JP2501337B2 - Supercharged compressor - Google Patents
Supercharged compressorInfo
- Publication number
- JP2501337B2 JP2501337B2 JP62167734A JP16773487A JP2501337B2 JP 2501337 B2 JP2501337 B2 JP 2501337B2 JP 62167734 A JP62167734 A JP 62167734A JP 16773487 A JP16773487 A JP 16773487A JP 2501337 B2 JP2501337 B2 JP 2501337B2
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- suction
- rotation speed
- suction pipe
- rpm
- 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
Landscapes
- Compressor (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Description
【発明の詳細な説明】 ［産業上の利用分野］ 本発明は、過給式圧縮機に係り、例えば空気調和機等
に使用されているロータリ圧縮機など、高速域で過給効
果を有効利用するのに好適な過給式圧縮機に関するもの
である。The present invention relates to a supercharged compressor, and effectively utilizes the supercharge effect in a high speed range such as a rotary compressor used in an air conditioner or the like. The present invention relates to a supercharged compressor suitable for
［従来の技術］ ロータリ圧縮機など従来の回転圧縮機の過給装置は、
例えば実開昭59−20594号公報に記載のように、アキュ
ムレータを共鳴器と兼用し、共鳴器に過給機能を具備さ
せることにより、回転圧縮機の圧縮効率を向上させるも
のであった。[Prior Art] A conventional supercharger for a rotary compressor such as a rotary compressor is
For example, as described in Japanese Utility Model Laid-Open No. 59-20594, the accumulator also serves as a resonator, and the resonator has a supercharging function to improve the compression efficiency of the rotary compressor.
上記従来技術を第６図を参照して説明する。 The above conventional technique will be described with reference to FIG.
第６図は、従来の過給式ロータリ圧縮機の縦断面図で
ある。FIG. 6 is a vertical sectional view of a conventional supercharged rotary compressor.
第６図において、１はケーシング、２は、インバータ
により回転数制御される電動機部、３は圧縮機構部、４
は、電動機部２と圧縮機構部３とを連結する回転軸、５
は、ケーシング１に固定されたシリンダ、6,7は、この
シリンダの上下端面を密閉するとともに回転軸４を支承
する上、下軸受、８は、回転軸４の偏心クランク部に嵌
着されたローラである。In FIG. 6, 1 is a casing, 2 is an electric motor part whose rotation speed is controlled by an inverter, 3 is a compression mechanism part, 4
Is a rotary shaft that connects the electric motor unit 2 and the compression mechanism unit 3 to each other.
Is a cylinder fixed to the casing 1, 6 and 7 seal the upper and lower end surfaces of the cylinder and support the rotary shaft 4, and a lower bearing 8 is fitted to an eccentric crank part of the rotary shaft 4. It's Laura.
ここには詳細な図示を省略しているが、シリンダ５に
はベーン溝が形設されており、ベーン溝にはベーンが挿
入され、ばねによってベーンの一端をローラ８の外周に
当接させるように構成されている。前記ベーンはローラ
８の回転に追従してシリンダ５内を往復動し、前記シリ
ンダ５内を吸込室と圧縮室とに仕切るようにして前記圧
縮機構部３が構成されている。９は、圧縮ガスの吐出室
を示す。Although not shown in detail here, a vane groove is formed in the cylinder 5, the vane is inserted in the vane groove, and one end of the vane is brought into contact with the outer periphery of the roller 8 by a spring. Is configured. The vane follows the rotation of the roller 8 and reciprocates in the cylinder 5 to partition the inside of the cylinder 5 into a suction chamber and a compression chamber. Reference numeral 9 indicates a discharge chamber for the compressed gas.
10は、圧縮機の吸込側に設けたアキュムレータ、11は
吐出パイプ、12は吸込パイプである。10 is an accumulator provided on the suction side of the compressor, 11 is a discharge pipe, and 12 is a suction pipe.
第６図に示すロータリ圧縮機では、吸込パイプ12はア
キュムレータ10内を貫通する構造となっており、その吸
込パイプ12に適当な面積を有する穴12aを設け、アキュ
ムレータ10内で圧縮機回転数と一致する周波数で共振を
生じさせ、脈動過給効果（以下共鳴効果という）を得る
ものである。In the rotary compressor shown in FIG. 6, the suction pipe 12 has a structure penetrating the inside of the accumulator 10. The suction pipe 12 is provided with a hole 12a having an appropriate area, and the number of rotations of the compressor is increased in the accumulator 10. Resonance is generated at the matching frequency to obtain a pulsating supercharging effect (hereinafter referred to as resonance effect).
［発明が解決しようとする問題点］ 上記従来技術では、第６図に示すように吸込パイプ12
はアキュムレータ10内を貫通する構造となっているた
め、液冷媒が流入した際、アキュムレータ10は液溜めと
しての機能を果すことができず、液冷媒が直接圧縮機に
吸い込まれやすくなっている。このため、液圧縮による
雑音増大や信頼性の低下という問題があった。[Problems to be Solved by the Invention] In the above-mentioned conventional technique, as shown in FIG.
Since has a structure that penetrates the inside of the accumulator 10, the accumulator 10 cannot function as a liquid reservoir when the liquid refrigerant flows in, and the liquid refrigerant is easily sucked directly into the compressor. Therefore, there is a problem that noise is increased and reliability is lowered due to liquid compression.
また、上記従来技術では、特定の圧縮機回転数に対
し、吸込パイプ12に穴12aを設けて共鳴効果を得るよう
にしているため、圧縮機をインバータ等を用いて回転数
制御する場合、過給効果を有効に利用するための最適な
回転数領域ということについて配慮されておらず、圧縮
効果を高めるのに過給効果を有効に利用していないとい
う問題があった。Further, in the above-mentioned conventional technique, since the hole 12a is provided in the suction pipe 12 to obtain the resonance effect with respect to a specific compressor rotation speed, when the rotation speed control of the compressor is performed using an inverter or the like, it is not possible No consideration has been given to the optimum rotation speed region for effectively utilizing the charging effect, and there is a problem that the supercharging effect is not effectively utilized for enhancing the compression effect.
さらに、アキュムレータの液溜めの機能を損なわない
で吸込配管に共鳴を生じさせる例としては特開昭57−12
2192号公報記載の技術が知られている。この従来技術
は、容積形吸入マフラから圧縮機要素のシリンダ室内へ
吸入ガスを導く吸入接続管の長さｌ（ｍ）を、圧縮機要
素の吸入行程周期をＴ（sec）、吸入ガスの吸入時状態
の音速をａ（m/sec）を用い、 （Ｔ・a/4−0.2）±0.1＝ｌ から算出するもので、吸入接続管で生じるガスの圧力脈
動を吸入接続管内で共振増幅させ、ガスの吸入効率向上
を図るようにしたものである。Further, as an example of causing resonance in the suction pipe without impairing the function of the accumulator liquid reservoir, JP-A-57-12
The technique described in Japanese Patent No. 2192 is known. In this prior art, the length l (m) of a suction connection pipe for guiding the suction gas from the positive displacement suction muffler into the cylinder chamber of the compressor element, the suction stroke cycle of the compressor element T (sec), and the suction gas suction The sound velocity in the time state is calculated from (T ・ a / 4−0.2) ± 0.1 = 1 using a (m / sec), and the pressure pulsation of gas generated in the suction connecting pipe is resonantly amplified in the suction connecting pipe. In addition, the gas inhalation efficiency is improved.
しかし、この従来技術は、一定速の運転回転数の圧縮
機に適しているが、過給効果を有効に利用するための最
適な回転数領域ということについて配慮されていないも
のであった。However, although this conventional technique is suitable for a compressor having a constant rotation speed, it does not consider the optimum rotation speed region for effectively utilizing the supercharging effect.
本発明は、上記従来技術の問題点を解決するためにな
されたもので、回転数が変化する圧縮機において、最高
回転数より低い回転数における過給効果を有効利用し、
その低めの回転数で最高回転数と同じ冷力を得て圧縮機
の効率を向上させうる過給式圧縮機を提供することを目
的とする。The present invention has been made in order to solve the above-mentioned problems of the prior art, and in a compressor in which the rotation speed changes, effectively utilizing the supercharging effect at a rotation speed lower than the maximum rotation speed
An object of the present invention is to provide a supercharged compressor that can obtain the same cooling power as the maximum rotation speed at the lower rotation speed and improve the efficiency of the compressor.
［問題点を解決するための手段］ 上記目的を達成するために、本発明に係る過給式圧縮
機の構成は、回転数制御される電動機部と、圧縮機部
と、吸込側に設けたアキュムレータとを有する過給式圧
縮機において、前記アキュムレータ内に開口する圧縮機
の吸込配管の、その開口部から圧縮機吸込口までの吸込
配管長さを、前記圧縮機の最高回転数より1500〜2000rp
m低い回転数領域で当該吸込配管が共鳴するように設定
したものである。[Means for Solving the Problems] In order to achieve the above object, the configuration of the supercharged compressor according to the present invention is provided with a motor part whose rotation speed is controlled, a compressor part, and a suction side. In a supercharged compressor having an accumulator, the suction pipe of the compressor opened in the accumulator, the suction pipe length from the opening to the compressor suction port, 1500 ~ from the maximum rotation speed of the compressor 2000rp
m The suction pipe is set to resonate in the low rotation speed region.
より詳しくは、上記目的は、圧縮機の吸込側に最高回
転数より1500〜2000rpm低い回転数領域で共鳴効果と慣
性効果が最大となる過給手段を設けることにより達成さ
れる。すなわち、圧縮機の吸込配管長さＬ（ｍ）は、圧
縮機の最高回転数をNmax（rpm）、押除量をＶ（m3）、
吸込配管の断面積をAs（m2）、冷媒の音速をＣ（m/s）
としたとき、 ただし、Nc＝1500〜2000（rpm）とするものである。More specifically, the above object is achieved by providing the suction side of the compressor with a supercharging means that maximizes the resonance effect and the inertial effect in the rotational speed range of 1500 to 2000 rpm lower than the maximum rotational speed. That is, the suction pipe length L (m) of the compressor is the maximum rotation speed of the compressor is Nmax (rpm), the pushing amount is V (m 3 ),
The cross-sectional area of the suction pipe is As (m 2 ) and the sonic velocity of the refrigerant is C (m / s)
And when However, Nc = 1500 to 2000 (rpm).
［作用］ 上記技術手段の働きを第１図ないし第４図を参照して
説明する。[Operation] The operation of the above technical means will be described with reference to FIGS. 1 to 4.
第１図は、本発明の一実施例に係る過給式ロータリ圧
縮機の縦断面図、第２図は、第１図の圧縮機における吸
込室の体積変化を示す線図、第３図は、慣性効果による
充てん効率の変化を示す線図、第４図は、第１図の圧縮
機における回転数変化にともなう圧縮効率線図である。1 is a longitudinal sectional view of a supercharged rotary compressor according to an embodiment of the present invention, FIG. 2 is a diagram showing a volume change of a suction chamber in the compressor of FIG. 1, and FIG. FIG. 4 is a diagram showing a change in filling efficiency due to an inertial effect, and FIG. 4 is a compression efficiency diagram with a change in rotation speed in the compressor shown in FIG.
第１図に示すように、ロータリ圧縮機の吸込側は、圧
縮機に液冷媒が吸入されるのを防止するためのアキュム
レータ13、アキュムレータ内から圧縮機の吸込口までを
つなぐ吸込パイプ14、圧縮機構部３などからなる。回転
軸４が回転すると、吸込行程での吸込室の容積は第２図
に示すように変化し、吸込行程にはいると吸込室内の圧
力が低下するため、吸込パイプ14内の冷媒ガスは圧縮機
構部へむかって加速され始める。加速された冷媒ガスは
慣性力を与えられ、吸込行程終了時に余分に押し込ま
れ、第３図に示すように圧縮機の充てん効率が向上す
る。As shown in FIG. 1, the suction side of the rotary compressor includes an accumulator 13 for preventing liquid refrigerant from being sucked into the compressor, a suction pipe 14 connecting the inside of the accumulator to a suction port of the compressor, The mechanical unit 3 and the like. When the rotary shaft 4 rotates, the volume of the suction chamber in the suction stroke changes as shown in FIG. 2, and the pressure in the suction chamber lowers in the suction stroke, so that the refrigerant gas in the suction pipe 14 is compressed. Acceleration begins toward the mechanical section. The accelerated refrigerant gas is given an inertial force and excessively pushed in at the end of the suction stroke, so that the filling efficiency of the compressor is improved as shown in FIG.
なお、ここに充てん効率とは、設計上の吸込質量（理
論押除量に比重を掛けたもの）に対する実際上の吸込質
量の比である。Here, the filling efficiency is the ratio of the actual suction mass to the designed suction mass (theoretical push amount multiplied by the specific gravity).
このような慣性力による過給効果、すなわち慣性効果
は、圧縮機の回転速度が大きく吸込ガスの流入速度が大
きいほど効果が増大する傾向となる。The supercharging effect due to the inertial force, that is, the inertial effect, tends to increase as the compressor rotation speed increases and the suction gas inflow speed increases.
一方、ロータリ圧縮機は冷媒ガスを間けつ的に吸引す
るので、吸込パイプ14内では流速が周期的に変化し、管
内の圧力も周期的に変動する。吸込パイプ14の圧力変動
の固有振動数と吸込の回数とが一致して共振すると、共
振により生じた圧力波の正の部分が吸込室内に閉じ込め
られて、充てん効率が増大する過給現象が生ずる。On the other hand, since the rotary compressor sucks the refrigerant gas intermittently, the flow velocity in the suction pipe 14 changes periodically, and the pressure in the pipe also changes periodically. When the natural frequency of the pressure fluctuation of the suction pipe 14 and the number of suction coincide with each other and resonate, the positive portion of the pressure wave generated by the resonance is confined in the suction chamber, and a supercharging phenomenon occurs in which the filling efficiency is increased. .
このときの吸込配管系の共鳴周波数ｆ（H2）は次の
（１）式で表わされる。The resonance frequency f (H 2 ) of the suction piping system at this time is expressed by the following equation (1).
ただし、ｍ＝1,2,3,…… C:冷媒の音速（m/s） L:吸込配管長さ（ｍ） V:押除量（m3） As:吸込配管の断面積（m2） 吸込配管系の共振によって充てん効率が向上する現象
を共鳴効果と呼び、実際の圧縮機の過給は前述した慣性
効果と共鳴効果が重畳したものである。 However, m = 1,2,3, ... C: Sonic velocity of refrigerant (m / s) L: Suction pipe length (m) V: Pushing amount (m 3 ) As: Suction pipe cross-sectional area (m 2 The phenomenon that the filling efficiency is improved by the resonance of the suction pipe system is called the resonance effect, and the actual supercharging of the compressor is a superposition of the inertia effect and the resonance effect described above.
したがって、回転数制御のロータリ圧縮機で過給効果
を高めるには、吸込冷媒ガス流速が大きい高速回転域で
吸込配管の共振を生じさせるのが最も効果的である。Therefore, in order to enhance the supercharging effect in the rotational speed controlled rotary compressor, it is most effective to cause the suction pipe to resonate in the high speed rotation region where the suction refrigerant gas flow velocity is high.
また、過給効果の生ずる回転数領域は、共振周波数ｆ
と一致する回転数をNf（rpm）とすると、第４図に示す
ように、Nf（rpm）を頂点として、その前後±1500〜200
0（rpm）である。本発明のように吸込配管長さをＬを設
定すれば、（１）式より Nf＝Nmax−Nc （Nc＝1500〜2000rpm） となり、第４図にハッチングで示すように慣性効果が大
きく高速領域で共鳴効果を生じさせ、有効過給領域も30
00〜4000rpmと広くできるので、過給効果を有効利用す
ることが可能である。In addition, the rotation speed region in which the supercharging effect occurs is the resonance frequency f
Assuming that the number of revolutions that coincides with N f (rpm) is N f (rpm) as the apex, as shown in FIG.
It is 0 (rpm). By setting the L suction pipe length as in the present invention, (1) N f = Nmax -Nc (Nc = 1500~2000rpm) becomes from the equation, the inertial effect is large and fast as indicated by hatching in FIG. 4 Creates a resonance effect in the area, and the effective supercharging area is also 30
Since it can be as wide as 00 to 4000 rpm, it is possible to effectively use the supercharging effect.
また、液冷媒が流入した際には、第１図に示すアキュ
ムレータ13内底部に液冷媒は溜まる構造となっており、
吸込パイプ14に直接液冷媒は吸い込まれないため、液圧
縮による騒音増大や信頼性の低下の虞れはない。Further, when the liquid refrigerant flows in, it has a structure in which the liquid refrigerant accumulates at the inner bottom portion of the accumulator 13 shown in FIG.
Since the liquid refrigerant is not directly sucked into the suction pipe 14, there is no risk of noise increase and reliability deterioration due to liquid compression.
［実施例］ 以下、本発明の一実施例を第１図および第５図を参照
して説明する。[Embodiment] An embodiment of the present invention will be described below with reference to FIGS. 1 and 5.
ここに、第５図は、第１図の圧縮機の回転数変化にと
もなう特性線図である。Here, FIG. 5 is a characteristic diagram with changes in the rotational speed of the compressor shown in FIG.
第１図の図中、先の第６図と同一符号のものは従来技
術と同等部分であるから、その説明を省略する。In the drawing of FIG. 1, the same reference numerals as those in FIG. 6 above are the same parts as those in the prior art, and therefore the description thereof will be omitted.
第１図に示すロータリ圧縮機は、吸込側にアキュムレ
ータ13を備え、吸込パイプ14はアキュムレータ13内に開
口している。そして、その開口部から圧縮機構部の吸込
口までの吸込配管長さＬを、次に述べるように設定して
いる。すなわち、 最高回転数Nmax＝12000rpm、 押除量Ｖ＝９cm3、 吸込パイプ14の断面積As＝1.0cm2、 冷媒の音速Ｃ＝170m/s、 Nc＝2000rpmとし、 吸込配管長さＬを下式により、 に設定したものである。The rotary compressor shown in FIG. 1 is equipped with an accumulator 13 on the suction side, and a suction pipe 14 is open in the accumulator 13. The suction pipe length L from the opening to the suction port of the compression mechanism is set as described below. That is, the maximum rotation speed Nmax = 12000 rpm, the pushing amount V = 9 cm 3 , the cross-sectional area of the suction pipe 14 As = 1.0 cm 2 , the sonic velocity of the refrigerant C = 170 m / s, Nc = 2000 rpm, and the suction pipe length L By the formula, Is set to.
このように吸込配管長さＬを設定すると、（１）式に
より、吸込パイプ14の共鳴周波数ｆは、166（Hz）とな
り、最高回転数より約2000rpm低い10000rpmで共鳴によ
る過給効果を得ることができる。When the suction pipe length L is set in this way, the resonance frequency f of the suction pipe 14 becomes 166 (Hz) according to the equation (1), and the supercharging effect by resonance can be obtained at 10000 rpm, which is about 2000 rpm lower than the maximum rotation speed. You can
第５図に、本実施例のロータリ圧縮機を運転した場合
の圧縮機回転数と、圧縮機冷力，容積効率ηv，断熱効
率ηadとの関係を測定した結果を示す。FIG. 5 shows the results of measurement of the relationship among the compressor rotation speed when the rotary compressor of the present embodiment is operated, and the compressor cooling power, volumetric efficiency η v , and adiabatic efficiency η ad .
圧縮機回転数を増加させてゆくと、回転数の上昇にと
もない冷力は比例して増加するが、7500rpm付近から過
給現象が生じ始め、容積効率ηvは急激に増加し、それ
にともない冷力も急増する。As the number of revolutions of the compressor increases, the cooling power increases in proportion to the increase in the number of revolutions.However, the supercharging phenomenon begins to occur at around 7500 rpm, and the volumetric efficiency η v sharply increases. Power also increases sharply.
この過給効果は、第５図に斜線部で示す有効過給領域
のように、吸込パイプ14の共鳴周波数と圧縮機回転数と
が一致する10000rpm付近で最大となり、それ以上では減
少する傾向を示すが、最高回転数12000rpmまでの広い領
域にわたって過給効果を得ることができる。This supercharging effect becomes maximum near 10000 rpm where the resonance frequency of the suction pipe 14 and the compressor speed match, as in the effective supercharging area shown by the shaded area in FIG. As shown, the supercharging effect can be obtained over a wide range up to the maximum rotation speed of 12000 rpm.
一般に共鳴効果は、圧縮機回転数の低速域では有効過
給領域の幅，高さが小さく、高速域では、慣性効果があ
るので共鳴効果の有効過給領域の幅，高さも大きくな
り、高速側で過給効果を利用するのが有効である。In general, the resonance effect has a small width and height of the effective supercharging region in the low speed region of the compressor speed, and has an inertial effect in the high speed region, so that the width and height of the effective supercharging region of the resonance effect also become large, and the high speed It is effective to use the supercharging effect on the side.
また、過給を生じさせることにより、第５図に破線で
示した過給なしの場合にくらべ、同一冷力を得るために
必要な回転数は低くて良く、圧縮機の効率を高めること
ができる。すなわち、過給なしの場合に12000rpmで得ら
れた冷力（Ａ点）を過給を生じさせた場合は約10500rpm
（Ｂ点）付近で得ることができる。Further, by causing supercharging, the number of rotations required to obtain the same cooling power may be lower than that in the case without supercharging shown by the broken line in FIG. 5, and the efficiency of the compressor can be improved. it can. That is, when supercharging is performed, the cold power (point A) obtained at 12000 rpm without supercharging is about 10500 rpm.
It can be obtained near (point B).
一方、断熱効率ηadは高速になればなるほど、圧縮機
構部の摩擦損失や吸込，吐出の流動損失が増加するため
低下する傾向であるので、高速域ではより低い回転数で
使用した方が効率は良い。この場合は12000rpmから1000
0rpmに回転数を低く使用することにより効率を約３％向
上させることができる。On the other hand, the adiabatic efficiency η ad tends to decrease as the speed increases, because the friction loss of the compression mechanism and the flow loss of suction and discharge increase, so it is more efficient to use at a lower rotational speed in the high speed range. is good. In this case 12000 rpm to 1000
The efficiency can be improved by about 3% by using a low rotation speed at 0 rpm.
本実施例によれば、圧縮機の最高回転数より2000rpm
低い回転数に吸込パイプの共鳴周波数を合わせることに
より、慣性および共鳴による過給効果の大きい高速回転
域で過給を生じさせ、また過給有効領域も広くできるの
で、過給効率を有効利用でき、圧縮機の効率を高めるこ
とができると同時に液冷媒の流入による騒音の増加や信
頼性の低下を防止できる。According to the present embodiment, the maximum rotation speed of the compressor is 2000 rpm.
By adjusting the resonance frequency of the suction pipe to a low rotation speed, supercharging occurs in the high-speed rotation range where the effect of supercharging due to inertia and resonance is large, and the effective supercharging area can be widened, so supercharging efficiency can be used effectively. In addition, the efficiency of the compressor can be increased, and at the same time, the increase in noise and the decrease in reliability due to the inflow of the liquid refrigerant can be prevented.
なお、前述の実施例では、圧縮機の最高回転数より20
00rpm低い回転数に吸込パイプの共鳴周波数を合わせる
例を説明したが、本発明はNc＝2000（rpm）に限定され
るものではなく、Nc＝1500〜2000（rpm）の範囲を採用
すれば、有効過給領域の幅を3000〜4000rpmと広くで
き、前述の実施例と同様の効果を期待できるものであ
る。It should be noted that in the above-mentioned embodiment, the maximum rotation speed of the compressor is 20
Although an example in which the resonance frequency of the suction pipe is adjusted to a low rpm of 00 rpm has been described, the present invention is not limited to Nc = 2000 (rpm), and if the range of Nc = 1500 to 2000 (rpm) is adopted, The width of the effective supercharging region can be widened to 3000 to 4000 rpm, and the same effect as that of the above-described embodiment can be expected.
また、前述の実施例はロータリ圧縮機の例を説明した
が、本発明はこれに限定されるものではなく、同様の効
果が期待できる範囲で他の圧縮機にも適用可能なもので
ある。Further, although the above-described embodiment has described the example of the rotary compressor, the present invention is not limited to this, and is applicable to other compressors as long as the same effect can be expected.
［発明の効果］ 以上詳細に説明したように、本発明によれば、回転数
が変化する圧縮機において、最高回転数より低い回転数
における過給効果を有効利用し、その低めの回転数で最
高回転数と同じ冷力を得て圧縮機の効率を向上させうる
過給式圧縮機を提供することができる。[Effects of the Invention] As described in detail above, according to the present invention, in a compressor whose rotational speed changes, the supercharging effect at a rotational speed lower than the maximum rotational speed is effectively used, and at a lower rotational speed. It is possible to provide a supercharged compressor that can obtain the same cooling power as the maximum rotation speed and improve the efficiency of the compressor.
第１図は、本発明の一実施例に係る過給式ロータリ圧縮
機の縦断面図、第２図は、第１図の圧縮機における吸込
室の体積変化を示す線図、第３図は、慣性効果による充
てん効率の変化を示す線図、第４図は、第１図の圧縮機
における回転数変化にともなう容積効率線図、第５図
は、第１図の圧縮機の回転数変化にともなう特性線図、
第６図は、従来の過給式ロータリ圧縮機の縦断面図であ
る。 ２…電動機部、３…圧縮機構部、４…回転軸、13…アキ
ュムレータ、14…吸込パイプ。1 is a longitudinal sectional view of a supercharged rotary compressor according to an embodiment of the present invention, FIG. 2 is a diagram showing a volume change of a suction chamber in the compressor of FIG. 1, and FIG. FIG. 4 is a diagram showing a change in filling efficiency due to an inertial effect, FIG. 4 is a volumetric efficiency diagram with a change in rotation speed of the compressor shown in FIG. 1, and FIG. 5 is a change in rotation speed of the compressor shown in FIG. Characteristic diagram with
FIG. 6 is a vertical sectional view of a conventional supercharged rotary compressor. 2 ... electric motor part, 3 ... compression mechanism part, 4 ... rotary shaft, 13 ... accumulator, 14 ... suction pipe.
フロントページの続き (72)発明者 中村 庸藏 茨城県土浦市神立町502番地 株式会社 日立製作所機械研究所内 (56)参考文献 特開 昭57−122192（ＪＰ，Ａ)Front page continuation (72) Inventor, Yozo Nakamura, 502 Jinritsucho, Tsuchiura City, Ibaraki Prefecture Machinery Research Laboratory, Hitachi, Ltd. (56) Reference JP-A-57-122192 (JP, A)
Claims (2)
と、吸込側に設けたアキュムレータとを有する過給式圧
縮機において、前記アキュムレータ内に開口する圧縮機
の吸込配管の、その開口部から圧縮機吸込口までの吸込
配管長さを、前記圧縮機の最高回転数より1500〜2000rp
m低い回転数領域で当該吸込配管が共鳴するように設定
したことを特徴とする過給式圧縮機。1. A supercharged compressor having an electric motor part whose rotation speed is controlled, a compressor part, and an accumulator provided on a suction side, the opening of a suction pipe of the compressor opening in the accumulator. The suction pipe length from the section to the compressor suction port is 1500 to 2000rp from the maximum rotation speed of the compressor.
m A supercharged compressor characterized in that the suction pipe is set to resonate in a low rotation speed region.
て、圧縮機の吸込配管長さＬ（ｍ）は、圧縮機の最高回
転数をNmax（rpm）、押除量をＶ（m3）、吸込配管の断
面積をAs（m2）、冷媒の音速をＣ（m/s）としたとき、 ただし、Nc＝1500〜2000（rpm）としたことを特徴とす
る過給式圧縮機。2. The suction pipe length L (m) of the compressor according to claim 1, wherein the maximum rotation speed of the compressor is Nmax (rpm) and the pushing amount is V (m 3). ), The cross-sectional area of the suction pipe is As (m 2 ) and the sonic velocity of the refrigerant is C (m / s), However, the supercharged compressor is characterized in that Nc = 1500 to 2000 (rpm).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62167734A JP2501337B2 (en) | 1987-07-07 | 1987-07-07 | Supercharged compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62167734A JP2501337B2 (en) | 1987-07-07 | 1987-07-07 | Supercharged compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6415489A JPS6415489A (en) | 1989-01-19 |
| JP2501337B2 true JP2501337B2 (en) | 1996-05-29 |
Family
ID=15855149
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62167734A Expired - Fee Related JP2501337B2 (en) | 1987-07-07 | 1987-07-07 | Supercharged compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2501337B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008240666A (en) * | 2007-03-28 | 2008-10-09 | Fujitsu General Ltd | Rotary compressor and heat pump system |
| WO2012056728A1 (en) * | 2010-10-29 | 2012-05-03 | ダイキン工業株式会社 | Screw compressor |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57122192A (en) * | 1981-01-20 | 1982-07-29 | Mitsubishi Electric Corp | Rotary compressor |
-
1987
- 1987-07-07 JP JP62167734A patent/JP2501337B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6415489A (en) | 1989-01-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH0569381U (en) | Suction muffler for hermetic electric compressor | |
| CN2893214Y (en) | Closed compressor | |
| JP2501337B2 (en) | Supercharged compressor | |
| JPS5916113B2 (en) | Horizontal rotary compressor | |
| CN103591025B (en) | The turbo charged rotary compressor of band air-breathing | |
| JPH0631629B2 (en) | Rotary compressor | |
| JPH0474556B2 (en) | ||
| JP2629419B2 (en) | Hermetic rotary compressor | |
| CN2625604Y (en) | Two-cylinder two-stage compressing hinge swinging piston compressor | |
| CN206054306U (en) | Compression mechanism and the rotary compressor with which | |
| JPH05202875A (en) | Rotary compressor | |
| JPS647251Y2 (en) | ||
| JPS61155666A (en) | Refrigerant compressor | |
| JPS6113757Y2 (en) | ||
| CN209083480U (en) | A kind of frequency conversion refrigerator compressor | |
| CN206054304U (en) | Compression mechanism and the rotary compressor with which | |
| JPH0575915B2 (en) | ||
| JPH06307362A (en) | Rotary compressor | |
| JPH0124392Y2 (en) | ||
| JP3056450U (en) | Lightweight roots type rotor | |
| JPS5852394Y2 (en) | hermetic compressor | |
| JPH0223837Y2 (en) | ||
| JPS63230970A (en) | Compressor | |
| JPH051663Y2 (en) | ||
| JPS6231675Y2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |