いる。回転軸７はフロント軸部７ａがラジアルベアリン
グ８を介してフロント側のブロック体１ａに支持され、
リヤ軸部７ｂがスライダ１０に摺動可能に嵌挿された状
態で配設されている。スライダ１０はリヤ側のブロック
体１ｂに摺動可能に嵌挿された筒状の移動体３０に対し
て、ラジアルベアリング９ａ及びスラストベアリング９
ｂを介して回転自在に支持されている。The cylinder block 1 has a plurality of pairs of cylinder bores 5a, 5b, located at opposite positions on the front side and rear side of the swash plate chamber 2.
The cylinder block 1 has a front shaft portion 7a, a rear shaft portion 7b, and a flat shaft portion formed between the two cylinder bores 5a and 5b. A rotating shaft 7 consisting of a connecting portion 7C is rotatably supported so as to extend parallel to the cylinder bores 5a and 5b, and a guide hole 7d is formed in the connecting portion 7C. The rotating shaft 7 has a front shaft portion 7a supported by a front block body 1a via a radial bearing 8,
The rear shaft portion 7b is slidably inserted into the slider 10. The slider 10 is connected to a radial bearing 9a and a thrust bearing 9 with respect to a cylindrical moving body 30 that is slidably fitted into the rear block body 1b.
It is rotatably supported via b.
スライダ１０の前端両側には軸ピン１１がリヤ軸部７ｂ
と直交する状態で突設され、軸ピン１１を介して斜板支
持体１２が前記斜板室２内においてスライダ１０に対し
て傾動可能に支持されている。斜板支持体１２の外周後
縁には斜板１３か嵌合固定され、前側には嵌合孔１２ｂ
を有する一対の連結部１２ａか突設されている。両連結
部１２ａは前記回転軸７の連結部７Ｃを挟持する状態に
配置され、嵌合孔１２ ｂを貫通ずるカイトピン１−１
１がカイト孔７ｄに嵌会する状態で挿通されている。A shaft pin 11 is attached to the rear shaft portion 7b on both sides of the front end of the slider 10.
A swash plate support 12 is supported in the swash plate chamber 2 via a shaft pin 11 so as to be tiltable with respect to the slider 10 . A swash plate 13 is fitted and fixed on the rear edge of the outer periphery of the swash plate support 12, and a fitting hole 12b is provided on the front side.
A pair of connecting portions 12a are provided in a protruding manner. Both connecting portions 12a are arranged to sandwich the connecting portion 7C of the rotating shaft 7, and the kite pin 1-1 is inserted through the fitting hole 12b.
1 is inserted into the kite hole 7d so as to fit therein.
これにより回転軸７の回転か斜板支持体１２を介して斜
板１３に伝達されると共に、カイトピン１４とカイト孔
７ｄとの係合により、スライダ１０の軸線方向への摺動
変位に応じて斜板１３か揺動可能となり、この揺動中心
Ｃが斜板１３の周縁側に設定されている。そして、前記
各両頭ピストン６は前記揺動中心Ｃを中心とした球の一
部となる形状に形成されると共に両頭ビスト・ン６の収
容部６ｂに形成された球面凹部６ａと係合状態に保持さ
れるシュー１５を介して前記斜板１３の周縁部に係合さ
れ、斜板１３の回転に伴って前後Ｊ＼往復摺動されるよ
うになっている。シュー１５の曲率半径を従来と同じに
して球面凹部６ａの深さを深くするため、収容部６１）
の長さＡは従来より小さく形成されている。As a result, the rotation of the rotating shaft 7 is transmitted to the swash plate 13 via the swash plate support 12, and due to the engagement between the kite pin 14 and the kite hole 7d, the rotation is transmitted to the swash plate 13 according to the sliding displacement of the slider 10 in the axial direction. The swash plate 13 can swing, and the center of swing C is set on the periphery side of the swash plate 13. Each of the double-headed pistons 6 is formed into a shape that becomes a part of a sphere centered on the swing center C, and is engaged with a spherical recess 6a formed in the housing portion 6b of the double-headed piston 6. It is engaged with the peripheral edge of the swash plate 13 via a shoe 15 that is held, and is slid back and forth back and forth as the swash plate 13 rotates. In order to keep the radius of curvature of the shoe 15 the same as the conventional one and increase the depth of the spherical recess 6a, a housing part 61) is used.
The length A is smaller than the conventional one.
第１図に示すように斜板１３は斜板揺動の軸方向すなわ
ち、軸ピン１１に支持される側を短径とする楕円となる
ように形成されている。短径の長さは回転軸７の軸線と
シ：Ｌ−１５の曲率中心との距離より若干長く形成され
、長径は斜板１３が最大容量時の斜板角度に配置された
状態で回転軸方向から見た外形か円形となり、かつピス
トン６が第２図に示ず圧縮行程上死点位置に配置された
状態で回転軸７とシュー１５の曲率中心すなわち斜板１
３の揺動中心Ｃを含む断面において、斜板１３の外周か
当該ビス１〜ン６のシュー１５の外側にはみ出さない長
さに形成されている。すなわち、斜板１３は従来、円形
に形成されていた斜板１３の直径を長径として軸ピン１
１に支持される側の径を短くして短径とした楕円に形成
されている。As shown in FIG. 1, the swash plate 13 is formed into an ellipse whose short axis is in the axial direction of the swash plate swinging, that is, the side supported by the shaft pin 11. The length of the minor axis is slightly longer than the distance between the axis of the rotating shaft 7 and the center of curvature of the shaft L-15, and the major axis is the length of the rotating shaft when the swash plate 13 is arranged at the swash plate angle at maximum capacity. The outer shape when viewed from the direction is circular, and the center of curvature of the rotating shaft 7 and the shoe 15, that is, the swash plate 1, with the piston 6 placed at the top dead center position of the compression stroke (not shown in FIG. 2).
In the cross section including the swing center C of No. 3, the outer periphery of the swash plate 13 is formed to a length that does not protrude outside the shoes 15 of the screws 1 to 6. That is, the swash plate 13 has been conventionally formed into a circular shape, but the diameter of the swash plate 13 is the long axis, and the shaft pin 1 is
It is formed into an ellipse with the diameter of the side supported by 1 being shortened and the minor axis.
シリンダブロック１と前後面ハウジング３，４との間に
はサイドプレート１６．１７及び弁板１８゜１９が介在
されている。前後面ハウジング３．４内には吸入室２０
．２１及び吐出室２２．２３か形成され、各吐出室２２
．２３は図示しない吐出口を介ｉ−て外部冷却回路に連
結されている。フロリヤ側吸入室２０は吸入通路２４を
介して斜板室２に連通ずるとともに、フロント側サイド
プレート１６の吸入孔１６ａ及び吸入弁１８ ａ、を介
してフロント側圧縮室Ｉ） ｆに接続されている。フロ
ント側吐出室２２はフロン１一側サイドプレート１６の
吐出孔１６ｂ及び吐出弁２５を介してフロント側吐出室
ト）ｆに接続されている。リヤ側吸入室２１は吸入通路
２６を介して斜板室２に連通ずるとともに、サイドプレ
ー１−１ フーｉ二の吸入孔１ フ ２１及び吸入弁１
９ａを介してリヤ側圧縮室Ｐｒに接続されている。リヤ
側吐出室２３はサイドプレートコフ上の吐出孔１７Ｉ）
及び吐出弁２７を介１〜てリヤ側圧縮室Ｐｒに接続され
ている。Side plates 16, 17 and valve plates 18 and 19 are interposed between the cylinder block 1 and the front and rear housings 3, 4. There is a suction chamber 20 inside the front and rear housings 3.4.
．． 21 and discharge chambers 22 and 23 are formed, each discharge chamber 22
．． 23 is connected to an external cooling circuit via a discharge port (not shown). The floral side suction chamber 20 communicates with the swash plate chamber 2 via a suction passage 24, and is also connected to the front side compression chamber I) through a suction hole 16a of the front side plate 16 and a suction valve 18a. . The front side discharge chamber 22 is connected to the front side discharge chamber (t)f via the discharge hole 16b of the side plate 16 on one side of the freon 1 and the discharge valve 25. The rear side suction chamber 21 communicates with the swash plate chamber 2 via the suction passage 26, and also includes the side play 1-1, the suction hole 1 of the hood 21, and the suction valve 1.
It is connected to the rear side compression chamber Pr via 9a. The rear side discharge chamber 23 has a discharge hole 17I on the side plate cuff)
and is connected to the rear compression chamber Pr via the discharge valve 27.
リヤ側吸入室２１の後側には該吸入室２１と連通ずる制
御圧室２８が配設され、制御圧室２８内には制御体２９
が前後方向へスライド可能に嵌入されている。制御体２
９の前端はスライダ］０を支持する前記移動体３０の後
部に当接し、制御圧室２８の圧力変化に応じてスライダ
１０か制御体２つ及び移動体３０を介して軸方向に移動
可能になっている。A control pressure chamber 28 communicating with the suction chamber 21 is disposed on the rear side of the rear suction chamber 21, and a control body 29 is disposed within the control pressure chamber 28.
is inserted so that it can slide forward and backward. Control body 2
The front end of the slider 9 comes into contact with the rear part of the movable body 30 that supports the slider 0, and is movable in the axial direction via the slider 10 or the two control bodies and the movable body 30 according to pressure changes in the control pressure chamber 28. It has become.
制御圧室２８、リヤ側吐出室２３、斜板室２及び外部冷
媒ガス回路（図示せず）と斜板室２とを接続する吸入管
路（図示せず）は図示しない容１制御弁機構に接続され
ており、制御体２９の前後の変位が吸入管路内の吸入圧
の変動により制御されるようになっている。すなわち、
吸入管路内の吸入圧に基く容量制御弁機構内の弁の開閉
により制御圧室２８が吐出圧相当の高圧と吸入圧相当の
低圧との間で変更され、斜板１３が第２図に示す傾角最
大位置と図示しない頭角最小位置との間でその傾角が変
わって圧縮容量が調節されるようになっている。The control pressure chamber 28, the rear discharge chamber 23, the swash plate chamber 2, and the suction pipe (not shown) that connects the swash plate chamber 2 with an external refrigerant gas circuit (not shown) are connected to a control valve mechanism (not shown). The longitudinal displacement of the control body 29 is controlled by fluctuations in the suction pressure within the suction pipe. That is,
By opening and closing the valve in the capacity control valve mechanism based on the suction pressure in the suction pipe, the control pressure chamber 28 is changed between a high pressure equivalent to the discharge pressure and a low pressure equivalent to the suction pressure, and the swash plate 13 is moved to the position shown in FIG. The compression capacity is adjusted by changing the inclination between the maximum inclination position shown and the minimum head angle position not shown.
次に、前記のように構成された斜板式可変容量圧縮機の
作用を説明する。Next, the operation of the swash plate type variable capacity compressor configured as described above will be explained.
さて一回転軸７の回転により斜板１３が回転されると、
その斜板１３の傾角に応じて両頭ピストン６が往復動さ
れ、冷媒ガスが吸入室２０．２１ からシリンダボア５
ａ、５ｂの圧縮室Ｐｆ、Ｐｒ内に吸入され、各圧縮室Ｐ
ｆ、Ｐｒで圧縮された後に吐出室２２．２３内へ吐出さ
れる。両頭ピストン６には斜板傾角が最大に設定された
最大容量時において、第２図に示すようにピストン６に
よるリヤ側での圧縮動作が完了する直前、あるいはフロ
ント側での圧縮動作が完了する直前にシリンダボア５ａ
、５ｂ内の圧力により最も大きな力が作用するので、斜
板１３はその反力と釣り合う力でシュー１５を介してピ
ストン６を押す必要がある。同図に示すように斜板１３
の外周縁がシュー１５の外端近くまで延出しているので
、斜板１３とシュー１５の接触面積が大きくなって斜板
１３の押圧力がシュー１５に円滑に伝達される。Now, when the swash plate 13 is rotated by one rotation of the rotation shaft 7,
The double-headed piston 6 is reciprocated according to the inclination angle of the swash plate 13, and the refrigerant gas is transferred from the suction chamber 20.21 to the cylinder bore 5.
It is sucked into the compression chambers Pf and Pr of a and 5b, and each compression chamber P
After being compressed by f and Pr, it is discharged into the discharge chamber 22.23. When the double-headed piston 6 is at its maximum capacity with the swash plate inclination set to its maximum angle, the piston 6 has a swash plate immediately before the compression operation on the rear side is completed, or the compression operation on the front side is completed, as shown in Fig. 2. Cylinder bore 5a just before
, 5b exerts the greatest force, so the swash plate 13 must push the piston 6 via the shoe 15 with a force that balances the reaction force. As shown in the figure, the swash plate 13
Since the outer peripheral edge of the shoe 15 extends close to the outer end of the shoe 15, the contact area between the swash plate 13 and the shoe 15 becomes large, and the pressing force of the swash plate 13 is smoothly transmitted to the shoe 15.
この状態で斜板１３を回転軸７の軸線方向から見た外形
は、第４図に示すように円となる。そして、斜板１３の
回転に伴うシュー１５の移動軌跡は鎖線で示すようにほ
ぼ軸中心Ｏを中心とする円となる。従って、第２図の状
態から斜板１３が９０度あるいは２７０度回転してピス
トン６が第３図に示す中間位置に移動した状態となって
も、斜板１３の外周縁とシュー１５との関係は第２図と
同１ロー−
じ状態に保持され、従来装置と異なり斜板１３の外周縁
がシュー１５と対応する部分より収容部６ｂの内側には
み出すことはなく、斜板１３とピストン６との干渉が確
実に防止される。In this state, the outer shape of the swash plate 13 when viewed from the axial direction of the rotating shaft 7 is a circle as shown in FIG. The locus of movement of the shoe 15 as the swash plate 13 rotates becomes a circle approximately centered on the axial center O, as shown by the chain line. Therefore, even if the swash plate 13 rotates 90 degrees or 270 degrees from the state shown in FIG. 2 and the piston 6 moves to the intermediate position shown in FIG. The relationship is maintained in the same row state as in FIG. 2, and unlike the conventional device, the outer peripheral edge of the swash plate 13 does not protrude inside the housing portion 6b from the part corresponding to the shoe 15, and the swash plate 13 and the piston Interference with 6 is reliably prevented.
又、収容部６ｂの長さＡを小さくして球面凹部６ａが深
く形成され、しかも前記のようにシュー１５と斜板１３
の外周部との関係が常に一定の状態となるので−従来と
異なりシュー１５が迫り出すことが防止されると共に、
球面凹部６ａとシュー１５との係合状態が安定して、圧
をｉａｍの運転時に斜板１３の回転運動が安定した状態
で円滑にピストン６の往復運動に変換される。In addition, the length A of the accommodating portion 6b is reduced to form a deep spherical recess 6a, and as described above, the shoe 15 and the swash plate 13 are
Since the relationship with the outer periphery of the shoe 15 is always constant, the shoe 15 is prevented from protruding unlike the conventional case, and
The engagement state between the spherical recess 6a and the shoe 15 is stable, and the rotational movement of the swash plate 13 is smoothly converted into the reciprocating movement of the piston 6 in a stable state during the operation of the iam.
なお、本発明は前記実施例に限定されるものではなく、
例えば、斜板１３を軸ピン１１によりスライダ１０に回
動可能に支持する構成に代えて、従来装置のようにスラ
イダの先端に形成した球面部で支持する梢成としたり、
斜板支持体１２と斜板１３とを一体形成してもよい、又
、斜板１３の形状は斜板１３の外形を斜板揺動の軸方向
を短径とする楕円とし、短径を回転軸７の軸線とシュー
１５の曲率中心との距離と、シュー１５の曲率半径との
和とほぼ等しい長さに、長径を最大容量時にピストン６
が圧縮行程上死点位置に配置された状態で回転軸７とシ
ュー１５の曲率中心を含む断面において斜板１３の外周
が当該ピストン６のシュニ１５の外側にはみ出さない長
さにそれぞれ設定された楕円であればよく、かならずし
も最大容量時に回転軸７の軸線方向から見た斜板１３の
外形が円形となる必要はない。Note that the present invention is not limited to the above embodiments,
For example, instead of the configuration in which the swash plate 13 is rotatably supported on the slider 10 by the shaft pin 11, a top configuration in which the swash plate 13 is supported by a spherical part formed at the tip of the slider as in the conventional device may be used.
The swash plate support 12 and the swash plate 13 may be integrally formed, and the shape of the swash plate 13 is an ellipse whose minor axis is in the axial direction of the swash plate swing. When the piston 6 is at maximum capacity, the major diameter is approximately equal to the sum of the distance between the axis of the rotating shaft 7 and the center of curvature of the shoe 15, and the radius of curvature of the shoe 15.
The outer periphery of the swash plate 13 is set to a length that does not protrude outside the shoe 15 of the piston 6 in a cross section including the rotating shaft 7 and the center of curvature of the shoe 15 when the shoe 15 is placed at the top dead center position of the compression stroke. The outer shape of the swash plate 13 when viewed from the axial direction of the rotating shaft 7 at maximum capacity does not necessarily have to be circular.
［発明の効果］
以−Ｅ詳述したように本発明によれば、斜板の厚さやピ
ストン及びシューの大きさを変更することなく、シュー
と係合する球面凹部を深くでき、斜板の回転運動が安定
した状態で円滑にピストンの往復運動に変換されるので
、動力消費の低減及び信頼性の向上を図ることができる
。[Effects of the Invention] As described in detail below, according to the present invention, the spherical recess that engages with the shoes can be deepened without changing the thickness of the swash plate or the sizes of the pistons and shoes. Since rotational motion is smoothly converted into reciprocating motion of the piston in a stable state, it is possible to reduce power consumption and improve reliability.
ピストンが圧縮行程上死点位置に移動した状態を示す圧
縮機の断面図、第３図は同じくピストンが中立位置に移
動した状態を示ず圧ｍａの断面図、第４図は作用を示す
概略図、第５図は従来４１１成の斜板式可変容量圧縮機
の断面図、第６．フ図はピストン、斜板及びシューの関
係を示す部分断面図、第８図は固定容量型斜板式圧縮機
の斜板の断面図、第９図は従来の可変容量型斜板式圧縮
機の斜板の断面図、第１０図は同じく作用を示す概略図
５第１１図はピストンが中立位置配置された状態の斜板
とピストンの関係を示す一部破断部分断面図、第１２図
はピストンの部分斜視図である。
シリンダブロック１、シリンダボア５ａ、５ｂ、両頭ピ
ストン６、球面四部６ａ、収容部６ｂ、回転軸７、スラ
イダ１０、軸ビン１１、斜板１３、シュー１５、制御圧
室２８、制御体２９、揺動中心Ｃ。
特許出願人 株式会社豊田自動織機製作所代理人
弁理士 恩田博宣（ほか１名）又〉−ノ
ロ１Ｈ１７，臂A cross-sectional view of the compressor showing the piston moving to the top dead center position of the compression stroke, FIG. 3 is a cross-sectional view of the pressure ma without showing the piston moving to the neutral position, and FIG. 4 is a schematic diagram showing the action. Figure 5 is a sectional view of a conventional swash plate type variable capacity compressor of 411 configuration, and Figure 6. Fig. 8 is a cross-sectional view of the swash plate of a fixed displacement swash plate compressor, and Fig. 9 is a sectional view of a conventional variable displacement swash plate compressor. A cross-sectional view of the plate, FIG. 10 is a schematic diagram showing the operation.5 FIG. FIG. Cylinder block 1, cylinder bores 5a, 5b, double-headed piston 6, four spherical parts 6a, housing part 6b, rotating shaft 7, slider 10, shaft pin 11, swash plate 13, shoe 15, control pressure chamber 28, control body 29, rocking Center C. Patent applicant Toyota Industries Corporation representative
Patent attorney Hironobu Onda (and 1 other person) - Noro 1H17, Tsuji
Claims (1)
ック内に回転軸を回転可能に収容支持すると共に、該回
転軸には両頭ピストンを往復駆動する斜板を相対回転不
能かつその周縁側を中心として前後に揺動可能に支持し
、その揺動中心位置をリヤ側シリンダボア寄りに設定す
ると共に、回転軸の回転に伴う揺動中心の回転領域上に
前記両頭ピストンの往復動領域を設定し、前記斜板の傾
角変更によりピストンストロークを変更して容量を調節
できるようにした可変容量型斜板式圧縮機において、 斜板の外形を斜板揺動の軸方向を短径とする楕円とし、
短径を回転軸の軸線とシューの曲率中心との距離と、シ
ューの曲率半径との和とほぼ等しい長さに、長径を最大
容量時にピストンが圧縮行程上死点位置に配置された状
態で回転軸とシューの曲率中心を含む断面において斜板
の外周が当該ピストンのシューの外側にはみ出さない長
さにそれぞれ設定した可変容量型斜板式圧縮機の斜板構
造。[Claims] 1. A rotary shaft is rotatably housed and supported in a cylinder block that reciprocably accommodates a double-headed piston, and a swash plate for reciprocating the double-headed piston is mounted on the rotary shaft and is relatively non-rotatable. The double-headed piston is supported so as to be able to swing back and forth around its peripheral edge, and its swing center position is set near the rear cylinder bore, and the double-headed piston moves reciprocatingly over the rotational region of the swing center as the rotating shaft rotates. In a variable capacity swash plate type compressor in which the capacity can be adjusted by setting a range and changing the piston stroke by changing the inclination angle of the swash plate, the outer shape of the swash plate is set such that the axial direction of the swash plate swings is the minor axis. As an ellipse,
The short axis should be approximately equal to the sum of the distance between the axis of the rotating shaft and the center of curvature of the shoe, and the radius of curvature of the shoe, and the long axis should be set at maximum capacity when the piston is at the top dead center position of the compression stroke. A swash plate structure for a variable capacity swash plate compressor, in which the outer periphery of the swash plate is set to a length that does not protrude outside the shoe of the piston in a cross section that includes the rotating shaft and the center of curvature of the shoe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1286626A JP2762623B2 (en) | 1989-11-02 | 1989-11-02 | Swash plate structure of variable capacity swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1286626A JP2762623B2 (en) | 1989-11-02 | 1989-11-02 | Swash plate structure of variable capacity swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03149361A true JPH03149361A (en) | 1991-06-25 |
| JP2762623B2 JP2762623B2 (en) | 1998-06-04 |
Family
ID=17706849
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1286626A Expired - Lifetime JP2762623B2 (en) | 1989-11-02 | 1989-11-02 | Swash plate structure of variable capacity swash plate compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2762623B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009127470A (en) * | 2007-11-21 | 2009-06-11 | Sanden Corp | Variable displacement swash plate type compressor |
-
1989
- 1989-11-02 JP JP1286626A patent/JP2762623B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009127470A (en) * | 2007-11-21 | 2009-06-11 | Sanden Corp | Variable displacement swash plate type compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2762623B2 (en) | 1998-06-04 |
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