JP2000274384A - Gas compressor - Google Patents
Gas compressorInfo
- Publication number
- JP2000274384A JP2000274384A JP11079878A JP7987899A JP2000274384A JP 2000274384 A JP2000274384 A JP 2000274384A JP 11079878 A JP11079878 A JP 11079878A JP 7987899 A JP7987899 A JP 7987899A JP 2000274384 A JP2000274384 A JP 2000274384A
- Authority
- JP
- Japan
- Prior art keywords
- pulley
- gas compressor
- inertia
- moment
- inertial moment
- 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.)
- Granted
Links
Landscapes
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、カーエアコン等
に用いられるロータリ型の気体圧縮機に関し、特に、気
体圧縮機運転中に発生する圧縮トルクの変動を抑制する
気体圧縮機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary type gas compressor used for a car air conditioner and the like, and more particularly, to a gas compressor which suppresses fluctuations in compression torque generated during operation of the gas compressor.
【０００２】[0002]
【従来の技術】ロータリ型の気体圧縮機には、ベーン
型、スクロール型等があるが、いずれの型のロータリ型
気体圧縮機でも気体を圧縮するロータ軸の１回転中に周
期的な圧縮トルク変動を生じる。例えば、図１および図
２に示した、ロータ１６側のベーン２が５枚で吐出弁
３、３がシリンダ室４の２か所に対称に配設された気体
圧縮機においては、シリンダ室４内の隣合う２枚のベー
ンで囲まれた圧縮室５が、吸入室６に連通し、かつ、シ
リンダ室４に開口したシリンダ入口孔（図示省略）を通
過する際、圧縮室５の容積増加に伴って吸入室６から冷
媒ガスを吸入し、ロータ軸１の回転とともに、圧縮室５
に閉じ込めた冷媒ガスを圧縮していって、吐出弁３を通
過する際、吐出弁３の吐出室８側とシリンダ室４すなわ
ち圧縮室５との圧力差により吐出弁３を開いて圧縮した
冷媒ガスを吐出室８に送り出す。この吸入・圧縮・吐出
のサイクルは、ロータ軸１回転中に、一方の吐出弁３側
で５回、他方の吐出弁３側でこれと位相を１／２サイク
ルずらして、やはり５回となり、計１０回となる。2. Description of the Related Art A rotary type gas compressor includes a vane type, a scroll type and the like. In any type of rotary type gas compressor, a periodic compression torque is generated during one rotation of a rotor shaft for compressing gas. Cause fluctuations. For example, in the gas compressor shown in FIGS. 1 and 2 in which the number of the vanes 2 on the rotor 16 side is five and the discharge valves 3 are arranged symmetrically at two places of the cylinder chamber 4, the cylinder chamber 4 When the compression chamber 5 surrounded by two adjacent vanes inside the cylinder communicates with the suction chamber 6 and passes through a cylinder inlet hole (not shown) opened to the cylinder chamber 4, the volume of the compression chamber 5 increases. As a result, the refrigerant gas is sucked from the suction chamber 6 and the compression chamber 5 is rotated with the rotation of the rotor shaft 1.
When the refrigerant gas confined in the compressor is compressed and passes through the discharge valve 3, the refrigerant compressed by opening the discharge valve 3 due to the pressure difference between the discharge chamber 8 side of the discharge valve 3 and the cylinder chamber 4, that is, the compression chamber 5. The gas is sent to the discharge chamber 8. During one rotation of the rotor shaft, the suction / compression / discharge cycle is performed five times on the one discharge valve 3 side, and the phase is shifted by サ イ ク ル cycle on the other discharge valve 3 side. The total is 10 times.
【０００３】そして、このサイクル１サイクルを周期と
して、圧縮機の圧縮トルクの変動が、図６に示すよう
に、発生する。すなわち、図２の５枚ベーン２吐出弁の
場合は、ロータ軸の１回転中に１０回、周期的に圧縮ト
ルク変動を生じる。[0003] With this cycle as one cycle, the fluctuation of the compression torque of the compressor occurs as shown in FIG. That is, in the case of the five-vane two-discharge valve in FIG. 2, the compression torque fluctuates periodically ten times during one rotation of the rotor shaft.
【０００４】[0004]
【発明が解決しようとする課題】気体圧縮機が自動車の
エンジンルームに搭載された場合、上記のロータ軸１
は、自動車のエンジンシャフト（クランクシャフト）か
ら回転動力を受けて回転する。すなわち、図示省略のエ
ンジンシャフトに取り付けられたプーリから図１のベル
ト９を介して気体圧縮機のプーリ１０に若干増速されて
回転動力が伝えられ、この回転動力は電磁クラッチ１１
を介してロータ軸１に伝えられる。従って、ロータ軸１
の回転速度はエンジンの回転数（回転速度）に比例して
増減する。When the gas compressor is mounted in an engine room of an automobile, the above-mentioned rotor shaft 1 is not used.
Rotates by receiving rotational power from the engine shaft (crankshaft) of the automobile. That is, the rotational power is transmitted from the pulley attached to the engine shaft (not shown) to the pulley 10 of the gas compressor through the belt 9 of FIG.
To the rotor shaft 1. Therefore, the rotor shaft 1
The rotation speed increases or decreases in proportion to the engine speed (rotation speed).
【０００５】また、気体圧縮機は、そのケース体１２の
取り付け部１２ａ、１２ａ‥‥でボルト等により自動車
ボディのシャーシに取り付けられている。[0005] The gas compressor is attached to a chassis of an automobile body by bolts or the like at attachment portions 12a, 12a # of a case body 12 thereof.
【０００６】気体圧縮機運転中の上記圧縮トルク変動
は、気体圧縮機外へ取り付け部１２ａやベルト９を介し
て機械振動力となって伝わり、振動しやすいステアリン
グや配管系等を振動させる。自動車走行中は、エンジン
音、走行音にかき消されてあまり気にならないが、特
に、静かなアイドリング中にエアコンを作動させ、気体
圧縮機が運転しているとき、そのときの気体圧縮機の回
転速度における圧縮トルク変動による振動が、ステアリ
ングや配管系等の共振周波数に近いと、上記の振動が異
常音となり、非常に気になるので、この異常音発生を防
止しなければならない。[0006] The fluctuation of the compression torque during the operation of the gas compressor is transmitted as mechanical vibration force to the outside of the gas compressor via the mounting portion 12a and the belt 9, and vibrates the easily oscillating steering and piping systems. While driving a car, the noise of the engine and the running noise drown out, so it is not much of a concern.In particular, when the air conditioner is operating during quiet idling and the gas compressor is operating, the rotation of the gas compressor at that time If the vibration caused by the fluctuation of the compression torque at the speed is close to the resonance frequency of the steering system or the piping system, the above-mentioned vibration becomes an abnormal sound, which is very worrisome.
【０００７】そこで、この発明は、気体圧縮機のロー
タ、ロータ軸、プーリ等の回転部の慣性モーメントを増
すことにより、圧縮トルク変動を抑えた気体圧縮機を提
供するものである。Accordingly, the present invention provides a gas compressor which suppresses fluctuations in compression torque by increasing the moment of inertia of a rotating part of a gas compressor such as a rotor, a rotor shaft and a pulley.
【０００８】[0008]
【課題を解決するための手段】上述の課題を解決するた
めに、請求項１の発明は、回転部が回転することにより
気体を圧縮する気体圧縮機において、上記回転部に慣性
モーメント付加部を設けたことを特徴とする。According to a first aspect of the present invention, there is provided a gas compressor for compressing a gas by rotating a rotating unit, wherein the rotating unit is provided with an inertia moment adding unit. It is characterized by having been provided.
【０００９】請求項１の発明においては、慣性モーメン
ト付加部により、気体圧縮機のロータ、ロータ軸、プー
リ等の回転部の慣性モーメントが増加し、これにより圧
縮トルク変動が抑制される。According to the first aspect of the present invention, the inertia moment adding section increases the inertia moment of the rotating section of the gas compressor, such as the rotor, the rotor shaft, and the pulley, thereby suppressing the fluctuation of the compression torque.
【００１０】請求項２の発明は、請求項１の発明におい
て、慣性モーメント付加部が、圧縮機本体のロータ軸に
固定されたプーリに設けられたことを特徴とする。According to a second aspect of the present invention, in the first aspect of the present invention, the inertia moment adding portion is provided on a pulley fixed to a rotor shaft of the compressor body.
【００１１】請求項２の発明においては、回転部の中で
も直径の大きいプーリに慣性モーメント付加部を設ける
から、質量の割りに慣性モーメントの大きい慣性モーメ
ント付加部となり、気体圧縮機の重量増加が少なく慣性
モーメントが効率よく増加する。According to the second aspect of the present invention, since the inertia moment adding portion is provided on the pulley having a large diameter among the rotating portions, the inertia moment adding portion has a large inertia moment relative to the mass, and the weight increase of the gas compressor is small. The moment of inertia increases efficiently.
【００１２】請求項３の発明は、請求項２の発明におい
て、慣性モーメント付加部が、プーリ外周部と気体圧縮
機本体を覆うケース体との間に、プーリ外周部から延設
されたことを特徴とする。According to a third aspect of the present invention, in the second aspect of the present invention, the inertia moment applying portion extends from the outer peripheral portion of the pulley between the outer peripheral portion of the pulley and the case body covering the main body of the gas compressor. Features.
【００１３】請求項３の発明においては、気体圧縮機の
大きさが大きくならずに、回転部の慣性モーメントが増
加する。According to the third aspect of the present invention, the inertia moment of the rotating portion increases without increasing the size of the gas compressor.
【００１４】請求項４の発明は、請求項２の発明におい
て、慣性モーメント付加部が、ベルト係合部よりも大径
となっていることを特徴とする。According to a fourth aspect of the present invention, in the second aspect of the present invention, the inertia moment applying portion has a larger diameter than the belt engaging portion.
【００１５】請求項４の発明においては、慣性モーメン
ト付加部と回転部の回転中心軸線との距離が大きいか
ら、回転部の質量増加が少ない割りに、慣性モーメント
が大きくなる。In the invention of claim 4, since the distance between the moment of inertia applying portion and the rotation center axis of the rotating portion is large, the moment of inertia increases despite the small increase in the mass of the rotating portion.
【００１６】請求項５の発明は、請求項２の発明におい
て、プーリの中径部ないし小径部が凹部を有することを
特徴とする。According to a fifth aspect of the present invention, in the second aspect of the present invention, the middle or small diameter portion of the pulley has a recess.
【００１７】請求項５の発明においては、慣性モーメン
ト付加部による質量の増加を凹部による質量の減少で補
償する。According to the fifth aspect of the present invention, the increase in mass due to the inertia moment adding portion is compensated for by the decrease in mass due to the concave portion.
【００１８】なお、この発明における「慣性モーメント
付加部」とは、圧縮機の製品としての機能（気体圧縮機
能、ロータへの伝動機能、外部との密閉機能等）の遂行
に必須の部分ではなく、もっぱら慣性モーメントを増加
するための部分をいう。ただし、上記の製品としての機
能遂行部分であっても、慣性モーメントを増加するため
にのみ、例えば、部分的に密度の高い材料に置き換える
ならば、この材料置き換え部分は「慣性モーメント付加
部」である。また、製造過程、流通過程等で使用する、
例えば、治具への取り付け部、回転バランス取りの重り
取り部を「慣性モーメント付加部」が兼ねることはあ
る。It is to be noted that the "moment of inertia adding portion" in the present invention is not a part indispensable for performing functions as a product of the compressor (a function of gas compression, a function of transmitting power to a rotor, a function of sealing with the outside, etc.). , Exclusively refers to the portion for increasing the moment of inertia. However, even in the above-described product functioning portion, if only a material having a high density is used to increase the moment of inertia only to increase the moment of inertia, for example, the material replacement portion is a `` moment of inertia adding portion ''. is there. Also used in the manufacturing process, distribution process, etc.
For example, the “moment of inertia adding unit” may also serve as a mounting part to a jig and a weight removing part for rotational balancing.
【００１９】[0019]
【発明の実施の形態】この発明の実施の形態を、以下、
図面を参照して説明する。Embodiments of the present invention will be described below.
This will be described with reference to the drawings.
【００２０】図１は、この発明の一実施の形態を示す断
面図、図２は、図１のＩＩ−ＩＩ断面図である。FIG. 1 is a sectional view showing an embodiment of the present invention, and FIG. 2 is a sectional view taken along line II-II of FIG.
【００２１】気体圧縮機は、ケース体１２の取付部１２
ａ、１２ａ‥‥でボルト等により自動車ボディのシャー
シに取り付けられている。また、圧縮対象の冷媒ガス
は、気体圧縮機に連結された吸入配管１３から吸入さ
れ、吐出配管２１から吐出される。The gas compressor includes a mounting portion 12 of the case body 12.
At a, 12a, it is attached to the chassis of the automobile body by bolts or the like. The refrigerant gas to be compressed is sucked from the suction pipe 13 connected to the gas compressor, and is discharged from the discharge pipe 21.
【００２２】気体圧縮機の回転部の回転動力は、自動車
のエンジンシャフトに取り付けられたプーリと気体圧縮
機のロータ軸１に取り付けられたプーリ１０との間に巻
き掛けられたベルト９により、プーリ１０に伝達され
る。プーリ１０は軸受２２を介してフロントサイドブロ
ック１４に回転自在に保持されている。そして、プーリ
１０に装着された電磁クラッチ１１が入っているとき
は、電磁クラッチ１１の摩擦板２２とプーリ１０が結合
され、ロータ軸１にプーリ１０が固定された状態になっ
て、ロータ軸１に伝達される。すなわち、電磁クラッチ
１１がＯＮとなっているときが、気体圧縮機の運転状
態、ＯＦＦとなっているときが、停止状態であり、停止
時は、プーリ１０と電磁クラッチ１１の本体部のみがベ
ルト９により空回転している。The rotational power of the rotating part of the gas compressor is generated by a belt 9 wound around a pulley attached to the engine shaft of the automobile and a pulley 10 attached to the rotor shaft 1 of the gas compressor. It is transmitted to 10. The pulley 10 is rotatably held on the front side block 14 via a bearing 22. When the electromagnetic clutch 11 mounted on the pulley 10 is engaged, the friction plate 22 of the electromagnetic clutch 11 is connected to the pulley 10, and the pulley 10 is fixed to the rotor shaft 1. Is transmitted to That is, when the electromagnetic clutch 11 is ON, the operation state of the gas compressor is OFF, and when the gas compressor is OFF, it is the STOP state. 9 is idle rotation.
【００２３】次に、図１および図２に従って、５枚ベー
ンで、シリンダ室の２か所に対称に吐出弁が配設された
気体圧縮機が、ロータ軸の１回転中に１０回生じる、周
期的圧縮トルク変動について、詳しく説明する。Next, according to FIGS. 1 and 2, a gas compressor having five vanes and symmetrically arranged discharge valves at two places in the cylinder chamber is generated ten times in one rotation of the rotor shaft. The periodic compression torque fluctuation will be described in detail.
【００２４】図１に示した気体圧縮機においては、エア
コンの冷媒循環系を循環してきた冷媒ガスは、気体圧縮
機の運転により、冷媒循環系の吸入配管１３から気体圧
縮機の吸入ポートの逆止弁６ａを通過して、吸入室６に
入った後、フロントサイドブロック１４とリアサイドブ
ロック１５とにそれぞれ設けられた図示省略のシリンダ
室入口孔を経由して、矢印Ａ（図２参照）のようにロー
タ１６、シリンダ１７、２枚のベーン２、２で囲まれ、
次第に容積が増加する圧縮室５に吸引される。In the gas compressor shown in FIG. 1, the refrigerant gas circulating in the refrigerant circulation system of the air conditioner is operated by the operation of the gas compressor to flow from the suction pipe 13 of the refrigerant circulation system to the suction port of the gas compressor. After passing through the stop valve 6a and entering the suction chamber 6, it passes through a cylinder chamber inlet hole (not shown) provided in each of the front side block 14 and the rear side block 15, and is indicated by an arrow A (see FIG. 2). And the rotor 16, the cylinder 17, and the two vanes 2, 2,
It is sucked into the compression chamber 5 whose volume gradually increases.
【００２５】５枚のベーン２、２、‥‥は、ロータ１６
に均等に配設された５か所のベーン溝にそれぞれ摺動自
在に挿入されていて、気体圧縮機の運転中、常にシリン
ダ１７の楕円形状の内壁に接するようになっている。こ
の作動原理は周知であり、この発明とは直接関係がない
ので、ここでは詳しい説明を省略する。The five vanes 2, 2,...
Are slidably inserted into five vane grooves evenly arranged so as to always contact the elliptical inner wall of the cylinder 17 during operation of the gas compressor. This principle of operation is well known and has no direct relation to the present invention, so that a detailed description is omitted here.
【００２６】ロータ１６の回動に伴い、圧縮室５は、上
記シリンダ室入口孔と、圧縮室５の後側（ロータ１６の
回転方向（矢印Ｂ）の反対側）のベーン２により遮断さ
れ、外部から閉ざされた圧縮室５の容積は小さくなって
いって、閉じ込めた冷媒ガスを圧縮する。次いで、圧縮
室５の前側（ロータ１６の回転方向（矢印Ｂ）側）のベ
ーン２が、シリンダ出口孔１８の開口部を通過すると、
圧縮室５内の圧縮されたガス圧が吐出室８に通じる吐出
室前室１９のガス圧よりも高いので、吐出弁３を開いて
圧縮ガスは吐出室前室１９に流入する。With the rotation of the rotor 16, the compression chamber 5 is shut off by the cylinder chamber inlet hole and the vane 2 on the rear side of the compression chamber 5 (opposite to the rotation direction of the rotor 16 (arrow B)). The volume of the compression chamber 5 closed from the outside is small, and compresses the trapped refrigerant gas. Next, when the vane 2 on the front side (the rotation direction (arrow B) side of the rotor 16) of the compression chamber 5 passes through the opening of the cylinder outlet hole 18,
Since the compressed gas pressure in the compression chamber 5 is higher than the gas pressure in the discharge chamber front chamber 19 communicating with the discharge chamber 8, the discharge valve 3 is opened and the compressed gas flows into the discharge chamber front chamber 19.
【００２７】圧縮ガスは、吐出室前室１９から油分離器
２０で冷媒ガスに混入している潤滑油を分離し、吐出室
８に入り、更に、吐出配管２１に送られて、冷媒循環系
を循環し、上記吸入配管１３に戻ってくる。The compressed gas separates the lubricating oil mixed in the refrigerant gas from the discharge chamber front chamber 19 with the oil separator 20, enters the discharge chamber 8, and is further sent to the discharge pipe 21, where the compressed gas is sent to the refrigerant circulation system. And returns to the suction pipe 13.
【００２８】上述の吸入・圧縮・吐出のサイクルの間
に、ロータ軸１、ロータ１６、プーリ１０、電磁クラッ
チ１１等の回転部に圧縮トルク変動を生じる。そして、
プーリ１０とエンジンシャフト側との間には、剛性が弱
いベルト９を介在しているから、この圧縮トルク変動は
エンジンシャフト側で吸収、抑制されることなく、機械
的振動（回転変動）を招くことになる。During the above-described suction / compression / discharge cycle, fluctuations in compression torque occur in rotating parts of the rotor shaft 1, the rotor 16, the pulley 10, the electromagnetic clutch 11, and the like. And
Since the belt 9 having low rigidity is interposed between the pulley 10 and the engine shaft side, the compression torque fluctuation is not absorbed and suppressed on the engine shaft side, but causes mechanical vibration (rotation fluctuation). Will be.
【００２９】この実施の形態では、奇数枚のベーンと対
称に配設した一対のシリンダ入口孔・シリンダ出口孔と
により、両シリンダ入口孔・シリンダ出口孔の吸入・圧
縮・吐出のサイクルに１８０°の位相差を付け、圧縮ト
ルク変動を平準化するようにしてあるが、それでも圧縮
トルク変動発生は避けられず、図６の破線で示すよう
な、回転部の１回転（３６０°）当たりベーン枚数の２
倍の１０サイクルの圧縮トルク変動が存在する。In this embodiment, the odd number of vanes and a pair of symmetrically arranged cylinder inlet holes and cylinder outlet holes make the cycle of suction, compression and discharge of both cylinder inlet holes and cylinder outlet holes 180 °. However, the occurrence of compression torque fluctuation is still unavoidable, and the number of vanes per one rotation (360 °) of the rotating unit as shown by the broken line in FIG. 2
There are twice as many cycles of compression torque variation.
【００３０】上記の圧縮トルク変動を抑制するこの発明
の実施の形態を、図３〜図５を参照して、以下に説明す
る。An embodiment of the present invention for suppressing the above-described fluctuation in compression torque will be described below with reference to FIGS.
【００３１】図３〜図５は、この発明の実施の形態のプ
ーリをそれぞれ示す断面図である。FIGS. 3 to 5 are sectional views showing pulleys according to the embodiment of the present invention.
【００３２】図３のプーリ１０は、プーリ１０の外周部
と気体圧縮機本体を覆うケース体１２との間に、プーリ
１０外周部から円環状の慣性モーメント付加部２４を延
設したもので、この実施の形態では、慣性モーメント付
加部２４はプーリ１０と一体形成されている。この慣性
モーメント付加部２４により、プーリ１０の慣性モーメ
ントは、０．２７×１０-3ｋｇｍ2増加し、１．２倍の
１．６５×１０-3ｋｇｍ2の慣性モーメントとなった。
このようにプーリ１０とケース体１２との間に慣性モー
メント付加部２４を設けると、気体圧縮機の大きさが大
きくならずに、回転部の慣性モーメントが増加する。な
お、慣性モーメント付加部２４を直径の大きい円環状に
すると、慣性モーメント／重量を効率よく大きくでき
て、しかも、回転時のバランスがくずれにくく、製作も
容易である。The pulley 10 shown in FIG. 3 has an annular moment of inertia adding portion 24 extending from the outer periphery of the pulley 10 between the outer periphery of the pulley 10 and the case body 12 covering the gas compressor body. In this embodiment, the moment of inertia adding section 24 is formed integrally with the pulley 10. The inertia moment adding section 24 increases the inertia moment of the pulley 10 by 0.27 × 10 −3 kgm 2 , which is 1.2 times as large as 1.65 × 10 −3 kgm 2 .
When the inertia moment applying portion 24 is provided between the pulley 10 and the case body 12 in this manner, the inertia moment of the rotating portion increases without increasing the size of the gas compressor. In addition, when the inertia moment applying portion 24 is formed in an annular shape having a large diameter, the inertia moment / weight can be efficiently increased, and the balance at the time of rotation is hardly lost, so that manufacturing is easy.
【００３３】この図３のプーリ１０を気体圧縮機に用い
たところ、圧縮トルク変動が図６の実線のように減少
し、この気体圧縮機を自動車に搭載して運転したとこ
ろ、図７の発明品１のように、アイドリング時の騒音が
従来品よりも８ｄＢ下がった。When the pulley 10 of FIG. 3 is used for a gas compressor, the fluctuation of the compression torque is reduced as shown by the solid line in FIG. 6, and when this gas compressor is mounted on an automobile and operated, the invention of FIG. As in the case of the product 1, the noise at the time of idling was 8 dB lower than that of the conventional product.
【００３４】図４のプーリ１０は、円環状の慣性モーメ
ント付加部２４をプーリ１０のベルト係合部１０ａより
も大径としてある。この実施の形態では、円環状の慣性
モーメント付加部２４はプーリ１０と一体形成されてい
る。この慣性モーメント付加部２４により、プーリ１０
の慣性モーメントは、０．５２×１０-3ｋｇｍ2増加
し、１．４倍の１．９０×１０-3ｋｇｍ2の慣性モーメ
ントとなった。このように慣性モーメント付加部２４を
ベルト係合部１０ａよりも大径とすると、慣性モーメン
ト付加部と回転部の回転中心軸線Ｃとの距離が大きくな
るから、回転部の質量増加が少ない割りに、慣性モーメ
ントが大きくなる。In the pulley 10 shown in FIG. 4, the annular moment of inertia applying portion 24 has a larger diameter than the belt engaging portion 10a of the pulley 10. In this embodiment, the annular moment of inertia applying portion 24 is formed integrally with the pulley 10. The inertia moment adding section 24 allows the pulley 10
Has increased by 0.52 × 10 −3 kgm 2, and increased by a factor of 1.4 to 1.90 × 10 −3 kgm 2 . If the inertia moment applying portion 24 is made larger in diameter than the belt engaging portion 10a, the distance between the inertia moment applying portion and the rotation center axis C of the rotating portion becomes large, so that the mass increase of the rotating portion is small. , The moment of inertia increases.
【００３５】この図４のプーリ１０を気体圧縮機に用い
たところ、圧縮トルク変動が図６の実線以上に減少し、
この気体圧縮機を自動車に搭載して運転したところ、図
７の発明品２のように、アイドリング時の騒音が従来品
よりも１１ｄＢ下がった。When the pulley 10 of FIG. 4 is used for a gas compressor, the fluctuation of the compression torque is reduced more than the solid line of FIG.
When this gas compressor was mounted on an automobile and operated, the noise during idling was reduced by 11 dB as compared with the conventional product, as in Invention 2 of FIG.
【００３６】図５のプーリ１０は、円環状の慣性モーメ
ント付加部２４をプーリ１０のベルト係合部１０ａより
も大径とするとともに、プーリ１０の重量増加を補償す
るため、慣性モーメントに影響の少ないプーリの中径部
から小径部にかけて円環状の凹部１０ｂ、１０ｂを設け
てある。この実施の形態では、円環状の慣性モーメント
付加部２４はプーリ１０と一体形成されている。図４の
プーリに比較して重量増加が少なく、慣性モーメントは
同程度に増加した。なお、凹部１０ｂを円環状にする
と、回転時のバランスがくずれにくく、製作も容易であ
る。In the pulley 10 shown in FIG. 5, the annular moment of inertia adding portion 24 has a larger diameter than the belt engaging portion 10a of the pulley 10, and the pulley 10 compensates for an increase in weight. Annular concave portions 10b, 10b are provided from the middle diameter portion to the small diameter portion of the small number of pulleys. In this embodiment, the annular moment of inertia applying portion 24 is formed integrally with the pulley 10. The weight increase was small compared to the pulley of FIG. 4, and the moment of inertia was increased to the same extent. In addition, when the concave portion 10b is formed in an annular shape, the balance at the time of rotation is hardly lost, and the manufacture is easy.
【００３７】この図５のプーリ１０を気体圧縮機に用い
たところ、圧縮トルク変動が図４のプーリとほぼ同じレ
ベルに減少し、この気体圧縮機を自動車に搭載して運転
したところ、アイドリング時の騒音が図４のプーリとほ
ぼ同じレベルで下がった。When the pulley 10 shown in FIG. 5 is used for a gas compressor, the fluctuation of the compression torque is reduced to substantially the same level as the pulley shown in FIG. The noise level of the pulley was reduced at almost the same level as the pulley of FIG.
【００３８】気体圧縮機の回転部の中でも、プーリ１０
は直径が大きく、しかも、寸法形状変更の余地が比較的
大きい。上述の実施の形態のように、プーリ１０の回転
中心軸線Ｃから離れた位置に慣性モーメント付加部２４
を設けると、質量の割りに慣性モーメントの大きい慣性
モーメント付加部となり、気体圧縮機の重量増加が少な
く慣性モーメントが効率よく増加する。Among the rotating parts of the gas compressor, the pulley 10
Has a large diameter, and the room for changing the dimensions and shapes is relatively large. As in the above-described embodiment, the moment of inertia adding unit 24 is located at a position away from the rotation center axis C of the pulley 10.
Is provided, an inertia moment adding portion having a large inertia moment is obtained for the mass, and the weight increase of the gas compressor is small and the inertia moment is efficiently increased.
【００３９】なお、プーリ１０に設けたこれらの慣性モ
ーメント付加部２４は、例えば、治具への取り付け部と
して、あるいは、回転バランス取りの重り取り部とし
て、製造過程、流通過程等で使用することもできる。The moment of inertia adding portion 24 provided on the pulley 10 is used in a manufacturing process, a distribution process, or the like, for example, as a portion to be attached to a jig or as a weight portion for rotating balance. Can also.
【００４０】上述の実施の形態では、慣性モーメント付
加部２４をプーリ１０と一体形成したが、プーリ１０の
本体部分を、従来品同様、鉄系とし、慣性モーメント付
加部２４には鉛、銅合金、ヘビーメタル等、鉄よりも密
度の大きい材料を使用すれば、一層、慣性モーメントを
増加することができる。この場合は、慣性モーメント付
加部２４をプーリ１０に、ろう付け、接着、溶接、ねじ
止め等の手法で固定する。また、回転時の万一の脱落事
故を予防し、バランスのくずれを防ぐために、図３〜図
５に破線ｄで示したようにに、プーリ１０の内径側に凹
環部を設けて、そこに慣性モーメント付加部２４の内径
側に設けた凸環部を嵌め込むような構造とすることが好
ましい。In the above-described embodiment, the inertia moment adding portion 24 is formed integrally with the pulley 10, but the main body of the pulley 10 is made of iron as in the conventional product, and the inertia moment adding portion 24 is made of lead or copper alloy. If a material having a higher density than iron, such as heavy metal, is used, the moment of inertia can be further increased. In this case, the moment of inertia adding section 24 is fixed to the pulley 10 by a technique such as brazing, bonding, welding, or screwing. Further, in order to prevent an accidental dropping accident during rotation and to prevent the balance from being lost, a concave ring portion is provided on the inner diameter side of the pulley 10 as shown by a broken line d in FIGS. It is preferable to adopt a structure in which a convex ring portion provided on the inner diameter side of the moment of inertia adding portion 24 is fitted into the inner ring.
【００４１】この発明における慣性モーメント付加部
は、回転部の他の部分に設けるようにしてもよい。例え
ば、ロータの外径付近の材料に鉛、銅合金、ヘビーメタ
ル等の質量の大きい材料を用いて、ロータ本来の機能部
分（ベーン溝面、ロータ軸との接合面、サイドブロック
との摺接面等）を被覆等により他の適材にしたり、電磁
クラッチの摩擦板に質量の大きい材料を張り付けたりし
てもよい。The moment of inertia adding section in the present invention may be provided in another portion of the rotating section. For example, a material having a large mass such as lead, copper alloy, or heavy metal is used as the material near the outer diameter of the rotor, and the original functional parts of the rotor (the vane groove surface, the joint surface with the rotor shaft, the sliding contact with the side block) Or other suitable material by coating or the like, or a material having a large mass may be attached to the friction plate of the electromagnetic clutch.
【００４２】[0042]
【発明の効果】以上詳細に説明したように、この発明
は、気体圧縮機のロータ、ロータ軸、プーリ等の回転部
に慣性モーメント付加部を設けたから、回転部の慣性モ
ーメントが増加し、圧縮トルク変動が抑制され、ステア
リングや配管系等の異常音発生を防止することができ
る。As described above in detail, according to the present invention, since the rotor, rotor shaft, pulley and other rotating parts of the gas compressor are provided with an inertia moment adding part, the inertia moment of the rotating part increases, and Torque fluctuation is suppressed, and occurrence of abnormal noises in the steering and piping systems can be prevented.
【００４３】慣性モーメント付加部を、回転部の中でも
直径の大きいプーリに設ければ、質量の割りに慣性モー
メントの大きい慣性モーメント付加部となり、慣性モー
メント付加部を設けたことによる気体圧縮機の重量増加
が少なくてすむ。If the inertia moment adding section is provided on the pulley having a large diameter among the rotating sections, the inertia moment adding section becomes a large inertia moment for the mass, and the weight of the gas compressor due to the provision of the inertia moment adding section. The increase is small.
【００４４】また、プーリに設ける慣性モーメント付加
部を、プーリ外周部と気体圧縮機本体を覆うケース体と
の間に、プーリ外周部から延設すれば、慣性モーメント
付加部を設けても、気体圧縮機の大きさを大きくするこ
となく慣性モーメントを増加させることができる。Further, if the inertia moment applying portion provided on the pulley is extended from the outer peripheral portion of the pulley between the outer peripheral portion of the pulley and the case body covering the gas compressor body, the inertia moment applying portion can be provided even if the inertia moment applying portion is provided. The moment of inertia can be increased without increasing the size of the compressor.
【００４５】更に、また、プーリに設ける慣性モーメン
ト付加部を、ベルト係合部よりも大径とすれば、慣性モ
ーメント付加部と回転部の回転中心軸線との距離が大き
いから、回転部の質量増加が少ない割りに、慣性モーメ
ントを大きくできる。Further, if the inertia moment applying portion provided on the pulley is made larger in diameter than the belt engaging portion, the distance between the inertia moment applying portion and the rotation center axis of the rotating portion is large. Although the increase is small, the moment of inertia can be increased.
【００４６】また、プーリに慣性モーメント付加部を設
けるとともに、慣性モーメント付加部よりも回転部の回
転中心軸線に近いプーリの中径部ないし小径部に凹部を
設けると、慣性モーメント付加部による質量の増加を凹
部による質量の減少で補償し、慣性モーメント付加部を
設けても、プーリの重量増加が抑えられる。Further, when the pulley is provided with an inertia moment adding portion and a concave portion is provided in a middle diameter portion or a small diameter portion of the pulley closer to the rotation center axis of the rotating portion than the inertia moment adding portion, the mass of the inertia moment adding portion is reduced. Even if the increase is compensated for by the decrease in mass due to the concave portion and the inertia moment adding portion is provided, the increase in the weight of the pulley can be suppressed.
【図１】この発明の実施の形態を示す縦断面図。FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention.
【図２】図１のＩＩ−ＩＩ断面図。FIG. 2 is a sectional view taken along line II-II of FIG.
【図３】図１の要部を示す断面図。FIG. 3 is a sectional view showing a main part of FIG. 1;
【図４】この発明の他の実施の形態の要部を示す断面
図。FIG. 4 is a sectional view showing a main part of another embodiment of the present invention.
【図５】この発明の更に他の実施の形態の要部を示す断
面図。FIG. 5 is a sectional view showing a main part of still another embodiment of the present invention.
【図６】気体圧縮機の圧縮トルク変動を示す説明図。FIG. 6 is an explanatory diagram showing compression torque fluctuation of the gas compressor.
【図７】気体圧縮機の回転部の慣性モーメントと騒音レ
ベルの関係を示す説明図。FIG. 7 is an explanatory diagram showing a relationship between a moment of inertia of a rotating part of the gas compressor and a noise level.
１ ロータ軸 ２ ベーン ４ シリンダ室 ５ 圧縮室 ９ ベルト １０ プーリ １０ａ ベルト係合部 １０ｂ 凹部 １２ ケース体 １２ａ 取り付け部 １６ ロータ １７ シリンダ ２４ 慣性モーメント付加部 ２５ 気体圧縮機本体 DESCRIPTION OF SYMBOLS 1 Rotor shaft 2 Vane 4 Cylinder chamber 5 Compression chamber 9 Belt 10 Pulley 10a Belt engagement part 10b Concave part 12 Case body 12a Attachment part 16 Rotor 17 Cylinder 24 Moment of inertia addition part 25 Gas compressor body
Claims (5)
する気体圧縮機において、上記回転部に慣性モーメント
付加部を設けたことを特徴とする気体圧縮機。1. A gas compressor for compressing gas by rotating a rotating unit, wherein the rotating unit is provided with an inertia moment adding unit.
ロータ軸に固定されたプーリに設けられたことを特徴と
する請求項１記載の気体圧縮機。2. The gas compressor according to claim 1, wherein the inertia moment adding section is provided on a pulley fixed to a rotor shaft of the compressor body.
と気体圧縮機本体を覆うケース体との間に、プーリ外周
部から延設されたことを特徴とする請求項２記載の気体
圧縮機。3. The gas compressor according to claim 2, wherein the moment of inertia adding portion extends from the outer peripheral portion of the pulley between the outer peripheral portion of the pulley and the case body covering the main body of the gas compressor.
よりも大径となっていることを特徴とする請求項２記載
の気体圧縮機。4. The gas compressor according to claim 2, wherein the inertia moment applying portion has a larger diameter than the belt engaging portion.
することを特徴とする請求項２記載の気体圧縮機。5. The gas compressor according to claim 2, wherein a middle diameter portion or a small diameter portion of the pulley has a concave portion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07987899A JP4011227B2 (en) | 1999-03-24 | 1999-03-24 | Gas compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07987899A JP4011227B2 (en) | 1999-03-24 | 1999-03-24 | Gas compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000274384A true JP2000274384A (en) | 2000-10-03 |
| JP4011227B2 JP4011227B2 (en) | 2007-11-21 |
Family
ID=13702503
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP07987899A Expired - Lifetime JP4011227B2 (en) | 1999-03-24 | 1999-03-24 | Gas compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4011227B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012012981A (en) * | 2010-06-30 | 2012-01-19 | Hori Engineering Co Ltd | Onboard compressor |
-
1999
- 1999-03-24 JP JP07987899A patent/JP4011227B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012012981A (en) * | 2010-06-30 | 2012-01-19 | Hori Engineering Co Ltd | Onboard compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4011227B2 (en) | 2007-11-21 |
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