JPH0396688A - Fluid compressor - Google Patents
Fluid compressorInfo
- Publication number
- JPH0396688A JPH0396688A JP1233411A JP23341189A JPH0396688A JP H0396688 A JPH0396688 A JP H0396688A JP 1233411 A JP1233411 A JP 1233411A JP 23341189 A JP23341189 A JP 23341189A JP H0396688 A JPH0396688 A JP H0396688A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- compression mechanism
- motor
- bearing
- center
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 17
- 230000006835 compression Effects 0.000 claims abstract description 24
- 238000007906 compression Methods 0.000 claims abstract description 24
- 230000005484 gravity Effects 0.000 claims abstract description 18
- 230000007423 decrease Effects 0.000 claims description 5
- 238000005057 refrigeration Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 239000007787 solid Substances 0.000 description 1
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
- F04C18/10—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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
［発明の目的コ
（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
体圧縮機に関する。DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention (Industrial Application Field) The present invention relates to a fluid compressor that compresses refrigerant gas in, for example, a refrigeration cycle.
（従来の技術）
例えば、本出願人による特開昭６４−
３６９９０号公報に開示されているような流体圧縮機（
以下、圧縮機と称する）が知られている。(Prior Art) For example, a fluid compressor (
(hereinafter referred to as a compressor) is known.
すなわち、第３図に示すように、このタイプの圧縮機１
は密閉ケース２の中に、密閉ケース２に固定された固定
子３とこの固定子３の内側に同軸的に配置された回転子
４とからなるモータ５を有している。そして、圧縮機１
は回転子４の内側に同軸的に配置されたシリンダ６を回
転子４と同芯的に回転させるようになっている。That is, as shown in FIG. 3, this type of compressor 1
The motor 5 includes a stator 3 fixed to the sealed case 2 and a rotor 4 disposed coaxially inside the stator 3, in a sealed case 2. And compressor 1
The cylinder 6 is arranged coaxially inside the rotor 4 and rotates concentrically with the rotor 4.
さらに、圧縮機１はシリンダ６内に、シリンダ６に対し
て偏心したピストン７を有している。そして、圧縮機１
は、ピストン７の外周に螺旋状の溝を形威されており、
この螺旋状の溝に適度な可撓性を有する螺旋状のブレー
ド８を嵌込んでいる。Furthermore, the compressor 1 has a piston 7 in the cylinder 6 that is eccentric with respect to the cylinder 6 . And compressor 1
A spiral groove is formed on the outer circumference of the piston 7,
A spiral blade 8 having appropriate flexibility is fitted into this spiral groove.
そして、この圧縮機１はシリンダ６の内部に、シリンダ
６の吐出側に位置するものほど徐々に容積が小さくなる
よう設定された複数の作動室を形成しており、シリンダ
６の吸込側の端部に位置する吸込室に例えば冷凍サイク
ル中の作動流体を吸込む。そして、圧縮機１は、モータ
５によりシリンダ６を回転させ、上記作動流体をシリン
ダの吐出側へ移送しながら徐々に圧縮し、圧縮されて高
圧になった作動流体を一旦密閉ケース４内に吐出して冷
凍サイクル中に戻す。The compressor 1 has a plurality of working chambers inside the cylinder 6, each having a volume that gradually decreases as it is located closer to the discharge side of the cylinder 6. For example, the working fluid in the refrigeration cycle is sucked into the suction chamber located in the section. Then, the compressor 1 rotates the cylinder 6 by the motor 5, gradually compresses the working fluid while transferring it to the discharge side of the cylinder, and once discharges the compressed and high-pressure working fluid into the sealed case 4. and return it to the refrigeration cycle.
また、圧縮＃１１は、シリンダ６の吸込側の端部に、密
閉ケース２の内壁面に固定された主軸受９を気密的に且
つ同軸的に嵌合している。さらに、圧縮機１は、吐出側
の端部に副軸受１０を同じく気密的に且つ同軸的に嵌合
している。そして、圧縮機１はシリンダ６およびピスト
ン７等を片側固定支持しており、副軸受１０を密閉ケー
ス２内に取付けられた仮ばね等の弾性支持部材１１に押
付けている。そして、圧縮機１は、弾性支持部材１１に
よって副軸受１０を回転，しないように規制している。Further, in the compression #11, a main bearing 9 fixed to the inner wall surface of the sealed case 2 is fitted to the suction side end of the cylinder 6 airtightly and coaxially. Furthermore, the compressor 1 has a sub-bearing 10 fitted to the discharge end thereof in an air-tight manner and coaxially. The compressor 1 has a cylinder 6, a piston 7, etc. fixedly supported on one side, and a sub-bearing 10 is pressed against an elastic support member 11, such as a temporary spring, installed in the sealed case 2. The compressor 1 is restricted by the elastic support member 11 so that the secondary bearing 10 does not rotate.
（発明が解決しようとする課題）
ところで、上述のような圧縮機１は、モータ５をシリン
ダ６の軸方向中間部に配置しており、さらに、モータ５
の重心部Ａをシリンダ６の軸方向中間部に位置させてい
た。そして、圧縮機１は、モータ５の重心部Ａを主軸受
９の先端側端而１２よりもシリンダ６の軸方向中間部寄
りの部位に位置させていた。(Problem to be Solved by the Invention) By the way, the compressor 1 as described above has the motor 5 disposed in the axially intermediate portion of the cylinder 6, and furthermore, the motor 5
The center of gravity A of the cylinder 6 was located at an axially intermediate portion of the cylinder 6. In the compressor 1, the center of gravity A of the motor 5 is located closer to the axially intermediate portion of the cylinder 6 than the tip end 12 of the main bearing 9.
すなわち、第３図中に示すように、主軸受９の基端側端
面１３上の上記モータ５（および、シリンダ６等）の軸
芯Ｂが通過する部位を基準位置Ｏとし、モータの重心部
Ａの位置をＬＭとし、さらに、生軸受９の先端側端面１
２上の上記モータ５（および、シリンダ６等）の軸芯Ｂ
が通過する部位をＬＢとすると、主軸受９の基端側端面
１３からとモータの重心部Ａまでの距ｉｆｆｌｔ Ｏ
Ｌ Ｍと、主軸受９の基端側端面１３から主軸受９の先
端側端面１２までの距離σＬＢとの関係は、すＬ，＞▼
Ｔ）となる。That is, as shown in FIG. 3, the part on the proximal end surface 13 of the main bearing 9 through which the axis B of the motor 5 (and cylinder 6, etc.) passes is defined as the reference position O, and the center of gravity of the motor The position A is LM, and the tip side end surface 1 of the raw bearing 9 is
Axis center B of the motor 5 (and cylinder 6, etc.) on 2
Let LB be the part through which
The relationship between L M and the distance σLB from the proximal end surface 13 of the main bearing 9 to the distal end surface 12 of the main bearing 9 is L,>▼
T).
そして、上述のようなタイプの圧縮機１の振動や騒音は
、回転運動の特性、および、シリンダ６やピストン７等
の支持方式等に起因し大きく影響を受ける。そして、従
来は、上述のようにＯＬ．＞ＯＬ，だったことから、例
えば調芯が不十分で固定子３と同転子４、或いは、同転
子４とシリンダ６との互いの軸芯の間にずれがあると、
ふれ回りが増長され、圧縮機１の運転振動や騒音が増大
するとともに、軸受摺動部の摩擦損失が増加してしまう
という不具合があった。The vibrations and noise of the compressor 1 of the type described above are greatly affected by the characteristics of the rotational motion, the support system of the cylinder 6, the piston 7, etc. Conventionally, as mentioned above, OL. >OL, for example, if the alignment is insufficient and there is a misalignment between the axes of the stator 3 and the rotor 4, or the rotor 4 and the cylinder 6,
There were problems in that the whirling increased, the operating vibration and noise of the compressor 1 increased, and the friction loss of the bearing sliding portion increased.
本発明の目的とするところは、振動や騙音を低減でき、
軸受摺動部の摩擦損失が少なく、高性能な流体圧縮機を
提供することにある。The purpose of the present invention is to reduce vibration and deceptive noise,
An object of the present invention is to provide a high-performance fluid compressor with low friction loss in bearing sliding parts.
［発明の構成］
（課題を解決するための手段及び作用）上記目的を達成
するために本発明は、螺旋状のブレードを巻装した回転
体を吸込側と吐出側とを有する円筒状のシリンダ内に偏
心配置しシリンダの吸込側から吐出側へ徐々にその容積
を小とする複数の作動室をシリンダ内に並設するととも
に、シリンダの少なくとも軸方向一端側にシリンダおよ
び回転体を支持する軸受部材を嵌合してなる圧縮機構部
と、シリンダと回転体とを相対的に回転させて作動室に
導入された作動流体をシリンダの吸込側から吐出側へ移
送しながら圧縮するとともに、その重心部を軸受部材内
の略軸芯上に位置させた駆動部とを具備したことにある
。[Structure of the Invention] (Means and Effects for Solving the Problems) In order to achieve the above object, the present invention provides a cylindrical cylinder having a suction side and a discharge side, in which a rotating body around which a spiral blade is wound is used. A bearing that supports a cylinder and a rotating body on at least one axial end of the cylinder, in which a plurality of working chambers are arranged eccentrically within the cylinder and whose volume gradually decreases from the suction side to the discharge side of the cylinder. A compression mechanism formed by fitting members, a cylinder, and a rotating body are rotated relative to each other, and the working fluid introduced into the working chamber is compressed while being transferred from the suction side to the discharge side of the cylinder, and its center of gravity is The driving part is located approximately on the axis within the bearing member.
こうすることによって本発明は、振動や騒音を低減でき
、輔受摺動部の摩擦損失を小とするとともに、性能を向
上できるようにしたことにある。By doing so, the present invention is able to reduce vibration and noise, reduce friction loss in the sliding portion of the support, and improve performance.
（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。(Example) Hereinafter, an example of the present invention will be described based on FIGS. 1 and 2.
第１図および第２図は本発明の一実施例を示すものであ
る。そして、第１図は冷凍サイクルに使用する冷媒ガス
用の流体圧縮機２１（以下、圧縮機と称する）を示して
いる。この圧縮機２１は密閉ケース２２と、この密閉ケ
ース２２の中に配設された駆動部としてのモータ２３、
および、このモータ２３によって回転駆動される圧縮機
構部２４とを備えている。1 and 2 show one embodiment of the present invention. FIG. 1 shows a fluid compressor 21 (hereinafter referred to as a compressor) for refrigerant gas used in a refrigeration cycle. This compressor 21 includes a closed case 22, a motor 23 as a drive section disposed inside the closed case 22,
and a compression mechanism section 24 rotationally driven by the motor 23.
上記モータ２３は、密閉ケース２２の内壁面に固定され
た環状の固定子２５と、この固定子２５の内側に配置さ
れた同じく環状の回転子２６とを有するものである。そ
して、モータ２３は、第２図中に示すようにその重心部
Ａの位置を、回転子２６の軸芯Ｂと回転子２６の径方向
に延びる中心線Ｃとの交点に位置させており、さらに、
その重心部Ａと回転子２６の重心部とを略同じ部位に位
置させている。そして、モータ２３は、密閉ケース２２
の軸方向一端側に偏倚した部位に配置されている。The motor 23 has an annular stator 25 fixed to the inner wall surface of the sealed case 22 and a similarly annular rotor 26 disposed inside the stator 25. As shown in FIG. 2, the motor 23 has its center of gravity A located at the intersection of the axis B of the rotor 26 and the center line C extending in the radial direction of the rotor 26. moreover,
The center of gravity A and the center of gravity of the rotor 26 are located at approximately the same location. The motor 23 is connected to the sealed case 22.
It is disposed at a position offset toward one end in the axial direction.
また、第１図に示すように上記圧縮機構部２４は、円筒
状に成形され吸込側と吐出側とを有する円筒状のシリン
ダ２７を有しており、このシリンダ２７の吸込側の端部
の外周面を回転子２６の内周面に回転子２６と同軸的に
固定している。さらに、圧縮機構部２４はシリンダ２７
の吸込側の端部に、密閉ケース２２の内壁面に固定され
密閉ケース２２の内部に突出する軸受部材としての主軸
受２８を同軸的に且つ摺動自在に嵌合している。Further, as shown in FIG. 1, the compression mechanism section 24 has a cylindrical cylinder 27 formed into a cylindrical shape and having a suction side and a discharge side. The outer peripheral surface is fixed to the inner peripheral surface of the rotor 26 coaxially with the rotor 26. Furthermore, the compression mechanism section 24 has a cylinder 27
A main bearing 28 as a bearing member fixed to the inner wall surface of the sealed case 22 and protruding into the sealed case 22 is coaxially and slidably fitted to the suction side end of the main bearing 28 .
さらに、圧縮機構部２４は、シリンダ２７の吸込側の端
部を主軸受２８によって気密的に閉塞されている。そし
て、圧縮機構部２４は、主軸受２８の先端側端面２９を
シリンダ２７の中に位置させており、この先端側端面２
９を回転子２６の内側に到達させている。そして、モー
タ２３の重心部Ａを主軸受２８内、即ち主軸受２８の先
端側端而２９と基端側端面３０この間における軸芯Ｂ上
の部位に位置させている。Furthermore, the compression mechanism section 24 has the suction side end of the cylinder 27 hermetically closed by a main bearing 28 . The compression mechanism section 24 has a distal end surface 29 of the main bearing 28 located within the cylinder 27, and the distal end surface 29 of the main bearing 28 is located within the cylinder 27.
9 reaches the inside of the rotor 26. The center of gravity A of the motor 23 is located within the main bearing 28, that is, on the axis B between the distal end 29 and the proximal end surface 30 of the main bearing 28.
また、圧縮機構部２４はシリンダ２７の他端側、即ち吐
出側の端部に副軸受３１を同軸的に且つ摺動自在に嵌合
している。そして、圧縮機構部２４はシリンダ２７の吐
出側を、密閉ケース２２の内壁に取付けられた板ばね等
の弾性支持部材３２に、副軸受３１を介して押付けてい
る。そして、圧縮機構部２４は弾性支持部材３２により
、副軸受３１を回転しないよう規制されている。つまり
、圧縮機構部２４は、シリンダ３１を片側固定支持され
ている。Further, the compression mechanism section 24 has a sub-bearing 31 coaxially and slidably fitted to the other end of the cylinder 27, that is, the end on the discharge side. The compression mechanism section 24 presses the discharge side of the cylinder 27 against an elastic support member 32 such as a leaf spring attached to the inner wall of the sealed case 22 via a sub-bearing 31. The compression mechanism section 24 is restricted by the elastic support member 32 so that the sub-bearing 31 does not rotate. In other words, the compression mechanism section 24 is fixedly supported on one side of the cylinder 31.
また、圧縮機構部２４はシリンダ２７の中に、螺旋状の
ブレード３３を巻装した円柱状の、回転体としてのピス
トン３４を配置している。そして、圧縮機構部２４はピ
ストン３４をシリンダ２７（および、回転子２６）に対
して偏心させており、ピストン３５の軸方向両端部に形
成された吸込側ジャーナル部３５および吐出側ジャーナ
ル部３６を、主軸受２８と副軸受３１とにそれぞれ差込
んでいる。Further, the compression mechanism section 24 has a cylindrical piston 34 as a rotary body around which a spiral blade 33 is wound, arranged in the cylinder 27 . The compression mechanism section 24 has a piston 34 eccentric to the cylinder 27 (and rotor 26), and a suction side journal section 35 and a discharge side journal section 36 formed at both axial ends of the piston 35. , are inserted into the main bearing 28 and the sub-bearing 31, respectively.
さらに、圧縮機構部２４は、ブレード３３によってシリ
ンダ２７とピストン３５との間に、シリンダ２７の吸込
側から吐出側に亘って並んだ複数の作動室３７・・・を
形成している。そして、圧縮機構部２４は作動室３７・
・・の容積を、シリンダ２７の吸込側から吐出側へいく
ほど徐々に小さくなるよう設定されている。Further, the compression mechanism section 24 forms a plurality of working chambers 37 arranged between the cylinder 27 and the piston 35 from the suction side to the discharge side of the cylinder 27 by the blade 33. The compression mechanism section 24 has a working chamber 37.
... is set to gradually decrease from the suction side to the discharge side of the cylinder 27.
そして、圧縮機構部２４は、モータ２５によりシリンダ
２７を回転駆動され、ブレード３３をピストン３４に形
成された螺旋状の溝に対して出入りさせながら、ピスト
ン３４をシリンダ２７と同期的に回転させるようになっ
ている。そして、シリンダ２７の吸込側から作動室３７
に導入した作動流体を、シリンダ２６の吐出側へ順次移
送しながら圧縮し、高温になった作動流体を一旦密閉ケ
ース２２内に吐出したのち、冷凍サイクル中に戻す。The compression mechanism section 24 rotates the cylinder 27 by the motor 25, and rotates the piston 34 synchronously with the cylinder 27 while moving the blade 33 in and out of the spiral groove formed in the piston 34. It has become. Then, from the suction side of the cylinder 27, the working chamber 37
The working fluid introduced into the cylinder 26 is compressed while being sequentially transferred to the discharge side of the cylinder 26, and the high-temperature working fluid is once discharged into the sealed case 22 and then returned to the refrigeration cycle.
ここで、第１図中のＤは、ピストン３４の軸芯を示して
いる。Here, D in FIG. 1 indicates the axis of the piston 34.
つまり、上述の圧縮機２１では、第２図中に示すように
、主軸受２８の基端側端面３０上の上記主軸受２８の軸
心Ｂが通過する位置を基準位置Ｏとし、モータ２３の重
心部Ａの位置をＬＭとし、さらに、主軸受２８の先端側
端面２９上の上記主軸受２８の軸心Ｃが通過する位置を
Ｌ．こすると、主軸受２８の基端側端面３０からモータ
の重心部Ａまでの距離『Ｌと、主軸受９の基端側端面１
３から主軸受９の先端側端面１２までの距離ＯＬＢとの
関係は、▼Ｔ．＜ ＴＬとなる。That is, in the compressor 21 described above, as shown in FIG. The position of the center of gravity A is LM, and the position on the tip end surface 29 of the main bearing 28 through which the axis C of the main bearing 28 passes is L. When rubbed, the distance "L" from the proximal end surface 30 of the main bearing 28 to the center of gravity A of the motor and the proximal end surface 1 of the main bearing 9
The relationship between the distance OLB from 3 to the front end face 12 of the main bearing 9 is ▼T. < becomes TL.
そして、圧縮機２１はモータ２３の重心部Ａを、主軸受
２８の、シリンダ２７を支持した部位に近づけており、
このことによって、回転子２６、シリンダ２７、および
主軸受２８等の径方向に働くモーメントを大幅に低減し
ている。The compressor 21 has the center of gravity A of the motor 23 close to the part of the main bearing 28 that supports the cylinder 27.
This significantly reduces the moment acting on the rotor 26, cylinder 27, main bearing 28, etc. in the radial direction.
したがって、上述の圧縮機２１は、回転子２６の固有振
動数、回転子２６とシリンダ２７や主軸受２８等との軸
芯のずれ、および、モータ２３の固定子２５と回転子２
６との偏心等を原因として発生する“ふれ回り“を低減
することができる。Therefore, the above-mentioned compressor 21 is limited by the natural frequency of the rotor 26, the misalignment between the rotor 26 and the cylinder 27, the main bearing 28, etc., and the stator 25 and rotor 2 of the motor 23.
"Wandering" that occurs due to eccentricity with respect to 6 can be reduced.
そして、圧縮機２１の運転振動や、振動に起因する騒音
等を低減でき、さらに、ふれ回りによる軸受摺動部の摩
擦損失を低減することができる。そして、軸受摺動部の
摩擦損失を低減できることから、圧縮機１１への入力を
低減することが可能になり、性能および信頼性を向上す
ることができる。The operating vibration of the compressor 21, the noise caused by the vibration, and the like can be reduced, and furthermore, the friction loss of the bearing sliding portion due to whirling can be reduced. Since the friction loss of the bearing sliding portion can be reduced, the input to the compressor 11 can be reduced, and performance and reliability can be improved.
なお、本実施例では、モータ２３をシリンダ２７の吸込
側の端部に配置してモータ２３の重心部Ａが主軸受２８
内に位置するようにしたが、本発明はこれに限定される
ものではなく、例えば、モータ２３をシリンダ２７の軸
方向中間部に配置するとともに、主軸受２８の軸方向の
寸法を延長して、モータ２３の重心部Ａが主軸受２８内
に位置するようにしてもよい。In this embodiment, the motor 23 is arranged at the suction side end of the cylinder 27 so that the center of gravity A of the motor 23 is located at the main bearing 28.
However, the present invention is not limited to this. For example, the motor 23 may be arranged in the axially intermediate portion of the cylinder 27, and the axial dimension of the main bearing 28 may be extended. , the center of gravity A of the motor 23 may be located within the main bearing 28.
また、本発明の圧縮機は冷凍サイクルに用いられるもの
だけでなく、他の用途の圧縮機にも適用することが可能
である。Further, the compressor of the present invention can be applied not only to those used in refrigeration cycles but also to compressors for other uses.
［発明の効果コ
以上説明したように本発明は、螺旋状のブレードを巻装
した回転体を吸込側と吐出側とを有する固筒状のシリン
ダ内に偏心配置しシリンダの吸込側から吐出側へ徐々に
その容積を小とする複数の作動室をシリンダ内に並設す
るとともに、シリンダの少なくとも軸方向一端側にシリ
ンダおよび回転体を支持する軸受部材を嵌合してなる圧
縮機構部と、シリンダと回転体とを相対的に回転させて
作動室に導入された作動流体をシリンダの吸込側から吐
出側へ移送しながら圧縮するとともに、その重心部を軸
受部材内の略軸芯上に位置させた駆動部とを備えたもの
である。[Effects of the Invention] As explained above, the present invention provides a rotating body with a spiral blade wound thereon, which is arranged eccentrically in a solid cylinder having a suction side and a discharge side. a compression mechanism section in which a plurality of working chambers whose volume gradually decreases are arranged in parallel in a cylinder, and a bearing member that supports the cylinder and the rotating body is fitted to at least one axial end side of the cylinder; The cylinder and rotating body are rotated relative to each other to compress the working fluid introduced into the working chamber while transferring it from the suction side to the discharge side of the cylinder, and the center of gravity is positioned approximately on the axis within the bearing member. The drive unit is equipped with a drive unit.
したがって本発明は、振動や騒音を低減でき、軸受摺動
部の摩擦損失を小とするとともに、性能を向上できると
いう効果がある。Therefore, the present invention has the effect of reducing vibration and noise, reducing friction loss in the sliding portion of the bearing, and improving performance.
第１図および第２図は本発明の一実施例を示すもので、
第１図は側断面図、第２図は要部を拡大しモータと主軸
受との位置関係を示す説明図、第３図は従来例を示す側
断面図である。
２１・・・流体圧縮機、２３・・・モータ（駆動部）、
２４・・・圧縮機構部、２７・・・シリンダ、２８・・
・主軸受（軸受部材）、３３・・・ブレード、３４・・
・ピストン（回転体）、３７・・・作動室、Ａ・・・モ
ータの重心部、Ｂ・・・軸受部材の軸芯。1 and 2 show an embodiment of the present invention,
FIG. 1 is a side sectional view, FIG. 2 is an enlarged explanatory view showing the positional relationship between the motor and the main bearing, and FIG. 3 is a side sectional view showing a conventional example. 21...Fluid compressor, 23...Motor (drive unit),
24... Compression mechanism section, 27... Cylinder, 28...
・Main bearing (bearing member), 33...Blade, 34...
- Piston (rotating body), 37... working chamber, A... center of gravity of motor, B... axial center of bearing member.
Claims (1)
を有する円筒状のシリンダ内に偏心配置し上記シリンダ
の吸込側から吐出側へ徐々にその容積を小とする複数の
作動室を上記シリンダ内に並設するとともに、上記シリ
ンダの少なくとも軸方向一端側に上記シリンダおよび上
記回転体を支持する軸受部材を嵌合してなる圧縮機構部
と、上記シリンダと上記回転体とを相対的に回転させて
上記作動室に導入された作動流体を上記シリンダの吸込
側から吐出側へ移送しながら圧縮するとともに、その重
心部を上記軸受部材内の略軸芯上に位置させた駆動部と
を具備した流体圧縮機。A rotating body wound with a spiral blade is eccentrically arranged in a cylindrical cylinder having a suction side and a discharge side, and a plurality of working chambers whose volume gradually decreases from the suction side to the discharge side of the cylinder are formed. A compression mechanism part is arranged in parallel in the cylinder and is fitted with a bearing member that supports the cylinder and the rotating body on at least one axial end side of the cylinder, and the cylinder and the rotating body are relatively connected to each other. a drive unit that compresses the working fluid introduced into the working chamber by rotating the cylinder from the suction side to the discharge side of the cylinder, and has its center of gravity located approximately on the axis within the bearing member; A fluid compressor equipped with
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1233411A JPH0396688A (en) | 1989-09-08 | 1989-09-08 | Fluid compressor |
| EP90111475A EP0416224B1 (en) | 1989-09-08 | 1990-06-18 | Fluid compressor |
| DE90111475T DE69002809T2 (en) | 1989-09-08 | 1990-06-18 | Liquid compressor. |
| US07/549,129 US5090875A (en) | 1989-09-08 | 1990-07-06 | Fluid compressor |
| KR1019900014228A KR940007759B1 (en) | 1989-09-08 | 1990-09-07 | Fluid compressor |
| CN90108181.7A CN1016260B (en) | 1989-09-08 | 1990-09-08 | Fluid compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1233411A JPH0396688A (en) | 1989-09-08 | 1989-09-08 | Fluid compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0396688A true JPH0396688A (en) | 1991-04-22 |
Family
ID=16954644
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1233411A Pending JPH0396688A (en) | 1989-09-08 | 1989-09-08 | Fluid compressor |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH0396688A (en) |
| KR (1) | KR940007759B1 (en) |
-
1989
- 1989-09-08 JP JP1233411A patent/JPH0396688A/en active Pending
-
1990
- 1990-09-07 KR KR1019900014228A patent/KR940007759B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| KR910006617A (en) | 1991-04-29 |
| KR940007759B1 (en) | 1994-08-24 |
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