JP2017194016A5 - - Google Patents
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- JP2017194016A5 JP2017194016A5 JP2016084924A JP2016084924A JP2017194016A5 JP 2017194016 A5 JP2017194016 A5 JP 2017194016A5 JP 2016084924 A JP2016084924 A JP 2016084924A JP 2016084924 A JP2016084924 A JP 2016084924A JP 2017194016 A5 JP2017194016 A5 JP 2017194016A5
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- JP
- Japan
- Prior art keywords
- flow
- flow path
- flow passage
- muffler
- rotary
- Prior art date
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- 239000012530 fluid Substances 0.000 claims description 9
- 238000007906 compression Methods 0.000 claims description 6
- 239000003507 refrigerant Substances 0.000 description 2
- 238000007599 discharging Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Description
本発明のロータリー圧縮機は、回転される回転軸と、回転軸に設けられるピストンロータおよびピストンロータが配置されるシリンダを有するロータリー式の圧縮機構と、回転軸の軸周りに配置されるマフラと、を備え、マフラは、圧縮機構により圧縮された流体を内側に受け入れるマフラ本体と、回転軸または回転軸の軸周りに位置する軸受部との間に、回転軸の軸方向に沿ってマフラの外部へと流体を流出させる所定の長さの吐出流路を形成する流路壁と、を備え、吐出流路は、回転軸の周方向の一部に位置する第1流路部と、周方向において第1流路部に隣接し、かつ、回転軸の径方向における寸法が第1流路部よりも大きく、第1流路部よりも断面積が大きい第2流路部と、を有し、第1流路部および第2流路部からそれぞれ流出した流体の圧力変動が干渉して打ち消し合うことを特徴とする。 The rotary compressor according to the present invention comprises a rotary compression mechanism having a rotary shaft, a piston rotor provided on the rotary shaft, and a cylinder on which the piston rotor is disposed, and a muffler disposed around the rotary shaft. The muffler is provided along the axial direction of the rotation axis between the muffler body that receives the fluid compressed by the compression mechanism inward and the bearing portion positioned around the rotation axis or the axis of the rotation axis. And a flow passage wall forming a discharge flow passage of a predetermined length for discharging the fluid to the outside, and the discharge flow passage includes a first flow passage portion positioned in a part of the circumferential direction of the rotation shaft; Adjacent to the first flow path portion in the direction, and the second flow path portion having a larger dimension in the radial direction of the rotation axis than the first flow path portion and a larger cross-sectional area than the first flow path portion Flow out of the first and second flow path portions. Wherein the pressure variation of the fluid are canceled by interference.
第2流路102の流速を基準とした流速比1/αにより、式(I)と等価な式を設定することもできる。その式を用いて、第1、第2流路部101,102を設計することも許容される。 An equation equivalent to equation (I) can also be set by the flow velocity ratio 1 / α based on the flow velocity of the second flow passage 102 . It is also permissible to design the first and second flow path portions 101 and 102 using the equation.
以下、上記の式(I)を得るプロセスについて説明する。
第1、第2流路部101,102への流入時の位相が同一、および振幅が同一の条件より、圧力変動p1,p2の波は式(i)により表される。tは時間、Pは圧力波の振幅、k1,k2は波数、ωは角周波数を示す。圧力変動p1,p2は、波数k1,k2のみが相違する。
p1(x,t)=Psin(k1x−ωt)
p2(x,t)=Psin(k2x−ωt) ・・・(i)
Hereinafter, the process for obtaining the above formula (I) will be described.
Under the conditions that the phases when flowing into the first and second flow path portions 101 and 102 are the same and the amplitudes are the same, the waves of the pressure fluctuations p 1 and p 2 are represented by equation (i). t represents time, P represents the pressure wave amplitude, k 1 and k 2 represent the wave number , and ω represents the angular frequency . The pressure fluctuations p 1 and p 2 differ only in the wavenumbers k 1 and k 2 .
p 1 (x, t) = P sin (k 1 x-ωt)
p 2 (x, t) = P sin (k 2 x-ωt) (i)
ここで、第1流路部101における冷媒の流速をv1、第2流路部102における冷媒の流速をv2と置くと、
v1=ω/k 1 v2=ω/k 2 ・・・(ii)
v1,v2のうち相対的に速いv1を基準とした流速比をαと置いて、
v1=αv2 (α>1)
式(ii)より、
k 2 =αk 1 ・・・(iii)
Here, v 1 the flow rate of refrigerant in the first flow path portion 101, when the flow rate of the refrigerant in the second flow path portion 102 puts the v 2,
v 1 = ω / k 1 v 2 = ω / k 2 (ii)
Assuming that the flow velocity ratio based on v 1 which is relatively faster among v 1 and v 2 is α,
v 1 = αv 2 (α> 1)
From equation (ii),
k 2 = α k 1 (iii)
Claims (8)
前記回転軸に設けられるピストンロータおよび前記ピストンロータが配置されるシリンダを有するロータリー式の圧縮機構と、
前記回転軸の軸周りに配置されるマフラと、を備え、
前記マフラは、
前記圧縮機構により圧縮された流体を内側に受け入れるマフラ本体と、
前記回転軸または前記回転軸の軸周りに位置する軸受部との間に、前記回転軸の軸方向に沿って前記マフラの外部へと前記流体を流出させる所定の長さの吐出流路を形成する流路壁と、を備え、
前記吐出流路は、
前記回転軸の周方向の一部に位置する第1流路部と、
前記周方向において前記第1流路部に隣接し、かつ、前記回転軸の径方向における寸法が前記第1流路部よりも大きく、前記第1流路部よりも断面積が大きい第2流路部と、を有し、
前記第1流路部および前記第2流路部からそれぞれ流出した前記流体の圧力変動が干渉して打ち消し合う、
ことを特徴とするロータリー圧縮機。 A rotating shaft that is rotated,
A rotary type compression mechanism having a piston rotor provided on the rotary shaft and a cylinder on which the piston rotor is disposed;
And a muffler disposed around the axis of the rotation axis,
The muffler is
A muffler body for receiving the fluid compressed by the compression mechanism inside;
Between the rotary shaft or a bearing portion positioned around the rotary shaft, a discharge flow passage of a predetermined length is formed to allow the fluid to flow out of the muffler along the axial direction of the rotary shaft. A flow passage wall, and
The discharge channel is
A first flow passage portion positioned in a part of a circumferential direction of the rotation shaft;
A second flow adjacent to the first flow passage in the circumferential direction and having a dimension in the radial direction of the rotation axis larger than that of the first flow passage and larger in cross-sectional area than the first flow passage possess a road section, the,
Pressure fluctuations of the fluid respectively flowing out from the first flow path portion and the second flow path portion interfere and cancel each other,
A rotary compressor characterized by
ことを特徴とする請求項1に記載のロータリー圧縮機。 The discharge flow path includes a plurality of the second flow path portions.
The rotary compressor according to claim 1, characterized in that:
ことを特徴とする請求項2に記載のロータリー圧縮機。 The cross-sectional area of each of the plurality of second flow path portions is different from each other,
The rotary compressor according to claim 2, characterized in that:
前記回転軸の軸周りの全周に亘り形成されており、
前記周方向において交互に配置される複数の前記第1流路部と複数の前記第2流路部とを有する、
ことを特徴とする請求項2または3に記載のロータリー圧縮機。 The discharge channel is
It is formed over the entire circumference around the axis of the rotation axis,
The plurality of first flow path portions and the plurality of second flow path portions alternately arranged in the circumferential direction
The rotary compressor according to claim 2 or 3, characterized in that:
ことを特徴とする請求項1から4のいずれか一項に記載のロータリー圧縮機。 The portion of the flow path wall that forms the second flow path portion is formed to have a substantially C-shaped cross section or a substantially V-shaped cross section.
The rotary compressor according to any one of claims 1 to 4, characterized in that.
前記回転軸に設けられるピストンロータおよび前記ピストンロータが配置されるシリンダを有するロータリー式の圧縮機構と、
前記回転軸の軸周りに配置されるマフラと、を備え、
前記マフラは、
前記圧縮機構により圧縮された流体を内側に受け入れるマフラ本体と、
前記回転軸または前記回転軸の軸周りに位置する軸受部との間に、前記回転軸の軸方向に沿って前記マフラの外部へと前記流体を流出させる所定の長さの吐出流路を形成する流路壁と、を備え、
前記吐出流路は、
前記回転軸の周方向の一部に位置する第1流路部と、
前記第1流路部よりも断面積が大きい第2流路部と、を有し、
前記第1流路部が、前記第2流路部から径方向外側に突出している、
ことを特徴とするロータリー圧縮機。 A rotating shaft that is rotated,
A rotary type compression mechanism having a piston rotor provided on the rotary shaft and a cylinder on which the piston rotor is disposed;
And a muffler disposed around the axis of the rotation axis,
The muffler is
A muffler body for receiving the fluid compressed by the compression mechanism inside;
Between the rotary shaft or a bearing portion positioned around the rotary shaft, a discharge flow passage of a predetermined length is formed to allow the fluid to flow out of the muffler along the axial direction of the rotary shaft. A flow passage wall, and
The discharge channel is
A first flow passage portion positioned in a part of a circumferential direction of the rotation shaft;
And a second flow passage portion having a cross-sectional area larger than that of the first flow passage portion,
The first channel portion protrudes radially outward from the second channel portion.
A rotary compressor characterized by
ことを特徴とする請求項6に記載のロータリー圧縮機。 Pressure fluctuations of the fluid respectively flowing out from the first flow path portion and the second flow path portion interfere and cancel each other,
The rotary compressor according to claim 6 , characterized in that:
前記第1流路部における流速をv1、
前記第2流路部における流速のv1に対する流速比をα、
所定の周波数をf、と置くと、
nが自然数であるとして、
α=n(v1/2fx0)+1
が成立する、
ことを特徴とする請求項1から7のいずれか一項に記載のロータリー圧縮機。 The length of the discharge channel is x 0 ,
The flow velocity in the first channel portion is v 1 ,
The flow velocity ratio of the flow velocity in the second flow passage to v 1 is α,
If you set the predetermined frequency f,
Assuming that n is a natural number,
α = n (v 1 / 2fx 0 ) +1
Is established,
The rotary compressor according to any one of claims 1 to 7 , characterized in that:
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016084924A JP6683532B2 (en) | 2016-04-21 | 2016-04-21 | Rotary compressor |
CN201780007733.XA CN108496009A (en) | 2016-04-21 | 2017-03-15 | Rotary compressor |
PCT/JP2017/010498 WO2017183367A1 (en) | 2016-04-21 | 2017-03-15 | Rotary compressor |
EP17785709.1A EP3399193A4 (en) | 2016-04-21 | 2017-03-15 | Rotary compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2016084924A JP6683532B2 (en) | 2016-04-21 | 2016-04-21 | Rotary compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
JP2017194016A JP2017194016A (en) | 2017-10-26 |
JP2017194016A5 true JP2017194016A5 (en) | 2019-05-09 |
JP6683532B2 JP6683532B2 (en) | 2020-04-22 |
Family
ID=60116029
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2016084924A Active JP6683532B2 (en) | 2016-04-21 | 2016-04-21 | Rotary compressor |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3399193A4 (en) |
JP (1) | JP6683532B2 (en) |
CN (1) | CN108496009A (en) |
WO (1) | WO2017183367A1 (en) |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH10176691A (en) * | 1996-12-17 | 1998-06-30 | Daikin Ind Ltd | Rotary compressor |
JP4215003B2 (en) * | 2005-02-04 | 2009-01-28 | ダイキン工業株式会社 | Compressor muffler structure |
CN202001312U (en) * | 2011-04-19 | 2011-10-05 | 上海日立电器有限公司 | Silencer for rotary compressor |
JP6148993B2 (en) * | 2014-02-21 | 2017-06-14 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
-
2016
- 2016-04-21 JP JP2016084924A patent/JP6683532B2/en active Active
-
2017
- 2017-03-15 WO PCT/JP2017/010498 patent/WO2017183367A1/en active Application Filing
- 2017-03-15 CN CN201780007733.XA patent/CN108496009A/en active Pending
- 2017-03-15 EP EP17785709.1A patent/EP3399193A4/en not_active Withdrawn
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