JPH07189900A - Piston in rotary swash plate type compressor - Google Patents
Piston in rotary swash plate type compressorInfo
- Publication number
- JPH07189900A JPH07189900A JP5332144A JP33214493A JPH07189900A JP H07189900 A JPH07189900 A JP H07189900A JP 5332144 A JP5332144 A JP 5332144A JP 33214493 A JP33214493 A JP 33214493A JP H07189900 A JPH07189900 A JP H07189900A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- swash plate
- head
- headed piston
- cylinder bore
- 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)
- 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
４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 4 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】そのために本発明は、回
転軸に傾動可能に支持された斜板の両面とシリンダボア
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を対象とし、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方向側及
び反対側の少なくとも一方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
部を設けた。To this end, the present invention uses a shoe interposed between both surfaces of a swash plate tiltably supported by a rotary shaft and a neck portion of a single-headed piston housed in a cylinder bore. Targeting a swinging swash plate compressor that converts the rotational movement of the swash plate into a reciprocating linear movement of a single-headed piston and controls the tilt angle of the swash plate by the difference between the pressure in the crank chamber and the suction pressure through the single-headed piston, In the invention described in claim 1, the circumferential surface side of the head of at least one of the single-headed pistons on the rotational direction side and the opposite side of the swash plate with respect to the central axis of the piston is recessed toward the central axis of the piston. A meat removing section was provided.
【０００８】請求項２に記載の発明では、回転軸と一体
的に回転するロータリバルブを介してシリンダボアの周
面に繋がる吸入ポートからシリンダボア内へ冷媒ガスを
供給する揺動斜板式圧縮機を対象とし、ピストンの中心
軸線に関して斜板の回転方向側及び反対側の少なくとも
一方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、前記吸入ポ
ートの周辺のシールを行なうためのシール面を前記肉取
り部側に張り出した。According to the second aspect of the present invention, the swash plate type compressor for supplying the refrigerant gas into the cylinder bore from the suction port connected to the peripheral surface of the cylinder bore through the rotary valve that rotates integrally with the rotary shaft is targeted. And, on the peripheral surface side of the head of at least one of the single-headed pistons on the rotation direction side and the opposite side of the swash plate with respect to the central axis of the piston, a chamfered portion that is recessed toward the central axis of the piston is provided, and A sealing surface for sealing the periphery of the suction port is extended to the meat removal portion side.
【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
の回転方向又は逆方向へ凹んでおり、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。肉取り部は前記特定部位から外れた位置にある。The flesh-cutting portion is recessed from the peripheral surface of the head of the single-headed piston in the direction of rotation of the swash plate or in the opposite direction, and it is easy to form a single-headed piston having the flesh-cutting 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. The meat removing portion is located outside the specific portion.
【００１０】請求項２に記載の発明では、片頭ピストン
が上死点位置付近にあるときには前記シール面が吸入ポ
ートの周辺のシールを行なう。According to the second aspect of the invention, when the single-headed piston is near the top dead center position, the sealing surface seals the periphery of the suction port.
【００１１】[0011]
【実施例】以下、本発明を具体化した一実施例を図１〜
図７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。回転
軸４は図１及び図２に示す矢印Ｒ方向に回転する。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.
It will be described with reference to 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. The rotating shaft 4 rotates in the arrow R direction shown in FIGS. 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】シリンダブロック１の中心部には収容孔１
２が形成されており、収容孔１２にはロータリバルブ１
３が回転可能に収容されている。ロータリバルブ１３は
回転軸４に連結されており、回転軸４とロータリバルブ
１３とは一体的に回転する。図３に示すようにロータリ
バルブ１３内には供給通路１３ａが形成されており、そ
の供給ポート１３ｂがロータリバルブ１３の周面に開口
している。収容孔１２の周面には複数の吸入ポート１２
ａが周方向に配列形成されている。各吸入ポート１２ａ
はシリンダボア１ａと１対１で連通している。回転軸４
の回転に伴って供給ポート１３ｂは吸入ポート１２ａと
順次連通してゆく。A housing hole 1 is formed in the center of the cylinder block 1.
2 is formed in the accommodation hole 12 of the rotary valve 1
3 is rotatably accommodated. The rotary valve 13 is connected to the rotary shaft 4, and the rotary shaft 4 and the rotary valve 13 rotate integrally. As shown in FIG. 3, a supply passage 13 a is formed in the rotary valve 13, and its supply port 13 b is open on the peripheral surface of the rotary valve 13. A plurality of suction ports 12 are provided on the peripheral surface of the accommodation hole 12.
a are arrayed in the circumferential direction. Each suction port 12a
Communicate with the cylinder bore 1a in a one-to-one relationship. Rotating shaft 4
The supply port 13b communicates with the suction port 12a sequentially with the rotation.
【００１４】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。これによりロータリ
バルブ１３内の供給通路１３ａから吸入ポート１２ａを
介してシリンダボア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-head 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 refrigerant gas sucked from the supply passage 13a in the rotary valve 13 into the cylinder bore 1a through the suction port 12a is compressed and discharged into the discharge chamber 3b.
【００１５】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 depending on 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.
【００１６】図２及び図４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 4, 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.
【００１７】図１、図４及び図５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の回転方向Ｒ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６は図１のＣ−Ｃ線拡大断面図である。As shown in FIGS. 1, 4 and 5, the head portion 10 of the single-headed piston 8 is formed with a thinning portion 8a.
The filleting portion 8a is recessed toward the central axis C 1 side on the peripheral surface side of the head 10 of the single-head piston 8 opposite to the rotation direction R of the swash plate 7 with respect to the central axis C 1 of the single-head piston 8. Has been done. FIG. 6 is an enlarged sectional view taken along the line CC of FIG.
【００１８】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の周面側かつ頭部１０の先端１０ａ1 側にはシ
ール面８ｂが肉取り部８ａ側に張り出し形成されてい
る。With respect to the central axis C 1 of the single-headed piston 8, a sealing surface is provided on the circumferential surface side of the head 10 of the single-headed piston 8 on the side opposite to the central axis C 0 of rotation of the swash plate 7 and on the tip 10a 1 side of the head 10. 8b is formed so as to project toward the meat removal portion 8a.
【００１９】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。型抜き形成は頭部１０の側面方
向に行われる。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。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. Die cutting is performed in the lateral direction of the head 10. 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.
【００２０】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。As shown in FIG. 1, the opening edge portion 1a 1 of the inner peripheral surface of the cylinder bore 1a on the side opposite to the rotation center axis C 0 of the swash plate 7 with respect to the center axis C 1 of the single- headed piston 8 is the opening of the cylinder bore 1a. Crank chamber 2a more than other areas
It projects to the side.
【００２１】図１の下側の片頭ピストン８は下死点位置
にある。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、頭部１０の周面がシリンダボア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 lower single-headed piston 8 in FIG. 1 is at the bottom dead center position. The inertial force of the one-headed piston 8 when the one-headed piston 8 is near the bottom dead center position is indicated 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. Reaction force Fs
Is the component force f 1 in the reciprocating direction of the single- headed piston 8 and the swash plate 7
Is decomposed into a component force f 2 in a direction away from the rotation center axis C 0 in the radial direction. The single-headed piston 8 tends to incline due to the component force f 2 , and the peripheral surface of the head 10 receives a reaction force Fa from the inner peripheral surface of the cylinder bore 1 a against the component force f 2 (pressing force), and the tip 10 a of the head 10 The edge portion 10a 1 receives a reaction force Fb against the component force f 2 (pressing force) from the inner peripheral surface of the cylinder bore 1a.
【００２２】斜板７の傾きをθ、頭部１０の先端１０ａ
から開口縁部位１ａ1 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，Ｌ
1 ，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
L 1 the distance to the opening edge portion 1a 1 from the distance from the tip 10a of the head 10 to the position P and L 2, theta, L
Between 1 , L 2 , F 0 , Fs, Fa and Fb, equation (1),
There are relationships shown in (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.
【００２３】本実施例では、肉取り部８ａはシリンダボ
ア１ａの開口縁部位１ａ1 との接触領域から外れてい
る。従って、開口縁部位１ａ1 を許容される範囲で延出
すれば距離Ｌ1 を稼ぐことができ、反力Ｆａ，Ｆｂの低
減化を図ることができる。片頭ピストン８が下死点位置
と上死点位置との中間位置から上死点位置側にあると圧
縮反力が慣性力に対する反力を上回るが、このときの分
力ｆ2 は回転中心軸線Ｃ 0 側を向く。従って、中心軸線
Ｃ1 に関して回転中心軸線Ｃ0 側の頭部１０の周面側が
シリンダボア１ａの内周面に押し付けられるが、肉取り
部８ａは頭部１０の周面の押し付け領域から外れてい
る。In this embodiment, the meat removing portion 8a is a cylinder
Opening edge part 1a of a1Out of contact area with
It Therefore, the opening edge portion 1a1Extended within the allowable range
Distance L1Can be earned, and the reaction forces Fa and Fb are low.
Can be reduced. One-headed piston 8 is at the bottom dead center position
From the middle position between the top dead center position and the top dead center position.
The reaction force exceeds the reaction force against the inertial force, but
Force f2Is the rotation center axis C 0Turn to the side. Therefore, the central axis
C1With respect to the rotation center axis C0The peripheral surface of the side head 10
It is pressed against the inner peripheral surface of the cylinder bore 1a, but
The portion 8a is out of the pressing area on the peripheral surface of the head 10.
It
【００２４】図１の上側の片頭ピストン８は上死点位置
付近にあり、シール面８ｂは吸入ポート１２ａの周囲を
包囲する。この包囲により吸入ポート１２ａ周辺のシー
ル性が高められ、吸入ポート１２ａ内に残留する高圧冷
媒ガスが頭部１０の周面に沿ってクランク室２ａ側に洩
れることが防止される。The upper single-head piston 8 in FIG. 1 is near the top dead center position, and the sealing surface 8b surrounds the suction port 12a. This surrounding improves the sealing property around the suction port 12a, and prevents the high-pressure refrigerant gas remaining in the suction port 12a from leaking to the crank chamber 2a side along the peripheral surface of the head 10.
【００２５】片頭ピストン８が下死点位置と上死点位置
との中間位置付近にある場合、斜板７が片頭ピストン８
に対して図７に示すような傾き状態で矢印Ｒ方向に回転
する。片頭ピストン８が前記中間位置付近にある場合に
は圧縮反力が慣性力の反力を上回り、圧縮反力の分力が
矢印Ｑ方向に作用する。そのため、シリンダボア１ａの
開口縁と頭部１０の側面とが当接するが、肉取り部８ａ
はこの側面とは反対側にあり、肉取り部８ａの縁部とシ
リンダボア１ａの開口縁との擦れ合いは生じない。When the single-headed piston 8 is located near the middle position between the bottom dead center position and the top dead center position, the swash plate 7 moves toward the single-headed piston 8
On the other hand, it rotates in the direction of arrow R in the tilted state as shown in FIG. When the single-headed piston 8 is near the intermediate position, the compression reaction force exceeds the reaction force of the inertial force, and the component force of the compression reaction force acts in the arrow Q direction. Therefore, the opening edge of the cylinder bore 1a and the side surface of the head portion 10 come into contact with each other.
Is on the side opposite to this side surface, and the edge portion of the chamfered portion 8a and the opening edge of the cylinder bore 1a do not rub against each other.
【００２６】図７に示すように首部９の支持凹部９ａの
周囲には傾斜面９ｃが形成されている。この傾斜面９ｃ
は斜板７との干渉を防止する上で有効である。型抜き形
成は頭部１０の側面方向に行われるため、傾斜面９ｃの
形成は型抜き形成のみで可能である。As shown in FIG. 7, an inclined surface 9c is formed around the support recess 9a of the neck 9. This inclined surface 9c
Is effective in preventing interference with the swash plate 7. Since the die-cutting formation is performed in the lateral direction of the head 10, the inclined surface 9c can be formed only by the die-cutting formation.
【００２７】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８に示すように吸入室３ａから
冷媒ガスをシリンダボア１ａに吸入すると共に、シリン
ダボア１ａから冷媒ガスを吐出室３ｂへ吐出する揺動斜
板式圧縮機の片頭ピストン８Ａにも本発明を適用でき
る。片頭ピストン８Ａは前記実施例の片頭ピストン８と
はシール面８ｂを無くした点のみが異なり、肉取り部８
ａは片頭ピストン８の場合と同様の位置に設けられてい
る。ロータリバルブを用いない揺動斜板式圧縮機ではシ
ール面８ｂは不要であり、シール面８ｂを無くせばそれ
だけ片頭ピストン８Ａが軽量になる。The present invention is, of course, not limited to the above-mentioned embodiment. For example, as shown in FIG. 8, the refrigerant gas is sucked into the cylinder bore 1a from the suction chamber 3a, and the refrigerant gas is discharged from the cylinder bore 1a into the discharge chamber 3b. The present invention can be applied to the single-headed piston 8A of the swinging swash plate type compressor for discharging. The single-headed piston 8A differs from the single-headed piston 8 of the above-described embodiment only in that the sealing surface 8b is eliminated, and the chamfered portion 8 is formed.
a is provided at the same position as in the case of the single-headed piston 8. The swash plate compressor that does not use a rotary valve does not require the sealing surface 8b, and the elimination of the sealing surface 8b reduces the weight of the single-headed piston 8A.
【００２８】又、本発明では図９〜図１１に示す片頭ピ
ストンの形状構成も可能である。図９の片頭ピストン８
Ｂでは肉取り部８ｃが片頭ピストン８Ｂの中心軸線に関
して斜板７の回転方向側の頭部１０の周面側に設けられ
ている。肉取り部８ｃの縁部８ｃ1 は圧縮反力の分力Ｑ
によってシリンダボア１ａの開口縁と擦れ易くなるが、
縁部８ｃ1 側の壁厚を増やすことにより縁部８ｃ1 とシ
リンダボア１ａの開口縁との擦れによるダメージを抑制
することができる。Further, in the present invention, the shape configuration of the single-headed piston shown in FIGS. 9 to 11 is also possible. Single-headed piston 8 in FIG.
In B, the chamfered portion 8c is provided on the peripheral surface side of the head portion 10 on the rotation direction side of the swash plate 7 with respect to the central axis of the single-headed piston 8B. The edge portion 8c 1 of the meat removing portion 8c has a component force Q of the compression reaction force.
Makes it easier to rub against the opening edge of the cylinder bore 1a,
It is possible to suppress the damage due to rubbing with the opening edge of the edge portion 8c 1 and the cylinder bore 1a by increasing the wall thickness of the edge portion 8c 1 side.
【００２９】図１０及び図１１の片頭ピストン８Ｃでは
肉取り部８ａ，８ｃが片頭ピストン８Ｃの中心軸線に関
して斜板７の回転方向側及び反対側の頭部１０の周面側
に設けられている。この片頭ピストン８Ｃは前記各実施
例の片頭ピストンより一層軽量になる。この片頭ピスト
ン８Ｃにおいても肉取り部８ｃの縁部８ｃ1 はシリンダ
ボア１ａの開口縁と擦れ易くなるが、縁部８ｃ1 側の壁
厚を増やして縁部８ｃ 1 とシリンダボア１ａの開口縁と
の擦れによるダメージの抑制が図られている。In the single-headed piston 8C shown in FIGS. 10 and 11,
The meat removing parts 8a and 8c are related to the central axis of the single-headed piston 8C.
Then, the rotation surface side of the swash plate 7 and the peripheral surface side of the head 10 on the opposite side
It is provided in. This single-headed piston 8C is used for each of the above
It is even lighter than the example single-headed piston. This one-headed fixie
Edge 8c of the meat removal portion 8c1Is a cylinder
It becomes easier to rub against the opening edge of the bore 1a, but the edge 8c1Side wall
Increase the thickness and edge 8c 1And the opening edge of the cylinder bore 1a
The damage due to the rubbing of the is suppressed.
【００３０】あるいは図１２に示す片頭ピストン８Ｄ、
図１３に示す片頭ピストン８Ｅのように前記分力Ｑによ
る押し付け力を受ける荷重受け面８ｄを設けてもよい。Alternatively, the single-headed piston 8D shown in FIG.
A load receiving surface 8d that receives the pressing force by the component force Q may be provided as in the single-headed piston 8E shown in FIG.
【００３１】[0031]
【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方向側及び反対側の少な
くとも一方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 in detail above, according to the present invention, the central axis of the piston is located on the circumferential surface side of the head of at least one of the single-headed pistons on the rotational direction side and the opposite side of the swash plate with respect to the central axis of the piston. Since the recessed portion is provided toward the side, it is possible to reduce the weight of the single-headed piston having an integral structure and to prevent the wear of the sliding contact portion between the single-headed piston and the cylinder bore. Play.
【００３２】請求項２に記載の発明では、ロータリバル
ブ用の吸入ポートの周辺のシールを行なうためのシール
面を前記肉取り部側に張り出したので、ロータリバルブ
使用の揺動斜板式圧縮機に使用し得るという優れた効果
を奏する。According to the second aspect of the present invention, since the sealing surface for sealing the periphery of the intake port for the rotary valve is extended to the chamfered portion side, the swing swash plate type compressor using the rotary valve is provided. It has an excellent effect that it can be used.
【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】 図１のＢ−Ｂ線断面図である。FIG. 3 is a sectional view taken along line BB of FIG.
【図４】 片頭ピストンの斜視図である。FIG. 4 is a perspective view of a single-headed piston.
【図５】 片頭ピストンの斜視図である。FIG. 5 is a perspective view of a single-headed piston.
【図６】 図１のＣ−Ｃ線断面図である。6 is a cross-sectional view taken along the line CC of FIG.
【図７】 要部断面図である。FIG. 7 is a sectional view of an essential part.
【図８】 別例の圧縮機全体の側断面図である。FIG. 8 is a side sectional view of the entire compressor of another example.
【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.
【図１１】図１０の片頭ピストンの縦断面図である。11 is a longitudinal sectional view of the single-headed piston of FIG.
【図１２】片頭ピストンの別例を示す斜視図である。FIG. 12 is a perspective view showing another example of a single-headed piston.
【図１３】片頭ピストンの別例を示す斜視図である。FIG. 13 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，８ｃ…
肉取り部、８ｂ…シール面、９…首部、１０…頭部、１
０ａ1 …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 piston, 8a, 8c ...
Meat removing portion, 8b ... Sealing surface, 9 ... Neck portion, 10 ... Head portion, 1
0a 1 ... Tip, C 0 ... Rotation center axis, C 1 ... Center axis.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 諸井 隆宏 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 Takahiro Moroi 2-chome, Toyota-cho, Kariya city, Aichi Prefecture Toyota Industries Corporation
Claims (2)
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方向側及び反対
側の少なくとも一方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 through a single-headed piston, in the swash plate rotation direction side with respect to the center axis of the piston, A piston in a rocking swash plate compressor in which at least one single-headed piston on the opposite side is provided with a chamfered portion recessed toward the central axis side of the piston on the peripheral surface side of the head.
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
の傾角を制御し、回転軸と一体的に回転するロータリバ
ルブを介してシリンダボアの周面に繋がる吸入ポートか
らシリンダボア内へ冷媒ガスを供給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方向側及び反対
側の少なくとも一方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、前記吸入ポートの周辺のシールを行なうためのシ
ール面を前記肉取り部側に張り出した揺動斜板式圧縮機
におけるピストン。2. A rotary motion of the swash plate is reciprocated by a shoe interposed between both surfaces of the swash plate tiltably supported by the rotary shaft and a neck portion of the one-head piston housed in the cylinder bore. 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 the single-headed piston, and connects to the peripheral surface of the cylinder bore via a rotary valve that rotates integrally with the rotary shaft. In an oscillating swash plate compressor that supplies refrigerant gas from the suction port into the cylinder bore, the piston is located on the circumferential surface side of the head of at least one of the single-headed pistons, which is the rotational direction side of the swash plate and the opposite side with respect to the central axis of the piston. In the swing swash plate type compressor in which a meat removal part is formed which is recessed toward the central axis side of the, and a sealing surface for sealing the periphery of the suction port is projected to the meat removal part side. Piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5332144A JP2924621B2 (en) | 1993-12-27 | 1993-12-27 | Piston in oscillating swash plate compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5332144A JP2924621B2 (en) | 1993-12-27 | 1993-12-27 | Piston in oscillating swash plate compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07189900A true JPH07189900A (en) | 1995-07-28 |
| JP2924621B2 JP2924621B2 (en) | 1999-07-26 |
Family
ID=18251640
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5332144A Expired - Fee Related JP2924621B2 (en) | 1993-12-27 | 1993-12-27 | Piston in oscillating swash plate compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2924621B2 (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0814261A2 (en) * | 1996-06-17 | 1997-12-29 | General Motors Corporation | Compressor piston |
| US5765464A (en) * | 1996-03-19 | 1998-06-16 | Sanden Corporation | Reciprocating pistons of piston-type compressor |
| US6024009A (en) * | 1997-05-16 | 2000-02-15 | Sanden Corporation | Reciprocating pistons of piston-type compressor |
| US6038960A (en) * | 1997-10-08 | 2000-03-21 | Sanden Corporation | Reciprocating pistons of piston-type compressor |
| EP0780572A3 (en) * | 1995-11-24 | 2000-10-04 | Calsonic Corporation | Swash-plate type compressor |
| EP1055817A3 (en) * | 1999-05-28 | 2001-05-02 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor wherein piston head has inner sliding portion for reducing local wear |
| US6324960B1 (en) | 1999-06-15 | 2001-12-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston for swash plate type compressor, including head portion having lubricant reservoir recess, and method of forming the recess |
| US6557454B2 (en) | 2000-07-12 | 2003-05-06 | Sanden Corporation | Compressor pistons |
| US6941852B1 (en) | 2004-02-26 | 2005-09-13 | Delphi Technologies, Inc. | Unitary hollowed piston with improved structural strength |
| WO2006006344A1 (en) * | 2004-07-08 | 2006-01-19 | Matsushita Electric Industrial Co., Ltd. | Compressor |
| US10145370B2 (en) | 2016-03-30 | 2018-12-04 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type swash plate compressor |
| US10267299B2 (en) | 2016-03-30 | 2019-04-23 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type swash plate compressor |
-
1993
- 1993-12-27 JP JP5332144A patent/JP2924621B2/en not_active Expired - Fee Related
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0780572A3 (en) * | 1995-11-24 | 2000-10-04 | Calsonic Corporation | Swash-plate type compressor |
| US5765464A (en) * | 1996-03-19 | 1998-06-16 | 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 |
| US6024009A (en) * | 1997-05-16 | 2000-02-15 | Sanden Corporation | Reciprocating pistons of piston-type compressor |
| DE19821915C2 (en) * | 1997-05-16 | 2003-10-30 | Sanden Corp | Piston type fluid displacer |
| US6038960A (en) * | 1997-10-08 | 2000-03-21 | Sanden Corporation | Reciprocating pistons of piston-type 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 |
| EP1055817A3 (en) * | 1999-05-28 | 2001-05-02 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type compressor wherein piston head has inner sliding portion for reducing local wear |
| US6324960B1 (en) | 1999-06-15 | 2001-12-04 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston for swash plate type compressor, including head portion having lubricant reservoir recess, and method of forming the recess |
| US6557454B2 (en) | 2000-07-12 | 2003-05-06 | Sanden Corporation | Compressor pistons |
| US6941852B1 (en) | 2004-02-26 | 2005-09-13 | Delphi Technologies, Inc. | Unitary hollowed piston with improved structural strength |
| WO2006006344A1 (en) * | 2004-07-08 | 2006-01-19 | Matsushita Electric Industrial Co., Ltd. | Compressor |
| US7478997B2 (en) | 2004-07-08 | 2009-01-20 | Panasonic Corporation | Compressor |
| US10145370B2 (en) | 2016-03-30 | 2018-12-04 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type swash plate compressor |
| US10267299B2 (en) | 2016-03-30 | 2019-04-23 | Kabushiki Kaisha Toyota Jidoshokki | Double-headed piston type swash plate compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2924621B2 (en) | 1999-07-26 |
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| A01 | Written decision to grant a patent or to grant a registration (utility model) |
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| LAPS | Cancellation because of no payment of annual fees |