JPH06346844A - Piston rotation regulating structure in swash plate type compressor - Google Patents
Piston rotation regulating structure in swash plate type compressorInfo
- Publication number
- JPH06346844A JPH06346844A JP5134872A JP13487293A JPH06346844A JP H06346844 A JPH06346844 A JP H06346844A JP 5134872 A JP5134872 A JP 5134872A JP 13487293 A JP13487293 A JP 13487293A JP H06346844 A JPH06346844 A JP H06346844A
- Authority
- JP
- Japan
- Prior art keywords
- rotation
- piston
- swash plate
- inner peripheral
- housing
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
Landscapes
- Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、ハウジングに収容され
た斜板の両面とピストンの首部との間に介在されたシュ
ーを介して斜板の回転運動をピストンの往復直線運動に
変換する斜板式圧縮機におけるピストン回動規制構造に
関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swash plate for converting a rotary motion of a swash plate into a reciprocating linear motion of a piston through a shoe interposed between both sides of a swash plate housed in a housing and a neck portion of the piston. The present invention relates to a piston rotation restriction structure in a plate compressor.
【０００２】[0002]
【従来の技術】この種の圧縮機ではピストンが回動して
斜板周縁とピストンの首部とが干渉して騒音を発生する
という問題がある。実開昭５４−５５７１１号公報に開
示される圧縮機では、斜板周縁に緩衝材を貼りつけて斜
板周縁とピストンの首部との干渉を和らげる対策が施さ
れている。実開昭６４−１３３９７３号公報に開示され
る圧縮機では、ハウジングの内周面と片頭ピストンの首
部の背面との間の干渉によって片頭ピストンの回動を規
制する対策が施されている。又、実開平４−４９６７６
号公報に開示される圧縮機では、ハウジング内周面と片
頭ピストンの首部の背面との間の凹凸の嵌合構造によっ
て片頭ピストンの首部を案内する対策が施されている。
この凹凸の嵌合構造によって片頭ピストンの回動が完全
に阻止される。2. Description of the Related Art In this type of compressor, there is a problem that the piston rotates and the peripheral edge of the swash plate interferes with the neck of the piston to generate noise. In the compressor disclosed in Japanese Utility Model Laid-Open No. 54-55711, a cushioning material is attached to the peripheral edge of the swash plate to reduce the interference between the peripheral edge of the swash plate and the neck of the piston. In the compressor disclosed in Japanese Utility Model Laid-Open No. 64-133973, a measure is taken to restrict the rotation of the single-headed piston by the interference between the inner peripheral surface of the housing and the back surface of the neck of the single-headed piston. In addition, the actual Kaihei 4-49676
In the compressor disclosed in the publication, measures are taken to guide the neck portion of the single-headed piston by means of a fitting structure of unevenness between the inner peripheral surface of the housing and the back surface of the neck portion of the single-headed piston.
This concavo-convex fitting structure completely prevents the rotation of the single-headed piston.
【０００３】[0003]
【発明が解決しようとする課題】しかし、実開昭５４−
５５７１１号公報に開示される対策では、斜板の周速度
が大きいために緩衝材と斜板周縁との当たりが強い。そ
のため、緩衝材の緩衝効果も充分でない上に緩衝材の損
傷進行が早く、実用的ではない。[Problems to be Solved by the Invention]
In the measures disclosed in Japanese Patent No. 55711, the cushioning material and the peripheral edge of the swash plate are strongly hit because the peripheral speed of the swash plate is high. Therefore, the cushioning effect of the cushioning material is not sufficient and the progress of damage to the cushioning material is rapid, which is not practical.
【０００４】実開昭６４−１３３９７３号公報に開示さ
れる対策では、不動のハウジングと片頭ピストンとの間
の干渉であるために実開昭５４−５５７１１号公報の対
策に比して騒音レベルが下がる。ハウジングと片頭ピス
トンとの干渉は少なくとも一方から突出する台形状の先
端平面と他方の平面との干渉であるが、このような干渉
構造では台の角と平面との当たりになる。そのため、角
当たりする部分の磨耗が大きい。摩耗が大きくなれば片
頭ピストンの回動量が大きくなり、騒音が大きくなる。In the countermeasure disclosed in Japanese Utility Model Laid-Open No. 64-133973, the noise level is lower than that in Japanese Utility Model Laid-Open No. 54-55711 because of the interference between the immovable housing and the single-headed piston. Go down. The interference between the housing and the single-headed piston is the interference between at least one trapezoidal tip flat surface protruding from one side and the other flat surface. In such an interference structure, the corner of the base and the flat surface hit each other. Therefore, the wear of the part that hits the corner is large. As the wear increases, the amount of rotation of the single-headed piston increases and the noise increases.
【０００５】実開平４−４９６７６号公報に開示される
対策では、片頭ピストンの回動が完全に抑えられるため
に片頭ピストンの回動による騒音は生じない。しかし、
凹凸嵌合構造によるガイド構成は片頭ピストンとハウジ
ングとの間の摩擦をもたらし、この摩擦部位の潤滑が必
要になる。しかし、クランク室において上方にある片頭
ピストンに対する凹凸嵌合構造部分をクランク室内の潤
滑油で良好に潤滑することはハウジング内周面における
凸構造あるいは凹み構造のために難しい。According to the countermeasure disclosed in Japanese Utility Model Laid-Open No. 4-49676, since the rotation of the single-headed piston is completely suppressed, noise due to the rotation of the single-headed piston does not occur. But,
The guide structure with the concavo-convex fitting structure causes friction between the single-headed piston and the housing, and it is necessary to lubricate this frictional portion. However, it is difficult to satisfactorily lubricate the concavo-convex fitting structure portion with respect to the upper single-head piston in the crank chamber with the lubricating oil in the crank chamber because of the convex or concave structure on the inner peripheral surface of the housing.
【０００６】本発明は、ピストンの回動による騒音及び
干渉する部位の摩耗を抑制することを目的とする。An object of the present invention is to suppress noise due to the rotation of the piston and wear of the interfering portion.
【０００７】[0007]
【課題を解決するための手段】そのために本発明では、
ハウジングの内周面に対向するピストンの背面上に、ピ
ストンの回動範囲を規制してピストンの首部と斜板周縁
との干渉を回避するための回動規制用凸曲面を設け、こ
の回動規制用凸曲面とハウジング内周面との間の回動ク
リアランスは前記首部と斜板周縁との間の回動クリアラ
ンスよりも小さく設定し、ピストンの周方向における回
動規制用凸曲面の曲率はピストンの周面の曲率よりも小
さく、かつハウジング内周面の曲率よりも大きくした。Therefore, according to the present invention,
On the back surface of the piston facing the inner peripheral surface of the housing, a rotation restricting convex curved surface for restricting the rotation range of the piston and avoiding interference between the neck of the piston and the peripheral edge of the swash plate is provided. The rotation clearance between the restriction convex curved surface and the housing inner peripheral surface is set to be smaller than the rotation clearance between the neck portion and the swash plate peripheral edge, and the curvature of the rotation restriction convex curved surface in the circumferential direction of the piston is It is smaller than the curvature of the peripheral surface of the piston and larger than the curvature of the inner peripheral surface of the housing.
【０００８】[0008]
【作用】ピストンの回動は回動規制用凸曲面とハウジン
グ内周面との間の干渉によって規制され、ピストンの首
部と斜板周縁とが干渉することはない。ハウジング内周
面と回動規制用凸曲面とは面接触に近い状態で干渉し、
騒音及び摩耗が抑制される。The rotation of the piston is restricted by the interference between the convex curved surface for restricting rotation and the inner peripheral surface of the housing, and the neck portion of the piston and the peripheral edge of the swash plate do not interfere with each other. The inner peripheral surface of the housing and the convex curved surface for rotation restriction interfere with each other in a state of near surface contact,
Noise and wear are suppressed.
【０００９】[0009]
【実施例】以下、本発明を具体化した一実施例を図１〜
図３に基づいて説明する。ハウジングを構成する接合さ
れた一対のシリンダブロック１，２には回転軸３が支持
されており、回転軸３上にはウェーブプレート４が止着
されている。シリンダブロック１，２には前後で対とな
る複数のシリンダボア１ａ，２ａが回転軸３を中心とす
る等間隔角度位置に配列形成されており、両頭ピストン
５がシリンダボア１ａ，２ａ内にスライド可能に嵌入さ
れている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment embodying the present invention will now be described with reference to FIGS.
It will be described with reference to FIG. A rotary shaft 3 is supported by a pair of joined cylinder blocks 1 and 2 forming a housing, and a wave plate 4 is fixedly mounted on the rotary shaft 3. A plurality of cylinder bores 1a, 2a forming a pair in the front and rear are arranged in the cylinder blocks 1, 2 at equidistant angular positions about the rotation shaft 3, and the double-headed piston 5 is slidable in the cylinder bores 1a, 2a. It has been inserted.
【００１０】ウェーブプレート４と両頭ピストン５との
間にはローラ６，７が介在されている。ローラ６，７は
両頭ピストン５の首部５ａに嵌合保持されており、ロー
ラ６，７の回転軸線の向きは回転軸３の軸線Ｌ1 を中心
とするウェーブプレート４の半径方向に設定されてい
る。ウェーブプレート４の前後両作用面Ｓ1 ，Ｓ2 は周
方向へ交互に凹凸を繰り返す２サイクル変位曲面に形成
されており、両作用面Ｓ 1 ，Ｓ2 上における半径方向線
は回転軸線Ｌ1 と直交する。従って、ローラ６，７はシ
リンダボア１ａ，２ａ内の両頭ピストン５に対して変位
することなくウェーブプレート４に対して相対的に転動
可能であり、ウェーブプレート４の回転に伴って往復動
する両頭ピストン５の往復動変位はウエーブプレート４
の変位曲線に一致する。Between the wave plate 4 and the double-headed piston 5
Rollers 6 and 7 are interposed between them. Rollers 6 and 7
It is fitted and held on the neck 5a of the double-headed piston 5, and
The orientation of the rotation axes of Las 6 and 7 is the axis L of the rotation axis 3.1Centered around
Is set in the radial direction of the wave plate 4
It Both front and rear working surfaces S of the wave plate 41, S2Is Zhou
Formed on a 2-cycle displacement curved surface that repeats unevenness in alternating directions
And both working surfaces S 1, S2Radial line on top
Is the axis of rotation L1Orthogonal to. Therefore, the rollers 6 and 7 are
Displacement with respect to double-headed piston 5 in Linda bores 1a, 2a
Rolling relative to the wave plate 4 without
It is possible and reciprocates as the wave plate 4 rotates.
The reciprocating displacement of the double-headed piston 5 is caused by the wave plate 4
Match the displacement curve of.
【００１１】２サイクル変位曲線を持つウェーブプレー
ト４の回転により両頭ピストン５が回転軸３の１回転に
対して２回往復動する。両頭ピストン５の往復動により
吸入室８の冷媒ガスが吸入弁９を押し退けつつ吸入ポー
ト１０からシリンダボア１ａ，２ａ内へ吸入される。シ
リンダボア１ａ，２ａ内の冷媒ガスは吐出弁１１を押し
退けつつ吐出ポート１２から吐出室１３へ吐出される。The rotation of the wave plate 4 having a two-cycle displacement curve causes the double-headed piston 5 to reciprocate twice for one rotation of the rotary shaft 3. Due to the reciprocating movement of the double-headed piston 5, the refrigerant gas in the suction chamber 8 is sucked into the cylinder bores 1a, 2a from the suction port 10 while pushing the suction valve 9 away. The refrigerant gas in the cylinder bores 1a, 2a is discharged from the discharge port 12 to the discharge chamber 13 while pushing the discharge valve 11 away.
【００１２】図２，３に示すように両頭ピストン５の首
部５ａの背面には台１４が一体形成されている。台１４
の幅は両頭ピストン５の径よりも大きくしてあり、台１
４の上面は円弧面形状の回動規制用凸曲面１４ａに形成
されている。回動規制用凸曲面１４ａの曲率は両頭ピス
トン５の周方向において両頭ピストン５の周面の曲率よ
りも小さく、かつシリンダブロック１，２の内周面１
ｂ，２ｂの曲率よりも大きくしてある。即ち、図２に示
すように回動規制用凸曲面１４ａの曲率半径Ｒ1はシリ
ンダブロック１，２の内周面１ｂ，２ｂの曲率半径Ｒ2
よりも小さく、回動規制用凸曲面１４ａの半径中心はシ
リンダブロック１，２の内周面１ｂ，２ｂの半径中心と
なる回転軸線Ｌ1 に一致する。As shown in FIGS. 2 and 3, a base 14 is integrally formed on the back surface of the neck portion 5a of the double-headed piston 5. Stand 14
The width of is larger than the diameter of the double-ended piston 5,
The upper surface of 4 is formed into a convex curved surface 14a for rotation restriction having an arcuate shape. The curvature of the rotation restricting convex curved surface 14a is smaller than the curvature of the circumferential surface of the double-headed piston 5 in the circumferential direction of the double-headed piston 5, and the inner circumferential surface 1 of the cylinder block 1, 2 is
It is made larger than the curvatures of b and 2b. That is, as shown in FIG. 2, the radius of curvature R 1 of the rotation restricting convex curved surface 14a is equal to the radius of curvature R 2 of the inner peripheral surfaces 1b and 2b of the cylinder blocks 1 and 2.
The radius center of the convex curved surface 14a for rotation regulation is smaller than that of the rotation axis L 1 which is the center of radius of the inner peripheral surfaces 1b, 2b of the cylinder blocks 1, 2.
【００１３】回動規制用凸曲面１４ａとシリンダブロッ
ク１，２の内周面１ｂ，２ｂとの間の回動クリアランス
Ｃ1 は首部５ａの腹面５ｂとウェーブプレート４の周縁
４ａとの間の回動クリアランスＣ2 よりも小さく設定し
てある。回動クリアランスＣ 1 ，Ｃ2 は両頭ピストン５
の中心軸線Ｌ2 を中心とした回転方向の間隔である。従
って、両頭ピストン５が回動すれば図２に鎖線で示すよ
うに回動規制用凸曲面１４ａがシリンダブロック１，２
の内周面１ｂ，２ｂに当接し、首部５ａの腹面５ｂとウ
ェーブプレート４の周縁４ａとが当接することはない。The convex curved surface 14a for restricting rotation and the cylinder block
Rotational clearance between inner peripheral surfaces 1b and 2b of wheels 1 and 2
C1Is the abdominal surface 5b of the neck 5a and the periphery of the wave plate 4
Rotation clearance C with 4a2Set smaller than
There is. Rotational clearance C 1, C2Is a double-ended piston 5
Center axis L of2Is the interval in the direction of rotation around. Servant
Then, if the double-headed piston 5 rotates, it will be shown by a chain line in FIG.
As shown in FIG.
Abutting on the inner peripheral surfaces 1b and 2b of the neck of the neck 5a and the abdominal surface 5b of the neck 5a.
The edge 4a of the wave plate 4 does not abut.
【００１４】回動規制用凸曲面１４ａは両頭ピストン５
の中心軸線Ｌ2 から最も遠い角部付近でシリンダブロッ
ク１，２の内周面１ｂ，２ｂに当接する。しかし、回動
規制用凸曲面１４ａとシリンダブロック１，２の内周面
１ｂ，２ｂとの当接は曲率が僅かに違う曲面同士の接触
であり、両者は面接触に近い状態で干渉する。そのた
め、両者の当たりは緩和され、騒音レベルは小さく、摩
耗もない。The convex curved surface 14a for restricting rotation is the double-headed piston 5.
The inner circumferential surface 1b of the cylinder block 1 near the farthest corner from the center axis L 2 of, abuts the 2b. However, the contact between the rotation restricting convex curved surface 14a and the inner peripheral surfaces 1b and 2b of the cylinder blocks 1 and 2 is contact between curved surfaces having slightly different curvatures, and the two interfere with each other in a state close to surface contact. Therefore, the contact between the two is reduced, the noise level is low, and there is no wear.
【００１５】この実施例では台１４の両端が両頭ピスト
ン５の両側部位よりも側方に張り出している。この張出
構成は回動クリアランスＣ1 の短縮化を可能にし、両頭
ピストン５の回動量を低減する。回動クリアランスＣ1
を短くするには内周面１ｂ，２ｂと回動規制用凸曲面１
４ａとを可及的に接近させればよいが、これは組み付け
誤差の影響もあって限界がある。両頭ピストン５の回動
量が少なくなれば回動規制用凸曲面１４ａと内周面１
ｂ，２ｂとの当たりが弱くなり、騒音レベル及び毛程度
が低減する。又、両頭ピストン５の回動量が少なくなれ
ばウェーブプレート４の半径方向に対するローラ６，７
の傾きが少なくなり、両頭ピストン５とウェーブプレー
ト４との間でのローラ６，７の噛み込みが解消される。In this embodiment, both ends of the base 14 project laterally beyond both sides of the double-headed piston 5. This overhanging structure enables the rotation clearance C 1 to be shortened and reduces the rotation amount of the double-headed piston 5. Rotating clearance C 1
In order to shorten the length, the inner peripheral surfaces 1b and 2b and the convex curved surface 1 for rotation restriction are
4a should be made as close as possible, but this is limited due to the influence of assembly error. If the amount of rotation of the double-headed piston 5 decreases, the convex curved surface 14a for rotation restriction and the inner peripheral surface 1
The contact with b and 2b is weakened, and the noise level and the degree of hair are reduced. If the amount of rotation of the double-headed piston 5 decreases, the rollers 6, 7 in the radial direction of the wave plate 4
Is reduced, and the engagement of the rollers 6 and 7 between the double-headed piston 5 and the wave plate 4 is eliminated.
【００１６】本発明を揺動斜板式圧縮機に具体化した実
施例を図４〜図６に基づいて説明する。圧縮機全体のハ
ウジングの一部となるシリンダブロック１５の前後には
フロントハウジング１６及びリヤハウジング１７が接合
固定されており、シリンダブロック１５及びフロントハ
ウジング１６には回転軸１８が回転可能に支持されてい
る。フロントハウジング１６内にて回転軸１８には回転
支持体１９が止着されており、その先端側には長孔１９
ａが透設されている。An embodiment in which the present invention is embodied in a swing swash plate type compressor will be described with reference to FIGS. A front housing 16 and a rear housing 17 are joined and fixed to the front and rear of a cylinder block 15 which is a part of the housing of the entire compressor, and a rotary shaft 18 is rotatably supported by the cylinder block 15 and the front housing 16. There is. A rotation support member 19 is fixedly attached to the rotation shaft 18 in the front housing 16, and a long hole 19 is attached to the tip end side thereof.
a is transparently provided.
【００１７】回転軸１８には球面状のブッシュ２０がス
ライド可能に支持されており、ブッシュ２０には斜板２
１が回転軸１８方向へ傾動可能に支持されている。斜板
２１には連結片２１ａが止着されていると共に、連結片
２１ａの先端部にはピン２１ｂが取り付けられている。
ピン２１ｂは長孔１９ａに係合しており、長孔１９ａは
斜板２１の傾動をピン２１ｂを介して案内する。これに
より斜板２１がブッシュ２０を中心に回転軸１８方向へ
揺動可能かつ回転軸１８と一体的に回転可能である。斜
板２１の傾動は長孔１９ａとピン２１ｂとのスライドガ
イド関係、ブッシュ２０のスライド作用及びブッシュ２
０の支持作用により案内される。A spherical bush 20 is slidably supported on the rotating shaft 18, and the swash plate 2 is attached to the bush 20.
1 is supported so as to be tiltable in the direction of the rotary shaft 18. A connecting piece 21a is fixed to the swash plate 21, and a pin 21b is attached to the tip of the connecting piece 21a.
The pin 21b is engaged with the elongated hole 19a, and the elongated hole 19a guides the tilting of the swash plate 21 via the pin 21b. As a result, the swash plate 21 can swing around the bush 20 in the direction of the rotary shaft 18 and can rotate integrally with the rotary shaft 18. The tilt of the swash plate 21 is due to the slide guide relationship between the elongated hole 19a and the pin 21b, the sliding action of the bush 20, and the bush 2
It is guided by the supporting action of zero.
【００１８】シリンダブロック１５に貫設されたシリン
ダボア１５ｂ内には片頭ピストン２２が収容されてい
る。片頭ピストン２２の首部２２ａの内側には半球状の
シュー２３が嵌入支持されている。斜板２１の周縁部は
両シュー２３間に入り込み、斜板２１の両面には両シュ
ー２３の端面が接する。従って、斜板２１の回転運動が
シュー２３を介して片頭ピストン２２の前後往復揺動に
変換され、片頭ピストン２２がシリンダボア１５ｂ内を
前後動する。これにより吸入室１７ａからシリンダボア
１５ｂ内へ吸入された冷媒ガスが圧縮されつつ吐出室１
７ｂへ吐出される。片頭ピストン２２のストロークがク
ランク室１５ａ内の圧力とシリンダボア１５ｂ内の吸入
圧との片頭ピストン２２を介した差圧に応じて変わり、
圧縮容量を左右する斜板２１の傾角が変化する。クラン
ク室１５ａ内の圧力はシリンダブロック１５内の容量制
御弁２４により制御される。A single-head piston 22 is housed in a cylinder bore 15b penetrating the cylinder block 15. A hemispherical shoe 23 is fitted and supported inside the neck portion 22 a of the single-headed piston 22. The peripheral portion of the swash plate 21 enters between the shoes 23, and the end faces of the shoes 23 are in contact with both surfaces of the swash plate 21. Therefore, the rotational movement of the swash plate 21 is converted into the forward and backward reciprocating swing of the single-headed piston 22 via the shoe 23, and the single-headed piston 22 moves back and forth in the cylinder bore 15b. As a result, the refrigerant gas sucked from the suction chamber 17a into the cylinder bore 15b is compressed and the discharge chamber 1 is compressed.
It is discharged to 7b. The stroke of the single-headed piston 22 changes depending on the pressure difference between the pressure in the crank chamber 15a and the suction pressure in the cylinder bore 15b through the single-headed piston 22,
The tilt angle of the swash plate 21, which influences the compression capacity, changes. The pressure in the crank chamber 15a is controlled by the capacity control valve 24 in the cylinder block 15.
【００１９】図５及び図６に示すように片頭ピストン２
２の首部２２ａの背面には台２５が一体形成されてい
る。台２５の幅は片頭ピストン２２の径よりも大きくし
てあり、台２５の上面は円弧面形状とは異なる回動規制
用凸曲面２５ａに形成されている。回動規制用凸曲面２
４ａの曲率は片頭ピストン２２の周方向において片頭ピ
ストン２２の周面の曲率よりも小さく、かつシリンダブ
ロック１５の内周面１５ｃの曲率よりも大きくしてあ
る。即ち、図５に示すように回動規制用凸曲面２５ａの
曲率半径はシリンダブロック１５の内周面１５ｃの曲率
半径Ｒ2 よりも小さい。又、回動規制用凸曲面２５ａと
シリンダブロック１５の内周面１５ｃとの間の回動クリ
アランスＣ1 は首部２２ａの腹面２２ｂと斜板２１の周
縁との間の回動クリアランスＣ2 よりも小さく設定して
ある。従って、回動規制用凸曲面２５ａと内周面１５ｃ
との干渉は僅かに曲率の異なる曲面接触となり、この実
施例でも前記実施例と同様の騒音抑制作用及び摩耗抑制
作用が得られる。As shown in FIGS. 5 and 6, the single-headed piston 2
A base 25 is integrally formed on the back surface of the second neck 22a. The width of the base 25 is larger than the diameter of the single-headed piston 22, and the upper surface of the base 25 is formed with a convex curved surface 25a for rotation restriction different from the arc surface shape. Convex curved surface 2 for rotation restriction
The curvature of 4a is smaller than the curvature of the peripheral surface of the single-headed piston 22 in the circumferential direction of the single-headed piston 22, and larger than the curvature of the inner peripheral surface 15c of the cylinder block 15. That is, as shown in FIG. 5, the radius of curvature of the rotation restricting convex curved surface 25 a is smaller than the radius of curvature R 2 of the inner peripheral surface 15 c of the cylinder block 15. Further, the rotation clearance C 1 between the rotation restricting convex curved surface 25a and the inner peripheral surface 15c of the cylinder block 15 is larger than the rotation clearance C 2 between the belly surface 22b of the neck portion 22a and the peripheral edge of the swash plate 21. It is set small. Accordingly, the rotation-regulating convex curved surface 25a and the inner peripheral surface 15c
The interference with the curved contact is slightly different in curvature, and this embodiment can also obtain the same noise suppressing effect and wear suppressing effect as those of the above-mentioned embodiments.
【００２０】この種の圧縮機ではクランク室１５ａの底
部に溜まる潤滑油によってクランク室１５ａ内の潤滑必
要部位の潤滑が行われる。クランク室１５ａ内の上方に
ある潤滑必要部位の潤滑はクランク室１５ａ底部の潤滑
油を斜板２１の回転によってかき上げて行われる。シリ
ンダブロック１５の内周面１５ａには凹凸はなく、台２
５の回動規制用凸曲面２５ａは内周面１５ａの円弧に沿
っている。従って、クランク室１５ａ底部からかき上げ
られた潤滑油は内周面１５ａに沿って流れ、回動規制用
凸曲面２５ａと内周面１５ａとの間の干渉部位が良好に
潤滑される。この潤滑は回動規制用凸曲面２５ａと内周
面１５ａとの間の干渉部位の摩耗防止に寄与する。In this type of compressor, the lubricating oil that collects at the bottom of the crank chamber 15a lubricates the lubrication-needed portion of the crank chamber 15a. Lubrication of the upper lubrication-needed portion in the crank chamber 15a is performed by scraping up the lubricating oil at the bottom of the crank chamber 15a by the rotation of the swash plate 21. There is no unevenness on the inner peripheral surface 15a of the cylinder block 15, and the base 2
The convex curved surface 25a for rotation restriction of No. 5 is along the circular arc of the inner peripheral surface 15a. Therefore, the lubricating oil scraped up from the bottom of the crank chamber 15a flows along the inner peripheral surface 15a, and the interference portion between the rotation restricting convex curved surface 25a and the inner peripheral surface 15a is well lubricated. This lubrication contributes to the prevention of wear of the interference portion between the rotation-regulating convex curved surface 25a and the inner peripheral surface 15a.
【００２１】本発明は勿論前記実施例にのみ限定される
ものではなく、例えば図７に示すように台１４の上面中
央部を凹ませて軽量化し、台１４の両端側にのみ回動規
制用凸曲面１４ｂを形成してもよい。Of course, the present invention is not limited to the above-described embodiment. For example, as shown in FIG. 7, the center portion of the upper surface of the base 14 is recessed to reduce the weight, and the rotation control is provided only on both ends of the base 14. The convex curved surface 14b may be formed.
【００２２】又、図８に示すように回動規制用凸曲面１
４ａを緩衝材２６で被覆したり、内周面１ｂ，２ｂ側を
緩衝材で被覆してもよい。Further, as shown in FIG. 8, the convex curved surface 1 for rotation restriction is used.
4a may be covered with the cushioning material 26, or the inner peripheral surfaces 1b and 2b may be covered with the cushioning material.
【００２３】[0023]
【発明の効果】以上詳述したように本発明は、ハウジン
グの内周面に対向するピストンの背面上に回動規制用凸
曲面を設け、ハウジング内周面と回動規制用凸曲面との
干渉でピストンの回動を規制するようにしたので、ピス
トンの回動による騒音及び干渉する部位の摩耗を抑制し
得るという優れた効果を奏する。As described in detail above, according to the present invention, the rotation restricting convex curved surface is provided on the rear surface of the piston facing the inner peripheral surface of the housing, and the inner peripheral surface of the housing and the rotation restricting convex curved surface are formed. Since the rotation of the piston is regulated by the interference, there is an excellent effect that the noise due to the rotation of the piston and the wear of the interfering portion can be suppressed.
【図１】 本発明をウェーブプレート式圧縮機に具体化
した実施例を示す圧縮機全体の側断面図である。FIG. 1 is a side sectional view of an entire compressor showing an embodiment in which the present invention is embodied in a wave plate compressor.
【図２】 図１のＡ−Ａ線拡大断面図である。FIG. 2 is an enlarged sectional view taken along the line AA of FIG.
【図３】 両頭ピストンの斜視図である。FIG. 3 is a perspective view of a double-headed piston.
【図４】 本発明を揺動斜板式圧縮機に具体化した実施
例を示す圧縮機全体の側断面図である。FIG. 4 is a side sectional view of the entire compressor showing an embodiment in which the present invention is embodied in a swing swash plate compressor.
【図５】 図４のＢ−Ｂ線拡大断面図である。5 is an enlarged sectional view taken along line BB of FIG.
【図６】 片頭ピストンの斜視図である。FIG. 6 is a perspective view of a single-headed piston.
【図７】 別例の要部拡大断面図である。FIG. 7 is an enlarged cross-sectional view of a main part of another example.
【図８】 別例の要部拡大断面図である。FIG. 8 is an enlarged sectional view of a main part of another example.
１，２…ハウジングとなるシリンダブロック、１ｂ，２
ｂ…内周面、５…両頭ピストン、５ａ…首部、１４ａ…
回動規制用凸曲面、Ｃ1 ，Ｃ2 …回動クリアランス。1, 2 ... Housing cylinder blocks 1b, 2
b ... inner peripheral surface, 5 ... double-headed piston, 5a ... neck, 14a ...
Rotation restricting convex curved surface, C 1, C 2 ... turning clearance.
Claims (1)
トンの首部との間に介在されたシューを介して斜板の回
転運動をピストンの往復直線運動に変換する斜板式圧縮
機において、 前記ハウジングの内周面に対向する前記ピストンの背面
上に、ピストンの回動範囲を規制してピストンの首部と
斜板周縁との干渉を回避するための回動規制用凸曲面を
設け、この回動規制用凸曲面とハウジング内周面との間
の回動クリアランスは前記首部と斜板周縁との間の回動
クリアランスよりも小さく設定し、ピストンの周方向に
おける回動規制用凸曲面の曲率はピストンの周面の曲率
よりも小さく、かつハウジング内周面の曲率よりも大き
くした斜板式圧縮機におけるピストン回動規制構造。1. A swash plate compressor for converting rotational movement of a swash plate into reciprocating linear movement of a piston through a shoe interposed between both surfaces of a swash plate housed in a housing and a neck of a piston. Provided on the rear surface of the piston facing the inner peripheral surface of the housing is a rotation restricting convex curved surface for restricting the rotation range of the piston to avoid interference between the neck portion of the piston and the swash plate peripheral edge. The rotation clearance between the motion-regulating convex curved surface and the housing inner peripheral surface is set smaller than the rotation clearance between the neck portion and the swash plate peripheral edge, and the curvature of the rotation-regulating convex curved surface in the circumferential direction of the piston is set. Is a piston rotation restriction structure in a swash plate compressor in which the curvature is smaller than the curvature of the peripheral surface of the piston and larger than the curvature of the inner peripheral surface of the housing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05134872A JP3125518B2 (en) | 1993-06-04 | 1993-06-04 | Piston rotation restriction structure for swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP05134872A JP3125518B2 (en) | 1993-06-04 | 1993-06-04 | Piston rotation restriction structure for swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06346844A true JPH06346844A (en) | 1994-12-20 |
| JP3125518B2 JP3125518B2 (en) | 2001-01-22 |
Family
ID=15138455
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP05134872A Expired - Fee Related JP3125518B2 (en) | 1993-06-04 | 1993-06-04 | Piston rotation restriction structure for swash plate compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3125518B2 (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0740076A2 (en) * | 1995-04-13 | 1996-10-30 | Calsonic Corporation | Variable displacement swash plate type compressor |
| EP0799994A1 (en) * | 1996-04-03 | 1997-10-08 | Sanden Corporation | Swash plate type compressor having an improved piston rotation regulating-structure |
| EP0819849A2 (en) * | 1996-07-15 | 1998-01-21 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston for compressors |
| US5720215A (en) * | 1996-11-25 | 1998-02-24 | General Motors Corporation | Automotive air conditioning compressor piston with eccentric anti rotation pad |
| EP0987436A2 (en) * | 1998-09-16 | 2000-03-22 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Single-headed-piston type refrigerant compressor with means for preventing rotation of the piston about its own axis within the cylinder bore |
| KR20000060868A (en) * | 1999-03-20 | 2000-10-16 | 신영주 | Wobble plate type compressor with variable displacement |
| US6293182B1 (en) | 1998-04-16 | 2001-09-25 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston-type compressor with piston guide |
| US6367368B1 (en) | 1999-12-29 | 2002-04-09 | Visteon Global Technologies, Inc. | Variable displacement compressor having piston anti-rotation structure |
| JP2003065222A (en) * | 2001-08-30 | 2003-03-05 | Sanden Corp | Piston of swash plate type compressor |
| US6546841B2 (en) | 2000-03-17 | 2003-04-15 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate compressor and piston therefor |
| WO2006030480A1 (en) * | 2004-09-13 | 2006-03-23 | Valeo Thermal Systems Japan Corporation | Piston for compressor |
| US7313999B2 (en) | 2003-08-01 | 2008-01-01 | Sanden Corporation | Piston for a reciprocating machine |
-
1993
- 1993-06-04 JP JP05134872A patent/JP3125518B2/en not_active Expired - Fee Related
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0740076A3 (en) * | 1995-04-13 | 1996-12-11 | Calsonic Corp | |
| US5706716A (en) * | 1995-04-13 | 1998-01-13 | Calsonic Corporation | Variable displacement swash plate type compressor |
| EP0740076A2 (en) * | 1995-04-13 | 1996-10-30 | Calsonic Corporation | Variable displacement swash plate type compressor |
| US5934172A (en) * | 1996-04-03 | 1999-08-10 | Sanden Corporation | Swash plate type compressor having an improved piston rotation regulating-structure |
| EP0799994A1 (en) * | 1996-04-03 | 1997-10-08 | Sanden Corporation | Swash plate type compressor having an improved piston rotation regulating-structure |
| EP0819849A2 (en) * | 1996-07-15 | 1998-01-21 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston for compressors |
| EP0819849A3 (en) * | 1996-07-15 | 2000-11-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston for compressors |
| EP0844391A3 (en) * | 1996-11-25 | 2000-10-25 | General Motors Corporation | Automotive air conditioning compressor piston with eccentric anti rotation pad |
| EP0844391A2 (en) * | 1996-11-25 | 1998-05-27 | General Motors Corporation | Automotive air conditioning compressor piston with eccentric anti rotation pad |
| US5720215A (en) * | 1996-11-25 | 1998-02-24 | General Motors Corporation | Automotive air conditioning compressor piston with eccentric anti rotation pad |
| EP0952341A3 (en) * | 1998-04-16 | 2003-05-14 | Kabushiki Kaisha Toyota Jidoshokki | Piston guide for a swash plate compressor |
| US6293182B1 (en) | 1998-04-16 | 2001-09-25 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston-type compressor with piston guide |
| US6220146B1 (en) | 1998-09-16 | 2001-04-24 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Single-headed-piston type refrigerant compressor with means for preventing rotation of the piston about its own axis within the cylinder bore |
| EP0987436A2 (en) * | 1998-09-16 | 2000-03-22 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Single-headed-piston type refrigerant compressor with means for preventing rotation of the piston about its own axis within the cylinder bore |
| EP0987436A3 (en) * | 1998-09-16 | 2003-11-19 | Kabushiki Kaisha Toyota Jidoshokki | Single-headed-piston type refrigerant compressor with means for preventing rotation of the piston about its own axis within the cylinder bore |
| KR20000060868A (en) * | 1999-03-20 | 2000-10-16 | 신영주 | Wobble plate type compressor with variable displacement |
| US6367368B1 (en) | 1999-12-29 | 2002-04-09 | Visteon Global Technologies, Inc. | Variable displacement compressor having piston anti-rotation structure |
| US6546841B2 (en) | 2000-03-17 | 2003-04-15 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate compressor and piston therefor |
| JP2003065222A (en) * | 2001-08-30 | 2003-03-05 | Sanden Corp | Piston of swash plate type compressor |
| US7313999B2 (en) | 2003-08-01 | 2008-01-01 | Sanden Corporation | Piston for a reciprocating machine |
| WO2006030480A1 (en) * | 2004-09-13 | 2006-03-23 | Valeo Thermal Systems Japan Corporation | Piston for compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3125518B2 (en) | 2001-01-22 |
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