JPH10196528A - Rotation preventing structure of piston in swash plate compressor - Google Patents

Rotation preventing structure of piston in swash plate compressor

Info

Publication number
JPH10196528A
JPH10196528A JP9002407A JP240797A JPH10196528A JP H10196528 A JPH10196528 A JP H10196528A JP 9002407 A JP9002407 A JP 9002407A JP 240797 A JP240797 A JP 240797A JP H10196528 A JPH10196528 A JP H10196528A
Authority
JP
Japan
Prior art keywords
swash plate
piston
peripheral surface
rotation
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP9002407A
Other languages
Japanese (ja)
Inventor
Isato Ikeda
勇人 池田
Masaaki Nishimoto
昌顕 西本
Motonobu Kawakami
素伸 川上
Tetsuya Yamaguchi
哲也 山口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyoda Automatic Loom Works Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyoda Automatic Loom Works Ltd filed Critical Toyoda Automatic Loom Works Ltd
Priority to JP9002407A priority Critical patent/JPH10196528A/en
Publication of JPH10196528A publication Critical patent/JPH10196528A/en
Pending legal-status Critical Current

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

PROBLEM TO BE SOLVED: To provide the rotation preventing structure of a piston in a swash plate compressor, which can improve durability, by reducing sliding resistance of the peripheral surface of a swash plate and a rotation regulating surface arranged on the shell part of the piston. SOLUTION: Extended parts 226, 227 are integrally formed in both end parts of the circumferential direction of the shell part 223 of a double-end piston 22 whose pair of head parts are connected to each other by the shell part 223. Circular arc-shaped rotation regulating surfaces 228, 229 are formed on the inner sides of these extended parts 226, 227, and brought into slide contact with the peripheral surface 341 of a swash plate 34. The end sliding parts of the rotation regulating surfaces 228, 229 of the extended parts 226, 227 are positioned further than the radius α of the piston 22 from the center axial line ε thereof, therefore the sliding resistance of the rotation regulating surfaces 228, 229 against the peripheral surface 341 of the swash plate 34 can be reduced.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】この発明は例えば車両空調装
置に用いられる斜板式圧縮機に関するものであり、さら
に詳しくは斜板の外周面に摺接するピストンの回動規制
面の摺動抵抗を低減して摩耗を抑制し、耐久性を向上す
ることができるピストンの回動防止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 type compressor for use in, for example, a vehicle air conditioner, and more particularly, to reducing a sliding resistance of a rotation restricting surface of a piston which slides on an outer peripheral surface of a swash plate. The present invention relates to a piston rotation preventing structure capable of suppressing wear and improving durability.

【０００２】[0002]

【従来の技術】一般に、両頭ピストン型の斜板式圧縮機
においては、複数のシリンダボアを有するシリンダブロ
ックの前後両端面に吸入室と吐出室を区画形成するフロ
ント及びリヤのハウジングが接合固定されている。シリ
ンダブロックの中央部に形成した斜板室には駆動シャフ
トにより揺動回転する斜板が収容され、該斜板の前後両
側面にはシューを介して前記シリンダボア内に収容され
た両頭ピストンが係留されている。そして、該両頭ピス
トンが斜板の回転運動により往復動されると、前記吸入
室からシリンダボア内の圧縮室へガスが吸入され、該圧
縮室内で圧縮されたガスは前記吐出室へ吐出される。2. Description of the Related Art In general, in a double head piston type swash plate type compressor, front and rear housings which define a suction chamber and a discharge chamber are fixedly joined to both front and rear end surfaces of a cylinder block having a plurality of cylinder bores. . The swash plate chamber formed in the center of the cylinder block accommodates a swash plate which is pivotally rotated by a drive shaft. On both front and rear sides of the swash plate, a double-headed piston accommodated in the cylinder bore is moored via shoes. ing. When the double-headed piston is reciprocated by the rotation of the swash plate, gas is sucked from the suction chamber into the compression chamber in the cylinder bore, and the gas compressed in the compression chamber is discharged to the discharge chamber.

【０００３】前記両頭ピストンはシリンダボア内で往復
動される際、圧縮反力や斜板の回転揺動運動によりその
中心軸線の周りで回動しようとする。この両頭ピストン
の回動防止は前記斜板の外周面を利用して行われる。こ
の回動防止構造を以下に説明する。[0003] When the double-headed piston is reciprocated in the cylinder bore, it tends to rotate around its central axis due to the compression reaction force and the rotational swinging motion of the swash plate. The rotation of the double-headed piston is prevented by using the outer peripheral surface of the swash plate. This rotation preventing structure will be described below.

【０００４】図７，８に示すように、両頭ピストン２２
は前後一対の頭部２２１，２２２と両頭部２２１，２２
２を連結する円弧状の胴部２２３とにより一体的に構成
されている。前記胴部２２３の内側の回動規制面２２
８，２２９は図８に示すように、斜板３４の外周面３４
１に対し組付上の所定のクリアランスをもって摺接する
ようになっている。そして、両頭ピストン２２が圧縮反
力や斜板３４の回転運動によりその中心軸線εの周りで
回動しようとするが、前記胴部２２３の回動規制面２２
８，２２９が斜板３４の外周面３４１に摺接して回動が
阻止される。[0004] As shown in FIGS.
Is a pair of front and rear heads 221 and 222 and both heads 221 and 22
2 are integrally formed with an arc-shaped body 223 connecting the two. The rotation regulating surface 22 inside the body portion 223
8, 229 are outer peripheral surfaces 34 of the swash plate 34 as shown in FIG.
1 comes into sliding contact with a predetermined clearance on assembly. Then, the double-headed piston 22 tries to rotate around its central axis ε due to the compression reaction force or the rotational movement of the swash plate 34, but the rotation restricting surface 22 of the body 223.
8, 229 slides on the outer peripheral surface 341 of the swash plate 34 to prevent rotation.

【０００５】[0005]

【発明が解決しようとする課題】ところが、上記斜板式
圧縮機のピストンの回動防止構造においては、前記胴部
２２３の回動規制面２２８，２２９の中心軸線εからの
最大距離が両頭ピストン２２の半径α以内に限定されて
いるので、斜板３４の外周面３４１に対する回動規制面
２２８，２２９の先端縁の摺動抵抗を低減するには限界
があった。この理由は両頭ピストン２２の回動力が同じ
であっても、回動規制面２２８，２２９の先端縁が中心
軸線εに近づけば近づくほど、梃子の原理で斜板３４の
外周面３４１に対する先端縁の押し付け力が増大するこ
とから明らかである。このため前記胴部２２３の回動規
制面２２８，２２９の摩耗が進行し易く耐久性が低下す
るという問題があった。又、斜板３４の外周面と胴部２
２３の摺接面との間には、前述したように組付上のクリ
アランス（０．１〜０．２ｍｍ）があり、前記摩耗が進
行するとこのクリアランスが大きくなって斜板の外周面
３４１と胴部２２３の回動規制面２２８，２２９との衝
突による騒音が大きくなるという問題もあった。However, in the structure for preventing the rotation of the piston of the swash plate type compressor, the maximum distance of the rotation restricting surfaces 228 and 229 of the body portion 223 from the center axis ε is the double-headed piston 22. Therefore, there is a limit in reducing the sliding resistance of the leading edge of the rotation regulating surfaces 228 and 229 with respect to the outer peripheral surface 341 of the swash plate 34. The reason for this is that even if the rotation power of the double-headed piston 22 is the same, the closer the leading edges of the rotation regulating surfaces 228 and 229 are to the central axis ε, the more the leading edge of the swash plate 34 with respect to the outer peripheral surface 341 by the principle of leverage. It is clear from the fact that the pressing force of the increases. For this reason, there has been a problem that the rotation restricting surfaces 228 and 229 of the body portion 223 are easily worn and the durability is reduced. The outer peripheral surface of the swash plate 34 and the body 2
As described above, there is a clearance (0.1 to 0.2 mm) on the assembly between the sliding surface of the swash plate 23 and the outer peripheral surface 341 of the swash plate. There is also a problem that noise due to collision with the rotation regulating surfaces 228 and 229 of the body 223 increases.

【０００６】この発明の目的は上記従来の技術に存する
問題点を解消して、斜板の外周面とピストンの胴部に設
けた回動規制面との摺動抵抗を低減して耐久性を向上す
ることができるとともに、斜板の外周面と回動規制面と
のクリアランスの増大による騒音を抑制することができ
る斜板式圧縮機におけるピストンの回動防止構造を提供
することにある。SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems in the prior art and reduce the sliding resistance between the outer peripheral surface of the swash plate and the rotation regulating surface provided on the body of the piston, thereby improving durability. It is an object of the present invention to provide a structure for preventing rotation of a piston in a swash plate compressor, which can improve noise and suppress noise caused by increase in clearance between an outer peripheral surface of a swash plate and a rotation restricting surface.

【０００７】[0007]

【課題を解決するための手段】請求項１記載の発明は上
記目的を達成するため、複数のシリンダボアを有するシ
リンダブロックの端面に吸入室と吐出室を区画形成する
ハウジングを接合固定し、斜板室に駆動シャフトにより
回転する斜板を収容し、該斜板の前後両側面にシューを
介して前記シリンダボア内に収容されたピストンを係留
し、該ピストンを斜板の回転運動により往復動させて、
前記吸入室からシリンダボア内の圧縮室へガスを吸入
し、該圧縮室内で圧縮されたガスを前記吐出室へ吐出す
るようにした斜板式圧縮機において、前記ピストンは斜
板に係留される胴部を備え、胴部の周方向両端縁のうち
少なくとも一方の端縁に対し、該胴部から側方へ延びて
前記斜板の外周面に接触してピストンの回動を阻止する
膨出部を設けている。According to a first aspect of the present invention, a housing defining a suction chamber and a discharge chamber is joined and fixed to an end face of a cylinder block having a plurality of cylinder bores. A swash plate that is rotated by a drive shaft is housed therein, and a piston housed in the cylinder bore is moored on both front and rear side surfaces of the swash plate via shoes, and the piston is reciprocated by the rotational motion of the swash plate.
In a swash plate type compressor configured to suck gas from the suction chamber into a compression chamber in a cylinder bore and discharge the gas compressed in the compression chamber to the discharge chamber, the piston is moored to a swash plate. A bulging portion that extends laterally from the trunk portion and contacts the outer peripheral surface of the swash plate to prevent rotation of the piston with respect to at least one of the two peripheral edges of the trunk portion. Provided.

【０００８】請求項２記載の発明は、請求項１におい
て、前記膨出部をピストン軸線方向から見て前記シリン
ダボアより外方に延出している。請求項３記載の発明
は、請求項１又は２において、前記膨出部を前記胴部の
周方向両端縁に設けている。According to a second aspect of the present invention, in the first aspect, the bulging portion extends outward from the cylinder bore when viewed from the axial direction of the piston. According to a third aspect of the present invention, in the first or second aspect, the bulging portion is provided at both circumferential edges of the body.

【０００９】請求項４記載の発明は、請求項１〜３のい
ずれか１項において、前記膨出部を前記胴部と一体に形
成している。請求項５記載の発明は、請求項１〜４のい
ずれか１項において、前記膨出部の内周面の曲率半径
を、斜板の外周面の曲率半径と同じに設定している。According to a fourth aspect of the present invention, in any one of the first to third aspects, the bulging portion is formed integrally with the trunk portion. According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the radius of curvature of the inner peripheral surface of the bulging portion is set to be the same as the radius of curvature of the outer peripheral surface of the swash plate.

【００１０】請求項６記載の発明は、請求項１〜４のい
ずれか１項において、前記膨出部の内周面の曲率半径
を、斜板の外周面の曲率半径よりも小さく設定してい
る。請求項７記載の発明は、請求項１，２，３，５，６
のいずれか１項において、前記膨出部を前記胴部と別体
に形成している。According to a sixth aspect of the present invention, in any one of the first to fourth aspects, the radius of curvature of the inner peripheral surface of the bulging portion is set smaller than the radius of curvature of the outer peripheral surface of the swash plate. I have. The invention according to claim 7 is the invention according to claims 1, 2, 3, 5, 6
In any one of the above, the bulging portion is formed separately from the trunk portion.

【００１１】請求項８記載の発明は、請求項４におい
て、ピストンの鍛造工程において前記胴部の周方向両側
に本来膨出形成される部位を利用して前記膨出部を形成
している。According to an eighth aspect of the present invention, in the fourth aspect, in the piston forging step, the bulging portion is formed by using a portion which is originally bulging on both circumferential sides of the body.

【００１２】請求項９記載の発明は、請求項１〜８のい
ずれか１項において、斜板式圧縮機を両頭ピストン型斜
板式圧縮機としている。According to a ninth aspect of the present invention, in any one of the first to eighth aspects, the swash plate type compressor is a double-headed piston type swash plate type compressor.

【００１３】[0013]

【発明の実施の形態】BEST MODE FOR CARRYING OUT THE INVENTION

（第１実施形態）以下、この発明の第１実施形態を図１
〜図４に基づいて詳細に説明する。(First Embodiment) Hereinafter, a first embodiment of the present invention will be described with reference to FIG.
This will be described in detail with reference to FIG.

【００１４】図１に示すように互いに対設される前後
（左右）一対のシリンダブロック１１，１２のフロント
側端面及びリヤ側端面にはバルブプレート１３，１４を
介してフロントハウジング１５及びリヤハウジング１６
が接合されている。これらのシリンダブロック１１，１
２、バルブプレート１３，１４及びフロントハウジング
１５、リヤハウジング１６は複数の締付ボルト１７によ
って互いに接合固定されている。As shown in FIG. 1, front and rear end faces of a pair of front and rear (left and right) cylinder blocks 11 and 12 which are opposed to each other are interposed via valve plates 13 and 14, respectively.
Are joined. These cylinder blocks 11, 1
2. The valve plates 13 and 14, the front housing 15, and the rear housing 16 are joined and fixed to each other by a plurality of tightening bolts 17.

【００１５】前記シリンダブロック１１，１２の中心孔
には駆動シャフト１８が前後一対のラジアルベアリング
１９，２０を介して回転可能に支持されている。前記シ
リンダブロック１１，１２の中心部には斜板室２１が形
成され、外周側にはシリンダボア１１１，１２１が所定
間隔をおいて複数箇所に形成されている。前記斜板室２
１にはシリンダブロック１２の外周に設けた吸入フラン
ジ（図示略）から冷媒ガスが導入されるようになってい
る。各シリンダボア１１１，１２１には両頭ピストン２
２が前後方向の往復動可能に収容されており、両頭ピス
トン２２の端面とバルブプレート１３，１４との間には
圧縮室２３が形成されている。A drive shaft 18 is rotatably supported in the center holes of the cylinder blocks 11 and 12 via a pair of front and rear radial bearings 19 and 20. A swash plate chamber 21 is formed at the center of the cylinder blocks 11 and 12, and cylinder bores 111 and 121 are formed at a plurality of locations at predetermined intervals on the outer peripheral side. The swash plate chamber 2
1 is configured such that refrigerant gas is introduced from a suction flange (not shown) provided on the outer periphery of the cylinder block 12. Each cylinder bore 111, 121 has a double-headed piston 2
The compression chamber 23 is formed between the end face of the double-headed piston 22 and the valve plates 13, 14.

【００１６】図１に示すように前記フロント及びリヤの
ハウジング１５，１６には外周寄りに吸入室２４，２５
が中央部寄りに吐出室２６，２７がそれぞれ区画形成さ
れている。前記バルブプレート１３，１４には従来周知
の吸入弁機構２９，２９が設けられている。前記吸入室
２４，２５は前記ボルト１７の挿通孔を兼用する吸入通
路３０，３１によって前記斜板室２１と連通されてい
る。前記バルブプレート１３，１４には従来周知の吐出
弁機構３２，３２が設けられている。吐出室２６，２７
はバルブプレート１３，１４及びシリンダブロック１
１，１２に形成した吐出通路３３（図２参照）及び吐出
フランジ（図示略）によって外部冷媒回路と連通されて
いる。As shown in FIG. 1, the front and rear housings 15 and 16 have suction chambers 24 and 25 near the outer periphery.
Are formed near the center, respectively. The valve plates 13 and 14 are provided with conventionally known suction valve mechanisms 29 and 29. The suction chambers 24 and 25 are connected to the swash plate chamber 21 by suction passages 30 and 31 which also serve as insertion holes for the bolts 17. The valve plates 13 and 14 are provided with conventionally known discharge valve mechanisms 32 and 32, respectively. Discharge chambers 26, 27
Are the valve plates 13 and 14 and the cylinder block 1
Discharge passages 33 (see FIG. 2) and discharge flanges (not shown) formed in the first and second parts 12 communicate with the external refrigerant circuit.

【００１７】前記斜板室２１には前記駆動シャフト１８
に嵌合固定した斜板３４が収容され、前記両頭ピストン
２２はシュー３５，３６を介して斜板３４に係留されて
いる。前記斜板３４のボス部とシリンダブロック１１，
１２の斜板室２１を形成する側壁との間にはスラストベ
アリング３７，３８が介在されている。そして、駆動シ
ャフト１８が回転されると斜板３４が揺動回転され、両
頭ピストン２２がシリンダボア１１１，１２１内で前後
方向に往復動され、圧縮動作が行われる。The swash plate chamber 21 contains the drive shaft 18.
A swash plate 34 fitted and fixed to the swash plate 34 is accommodated, and the double-headed piston 22 is moored to the swash plate 34 via shoes 35 and 36. The boss of the swash plate 34 and the cylinder block 11,
Thrust bearings 37 and 38 are interposed between the swash plate chamber 21 and the side wall forming the swash plate chamber 21. When the drive shaft 18 is rotated, the swash plate 34 swings and rotates, and the double-headed piston 22 reciprocates in the cylinder bores 111 and 121 in the front-rear direction, thereby performing a compression operation.

【００１８】次に、本発明の要部である両頭ピストン２
２の回動防止構造について説明する。前記両頭ピストン
２２は前後両端の頭部２２１，２２２と、両頭部２２
１，２２２を一体的に連結する胴部２２３とにより構成
されている。又、前記頭部２２１，２２２の間には胴部
２２３の内側において前記斜板３４の外周部を係留する
凹所２２４が形成されている。この凹所２２４の前後両
側面には前記シュー３５，３６の球面部を摺接係合する
係合凹部２２５，２２５が形成されている。Next, the double-headed piston 2 which is an essential part of the present invention
The rotation preventing structure 2 will be described. The double-headed piston 22 has front and rear heads 221 and 222,
1 and 222 are integrally connected to each other. A recess 224 is formed between the heads 221 and 222 to anchor the outer periphery of the swash plate 34 inside the body 223. Engaging concave portions 225 and 225 are formed on both front and rear side surfaces of the concave portion 224 to slidably engage the spherical portions of the shoes 35 and 36.

【００１９】前記両頭ピストン２２の胴部２２３の周方
向の両端部には、側方に張り出すように膨出部２２６，
２２７が一体に形成されている。膨出部２２６，２２７
はピストン軸線方向において凹所２２４に対応する位置
に形成され、この膨出部２２６，２２７の内側面には斜
板３４の外周面３４１と摺接してピストン２２の中心軸
線εの周りでの回動を規制する回動規制面２２８，２２
９が形成されている。前記回動規制面２２８，２２９の
曲率半径は斜板３４の外周面の曲率半径と同じに設定さ
れている。又、図２及び図３から明らかなように、膨出
部２２６，２２７は軸線方向から見て、シリンダボア１
１１，１２１（即ち頭部２２１，２２２）より外方に延
出されており、膨出部２２６，２２７の両先端間の距離
は、シリンダボア１１１，１２１の直径より大きく設定
されている。At both ends of the body 223 of the double-headed piston 22 in the circumferential direction, bulging portions 226 and 226 are provided so as to project laterally.
227 are integrally formed. Swelling parts 226, 227
Are formed at positions corresponding to the recesses 224 in the axial direction of the piston, and the inner surfaces of the bulging portions 226 and 227 are brought into sliding contact with the outer peripheral surface 341 of the swash plate 34 to rotate around the central axis ε of the piston 22. Rotation restriction surfaces 228, 22 for restricting movement
9 are formed. The radius of curvature of the rotation restricting surfaces 228 and 229 is set to be the same as the radius of curvature of the outer peripheral surface of the swash plate 34. Further, as is clear from FIGS. 2 and 3, the bulging portions 226, 227 have the cylinder bore 1
11 and 121 (that is, the heads 221 and 222), the distance between both ends of the bulging portions 226 and 227 is set to be larger than the diameter of the cylinder bores 111 and 121.

【００２０】次に、前記のように構成した斜板式圧縮機
の動作を説明する。今、駆動シャフト１８の回転により
斜板３４が回転されるとシュー３５，３６を介して各両
頭ピストン２２がシリンダボア１１１，１２１内で前後
方向に往復動される。この両頭ピストン２２の往復運動
により吸入フランジ（図示略）から斜板室２１内に導か
れた冷媒ガスは該斜板室２１からシリンダブロッ１１，
１２に形成した吸入通路３０，３１を通って吸入室２
４，２５に導かれる。この吸入室２４，２５内の冷媒ガ
スはバルブプレート１３，１４に設けた吸入弁機構２
９，２９からシリンダボア内の圧縮室２３に吸入され
る。圧縮されたガスは、吐出弁機構３２，３２から吐出
室２６，２７へ吐出される。さらに、吐出室２６，２７
に吐出された冷媒ガスは吐出通路３３を介して吐出フラ
ンジ（図示略）から外部冷媒回路に圧送され、例えば車
両空調装置の蒸発器に送られて、室内の空調に供され
る。Next, the operation of the swash plate compressor constructed as described above will be described. Now, when the swash plate 34 is rotated by the rotation of the drive shaft 18, each double-headed piston 22 reciprocates in the cylinder bores 111 and 121 in the front-rear direction via the shoes 35 and 36. The refrigerant gas guided into the swash plate chamber 21 from the suction flange (not shown) by the reciprocating motion of the double-headed piston 22 is transferred from the swash plate chamber 21 to the cylinder block 11,
The suction chamber 2 passes through suction passages 30 and 31 formed in the suction chamber 2.
4 and 25. Refrigerant gas in the suction chambers 24 and 25 is supplied to a suction valve mechanism 2 provided on valve plates 13 and 14.
It is sucked from 9, 29 into the compression chamber 23 in the cylinder bore. The compressed gas is discharged from the discharge valve mechanisms 32, 32 to the discharge chambers 26, 27. Further, the discharge chambers 26 and 27
Is discharged from a discharge flange (not shown) through a discharge passage 33 to an external refrigerant circuit, and is sent to, for example, an evaporator of a vehicle air conditioner to be used for indoor air conditioning.

【００２１】前述した圧縮動作において、両頭ピストン
２２は、圧縮室２３内のガスの圧縮反力あるいは斜板３
４の揺動回転によりシュー３５，３６を介して伝達され
る外力によって、中心軸線εの周りで回動しようとす
る。しかし、その回動力は膨出部２２６，２２７の内周
面に形成した回動規制面２２８，２２９が斜板３４の外
周面３４１に摺接することによって阻止される。In the above-described compression operation, the double-headed piston 22 applies the gas compression reaction force in the compression chamber 23 or the swash plate 3.
Due to the external force transmitted through the shoes 35 and 36 due to the swinging rotation of No. 4, it is about to rotate around the central axis ε. However, the turning power is prevented by the rotation regulating surfaces 228 and 229 formed on the inner peripheral surfaces of the bulging portions 226 and 227 slidingly contacting the outer peripheral surface 341 of the swash plate 34.

【００２２】次に、第１実施形態の構成により得られる
作用効果について説明する。 ○ 前記第１実施形態では両頭ピストン２２の胴部２２
３の周方向の両端部に膨出部２２６，２２７を形成し、
両膨出部２２６，２２７をピストン軸線方向からみてシ
リンダボア１１１，１２１より外方に延出し、膨出部２
２６，２２７の内側に形成した回動規制面２２８，２２
９を斜板３４の外周面３４１に摺接するようにした。こ
のため、図４に示すように両頭ピストン２２の中心軸線
εから斜板３４の外周面３４１に対する回動規制面２２
８，２２９の先端摺接部までの距離βをピストンの半径
α以上に大きくすることができる。従って、回動規制面
２２８，２２９の先端摺接部における押圧力を梃子の原
理で抑制して摺動抵抗を低減でき、その摺接面の摩耗を
抑制し、耐久性を向上することができる。Next, the operation and effect obtained by the configuration of the first embodiment will be described. In the first embodiment, the body 22 of the double-headed piston 22 is used.
3, bulging portions 226, 227 are formed at both ends in the circumferential direction,
The two bulging portions 226 and 227 extend outward from the cylinder bores 111 and 121 when viewed from the piston axial direction, and
Rotation regulating surfaces 228, 22 formed inside 26, 227
9 is in sliding contact with the outer peripheral surface 341 of the swash plate 34. For this reason, as shown in FIG. 4, the rotation regulating surface 22 from the center axis ε of the double-headed piston 22 to the outer peripheral surface 341 of the swash plate 34.
8,229 to the tip sliding contact portion can be made larger than the radius α of the piston. Accordingly, the pressing force at the sliding end portions of the rotation regulating surfaces 228 and 229 can be suppressed based on the principle of leverage, thereby reducing the sliding resistance, suppressing the abrasion of the sliding contact surfaces, and improving the durability. .

【００２３】又、膨出部２２６，２２７の回動規制面２
２８，２２９の摩耗が抑制できるので、該回動規制面２
２８，２２９と斜板３４の外周面３４１との間の組付上
の寸法公差に基づくクリアランスの増大を無くして、回
動規制面２２８，２２９の外周面３４１への衝突による
騒音を抑制することができる。The rotation restricting surface 2 of the bulging portions 226, 227
28, 229 can be suppressed.
Eliminating an increase in clearance due to a dimensional tolerance in assembly between the outer peripheral surface 341 of the swash plate 34 and the outer peripheral surface 341 of the swash plate 34, and suppressing noise caused by collision of the rotation restricting surfaces 228, 229 with the outer peripheral surface 341. Can be.

【００２４】○ 前記第１実施形態では両頭ピストン２
２の胴部２２３の周方向の両端部に膨出部２２６，２２
７を形成したので、一方のみに設ける場合と比較して回
動規制面２２８，２２９と斜板３４の外周面３４１との
摺接面の摩耗を抑制し、耐久性を向上し易く、騒音の低
減が図り易い。In the first embodiment, the double-headed piston 2
Bulging portions 226 and 22 at both circumferential ends of the body portion 223
7, the abrasion of the sliding contact surface between the rotation regulating surfaces 228, 229 and the outer peripheral surface 341 of the swash plate 34 is suppressed as compared with the case where only one of them is provided. Reduction is easy.

【００２５】○ 前記第１実施形態では、回動規制面２
２８，２２９の曲率半径を斜板３４の外周面３４１の曲
率半径と同一にしたので、外周面３４１に対し回動規制
面２２８，２２９を面接触させてその摩耗を抑制するこ
とができる。In the first embodiment, the rotation restricting surface 2
Since the radii of curvature of the swash plate 34 are the same as the radii of curvature of the swash plate 34, the rotation restricting surfaces 228 and 229 are brought into surface contact with the outer peripheral surface 341 to suppress the wear thereof.

【００２６】○ 前記第１実施形態では胴部２２３に対
し両膨出部２２６，２２７を一体に形成したので、両頭
ピストン２２の成型時に同時成型でき、製造を容易に行
いコストダウンを図ることができる。In the first embodiment, since the both bulging portions 226 and 227 are formed integrally with the body portion 223, they can be molded simultaneously when the double-headed piston 22 is molded, thereby facilitating manufacture and reducing costs. it can.

【００２７】なお、前記第１実施形態は、次のように変
更することもできる。 ・ 前記両膨出部２２６，２２７の内側の回動規制面２
２８，２２９の曲率半径を斜板３４の外周面の曲率半径
よりも小さくして、膨出部２２６，２２７の先端部側の
回動規制面２２８，２２９が斜板３４の外周面３４１に
優先的に接触するようにすること。The first embodiment can be modified as follows. A rotation regulating surface 2 inside the bulging portions 226, 227;
The radii of curvature of the swash plate 34 are made smaller than the radii of curvature of the outer peripheral surface of the swash plate 34, and the rotation regulating surfaces 228, 229 on the tip end side of the bulging portions 226, 227 have priority over the outer peripheral surface 341 of the swash plate 34. To make contact.

【００２８】この実施形態ではシリンダボア内で回動し
ようとするピストン２２の膨出部２２６，２２７の先端
部側の回動規制面２２８，２２９の斜板３４の外周面に
対する押圧力が最も小さくなり、摺動抵抗が最も小さい
部分を有効に利用することができる。In this embodiment, the pressing force of the rotation restricting surfaces 228, 229 on the distal end side of the bulging portions 226, 227 of the piston 22 that is about to rotate in the cylinder bore against the outer peripheral surface of the swash plate 34 is minimized. In addition, the portion having the smallest sliding resistance can be effectively used.

【００２９】・ 前記両頭ピストン２２の鍛造工程にお
いて前記胴部２２３に周方向両側に本来張り出し形成さ
れる部位を利用して膨出部２２６，２２７を形成するこ
と。この実施形態では膨出部２２６，２２７の形成をさ
らに容易に行うことができる。 （第２実施形態）次に、本発明の第２実施形態を図５に
基づいて説明する。In the forging process of the double-headed piston 22, bulging portions 226 and 227 are formed on the body portion 223 by using portions which are originally formed on both sides in the circumferential direction. In this embodiment, the formation of the bulging portions 226 and 227 can be performed more easily. (Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG.

【００３０】この第２実施形態では、前述した第１実施
形態の圧縮機において胴部２２３に対し一体型の膨出部
２２６，２２７に代えて、板状の部材により形成した別
体の膨出部４１を胴部２２３に嵌装している。In the second embodiment, a separate bulge formed by a plate-like member is used instead of the bulges 226 and 227 integrated with the body 223 in the compressor of the first embodiment described above. The part 41 is fitted on the body part 223.

【００３１】従って、第２実施形態においては、膨出部
４１の材料をピストン２２の材質に影響されることな
く、鉄系材料よりなる斜板３４の材質に適合した耐摩耗
性の高い材料を選定することができる。 （第３実施形態）図６に示す第３実施形態は、ピストン
２２の成型時に別体の膨出部４２の基端部をインサート
成型し、その先端部を斜板３４の外周面３４１に面接触
するようにしたものである。Therefore, in the second embodiment, the material of the swelling portion 41 is not affected by the material of the piston 22, and is made of a material having a high wear resistance suitable for the material of the swash plate 34 made of an iron-based material. Can be selected. (Third Embodiment) In a third embodiment shown in FIG. 6, the base end of the separate bulging portion 42 is insert-molded when the piston 22 is formed, and the distal end is formed on the outer peripheral surface 341 of the swash plate 34. The contact is made.

【００３２】この第３実施形態においても第２実施形態
と同様の作用効果を奏する。 （その他の実施形態）前記各実施形態はさらに次のよう
に具体化することができる。The third embodiment has the same operation and effect as the second embodiment. (Other Embodiments) Each of the above embodiments can be further embodied as follows.

【００３３】・図６に示す実施形態において、膨出部４
２を１箇所のみとすること。 ・図１〜図４の実施形態において、膨出部２２６，２２
７の前後両端部に面取り部を設け、ピストン２２の往復
動時に膨出部２２６，２２７が受ける抵抗を軽減するよ
うにすること。In the embodiment shown in FIG.
2 is only one place. -In the embodiment of Figs.
7 are provided with chamfered portions at both front and rear ends to reduce the resistance of the bulging portions 226 and 227 when the piston 22 reciprocates.

【００３４】・斜板の片側のみにピストンを備える片頭
ピストン型斜板式圧縮機に適用すること。 ・上記の片頭ピストン型斜板式圧縮機において、胴部の
寸法をピストンの直径よりも小さく設定し、この胴部の
両側縁の少なくとも一方に膨出部を形成すること。この
場合においてピストンの中心軸線から膨出部の先端まで
の距離がピストンの半径よりも大きくなるのが望ましい
が、小さい場合も前述した膨出部の先端部側の回動規制
面の斜板の外周面に対する押圧力が小さくなり、摺動抵
抗を低減することができる。 （定義）この明細書において、膨出部とは両頭ピストン
２２の胴部２２３あるいは片頭ピストンの胴部に一体又
は別体に取り付けられて、胴部２２３よりもピストンの
径方向の外方に飛び出しているものをも含むものとす
る。The present invention is applied to a single head piston type swash plate type compressor having a piston on only one side of the swash plate. In the single-headed piston type swash plate compressor, the size of the body is set smaller than the diameter of the piston, and a bulge is formed on at least one of both side edges of the body. In this case, it is desirable that the distance from the center axis of the piston to the tip of the bulging portion is larger than the radius of the piston. The pressing force on the outer peripheral surface is reduced, and the sliding resistance can be reduced. (Definition) In this specification, the bulging portion is integrally or separately attached to the body portion 223 of the double-headed piston 22 or the body portion of the single-headed piston, and projects outward from the body portion 223 in the radial direction of the piston. Including those that have

【００３５】[0035]

【発明の効果】この発明は特許請求の範囲のように構成
したので、次のような効果がある。請求項１記載の発明
は斜板の外周面とピストンの胴部に設けた回動規制面と
の摺動抵抗を低減して耐久性を向上することができると
ともに、斜板の外周面と回動規制面とのクリアランスの
増大による騒音を抑制することができる。The present invention has the following advantages because it is configured as in the appended claims. The invention according to claim 1 can reduce the sliding resistance between the outer peripheral surface of the swash plate and the rotation restricting surface provided on the body of the piston to improve the durability, and at the same time, reduce the sliding resistance. Noise due to an increase in clearance with the motion regulation surface can be suppressed.

【００３６】請求項２記載の発明は請求項１記載の発明
の効果に加えて、膨出部の形成範囲を大きく設定して、
斜板の外周面と回動規制面との摺動抵抗をさらに低減し
て耐久性を向上することができる。According to the second aspect of the present invention, in addition to the effect of the first aspect of the present invention, the formation range of the bulging portion is set large,
The sliding resistance between the outer peripheral surface of the swash plate and the rotation restricting surface can be further reduced, and the durability can be improved.

【００３７】請求項３記載の発明は請求項１又は２記載
の発明の効果をさらに向上することができる。請求項４
記載の発明は、請求項１〜３のいずれかに記載の発明の
効果に加えて、部品点数を増やすことなく製造を容易に
行うことができる。The invention of claim 3 can further improve the effect of the invention of claim 1 or 2. Claim 4
According to the invention described above, in addition to the effects of the invention according to any one of claims 1 to 3, manufacturing can be easily performed without increasing the number of parts.

【００３８】請求項５記載の発明は、請求項１〜４のい
ずれかに記載の発明の効果に加えて、回動規制面と斜板
の外周面との接触面積を広くして、局部摩耗を抑制し、
耐久性を向上することができる。According to a fifth aspect of the present invention, in addition to the effects of the first aspect of the present invention, the contact area between the rotation restricting surface and the outer peripheral surface of the swash plate is increased so that local wear is reduced. To suppress
Durability can be improved.

【００３９】請求項６記載の発明は、請求項１〜４のい
ずれかに記載の発明の効果に加えて、膨出部の先端部の
最も摺動抵抗の小さい部分を有効に活用して耐久性を向
上することができる。According to a sixth aspect of the present invention, in addition to the effects of the first to fourth aspects of the present invention, the end portion of the bulging portion is effectively utilized to minimize the sliding resistance and is durable. Performance can be improved.

【００４０】請求項７記載の発明は、請求項１，２，
３，５，６のいずれかに記載の発明の効果に加えて、膨
出部の材質選定の自由度が高くなり、斜板の材質を考慮
して膨出部の耐摩耗性に優れた材料を選定することがで
きる。The invention according to claim 7 is based on claims 1, 2, and
In addition to the effects of the invention described in any one of 3, 5, and 6, the degree of freedom in selecting the material of the bulging portion is increased, and the material of the bulging portion is excellent in wear resistance in consideration of the material of the swash plate. Can be selected.

【００４１】請求項８記載の発明は、請求項４に記載の
発明の効果に加えて、ピストンの鍛造工程に発生する胴
部の周方向の両端部に形成される張り出し部を利用する
ことができ、製造を容易に行うことができる。According to an eighth aspect of the present invention, in addition to the effects of the fourth aspect of the present invention, it is possible to utilize overhang portions formed at both circumferential ends of a body portion generated in a piston forging process. It can be easily manufactured.

【００４２】請求項９記載の発明は両頭ピストン型斜板
式圧縮機において斜板の外周面と両頭ピストンの胴部に
設けた回動規制面との摺動抵抗を低減して耐久性を向上
することができるとともに、斜板の外周面と回動規制面
とのクリアランスの増大による騒音を抑制することがで
きる。According to the ninth aspect of the present invention, in the double-headed piston type swash plate type compressor, the sliding resistance between the outer peripheral surface of the swash plate and the rotation regulating surface provided on the body of the double-headed piston is reduced to improve the durability. In addition to this, it is possible to suppress noise due to an increase in clearance between the outer peripheral surface of the swash plate and the rotation restricting surface.

【図面の簡単な説明】[Brief description of the drawings]

【図１】 この発明を具体化した第１実施形態の斜板式
圧縮機の中央部縦断面図。FIG. 1 is a longitudinal sectional view of a central portion of a swash plate type compressor according to a first embodiment of the present invention.

【図２】 図１のI −I 線断面図。FIG. 2 is a sectional view taken along line II of FIG. 1;

【図３】 両頭ピストンの斜視図。FIG. 3 is a perspective view of a double-headed piston.

【図４】 要部の拡大断面図。FIG. 4 is an enlarged sectional view of a main part.

【図５】 この発明の第２実施形態の要部横断面図。FIG. 5 is a cross-sectional view of a main part of a second embodiment of the present invention.

【図６】 この発明の第３実施形態の要部横断面図。FIG. 6 is a cross-sectional view of a main part of a third embodiment of the present invention.

【図７】 従来の両頭ピストンを示す斜視図。FIG. 7 is a perspective view showing a conventional double-ended piston.

【図８】 従来のピストンの組み付け状態を示す横断面
図。FIG. 8 is a cross-sectional view showing an assembled state of a conventional piston.

【符号の説明】[Explanation of symbols]

１１，１２…シリンダブロック、１１１，１２１…シリ
ンダボア、１３，１４…バルブプレート、１５，１６…
フロント及びリヤのハウシング、１８…駆動シャフト、
２１…斜板室、２２…ピストン、２２１，２２２…頭
部、２２３…胴部、２２４…凹部、２２６，２２７…膨
出部、２２８，２２９…回動規制面、２３…圧縮室、２
４，２５…吸入室、２６，２７…吐出室、３４…斜板、
３４１…外周面。11, 12 ... cylinder block, 111, 121 ... cylinder bore, 13, 14 ... valve plate, 15, 16 ...
Front and rear housing, 18 ... drive shaft,
Reference numeral 21: swash plate chamber, 22: piston, 221, 222 ... head, 223 ... trunk, 224 ... recess, 226, 227 ... bulge, 228, 229 ... rotation regulating surface, 23: compression chamber, 2
4, 25 ... suction chamber, 26, 27 ... discharge chamber, 34 ... swash plate,
341...

───────────────────────────────────────────────────── フロントページの続き (72)発明者 山口 哲也 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 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Tetsuya Yamaguchi 2-1-1 Toyota-cho, Kariya-shi, Aichi Prefecture Inside Toyota Industries Corporation

Claims (9)

【特許請求の範囲】[Claims] 【請求項１】 複数のシリンダボアを有するシリンダブ
ロックの端面に吸入室と吐出室を区画形成するハウジン
グを接合固定し、斜板室に駆動シャフトにより回転する
斜板を収容し、該斜板の前後両側面にシューを介して前
記シリンダボア内に収容されたピストンを係留し、該ピ
ストンを斜板の回転運動により往復動させて、前記吸入
室からシリンダボア内の圧縮室へガスを吸入し、該圧縮
室内で圧縮されたガスを前記吐出室へ吐出するようにし
た斜板式圧縮機において、 前記ピストンは斜板に係留される胴部を備え、胴部の周
方向両端縁のうち少なくとも一方の端縁に対し、該胴部
から側方へ延びて前記斜板の外周面に接触してピストン
の回動を阻止する膨出部を設けた斜板式圧縮機における
ピストンの回動防止構造。A swash plate that is rotated by a drive shaft is accommodated in a swash plate chamber, and a front and rear side of the swash plate is fixed to an end surface of a cylinder block having a plurality of cylinder bores. A piston housed in the cylinder bore is moored to the surface via a shoe, and the piston is reciprocated by the rotational motion of the swash plate to suck gas from the suction chamber into a compression chamber in the cylinder bore, and In the swash plate compressor configured to discharge the gas compressed in the discharge chamber, the piston includes a body that is moored to the swash plate, and at least one of the circumferential ends of the body is provided at one end. On the other hand, a piston rotation preventing structure in a swash plate type compressor provided with a bulging portion extending laterally from the body to contact the outer peripheral surface of the swash plate to prevent rotation of the piston. 【請求項２】 請求項１において、前記膨出部はピスト
ン軸線方向から見て前記シリンダボアより外方に延出し
ている斜板式圧縮機におけるピストンの回動防止構造。2. The swash plate compressor according to claim 1, wherein the bulging portion extends outward from the cylinder bore when viewed from a piston axial direction. 【請求項３】 請求項１又は２において、前記膨出部は
前記胴部の周方向両端縁に設けられている斜板式圧縮機
におけるピストンの回動防止構造。3. The structure for preventing rotation of a piston in a swash plate type compressor according to claim 1, wherein the bulging portion is provided on both circumferential edges of the body. 【請求項４】 請求項１〜３のいずれか１項において、
前記膨出部は前記胴部と一体に形成されている斜板式圧
縮機におけるピストンの回動防止構造。4. The method according to claim 1, wherein
The swelling portion is formed integrally with the body portion, and the swash plate compressor has a piston rotation preventing structure. 【請求項５】 請求項１〜４のいずれか１項において、
前記膨出部の内周面の曲率半径は、斜板の外周面の曲率
半径と同じに設定されている斜板式圧縮機におけるピス
トンの回動防止構造。5. The method according to claim 1, wherein:
A structure for preventing rotation of a piston in a swash plate type compressor, wherein a radius of curvature of an inner peripheral surface of the bulging portion is set to be equal to a radius of curvature of an outer peripheral surface of the swash plate. 【請求項６】 請求項１〜４のいずれか１項において、
前記膨出部の内周面の曲率半径は、斜板の外周面の曲率
半径よりも小さく設定されている斜板式圧縮機における
ピストンの回動防止構造。6. The method according to claim 1, wherein:
A structure for preventing rotation of a piston in a swash plate compressor, wherein a radius of curvature of an inner peripheral surface of the bulging portion is set smaller than a radius of curvature of an outer peripheral surface of the swash plate. 【請求項７】 請求項１，２，３，５，６のいずれか１
項において、前記膨出部は前記胴部と別体に形成されて
いる斜板式圧縮機におけるピストンの回動防止構造。7. One of claims 1, 2, 3, 5, and 6
In the paragraph, the swelling portion is formed separately from the trunk portion, and the piston is prevented from rotating in the swash plate compressor. 【請求項８】 請求項４において、前記膨出部はピスト
ンの鍛造工程において前記胴部の周方向両側に本来膨出
形成される部位を利用して形成されたものである斜板式
圧縮機におけるピストンの回動防止構造。8. The swash plate type compressor according to claim 4, wherein the bulging portion is formed by utilizing portions which are originally bulging and formed on both sides in a circumferential direction of the body portion in a piston forging process. Piston rotation prevention structure. 【請求項９】 請求項１〜８のいずれか１項において、
斜板式圧縮機は複数のシリンダボアを有するシリンダブ
ロックの前後両端面に吸入室と吐出室を区画形成するフ
ロント及びリヤのハウジングを接合固定し、シリンダブ
ロックの中央部に形成した斜板室に駆動シャフトにより
回転する斜板を収容し、該斜板の前後両側面にシューを
介して前記シリンダボア内に収容された両頭ピストンを
係留し、該両頭ピストンを斜板の回転運動により往復動
させるようにした両頭ピストン型である斜板式圧縮機に
おけるピストンの回動防止構造。9. The method according to claim 1, wherein:
In the swash plate type compressor, a front and rear housing that defines a suction chamber and a discharge chamber are joined and fixed to front and rear end surfaces of a cylinder block having a plurality of cylinder bores, and a drive shaft is attached to a swash plate chamber formed in the center of the cylinder block. A double-headed head that houses a rotating swash plate, and anchors a double-headed piston housed in the cylinder bore via a shoe on both front and rear side surfaces of the swash-plate, and reciprocates the double-headed piston by the rotational motion of the swash plate. A structure for preventing rotation of a piston in a piston type swash plate type compressor.
JP9002407A 1997-01-09 1997-01-09 Rotation preventing structure of piston in swash plate compressor Pending JPH10196528A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP9002407A JPH10196528A (en) 1997-01-09 1997-01-09 Rotation preventing structure of piston in swash plate compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP9002407A JPH10196528A (en) 1997-01-09 1997-01-09 Rotation preventing structure of piston in swash plate compressor

Publications (1)

Publication Number Publication Date
JPH10196528A true JPH10196528A (en) 1998-07-31

Family

ID=11528400

Family Applications (1)

Application Number Title Priority Date Filing Date
JP9002407A Pending JPH10196528A (en) 1997-01-09 1997-01-09 Rotation preventing structure of piston in swash plate compressor

Country Status (1)

Country Link
JP (1) JPH10196528A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100598767B1 (en) 2004-11-16 2006-07-13 한국기계연구원 Cylinder block with hydrostatic bearing of hydraulic piston pump·motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100598767B1 (en) 2004-11-16 2006-07-13 한국기계연구원 Cylinder block with hydrostatic bearing of hydraulic piston pump·motor

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