JPH076499B2 - Rolling prevention structure of double-headed piston in disk cam type reciprocating compressor - Google Patents

Rolling prevention structure of double-headed piston in disk cam type reciprocating compressor

Info

Publication number
JPH076499B2
JPH076499B2 JP61302594A JP30259486A JPH076499B2 JP H076499 B2 JPH076499 B2 JP H076499B2 JP 61302594 A JP61302594 A JP 61302594A JP 30259486 A JP30259486 A JP 30259486A JP H076499 B2 JPH076499 B2 JP H076499B2
Authority
JP
Japan
Prior art keywords
double
headed piston
cam
pair
reciprocating compressor
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.)
Expired - Lifetime
Application number
JP61302594A
Other languages
Japanese (ja)
Other versions
JPS63154868A (en
Inventor
光弘 服部
正行 谷川
克則 河合
好司 岡本
Original Assignee
株式会社豊田自動織機製作所
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 株式会社豊田自動織機製作所 filed Critical 株式会社豊田自動織機製作所
Priority to JP61302594A priority Critical patent/JPH076499B2/en
Priority to US07/122,256 priority patent/US4756239A/en
Publication of JPS63154868A publication Critical patent/JPS63154868A/en
Publication of JPH076499B2 publication Critical patent/JPH076499B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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

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  • Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

【発明の詳細な説明】 〔産業上の利用分野〕 本発明は円盤カム式の往復動型圧縮機、更に具体的には
波板状に形成する円盤カムと両頭ピストンとの間にコロ
を係留させ、同コロの滑り回転を介して円盤カムの回転
を両頭ピストンに対して該カムの１回転で２往復動とし
て伝達する事によって圧縮作用を得る様に設けられる圧
縮機において、上記両頭ピストンの上死点及び下死点位
置におけるローリングを防止するための改良に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a disk cam type reciprocating compressor, and more specifically, a roller cam moored between a disk cam and a double-headed piston formed in a corrugated plate shape. In the compressor provided so that the rotation of the disc cam is transmitted to the double-headed piston as two reciprocating motions by one rotation of the cam via the sliding rotation of the roller, The present invention relates to an improvement for preventing rolling at top dead center and bottom dead center positions.

〔従来の技術〕[Conventional technology]

一般に円盤カム式の圧縮機においては第１図及び第10図
乃至第12図の各図面に表わす様にシリンダーブロック16
内にカム室５を間に存して前後各一対のシリンダーボア
４が回転軸３と平行させて一定間隔毎に穿設される。そ
してカム室５には上記回転軸３に固着させて前後両側面
に波状湾曲面13′を形成する円盤カム13が回転自在に設
けられる一方、各シリンダーボア４にはカム室５を貫通
させて両頭型のピストン８が進退自在に嵌挿される。そ
して又、同ピストン８の後背部に形成する受け座15,15
と円盤カム13の波状湾曲面13′間には前後各一対のコロ
14F,14Rが係留されるのであるが、両コロ14F,14Rはその
回転中心線ａが両頭ピストン８の前後方向に沿う中心線
ｂと同一線上にある様に設けられ、両コロ14F,14Rの滑
り回転を介して円盤カム13の回転を各ピストン８に対し
て往復動として伝達する事が出来る様に設けられる。Generally, in a disk cam type compressor, a cylinder block 16 is provided as shown in each of FIGS. 1 and 10 to 12.
A pair of front and rear cylinder bores 4 are bored at regular intervals in parallel with the rotary shaft 3 with a cam chamber 5 interposed therebetween. The cam chamber 5 is rotatably provided with a disk cam 13 which is fixed to the rotary shaft 3 and forms wavy curved surfaces 13 'on both front and rear surfaces, while each cylinder bore 4 is penetrated by the cam chamber 5. A double-headed piston 8 is inserted so that it can move back and forth. Also, the receiving seats 15, 15 formed on the rear part of the piston 8
Between the wavy curved surface 13 'of the disk cam 13 and the pair of front and rear rollers.
Although 14F and 14R are moored, both rollers 14F and 14R are provided so that the rotation center line a thereof is on the same line as the center line b along the front-rear direction of the double-headed piston 8. It is provided so that the rotation of the disk cam 13 can be transmitted as a reciprocating motion to each piston 8 through the sliding rotation.

〔発明が解決しようとする問題点〕[Problems to be solved by the invention]

しかして上記の様な従来構造の円盤カム式往復動型圧縮
機においては、両頭ピストン８と円盤カム13間に係留す
る前後各一対の円柱コロ14F,14Rをその回転中心線ａが
両頭ピストン８の前後方向に沿う中心線ｂと同一線上に
ある様に設けられている事により、両頭ピストン８が上
死点若しくは下死点に達したが状態において同両頭ピス
トン８が円盤カム13の周方向に向けてローリングすると
いう不具合、そしてこのローリングに起因して騒音を発
生するという不具合を生ずる点に問題点を有する。即
ち、両頭ピストン８が下死点より上死点に向けて或いは
上死点より下死点に向けて往復動する行程においては第
12図に表わす様に円盤カム13に対する両コロ14F,14Rの
接点i,iがピストン８の前後方向に沿う中心線ｂを間に
存してその両側に対峙する状態にあり、そのバランス作
用によって両頭ピストン８のローリングを防止する事が
出来るのあるが、両頭ピストン８が上死点若しくは下死
点に到達した状態においては第11図に表わす様に円盤カ
ム13に対する両コロ14F,14Rの接点i,iがピストン８の前
後方向に沿う中心線ｂと同一線上に対峙する状態となる
事により、両頭ピストン８にローリングが生じると共
に、このローリング作用により両頭ピストン８のブリッ
ジ部８′が円盤カム13の外周部に衝当し、その衝撃によ
り騒音が発生するという不具合を生ずる事となるのであ
る。In the conventional disc cam type reciprocating compressor having the above-mentioned structure, however, a pair of front and rear cylindrical rollers 14F and 14R moored between the double-headed piston 8 and the disc cam 13 are connected to the double-headed piston 8 when the center of rotation a is double-headed. Since the double-headed piston 8 reaches the top dead center or the bottom dead center even if the double-headed piston 8 reaches the top dead center or the bottom dead center, the double-headed piston 8 moves in the circumferential direction of the disc cam 13. However, there is a problem in that it causes a problem of rolling toward the front and a problem of generating noise due to this rolling. That is, in the stroke in which the double-headed piston 8 reciprocates from the bottom dead center toward the top dead center or from the top dead center toward the bottom dead center,
As shown in FIG. 12, the contacts i, i of both rollers 14F, 14R with respect to the disk cam 13 face each other on both sides of the center line b extending in the front-rear direction of the piston 8 and face each other by the balance action. Although it is possible to prevent the rolling of the double-headed piston 8, when the double-headed piston 8 reaches the top dead center or the bottom dead center, the contact points of both rollers 14F, 14R with respect to the disc cam 13 as shown in FIG. Since i and i are in a state of facing each other on the same line as the center line b extending in the front-rear direction of the piston 8, rolling occurs in the double-headed piston 8 and the bridge portion 8 ′ of the double-headed piston 8 causes the disc cam to move due to this rolling action. If it hits the outer peripheral portion of 13, the shock will cause noise, resulting in a problem.

本発明は上記の様な問題点を解決するためにその改善を
試みたものであって、両頭ピストンが上死点若しくは下
死点に到達した状態における両頭ピストンのローリング
を防止する事が出来る様にする事により、同両頭ピスト
ンのブリッジ部が円盤カムの外周部に衝当する事なく往
復動させる事が出来る様にする点にその解決すべき問題
点を有する。即ち、本発明は両頭ピストンが上死点若し
くは下死点に到達した状態において、往復行程と同様円
盤カムに対する両コロの接点が両頭ピストンの前後方向
に沿う中心線を間に存して対峙する状態が得られる様に
する事により、上記問題点を解決する様にした事を特徴
とするものであって、その具体的な手段と作用は次の通
りである。The present invention attempts to improve the above-mentioned problems, and it is possible to prevent rolling of the double-headed piston when the double-headed piston reaches the top dead center or the bottom dead center. Therefore, there is a problem to be solved in that the bridge portion of the double-headed piston can reciprocate without hitting the outer peripheral portion of the disc cam. That is, in the present invention, when the double-headed piston reaches the top dead center or the bottom dead center, the contact points of both rollers with respect to the disc cam face each other with the center line along the front-rear direction of the double-headed piston in between, as in the reciprocating stroke. The present invention is characterized in that the above problems are solved by obtaining a state, and the concrete means and action are as follows.

〔問題点を解決するための手段〕[Means for solving problems]

シリンダーブロック内にカム室を間に存して前後一対を
なす様にフロント側とリヤ側に対峙させて複数組のシリ
ンダーボアを回転軸と平行させて穿設し、各シリンダー
ボアには両頭ピストンを往復動自在に嵌挿させる一方、
カム室には上記回転軸に固着させて波板状に湾曲形成す
る円盤カムを回転自在に設け、同円盤カムと両頭ピスト
ン間には前後各一対のコロを係留させて成る円盤カム式
往復動型圧縮機において、 上記前後各一対のコロを両頭ピストンの前後方向に沿う
中心線を間に存してその両側に若干偏位させて係留す
る。Plural sets of cylinder bores are bored in parallel with the rotation axis by facing the front side and the rear side so as to form a pair of front and rear with a cam chamber inside the cylinder block, and each cylinder bore has a double-headed piston. While inserting and reciprocating freely,
The cam chamber is rotatably provided with a disc cam that is fixed to the rotary shaft and curved in the shape of a corrugated plate, and a pair of front and rear rollers are moored between the disc cam and the two-headed piston. In the mold compressor, the pair of front and rear rollers are moored while being slightly offset on both sides of the double-headed piston with a center line extending in the front-rear direction therebetween.

〔作 用〕[Work]

両頭ピストンが上死点若しくは下死点に到達した状態に
おいて、円盤カムに対する両コロの接点を両頭ピストン
の前後方向に沿う中心線を間に存してその両側に対峙す
る状態が得られ、両コロによって両頭ピストンのローリ
ングを抑止する作用が得られる。In the state where the double-headed piston reaches the top dead center or the bottom dead center, it is possible to obtain a state where the contact points of both rollers with respect to the disc cam face each other on both sides of the center line along the front-rear direction of the double-headed piston. The action of suppressing the rolling of the double-headed piston is obtained by the rollers.

〔実施例〕〔Example〕

以下に本発明の具体的な実施例を例示の図面について説
明する。Specific examples of the present invention will be described below with reference to the accompanying drawings.

第１図乃至第５図は第１の実施例を表わす図面であっ
て、各図面において１は圧縮機の外殻を形成するハウジ
ング、16は同じくシリンダーブロックを示す。そしてシ
リンダーブロック16において、同シリンダーブロック16
はフロントシリンダーブロック16Fとリヤシリンダーブ
ロック16Rより成り、両シリンダーブロック16F,16Rには
その中心部に位置して軸受け部2F,2Rが設けられ、両軸
受け部2F,2Rには回転軸３が回転自在に支承される。そ
して同回転軸３の一端は後述するフロントハウジング1F
を貫通して電磁クラッチ（図示省略）に連結され、同電
磁クラッチの接続及び離断を介してエンジン（図示省
略）の駆動力を同回転軸３に伝達する事が出来る様に設
けられる。又、両シリンダーブロック16F,16Rにはカム
室５が形成され、同カム室５には円盤カム13が前記回転
軸３に軸架させて回転自在に設けられる。同円盤カム13
はその前後両側面を周方向に延在させて波板状に湾曲さ
せて形成される（以下「波状湾曲面13′」という）。そ
して又、両シリンダーブロック16F,16Rには同カム室５
を間に存して適数個のシリンダーボア４が回転軸３と平
行させて穿設される。即ち、回転軸３を囲繞する如く同
一円周上に一定間隔毎に配列させて設けられる。しかし
て各シリンダーボア４はカム等５を間に存して前後一対
を成す様にフロント側とリヤ側に分割して設けられ、同
各一対のシリンダーボア４には後述するバルブプレート
6F,6Rとの間に圧縮室７を存して両頭ピストン８が進退
自在に嵌挿される。更に具体的には両頭ピストン８は前
後一対のピストンヘッド8F,8Rと両ピストンヘッド8F,8R
を繋ぐブリッジ部８′より成り、両ピストンヘッド8F,8
Rは上記前後各一対のシリンダーボア４内に嵌挿される
と共に、ブリッジ部８′は円盤カム13の外周部との間に
適宜のクリアランスＳを存在してカム室５内を横断する
如く設けられる。そして又、両ピストンヘッド8F,8Rの
後背部には後述するコロ14F,14Rの受け座15,15が対向さ
せて凹設されると共に、同受け座15,15と前記円盤カム1
3の波状湾曲面13′間には円柱状に形成する前後各一対
のコロ14F,14Rがその回転中心線ａを夫々円盤カム13の
半径方向に延在させて遊転自在に係留され、円盤カム13
の回転を各両頭ピストン８に対して往復運動として伝達
する事が出来る様に設けられる。しかして上記前後各一
対のコロ14F,14Rは両頭ピストン８のその前後方向（長
手方向）に沿う中心線ｂを間に存してその両側に若干偏
位させて係留される。即ち、両コロ14F,14Rは第４図に
表わす様に両頭ピストン８の中心線ｂに対してその中心
点ｃを距離ｄだけ円盤カム８の周方向に偏位させて設け
られると共に、その回転中心線ａは第２図に表わす様に
回転軸３の中心点ｅと両頭ピストン８を中心点ｆとを結
ぶ中心線ｇに対して若干の偏位角θを存して設けられ
る。1 to 5 are drawings showing a first embodiment, in each of which 1 is a housing forming an outer shell of a compressor and 16 is a cylinder block. And in the cylinder block 16, the cylinder block 16
Consists of a front cylinder block 16F and a rear cylinder block 16R. Both cylinder blocks 16F, 16R are provided with bearings 2F, 2R located in the center thereof, and both bearings 2F, 2R rotate the rotary shaft 3. Freely supported. One end of the rotary shaft 3 has a front housing 1F described later.
And is connected to an electromagnetic clutch (not shown) through which the driving force of an engine (not shown) can be transmitted to the rotary shaft 3 through connection and disconnection of the electromagnetic clutch. A cam chamber 5 is formed in each of the cylinder blocks 16F and 16R, and a disk cam 13 is rotatably provided in the cam chamber 5 while being mounted on the rotary shaft 3. Same disc cam 13
Is formed by extending both front and rear side surfaces thereof in the circumferential direction and curving in a corrugated plate shape (hereinafter referred to as "corrugated curved surface 13 '"). Also, the same cam chamber 5 is installed in both cylinder blocks 16F and 16R.
A suitable number of cylinder bores 4 are bored in parallel with the rotating shaft 3. That is, they are arranged at regular intervals on the same circumference so as to surround the rotary shaft 3. Therefore, each cylinder bore 4 is divided into a front side and a rear side so as to form a front-rear pair with a cam 5 or the like interposed therebetween, and each pair of cylinder bores 4 has a valve plate described later.
The double-headed piston 8 is inserted so as to be able to move back and forth, with the compression chamber 7 existing between 6F and 6R. More specifically, the double-headed piston 8 is a pair of front and rear piston heads 8F, 8R and both piston heads 8F, 8R.
It consists of a bridge part 8'that connects the two piston heads 8F, 8
The R is fitted into the pair of front and rear cylinder bores 4, and the bridge portion 8'is provided so as to cross the inside of the cam chamber 5 with a proper clearance S between the bridge portion 8'and the outer peripheral portion of the disc cam 13. . Further, receiving seats 15 and 15 of rollers 14F and 14R, which will be described later, are provided in a recessed manner so as to face each other at the rear part of both piston heads 8F and 8R.
A pair of front and rear rollers 14F and 14R formed in a columnar shape between the three wavy curved surfaces 13 'are rotatably moored with their rotation center lines a extending in the radial direction of the disc cam 13, respectively. Cam 13
Is provided so that it can be transmitted as a reciprocating motion to each double-headed piston 8. Therefore, the pair of front and rear rollers 14F, 14R are moored with the center line b of the double-headed piston 8 along the front-rear direction (longitudinal direction) interposed therebetween and slightly offset on both sides thereof. That is, as shown in FIG. 4, both rollers 14F and 14R are provided with their center points c displaced from the center line b of the double-headed piston 8 by a distance d in the circumferential direction of the disk cam 8 and the rotation thereof. As shown in FIG. 2, the center line a is provided with a slight deviation angle θ with respect to the center line g connecting the center point e of the rotating shaft 3 and the center point f of the double-headed piston 8.

又、前述のハウジング１において、1Fはフロントバルブ
プレート6Fを間に挟んでフロントシリンダーブロック16
Fの開口端を被覆するフロントハウジング、1Rは同じく
リヤバルブプレート6Rを間に挟んでリヤシリンダーブロ
ック16Rの開口端を被覆するリヤハウジングであって、
両ハウジング1F,1Rには前記各シリンダーボア４と相対
応して吸入室9F,9Rと吐出室10F,10Rが設けられる。そし
てフロントバルブプレート6F及びリヤバルブプレート6R
には上記吸入室9F,9Rと相対応して吸入口が、又、吐出
室10F,10Rと相対応して吐出口が夫々開口される。そし
て又、吸入口には圧縮室７側に位置して吸入弁11F,11R
が両頭ピストン８の吸入行程を介して開閉自在な如く設
けられ、又、吐出口には吐出口10F,10R側に位置して吐
出弁12F,12Rが両頭ピストン８の圧縮行程を介して開閉
自在な如く設けられる。Further, in the above-mentioned housing 1, 1F is the front cylinder block 16 with the front valve plate 6F interposed therebetween.
A front housing that covers the open end of F, 1R is a rear housing that covers the open end of the rear cylinder block 16R with the rear valve plate 6R interposed therebetween,
Both housings 1F, 1R are provided with suction chambers 9F, 9R and discharge chambers 10F, 10R corresponding to the respective cylinder bores 4. And front valve plate 6F and rear valve plate 6R
The suction port is opened in correspondence with the suction chambers 9F, 9R, and the discharge port is opened in correspondence with the discharge chambers 10F, 10R. In addition, the suction port is located on the compression chamber 7 side and the suction valves 11F and 11R are provided.
Is provided so that it can be opened and closed through the suction stroke of the double-headed piston 8, and the discharge valves 12F and 12R located at the discharge ports 10F and 10R are freely openable and closable through the compression stroke of the double-headed piston 8. It is provided as follows.

第６図乃至第９図は第２の実施例を表わす図面であっ
て、上記第１の実施例においては前後各一対のコロ14F,
14Rは回転軸３の中心点ｅと両頭ピストン８の中心点ｆ
とを結ぶ中心線ｇに対して若干の偏位角θを存して設け
られるのに対して、本実施例においては前後各一対のコ
ロ14F,14Rの回転中心線ａは第６図に表わす様に回転軸
３の中心点ｅと両頭ピストン８の中心点ｆとを結ぶ中心
線ｇに対してその間に若干の距離ｈを存して相互に平行
させて設けられる。6 to 9 are drawings showing a second embodiment, and in the first embodiment, a pair of front and rear rollers 14F,
14R is the center point e of the rotary shaft 3 and the center point f of the double-headed piston 8.
In the present embodiment, the rotation center line a of each pair of front and rear rollers 14F and 14R is shown in FIG. In this way, the center point g connecting the center point e of the rotary shaft 3 and the center point f of the double-headed piston 8 is provided in parallel with each other with a slight distance h therebetween.

尚、上記両実施例においては円柱状に形成するコロを使
用しているが、中空部を存して円筒状に形成するコロを
使用することも可能である。It should be noted that although the rollers formed in a cylindrical shape are used in both of the above-described examples, it is also possible to use a roller formed in a cylindrical shape having a hollow portion.

次にその作用を第１図乃至第５図の各図面に表わす第１
の実施例について説明する。Next, the operation will be described with reference to FIG. 1 to FIG.
An example will be described.

電磁クラッチ（図示省略）の接続操作を介してエンジン
の駆動力を回転軸３に伝える事により、カム室５におい
て円盤カム13が回転する状態が得られる。そして同円盤
カム13の波状湾曲面13′と両頭ピストン８の後背部に凹
設する受け座15,15間にはコロ14F,14Rが係留されている
事により、円盤カム13の回転は同コロ14F,14Rの滑り回
転を介して両頭ピストン８に伝達され、各両頭ピストン
８が各シリンダーボア４内において連続的に往復動する
状態が得られる。そしてこの様に両頭ピストン８が連続
的に往復動を繰り返す状態において、両頭ピストン８が
下死点より上死点或いは上死点より下死点に至る行程に
おいては従来構造と同様円盤カム13の波状湾曲面13′に
対する両コロ14F,14Rの接点i,iが両頭ピストン８の前後
方向に沿う中心線ｂを間に存してその両側に対峙する状
態（第13図参照）が得られると共に、両頭ピストン８が
上死点若しくは下死点に到達した状態においても第３図
に表わす様に円盤カム13の波状湾曲面13′に対する両コ
ロ14F,14Rの接点i,iが両頭ピストン８の前後方向に沿う
中心線ｂを間に存してその両側に対峙する状態が得ら
れ、此により両頭ピストン８が円盤カム13の周方向にロ
ーリングするのを阻止する事が出来る。即ち、両頭ピス
トン８のブリッジ部８′が円盤カム13の外周部に衝当す
る事なく往復動する状態が得られる。By transmitting the driving force of the engine to the rotary shaft 3 through the connection operation of the electromagnetic clutch (not shown), the disk cam 13 can be rotated in the cam chamber 5. Since the rollers 14F and 14R are moored between the wavy curved surface 13 'of the disk cam 13 and the receiving seats 15 and 15 recessed in the rear portion of the double-headed piston 8, the disk cam 13 rotates in the same manner. It is transmitted to the double-headed pistons 8 through the sliding rotations of 14F and 14R, so that the double-headed pistons 8 are continuously reciprocated in the respective cylinder bores 4. In this way, in the state where the double-headed piston 8 continuously reciprocates, the double-headed piston 8 travels from the bottom dead center to the top dead center or from the top dead center to the bottom dead center in the same manner as in the conventional structure. While the contact points i, i of the rollers 14F, 14R with respect to the wavy curved surface 13 'face each other on both sides of the center line b extending in the front-back direction of the double-headed piston 8 (see FIG. 13), As shown in FIG. 3, even when the double-headed piston 8 reaches the top dead center or the bottom dead center, the contacts i, i of the two rollers 14F, 14R with respect to the wavy curved surface 13 'of the disc cam 13 are connected to the double-headed piston 8. A state in which a center line b extending along the front-rear direction is interposed and faces each other on both sides of the center line b can be obtained, which can prevent the double-headed piston 8 from rolling in the circumferential direction of the disc cam 13. That is, a state in which the bridge portion 8'of the double-headed piston 8 reciprocates without hitting the outer peripheral portion of the disc cam 13 can be obtained.

尚、本実施例においては円柱状に形成するコロを使用し
ている事により、両コロは波状湾曲面13′と受け座15間
に若干の隙間を存して係留されており、その隙間分だけ
両頭ピストン８が若干ローリングする事となるのである
が、このローリング分を予め計算にいれて隙間Ｓを設定
しておく事により、ブリッジ部が円盤カム13の外周部に
衝当するのを防止する事が可能である。In this embodiment, since the rollers formed in a columnar shape are used, both rollers are moored with a slight gap between the wavy curved surface 13 'and the receiving seat 15, and the amount of the gap is fixed. Only the double-headed piston 8 will roll slightly, but by setting the gap S by calculating this rolling amount in advance, the bridge portion is prevented from hitting the outer peripheral portion of the disc cam 13. It is possible to do

〔発明の効果〕〔The invention's effect〕

本発明は以上の様に構成されるものであって、上記の様
に円盤カムを間に挟んでその両側に係留される前後各一
対のコロを両頭ピストンの前後方向に沿う中心線を間に
存してその両側に若干偏位させて設けた事により、そし
て両頭ピストンが上死点若しくは下死点に到達した状態
において円盤カムに対する両コロの接点が両頭ピストン
の前後方向に沿う中心線を間に存してその両側に対峙す
る状態が得られる様にした事により、両頭ピストンのロ
ーリングを効果的に抑止する事が出来るに至った。即
ち、上死点若しくは下死点において両頭ピストンのブリ
ッジ部を円盤カムの外周部に衝当させる事なく往復動さ
せる事が可能となり、此により騒音を発生させる事なく
静粛な圧縮機の運転状態を得る事が出来るに至った。The present invention is configured as described above, and as described above, a pair of front and rear rollers moored on both sides of the disc cam is sandwiched between the center lines along the front-rear direction of the double-headed piston. However, when the two-headed piston reaches the top dead center or the bottom dead center, the contact points of both rollers with respect to the disk cam form the center line along the front-rear direction of the two-headed piston. By making it possible to obtain a state of facing each other on both sides of the space, it has become possible to effectively suppress the rolling of the double-headed piston. That is, at the top dead center or the bottom dead center, the bridge part of the double-headed piston can be reciprocated without hitting the outer peripheral part of the disk cam, which allows the quiet operation state of the compressor without generating noise. It came to be able to obtain.

そして上記の様に両頭ピストンのローリングを抑止する
事が出来る事により、円盤カムの外周部及び両頭ピスト
ンのブリッジ部における摩耗及びカシリ等を防止する事
が出来る事に加えて、円盤カムの外周部及び両頭ピスト
ンのブリッジ部における仕上げ度合を粗にする事が可能
となり、此により加工工数及び加工コストをその分だけ
低減させる事が出来るに至った。And by suppressing the rolling of the double-headed piston as described above, in addition to being able to prevent wear and caulking in the outer peripheral part of the disc cam and the bridge part of the double-headed piston, the outer peripheral part of the disc cam can be prevented. Further, it becomes possible to roughen the finishing degree in the bridge portion of the double-headed piston, and thereby the processing man-hour and the processing cost can be reduced accordingly.

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

第１図乃至第５図は第１の実施例を表わす図面であっ
て、第１図は円盤カム式圧縮機の全体を表わす横断面
図、第２図はコロ係留部の側断面図、第３図は同平断面
図、第４図は第５図におけるＢ−Ｂ線断面図、第５図は
第４図におけるＡ−Ａ線断面図である。第６図乃至第９
図は第２の実施例を表わす図面であって、第６図はコロ
係留部の側断面図、第７図は同平断面図、第８図は第９
図におけるＤ−Ｄ線断面図、第９図は第８図におけるＣ
−Ｃ線断面図である。又、第10図乃至第12図は従来構造
を表わす図面であって、第10図はコロ係留部の側断面
図、第11図は両頭ピストンが上死点若しくは下死点に到
達した状態を表わすコロ係留部の平断面図、第12図は同
じく両頭ピストンが上死点若しくは下死点に至る行程を
表わすコロ係留部の平断面図、第13図は第14図における
Ｆ−Ｆ線断面図、第14図は第13図におけるＥ−Ｅ線断面
図である。 １……ハウジング、1F……フロントハウジング、1R……
リヤハウジング、2F,2R……軸受け部、３……回転軸、
４……シリンダーボア、５……カム室、6F……フロント
バルブプレート、6R……リヤバルブプレート、７……圧
縮室、８……両頭ピストン、8F,8R……ピストンヘッ
ド、８′……ブリッジ部、9F,9R……吸入室、10F,10R…
…吐出室、11F,11R……吸入弁、12F,12R……吐出弁、13
……円盤カム、13′……波状湾曲面、14F,14R……コ
ロ、15……受け座、16……シリンダーブロック、16F…
…フロントシリンダーブロック、16R……リヤシリンダ
ーブロック、ａ……回転中心線、ｂ……中心線、ｃ……
中心点、ｄ……距離、ｅ……中心点、ｆ……中心点、ｇ
……中心線、ｈ……距離、ｉ……接点、θ……偏位角、
Ｓ……クリアランス。1 to 5 are drawings showing a first embodiment, wherein FIG. 1 is a transverse sectional view showing the whole of a disk cam type compressor, FIG. 2 is a side sectional view of a roller mooring portion, and FIG. 3 is the same plane sectional view, FIG. 4 is a sectional view taken along the line BB in FIG. 5, and FIG. 5 is a sectional view taken along the line AA in FIG. 6 to 9
FIG. 6 is a view showing a second embodiment, FIG. 6 is a side sectional view of a roller mooring portion, FIG. 7 is the same plane sectional view, and FIG.
FIG. 9 is a sectional view taken along line D-D in FIG.
It is a -C line sectional view. 10 to 12 are drawings showing a conventional structure, FIG. 10 is a side sectional view of a roller mooring portion, and FIG. 11 shows a state in which a double-headed piston reaches top dead center or bottom dead center. Fig. 12 is a plane sectional view of the roller mooring portion, and Fig. 12 is a plane sectional view of the roller mooring portion, which also shows the process in which the double-headed piston reaches the top dead center or the bottom dead center, and Fig. 13 is a sectional view taken along line FF in Fig. 14. FIG. 14 is a sectional view taken along the line EE in FIG. 1 …… Housing, 1F …… Front housing, 1R ……
Rear housing, 2F, 2R …… Bearing part, 3 …… Rotary shaft,
4 ... Cylinder bore, 5 ... Cam chamber, 6F ... Front valve plate, 6R ... Rear valve plate, 7 ... Compression chamber, 8 ... Double-headed piston, 8F, 8R ... Piston head, 8 '... Bridge, 9F, 9R ... Inhalation chamber, 10F, 10R ...
… Discharge chamber, 11F, 11R …… Suction valve, 12F, 12R …… Discharge valve, 13
…… Disc cam, 13 ′ …… Wavy curved surface, 14F, 14R …… Roller, 15 …… Catch, 16 …… Cylinder block, 16F…
… Front cylinder block, 16R …… Rear cylinder block, a …… Rotation center line, b …… Center line, c ……
Center point, d ... Distance, e ... Center point, f ... Center point, g
…… Center line, h …… distance, i …… contact point, θ …… deflection angle,
S: Clearance.

Claims (3)

【特許請求の範囲】[Claims] 【請求項１】シリンダーブロック内にカム室を間に存し
て前後一対をなす様にフロント側とリヤ側に対峙させて
複数組のシリンダーボアを回転軸と平行させて穿設し、
各シリンダーボアには両頭ピストンを往復動自在に嵌挿
させる一方、カム室には上記回転軸に固着させて波板状
に湾曲形成する円盤カムを回転自在に設け、同円盤カム
と両頭ピストン間には前後各一対のコロを係留させて成
る円盤カム式往復動型圧縮機において、上記前後各一対
のコロを両頭ピストンの前後方向に沿う中心線を間に存
してその両側に若干偏位させて配設して成る円盤カム式
往復動型圧縮機における両頭ピストンのローリング防止
構造。1. A plurality of sets of cylinder bores are bored in parallel with a rotation axis by facing a front side and a rear side so as to form a pair of front and rear with a cam chamber interposed in the cylinder block.
A double-headed piston is reciprocally fitted in each cylinder bore, while a disc cam that is fixed to the rotary shaft and curved to form a corrugated plate is rotatably provided in the cam chamber. In the disk cam type reciprocating compressor in which a pair of front and rear rollers are moored, the pair of front and rear rollers are slightly displaced on both sides of the center line along the front-back direction of the double-headed piston. A double-headed piston rolling prevention structure in a disk cam type reciprocating compressor that is arranged in parallel. 【請求項２】上記前後各一対のコロはその回転中心線を
回転軸と両頭ピストンの中心点とを結ぶ中心線に対して
若干の偏位角を存して設けた事を特徴とする特許請求の
範囲第１項に記載の円盤カム式往復動型圧縮機における
両頭ピストンのローリング防止構造。2. A pair of front and rear rollers provided with a slight deviation angle with respect to a center line connecting a rotation shaft and a center point of a double-headed piston. A structure for preventing rolling of a double-headed piston in a disk cam type reciprocating compressor according to claim 1. 【請求項３】上記前後各一対のコロはその回転中心線を
回転軸と両頭ピストンの中心点とを結ぶ中心線に対して
相互に平行させて設けた事を特徴とする特許請求の範囲
第１項に記載の円盤カム式往復動型圧縮機における両頭
ピストンのローリング防止構造。3. The pair of front and rear rollers are provided such that their rotation center lines are parallel to each other with respect to the center line connecting the rotation shaft and the center point of the double-headed piston. A rolling prevention structure for a double-headed piston in the disc cam reciprocating compressor according to item 1.
JP61302594A 1986-11-28 1986-12-18 Rolling prevention structure of double-headed piston in disk cam type reciprocating compressor Expired - Lifetime JPH076499B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP61302594A JPH076499B2 (en) 1986-12-18 1986-12-18 Rolling prevention structure of double-headed piston in disk cam type reciprocating compressor
US07/122,256 US4756239A (en) 1986-11-28 1987-11-18 Anti-rolling structure for double headed piston of disc cam type reciprocative compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP61302594A JPH076499B2 (en) 1986-12-18 1986-12-18 Rolling prevention structure of double-headed piston in disk cam type reciprocating compressor

Publications (2)

Publication Number Publication Date
JPS63154868A JPS63154868A (en) 1988-06-28
JPH076499B2 true JPH076499B2 (en) 1995-01-30

Family

ID=17910857

Family Applications (1)

Application Number Title Priority Date Filing Date
JP61302594A Expired - Lifetime JPH076499B2 (en) 1986-11-28 1986-12-18 Rolling prevention structure of double-headed piston in disk cam type reciprocating compressor

Country Status (1)

Country Link
JP (1) JPH076499B2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114941616A (en) * 2022-04-11 2022-08-26 北京空天技术研究所 Double-motion-freedom-degree piston single pump

Also Published As

Publication number Publication date
JPS63154868A (en) 1988-06-28

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