JPH07189897A - Piston in rotary swash plate type compressor - Google Patents
Piston in rotary swash plate type compressorInfo
- Publication number
- JPH07189897A JPH07189897A JP5332141A JP33214193A JPH07189897A JP H07189897 A JPH07189897 A JP H07189897A JP 5332141 A JP5332141 A JP 5332141A JP 33214193 A JP33214193 A JP 33214193A JP H07189897 A JPH07189897 A JP H07189897A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- swash plate
- headed piston
- head
- headed
- 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
- 230000002093 peripheral effect Effects 0.000 claims abstract description 21
- 235000013372 meat Nutrition 0.000 description 9
- 238000003825 pressing Methods 0.000 description 5
- 239000013585 weight reducing agent Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- 239000011800 void material Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
【０００１】本発明は、回転軸に傾動可能に支持された
斜板の両面と片頭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片頭ピストンの往復直線
運動に変換すると共に、クランク室内の圧力と吸入圧と
の片頭ピストンを介した差により斜板の傾角を制御する
揺動斜板式圧縮機におけるピストンに関するものであ
る。The present invention converts the rotational movement of a swash plate into a reciprocating linear movement of a single-head piston through a shoe interposed between both surfaces of a swash plate tiltably supported by a rotary shaft and the neck of a single-head piston. In addition, the present invention relates to a piston in a swing swash plate compressor that controls the tilt angle of the swash plate by the difference between the pressure in the crank chamber and the suction pressure via a single-headed piston.
【０００２】[0002]
【従来の技術】特開昭６０−１７５７８３号公報、実開
平４−１０９４８１号公報に開示されるこの種の圧縮機
では、半球状のシューの球面部が片頭ピストンの首部の
球面凹部に嵌まり込み支持されていると共に、端面部が
斜板面に接している。このようなシュー支持構造によっ
て斜板の回転に伴って片頭ピストンが回転軸方向に往復
動可能である。又、回転軸に傾動可能かつ回転軸と一体
的に回転可能に支持された回転板上に斜板を相対回転可
能に支持すると共に、斜板と片頭ピストンとをピストン
ロッドで連結した揺動斜板式圧縮機においては斜板回り
止め機構が必要であるが、特開昭６０−１７５７８３号
公報、実開平４−１０９４８１号公報の揺動斜板式圧縮
機では回転板及び回り止め機構が不要となり、機構の簡
素化が著しい。2. Description of the Related Art In a compressor of this type disclosed in Japanese Patent Laid-Open No. 60-175783 and Japanese Utility Model Laid-Open No. 1094881, the spherical portion of a hemispherical shoe fits into a spherical concave portion of a neck portion of a single-headed piston. The end surface is in contact with the swash plate surface. With such a shoe support structure, the single-headed piston can reciprocate in the rotation axis direction as the swash plate rotates. In addition, a swash plate is rotatably supported on a rotary plate which is tiltably supported by the rotary shaft and is rotatable integrally with the rotary shaft, and a swash plate and a single-head piston are connected by a piston rod. The plate type compressor requires a swash plate rotation preventing mechanism, but the swinging swash plate type compressor disclosed in JP-A-60-175783 and Japanese Utility Model Application Laid-Open No. 4-109481 does not require a rotating plate and a rotation preventing mechanism. The mechanism is remarkably simplified.
【０００３】この圧縮機には中空形状の片頭ピストンが
用いられている。片頭ピストンを中空形状とすることに
よって圧縮機全体の軽量化を図ることができる。しかも
片頭ピストンの軽量化はピストン慣性力の低減をもたら
し、高速回転時の容量制御性が向上する。即ち、ピスト
ン重量が大きいと高速回転時のピストン慣性力が大きく
なる。ピストン慣性力が大きいと吸入行程から吐出行程
への切り換え時には大きなピストン慣性力が斜板に加わ
り、斜板傾角が不要に大きくなる。このような不要な斜
板傾角増大を抑えるにはクランク室内の圧力を高くする
必要がある。即ち、斜板傾角が大きくなるほどクランク
室内の圧力を高めなければならない。しかし、このよう
な制御特性は、クランク室内の本来の圧力制御（斜板傾
角を大きくするにはクランク室内の圧力を降圧するこ
と）に反し、容量制御が不能となる。ピストンを軽量化
すればこのような容量制御不能は解消される。A hollow single-headed piston is used in this compressor. By making the single-headed piston hollow, it is possible to reduce the weight of the entire compressor. Moreover, the weight reduction of the single-headed piston reduces the piston inertial force and improves the capacity controllability at high speed rotation. That is, when the weight of the piston is large, the inertial force of the piston during high-speed rotation becomes large. If the piston inertial force is large, a large piston inertial force is applied to the swash plate when switching from the intake stroke to the discharge stroke, and the swash plate tilt angle becomes unnecessarily large. In order to suppress such an unnecessary increase in the tilt angle of the swash plate, it is necessary to increase the pressure in the crank chamber. That is, the pressure in the crank chamber must be increased as the tilt angle of the swash plate increases. However, such control characteristics are contrary to the original pressure control in the crank chamber (reducing the pressure in the crank chamber in order to increase the swash plate inclination angle), and the capacity control becomes impossible. By reducing the weight of the piston, such a capacity control failure can be solved.
【０００４】[0004]
【発明が解決しようとする課題】実開平４−１０９４８
１号公報の片頭ピストンでは２つの部品を溶接して片頭
ピストンを構成する製作工程が必要となるが、これは製
作コストの上昇をもたらす。[Problems to be Solved by the Invention]
The single-headed piston disclosed in Japanese Patent No. 1 requires a manufacturing process in which two parts are welded together to form a single-headed piston, which causes an increase in manufacturing cost.
【０００５】特開昭６０−１７５７８３号公報の片頭ピ
ストンでは、頭部の中空部は首部側に開口しており、こ
の開口側から中空化加工を施せる。しかし、奥深くまで
削り込むことはできず、頭部の中空部の容積を大きくで
きない。従って、片頭ピストンの軽量化は十分ではな
く、実開平４−１０９４８１号公報の場合と同様に２つ
の部品を溶接して片頭ピストンを構成する必要がある。In the single-headed piston disclosed in Japanese Patent Laid-Open No. 60-175783, the hollow portion of the head is open toward the neck side, and hollowing can be performed from this opening side. However, it cannot be carved deeply and the volume of the hollow part of the head cannot be increased. Therefore, the weight reduction of the single-headed piston is not sufficient, and it is necessary to construct the single-headed piston by welding two parts as in the case of Japanese Utility Model Laid-Open No. 109481/1992.
【０００６】本発明は、一体構成の片頭ピストンの軽量
化及びピストンとシリンダボアとの間の摺接部位の摩耗
の防止を図ることを目的とする。It is an object of the present invention to reduce the weight of a single-headed piston having an integral structure and prevent wear of a sliding contact portion between the piston and the cylinder bore.
【０００７】[0007]
【課題を解決するための手段】そのために請求項１に記
載の発明では、ピストンの中心軸線に関して斜板の回転
中心軸線とは反対側の片頭ピストンの頭部の周面側に
は、ピストンの中心軸線側に向けて凹ませた肉取り部を
設け、肉取り部の中央部には荷重受け面を残した。Therefore, according to the invention described in claim 1, the piston of the piston is provided on the circumferential surface side of the head of the single-headed piston opposite to the rotation center axis of the swash plate with respect to the center axis of the piston. A flesh-removing portion is provided which is recessed toward the central axis side, and a load receiving surface is left in the center of the replenishing portion.
【０００８】請求項２に記載の発明では、前記荷重受け
面を片頭ピストンの頭部側の周面から延出した。請求項
３に記載の発明では、片頭ピストンが下死点位置にある
ときには前記荷重受け面がシリンダボアの開口縁の内側
にあるようにした。According to the second aspect of the invention, the load receiving surface extends from the peripheral surface on the head side of the single-headed piston. According to the third aspect of the present invention, the load receiving surface is located inside the opening edge of the cylinder bore when the single-headed piston is at the bottom dead center position.
【０００９】[0009]
【作用】肉取り部は片頭ピストンの頭部の周面から斜板
の半径方向へ凹んでおり、肉取り部を有する一体構成の
片頭ピストンの形成は容易である。片頭ピストンが下死
点付近にあるときには片頭ピストンの慣性力が最も大き
く、斜板はこの慣性力の反力を片頭ピストンに与える。
この反力は斜板の回転中心軸線から半径方向へ離間する
方向への分力を有し、この分力が片頭ピストンの頭部周
面の特定部位をシリンダボアの周面に押し付ける。この
押し付け力は片頭ピストンとシリンダボアとの間の摺接
部位の摩耗を防止するために小さいほどよく、荷重受け
面は前記押し付け力を小さくするのに寄与する。The thinning portion is recessed in the radial direction of the swash plate from the peripheral surface of the head of the single-headed piston, and it is easy to form an integrally constructed single-headed piston having the thinning portion. When the one-headed piston is near the bottom dead center, the inertial force of the one-headed piston is the largest, and the swash plate gives a reaction force of this inertial force to the one-headed piston.
This reaction force has a component force in the direction away from the rotation center axis of the swash plate in the radial direction, and this component force presses a specific portion of the head peripheral surface of the single-headed piston against the peripheral surface of the cylinder bore. This pressing force should be as small as possible in order to prevent abrasion of the sliding contact portion between the single-headed piston and the cylinder bore, and the load receiving surface contributes to reduce the pressing force.
【００１０】請求項３に記載の発明では、前記分力によ
って荷重受け面に当たるシリンダボアの周面は開口縁と
なる。そのため、前記押し付け力が最も小さくなる。According to the third aspect of the invention, the peripheral surface of the cylinder bore that contacts the load receiving surface by the component force becomes an opening edge. Therefore, the pressing force is the smallest.
【００１１】[0011]
【実施例】以下、本発明を具体化した一実施例を図１〜
図５に基づいて説明する。図１に示すように圧縮機全体
のハウジングの一部となるシリンダブロック１の前後に
はフロントハウジング２及びリヤハウジング３が接合固
定されている。シリンダブロック１及びフロントハウジ
ング２には回転軸４が回転可能に支持されている。フロ
ントハウジング２内にて回転軸４には回転支持体５が止
着されており、回転支持体５の周縁部に形成された支持
アーム５ａにはガイド孔５ｂが形成されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment embodying the present invention will now be described with reference to FIGS.
A description will be given based on FIG. As shown in FIG. 1, a front housing 2 and a rear housing 3 are joined and fixed in front of and behind a cylinder block 1 which is a part of the housing of the entire compressor. A rotary shaft 4 is rotatably supported by the cylinder block 1 and the front housing 2. A rotation support body 5 is fixed to the rotation shaft 4 in the front housing 2, and a guide hole 5b is formed in a support arm 5a formed on the peripheral portion of the rotation support body 5.
【００１２】回転軸４には斜板７が回転軸４方向へ傾動
可能かつスライド可能に支持されている。斜板７には連
結片７ａが止着されていると共に、連結片７ａの先端部
にはガイドピン６が取り付けられている。ガイドピン６
はガイド孔５ｂに係合しており、ガイド孔５ｂはガイド
ピン６を介して斜板７の傾動を案内する。これにより斜
板７が回転軸４方向へ揺動可能かつ回転軸４と一体的に
回転可能である。A swash plate 7 is supported on the rotary shaft 4 so as to be tiltable and slidable in the direction of the rotary shaft 4. A connecting piece 7a is fixed to the swash plate 7, and a guide pin 6 is attached to the tip of the connecting piece 7a. Guide pin 6
Engage with the guide hole 5b, and the guide hole 5b guides the tilting of the swash plate 7 via the guide pin 6. As a result, the swash plate 7 can swing in the direction of the rotating shaft 4 and can rotate integrally with the rotating shaft 4.
【００１３】クランク室２ａ、リヤハウジング３内の吸
入室３ａ及び吐出室３ｂを互いに接続するようにシリン
ダブロック１に貫設されたシリンダボア１ａ内には片頭
ピストン８が収容されている。片頭ピストン８の首部９
の内側には一対の半球状の支持凹部９ａが対向形成され
ており、支持凹部９ａには半球状のシュー１１が嵌入支
持されている。斜板７の周縁部は両シュー１１間に入り
込み、斜板７の両面には両シュー１１の端面が接する。
従って、斜板７の回転運動がシュー１１を介して片頭ピ
ストン８の前後往復揺動に変換され、片頭ピストン８が
シリンダボア１ａ内を前後動する。これにより吸入室３
ａからシリンダボア１ａ内へ吸入された冷媒ガスが圧縮
されつつ吐出室３ｂへ吐出される。A single-headed piston 8 is housed in a cylinder bore 1a penetrating the cylinder block 1 so as to connect the crank chamber 2a, the suction chamber 3a and the discharge chamber 3b in the rear housing 3 to each other. Neck 9 of single-headed piston 8
A pair of hemispherical support recesses 9a are formed inside the inner surface of the support, and hemispherical shoes 11 are fitted and supported in the support recesses 9a. The peripheral edge of the swash plate 7 is inserted between the shoes 11, and the end faces of the shoes 11 are in contact with both surfaces of the swash plate 7.
Therefore, the rotational movement of the swash plate 7 is converted into the forward / backward reciprocating swing of the single-headed piston 8 via the shoe 11, and the single-headed piston 8 moves back and forth in the cylinder bore 1a. As a result, the suction chamber 3
The refrigerant gas sucked into the cylinder bore 1a from a is discharged to the discharge chamber 3b while being compressed.
【００１４】片頭ピストン８のストロークはクランク室
２ａ内の圧力とシリンダボア１ａ内の吸入圧との片頭ピ
ストン８を介した差圧に応じて変わり、圧縮容量を左右
する斜板７の傾角が変化する。クランク室２ａ内の圧力
はシリンダブロック１内の図示しない容量制御弁により
制御される。The stroke of the single-headed piston 8 changes according to the pressure difference between the pressure in the crank chamber 2a and the suction pressure in the cylinder bore 1a through the single-headed piston 8, and the inclination angle of the swash plate 7 that affects the compression capacity changes. . The pressure in the crank chamber 2a is controlled by a capacity control valve (not shown) in the cylinder block 1.
【００１５】図２及び図３に示すように片頭ピストン８
の首部９の背面には回り止め部９ｂが一体形成されてい
る。回り止め部９ｂはフロントハウジング２の内周面形
状と略同径の円周面を有しており、回り止め部９ｂの円
周面がフロントハウジング２の内壁面に接して片頭ピス
トン８の回転を防止する。As shown in FIGS. 2 and 3, the single-headed piston 8
An anti-rotation portion 9b is integrally formed on the back surface of the neck portion 9 of the. The rotation stopping portion 9b has a circumferential surface having substantially the same diameter as the inner peripheral surface of the front housing 2, and the rotation preventing portion 9b contacts the inner wall surface of the front housing 2 to rotate the single-headed piston 8. Prevent.
【００１６】図１、図３及び図４に示すように片頭ピス
トン８の頭部１０には肉取り部８ａが形成されている。
肉取り部８ａは、片頭ピストン８の中心軸線Ｃ1 に関し
て斜板７の回転中心軸線Ｃ0 とは反対側の片頭ピストン
８の頭部１０の周面側にて中心軸線Ｃ1 側に向けて凹み
形成されている。図４は図１のＢ−Ｂ線拡大断面図、図
５は図１のＣ−Ｃ線拡大断面図である。As shown in FIGS. 1, 3 and 4, the head portion 10 of the single-headed piston 8 is formed with a thinning portion 8a.
The filleting portion 8a faces the central axis C 1 side on the peripheral surface side of the head 10 of the single-head piston 8 on the side opposite to the rotation central axis C 0 of the swash plate 7 with respect to the central axis C 1 of the single-head piston 8. It is dented. 4 is an enlarged sectional view taken along line BB of FIG. 1, and FIG. 5 is an enlarged sectional view taken along line CC of FIG.
【００１７】肉取り部８ａの内には荷重受け面８ｂが残
されている。荷重受け面８ｂは頭部１０の先端１０ａ側
の周面から延出形成されている。片頭ピストン８は肉取
り部８ａの形成によって軽量化される。肉取り部８ａは
頭部１０の周面から切削形成したり、あるいは型抜き形
成され、片頭ピストン８は一体構成である。従って、片
頭ピストン８の素材として一体のブロックを用いること
ができ、ピストン製作が従来よりも容易となり、製作コ
ストが低減する。A load receiving surface 8b is left inside the meat removing portion 8a. The load receiving surface 8b is formed so as to extend from the peripheral surface of the head 10 on the side of the tip 10a. The single-headed piston 8 is made lighter by forming the meat removal portion 8a. The meat removing portion 8a is formed by cutting from the peripheral surface of the head portion 10 or is formed by die cutting, and the single-headed piston 8 has an integral structure. Therefore, an integral block can be used as a material for the single-headed piston 8, and the piston can be manufactured more easily than before, and the manufacturing cost can be reduced.
【００１８】図１に示すように、片頭ピストン８の中心
軸線Ｃ1 に関して斜板７の回転中心軸線Ｃ0 とは反対側
のシリンダボア１ａの内周面部の開口縁部位１ａ1 はシ
リンダボア１ａの開口縁の他部位よりもクランク室２ａ
側に突出している。図１の下側の片頭ピストン８は下死
点位置にあり、この状態では肉取り部８ａは開口縁部位
１ａ1 からクランク室２ａ側にはみ出している。又、荷
重受け面８ｂは開口縁部位１ａ1 の内側にある。即ち、
荷重受け面８ｂの縁部８ｂ1 と開口縁部位１ａ 1 とは一
致する。As shown in FIG. 1, the center of the single-headed piston 8
Axis C1With respect to the center axis C of rotation of the swash plate 70The other side
Opening edge portion 1a of the inner peripheral surface of the cylinder bore 1a of1Is
Crank chamber 2a more than other parts of the opening edge of Linda bore 1a
It projects to the side. The single-headed piston 8 on the lower side of FIG.
It is at a point position, and in this state, the meat removal portion 8a is the opening edge portion.
1a1From the crank chamber 2a side. Also, the load
The heavy receiving surface 8b is the opening edge portion 1a.1Inside. That is,
Edge 8b of load receiving surface 8b1And opening edge portion 1a 1Is one
To hit.
【００１９】片頭ピストン８が下死点位置付近にあると
きの片頭ピストン８の慣性力は図１の矢印Ｆ0 で表され
る。片頭ピストン８は斜板７の傾きによって位置Ｐから
慣性力Ｆ0 の反力を矢印Ｆｓで示すように受ける。反力
Ｆｓは、片頭ピストン８の往復動方向の分力ｆ1 と、斜
板７の回転中心軸線Ｃ0 から半径方向へ離間する方向へ
の分力ｆ2 とに分解される。片頭ピストン８は分力ｆ2
により傾こうとし、荷重受け面８ｂの縁部８ｂ1 がシリ
ンダボア１ａの内周面から分力ｆ2 （押し付け力）に対
する反力Ｆａを受けると共に、頭部１０の先端１０ａの
縁部１０ａ1 がシリンダボア１ａの内周面から分力ｆ2
（押し付け力）に対する反力Ｆｂを受ける。The inertial force of the one-headed piston 8 when the one-headed piston 8 is near the bottom dead center position is represented by an arrow F 0 in FIG. The single-headed piston 8 receives the reaction force of the inertial force F 0 from the position P due to the inclination of the swash plate 7 as shown by an arrow Fs. The reaction force Fs is decomposed into a component force f 1 in the reciprocating direction of the single- headed piston 8 and a component force f 2 in a direction away from the rotation center axis C 0 of the swash plate 7 in the radial direction. The single-headed piston 8 has a component force f 2
And the edge portion 8b 1 of the load receiving surface 8b receives a reaction force Fa from the inner peripheral surface of the cylinder bore 1a against the component force f 2 (pressing force), and the edge portion 10a 1 of the tip 10a of the head 10 is From the inner peripheral surface of the cylinder bore 1a, the component force f 2
It receives a reaction force Fb against (pressing force).
【００２０】斜板７の傾きをθ、頭部１０の先端１０ａ
から荷重受け面８ａの縁部８ａ1 までの距離をＬ1 、頭
部１０の先端１０ａから位置Ｐまでの距離をＬ2 とする
と、θ，Ｌ1 ，Ｌ2 ，Ｆ0 ，Ｆｓ，Ｆａ，Ｆｂの間には
式（１），（２），（３）で示す関係がある。 Ｆｓ・ cosθ＝Ｆ0 ・・・（１） Ｆｓ・ sinθ−Ｆａ＋Ｆｂ＝０ ・・・（２） Ｌ1 ・Ｆａ−Ｌ2 ・Ｆｓ・ sinθ＝０・・・（３） 式（１），（２），（３）より次式（４），（５）が得
られる。 Ｆａ＝Ｌ2 ・Ｆｓ・ sinθ／Ｌ1 ・・・（４） Ｆｂ＝（Ｌ2 −Ｌ1 ）・Ｆｓ・ sinθ／Ｌ1 ・・・（５） 式（４），（５）は距離Ｌ1 が大きくなるほど反力Ｆ
ａ，Ｆｂが小さくなることを表す。反力Ｆａ，Ｆｂが小
さいほど片頭ピストン８とシリンダボア１ａ内周面との
間の摺接部位の摩耗を少なくできる。The inclination of the swash plate 7 is θ, and the tip 10a of the head 10 is
The distance from to the edge 8a 1 of the load bearing surface 8a L 1, and the distance from the tip 10a of the head 10 to the position P and L 2, θ, L 1, L 2, F 0, Fs, Fa, There is a relationship between Fb as shown in equations (1), (2) and (3). Fs · cos θ = F 0 (1) Fs · sin θ−Fa + Fb = 0 (2) L 1 · Fa−L 2 · Fs · sin θ = 0 (3) Formulas (1), ( The following equations (4) and (5) are obtained from 2) and (3). Fa = L 2 · Fs · sin θ / L 1 (4) Fb = (L 2 −L 1 ) · Fs · sin θ / L 1 (5) Equations (4) and (5) are distances L Reaction force F increases as 1 increases
It shows that a and Fb become small. The smaller the reaction forces Fa and Fb, the less the wear of the sliding contact portion between the single-headed piston 8 and the inner peripheral surface of the cylinder bore 1a.
【００２１】本実施例では、肉取り部８ａの中央部にあ
る荷重受け面８ｂの配置位置によって距離Ｌ1 を稼ぐこ
とができ、荷重受け面８ｂの配置により反力Ｆａ，Ｆｂ
の低減化が図られている。又、片頭ピストン８が下死点
位置にあるときには、頭部１０の先端１０ａ1 側から延
出する荷重受け面８ｂの縁部８ｂ1 とシリンダボア１ａ
の開口縁部位１ａ1 とが一致するようにしてある。即
ち、荷重受け面８ｂの長短も片頭ピストン８の軽量化に
影響を与えるが、前記一致構成により片頭ピストン８の
軽量化及び反力Ｆａ，Ｆｂの低減化のバランスが最もよ
い。さらに開口縁部位１ａ1 をクランク室２ａ側に延出
することによって距離Ｌ1 が稼がれており、開口縁部位
１ａ1 の延出構成も反力Ｆａ，Ｆｂの低減化に寄与して
いる。In this embodiment, the distance L 1 can be increased by the position of the load receiving surface 8b at the center of the meat removing portion 8a, and the reaction forces Fa and Fb can be obtained by the arrangement of the load receiving surface 8b.
Is being reduced. When the single- headed piston 8 is at the bottom dead center position, the edge 8b 1 of the load receiving surface 8b extending from the tip 10a 1 side of the head 10 and the cylinder bore 1a.
The opening edge portion 1a 1 of the above is matched. That is, although the length of the load receiving surface 8b also affects the weight reduction of the single-headed piston 8, the weight balance of the single-headed piston 8 and the reduction of the reaction forces Fa and Fb are the best balance due to the coincident structure. Further, the distance L 1 is increased by extending the opening edge portion 1a 1 to the crank chamber 2a side, and the extension configuration of the opening edge portion 1a 1 also contributes to the reduction of the reaction forces Fa and Fb.
【００２２】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６〜図１０に示す片頭ピストン
の形状構成も可能である。図６の片頭ピストン８Ａでは
荷重受け面８ｃが頭部１０の先端１０ａ1 側から肉取り
部８ａの中央部を通って基端側の周面まで繋がってい
る。片頭ピストン８Ａが下死点位置にあるときには荷重
受け面８ｃはシリンダボア１ａの開口縁部位１ａ1 上に
ある。この構成では片頭ピストン８Ａの強度が前記実施
例の片頭ピストン８よりも向上する。The present invention is, of course, not limited to the above-mentioned embodiment, and the shape configuration of the single-headed piston shown in FIGS. 6 to 10 is also possible. In the single-headed piston 8A of FIG. 6, the load receiving surface 8c is connected from the tip 10a 1 side of the head 10 to the peripheral surface on the base end side through the central portion of the meat removal portion 8a. The load bearing surface 8c when the single-headed piston 8A is at the bottom dead center position is on the opening edge portion 1a 1 of the cylinder bore 1a. With this configuration, the strength of the single-headed piston 8A is improved as compared with the single-headed piston 8 of the above embodiment.
【００２３】図７の片頭ピストン８Ｂでは荷重受け面８
ｄが頭部１０の周方向に肉取り部８ａの中央部を通って
周面に繋がっている。片頭ピストン８Ｂが下死点位置に
あるときには荷重受け面８ｄはシリンダボア１ａの開口
縁部位１ａ1 上又は開口縁部位１ａ1 の内側にある。こ
の構成では片頭ピストン８Ｂの強度が前記実施例の片頭
ピストン８よりも向上する。In the single-headed piston 8B of FIG. 7, the load receiving surface 8
d is connected to the peripheral surface in the circumferential direction of the head 10 through the central portion of the meat removal portion 8a. When the single-headed piston 8B is at the bottom dead center position, the load receiving surface 8d is on the opening edge portion 1a 1 of the cylinder bore 1a or inside the opening edge portion 1a 1 . With this configuration, the strength of the single-headed piston 8B is improved as compared with the single-headed piston 8 of the above embodiment.
【００２４】図８の片頭ピストン８Ｃでは荷重受け面８
ｅが肉取り部８ａの中央部に残されている。片頭ピスト
ン８Ｃが下死点位置にあるときには荷重受け面８ｅはシ
リンダボア１ａの開口縁部位１ａ1 上又は開口縁部位１
ａ1 の内側にある。この構成では荷重受け面８ｅの長さ
が前記各実施例に比べて最も短く、片頭ピストン８Ｃの
軽量化の割合が最も高くなる。In the single-headed piston 8C shown in FIG.
e is left in the center of the meat removal portion 8a. When the single-headed piston 8C is at the bottom dead center position, the load receiving surface 8e is on the opening edge portion 1a 1 of the cylinder bore 1a or on the opening edge portion 1
It is inside a 1 . In this configuration, the length of the load receiving surface 8e is the shortest as compared with the above-mentioned respective embodiments, and the weight reduction ratio of the single-headed piston 8C is the highest.
【００２５】図９の片頭ピストン８Ｄでは荷重受け面８
ｆ1 ，８ｆ2 が頭部１０の周方向に延出して接近配置さ
れている。片頭ピストン８Ｄが下死点位置にあるときに
は荷重受け面８ｆ1 ，８ｆ2 はシリンダボア１ａの開口
縁部位１ａ1 上又は開口縁部位１ａ1 の内側にある。こ
の構成では図７の実施例に近い強度向上効果が得られ
る。In the single-headed piston 8D shown in FIG. 9, the load receiving surface 8
f 1 and 8 f 2 extend in the circumferential direction of the head 10 and are arranged close to each other. When the single-headed piston 8D is at the bottom dead center position, the load receiving surfaces 8f 1 and 8f 2 are on the opening edge portion 1a 1 of the cylinder bore 1a or inside the opening edge portion 1a 1 . With this configuration, a strength improving effect similar to that of the embodiment of FIG. 7 can be obtained.
【００２６】図１０の片頭ピストン８Ｅでは荷重受け面
８ｇが頭部１０の基端側から肉取り部８ａの中央部まで
延出している。片頭ピストン８Ｅが下死点位置にあると
きには荷重受け面８ｇの先端部はシリンダボア１ａの開
口縁部位１ａ1 上又は開口縁部位１ａ1 の内側にある。
この構成では第１実施例の片頭ピストン８と同様の作用
効果が得られる。In the single-headed piston 8E shown in FIG. 10, the load receiving surface 8g extends from the base end side of the head portion 10 to the central portion of the meat removing portion 8a. When the single-headed piston 8E is in the bottom dead center position, the tip of the load receiving surface 8g is on the opening edge portion 1a 1 of the cylinder bore 1a or inside the opening edge portion 1a 1 .
With this configuration, the same effect as that of the single-headed piston 8 of the first embodiment can be obtained.
【００２７】[0027]
【発明の効果】以上詳述したように本発明は、ピストン
の中心軸線に関して斜板の回転中心軸線とは反対側の片
頭ピストンの頭部の周面側には、ピストンの中心軸線側
に向けて凹ませた肉取り部を設け、肉取り部の中央部に
は荷重受け面を残したので、一体構成の片頭ピストンの
軽量化を達成し得ると共に、片頭ピストンとシリンダボ
アとの間の摺接部位の摩耗を防止し得るという優れた効
果を奏する。As described above in detail, according to the present invention, the peripheral surface side of the head of the single-headed piston opposite to the rotation center axis of the swash plate with respect to the center axis of the piston is directed toward the center axis of the piston. Since the flesh-relieving part that is recessed is provided and the load receiving surface is left in the center of the flesh-removing part, it is possible to reduce the weight of the single-headed piston with an integral structure and to make sliding contact between the single-headed piston and the cylinder bore. It has an excellent effect of preventing abrasion of the part.
【図１】 本発明を具体化した一実施例の圧縮機全体の
側断面図である。FIG. 1 is a side sectional view of an entire compressor according to an embodiment of the present invention.
【図２】 図１のＡ−Ａ線断面図である。FIG. 2 is a sectional view taken along line AA of FIG.
【図３】 片頭ピストンの斜視図である。FIG. 3 is a perspective view of a single-headed piston.
【図４】 図１のＢ−Ｂ線断面図である。FIG. 4 is a sectional view taken along line BB of FIG.
【図５】 図１のＣ−Ｃ線断面図である。5 is a cross-sectional view taken along the line CC of FIG.
【図６】 片頭ピストンの別例を示す斜視図である。FIG. 6 is a perspective view showing another example of a single-headed piston.
【図７】 片頭ピストンの別例を示す斜視図である。FIG. 7 is a perspective view showing another example of a single-headed piston.
【図８】 片頭ピストンの別例を示す斜視図である。FIG. 8 is a perspective view showing another example of a single-headed piston.
【図９】 片頭ピストンの別例を示す斜視図である。FIG. 9 is a perspective view showing another example of a single-headed piston.
【図１０】片頭ピストンの別例を示す斜視図である。FIG. 10 is a perspective view showing another example of a single-headed piston.
１ａ…シリンダボア、１ａ1 …開口縁部位、８，８Ａ，
８Ｂ，８Ｃ，８Ｄ，８Ｅ…片頭ピストン、８ａ…肉取り
部、８ｂ，８ｃ，８ｄ，８ｅ，８ｆ1 ，８ｆ2，８ｇ…
荷重受け面、９…首部、１０…頭部、１０ａ1 …先端、
Ｃ0 …回転中心軸線、Ｃ1 …中心軸線。1a ... cylinder bore, 1a 1 ... opening edge portion, 8, 8A,
8B, 8C, 8D, 8E ... single-headed pistons, 8a ... trimmed void portion, 8b, 8c, 8d, 8e , 8f 1, 8f 2, 8g ...
Load receiving surface, 9 ... neck, 10 ... head, 10a 1 ... tip,
C 0 ... central axis of rotation, C 1 ... central axis.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 平松 修 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 Osamu Hiramatsu 2-chome, Toyota-cho, Kariya city, Aichi stock company Toyota Industries Corp.
Claims (3)
とシリンダボア内に収容された片頭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片頭ピ
ストンの往復直線運動に変換すると共に、クランク室内
の圧力と吸入圧との片頭ピストンを介した差により斜板
の傾角を制御する揺動斜板式圧縮機において、 ピストンの中心軸線に関して斜板の回転中心軸線とは反
対側の片頭ピストンの頭部の周面側には、ピストンの中
心軸線側に向けて凹ませた肉取り部を設け、肉取り部の
中央部には荷重受け面を残した揺動斜板式圧縮機におけ
るピストン。Claim: What is claimed is: 1. A rotary motion of a swash plate is reciprocated by a shoe interposed between both surfaces of a swash plate tiltably supported by a rotary shaft and a neck portion of a single-head piston housed in a cylinder bore. In a swinging swash plate compressor that converts to linear motion and controls the tilt angle of the swash plate by the difference between the pressure in the crank chamber and the suction pressure via a single-headed piston, the rotation center axis of the swash plate with respect to the center axis of the piston Is provided on the opposite side of the head of the single-headed piston, and is provided with a recessed portion that is recessed toward the center axis of the piston. Piston in plate compressor.
周面から延出している請求項１に記載の揺動斜板式圧縮
機におけるピストン。2. The piston in a swing swash plate type compressor according to claim 1, wherein the load receiving surface extends from a peripheral surface on the head side of the single-headed piston.
位置にあるときにはシリンダボアの開口縁の内側にある
請求項１及び請求項２のいずれかに記載の揺動斜板式圧
縮機におけるピストン。3. The piston in a swing swash plate compressor according to claim 1, wherein the load receiving surface is inside the opening edge of the cylinder bore when the single-headed piston is at the bottom dead center position. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33214193A JP3550707B2 (en) | 1993-12-27 | 1993-12-27 | Piston in oscillating swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33214193A JP3550707B2 (en) | 1993-12-27 | 1993-12-27 | Piston in oscillating swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07189897A true JPH07189897A (en) | 1995-07-28 |
| JP3550707B2 JP3550707B2 (en) | 2004-08-04 |
Family
ID=18251603
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33214193A Expired - Fee Related JP3550707B2 (en) | 1993-12-27 | 1993-12-27 | Piston in oscillating swash plate compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3550707B2 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0809024A1 (en) * | 1996-05-21 | 1997-11-26 | Sanden Corporation | Reciprocating pistons of piston type compressor |
| EP0814261A2 (en) * | 1996-06-17 | 1997-12-29 | General Motors Corporation | Compressor piston |
| FR2755190A1 (en) * | 1996-10-25 | 1998-04-30 | Toyoda Automatic Loom Works | Air-conditioner compressor with light-weight pistons |
| EP0952341A2 (en) | 1998-04-16 | 1999-10-27 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston guide for a swash plate compressor |
| US6038960A (en) * | 1997-10-08 | 2000-03-21 | Sanden Corporation | Reciprocating pistons of piston-type compressor |
| US6050783A (en) * | 1997-01-10 | 2000-04-18 | Sanden Corporation | Reciprocating compressor in which a blowby gas can be returned into a suction chamber with a lubricating oil within a crank chamber kept at a sufficient level |
| WO2002064978A1 (en) * | 2001-02-14 | 2002-08-22 | Daimlerchrysler Ag | Piston for a compressor |
| US6484621B1 (en) | 1999-05-28 | 2002-11-26 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor wherein piston head has inner sliding portion for reducing local wear |
| EP1568884A2 (en) * | 2004-02-26 | 2005-08-31 | Delphi Technologies, Inc. | Reinforced hollow piston structure for swash plate compressor |
| KR100558703B1 (en) * | 1999-03-20 | 2006-03-10 | 한라공조주식회사 | Piston to minimize stress |
| KR100779068B1 (en) * | 2001-08-10 | 2007-11-27 | 한라공조주식회사 | Swash plate compressor |
-
1993
- 1993-12-27 JP JP33214193A patent/JP3550707B2/en not_active Expired - Fee Related
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5899135A (en) * | 1996-05-21 | 1999-05-04 | Sanden Corporation | Reciprocating pistons of piston type compressor |
| EP0809024A1 (en) * | 1996-05-21 | 1997-11-26 | Sanden Corporation | Reciprocating pistons of piston type compressor |
| EP0814261A2 (en) * | 1996-06-17 | 1997-12-29 | General Motors Corporation | Compressor piston |
| EP0814261A3 (en) * | 1996-06-17 | 1999-08-04 | General Motors Corporation | Compressor piston |
| FR2755190A1 (en) * | 1996-10-25 | 1998-04-30 | Toyoda Automatic Loom Works | Air-conditioner compressor with light-weight pistons |
| US6050783A (en) * | 1997-01-10 | 2000-04-18 | Sanden Corporation | Reciprocating compressor in which a blowby gas can be returned into a suction chamber with a lubricating oil within a crank chamber kept at a sufficient level |
| US6038960A (en) * | 1997-10-08 | 2000-03-21 | Sanden Corporation | Reciprocating pistons of piston-type compressor |
| US6293182B1 (en) | 1998-04-16 | 2001-09-25 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston-type compressor with piston guide |
| EP0952341A2 (en) | 1998-04-16 | 1999-10-27 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston guide for a swash plate compressor |
| EP0952341A3 (en) * | 1998-04-16 | 2003-05-14 | Kabushiki Kaisha Toyota Jidoshokki | Piston guide for a swash plate compressor |
| KR100558703B1 (en) * | 1999-03-20 | 2006-03-10 | 한라공조주식회사 | Piston to minimize stress |
| US6484621B1 (en) | 1999-05-28 | 2002-11-26 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor wherein piston head has inner sliding portion for reducing local wear |
| WO2002064978A1 (en) * | 2001-02-14 | 2002-08-22 | Daimlerchrysler Ag | Piston for a compressor |
| US6925925B2 (en) | 2001-02-14 | 2005-08-09 | Daimlerchrysler Ag | Piston for a compressor |
| KR100779068B1 (en) * | 2001-08-10 | 2007-11-27 | 한라공조주식회사 | Swash plate compressor |
| EP1568884A2 (en) * | 2004-02-26 | 2005-08-31 | Delphi Technologies, Inc. | Reinforced hollow piston structure for swash plate compressor |
| EP1568884A3 (en) * | 2004-02-26 | 2009-03-04 | Delphi Technologies, Inc. | Reinforced hollow piston structure for swash plate compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3550707B2 (en) | 2004-08-04 |
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