JP2798981B2 - Fluid machinery - Google Patents
Fluid machineryInfo
- Publication number
- JP2798981B2 JP2798981B2 JP1166887A JP16688789A JP2798981B2 JP 2798981 B2 JP2798981 B2 JP 2798981B2 JP 1166887 A JP1166887 A JP 1166887A JP 16688789 A JP16688789 A JP 16688789A JP 2798981 B2 JP2798981 B2 JP 2798981B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- rotating body
- piston
- peripheral surface
- grooves
- 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 - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/10—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member
- F04C18/107—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth equivalents, e.g. rollers, than the inner member with helical teeth
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
【発明の詳細な説明】 ［発明の目的］ （産業上の利用分野） 本発明は、例えば冷凍サイクルの冷媒ガスを圧縮する
流体機械に関する。[Detailed Description of the Invention] [Object of the Invention] (Industrial application field) The present invention relates to a fluid machine for compressing refrigerant gas of a refrigeration cycle, for example.
（従来の技術） 例えば、本出願人による特願昭63−170692号明細書、
或いは特開昭64−36990号明細書などに開示されている
ような流体機械の一つである流体圧縮機（以下、圧縮機
と称する）１が知られている。すなわち、このタイプの
圧縮機１は、第３図に示すように、密閉ケース２の内部
に設けられロータ３とテータ４とからなるモータ５によ
り、ロータ３に固定され圧縮機構部６を構成するシリン
ダ７を回転させるものである。(Prior Art) For example, the specification of Japanese Patent Application No.
Alternatively, a fluid compressor (hereinafter, referred to as a compressor) 1 which is one of fluid machines disclosed in Japanese Patent Application Laid-Open No. 64-36990 is known. That is, as shown in FIG. 3, the compressor 1 of this type is fixed to the rotor 3 by a motor 5 provided inside the closed case 2 and including the rotor 3 and the theta 4 to constitute a compression mechanism 6. The cylinder 7 is rotated.
そして、この圧縮機１は、シリンダ２内に、シリンダ
７の内部にシリンダ７の軸心Ａに対して偏心量ｅを有す
るピストン８を軸支している。さらに、圧縮機１は、こ
のピストン８に外周に１つの螺旋状の溝９を、第４図に
概略的に示すように、ピストン８の軸方向一端側から他
端側へ徐々に小さくなるピッチで連続的に形成してい
る。そして、圧縮機１はこの溝９に、適度な可撓性を有
する螺旋状のブレード10を嵌め込んでいる。In the compressor 1, a piston 8 having an eccentric amount e with respect to the axis A of the cylinder 7 is supported inside the cylinder 7. Further, the compressor 1 is provided with a single spiral groove 9 on the outer periphery of the piston 8, as schematically shown in FIG. 4, a pitch gradually decreasing from one axial end of the piston 8 to the other axial end. Are formed continuously. The compressor 1 has a spiral blade 10 having appropriate flexibility fitted in the groove 9.
ここで、図中のＢはピストン８の軸心を示している。 Here, B in the figure indicates the axis of the piston 8.
さらに、この圧縮機１は、シリンダ７の内部に、上記
ブレード10によって仕切られ、シリンダ７の吐出端側に
位置するものほど徐々に容積が小さくなる複数の作動室
11…を有している。そして、最も吸込端側の端に位置す
る吸込室11aに例えば冷凍サイクル中の冷媒ガスを吸込
み、シリンダ７とピストン８とを相対的に、且つ同期的
に回転させる。そして、圧縮機１は、上記冷媒ガスを圧
縮しながらシリンダ７の吐出端側へ移送し、圧縮した冷
媒ガスを密閉ケース内等に吐出して冷媒サイクル中に戻
す。Further, the compressor 1 has a plurality of working chambers partitioned inside the cylinder 7 by the blades 10, the volume of which is gradually reduced toward the discharge end side of the cylinder 7.
11 ... Then, for example, refrigerant gas in a refrigeration cycle is sucked into the suction chamber 11a located at the end closest to the suction end, and the cylinder 7 and the piston 8 are relatively and synchronously rotated. Then, the compressor 1 transfers the compressed refrigerant gas to the discharge end side of the cylinder 7 while compressing the refrigerant gas, discharges the compressed refrigerant gas into a closed case or the like, and returns the refrigerant gas to the refrigerant cycle.
また、ピストン８の外周に螺旋状のブレード10を巻装
したタイプの圧縮機として、例えば、本出願人が特願昭
63−170693号明細書に開示したようなものがある。As a compressor of the type in which a spiral blade 10 is wound around the outer periphery of a piston 8, for example,
There is one such as disclosed in the specification of JP 63-176993.
すなわち、このタイプのものは、第５図に概略的に示
すように２つの螺旋状の溝９、９を、ピストン８に軸心
方向中間部から両端部に亘ってそれぞれ形成し、この溝
９、９にそれぞれ螺旋状のブレードを嵌め込んでいる。
そして、このタイプの圧縮機は、冷媒ガスをシリンダ
の、例えば軸心方向中間部から吸込み、この冷媒ガスを
２方向、即ちシリンダの軸心方向両端部へそれぞれ移送
しながら圧縮して、シリンダ両端部から吐出するように
なっている。That is, in this type, two helical grooves 9, 9 are formed in the piston 8 from the axial center part to both end parts, respectively, as schematically shown in FIG. , 9 are fitted with spiral blades, respectively.
This type of compressor sucks refrigerant gas from, for example, an axially middle portion of the cylinder, compresses the refrigerant gas while transferring the refrigerant gas to two directions, that is, both ends in the axial direction of the cylinder, and compresses both ends of the cylinder. The liquid is discharged from the section.
ここで、第５図中に12で示すのは、シリンダ内に冷媒
ガスを供給する吸込み通路である。Here, reference numeral 12 in FIG. 5 denotes a suction passage for supplying a refrigerant gas into the cylinder.
（発明が解決しようとする課題） ところで、第５図に要部を示すようにピストン８（お
よび、シリンダ）の軸心方向両端部から移送・圧縮した
冷媒ガスを吐出するようにした圧縮機には、ピストン８
に両端側から中間部側へ向かって作用するスラスト力が
衡り合うこと、およびピストンに１つの溝を形成したタ
イプのものに比べて、同じ能力を有する場合には、ブレ
ードの変形応力が小さいことなどの長所がある。(Problems to be Solved by the Invention) By the way, as shown in FIG. 5, a compressor which discharges refrigerant gas transferred and compressed from both axial ends of a piston 8 (and a cylinder) is shown. Is the piston 8
When the thrust forces acting from both end sides toward the middle part are balanced, and when the piston has the same capacity as that of the type having one groove formed therein, the deformation stress of the blade is small. There are advantages such as things.
さらに、第３図〜第５図に示すようなタイプの圧縮機
では、負荷トルクや吐出脈動は、第６図中に示すよう
に、ピストンの回転角に伴ってsinカーブを描きながら
変動するが、第５図に示すような、冷媒ガスの移送・圧
縮を２方向に行うタイプのものでは、負荷トルクや吐出
脈動の値は、１方向への移送・圧縮に関する値を２倍し
た大きさに略等しくなる。Further, in a compressor of the type shown in FIGS. 3 to 5, the load torque and the discharge pulsation fluctuate while drawing a sin curve with the rotation angle of the piston as shown in FIG. As shown in FIG. 5, in the type in which the transfer and compression of the refrigerant gas is performed in two directions, the values of the load torque and the discharge pulsation are twice as large as the values related to the transfer and compression in one direction. It is almost equal.
このため、冷媒ガスの移送・圧縮を２方向に行うタイ
プの圧縮機の前述のような長所をのばし、圧縮機の性能
を高めるためには、負荷トルクや吐出脈動等の変動を小
とすることが必要である。Therefore, in order to extend the above-mentioned advantages of the compressor of the type which transfers and compresses the refrigerant gas in two directions, and to improve the performance of the compressor, it is necessary to reduce fluctuations in load torque and discharge pulsation. is required.
本発明の目的とするところは、負荷トルクや吐出脈動
等の小さい流体機械を提供することにある。An object of the present invention is to provide a fluid machine with small load torque and discharge pulsation.
［発明の構成］ （課題を解決するための手段および作用） 上記目的を達成するために本発明は、吸込側と吐出側
とを有するシリンダと、このシリンダ内にシリンダの軸
方向に沿うとともに偏心して配置され、その一部がシリ
ンダの内周面に接触した状態でシリンダと相対的に回転
可能な円柱状の回転体と、この回転体の外周に設けら
れ、それぞれが互いに異なる向きに形成され回転体の中
間部から両端部に亘って形成されるとともに、互いに位
相を約180度ずらした２つの螺旋状の溝と、両溝に回転
体の略径方向に出入自在にそれぞれ嵌め込まれるととも
に、シリンダの内周面に密着する外周面を有し、シリン
ダの内周面と回転体の外周面との間の空間を複数の作動
室に区画する２つの螺旋状のブレードと、シリンダと回
転体とを相対的に回転させ、シリンダの吸込側から作動
室に流入した流体をシリンダ吐出側の作動室へ順次移送
する駆動手段とを具備したことにある。[Constitution of the Invention] (Means and Actions for Solving the Problems) In order to achieve the above object, the present invention provides a cylinder having a suction side and a discharge side, and a cylinder in the cylinder along the axial direction of the cylinder. A cylindrical rotating body that is rotatable relative to the cylinder while a part thereof is in contact with the inner circumferential surface of the cylinder, and provided on the outer circumference of the rotating body, each of which is formed in a different direction from each other. While being formed from the middle part of the rotating body to both ends, the two spiral grooves whose phases are shifted from each other by about 180 degrees, and are fitted into both grooves so as to be able to freely enter and exit substantially in the radial direction of the rotating body, Two helical blades having an outer peripheral surface in close contact with the inner peripheral surface of the cylinder, and partitioning a space between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotating body into a plurality of working chambers; And relative times Is allowed, lies in the and a driving means for sequentially transferring the fluid flowing into the working chamber from the suction side of the cylinder to the working chamber of the cylinder discharge side.
こうすることによって本発明は、負荷トルクや吐出脈
動等の変動を大幅に低減できるようにしたことにある。By doing so, the present invention is to greatly reduce fluctuations in load torque, discharge pulsation, and the like.
また、回転体の中間部に形成された２つの溝の始点を
軸方向に交差させることなく近接させたことにより、回
転体を短く形成できるようにしたことにある。Further, the starting point of the two grooves formed in the intermediate portion of the rotating body is made close to each other without intersecting in the axial direction, so that the rotating body can be formed short.
（実施例） 以下、本発明の一実施例を第１図および第２図に基づ
いて説明する。(Embodiment) An embodiment of the present invention will be described below with reference to FIG. 1 and FIG.
第１図は本発明の一実施例の要部を概略的に示すもの
である。そして、図中の21は、流体機械であって例えば
冷凍サイクルに使用される流体圧縮機の圧縮機構部を構
成する、回転体としてのピストンである。このピストン
21は、略一定の外径を有する円柱状に形成されたもの
で、図示しないシリンダの中に収納され軸支されてい
る。そして、ピストン21は、上記シリンダの軸心に対し
て偏心しており、さらに、その外周面の一部の軸心方向
略全長に亘る部分をシリンダに接している。FIG. 1 schematically shows a main part of one embodiment of the present invention. Further, reference numeral 21 in the figure denotes a fluid machine, for example, a piston as a rotating body which constitutes a compression mechanism of a fluid compressor used in a refrigeration cycle. This piston
Numeral 21 is formed in a columnar shape having a substantially constant outer diameter, and is accommodated in a cylinder (not shown) and supported by a shaft. The piston 21 is eccentric with respect to the axis of the cylinder, and a portion of the outer peripheral surface, which extends over substantially the entire length in the axial direction, is in contact with the cylinder.
また、ピストン21はその外周面に、ピストン21の軸心
方向中間部と両端部との間に亘ってそれぞれ形成された
２つの螺旋状の溝22、23を有している。そして、ピスト
ン21は、この溝22、23の幅を略一定に設定されており、
さらに、溝22、23の深さ方向をピストンその径方向に略
一致させている。Further, the piston 21 has two spiral grooves 22, 23 formed on the outer peripheral surface thereof between the axially intermediate portion and both end portions of the piston 21, respectively. The width of the grooves 22 and 23 of the piston 21 is set substantially constant,
Further, the depth direction of the grooves 22, 23 is made substantially coincident with the radial direction of the piston.
さらに、ピストン21は溝22、23を互いに逆向きに傾斜
させており、溝22、23のそれぞれの巻方向を互いに逆方
向に設定されている。また、ピストン21は、溝22、23の
それぞれのピッチを、軸心方向中間部から両端部へいく
ほど徐々に小さくなるよう設定されている。そして、ピ
ストン21は溝22、23を、それぞれの位相を互いに約180
゜ずらした状態で形成されている。そして、ピストン21
は両溝22、23の始点を、溝22、23を互いに交差させるこ
となく、近接させている。Further, the piston 21 has the grooves 22 and 23 inclined in opposite directions, and the winding directions of the grooves 22 and 23 are set to be opposite to each other. Further, the piston 21 is set so that the pitch of each of the grooves 22 and 23 is gradually reduced from the middle portion in the axial direction to both ends. Then, the piston 21 makes the grooves 22 and 23
It is formed in a shifted state. And piston 21
Makes the starting points of the grooves 22, 23 close to each other without intersecting the grooves 22, 23 with each other.
そして、ピストン21は溝22、23に、適度な可撓性を有
する螺旋状のブレード（図示しない）を出入自在にねじ
込まれている。そして、上記シリンダの内周面とその外
周面との間に、上記ブレードによって仕切られピストン
21の軸心方向に沿って並ぶとともに、ピストン21の軸心
方向中間部から端部へいくほどその容積が小さくなる三
日月状の複数の作動室を形成している。The piston 21 has a spiral blade (not shown) having appropriate flexibility screwed into and out of the grooves 22 and 23. The piston is partitioned by the blade between the inner peripheral surface and the outer peripheral surface of the cylinder.
A plurality of crescent-shaped working chambers are arranged along the axial direction of the piston 21, and the volume of the piston 21 decreases from the middle to the end in the axial direction of the piston 21.
ここで、第１図中に24で示すのは、シリンダ内に冷媒
ガスを供給する吸込み通路である。Here, what is indicated by 24 in FIG. 1 is a suction passage for supplying refrigerant gas into the cylinder.
すなわち、モータ等の駆動手段により圧縮機構部が駆
動されると、ピストン21と上記シリンダとが相対的に回
転し、シリンダ内の軸方向中間部の作動室に冷媒ガスが
吸い込まれる。そして、この冷媒ガスは、ピストン21と
シリンダとの相対的回転にともない２方向に分かれて、
ピストン21（および、シリンダ）の軸心方向両端部側の
作動室に順次移送され圧縮される。そして、圧縮された
冷媒ガスは、ピストン21（および、シリンダ）の軸心方
向両端部から、ピストン21が180゜回転する毎に交互に
吐出され、冷凍サイクル中に戻される。That is, when the compression mechanism is driven by a driving unit such as a motor, the piston 21 and the cylinder rotate relatively, and the refrigerant gas is sucked into the working chamber at the axially intermediate portion in the cylinder. This refrigerant gas is divided into two directions with the relative rotation of the piston 21 and the cylinder,
The pistons 21 (and cylinders) are sequentially transferred to the working chambers at both ends in the axial direction and are compressed. Then, the compressed refrigerant gas is alternately discharged from both axial ends of the piston 21 (and the cylinder) every time the piston 21 rotates 180 °, and returned to the refrigeration cycle.
さらに、上述の圧縮機の各移送・圧縮方向のそれぞれ
の負荷トルクや吐出脈動は、第２図中に一点鎖線Ｃおよ
び点線Ｄで示すようにピストン21の回転角に伴ってsin
カーブを描きながら変動する。しかし、ピストン21の螺
旋状の溝22、23の位相が互いに180゜ずれていることか
ら、各方向の負荷トルクや吐出脈動は重なり合い、圧縮
機全体の負荷トルクや吐出脈動は、実線Ｅで示すように
変動の小さな曲線を描く。Further, the load torque and the discharge pulsation in each transfer / compression direction of the compressor described above are caused by the sin angle with the rotation angle of the piston 21 as shown by the dashed line C and the dotted line D in FIG.
It fluctuates while drawing a curve. However, since the phases of the spiral grooves 22 and 23 of the piston 21 are shifted from each other by 180 °, the load torque and the discharge pulsation in each direction overlap, and the load torque and the discharge pulsation of the entire compressor are shown by a solid line E. Draw a curve with small fluctuations.
したがって、上述の圧縮機は、負荷トルクや吐出脈動
等の変動を大幅に低減することが可能である。Therefore, the above-described compressor can greatly reduce fluctuations in load torque, discharge pulsation, and the like.
また、本実施例では溝22、23の始点を、溝22、23を互
いに交差させることなく、近接させているので、第１図
中に２点鎖線Ｆで示すように、ピストン21の軸心方向の
寸法を従来のもののピストンよりも長さＧの分だけ小さ
く設定することが出来る。In this embodiment, since the starting points of the grooves 22 and 23 are close to each other without intersecting the grooves 22 and 23, as shown by a two-dot chain line F in FIG. The dimension in the direction can be set smaller than the conventional piston by the length G.
さらに、溝22、23の形状を対称形状とし、溝22、23の
傾きを軸心方向に対して略等しく設定すれば、負荷トル
クおよび吐出脈動の変動をより小さくすることができ
る。Further, if the shapes of the grooves 22 and 23 are symmetrical and the inclinations of the grooves 22 and 23 are set to be substantially equal to the axial direction, fluctuations in load torque and discharge pulsation can be further reduced.
なお、本発明の流体機械は、冷凍サイクルを構成する
圧縮機に限らず、他の用途の流体機械にも適用すること
ができる。In addition, the fluid machine of the present invention is not limited to a compressor constituting a refrigeration cycle, and can be applied to a fluid machine for other uses.
［発明の効果］ 以上説明したように本発明は、吸込側と吐出側とを有
するシリンダと、このシリンダ内にシリンダの軸方向に
沿うとともに偏心して配置され、その一部がシリンダの
内周面に接触した状態でシリンダと相対的に回転可能な
円柱状の回転体と、この回転体の外周に設けられ、それ
ぞれが互いに異なる向きに形成され、回転体の中間部か
ら両端部に亘って形成されるとともに、互いに位相を約
180度ずらした２つの螺旋状の溝と、両溝に回転体の略
径方向に出入自在にそれぞれ嵌め込まれるとともに、シ
リンダの内周面に密着する外周面を有し、シリンダの内
周面と回転体の外周面との間の空間を複数の作動室に区
画する２つの螺旋状のブレードと、シリンダと回転体と
を相対的に回転させ、シリンダの吸込側から作動室に流
入した流体をシリンダ吐出側の作動室へ順次移送する駆
動手段とを備えたものである。[Effects of the Invention] As described above, the present invention provides a cylinder having a suction side and a discharge side, and is disposed eccentrically in the cylinder along the axial direction of the cylinder, and a part thereof is formed on the inner peripheral surface of the cylinder. And a cylindrical rotating body rotatable relative to the cylinder in a state of being in contact with the cylinder, and provided on the outer periphery of the rotating body, each formed in a different direction from each other, and formed from an intermediate portion to both end portions of the rotating body. And at the same time phase with each other
It has two spiral grooves shifted by 180 degrees and an outer peripheral surface that is fitted into both grooves so as to be able to enter and exit substantially in the radial direction of the rotating body, and has an outer peripheral surface that is in close contact with the inner peripheral surface of the cylinder. Two helical blades that partition the space between the outer peripheral surface of the rotating body into a plurality of working chambers, the cylinder and the rotating body are relatively rotated, and the fluid flowing into the working chamber from the suction side of the cylinder is removed. Drive means for sequentially transferring the working chamber to the working chamber on the cylinder discharge side.
したがって本発明は、負荷トルクや吐出脈動等の変動
を大幅に低減できるという効果がある。また、回転体を
短く形成できるという効果がある。Therefore, the present invention has an effect that fluctuations such as load torque and discharge pulsation can be significantly reduced. Further, there is an effect that the rotating body can be formed short.
第１図および第２図は本発明の一実施例の要部を示すも
ので、第１図はピストンを概略的に示すは側面図、第２
図はピストンの回転角と負荷トルクおよび吐出脈動との
関係を示すグラフ、第３図〜第６図は従来例を示すもの
で、第３図は流体を１方向に移送・圧縮するタイプの流
体圧縮機の全体を示す側断面図、第４図は同じく流体を
１方向に移送・圧縮するタイプの流体圧縮機のピストン
を概略的に示す側面図、第５図は流体を２方向に移送・
圧縮するタイプの流体圧縮機の同じくピストンを概略的
に示す側面図、第６図は同じく流体を２方向に移送・圧
縮するタイプの流体圧縮機のピストンの回転角と負荷ト
ルクおよび吐出脈動との関係を示すグラフである。 ５……モータ（駆動手段）、７……シリンダ、10……ブ
レード、21……ピストン（回転体）、22、23……螺旋状
の溝。1 and 2 show the essential parts of an embodiment of the present invention. FIG. 1 is a side view schematically showing a piston, and FIG.
FIG. 3 is a graph showing the relationship between the rotation angle of the piston and the load torque and the discharge pulsation. FIGS. 3 to 6 show a conventional example, and FIG. 3 shows a fluid of the type for transferring and compressing the fluid in one direction. FIG. 4 is a side sectional view schematically showing a piston of a fluid compressor of the same type for transferring and compressing a fluid in one direction, and FIG. 5 is a side view showing the entirety of the compressor.
FIG. 6 is a side view schematically showing a piston of a compression type fluid compressor, and FIG. 6 is a graph showing the relationship between the rotation angle of the piston, load torque, and discharge pulsation of the same type of fluid compressor which transfers and compresses fluid in two directions. It is a graph which shows a relationship. 5 ... motor (drive means), 7 ... cylinder, 10 ... blade, 21 ... piston (rotating body), 22, 23 ... spiral groove.
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.6，ＤＢ名) F04C 2/30 - 2/352 F04C 18/30 - 18/352──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. 6 , DB name) F04C 2/30-2/352 F04C 18/30-18/352
Claims (2)
のシリンダ内にシリンダの軸方向に沿うとともに偏心し
て配置され、その一部が上記シリンダの内周面に接触し
た状態で上記シリンダと相対的に回転可能な円柱状の回
転体と、この回転体の外周に設けられ、それぞれが互い
に異なる向きに形成され上記回転体の中間部から両端部
に亘って延びるとともに、互いに位相を約180度ずらし
た２つの螺旋状の溝と、上記両溝に、回転体の略径方向
に出入自在にそれぞれ嵌め込まれるとともに、上記シリ
ンダの内周面に密着する外周面を有し、上記シリンダの
内周面と上記回転体の外周面との間の空間を複数の作動
室に区画する２つの螺旋状のブレードと、上記シリンダ
と上記回転体とを相対的に回転させ、シリンダの吸込側
から上記作動室に流入した流体をシリンダ吐出側の作動
室へ順次移送する駆動手段とを具備した流体機械。1. A cylinder having a suction side and a discharge side, and disposed eccentrically in the cylinder along the axial direction of the cylinder, a part of which is in contact with the inner peripheral surface of the cylinder. A relatively rotatable cylindrical rotating body, provided on the outer periphery of the rotating body, each formed in a different direction from each other, extending from an intermediate portion to both ends of the rotating body, and having a phase of about 180 The two spiral grooves which are staggered and the outer peripheral surface which is fitted in the both grooves so as to be able to freely enter and exit substantially in the radial direction of the rotating body and which is in close contact with the inner peripheral surface of the cylinder. Two helical blades that partition the space between the peripheral surface and the outer peripheral surface of the rotating body into a plurality of working chambers, the cylinder and the rotating body are relatively rotated, and the cylinder is rotated from the suction side of the cylinder. Flow into the working chamber Fluid machine where the fluid; and a driving means for sequentially transferring the working chamber of the cylinder discharge side.
点を軸方向に交差させることなく近接させた請求項１に
記載の流体機械。2. The fluid machine according to claim 1, wherein the starting points of the two grooves formed in the intermediate portion of the rotating body are close to each other without intersecting in the axial direction.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1166887A JP2798981B2 (en) | 1989-06-30 | 1989-06-30 | Fluid machinery |
| US07/535,563 US5090874A (en) | 1989-06-30 | 1990-06-11 | Fluid compressor |
| EP90111118A EP0405224B1 (en) | 1989-06-30 | 1990-06-12 | Fluid compressor |
| DE90111118T DE69002801T2 (en) | 1989-06-30 | 1990-06-12 | Fluid compressor. |
| KR1019900009742A KR940003309B1 (en) | 1989-06-30 | 1990-06-27 | Fluid compressor |
| CN90103374A CN1015304B (en) | 1989-06-30 | 1990-06-30 | Fluid compression engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1166887A JP2798981B2 (en) | 1989-06-30 | 1989-06-30 | Fluid machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0333487A JPH0333487A (en) | 1991-02-13 |
| JP2798981B2 true JP2798981B2 (en) | 1998-09-17 |
Family
ID=15839464
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1166887A Expired - Fee Related JP2798981B2 (en) | 1989-06-30 | 1989-06-30 | Fluid machinery |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2798981B2 (en) |
| KR (1) | KR940003309B1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104514713A (en) * | 2013-09-26 | 2015-04-15 | 孔水友 | Coaxial-spiral-fan forward- and reverse-convoluting compressor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004278439A (en) | 2003-03-17 | 2004-10-07 | Toshiba Kyaria Kk | Fluid machine |
-
1989
- 1989-06-30 JP JP1166887A patent/JP2798981B2/en not_active Expired - Fee Related
-
1990
- 1990-06-27 KR KR1019900009742A patent/KR940003309B1/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104514713A (en) * | 2013-09-26 | 2015-04-15 | 孔水友 | Coaxial-spiral-fan forward- and reverse-convoluting compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| KR910001255A (en) | 1991-01-30 |
| JPH0333487A (en) | 1991-02-13 |
| KR940003309B1 (en) | 1994-04-20 |
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