JPH0444863Y2 - - Google Patents
Info
- Publication number
- JPH0444863Y2 JPH0444863Y2 JP18466786U JP18466786U JPH0444863Y2 JP H0444863 Y2 JPH0444863 Y2 JP H0444863Y2 JP 18466786 U JP18466786 U JP 18466786U JP 18466786 U JP18466786 U JP 18466786U JP H0444863 Y2 JPH0444863 Y2 JP H0444863Y2
- Authority
- JP
- Japan
- Prior art keywords
- cam
- roller
- double
- piston
- disc cam
- 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
Links
- 230000000694 effects Effects 0.000 description 6
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
Landscapes
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案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の回転を介し
て両頭ピストンを往復動させる事によつて圧縮作
用を得る様に様に設けられる圧縮機において、同
円盤カムと両頭ピストンとの間に係留されるコロ
部分の改良、即ち、円盤カム式往復動型圧縮機に
おけるコロの係留構造に関する。[Detailed description of the invention] [Industrial application field] The present invention is a disc cam type reciprocating compressor, more specifically, it reciprocates a double-ended piston through the rotation of a disc cam formed in the shape of a corrugated plate. In a compressor that is installed in a similar manner to obtain a compression effect by moving the disk cam, improvements are made to the roller portion moored between the disk cam and the double-headed piston. Regarding mooring structure.
一般に円盤カム式の圧縮機においては第４図と
第５図の両図面に表わす様にハウジング１（若し
くはシリンダーブロツク）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に軸架させて波板状に湾曲
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の後背部と円盤カム１３
間には円柱状に形成するコロ１４が係留され、同
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。更
に具体的には円盤カム１３は波状に湾曲形成され
ていることにより、コロ１４の係留部においてピ
ストン８が下死点より上死点に至る間に円盤カム
１３とピストン８間の間隔が微妙に変化すること
となるのであるが、この様な間隔の変化に対応さ
せるべくコロ１４は円盤カム１３とピストン８に
対して微小隙間を存して係留され、同円盤カム１
３とピストン８に対して滑りを生じさせ乍ら動力
伝達を行なうことが出来る様に設けられる。（実
開昭57−114184号公報）
〔考案が解決しようとする問題点〕
しかして上記の様な従来構造の円盤カム式圧縮
機にあつては、コロ１４の係留部に微小隙間が設
けられている事により、円盤カム１３とピストン
８との間に滑り作用が得られ、此によりスムーズ
な動力伝達が得られる反面、圧縮機の運転時にお
いてピストン８の往復運動により所謂ガタ付きが
生じ、その衝撃により騒音が発生するという不具
合に加えて、この衝撃によりコロ１４と円盤カム
１３に早期摩耗及び剥離が生じ易い点、即ち、コ
ロ１４と円盤カム１３の耐久性が損われるという
不具合を生ずる点に第１の問題点を有する。
In general, in a disk cam type compressor, a pair of front and rear cylinder bores 4 rotate with a cam chamber 5 between them in a housing 1 (or cylinder block), as shown in FIGS. 4 and 5. The holes are drilled parallel to the axis 3 at regular intervals. The cam chamber 5 is rotatably provided with a disc cam 13 which is mounted on the rotating shaft 3 and curved in the shape of a corrugated plate, while a double-headed piston is inserted through the cam chamber 5 into each cylinder bore 4. 8 is inserted so that it can move forward and backward.
Also, the rear part of the same piston 8 and the disc cam 13
A cylindrical roller 14 is moored between them, and is provided so that the rotation of the disc cam 13 can be transmitted to each piston 8 as reciprocating motion. More specifically, since the disk cam 13 is curved in a wave-like manner, the distance between the disk cam 13 and the piston 8 is slight while the piston 8 moves from the bottom dead center to the top dead center at the mooring part of the roller 14. In order to accommodate this change in spacing, the roller 14 is moored to the disc cam 13 and the piston 8 with a small gap, and the disc cam 1
The piston 3 and the piston 8 are provided so as to be able to transmit power while causing slippage. (Publication of Utility Model Application No. 57-114184) [Problem to be solved by the invention] However, in the disk cam type compressor of the conventional structure as described above, a small gap is provided in the mooring part of the rollers 14. Due to this, a sliding action is obtained between the disc cam 13 and the piston 8, and although smooth power transmission is obtained, the reciprocating movement of the piston 8 during compressor operation causes so-called rattling. In addition to the problem that the impact generates noise, this impact tends to cause premature wear and peeling of the rollers 14 and the disk cam 13, which causes a problem that the durability of the rollers 14 and the disk cam 13 is impaired. The first problem lies in this point.
又、往復動型の圧縮機としては上記の様な円盤
カム式の圧縮機の他に斜板式の圧縮機があり、同
斜板式の圧縮機においては斜板（円盤カムに相当
する）と両頭ピストンの間にシユーが係留される
のであるが、このシユーと比較してコロの重量が
重いためにその分だけ往復質量が大きくなり、往
復運動部分におけるトルクの変動幅が大きくなつ
てしまうという不具合を生ずる点に第２の問題点
を有する。 In addition to the disc cam type compressor mentioned above, there is also a swash plate type compressor as a reciprocating compressor. The shoe is moored between the pistons, but since the weight of the roller is heavier than the shoe, the reciprocating mass increases accordingly, resulting in a larger range of torque fluctuations in the reciprocating part. There is a second problem in that this occurs.
本考案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つて、円盤カムと両頭ピ
ストンとの間に形成されるコロの係留部におい
て、同円盤カムと両頭ピストンとの間に形成され
る間隔の変化に対応して同コロを常時円盤カムと
両頭ピストン間に隙間を生ずる事なく係留する状
態を保持す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、本考案は円盤カムと
ピストンとの間に形成されるコロの係留部におい
て、同コロを内径方向に向けて屈撓変形可能に形
成する事によつて、そして同コロをその屈撓変形
を介して円盤カムとピストン間に係留させる様に
する事によつて、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つて、その具体的な手段
と作用は次の通りである。 The present invention is an attempt to improve the above-mentioned problems, and in the mooring part of the roller formed between the disc cam and the double-ended piston, the disc cam and the double-ended piston The problem to be solved is to be able to maintain the moored state of the roller at all times without creating a gap between the disk cam and the double-ended piston in response to changes in the gap formed between the disk cam and the double-ended piston. . That is, the present invention has been developed by forming the roller in the mooring part of the roller formed between the disc cam and the piston so that the roller can be bent and deformed in the inner diameter direction, and by making the roller bendable and deformable in the inner diameter direction. The feature is that the above problem is solved by mooring between the disc cam and the piston via a cam.The specific means and operation thereof are as follows. be.
シリンダーブロツ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
軸に軸架させて波板状に湾曲させて形成する円盤
カムを回転自在に設け、同円盤カムと両頭ピスト
ン間にはコロを係留させて成る円盤カム式圧縮機
において、
上記コロを中空円筒状に形成する。
Inside the cylinder block, multiple sets of cylinder bores are bored parallel to the axis of rotation, facing each other on the front and rear sides to form a pair of front and rear cylinders, with a cam chamber in between, and each cylinder bore is equipped with a double-headed piston. A disc cam is fitted in the cam chamber so as to be reciprocally movable, and a disc cam, which is curved into a corrugated plate shape and mounted on the above-mentioned rotating shaft, is rotatably installed in the cam chamber, and a roller is installed between the disc cam and the double-ended piston. In a moored disk cam type compressor, the rollers are formed into a hollow cylindrical shape.
同コロを圧縮変形させた状態にて円盤カムと
両頭ピストン間に介装させる。即ち、この圧縮
変形を介してコロが円盤カムと両頭ピストンに
対して常時圧接する状態が得られる様にする。 The roller is compressed and deformed and inserted between the disc cam and the double-headed piston. That is, through this compressive deformation, a state is obtained in which the rollers are constantly in pressure contact with the disc cam and the double-headed piston.
コロを圧縮変形させた状態にて円盤カムと両頭
ピストン間に組付ける事により、その反力によつ
て円盤カムと両頭ピストンとの間に生ずる間隔の
変化を吸収することが出来る。即ち、常時円盤カ
ムと両頭ピストンとの間に隙間を生ずる事なくコ
ロを係留する状態が得られ、これにより圧縮機の
運転時においてコロの係留部におけるガタ付きの
発生を防止する事が出来る。
By assembling the rollers between the disc cam and the double-headed piston in a compressed and deformed state, it is possible to absorb changes in the distance between the disc cam and the double-headed piston due to the reaction force. That is, a condition is obtained in which the rollers are always moored without creating a gap between the disk cam and the double-ended piston, and thereby it is possible to prevent the occurrence of wobbling at the mooring portion of the rollers during operation of the compressor.
以下に本考案の具体的な実施例を例示の図面に
ついて説明する。
Hereinafter, specific embodiments of the present invention will be described with reference to the illustrative drawings.
第１図と第２図の両図面において、１６はシリ
ンダーブロツクを示す。同シリンダーブロツク１
６はフロントシリンダーブロツク１６Ｆとリヤシ
リンダーブロツク１６Ｒより成り、両シリンダー
ブロツク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、同軸受け部２
Ｆ，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ツチ（図示省略）
に連結され、同電磁クラツ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
リンダーブロツク１６Ｆ，１６Ｒには適数個のシ
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を囲撓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。 In both FIGS. 1 and 2, 16 designates a cylinder block. Same cylinder block 1
6 consists of a front cylinder block 16F and a rear cylinder block 16R, and both cylinder blocks 16F and 16R are provided with bearing portions 2F and 2R located at their centers.
A rotating shaft 3 is rotatably supported on F and 2R.
One end of the rotating shaft 3 passes through the front housing 1F, which will be described later, and connects to an electromagnetic clutch (not shown).
The driving force of the engine (not shown) is connected to the rotary shaft 3 through the connection and disconnection of the electromagnetic clutch.
It is set up so that it can be transmitted to. Further, an appropriate number of cylinder bores 4 are bored in both cylinder blocks 16F and 16R parallel to the rotating shaft 3. That is, they are arranged at regular intervals on the same circumference so as to surround the rotating shaft 3.
しかして各シリンダーボア４はカム室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。又、１Ｆはフロントバルブプレート６
Ｆを間に挟んでフロントシリンダーブロツク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
ヤシリンダーブロツク１６Ｒの開口端を被覆する
リヤハウジングであつて、両ハウジング１Ｆ，１
Ｒ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が環状の隔
壁を間に存して同心円状に設けられる。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、吐出口には吐出室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。 Each cylinder bore 4 is divided into a front side and a rear side so as to form a front and rear pair with a cam chamber 5 in between.
A compression chamber 7 is provided between valve plates 6F and 6R, which will be described later, and a double-headed piston 8 is fitted therein so as to be able to move forward and backward. Also, 1F is the front valve plate 6
Front cylinder block 16 with F in between
Front housing that covers the open end of F, 1R
is a rear housing that similarly covers the open end of the rear cylinder block 16R with the rear valve plate 6R in between, and both housings 1F, 1
In R, suction chambers 9F, 9R and discharge chambers 10F, 10R are provided concentrically in correspondence with each cylinder bore 4 with an annular partition between them. The front valve plate 6F and the rear valve plate 6R have suction ports corresponding to the suction chambers 9F and 9R, and discharge ports corresponding to the discharge chambers 10F and 10R, respectively. Further, suction valves 11F and 11R are provided at the suction port so as to be located on the side of the compression chamber 7 and can be opened and closed via the suction stroke of the double-headed piston 8, and discharge chambers 10F and 10R are provided at the discharge port.
Discharge valves 12F and 12R are provided on the sides so as to be openable and closable through the compression stroke of the double-headed piston 8.
一方、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）。そして同円盤カム１３と前記両
頭ピストン８間にはコロ１４がその回転中心を
夫々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。更に詳しくは、各コロ１４は中空部１４′を
存して円筒状に形成され、その外周面が上記波状
湾曲面１３′と両頭ピストン８の後背面に嵌着す
る滑り部材１５に対して両当たり可能に設けられ
る。即ち、各コロ１４は中空部１４′を介して屈
撓変形自在に形成し、且つ両頭ピストン８が上死
点にある時の滑り部材１５のコロ嵌合部１５′底
面と前記湾曲面１３′との間隔Ａよりも大径若し
くは略同径寸法を存して形成され、同コロ１４を
内径方向に圧縮変形させた状態にて円盤カム１３
と両頭ピストン８間に介装させる事により、波状
湾曲面１３′と滑り部材１５に対して常時摺接状
態にある様に設けられる。 On the other hand, in the cam chamber 5, a disc cam 13 is rotatably mounted on the rotating shaft 3. The disc cam 13 is formed by extending both its front and rear surfaces in the circumferential direction and curved into a corrugated plate shape (hereinafter referred to as "wavy curved surface 13'"). A roller 14 is moored between the disc cam 13 and the double-headed piston 8 so that the roller 14 can freely rotate with its rotation center extending in the radial direction.
It is provided so that the rotation of the disk cam 13 can be transmitted to each double-ended piston 8 as a reciprocating motion. More specifically, each roller 14 is formed into a cylindrical shape with a hollow portion 14', and its outer circumference faces both the wavy curved surface 13' and the sliding member 15 fitted to the rear surface of the double-ended piston 8. It is set up so that it can be hit. That is, each roller 14 is formed to be flexible and deformable through a hollow portion 14', and when the double-headed piston 8 is at the top dead center, the bottom surface of the roller fitting portion 15' of the sliding member 15 and the curved surface 13' are formed. The disk cam 13 is formed to have a diameter larger than or approximately the same diameter as the distance A between the disk cam 13 and the roller 14 in a state where the roller 14 is compressed and deformed in the inner diameter direction.
By interposing it between the piston 8 and the double-headed piston 8, it is provided so that it is always in sliding contact with the wavy curved surface 13' and the sliding member 15.
次にその作用について説明する。 Next, its effect will be explained.
電磁クラツチ（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と両頭ピストン
８間には波状湾曲面１３′と滑り部材１５に当接
させてコロ１４が係留されている事により、円盤
カム１３の回転は同コロ１４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。しかして各コロ１４は中空部１４′を介
して内径方向に向けて若干圧縮変形させた状態に
て円盤カム１３と両頭ピストン８間に係留されて
いることにより、各コロ１４はその反力によつて
波状湾曲面１３′と滑り部材１５に対して常時圧
接する状態、即ち、両頭ピストン８と円盤カム１
３間に生ずる間隔の変化に対応して波状湾曲面１
３′と滑り部材１５に対して常時その間に隙間を
生ずる事なく係留する状態が得られる。そしてこ
の様にコロ１４を波状湾曲面１３′と滑り部材１
５に対して常時その間に隙間を生ずる事なく係留
する事が出来る事により、圧縮機の運転時におい
て同係留部にガタ付きを生ずる事なく圧縮作用を
得る事が出来る。即ち、同係留部における衝撃音
の発生を防止する事が出来ると共に、上記ガタ付
きに起因するコロ１４と円盤カム１３の早期摩耗
及び剥離を抑止する事が出来る。 By transmitting the driving force of the engine to the rotating shaft 3 through the connection operation of an electromagnetic clutch (not shown),
A state in which the disc cam 13 rotates in the cam chamber 5 is obtained. A roller 14 is moored between the disc cam 13 and the double-headed piston 8 in contact with the wavy curved surface 13' and the sliding member 15, so that the rotation of the disc cam 13 is transmitted via the roller 14 to the double-headed piston. 8, and a state is obtained in which each double-ended piston 8 continuously reciprocates within each cylinder bore 4. Since each roller 14 is moored between the disk cam 13 and the double-headed piston 8 while being slightly compressed and deformed in the inner radial direction through the hollow portion 14', each roller 14 responds to the reaction force. Therefore, the state in which the wavy curved surface 13' and the sliding member 15 are constantly in pressure contact, that is, the double-ended piston 8 and the disc cam 1
The wavy curved surface 1 corresponds to the change in the interval that occurs between 3.
3' and the sliding member 15 are always moored without any gap between them. In this way, the roller 14 is connected to the wavy curved surface 13' and the sliding member 1.
5 can be moored without creating any gap between them at all times, so that a compressive action can be obtained without causing rattling in the mooring portion during operation of the compressor. That is, it is possible to prevent impact noise from occurring in the mooring portion, and to prevent early wear and peeling of the rollers 14 and disc cam 13 due to the above-mentioned rattling.
尚、上記実施例の様にコロ１４を中空円筒状に
形成する事に加えて、円盤カム１３と滑り部材１
５を中空状に形成する事も可能である。 In addition to forming the roller 14 in a hollow cylindrical shape as in the above embodiment, the disc cam 13 and the sliding member 1
5 can also be formed into a hollow shape.
本考案は以上の様に構成されるものであつて、
上記の様に円盤カムと両頭ピストンとの間に係留
されるコロを中空円筒状に形成し、そして同コロ
を内径方向に向けて圧縮変形させた状態にて円盤
カムと両頭ピストン間に介装させる様にした事に
より、同コロを円盤カムと両頭ピストンとの間に
常時隙間を生ずる事なく係留する状態を得る事が
出来るに至つた。そしてこの様に円盤カムと両頭
ピストンとの間に隙間を生ずる事なくコロを係留
させる事が出来る事により、同係留部において騒
音を発生させる事なく圧縮機を運転させる事が出
来ると共に、同コロ及び円盤カムの早期摩耗及び
剥離を効果的に防止する事が出来るに至つた。
The present invention is constructed as described above.
As mentioned above, the roller moored between the disc cam and the double-headed piston is formed into a hollow cylindrical shape, and the roller is compressed and deformed in the inner radial direction and then interposed between the disc cam and the double-headed piston. By doing so, it became possible to obtain a state in which the roller is always moored between the disc cam and the double-ended piston without creating a gap. Since the roller can be moored without creating a gap between the disc cam and the double-ended piston in this way, the compressor can be operated without generating noise at the mooring part, and the roller It has also become possible to effectively prevent early wear and peeling of the disc cam.
又、本考案においては上記の様にコロを中空円
筒状に形成した事により、その分だけ軽量化する
事が出来る事に加えて両頭ピストンを往復運動部
分の質量を小さくする事が可能となり、此により
同係留部におけるトルクの変動幅を小さくする事
が出来るに至つた。加えて運転時に発生する摩擦
熱のその放熱効果を高める事が出来るに至つた。 In addition, in this invention, by forming the rollers into a hollow cylindrical shape as described above, it is possible to reduce the weight accordingly, and in addition, it is possible to reduce the mass of the reciprocating part of the double-headed piston. This made it possible to reduce the range of torque fluctuations in the mooring section. In addition, it has become possible to enhance the heat dissipation effect of the frictional heat generated during operation.
即ち、本考案においては上記の様な効果が得ら
れる事により、コロ及び円盤カムの耐久性を著し
く向上させる事が出来るに至つた。 That is, in the present invention, by obtaining the above-mentioned effects, it has become possible to significantly improve the durability of the rollers and disk cam.
第１図は円盤カム式圧縮機の全体を表わす縦断
面図、第２図と第３図は係留部におけるコロの作
用状態を表わす拡大図である。又、第４図と第５
図は従来構造を表わす図面であつて、第４図は円
盤カム式圧縮機の全体を表わす縦断面図、第５図
は同平断面図である。
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，６Ｒ……バルブプレート、
７……圧縮室、８……両頭ピストン、９Ｆ，９Ｒ
……吸入室、１０Ｆ，１０Ｒ……吐出室、１１
Ｆ，１１Ｒ……吸入弁、１２Ｆ，１２Ｒ……吐出
弁、１３……円盤カム、１３′……波状湾曲面、
１４……コロ、１４′……中空部、１５……滑り
部材、１５′……コロ嵌合部、１６……シリンダ
ーブロツク、１６Ｆ……フロントシリンダーブロ
ツク、１６Ｒ……リヤシリンダーブロツク。
FIG. 1 is a longitudinal cross-sectional view showing the entire disk cam type compressor, and FIGS. 2 and 3 are enlarged views showing the operating state of the rollers in the mooring section. Also, Figures 4 and 5
The drawings are drawings showing a conventional structure, and FIG. 4 is a longitudinal cross-sectional view showing the entire disc cam type compressor, and FIG. 5 is a planar cross-sectional view thereof. 1... Housing, 1F... Front housing, 1R... Rear housing, 2F, 2R... Bearing section, 3... Rotating shaft, 4... Cylinder bore,
5...Cam chamber, 6F, 6R...Valve plate,
7...Compression chamber, 8...Double-ended piston, 9F, 9R
...Suction chamber, 10F, 10R...Discharge chamber, 11
F, 11R... Suction valve, 12F, 12R... Discharge valve, 13... Disc cam, 13'... Wavy curved surface,
14... Roller, 14'... Hollow part, 15... Sliding member, 15'... Roller fitting part, 16... Cylinder block, 16F... Front cylinder block, 16R... Rear cylinder block.
Claims (1)
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
軸に軸架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、上記コロを中空円筒状に形成すると
共に、同コロを内径方向に向けて変形させた状態
にて円盤カムと両頭ピストン間に介装させて成る
円盤カム式往復動型圧縮機におけるコロの係留構
造。 Inside the cylinder block, multiple sets of cylinder bores are bored parallel to the axis of rotation, facing each other on the front and rear sides to form a pair of front and rear cylinders, with a cam chamber in between, and each cylinder bore is equipped with a double-headed piston. A disc cam is fitted in the cam chamber so as to be able to reciprocate, while a disc cam which is mounted on the rotating shaft and curved in the shape of a corrugated plate is rotatably installed in the cam chamber, and a roller is moored between the disc cam and the double-ended piston. In the disk cam type reciprocating compressor, the roller is formed into a hollow cylindrical shape, and the roller is deformed in the inner diameter direction and is interposed between the disk cam and the double-headed piston. Mooring structure of rollers in a cam type reciprocating compressor.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18466786U JPH0444863Y2 (en) | 1986-11-28 | 1986-11-28 | |
| 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 |
|---|---|---|---|
| JP18466786U JPH0444863Y2 (en) | 1986-11-28 | 1986-11-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6390081U JPS6390081U (en) | 1988-06-11 |
| JPH0444863Y2 true JPH0444863Y2 (en) | 1992-10-22 |
Family
ID=31132559
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18466786U Expired JPH0444863Y2 (en) | 1986-11-28 | 1986-11-28 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0444863Y2 (en) |
-
1986
- 1986-11-28 JP JP18466786U patent/JPH0444863Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6390081U (en) | 1988-06-11 |
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