JPH08284807A - Reciprocating type displacement machine - Google Patents

Abstract

PURPOSE: To decrease the mechanical abrasion loss of a sliding part, so as to alleviate the severity of the sliding condition by making the sliding part on which the large sliding load acts perform the small oscillating and sliding movement by using a lever member so supported and restricted as to draw the conical locus. CONSTITUTION: When a driving arm 9 is rotated by a driving motor 7, the center of a spherical surface 4a is restricted on the spherical contraposition center, namely, the fixed point to a supporting part 1a of a main frame, a cylindrical surface part 4d performs the revolution motion by the driving arm 9, and therefore, the center axis of a lever member 4 performs the motion for drawing the locus of two conical surfaces taking the center of the spherical surface 4a as the vertex. When an operating chamber 33 is in compression stroke, spherical surfaces 4d, 4c are subjected to relatively large load through a connecting rod 17, and are supported by the spherical part 4a and the supporting part of the cylindrical surface part 4d, and sliding load acting on the cylindrical surface part 4d becomes sufficiently small by the principle of the lever in comparison with sliding load acting on the spherical parts 4a, 4b, 4c.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明はレシプロ式の容積型機械
に係り、特に気体の圧縮に用いるレシプロ式圧縮機や、
車両等の原動機に用いるレシプロ式内燃機関に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating positive displacement machine, and more particularly to a reciprocating compressor used for compressing gas,
The present invention relates to a reciprocating internal combustion engine used for a prime mover such as a vehicle.

【０００２】[0002]

【従来の技術】従来のレシプロ式の容積型機械に、例え
ばクランクシャフトの回転によるクランクピン部の公転
運動とピストンの往復運動とを連動させ、ピストン頭部
に形成された作動室の容積が周期的に変化する事を利用
して、作動流体の移送や圧縮あるいは作動流体からの動
力の取り出しを行なう構造のものがあった。2. Description of the Related Art In a conventional reciprocating displacement machine, for example, the revolving motion of a crank pin portion and the reciprocating motion of a piston caused by the rotation of a crankshaft are interlocked with each other so that the volume of a working chamber formed in a piston head is cyclic. There is a structure in which the working fluid is transferred or compressed or the power is taken out from the working fluid by utilizing the fact that the working fluid changes.

【０００３】[0003]

【発明が解決しようとする課題】上記従来の技術では、
ピストン頭部の作動流体の圧力により、クランクピン部
やクランクシャフト軸受部の様に比較的摺動速度の大き
い回転摺動部に比較的大きな荷重が作用するので、機械
摩擦損失が大きく容積型機械としての効率を低下させる
原因となり、また過酷な運転状態においては摺動条件が
厳しくなり、摩耗・焼き付きが発生して容積型機械とし
ての信頼性も低下させるという問題があった。 本発明
の目的は、レシプロ式の容積型機械において、ピストン
の往復運動と入出力軸の回転運動とを連動させる為の機
構の各摺動部で発生する機械摩擦損失を低減して容積型
機械としての効率を向上させ、更に、その各摺動部の摺
動条件を緩和して容積型機械としての信頼性を向上させ
る事である。SUMMARY OF THE INVENTION In the above conventional technique,
Due to the pressure of the working fluid in the piston head, a relatively large load acts on the rotating and sliding parts with a relatively high sliding speed, such as the crank pin part and the crankshaft bearing part. There is a problem in that the sliding condition becomes severe under severe operating conditions, wear and seizure occur, and the reliability of the positive displacement machine also deteriorates. An object of the present invention is, in a reciprocating positive displacement machine, reducing the mechanical friction loss generated at each sliding portion of a mechanism for interlocking the reciprocating motion of a piston and the rotational motion of an input / output shaft to reduce the positive displacement machine. Efficiency is improved, and the sliding condition of each sliding portion is relaxed to improve the reliability as a positive displacement machine.

【０００４】[0004]

【課題を解決するための手段】上記本発明の目的は以下
の様にして達成される。まず、ピストンの往復運動と入
出力軸の回転運動とを連動させる機構の構成要素とし
て、従来のクランクシャフトに代え、固定フレーム部材
により一箇所を球面対偶で支持されたてこ部材を採用す
る。次に、入出力軸に相当する回転部材によりその回転
軸から半径方向に偏位した位置で前記てこ部材を回転支
持し、固定フレーム部材による球面対偶支持部を頂点と
した前記てこ部材の円錐状軌跡の運動と前記回転部材の
回転運動とを連動させる。次に、前記てこ部材上で前記
固定フレーム部材との球面対偶部からの距離が、前記固
定フレーム部材との球面対偶部から前記回転部材による
回転支持部までの距離より十分小さくなる位置で、前記
てこ部と球面対偶連結部材とを球面対偶で連結する。更
に、前記てこ部材の円錐状軌跡の運動の際に前記球面対
偶連結部材が行なう公転運動とピストンの往復運動とを
連動させる。The above object of the present invention is achieved as follows. First, as a constituent element of a mechanism for interlocking the reciprocating motion of a piston and the rotary motion of an input / output shaft, a lever member supported by a fixed frame member at one place with a spherical pair is adopted instead of a conventional crankshaft. Next, the lever member is rotatably supported by a rotary member corresponding to the input / output shaft at a position displaced in the radial direction from the rotary shaft, and the conical shape of the lever member having the spherical pair support portion by the fixed frame member as the apex. The motion of the locus and the rotary motion of the rotary member are interlocked. Next, at a position on the lever member where the distance from the spherical pair portion to the fixed frame member is sufficiently smaller than the distance from the spherical pair portion to the fixed frame member to the rotation support portion by the rotating member, The lever portion and the spherical pair connecting member are connected by the spherical pair. Furthermore, the revolving motion of the piston and the reciprocating motion of the spherical pair connecting member during the conical locus motion of the lever member are interlocked.

【０００５】[0005]

【作用】上記の課題を解決するための手段においては、
まず、ピストン頭部の作動流体の圧力により、球面対偶
連結部材を介して該球面対偶連結部材とてこ部材との球
面対偶部を荷重点として、てこ部材に荷重が作用する。
一方、てこ部材は固定フレーム部材による球面対偶支持
部と回転部材による回転支持部の２ヵ所で支持されてい
るが、その球面対偶支持部を支点とし回転支持部を力点
とすれば、前述の様に支点から荷重点までの距離に比べ
て支点から力点までの距離が十分大きくなるように構成
されているので、てこの原理により、力点に作用する荷
重は荷重点および支点に作用する荷重に比べて十分小さ
くなる。In the means for solving the above problems,
First, by the pressure of the working fluid of the piston head, a load acts on the lever member via the spherical pair connection member with the spherical pair portion of the spherical pair connection member and the lever member as a load point.
On the other hand, the lever member is supported at two points, that is, the spherical pair support portion by the fixed frame member and the rotation support portion by the rotating member. If the spherical pair support portion is used as the fulcrum and the rotation support portion is the force point, Since the distance from the fulcrum to the force point is sufficiently larger than the distance from the fulcrum to the load point, the load acting on the power point is compared to the load acting on the load point and the fulcrum by the lever principle. Becomes small enough.

【０００６】すなわち、てこ部材と回転部材との回転対
偶部に作用する荷重は、てこ部材と球面対偶連結部材と
の球面対偶部に作用する荷重やてこ部材と固定フレーム
部材との球面対偶部に作用する荷重に比べて十分小さく
なる。なお、てこ部材から回転部材に作用する荷重が十
分小さくなる事により、回転部材の回転を支える軸受部
に作用する荷重も十分小さくなる。ところで、てこ部材
と相対運動を行なう部材の中で、入出力軸に相当する回
転部材は当然自転運動を行ない、摩擦力によって、てこ
部材に自転させようとする回転駆動トルクを作用する
が、その摩擦力を発生させる回転対偶部荷重が小さいの
で、その回転駆動トルクの大きさは小さい。That is, the load acting on the rotating pair portion of the lever member and the rotating member is the load acting on the spherical pair portion of the lever member and the spherical pair connecting member, and the spherical pair portion of the lever member and the fixed frame member. It is sufficiently smaller than the applied load. Since the load acting on the rotating member from the lever member is sufficiently small, the load acting on the bearing portion that supports the rotation of the rotating member is also sufficiently small. By the way, among the members that perform relative motion with the lever member, the rotary member corresponding to the input / output shaft naturally performs rotation motion, and frictional force acts on the lever member to rotate the rotary drive torque. Since the rotating pair load that generates the frictional force is small, the magnitude of the rotational driving torque is small.

【０００７】一方、固定フレーム部材や球面対偶連結部
材は連続的な自転運動を行なわず、摩擦力によって、て
こ部材に自転させまいとする回転抵抗トルクを作用する
が、その摩擦力を発生させる球面対偶部荷重が大きい事
等によりその回転抵抗トルクの大きさは大きい。この結
果、てこ部材は自転運動をほとんど行なわない。したが
って、てこ部材は固定フレーム部材と球面対偶連結部材
に対しては、ほぼその円錐運動の頂角を振幅とする揺動
摺動が主体となり、回転部材に対してのみ相対的に連続
な回転摺動を行なう。On the other hand, the fixed frame member and the spherical pair connecting member do not perform continuous rotation motion, but a frictional force exerts a rotational resistance torque that prevents the lever member from rotating, but a spherical surface that generates the frictional force. The magnitude of the rotational resistance torque is large due to the large load on the even parts. As a result, the lever member makes almost no rotation movement. Therefore, the lever member mainly swings and slides about the apex angle of its conical motion with respect to the fixed frame member and the spherical pair connecting member, and is relatively continuous with the rotating member only. Make a move.

【０００８】以上の結果、ピストンの往復運動と入出力
軸の回転運動とを連動させる機構の各摺動部において、
てこ部材と回転部材との間の摺動部及び回転部材の軸受
部では回転摺動であるため摺動速度は大きいが摺動荷重
が低減され、てこ部材と固定フレーム部材との間の摺動
部及びてこ部材と球面対偶連結部材との間の摺動部では
摺動荷重は大きいが揺動摺動となる事により摺動速度が
低減される。したがって、それらの摺動部における機械
摩擦損失の総和が小さくなり摺動条件が特に厳しい摺動
部も無くなる事により、容積型機械としての効率と信頼
性の向上が図れる。As a result of the above, in each sliding portion of the mechanism for interlocking the reciprocating motion of the piston and the rotary motion of the input / output shaft,
Since the sliding portion between the lever member and the rotating member and the bearing portion of the rotating member are rotating and sliding, the sliding speed is high, but the sliding load is reduced, and the sliding between the lever member and the fixed frame member. Although the sliding load is large in the sliding portion between the portion and the lever member and the spherical pair connecting member, the sliding speed is reduced due to rocking sliding. Therefore, the total of mechanical friction loss in the sliding parts is reduced, and the sliding parts under particularly strict sliding conditions are eliminated, so that the efficiency and reliability of the positive displacement machine can be improved.

【０００９】[0009]

【実施例】以下、本発明の実施例を図１ないし図１１に
より説明する。図１は本発明の第１の実施例であるレシ
プロ式圧縮機を示す断面図、図２は図１におけるＩ−Ｉ
断面図、図３は圧縮機駆動軸を90゜ ずつ回転させた場合
の図２における各部品の動きを説明した図、図４および
図５は第１の実施例における各球面支持部材の構成を説
明する斜視図、図６は本発明の第２の実施例である内燃
機関を示す断面図、図７は図６におけるII−II断面図、
図８は本発明の第３の実施例であるレシプロ式圧縮機を
示す断面図、図９は図８における III−III 断面図、図
１０は本発明の第４の実施例である内燃機関を示す断面
図、図１１は本発明の第５の実施例である内燃機関を示
す断面図である。Embodiments of the present invention will be described below with reference to FIGS. FIG. 1 is a cross-sectional view showing a reciprocating compressor which is a first embodiment of the present invention, and FIG. 2 is II in FIG.
FIG. 3 is a cross-sectional view, FIG. 3 is a view for explaining the movement of each component in FIG. 2 when the compressor drive shaft is rotated by 90 °, and FIGS. 4 and 5 show the structure of each spherical support member in the first embodiment. 6 is a sectional view showing an internal combustion engine which is a second embodiment of the present invention, FIG. 7 is a sectional view taken along line II-II in FIG.
8 is a sectional view showing a reciprocating compressor which is a third embodiment of the present invention, FIG. 9 is a sectional view taken along the line III-III in FIG. 8, and FIG. 10 is an internal combustion engine which is the fourth embodiment of the present invention. FIG. 11 is a sectional view showing an internal combustion engine which is a fifth embodiment of the present invention.

【００１０】図１ないし図５により本発明の第１の実施
例であるレシプロ式圧縮機を説明する。メインフレーム
１にはシリンダ２が２つ同方向に取り付けられ、シリン
ダ２にはピストンボア部２ａが形成されており、そのそ
れぞれにピストン３が往復動可能に挿入されている。メ
インフレーム１は、更に、２つのシリンダ２の取付け部
の中央から延びる軸支持部１ａを有している。軸支持部
１ａでは、軸状のてこ部材４の球面部４ａが球面支持部
材５を介して球面対偶で支持されている。球面支持部材
５は、図４に示す様に内周球面部５ａと外周円筒面部５
ｂを持ち、２つが軸方向から組み合わされて固定ナット
６により前記軸支持部１ａに固定されている。なお、図
４は球面支持部材５の概略形状を示すものであり、給油
溝等の詳細部は省略して図示されている。また、実際の
組立ての際は、当然、てこ部材の球面部４ａを間に挾ん
で軸方向から組み合わされるものである。てこ部材４に
は、もう２つの球面部４ｂ、４ｃが球面部４ａを挾んで
両側に形成されており、更に、球面部４ｃの外側又はて
こ部材の一端には円筒面部４ｄが形成されている。な
お、てこ部材４において、円筒面部４ｄの球面部４ａか
らの距離は、球面部４ｂ、４ｃの球面部４ａからの距離
に比べて、十分大きくなっている。A reciprocating compressor according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 5. Two cylinders 2 are attached to the main frame 1 in the same direction, a piston bore portion 2a is formed in the cylinder 2, and a piston 3 is reciprocally inserted in each of them. The main frame 1 further has a shaft support portion 1a extending from the center of the mounting portion of the two cylinders 2. In the shaft support portion 1 a, the spherical portion 4 a of the shaft-shaped lever member 4 is supported by the spherical pair via the spherical support member 5. As shown in FIG. 4, the spherical surface supporting member 5 includes an inner peripheral spherical surface portion 5a and an outer peripheral cylindrical surface portion 5.
It has b, and two are combined from the axial direction and are fixed to the shaft supporting portion 1a by a fixing nut 6. Note that FIG. 4 shows a schematic shape of the spherical support member 5, and detailed portions such as an oil supply groove are omitted. Further, in the actual assembling, of course, the spherical portion 4a of the lever member is sandwiched between and assembled in the axial direction. The lever member 4 has two spherical surfaces 4b and 4c formed on both sides of the spherical surface 4a, and a cylindrical surface 4d is formed outside the spherical surface 4c or at one end of the lever member. . In the lever member 4, the distance of the cylindrical surface portion 4d from the spherical surface portion 4a is sufficiently larger than the distance of the spherical surface portions 4b and 4c from the spherical surface portion 4a.

【００１１】てこ部材の円筒面部４ｄは、駆動用モータ
７の主軸８に固定されて回転する駆動アーム９により、
モータ回転軸から半径方向に偏位した位置で球面ブッシ
ュ１０を介して相対的な回転が可能に支持されている。
球面ブッシュ１０は外周球面部と内周円筒面部とを持
ち、その外周球面部が球面支持部材１１を介して駆動ア
ーム９により球面対偶で支持され、その内周円筒面部で
てこ部材の円筒面部４ｄを回転可能に支持している。球
面支持部材１１は内周球面部と外周円筒面部を持ち、そ
の外周円筒面部が駆動アーム９の半径方向に偏位した位
置に挿入され、固定ナット１２により固定されている。The cylindrical surface portion 4d of the lever member is fixed to the main shaft 8 of the drive motor 7 by the drive arm 9 which rotates.
It is rotatably supported via a spherical bush 10 at a position displaced in the radial direction from the motor rotation shaft.
The spherical bush 10 has an outer peripheral spherical surface portion and an inner peripheral cylindrical surface portion, and the outer peripheral spherical surface portion is supported by the drive arm 9 via the spherical surface pair 11 in a spherical pair, and the inner peripheral cylindrical surface portion 4d of the lever member. Is rotatably supported. The spherical support member 11 has an inner peripheral spherical surface portion and an outer peripheral cylindrical surface portion, and the outer peripheral cylindrical surface portion is inserted into a position displaced in the radial direction of the drive arm 9 and fixed by a fixing nut 12.

【００１２】駆動用モータ７の主軸８は軸受フレーム１
３の軸受部１３ａと軸受サブフレーム１４の軸受部１４
ａとで回転支持され、それらの間の部分にモータロータ
部７ａが固定されている。軸受フレーム１３と軸受サブ
フレーム１４とは、間にモータステータ部７ｂを挾ん
で、ボルト１５、１６によりメインフレーム１に固定さ
れている。その際、軸受部１３ａ、１４ａの中心軸とス
テータ部７ｂの内周中心軸がメインフレームの軸支持部
１ａにおけるてこ部材４との球面対偶中心を通るよう
に、メインフレーム１に固定されている。The main shaft 8 of the drive motor 7 is the bearing frame 1
Bearing part 13a of No. 3 and bearing part 14 of bearing subframe 14
The motor rotor portion 7a is fixed to a portion between them and is rotatably supported by a. The bearing frame 13 and the bearing subframe 14 are fixed to the main frame 1 by bolts 15 and 16 with the motor stator portion 7b sandwiched therebetween. At this time, the bearings 13a, 14a and the stator 7b are fixed to the main frame 1 so that the central axes thereof pass through the spherical pair center of the lever member 4 of the shaft support 1a of the main frame. .

【００１３】２つのコンロッド１７には、その両端の大
端部１７ａと小端部１７ｂに内周円筒面部が形成されて
いる。大端部１７ａはてこ部材の球面部４ｂ、４ｃに球
面支持部材１８を介し球面対偶で連結されており、小端
部１７ｂはピストン３にピストンピン１９を介して揺動
可能に連結されている。球面支持部材１８は、図５に示
す様に内周球面部１８ａと外周円筒面部１８ｂを持ち、
２つが半径方向から組み合わさた状態で固定ブッシュ２
０の内周円筒面に焼きばめ等で組み込まれ一体に固定さ
れている。なお、図５は球面支持部材１８の概略形状を
示すものであり、給油溝等の詳細部は省略して図示され
ている。また、実際の組立ての際は、当然、てこ部材の
球面部４ｂ、４ｃを間に挾んで半径方向から組み合わさ
れるものである。固定ブッシュ２０の外周円筒面は、コ
ンロッドの大端部１７ａの内周円筒面部に挿入され、軸
方向に滑動出来る構造としてある。Each of the two connecting rods 17 has an inner peripheral cylindrical surface portion formed at a large end portion 17a and a small end portion 17b at both ends thereof. The large end 17a is connected to the spherical surfaces 4b and 4c of the lever member via a spherical support member 18 in a spherical pair, and the small end 17b is swingably connected to the piston 3 via a piston pin 19. . The spherical support member 18 has an inner peripheral spherical surface portion 18a and an outer peripheral cylindrical surface portion 18b as shown in FIG.
Fixed bush 2 with the two assembled in the radial direction
It is incorporated into the inner peripheral cylindrical surface of No. 0 by shrink fitting etc. and is fixed integrally. Note that FIG. 5 shows a schematic shape of the spherical support member 18, and detailed portions such as an oil supply groove are omitted. Further, in the actual assembly, naturally, the spherical members 4b and 4c of the lever member are sandwiched between and assembled in the radial direction. The outer peripheral cylindrical surface of the fixed bush 20 is inserted into the inner peripheral cylindrical surface portion of the large end portion 17a of the connecting rod so as to be slidable in the axial direction.

【００１４】各々のコンロッドの大端部１７ａの軸方向
両端面は、スペーサ２１を挾む事により平行な隙間を形
成する２つのガイドプレート２２の間で滑動し、その面
外への傾斜が規制される構造となっている。前記ガイド
プレート２２とスペーサ２１は、メインフレームの軸支
持部１ａから突出させて設けたガイド座面１ｂに、ボル
ト２３により固定されている。The axially opposite end surfaces of the large end portion 17a of each connecting rod slide between two guide plates 22 that form a parallel gap by sandwiching the spacer 21, and the inclination to the out-of-plane side is restricted. It is structured to be. The guide plate 22 and the spacer 21 are fixed by a bolt 23 to a guide seat surface 1b provided so as to project from the shaft support portion 1a of the main frame.

【００１５】メインフレーム１に取り付けられたシリン
ダ２のピストンボア部２ａの外周側開口部は、シリンダ
ヘッド２４により閉塞され、その外側に更にカバ２５が
取り付けられている。なお、シリンダ２、シリンダヘッ
ド２４、カバ２５は、いずれもボルト２６によりメイン
フレーム１に固定されている。The outer peripheral side opening of the piston bore portion 2a of the cylinder 2 attached to the main frame 1 is closed by a cylinder head 24, and a cover 25 is further attached to the outside thereof. The cylinder 2, the cylinder head 24, and the cover 25 are all fixed to the main frame 1 with bolts 26.

【００１６】シリンダヘッド２４には吐出ポート２４ａ
が形成されており、吐出弁２７と吐出弁押さえ２８とが
取り付けられている。一方、ピストン３には吸入ポート
３ａが形成されており、これを開閉する吸入弁２９が取
り付けられている。The cylinder head 24 has a discharge port 24a.
Is formed, and a discharge valve 27 and a discharge valve retainer 28 are attached. On the other hand, a suction port 3a is formed in the piston 3, and a suction valve 29 for opening and closing the suction port 3a is attached.

【００１７】上記の構造全体は、上チャンバ３０、下チ
ャンバ３１で形成される密閉容器内に防振バネ３２を介
して支持されている。The entire structure described above is supported in a closed container formed by the upper chamber 30 and the lower chamber 31 via a vibration-proof spring 32.

【００１８】以上の構成で、駆動用モータ７により駆動
アーム９が回転すると、てこ部材４の中心軸は、球面部
４ａの中心がメインフレームの軸支持部１ａとの球面対
偶中心すなわち定点に拘束され、円筒面部４ｄが駆動ア
ーム９により公転運動を行なうので、球面部４ａの中心
を頂点とする２つの円錐面を軌跡として描く運動を行な
う。その際、てこ部材４の球面部４ｂ、４ｃのそれぞれ
の中心は、上記円錐面とその中心軸に直角な面との交差
線である円を軌跡として描く運動を行なう。すなわち、
従来のクランクシャフトの回転によりそのクランクピン
部に公転運動が与えられるのと同様に、上記の機構によ
り、てこ部材の球面部４ｂ、４ｃにも公転運動を与える
事が出来る。With the above construction, when the drive arm 9 is rotated by the drive motor 7, the center axis of the lever member 4 is constrained at the center of the spherical surface portion 4a to the spherical pair center with the shaft support portion 1a of the main frame, that is, at a fixed point. Then, since the cylindrical surface portion 4d revolves by the drive arm 9, the cylindrical surface portion 4d performs a movement that draws two conical surfaces with the center of the spherical surface portion 4a as the apex. At this time, the centers of the spherical surfaces 4b, 4c of the lever member 4 perform a motion that draws a circle, which is a line of intersection between the conical surface and a surface perpendicular to the central axis, as a locus. That is,
Similarly to the conventional rotation of the crankshaft, which revolves the crankpin portion, the above mechanism can also revolve the spherical portions 4b and 4c of the lever member.

【００１９】したがって、大端部１７ａを球面部４ｂ、
４ｃに球面対偶で連結された２つのコンロッド１７は、
それぞれ、従来のクランクシャフトを用いた機構におけ
るコンロッドと同様な運動を行ない、ピストンピン１９
を介してピストン３に往復運動を与える事になる。Therefore, the large end portion 17a is replaced by the spherical portion 4b,
The two connecting rods 17 connected to 4c by the spherical pair are
Each performs the same movement as the connecting rod in the mechanism using the conventional crankshaft, and the piston pin 19
The reciprocating motion is given to the piston 3 via.

【００２０】この結果、ピストン３とシリンダのピスト
ンボア部２ａとシリンダヘッド２４とによって囲まれて
形成される作動室３３は、上記ピストン３の往復運動に
より周期的に容積の変化を繰り返す事になり、本実施例
の上記機構が容積型圧縮機のための機構として機能出来
ることがわかる。なお、ピストン３には、作動室３３の
気密のためピストンリング３４が組み込まれている。As a result, the working chamber 33 formed by being surrounded by the piston 3, the piston bore portion 2a of the cylinder, and the cylinder head 24 is repeatedly changed in volume by the reciprocating motion of the piston 3. It is understood that the above mechanism of this embodiment can function as a mechanism for the positive displacement compressor. A piston ring 34 is incorporated in the piston 3 for hermetically sealing the working chamber 33.

【００２１】作動ガスは、まず、低圧配管３５の上チャ
ンバ３０への取り付け部である吸入口３６より密閉容器
内の低圧空間３７に流入し、作動室３３の容積の増大時
にピストン３の背面部から吸入ポート３ａ、吸入弁２９
を通過して、作動室３３の中に吸入される。次に、作動
室３３の容積の減少時に圧縮されて吐出圧力に達した
後、シリンダヘッドの吐出ポート２４ａ、吐出弁２７を
通過して、シリンダヘッド２４とカバ２５とで囲まれた
高圧空間３８に吐出され、高圧配管３９を通ってその下
チャンバ３１への取り付け部である吐出口４０より圧縮
機外に流出する。The working gas first flows into the low-pressure space 37 in the closed container through the suction port 36 which is a mounting portion of the low-pressure pipe 35 to the upper chamber 30, and when the volume of the working chamber 33 increases, the rear surface of the piston 3 is increased. To suction port 3a, suction valve 29
And is sucked into the working chamber 33. Next, after the volume of the working chamber 33 is reduced and reaches the discharge pressure, it passes through the discharge port 24 a and the discharge valve 27 of the cylinder head and is surrounded by the high pressure space 38 surrounded by the cylinder head 24 and the cover 25. Is discharged to the outside of the compressor through the discharge port 40 which is a mounting portion to the lower chamber 31 through the high pressure pipe 39.

【００２２】各摺動部の給油経路は、以下の通りであ
る。下チャンバ３１底部に溜められた潤滑油４１は駆動
用モータの前記主軸８の下端部で駆動される例えばトロ
コイドポンプ等の給油ポンプ４２により、前記主軸８の
内部に形成した給油通路８ａを経由して、まず、軸受サ
ブフレームの軸受部１４ａと軸受フレームの軸受部１３
ａに給油される。残りの潤滑油４１は、更に、軸受フレ
ーム１３の内部に形成した給油通路１３ｂとメインフレ
ーム１の内部に形成した給油通路１ｃと球面支持部材５
の内外周を連絡する給油通路と内周に形成された給油溝
を経由して、てこ部材の球面部４ａと球面支持部材５と
の揺動摺動部に給油される。次にその一部が球面部４
ａ、４ｂ、４ｃの表面に開口し内部で互いに連通する様
にてこ部材４に形成した給油通路４ｅを経由して、前記
球面部４ｂ、４ｃと球面支持部材１８との揺動摺動部に
給油され、更にその一部が球面支持部材１８の内周に形
成された給油溝と内外周を連絡する給油通路、固定ブッ
シュ２０の内外周を連絡する給油通路、および前記コン
ロッド１７の大端部１７ａ内周に形成された給油溝と内
部に形成した給油通路１７c を経由して、コンロッドの
小端部１７ｂとピストンピン１９との揺動摺動部に給油
される。シリンダのピストンボア部２ａとピストン３と
の前記往復摺動部には、上記の各摺動部を潤滑したあと
の潤滑油がミスト状となって作動ガスの流れにのり、前
記ピストンボア部２ａの内周面に付着する事によって給
油される。てこ部材の球面部４ａから給油通路４ｅに供
給された前記潤滑油の一部は、最後にてこ部材の円筒面
部４ｄと球面ブッシュ１０の内周円筒面部との相対回転
摺動部に給油され、主要摺動部への給油が確保される。The oil supply path of each sliding portion is as follows. Lubricating oil 41 stored in the bottom of the lower chamber 31 passes through an oil supply passage 8a formed inside the main shaft 8 by an oil supply pump 42, such as a trochoid pump, which is driven by the lower end of the main shaft 8 of a drive motor. First, the bearing portion 14a of the bearing sub-frame and the bearing portion 13 of the bearing frame
A is refueled. The remaining lubricating oil 41 further includes an oil supply passage 13b formed inside the bearing frame 13, an oil supply passage 1c formed inside the main frame 1, and the spherical support member 5.
Oil is supplied to the oscillating sliding portion between the spherical surface portion 4a of the lever member and the spherical surface supporting member 5 via an oil supply passage connecting the inner and outer circumferences and an oil supply groove formed in the inner circumference. Next, a part of it is spherical part 4.
a, 4b, 4c through the oil supply passage 4e formed in the lever member 4 so as to communicate with each other inside the rocking sliding portion between the spherical surface portions 4b, 4c and the spherical surface supporting member 18. Oil supply passage, which is communicated with the oil supply groove formed in the inner circumference of the spherical support member 18 and communicates the inner and outer circumferences, the oil supply passage which communicates the inner and outer circumferences of the fixed bush 20, and the large end portion of the connecting rod 17. Oil is supplied to the oscillating sliding portion between the small end portion 17b of the connecting rod and the piston pin 19 via the oil supply groove formed on the inner periphery of 17a and the oil supply passage 17c formed inside. At the reciprocating sliding portion between the piston bore portion 2a and the piston 3 of the cylinder, the lubricating oil after lubricating the sliding portions becomes a mist and flows into the working gas flow, and the piston bore portion 2a It is refueled by adhering to the inner surface of the. A part of the lubricating oil supplied from the spherical surface portion 4a of the lever member to the oil supply passage 4e is finally supplied to the relative rotational sliding portion between the cylindrical surface portion 4d of the lever member and the inner peripheral cylindrical surface portion of the spherical bush 10, Oil supply to the main sliding parts is secured.

【００２３】ここで、本実施例におけるてこ部材４の摺
動部である球面部４ａ、４ｂ、４ｃと円筒面部４ｄのそ
れぞれに作用する摺動荷重の大小関係を考えると以下の
ようになる。まず、２つのピストン３のどちらか一方に
着目すると、その頭部の面積に作動室３３の圧力と低圧
空間３７の圧力との差圧が作用し、作動室３３が圧縮行
程や吐出行程の時にはコンロッド１７を介して球面部４
ｂあるいは４ｃに比較的大きな荷重が作用する。その荷
重は球面部４ａと円筒面部４ｄの支持部により支えられ
るが、前記した様に球面部４ｂあるいは４ｃと球面部４
ａとの距離に比べて円筒面部４ｄと球面部４ａとの距離
は十分大きくなっている。すなわち、球面部４ｂあるい
は４ｃを荷重点、球面部４ａを支点、円筒面部４ｄを力
点とするてこが構成されているので、てこの原理によ
り、円筒面部４ｄに作用する摺動荷重は球面部４ａ、４
ｂあるいは４ｃに作用する摺動荷重に比べて十分小さく
なる。もう一方のピストン３からの荷重を考えた場合も
同様である。また、軸受フレームの軸受部１３ａや軸受
サブフレームの軸受部１４ａにおける駆動用モータ７の
主軸８の回転摺動荷重は、てこ部材の円筒面部４ｄに作
用する摺動荷重の反作用力が駆動アーム９に作用する事
により発生するものであるので、やはり十分小さくな
る。Here, considering the magnitude relation of the sliding load acting on each of the spherical surface portions 4a, 4b, 4c and the cylindrical surface portion 4d, which are the sliding portions of the lever member 4 in the present embodiment, it is as follows. First, focusing on one of the two pistons 3, the pressure difference between the pressure in the working chamber 33 and the pressure in the low-pressure space 37 acts on the area of the head, and when the working chamber 33 is in the compression stroke or the discharge stroke. Spherical part 4 via connecting rod 17
A relatively large load acts on b or 4c. The load is supported by the support portion of the spherical surface portion 4a and the cylindrical surface portion 4d, but as described above, the spherical surface portion 4b or 4c and the spherical surface portion 4d.
The distance between the cylindrical surface portion 4d and the spherical surface portion 4a is sufficiently larger than the distance with a. That is, since the lever having the spherical surface portion 4b or 4c as a load point, the spherical surface portion 4a as a fulcrum, and the cylindrical surface portion 4d as a force point is constructed, the sliding load acting on the cylindrical surface portion 4d is caused by the lever principle. Four
It is sufficiently smaller than the sliding load acting on b or 4c. The same applies when considering the load from the other piston 3. In addition, the rotational sliding load of the main shaft 8 of the drive motor 7 in the bearing portion 13a of the bearing frame and the bearing portion 14a of the bearing subframe is the reaction force of the sliding load acting on the cylindrical surface portion 4d of the lever member, which is the driving arm 9. Since it is generated by the action of, it is still sufficiently small.

【００２４】ところで、てこ部材４にはその円筒面部４
ｄに対し、連続的に自転運動を行なう駆動アーム９に装
着された球面ブッシュ１０との摩擦力により、てこ部材
４をその中心軸まわりに自転させようとする自転駆動ト
ルクが作用するが、一方で球面部４ａ、４ｂ、４ｃに対
し、静止部材であるメインフレーム１に装着された球面
支持部材５との摩擦力と、微小角度の揺動のみを行なう
コンロッド１７に装着された球面支持部材１８との摩擦
力とにより、てこ部材４をその中心軸まわりに連続的な
自転をさせまいとする自転抵抗トルクが作用する。前述
の摺動荷重の大小関係より、自転抵抗トルクが自転駆動
トルクに比べて十分大きくなる事は明白であり、てこ部
材４はその中心軸まわりにほとんど自転しない。この結
果、てこ部材４は円筒面部４ｄにおいてのみ連続的な相
対回転摺動を行なって比較的大きな摺動速度となり、球
面部４ａ、４ｂ、４ｃにおいては、ほぼ、てこ部材４の
中心軸の運動軌跡である前記円錐面の頂角を振幅角度と
する揺動摺動を行なうため十分小さな摺動速度となる。By the way, the lever member 4 has a cylindrical surface portion 4
A rotation driving torque for rotating the lever member 4 around its central axis acts on the d by a frictional force with the spherical bush 10 mounted on the drive arm 9 that continuously performs a rotation motion. With respect to the spherical surface portions 4a, 4b, 4c, the frictional force between the spherical surface supporting member 5 mounted on the main frame 1 which is a stationary member and the spherical surface supporting member 18 mounted on the connecting rod 17 which only swings at a minute angle. Due to the frictional force between and, a rotation resistance torque that prevents the lever member 4 from continuously rotating around its central axis acts. From the magnitude relationship of the sliding load described above, it is clear that the rotation resistance torque is sufficiently larger than the rotation driving torque, and the lever member 4 hardly rotates about its central axis. As a result, the lever member 4 makes a relative relative sliding motion only at the cylindrical surface portion 4d to have a relatively large sliding speed, and at the spherical surface portions 4a, 4b, 4c, the movement of the central axis of the lever member 4 is almost the same. Since swinging sliding is performed with the apex angle of the conical surface, which is the locus, as the amplitude angle, the sliding speed is sufficiently small.

【００２５】したがって、本発明の第一の実施例によれ
ば、レシプロ式圧縮機の主要摺動部のいずれにおいて
も、必ず、摺動荷重と摺動速度の一方が十分小さくなる
ので、まず、各摺動部の機械摩擦損失がいずれも小さく
なり、その事により全体の機械摩擦損失も小さくなって
効率の高いレシプロ式圧縮機を提供出来るという効果が
ある。Therefore, according to the first embodiment of the present invention, in any of the main sliding portions of the reciprocating compressor, one of the sliding load and the sliding speed is always sufficiently small. The mechanical friction loss of each sliding portion is reduced, and as a result, the mechanical friction loss of the whole is also reduced, and it is possible to provide a highly efficient reciprocating compressor.

【００２６】また、本発明の第一の実施例によれば、主
要摺動部のいずれにおいても、必ず、摺動荷重を受圧面
積で除した面圧と摺動速度の一方が十分小さくなるの
で、各摺動部の摺動状態の苛酷度がいずれも緩和され、
信頼性の高いレシプロ式圧縮機を提供出来るという効果
がある。Further, according to the first embodiment of the present invention, in any of the main sliding portions, one of the surface pressure obtained by dividing the sliding load by the pressure receiving area and the sliding speed is sufficiently small. , The severity of the sliding state of each sliding part is alleviated,
This has the effect of providing a highly reliable reciprocating compressor.

【００２７】図６および図７に本発明の第２の実施例で
ある内燃機関を示す。メインフレーム４３には、２個の
シリンダ４４がそれぞれのシリンダボア部４４ａを水平
方向にして互いに逆方向に向けて取り付けられている。
そのシリンダボア部４４ａのそれぞれにピストン４５が
互いに逆方向を向いて往復動可能に挿入されている。メ
インフレーム４３は、更に、２つのシリンダ４４の取付
け部の中央に軸支持部４３ａを有している。軸支持部４
３ａで、軸状のてこ部材４６の球面部４６ａが球面支持
部材４７を介して球面対偶で支持されている。球面支持
部材４７は、内周球面部と外周円筒面部を持ち、２つが
軸方向から組み合わされて固定ナット４８により前記軸
支持部４３ａに固定されている。てこ部材４６には、も
う２つの球面部４６ｂ、４６ｃが球面部４６ａを挾んで
両側に形成されており、更に、球面部４６ｃの外側には
円筒面部４６ｄが形成されている。なお、てこ部材４６
において、円筒面部４６ｄの球面部４６ａからの距離
は、球面部４６ｂ、４６ｃの球面部４６ａからの距離に
比べて、十分大きくなっている。6 and 7 show an internal combustion engine which is a second embodiment of the present invention. Two cylinders 44 are attached to the main frame 43 so that their cylinder bores 44a are in the horizontal direction and are oriented in mutually opposite directions.
A piston 45 is inserted in each of the cylinder bore portions 44a so as to be capable of reciprocating in directions opposite to each other. The main frame 43 further has a shaft support portion 43a at the center of the mounting portion of the two cylinders 44. Shaft support 4
At 3a, the spherical portion 46a of the shaft-like lever member 46 is supported by the spherical pair via the spherical support member 47. The spherical support member 47 has an inner peripheral spherical surface portion and an outer peripheral cylindrical surface portion, and the two are combined in the axial direction and fixed to the shaft supporting portion 43a by a fixing nut 48. The lever member 46 has two spherical surfaces 46b and 46c formed on both sides of the spherical surface 46a, and a cylindrical surface 46d is formed outside the spherical surface 46c. The lever member 46
In, the distance of the cylindrical surface portion 46d from the spherical surface portion 46a is sufficiently larger than the distance of the spherical surface portions 46b and 46c from the spherical surface portion 46a.

【００２８】てこ部材の円筒面部４６ｄは、出力軸４９
に固定されて回転する従動アーム５０により、出力軸４
９の回転軸から半径方向に偏位した位置で球面ブッシュ
５１を介して相対的な回転が可能に支持されている。球
面ブッシュ５１は外周球面部と内周円筒面部とを持ち、
その外周球面部が球面支持部材５２を介して従動アーム
５０により球面対偶で支持され、その内周円筒面部でて
こ部材の円筒面部４６ｄを回転可能に支持している。球
面支持部材５２は内周球面部と外周円筒面部を持ち、そ
の外周円筒面部が従動アーム５０の半径方向に偏位した
位置に挿入され、固定ナット５３により固定されてい
る。The cylindrical surface portion 46d of the lever member has an output shaft 49
The output shaft 4 is fixed by the driven arm 50 fixed to the
It is rotatably supported via a spherical bush 51 at a position radially displaced from the rotation axis of the shaft 9. The spherical bush 51 has an outer peripheral spherical surface portion and an inner peripheral cylindrical surface portion,
The outer peripheral spherical surface portion is supported by the driven arm 50 via the spherical surface support member 52 in a spherical pair, and the inner peripheral cylindrical surface portion rotatably supports the cylindrical surface portion 46d of the lever member. The spherical support member 52 has an inner peripheral spherical surface portion and an outer peripheral cylindrical surface portion, and the outer peripheral cylindrical surface portion is inserted into a position displaced in the radial direction of the driven arm 50 and fixed by a fixing nut 53.

【００２９】出力軸４９は軸受フレーム５４の軸受部５
４ａで回転支持されており、該軸受部５４ａを貫通し
て、前記従動アーム５０が固定されている側の反対側ま
で延びており、負荷（図示せず）に接続出来る様になっ
ている。軸受フレーム５４は、その軸受部５４ａの中心
軸がメインフレームの軸支持部４３ａにおけるてこ部材
４６との球面対偶中心を通るように、メインフレーム４
３に固定されている。The output shaft 49 is the bearing portion 5 of the bearing frame 54.
It is rotatably supported by 4a, extends through the bearing 54a to the side opposite to the side on which the driven arm 50 is fixed, and can be connected to a load (not shown). The bearing frame 54 is arranged such that the center axis of the bearing portion 54a passes through the center of the spherical pair with the lever member 46 in the shaft supporting portion 43a of the main frame.
It is fixed at 3.

【００３０】コンロッド５５には、その両端の大端部５
５ａと小端部５５ｂに内周円筒面部が形成されている。
大端部５５ａはてこ部材の球面部４６ｂ、４６ｃに球面
支持部材５６を介し球面対偶で連結されており、小端部
５５ｂはピストン４５にピストンピン５７を介して揺動
可能に連結されている。球面支持部材５６は、内周球面
部と外周円筒面部を持ち、２つが半径方向から組み合わ
さた状態で固定ブッシュ５８の内周円筒面に焼きばめ等
で組み込まれ一体に固定されている。固定ブッシュ５８
の外周円筒面は、コンロッドの大端部５５ａの内周円筒
面部に挿入され、軸方向に滑動出来る構造としてある。The connecting rod 55 has large ends 5 at both ends thereof.
An inner peripheral cylindrical surface portion is formed at 5a and the small end portion 55b.
The large end 55a is connected to the spherical surfaces 46b and 46c of the lever member via a spherical support member 56 in a spherical pair, and the small end 55b is swingably connected to the piston 45 via a piston pin 57. . The spherical support member 56 has an inner peripheral spherical surface portion and an outer peripheral cylindrical surface portion, and is assembled and fixed integrally on the inner peripheral cylindrical surface of the fixed bush 58 by shrink fitting or the like in a state where the two are combined in the radial direction. Fixed bush 58
The outer peripheral cylindrical surface of is inserted into the inner peripheral cylindrical surface of the large end portion 55a of the connecting rod, and has a structure capable of sliding in the axial direction.

【００３１】各々のコンロッドの大端部５５ａの軸方向
両端面は、スペーサ５９を挾む事により平行な隙間を形
成する２つのガイドプレート６０の間で滑動し、その面
外への傾斜が規制される構造となっている。前記ガイド
プレート６０とスペーサ５９は、メインフレームの軸支
持部４３ａから突出させて設けたガイド座面４３ｂに、
ボルト６１により固定されている。The axially opposite end surfaces of the large end 55a of each connecting rod slide between two guide plates 60 that form a parallel gap by sandwiching the spacer 59, and the inclination to the out-of-plane is restricted. It is structured to be. The guide plate 60 and the spacer 59 are provided on a guide seat surface 43b provided so as to project from the shaft support portion 43a of the main frame,
It is fixed by bolts 61.

【００３２】２つのシリンダのシリンダボア部４４ａの
外周側開口部は、それぞれシリンダヘッド６２により閉
塞されており、シリンダボア部４４ａとピストン４５と
シリンダヘッド６２とにより囲まれた作動室６３が形成
されている。なお、ピストン４５には、作動室６３の気
密のためピストンリング６４が組み込まれている。シリ
ンダヘッド６２の各々には吸気ポート６２ａと排気ポー
ト６２ｂが形成されており、それらはそれぞれ吸気弁６
５と排気弁６６によって、開閉される構造になってい
る。吸気弁６５と排気弁６６とを適切なタイミングで駆
動して吸気ポート６２ａと排気ポート６２ｂを開閉する
ための動弁機構は図示していないが、従来の４サイクル
内燃機関の動弁機構と全く同様に、カムシャフト等を用
い出力軸４９の２回転を１周期としてその間に吸気弁６
５と排気弁６６に１往復動を与えるものである。シリン
ダヘッド６２の各々には、また、点火プラグ６７が装着
されており、図示しない点火時期制御装置により、やは
り出力軸４９の２回転を１周期として、適当なタイミン
グに作動室６３の内部でスパークを発生させる構造であ
る。The outer peripheral openings of the cylinder bores 44a of the two cylinders are closed by cylinder heads 62, respectively, and a working chamber 63 surrounded by the cylinder bores 44a, the piston 45 and the cylinder head 62 is formed. . A piston ring 64 is incorporated in the piston 45 to hermetically seal the working chamber 63. An intake port 62a and an exhaust port 62b are formed in each of the cylinder heads 62.
5 and the exhaust valve 66 are opened and closed. Although a valve mechanism for driving the intake valve 65 and the exhaust valve 66 at appropriate timings to open and close the intake port 62a and the exhaust port 62b is not shown, it is completely different from the valve mechanism of the conventional 4-cycle internal combustion engine. Similarly, using the camshaft or the like, two rotations of the output shaft 49 are defined as one cycle, and the intake valve 6
5 and the exhaust valve 66 are given one reciprocating motion. An ignition plug 67 is also attached to each of the cylinder heads 62, and an ignition timing control device (not shown) also sets two revolutions of the output shaft 49 as one cycle to spark the inside of the working chamber 63 at an appropriate timing. Is a structure for generating.

【００３３】図示していない動弁機構は、まず、ピスト
ン４５の往復運動により作動室６３の容積が増大する吸
気行程の間、吸気弁６５を開いて燃料と空気との混合気
を作動室６３内部に導き、これに続き作動室６３の容積
が減少・増大する圧縮・膨張行程で混合気が圧縮され点
火プラグ６７によって点火され膨張する間、吸気弁６５
と排気弁６６とを閉じて作動室６３を外界と隔離された
空間とし、次に作動室６３の容積が減少する排気行程で
排気弁６６を開いて燃焼終了ガスが作動室６３の外への
排出されるのを可能にする。In a valve operating mechanism (not shown), first, during the intake stroke in which the volume of the working chamber 63 increases due to the reciprocating motion of the piston 45, the intake valve 65 is opened to generate a mixture of fuel and air in the working chamber 63. During the compression / expansion stroke in which the volume of the working chamber 63 is reduced / increased, the mixture is compressed and ignited by the ignition plug 67 to expand, while the intake valve 65 is introduced.
And the exhaust valve 66 are closed to make the working chamber 63 a space isolated from the outside, and then the exhaust valve 66 is opened in the exhaust stroke in which the volume of the working chamber 63 decreases, so that the combustion completed gas is discharged to the outside of the working chamber 63. Allows to be discharged.

【００３４】ピストン４５に往復運動させるには、図示
しない駆動手段によって始動時のみ出力軸４９を外部か
ら回転駆動する必要があるが、作動室６３内で混合気の
燃焼が開始されると、それが膨張する際にピストン４５
を押して行なう仕事により、自力で往復運動をする様に
なる。まず、膨張行程において作動室６３内の燃焼ガス
がピストン４５を押す力は、ピストンピン５７、コンロ
ッド５５、球面支持部材５６等を介して、まず、てこ部
材の球面部４６ｂ、４６ｃに作用する。In order to reciprocate the piston 45, it is necessary to rotate the output shaft 49 from the outside only by starting by a driving means (not shown), but when combustion of the air-fuel mixture in the working chamber 63 is started, When the piston expands 45
The work done by pressing makes you reciprocate by yourself. First, the force of the combustion gas in the working chamber 63 pushing the piston 45 in the expansion stroke first acts on the spherical surface portions 46b and 46c of the lever member via the piston pin 57, the connecting rod 55, the spherical surface supporting member 56 and the like.

【００３５】一方、てこ部材４６は、球面部４６ａの中
心がメインフレームの軸支持部４３ａとの球面対偶中心
すなわち定点に拘束され、円筒面部４６ｄが従動アーム
５０により公転運動を行なう様に拘束されているので、
球面部４６ｂ、４６ｃに作用する上記の力により、球面
部４６ａの中心を頂点とする２つの円錐面を軌跡として
描く運動を行なう。従動アームはフライホイル及びバラ
ンスウェイト機能を兼ねる。前記てこ部材４６の円錐状
の運動により、出力軸４９が内部から回転駆動され、膨
張行程以外の間も慣性により連続的な回転を継続する。
一般的には燃焼ガスが膨張行程の間にピストン４５に対
して行なう仕事は、膨張行程以外の間も含めて各摺動部
で消費される摩擦仕事より大きくできるので、動力を出
力軸４９より外部に取り出す事が可能になる。On the other hand, in the lever member 46, the center of the spherical surface portion 46a is constrained to the center of the spherical pair with the shaft support portion 43a of the main frame, that is, a fixed point, and the cylindrical surface portion 46d is constrained by the driven arm 50 so as to revolve. Because
Due to the above-mentioned force acting on the spherical surface portions 46b and 46c, a motion is drawn in which two conical surfaces having the center of the spherical surface portion 46a as a vertex are drawn as loci. The driven arm also functions as a flywheel and a balance weight. Due to the conical movement of the lever member 46, the output shaft 49 is rotationally driven from the inside, and continuous rotation is continued by inertia even during the period other than the expansion stroke.
In general, the work performed by the combustion gas on the piston 45 during the expansion stroke can be made larger than the friction work consumed at each sliding portion during the expansion stroke as well, so that the power is output from the output shaft 49. It can be taken out.

【００３６】各摺動部の給油経路は、以下の通りであ
る。メインフレーム４３底部に溜められた潤滑油６８
は、まず給油ポンプ６９により、軸受フレーム５４の内
部に形成した給油通路５４ｂを経由して軸受フレームの
軸受部５４ａと出力軸４９との回転摺動部に給油され、
同時に、メインフレームの軸支持部４３ａの内部に形成
した給油通路４３ｃと球面支持部材４７に形成した給油
通路、給油溝とを経由しててこ部材の球面部４６ａと球
面支持部材４７との揺動摺動部に給油される。その他の
摺動部への給油は、第１の実施例の場合と同様に、てこ
部材４６に形成した給油通路４６ｅ、球面支持部材５６
に形成した給油溝、給油通路、コンロッド５５に形成し
た給油溝、給油通路５５ｃ等を経由して行なわれる。な
お、本実施例では、軸受部５４ａから外側に向かって流
出した潤滑油６８は、軸受フレーム５４の外側のシール
フレーム７０に装着されたオイルシール７１により外部
に漏洩するのを防止され、軸受フレーム５４に設けた油
還流孔５４ｃよりメインフレーム４３底部に戻る。The oil supply path of each sliding portion is as follows. Lubricating oil 68 accumulated on the bottom of the main frame 43
First, the oil supply pump 69 supplies oil to the rotary sliding portion between the bearing portion 54a of the bearing frame and the output shaft 49 via the oil supply passage 54b formed inside the bearing frame 54,
At the same time, the swinging of the spherical surface portion 46a of the lever member and the spherical support member 47 via the oil supply passage 43c formed inside the shaft support portion 43a of the main frame, the oil supply passage formed in the spherical surface support member 47, and the oil supply groove. Oil is applied to the sliding parts. As for the oil supply to the other sliding portions, as in the case of the first embodiment, the oil supply passage 46e formed in the lever member 46 and the spherical support member 56 are provided.
Is performed via the oil supply groove formed in the above, the oil supply passage, the oil supply groove formed in the connecting rod 55, the oil supply passage 55c, and the like. In the present embodiment, the lubricating oil 68 that has flowed outward from the bearing portion 54a is prevented from leaking to the outside by the oil seal 71 attached to the seal frame 70 on the outer side of the bearing frame 54, and thus the bearing frame. It returns to the bottom of the main frame 43 from the oil circulation hole 54c provided in 54.

【００３７】ところで、本実施例における各摺動部の摺
動荷重と摺動速度の大小関係は、第１の実施例の場合と
全く同様なてこの原理により、てこ部材の円筒面部４６
ｄと球面ブッシュ５１の内周円筒面部との回転摺動部や
出力軸４９と軸受フレームの軸受部５４ａとの回転摺動
部の様に比較的摺動速度の大きい摺動部では、摺動荷重
が十分小さくなり、てこ部材の球面部４６ａと球面支持
部材４７との揺動摺動部や球面部４６ｂあるいは４６ｃ
と球面支持部材５６との揺動摺動部の様に比較的摺動荷
重の大きい摺動部では、摺動速度が十分小さくなる。By the way, the magnitude relationship between the sliding load and the sliding speed of each sliding portion in this embodiment is exactly the same as in the case of the first embodiment, based on the principle of leverage, and the cylindrical surface portion 46 of the lever member.
In a sliding portion having a relatively high sliding speed, such as a rotational sliding portion between d and the inner peripheral cylindrical surface portion of the spherical bush 51 or a rotational sliding portion between the output shaft 49 and the bearing portion 54a of the bearing frame, sliding is performed. The load becomes sufficiently small, and the swing sliding portion between the spherical surface portion 46a of the lever member and the spherical surface supporting member 47 or the spherical surface portion 46b or 46c.
In a sliding portion having a relatively large sliding load, such as an oscillating sliding portion between the spherical support member 56 and the spherical support member 56, the sliding speed becomes sufficiently small.

【００３８】一方、本実施例における２つの作動室６３
の容積変化の位相関係は、第一の実施例の場合の２つの
作動室３３の容積変化が互いに逆位相であったのと全く
異なり、互いに同位相である。これは、ピストンに連結
されたてこ部材の２つの球面部がてこ部材の傾斜により
必ず互いに逆方向に偏位する点では共通であるものの、
第１の実施例の場合のシリンダの２つのシリンダボア部
２ａが互いに同方向に向けて形成されいるのに対し、本
実施例の場合のシリンダの２つのシリンダボア部４４ａ
は互いに逆方向に向けて形成されている点で、構造が異
なるためである。本実施例の４サイクル内燃機関の様
に、作動室の容積変化を利用した吸気行程、圧縮行程、
膨張行程、排気行程の４つの行程がピストンの往復運動
の片道毎に切り替わり２往復で１周期となる場合、２つ
の作動室での行程のずれを交互に等間隔にするには、そ
れらの作動室の容積変化の位相を１往復分だけずらせば
良い。ところが、容積変化の周期は１往復が１周期であ
るので、結局、２つの作動室での行程のずれを交互に等
間隔にするには、容積変化を同位相とする事が必要であ
る。On the other hand, the two working chambers 63 in this embodiment.
The phase relation of the volume change of is completely different from the volume change of the two working chambers 33 in the case of the first embodiment, but is in the same phase. Although this is common in that the two spherical portions of the lever member connected to the piston are always displaced in opposite directions due to the inclination of the lever member,
While the two cylinder bore portions 2a of the cylinder in the first embodiment are formed in the same direction as each other, the two cylinder bore portions 44a of the cylinder in the present embodiment are formed.
This is because the structures are different in that they are formed in directions opposite to each other. Like the four-cycle internal combustion engine of this embodiment, the intake stroke, the compression stroke, which utilizes the volume change of the working chamber,
When the four strokes of the expansion stroke and the exhaust stroke are switched for each one-way movement of the reciprocating motion of the piston to form one cycle of two reciprocating strokes, in order to make the deviations of the strokes in the two working chambers alternately equal intervals, the operation of those strokes is performed. It suffices to shift the phase of the volume change of the chamber by one round trip. However, since the cycle of the volume change is one cycle of one reciprocation, it is necessary to make the volume changes in the same phase in the end in order to make the deviations of the strokes in the two working chambers alternately equal intervals.

【００３９】以上は４サイクルの例で説明したが、本発
明は２サイクル内燃機関としても実施することができ
る。その場合、作動室の各行程の変化はピストンの１往
復で１周期となるので、２つの作動室での行程のずれを
交互に等間隔にするには、第１の実施例の場合と同じ
く、それらの作動室の容積変化の位相を半往復分だけず
らして逆位相とすれば良く、２つのシリンダは図１の如
く同方向に配列することが好ましい。２サイクルの実施
例は、機械的には図１，２と同様に図示することができ
るので、その図示は省略する。Although the example of four cycles has been described above, the present invention can also be implemented as a two-cycle internal combustion engine. In that case, since the change of each stroke of the working chamber is one cycle for one reciprocation of the piston, in order to alternately make the deviations of the strokes of the two working chambers at equal intervals, as in the case of the first embodiment. The phases of the volume changes of the working chambers may be shifted by half the number of reciprocations so as to have opposite phases, and the two cylinders are preferably arranged in the same direction as shown in FIG. The two-cycle embodiment can be mechanically illustrated in the same manner as in FIGS. 1 and 2, and the illustration thereof is omitted.

【００４０】したがって、まず、本発明の第２の実施例
によれば、レシプロ式内燃機関の主要摺動部のいずれに
おいても、必ず、摺動荷重と摺動速度の一方が十分小さ
くなるので、まず、各摺動部の機械摩擦損失がいずれも
小さくなり、その事により全体の機械摩擦損失も小さく
なって効率の高いレシプロ式内燃機関を提供出来るとい
う効果がある。Therefore, according to the second embodiment of the present invention, one of the sliding load and the sliding speed is always sufficiently small in any of the main sliding parts of the reciprocating internal combustion engine. First, the mechanical friction loss of each sliding portion is reduced, and as a result, the mechanical friction loss of the whole is also reduced, and it is possible to provide a highly efficient reciprocating internal combustion engine.

【００４１】また、本発明の第２の実施例によれば、主
要摺動部のいずれにおいても、必ず、摺動荷重を受圧面
積で除した面圧と摺動速度の一方が十分小さくなるの
で、各摺動部の摺動状態の苛酷度がいずれも緩和され、
信頼性の高いレシプロ式内燃機関を提供出来るという効
果がある。Further, according to the second embodiment of the present invention, in any of the main sliding portions, one of the surface pressure obtained by dividing the sliding load by the pressure receiving area and the sliding speed is sufficiently small. , The severity of the sliding state of each sliding part is alleviated,
This has the effect of providing a highly reliable reciprocating internal combustion engine.

【００４２】更に、本発明の第２の実施例によれば、２
気筒４サイクルの内燃機関で、２つの作動室での行程の
ずれを交互に等間隔に出来るので、スムースな運転を行
なう低振動のレシプロ式内燃機関を提供出来るという効
果がある。Further, according to the second embodiment of the present invention, 2
In the four-cylinder internal combustion engine, the deviations of the strokes in the two working chambers can be alternately arranged at equal intervals, so that it is possible to provide a low-vibration reciprocating internal combustion engine that operates smoothly.

【００４３】図８および図９に本発明の第３の実施例で
あるレシプロ式圧縮機を示す。本実施例は第１の実施例
と共通部分が多いので、全体の説明は省略し本実施例特
有の構造を中心に説明する。本実施例のてこ部材７２に
は、第一の実施例におけるてこ部材４の球面部４ｂ、４
ｃに対応する球面部が無く、円筒面部７２ｂ、７２ｃが
形成されている。そして、それらの円筒面部に外周球面
部と内周円筒面部とを持つ球面ブッシュ７３がそれぞれ
滑動可能に挿入されている。２つの球面ブッシュ７３の
それぞれには、内周球面部を持つコンロッド７４の大端
部７４ａが球面対偶で連結されているが、その大端部７
４ａはほぼ半周の内周球面を持つ他の大端部部材７５と
ボルト７６で結合されて一周のリング形状を形成されて
いる。FIGS. 8 and 9 show a reciprocating compressor which is a third embodiment of the present invention. Since this embodiment has a lot in common with the first embodiment, the description of the whole is omitted and the structure peculiar to this embodiment will be mainly described. The lever member 72 of this embodiment includes the spherical portions 4b, 4b of the lever member 4 of the first embodiment.
There is no spherical surface portion corresponding to c, and cylindrical surface portions 72b and 72c are formed. A spherical bush 73 having an outer peripheral spherical surface portion and an inner peripheral cylindrical surface portion is slidably inserted into these cylindrical surface portions. A large end portion 74a of a connecting rod 74 having an inner peripheral spherical surface portion is connected to each of the two spherical bushes 73 by a spherical pair.
4a is connected to another large end member 75 having an inner peripheral spherical surface of approximately half circumference by a bolt 76 to form a ring shape of one circumference.

【００４４】第１の実施例のてこ部材４は、球面部４
ｂ、４ｃに装着された球面支持部材１８の外周部の固定
ブッシュ２０がコンロッドの大端部１７ａの内周円筒面
部に対して滑動できるため、メインフレームの軸支持部
１ａによってのみ主軸８の回転軸方向に拘束され、過剰
に拘束される事はない。本実施例のてこ部材７２も、円
筒面部７２ｂ、７２ｃが球面ブッシュ７３に対して滑動
できるので、主軸８の回転軸方向に拘束するのは、やは
りメインフレームの軸支持部１ａのみになり、過剰に拘
束される事は無い。本実施例によれば、形状の大きな部
材であるコンロッドを２分割してその内周球面部により
球面ブッシュ７３を包囲するので、ボルト７６による２
分割球面の固定ができ、真球度を出し易い。The lever member 4 of the first embodiment has a spherical portion 4
Since the fixed bush 20 on the outer peripheral portion of the spherical support member 18 mounted on b and 4c can slide with respect to the inner peripheral cylindrical surface portion of the large end portion 17a of the connecting rod, the rotation of the main shaft 8 can be performed only by the shaft support portion 1a of the main frame. It is restrained in the axial direction and is not restrained excessively. Also in the lever member 72 of this embodiment, since the cylindrical surface portions 72b and 72c can slide with respect to the spherical bush 73, it is only the shaft support portion 1a of the main frame that restrains the main shaft 8 in the rotation axis direction. You will not be bound by. According to the present embodiment, the connecting rod, which is a member having a large shape, is divided into two and the spherical bush 73 is surrounded by the spherical surface portion of the connecting rod.
The split spherical surface can be fixed, making it easy to obtain a sphericity.

【００４５】上記第１、第３実施例では、気体圧縮機の
例で説明したが、本発明は液体の移送に実施することが
でき、その場合吸入弁をシリンダヘッドに設けることが
好ましい。Although the first and third embodiments have been described with reference to the example of the gas compressor, the present invention can be applied to the transfer of liquid, and in that case, it is preferable to provide the suction valve on the cylinder head.

【００４６】図１０に本発明の第４の実施例である内燃
機関を示す。本実施例は第２の実施例と共通部分が多い
ので、全体の説明は省略し本実施例特有の構造を中心に
説明する。本実施例のてこ部材７７には、第２の実施例
におけるてこ部材４６の球面部４６ｂに対応する球面部
が無く、メインフレーム７８の軸支持部７８ａによって
球面対偶支持される球面部７７ａの片側にのみ球面部７
７ｂが形成されている。てこ部材の球面部７７ａは、球
面支持部材７９を介してメインフレーム７８の軸支持部
７８ａにより球面対偶で支持されているが、その際、球
面支持部材７９は２つが半径方向から組み合わされて状
態で固定ブッシュ８０の内周円筒面に焼きばめ等で組み
込まれ一体に固定されている。固定ブッシュ８０の外周
円筒面は、メインフレーム７８の軸支持部７８ａに設け
た内周円筒面に挿入され、軸方向に滑動出来る構造にな
っている。球面部７７ｂには、第３の実施例と同様に、
コンロッド８１の大端部８１ａと他の大端部部材８２と
がボルトで結合されて一周のリング形状となり、球面対
偶で連結されている。FIG. 10 shows an internal combustion engine which is a fourth embodiment of the present invention. Since this embodiment has a lot in common with the second embodiment, the description of the whole is omitted and the structure peculiar to this embodiment will be mainly described. The lever member 77 of the present embodiment does not have a spherical surface portion corresponding to the spherical surface portion 46b of the lever member 46 in the second embodiment, and one side of the spherical surface portion 77a supported by the shaft support portion 78a of the main frame 78 in a spherical pair. Only spherical part 7
7b is formed. The spherical surface portion 77a of the lever member is supported in a spherical pair by the shaft supporting portion 78a of the main frame 78 via the spherical surface supporting member 79. At this time, the spherical supporting member 79 is in a state in which two are combined in the radial direction. Is fixed to the inner peripheral cylindrical surface of the fixed bush 80 by shrink fitting or the like. The outer peripheral cylindrical surface of the fixed bush 80 is inserted into the inner peripheral cylindrical surface provided on the shaft support portion 78a of the main frame 78, and has a structure capable of sliding in the axial direction. In the spherical surface portion 77b, as in the third embodiment,
The large end portion 81a of the connecting rod 81 and the other large end portion member 82 are joined by bolts to form a ring shape of one round, and are connected by a spherical pair.

【００４７】本実施例のてこ部材７７は、球面対偶で直
接連結されたコンロッド８１と大端部部材８２がガイド
プレート６０により挾まれて軸方向の移動を規制されて
いるので、球面部７７ｂにおいて軸方向の動きを拘束さ
れるが、固定ブッシュ８０がメインフレーム７８の軸支
持部７８ａに対して軸方向に滑動出来る構造であるた
め、球面部７７ａでは軸方向の動きを拘束されず、過剰
に拘束される事は無い。In the lever member 77 of the present embodiment, the connecting rod 81 and the large end member 82, which are directly connected by the spherical pair, are sandwiched by the guide plate 60 so as to be restricted from moving in the axial direction. Although the movement in the axial direction is restrained, the fixed bush 80 has a structure capable of sliding in the axial direction with respect to the shaft support portion 78a of the main frame 78. Therefore, the spherical portion 77a does not restrain the movement in the axial direction and is excessive. There will be no restraint.

【００４８】図１１に本発明の第５の実施例である内燃
機関を示す。本実施例も第２の実施例と共通部分が多い
ので、全体の説明は省略し本実施例特有の構造を中心に
説明する。本実施例のてこ部材８３には、第２の実施例
におけるてこ部材の球面部４６ｃに対応する球面部が無
く、第２の実施例における球面部４６ａの代わりに円筒
面部８３ａが形成されている。その円筒面部８３ａに
は、外周球面部と内周円筒面部とを持つ球面ブッシュ８
４が滑動可能に挿入されており、その球面ブッシュ８４
は球面支持部材８５を介してメインフレーム８６の軸支
持部８６ａにより球面対偶で支持されている。その際、
球面支持部材８５は２つが軸方向から組み合わされて固
定ナット８７で前記メインフレームの軸支持部８６ａに
固定されている。球面部８３ｂには第３の実施例と同様
に、コンロッド８１の大端部８１ａと他の大端部部材８
２とがボルトで結合されて一周のリング形状となり、球
面対偶で連結されている。FIG. 11 shows an internal combustion engine which is a fifth embodiment of the present invention. Since this embodiment also has many parts in common with the second embodiment, the overall description will be omitted and the structure peculiar to this embodiment will be mainly described. The lever member 83 of this embodiment does not have a spherical surface portion corresponding to the spherical surface portion 46c of the lever member of the second embodiment, and a cylindrical surface portion 83a is formed instead of the spherical surface portion 46a of the second embodiment. . The cylindrical surface portion 83a has a spherical bush 8 having an outer peripheral spherical surface portion and an inner peripheral cylindrical surface portion.
4 is slidably inserted into the spherical bush 84.
Are supported by the shaft support portion 86a of the main frame 86 via the spherical support member 85 in a spherical pair. that time,
Two spherical support members 85 are combined in the axial direction and fixed to a shaft support portion 86a of the main frame by a fixing nut 87. Similar to the third embodiment, the spherical surface portion 83b has a large end portion 81a of the connecting rod 81 and another large end portion member 8a.
The two are connected to each other by bolts to form a ring shape, and are connected by a spherical pair.

【００４９】本実施例のてこ部材８３は、球面対偶で直
接連結されたコンロッド８１と大端部部材８２がガイド
プレート６０により挾まれて軸方向の移動を規制されて
いるので、球面部８３ｂにおいて軸方向の動きを拘束さ
れるが、円筒面部８３ａでは球面ブッシュ８４の内周円
筒面部に対して滑動出来る構造であるため軸方向の動き
を拘束されず、やはり過剰に拘束される事は無い。In the lever member 83 of this embodiment, the connecting rod 81 and the large end member 82, which are directly connected to each other by the spherical pair, are sandwiched by the guide plate 60 so as to be restricted from moving in the axial direction. Although the movement in the axial direction is restrained, the cylindrical surface portion 83a has a structure in which it can slide with respect to the inner circumferential cylindrical surface portion of the spherical bush 84, so that the movement in the axial direction is not restrained and is not restrained excessively.

【００５０】上記第３、第４、第５の実施例では、いず
れもコンロッドの大端部を２分割にしてボルトにより締
結し、それらに直接内周球面部を形成して分解組立てが
可能な構造としているので、前記内周球面部を一体化し
た状態で機械加工する事により全体の真球度を精度良く
加工し、その後、一度分解して内部に相手部材の球面部
を組込む事が可能であり、コンロッドとてこ部材との球
面対偶部の確実で高精度な製作が可能となる。もちろん
第１の実施例や第２の実施例と同様に、てこ部材の効果
によって、機械摩擦損失を低減し、各摺動部における摺
動条件の苛酷度を緩和する事も出来る。In each of the third, fourth and fifth embodiments, the large end portion of the connecting rod is divided into two and fastened with bolts, and the inner peripheral spherical surface portion is directly formed on them to enable disassembly and assembly. Since it has a structure, it is possible to accurately machine the entire sphericity by machining the inner peripheral spherical part in an integrated state, and then disassemble it once and assemble the spherical part of the mating member inside Therefore, it is possible to manufacture the spherical pair of the connecting rod and the lever member with certainty and high accuracy. Of course, similarly to the first and second embodiments, the effect of the lever member can reduce mechanical friction loss and alleviate the severity of sliding conditions in each sliding portion.

【００５１】第２、第４、第５実施例では、ピストンの
駆動力は燃焼ガス膨張により付与されるようにしたが、
圧油等の圧力流体により付与するようにしてもよい。ま
た第４、第５実施例は、第１実施例のような流体の圧縮
や移送に適用することができるが、その図示は省略す
る。また本発明における球面対偶は、上記のような球面
とこれと補完関係の球面凹部による各実施例に限られる
ことなく、これと同様の機能を有する例えばユニバーサ
ルジョイント、カルダン継ぎ手等の手段を包含するもの
である。In the second, fourth and fifth embodiments, the driving force of the piston is given by the combustion gas expansion.
It may be applied by a pressure fluid such as pressure oil. The fourth and fifth embodiments can be applied to the compression and transfer of fluid as in the first embodiment, but the illustration thereof is omitted. Further, the spherical pair in the present invention is not limited to each embodiment of the spherical surface and the spherical concave portion having a complementary relationship with the spherical surface as described above, but includes means having a similar function to this, such as a universal joint and a cardan joint. It is a thing.

【００５２】[0052]

【発明の効果】本発明によれば、レシプロ式容積型機械
における摺動部の機械摩擦損失を低減し、その摺動条件
の苛酷度を緩和する事が可能であり、レシプロ式容積型
機械の効率と信頼性とを向上出来るという効果がある。According to the present invention, it is possible to reduce the mechanical friction loss of the sliding portion in the reciprocating positive displacement machine and to reduce the severity of the sliding condition. There is an effect that efficiency and reliability can be improved.

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

【図１】本発明の第１の実施例であるレシプロ式圧縮機
を示す断面図FIG. 1 is a sectional view showing a reciprocating compressor according to a first embodiment of the present invention.

【図２】図１におけるI −I 断面図FIG. 2 is a sectional view taken along line I-I in FIG.

【図３】圧縮機駆動軸を90゜ ずつ回転させた場合の図２
における各部品の動きを説明した図[Figure 3] Figure 2 when the compressor drive shaft is rotated by 90 °
For explaining the movement of each part in

【図４】第１の実施例における各球面支持部材の構成を
説明する斜視図FIG. 4 is a perspective view illustrating the configuration of each spherical surface supporting member in the first embodiment.

【図５】第１の実施例における各球面支持部材の構成を
説明する斜視図FIG. 5 is a perspective view illustrating the configuration of each spherical surface supporting member in the first embodiment.

【図６】本発明の第２の実施例である内燃機関を示す断
面図FIG. 6 is a sectional view showing an internal combustion engine that is a second embodiment of the present invention.

【図７】図６におけるII−II断面図7 is a sectional view taken along line II-II in FIG.

【図８】本発明の第３の実施例であるレシプロ式圧縮機
を示す断面図FIG. 8 is a sectional view showing a reciprocating compressor which is a third embodiment of the present invention.

【図９】図８におけるIII −III 断面図9 is a sectional view taken along line III-III in FIG.

【図１０】本発明の第４の実施例である内燃機関を示す
断面図FIG. 10 is a sectional view showing an internal combustion engine which is a fourth embodiment of the present invention.

【図１１】本発明の第５の実施例である内燃機関を示す
断面図である。FIG. 11 is a sectional view showing an internal combustion engine that is a fifth embodiment of the present invention.

【符号の説明】[Explanation of symbols]

１…メインフレーム、１ａ…軸支持部、１ｂ…ガイド座
面、１ｃ…給油通路、２…シリンダ、２ａ…ピストンボ
ア部、３…ピストン、３ａ…吸入ポート、４…てこ部
材、４ａ…球面部、４ｂ…球面部、４ｃ…球面部、４ｄ
…円筒面部、４ｅ…給油通路、５…球面支持部材、５ａ
…内周球面部、５ｂ…外周円筒面部、６…固定ナット、
７…駆動用モータ、７ａ…ロータ部、７ｂ…ステータ
部、８…主軸、８ａ…給油通路、９…駆動アーム、１０
…球面ブッシュ、１１…球面支持部材、１２…固定ナッ
ト、１３…軸受フレーム、１３ａ…軸受部、１３ｂ…給
油通路、１４…軸受サブフレーム、１４ａ…軸受部、１
５…ボルト、１６…ボルト、１７…コンロッド、１７ａ
…大端部、１７ｂ…小端部、１７ｃ…給油通路、１８…
球面支持部材、１８ａ…内周球面部、１８ｂ…外周円筒
面部、１９…ピストンピン、２０…固定ブッシュ、２１
…スペーサ、２２…ガイドプレート、２３…ボルト、２
４…シリンダヘッド、２４ａ…吐出ポート、２５…カ
バ、２６…ボルト、２７…吐出弁、２８…吐出弁押さ
え、２９…吸入弁、３０…上チャンバ、３１…下チャン
バ、３２…防振バネ、３３…作動室、３４…ピストンリ
ング、３５…低圧配管、３６…吸入口、３７…低圧空
間、３８…高圧空間、３９…高圧配管、４０…吐出口、
４１…潤滑油、４２…給油ポンプ、４３…メインフレー
ム、４３ａ…軸支持部、４３ｂ…ガイド座面、４３ｃ…
給油通路、４４…シリンダ、４４ａ…シリンダボア部、
４５…ピストン、４６…てこ部材、４６ａ…球面部、４
６ｂ…球面部、４６ｃ…球面部、４６ｄ…円筒面部、４
６ｅ…給油通路、４７…球面支持部材、４８…固定ナッ
ト、４９…出力軸、５０…従動アーム、５１…球面ブッ
シュ、５２…球面支持部材、５３…固定ナット、５４…
軸受フレーム、５４ａ…軸受部、５４ｂ…給油通路、５
４ｃ…油還流孔、５５…コンロッド、５５ａ…大端部、
５５ｂ…小端部、５５ｃ…給油通路、５６…球面支持部
材、５７…ピストンピン、５８…固定ブッシュ、５９…
スペーサ、６０…ガイドプレート、６１…ボルト、６２
…シリンダヘッド、６２ａ…吸気ポート、６２ｂ…排気
ポート、６３…作動室、６４…ピストンリング、６５…
吸気弁、６６…排気弁、６７…点火プラグ、６８…潤滑
油、６９…給油ポンプ、７０…シールフレーム、７１…
オイルシール、７２…てこ部材、７２ａ…球面部、７２
ｂ…円筒面部、７２ｃ…円筒面部、７２ｄ…円筒面部、
７２ｅ…給油通路、７３…球面ブッシュ、７４…コンロ
ッド、７４ａ…大端部、７４ｂ…小端部、７５…大端部
部材、７６…ボルト、７７…てこ部材、７７ａ…球面
部、７７ｂ…球面部、７８…メインフレーム、７８ａ…
軸支持部、７９…球面支持部材、８０…固定ブッシュ、
８１…コンロッド、８１ａ…大端部、８１ｂ…小端部、
８２…大端部部材、８３…てこ部材、８３ａ…円筒面
部、８３ｂ…球面部、８４…球面ブッシュ、８５…球面
支持部材、８６…メインフレーム、８６ａ…軸支持部、
８７…固定ナットDESCRIPTION OF SYMBOLS 1 ... Main frame, 1a ... Shaft support part, 1b ... Guide seat surface, 1c ... Oil supply passage, 2 ... Cylinder, 2a ... Piston bore part, 3 ... Piston, 3a ... Suction port, 4 ... Lever member, 4a ... Spherical part 4b ... Spherical part, 4c ... Spherical part, 4d
... Cylindrical surface portion, 4e ... Oil supply passage, 5 ... Spherical support member, 5a
... inner spherical surface, 5b outer cylindrical surface, 6 fixing nut,
7 ... Drive motor, 7a ... Rotor part, 7b ... Stator part, 8 ... Main shaft, 8a ... Oil supply passage, 9 ... Drive arm, 10
... spherical bush, 11 ... spherical support member, 12 ... fixed nut, 13 ... bearing frame, 13a ... bearing part, 13b ... oil supply passage, 14 ... bearing sub-frame, 14a ... bearing part, 1
5 ... Bolt, 16 ... Bolt, 17 ... Connecting rod, 17a
… Large end, 17b… Small end, 17c… Oil supply passage, 18…
Spherical support member, 18a ... inner peripheral spherical surface portion, 18b ... outer peripheral cylindrical surface portion, 19 ... piston pin, 20 ... fixed bush, 21
… Spacers, 22… Guide plates, 23… Bolts, 2
4 ... Cylinder head, 24a ... Discharge port, 25 ... Cover, 26 ... Bolt, 27 ... Discharge valve, 28 ... Discharge valve retainer, 29 ... Suction valve, 30 ... Upper chamber, 31 ... Lower chamber, 32 ... Anti-vibration spring, 33 ... Working chamber, 34 ... Piston ring, 35 ... Low pressure pipe, 36 ... Suction port, 37 ... Low pressure space, 38 ... High pressure space, 39 ... High pressure pipe, 40 ... Discharge port,
41 ... Lubricating oil, 42 ... Oil pump, 43 ... Main frame, 43a ... Shaft support part, 43b ... Guide seat surface, 43c ...
Oil supply passage, 44 ... Cylinder, 44a ... Cylinder bore part,
45 ... Piston, 46 ... Lever member, 46a ... Spherical part, 4
6b ... spherical surface portion, 46c ... spherical surface portion, 46d ... cylindrical surface portion, 4
6e ... Oil supply passage, 47 ... Spherical support member, 48 ... Fixing nut, 49 ... Output shaft, 50 ... Follower arm, 51 ... Spherical bush, 52 ... Spherical support member, 53 ... Fixing nut, 54 ...
Bearing frame, 54a ... Bearing portion, 54b ... Oil supply passage, 5
4c ... Oil return hole, 55 ... Connecting rod, 55a ... Large end,
55b ... small end portion, 55c ... oil supply passage, 56 ... spherical surface support member, 57 ... piston pin, 58 ... fixing bush, 59 ...
Spacer, 60 ... Guide plate, 61 ... Bolt, 62
... cylinder head, 62a ... intake port, 62b ... exhaust port, 63 ... working chamber, 64 ... piston ring, 65 ...
Intake valve, 66 ... Exhaust valve, 67 ... Spark plug, 68 ... Lubricating oil, 69 ... Lubrication pump, 70 ... Seal frame, 71 ...
Oil seal, 72 ... Lever member, 72a ... Spherical part, 72
b ... Cylindrical surface portion, 72c ... Cylindrical surface portion, 72d ... Cylindrical surface portion,
72e ... Oil supply passage, 73 ... Spherical bush, 74 ... Connecting rod, 74a ... Large end, 74b ... Small end, 75 ... Large end member, 76 ... Bolt, 77 ... Lever member, 77a ... Spherical part, 77b ... Spherical surface Part, 78 ... Main frame, 78a ...
Shaft support, 79 ... Spherical support member, 80 ... Fixed bush,
81 ... connecting rod, 81a ... large end, 81b ... small end,
82 ... Large end member, 83 ... Lever member, 83a ... Cylindrical surface part, 83b ... Spherical part, 84 ... Spherical bush, 85 ... Spherical support member, 86 ... Main frame, 86a ... Shaft support part,
87 ... Fixing nut

───────────────────────────────────────────────────── フロントページの続き (72)発明者 富田好勝 茨城県土浦市神立町502番地 株式会社日 立製作所機械研究所内 (72)発明者 椎林正夫 茨城県土浦市神立町502番地 株式会社日 立製作所機械研究所内 (72)発明者 蝿田芳夫 茨城県土浦市神立町502番地 株式会社日 立製作所機械研究所内 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Yoshikatsu Tomita, 502 Jinritsucho, Tsuchiura-shi, Ibaraki Prefecture, 502 Hiritsu Seisakusho Mechanical Research Co., Ltd. (72) Inventor, Yoshio Kaeda, 502, Kamidate-cho, Tsuchiura, Ibaraki Prefecture.

Claims (9)

【特許請求の範囲】[Claims] 【請求項１】 固定フレーム部材と、前記固定フレーム
部材により１ヶ所を球面対偶で支持される軸状のてこ部
材と、それ自身が回転しながらその回転軸から半径方向
に偏位した位置で前記てこ部材を相対回転が可能に支持
して前記てこ部材に円錐状の運動軌跡を与える回転駆動
部材と、前記てこ部材の前記固定フレーム部材との球面
対偶部からの距離が該球面対偶部から前記回転駆動部材
による相対回転支持部までの距離に比べて十分小さい位
置で前記てこ部材と一部が球面対偶で連結される球面対
偶連結部材と、前記球面対偶連結部材と他の部分で連結
されて往復運動を行なうピストンと、前記ピストンの往
復運動の案内となるピストンボア部を有し前記固定フレ
ーム部材と別体または一体に成形されたシリンダブロッ
クと、前記シリンダブロックのピストンボア部の一方の
開口部を閉塞するシリンダヘッドとを構成要素に持ち、
前記回転駆動部材の回転により前記ピストンを往復運動
させ、前記シリンダブロックと前記ピストンと前記シリ
ンダヘッドとに囲まれた作動空間の容積を周期的に変化
させる事により、流体の移送や圧縮を行なうレシプロ式
容積型機械。1. A fixed frame member, a shaft-shaped lever member supported by the fixed frame member at one location in a spherical pair, and a position displaced in the radial direction from the rotation axis while rotating itself. The distance from the spherical even part between the rotary drive member that supports the lever member so as to be capable of relative rotation and that gives the lever member a conical motion locus, and the fixed frame member, and the distance from the spherical even part is from the spherical even part. A spherical pair connecting member, a part of which is connected to the lever member by a spherical pair, at a position sufficiently smaller than the distance to the relative rotation support portion by the rotation driving member, and the spherical pair connecting member and another portion. A piston that reciprocates, a cylinder block that has a piston bore portion that guides the reciprocating motion of the piston, and is formed separately or integrally with the fixed frame member; Having a cylinder head that closes one opening of the piston bore of the block and the component,
A reciprocator that transfers or compresses fluid by reciprocating the piston by the rotation of the rotary drive member and periodically changing the volume of the working space surrounded by the cylinder block, the piston, and the cylinder head. Positive displacement machine. 【請求項２】 固定フレーム部材と、前記固定フレーム
部材により１ヶ所を球面対偶で支持される軸状のてこ部
材と、それ自身が回転可能でありその回転軸から半径方
向に偏位した位置で前記てこ部材と回転対偶で連結され
前記てこ部材の円錐状軌跡を描く運動により回転させら
れる回転従動部材と、前記固定フレーム部材と別体また
は一体に形成されピストンボア部を有するシリンダブロ
ックと、前記シリンダブロックのピストンボア部の一方
の開口部を閉塞するシリンダヘッドと、前記シリンダブ
ロックのピストンボア部の中で往復運動を行なうピスト
ンと、前記てこ部材の前記固定フレーム部材との球面対
偶部からの距離が該球面対偶部から前記回転従動部材と
の回転対偶部までの距離に比べて十分小さい位置で前記
てこ部材と一部が球面対偶で連結され他の部分が前記ピ
ストンと連結された球面対偶連結部材とを構成要素に持
ち、作動流体の力により前記シリンダブロックと前記ピ
ストンと前記シリンダヘッドとに囲まれた作動空間の容
積を変化させて前記ピストンに往復運動を発生させ、前
記回転従動部材を出力軸として回転駆動し、作動流体か
ら動力を取り出すレシプロ式容積型機械。2. A fixed frame member, a shaft-shaped lever member supported by the fixed frame member at one location in a spherical pair, and a position which is itself rotatable and radially displaced from the rotation axis. A rotary driven member that is connected to the lever member by a rotational pair and is rotated by a motion that draws a conical locus of the lever member; a cylinder block that is formed separately or integrally with the fixed frame member and that has a piston bore portion; A cylinder head that closes one opening of the piston bore portion of the cylinder block, a piston that reciprocates in the piston bore portion of the cylinder block, and a spherical pair portion of the lever member and the fixed frame member. The lever member and a part of the lever member are at a position where the distance is sufficiently smaller than the distance from the spherical pair to the rotating pair with the rotary driven member. A spherical pair connecting member having a pair of surfaces connected to the piston and the other portion being connected to the piston is included in the component, and the volume of the working space surrounded by the cylinder block, the piston, and the cylinder head by the force of the working fluid. To generate a reciprocating motion in the piston and rotationally drive the rotary driven member as an output shaft to extract power from the working fluid. 【請求項３】 請求項１又は請求項２に記載のレシプロ
式容積型機械において、てこ部材と球面対偶連結部材と
の球面対偶による連結部は、てこ部材の固定フレーム部
材による球面対偶支持部の両側に形成されている事を特
徴とするレシプロ式容積型機械。3. The reciprocating positive displacement machine according to claim 1 or 2, wherein the connecting portion of the lever member and the spherical pair connecting member by the spherical pair is a spherical pair supporting portion formed by a fixed frame member of the lever member. Reciprocating positive displacement machine characterized by being formed on both sides. 【請求項４】 請求項１ないし請求項３の何れかに記載
のレシプロ式容積型機械において、てこ部材と固定フレ
ーム部材との球面対偶およびてこ部材と球面対偶連結部
材との球面対偶の少なくとも一つは、球状外周面と球状
内周面とを滑動可能に当接させて構成した球面対偶であ
る事を特徴とするレシプロ式容積型機械。4. The reciprocating positive displacement machine according to any one of claims 1 to 3, wherein at least one of a spherical pair of the lever member and the fixed frame member and a spherical pair of the lever member and the spherical pair connecting member. The second is a reciprocating positive displacement machine characterized in that it is a spherical pair made up of a spherical outer peripheral surface and a spherical inner peripheral surface slidably abutting against each other. 【請求項５】 請求項１ないし請求項４の何れかに記載
のレシプロ式容積型機械において、てこ部材と固定フレ
ーム部材との球面対偶の中心は固定フレーム部材または
てこ部材に対して移動出来る構造である事を特徴とする
レシプロ式容積型機械。5. The reciprocating positive displacement machine according to claim 1, wherein the center of the spherical pair of the lever member and the fixed frame member is movable with respect to the fixed frame member or the lever member. A reciprocating positive displacement machine characterized by: 【請求項６】 請求項１ないし請求項４の何れかに記載
のレシプロ式容積型機械において、てこ部材と球面対偶
連結部材との球面対偶の中心は球面対偶連結部材または
てこ部材に対して移動出来る構造である事を特徴とする
レシプロ式容積型機械。6. The reciprocating positive displacement machine according to claim 1, wherein the center of the spherical pair of the lever member and the spherical pair connecting member moves with respect to the spherical pair connecting member or the lever member. Reciprocating positive displacement machine characterized by its structure. 【請求項７】 請求項１ないし請求項４の何れかに記載
のレシプロ式容積型機械において、球面対偶連結部材は
回転駆動部材あるいは回転従動部材の回転軸に直角な面
に対する傾斜を規制された構造である事を特徴とするレ
シプロ式容積型機械。7. The reciprocating positive displacement machine according to any one of claims 1 to 4, wherein the spherical pair connecting member is restricted in inclination with respect to a plane perpendicular to the rotation axis of the rotation driving member or the rotation driven member. Reciprocating displacement machine characterized by its structure. 【請求項８】 請求項１ないし請求項４の何れかに記載
のレシプロ式容積型機械において、球面対偶連結部材は
一端をてこ部材と球面対偶により連結され、他の一端を
ピストンと回転対偶により連結されたコンロッドである
事を特徴とするレシプロ式容積型機械。8. The reciprocating positive displacement machine according to claim 1, wherein the spherical pair connecting member has one end connected by a lever member and a spherical pair, and the other end by a piston and a rotating pair. A reciprocating positive displacement machine characterized by being connected connecting rods. 【請求項９】 請求項８に記載のレシプロ式容積型機械
において、コンロッドはてこ部材と球面対偶で連結され
る一端部が、内周を球面に形成されたリング形状であ
り、そのリング形状部分はほぼ半周ずつの内周球面を持
つ２つの部材を結合してリング形状とした事を特徴とす
るレシプロ式容積型機械。9. The reciprocating positive displacement machine according to claim 8, wherein the connecting rod has a ring shape whose one end connected to the lever member with a spherical pair has a spherical inner surface. Is a reciprocating positive displacement machine characterized in that two members having an inner spherical surface of approximately half circumference are joined to form a ring shape.