JPS6173585A - Torque controller of sealed compressor - Google Patents
Torque controller of sealed compressorInfo
- Publication number
- JPS6173585A JPS6173585A JP59191539A JP19153984A JPS6173585A JP S6173585 A JPS6173585 A JP S6173585A JP 59191539 A JP59191539 A JP 59191539A JP 19153984 A JP19153984 A JP 19153984A JP S6173585 A JPS6173585 A JP S6173585A
- Authority
- JP
- Japan
- Prior art keywords
- torque
- compressor
- motor
- power supply
- vibration
- 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
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
- H02P23/00—Arrangements or methods for the control of AC motors characterised by a control method other than vector control
- H02P23/16—Controlling the angular speed of one shaft
Landscapes
- Engineering & Computer Science (AREA)
- Power Engineering (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Control Of Electric Motors In General (AREA)
- Control Of Positive-Displacement Air Blowers (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は密閉形圧縮機に係るもので、特に電動機のトル
クを制御することにより低振動化を図っ−た密閉形圧縮
機を提供するものである。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a hermetic compressor, and in particular provides a hermetic compressor that achieves low vibration by controlling the torque of an electric motor. be.
従来の密閉形圧縮機の防振構造につpzでは、日本冷凍
協会出版「密閉形冷凍機」と題する文献1こ論じられて
いる様に圧縮機の振動が取付台や吐出、吸込配管系に伝
播するのを抑制するためにばね及びダッシュポ・ソトを
介して圧縮機を取付台をこ接続する構造か知られている
(第1図)。Regarding the vibration isolation structure of conventional hermetic compressors, as discussed in the literature 1 entitled "Hermetic Refrigerator" published by the Japan Refrigeration Association, the vibration of the compressor is caused by damage to the mounting base, discharge, and suction piping systems. A structure is known in which a compressor is connected to a mounting base via a spring and a dash port in order to suppress the propagation (FIG. 1).
しかしながら、本手法は圧縮機自体の振動を低減するも
のではなく、取付台(こ伝達する圧縮機の振動を無くす
ことはできなかった。However, this method does not reduce the vibrations of the compressor itself, and it was not possible to eliminate the vibrations of the compressor transmitted by the mounting base.
本発明の目的は従来の密閉形圧縮機の振動原因である負
荷トルクとモータ出力トルりとの差をOにすることによ
り、無振動の密閉形圧縮機を提供せんとしたものである
。An object of the present invention is to provide a vibration-free hermetic compressor by reducing the difference between the load torque and motor output torque, which is the cause of vibration in conventional hermetic compressors, to zero.
すなわち、圧縮機が1回転する間の負荷トルりの変化に
同期して、常に等しいモータ出力トルりが生ずるようモ
ータ出力を制御することによって両トルクの差を0とし
たものである。その制御は圧縮機の回転方向加速度を検
知する回転振動検出器より取り出した加速度信号をモー
タ駆動制御部に入力人、その信号にもとづきマイコン等
の制御部により演算処理し、その指令により、モータに
供給する電圧又は電流を制御調整し、加速度信号に比例
したモータトルクを発生する様に制御するものである。That is, the difference between both torques is made zero by controlling the motor output so that the same motor output torque is always produced in synchronization with the change in load torque during one revolution of the compressor. To control this, a person inputs an acceleration signal extracted from a rotational vibration detector that detects the rotational acceleration of the compressor into the motor drive control unit, and based on that signal, a control unit such as a microcomputer performs arithmetic processing, and according to the command, the motor is The supplied voltage or current is controlled and adjusted so as to generate a motor torque proportional to the acceleration signal.
以下、本発明の一実施例を第2図、第3図により説明す
る。lはケースであり、電動要素及び圧縮要素を収納し
ている。2はステータであり、・ンース1(こ固着しで
ある。3はロータ、4は軸であり、ロータ3と軸4か圧
入固定しである。5は主軸受、6は端部軸受であり、軸
4を支持し、主軸受5かケースに固定されている。7は
シリンダブロックであり、主軸受5及び端部軸受6と共
に締結しである。8はローラであり軸4のクランク部に
嵌入しである。9はベーンでありシリンダ室内を吸込室
10と圧縮室11に仕切っている。12は防振部材であ
り、圧縮機を支持している。13は回転方向加速度検知
器であり、ケースに固着され、回転方向加速度信号を検
出する。14は制御部であり、回転方向加速度信号に比
例したモータトルクを発生させる指令信号を電源駆動部
15(こ送信する。電源駆動部15では指令信号により
、圧縮機ステータ2への供給電源を調整する。An embodiment of the present invention will be described below with reference to FIGS. 2 and 3. 1 is a case, which houses the electric element and the compression element. 2 is a stator, and 1 is fixed. 3 is a rotor, 4 is a shaft, and the rotor 3 and shaft 4 are press-fitted and fixed. 5 is a main bearing, and 6 is an end bearing. , supports the shaft 4, and is fixed to the main bearing 5 or case. 7 is a cylinder block, which is fastened together with the main bearing 5 and end bearing 6. 8 is a roller, which is attached to the crank part of the shaft 4. 9 is a vane that partitions the cylinder chamber into a suction chamber 10 and a compression chamber 11. 12 is a vibration isolating member that supports the compressor. 13 is a rotational direction acceleration detector. , which is fixed to the case and detects a rotational direction acceleration signal. 14 is a control section, which transmits a command signal for generating a motor torque proportional to the rotational direction acceleration signal to a power supply drive section 15. The power supply drive section 15 The power supply to the compressor stator 2 is adjusted based on the command signal.
この様な密閉形圧縮機においては圧縮室11内の高圧ガ
ス(こよる力が軸4に対して、反時計方向に押しもどそ
うとした負荷トルク−T6として作用し、シリンダブロ
ック7に対しては同じトルクT、が時計方向に反力とし
て作用している。一方モータ出カトルクーT、かロータ
3及び軸4の回転軸系の反力としてステータ2(こ作用
し、その結果ケース1に固定されているステータ2やシ
リンダブロック7、主軸受5、端部軸受6などの非回転
体側においてはT、 −Tw なるトルク差が生じて
いる。このトルク差(T、−T、)iこ対し、非回転体
の質量慣性モーメントJ、、が1→イーの角加速度で回
転変動するときの慣性トルクJ、、4T′Lとバネ定数
Kを有する防振部材12がθだけ回転変位するときの復
元トルクにθとで釣合を保っており、これらの釣合はと
して表わされる。In such a hermetic compressor, the high-pressure gas in the compression chamber 11 acts on the shaft 4 as a load torque -T6 that tries to push it back counterclockwise, and on the cylinder block 7. The same torque T acts in the clockwise direction as a reaction force.On the other hand, the motor output torque T acts on the stator 2 as a reaction force from the rotating shaft system of the rotor 3 and shaft 4, and as a result, the motor is fixed to the case 1. A torque difference of T, -Tw occurs on the non-rotating body side such as the stator 2, cylinder block 7, main bearing 5, and end bearing 6.This torque difference (T, -T,)i , when the mass moment of inertia J, of a non-rotating body changes rotationally with an angular acceleration of 1→E, the inertia torque J, , 4T′L and the vibration isolating member 12 having a spring constant K is rotationally displaced by θ. A balance is maintained between the restoring torque and θ, and these balances are expressed as.
ここでモータ出力トルクはケース1の回転変動d2θ
の角加速度に比例して増減するトルクに’dt2 と
回転変動に関係なく常に発生する一定トルクT、のd2
θ
和として T、=Tw+Kwdt2 と表わされる。Here, the motor output torque is the torque that increases or decreases in proportion to the angular acceleration of the rotational fluctuation d2θ in case 1, and the constant torque T that is always generated regardless of the rotational fluctuation, d2.
The sum of θ is expressed as T,=Tw+Kwdt2.
ここで心は回転変動角加速度に対するモータ出力トルク
の比例常数である。したがって非回転系の釣d2θ
合の関係は、(J、、 十Kv)−7H+にθ=T、−
T。Here, the center is the proportional constant of the motor output torque with respect to the rotational fluctuation angular acceleration. Therefore, the relationship of balance d2θ of the non-rotating system is (J,, 10Kv)-7H+, θ=T, -
T.
となり、非回転系の回転慣性は見かけ上(J、、+に、
)に増加し、回転剛性の増大と同等な効果を優るこ
とが出来、回転方向角加速度の減少により、圧縮機の回
転方向振動を減少させることが出来る。Therefore, the rotational inertia of the non-rotating system is apparently (J, , +,
), it is possible to achieve an effect equivalent to that of an increase in rotational rigidity, and by decreasing the rotational angular acceleration, it is possible to reduce the rotational vibration of the compressor.
この関係を圧縮機一回転について図示すると第3図のと
と(なる。圧縮機艮加振力として作用する残差トルクT
、 −T、は回転角加速度(こ比例して増d2θ
d2θ
減するトルクに、 了(=J 、、Tσ→K f) )
分だけ減少t
し、O(こ近づ(ため、根本的(こ振動加振源がとり除
かれ、無振動の密閉形圧縮機か可能となるものである。If this relationship is illustrated for one rotation of the compressor, it becomes as shown in Figure 3.
, −T is the rotational angular acceleration (which increases proportionally to d2θ
d2θ decreases in torque (=J,,Tσ→K f))
As a result, the fundamental source of vibration excitation is eliminated, making it possible to create a vibration-free hermetic compressor.
第4図は本発明における他の実施例を示すもので、ケー
ス1に加速度検知器を固着する代わりに圧縮機取付台に
圧縮機の回転方向変位を検知する変位検知器16を設け
、変位検知器16の出力信号を変位検知器16と制御部
14の間に設けられた微分器17により、変位を加速度
(こ変換し、制御部に加速度信号を転送する。このよう
な本実施例のごとき構成にすると、振動源である圧縮機
に検知器を取り付ける必要かなく、外部から回転方向角
加速度を検知可能となるため、検知器の信頼性が向上出
来、高信頼性の無振動密閉形圧縮機が可能となる。FIG. 4 shows another embodiment of the present invention, in which instead of fixing an acceleration detector to the case 1, a displacement detector 16 for detecting displacement in the rotational direction of the compressor is provided on the compressor mounting base to detect displacement. A differentiator 17 provided between the displacement detector 16 and the control unit 14 converts the output signal of the detector 16 into an acceleration signal, and transfers the acceleration signal to the control unit. With this configuration, it is not necessary to attach a detector to the compressor, which is the vibration source, and the rotational angular acceleration can be detected from the outside, which improves the reliability of the detector and enables highly reliable vibration-free sealed compression. machine becomes possible.
以上説明のごとく本発明によれば、圧縮機の回転変動角
加速度に比例したモータトルクを出力させることにより
、圧縮機の加振トルクとなる負荷トルクとモータ出力ト
ルクとの残差トルクをOにできるので無振動の密閉形圧
縮機を提供することか出来る。As explained above, according to the present invention, by outputting a motor torque proportional to the rotational fluctuation angular acceleration of the compressor, the residual torque between the load torque and the motor output torque, which is the excitation torque of the compressor, is reduced to O. Therefore, it is possible to provide a vibration-free hermetic compressor.
第1図は本発明の密閉形圧縮機の構造及び制圓ブロック
図、第2図は本発明の密閉形圧縮機の非回転体側に働ら
くトルク曲線図、第3図は本発明の他の実施例、第4図
は従来の密閉形圧縮機の防振構造を示す図である。
1・・・ケース、2・・・ステータ、3・・・ロータ、
4・・・軸、5・・・主軸受、6・・・端部軸受、7・
・・シリンダブロック、8・・・ローラ、9・・・ベー
ン、10・・・吸込室、−11・・・圧縮室、12・・
・防振部材、13・・・回転方向加速度検知器、14・
・・制御部、15・・・電源駆動部、16・・・変位検
知器、17・・・微分器、18・・・圧縮機、工9・・
・バネ、20・・・ダッシュポット、21・・・取付′
$1図
0 回転円 ルFig. 1 is a structure and control block diagram of the hermetic compressor of the present invention, Fig. 2 is a torque curve diagram acting on the non-rotating body side of the hermetic compressor of the present invention, and Fig. 3 is a diagram of the torque curve acting on the non-rotating body side of the hermetic compressor of the present invention. Embodiment FIG. 4 is a diagram showing a vibration isolation structure of a conventional hermetic compressor. 1... Case, 2... Stator, 3... Rotor,
4... Shaft, 5... Main bearing, 6... End bearing, 7...
...Cylinder block, 8...Roller, 9...Vane, 10...Suction chamber, -11...Compression chamber, 12...
・Vibration isolation member, 13... Rotational direction acceleration detector, 14.
...Control unit, 15...Power drive unit, 16...Displacement detector, 17...Differentiator, 18...Compressor, Engineering 9...
・Spring, 20... Dashpot, 21... Installation'
$1 Figure 0 Rotating circle
Claims (1)
出信号を処理し、制御する制御回路、指令信号により電
源の駆動を行う電源駆動回路を有し、密閉形圧縮機に供
給する電源電圧或いは電流を制御することを特徴とした
密閉形圧縮機のトルク制御装置。 2、密閉形圧縮機の回転角変動を検知する回転変動変位
検知器とその検出信号を処理し、制御する制御回路、制
御回路の指令信号により、電源の駆動を行う電源駆動回
路を有し、密閉形圧縮機に供給する電源電圧或いは電流
を制御することを特徴とした特許請求範囲1項記載の密
閉形圧縮機のトルク制御装置。[Claims] 1. The hermetic type compressor has a rotational angular acceleration detector installed in the hermetic compressor, a control circuit that processes and controls the detection signal, and a power supply drive circuit that drives the power supply based on the command signal. A torque control device for a hermetic compressor, characterized by controlling the power supply voltage or current supplied to the compressor. 2. It has a rotational fluctuation displacement detector that detects the rotational angle fluctuation of the hermetic compressor, a control circuit that processes and controls the detection signal, and a power supply drive circuit that drives the power supply according to the command signal of the control circuit, The torque control device for a hermetic compressor according to claim 1, which controls a power supply voltage or current supplied to the hermetic compressor.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59191539A JPS6173585A (en) | 1984-09-14 | 1984-09-14 | Torque controller of sealed compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59191539A JPS6173585A (en) | 1984-09-14 | 1984-09-14 | Torque controller of sealed compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS6173585A true JPS6173585A (en) | 1986-04-15 |
Family
ID=16276351
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP59191539A Pending JPS6173585A (en) | 1984-09-14 | 1984-09-14 | Torque controller of sealed compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6173585A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63289245A (en) * | 1987-05-22 | 1988-11-25 | Hitachi Ltd | Torque control device for internal combustion engine |
JPS63290182A (en) * | 1987-05-22 | 1988-11-28 | Hitachi Ltd | Torque control type rotary motor machine |
JP2013011187A (en) * | 2011-06-28 | 2013-01-17 | Furukawa Industrial Machinery Systems Co Ltd | Uniaxial eccentric screw pump |
-
1984
- 1984-09-14 JP JP59191539A patent/JPS6173585A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63289245A (en) * | 1987-05-22 | 1988-11-25 | Hitachi Ltd | Torque control device for internal combustion engine |
JPS63290182A (en) * | 1987-05-22 | 1988-11-28 | Hitachi Ltd | Torque control type rotary motor machine |
JP2013011187A (en) * | 2011-06-28 | 2013-01-17 | Furukawa Industrial Machinery Systems Co Ltd | Uniaxial eccentric screw pump |
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