JP2014105606A5 - - Google Patents
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- JP2014105606A5 JP2014105606A5 JP2012257840A JP2012257840A JP2014105606A5 JP 2014105606 A5 JP2014105606 A5 JP 2014105606A5 JP 2012257840 A JP2012257840 A JP 2012257840A JP 2012257840 A JP2012257840 A JP 2012257840A JP 2014105606 A5 JP2014105606 A5 JP 2014105606A5
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- port portion
- opening area
- downstream
- scroll
- upstream
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- 238000011144 upstream manufacturing Methods 0.000 claims description 32
- 239000003507 refrigerant Substances 0.000 claims description 14
- 238000007906 compression Methods 0.000 claims description 5
- 230000000694 effects Effects 0.000 description 4
- 239000002826 coolant Substances 0.000 description 2
- 210000001015 Abdomen Anatomy 0.000 description 1
- 230000000875 corresponding Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006011 modification reaction Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
Description
そこで本発明者は、構造物との共振を避けるように音響固有値を調整することに着目し、本発明を完成するに到った。
すなわち本発明のスクロール型圧縮機は、主軸の偏心軸部に回転自在に連結される旋回スクロールと、旋回スクロールと対向することで冷媒を圧縮する圧縮室を形成し、かつ圧縮された冷媒を高圧室に向けて吐出する吐出ポートが形成される端板を有する固定スクロールと、を備え、吐出ポートは、圧縮室に連なり、開口面積A1である上流ポート部と、上流ポート部に連なり、開口面積A2が上流ポート部の開口面積A1より大きい下流ポート部、とからなり、上流ポート部と下流ポート部の境界には、振動モードの腹が生じ、下流ポート部の開口面積A2は、上流ポート部の開口面積A1との関係で振動モードの腹が生じるように設定されることを特徴とする。
本発明のスクロール型圧縮機は、上流ポート部および下流ポート部の開口面積を互いに相違させることにより上流ポート部と下流ポート部の境界には振動モードの腹を生じさせることで、上述したL1の部分に上流ポート部のみが該当するようにした。このことは、上述した冷媒通路の距離Lを短くすることになり、公式(1)で求められる音響固有値を、構造物との共振が避けられるように高く調整できる。
Therefore, the present inventor has focused on adjusting the acoustic eigenvalue so as to avoid resonance with the structure, and has completed the present invention.
That is, the scroll type compressor of the present invention forms a turning scroll that is rotatably connected to the eccentric shaft portion of the main shaft, a compression chamber that compresses the refrigerant by facing the turning scroll, and the compressed refrigerant is high-pressure. A fixed scroll having an end plate on which a discharge port for discharging toward the chamber is formed . The discharge port is connected to the compression chamber, and is connected to the upstream port portion having an opening area A1 and the upstream port portion. the opening area A1 is greater than the downstream port of A2 is upstream port section consists city, a boundary of the upstream port unit and the downstream port unit, antinodes of vibration mode Ji live, the opening area A2 of the downstream port unit, upstream port It is set so that an antinode of vibration mode is generated in relation to the opening area A1 of the part .
The scroll compressor according to the present invention generates an antinode of vibration mode at the boundary between the upstream port portion and the downstream port portion by making the opening areas of the upstream port portion and the downstream port portion different from each other . Only the upstream port part is applicable to the part. This shortens the distance L of the refrigerant passage described above, and the acoustic eigenvalue obtained by the formula (1) can be adjusted high so as to avoid resonance with the structure.
本発明における吐出ポートは、いくつかの形態を包含する。
下流ポート部について、開口面積A2が冷媒の流れる向きで一定とすることができるし、段階的に又は連続的に拡大させることもできる。加工性の点で径の等しい円形のポートにすることが好ましい。
The discharge port in the present invention includes several forms.
About the downstream port part, opening area A2 can be made constant by the direction through which a refrigerant | coolant flows , and can also be expanded in steps or continuously. It is preferable to use a circular port with the same diameter in terms of workability.
本発明によれば、上流ポート部および下流ポート部の開口面積を異ならせることにより上流ポート部と下流ポート部の境界に振動モードの腹を生じさせて、冷媒通路の距離Lを短くすることにより、音響固有値を低く調整し、構造物との共振を避けることができる。したがって、本発明のスクロール型圧縮機は、混合冷媒を使用する際に生じる特定の周波数域の騒音を低減できる。 According to the present invention, by Rukoto with different opening area of the upstream port unit and the downstream port unit causes belly boundaries vibration mode of the upstream port unit and the downstream port unit, to shorten the distance L of the refrigerant passages Thus, the acoustic eigenvalue can be adjusted to be low and resonance with the structure can be avoided. Therefore, the scroll compressor according to the present invention can reduce noise in a specific frequency range that is generated when the mixed refrigerant is used.
本実施形態は、吐出ポート23が、冷媒の流れる向きF(図2(a))を基準として、上流側に位置する上流ポート部23Aと、上流ポート部23Aよりも下流側に位置する下流ポート部23Bから構成される。上流ポート部23Aは圧縮室PRに連なり、下流ポート部23Bは上流ポート部23Aに連なる。上流ポート部23Aは、図2(b)に示すように、開口形状が円形をしており、その開口面積をA1とする。また、下流ポート部23Bは、開口形状が扇型をしており、その開口面積をA2とする。本実施形態は、上流ポート部23Aの開口面積A1より、下流ポート部23Bの開口面積A2が大きい。しかも、この開口面積の相違に基づいて、上流ポート部23Aと下流ポート部23Bは、その境界部分に振動モードの腹が生じている。このように、吐出ポート23が、上流ポート部23Aと下流ポート部23Bからなることによる作用・効果については後述する。 In the present embodiment, the discharge port 23 has an upstream port portion 23A located on the upstream side and a downstream port located on the downstream side of the upstream port portion 23A with reference to the refrigerant flow direction F (FIG. 2A). It consists of part 23B. The upstream port portion 23A is continuous with the compression chamber PR, and the downstream port portion 23B is continuous with the upstream port portion 23A. As shown in FIG. 2B, the upstream port portion 23A has a circular opening shape, and the opening area is A1. Further, the downstream port portion 23B has a fan-shaped opening shape, and its opening area is A2. In the present embodiment, the opening area A2 of the downstream port portion 23B is larger than the opening area A1 of the upstream port portion 23A. Moreover, based on the difference in opening area, the upstream port portion 23A and the downstream port portion 23B have antinodes in the vibration mode at the boundary portion. Thus, the operation and effect of the discharge port 23 including the upstream port portion 23A and the downstream port portion 23B will be described later.
本実施形態は、固定スクロール20の吐出ポート23が、上述した上流ポート部23Aと下流ポート部23Bからなり、上流ポート部23Aの開口面積A1より下流ポート部23Bの開口面積A2が大きく、しかも、上流ポート部23Aと下流ポート部23Bは、その境界に振動モードの腹が生じている。そうすることによる作用・効果を図3をも参照して説明する。 In the present embodiment, the discharge port 23 of the fixed scroll 20 includes the upstream port portion 23A and the downstream port portion 23B described above, and the opening area A2 of the downstream port portion 23B is larger than the opening area A1 of the upstream port portion 23A. The upstream port portion 23A and the downstream port portion 23B have vibration mode antinodes at their boundaries. The action and effect by doing so will be described with reference to FIG.
はじめに、図3(b)に示す開口面積が一定の従来の吐出ポート123について説明する。この開口面積を、本実施形態の上流ポート部23Aと同じA1とする。つまり、吐出ポート123は、本実施形態の上流ポート部23Aが下流側の末端まで繋がっているものと同等である。
図3(b)において、下記の式(1)にける波長λは、下記で定義されるL1’,L2’,L3’の合計値で特定される。従来の吐出ポート123を適用する場合、流路C1’と流路C2’は振動モードが連続的であるが、流路C3’はそれよりも上流側の流路C1及び流路C2とはその境界に振動モードの腹が生じる。そして、流路C1’と流路C2’の合計の長さL’(L1’+L2’)は、境界条件を考慮すると、λ=4L’となる。前述したように、R410A,407C等の混合冷媒の冷媒流路における音速は、160〜180m/s程度であり、固定端板の厚さ(L2’)が10〜20mm、スクロール歯丈(L1’)が10〜20mmとすると、音響固有値(f)は1〜2kHzとなる(c=160m/sとした場合)。しかしこれでは、構造物との共振が生じうる。
First, a conventional discharge port 123 having a constant opening area shown in FIG. This opening area is set to A1 which is the same as the upstream port portion 23A of the present embodiment. That is, the discharge port 123 is the same as that in which the upstream port portion 23A of the present embodiment is connected to the downstream end.
In FIG. 3B, the wavelength λ in the following equation (1) is specified by the total value of L1 ′, L2 ′, and L3 ′ defined below. When the conventional discharge port 123 is applied, the vibration mode is continuous between the flow path C1 ′ and the flow path C2 ′, but the flow path C3 ′ is the same as the flow path C1 and the flow path C2 on the upstream side. An antinode of vibration mode occurs at the boundary. Then, the total length L ′ (L1 ′ + L2 ′) of the channel C1 ′ and the channel C2 ′ is λ = 4L ′ in consideration of boundary conditions. As described above, the speed of sound in the refrigerant flow path of the mixed refrigerant such as R410A and 407C is about 160 to 180 m / s, the thickness (L2 ′) of the fixed end plate is 10 to 20 mm, the scroll tooth height (L1 ′). ) Is 10 to 20 mm, the acoustic eigenvalue (f) is 1 to 2 kHz (when c = 160 m / s). However, this can cause resonance with the structure.
そこで、本実施形態の図3(a)に示すように、吐出ポート23の開口を途中から大きく拡張させ、上流ポート部23Aまでと下流ポート部23B以降との間に振動モードの腹を生じさせる。そうすると、従来のL’に相当するLが短くなるので、音響固有値(f)を上げることができ、したがって、構造物との共振を避けることができる。例えば、固定端板21の厚さの1/4の位置から下流ポート部23Bを形成したとすると、音響固有値(f)は1.6〜3.2kHzとなる。 Therefore, as shown in FIG. 3A of the present embodiment, the opening of the discharge port 23 is greatly expanded from the middle, and an antinode of vibration mode is generated between the upstream port portion 23A and the downstream port portion 23B. . Then, since L corresponding to conventional L ′ is shortened, the acoustic eigenvalue (f) can be increased, and resonance with the structure can be avoided. For example, if the downstream port portion 23B is formed from a position that is ¼ of the thickness of the fixed end plate 21, the acoustic eigenvalue (f) is 1.6 to 3.2 kHz.
本実施形態において、下流ポート部23Bの開口面積A2は、上流ポート部23Aの開口面積A1との関係で振動モードの腹が生じるように設定される。また、上流ポート部23Aの長さL2は、周囲の構造物の振動を考慮して、構造物との共振を避けることができる音響固有値(f)が得られるように設定される。いずれも、シミュレーションによる振動試験を行えば求めることができる。 In the present embodiment, the opening area A2 of the downstream port portion 23B is set so as to cause vibration mode antinodes in relation to the opening area A1 of the upstream port portion 23A. The length L2 of the upper flow ports 23 A, considering the vibration of the surrounding structure, the acoustic eigenvalue can avoid resonance with structure (f) is set so as to obtain. Both can be obtained by performing a vibration test by simulation.
Claims (5)
前記旋回スクロールと対向することで冷媒を圧縮する圧縮室を形成し、かつ圧縮された前記冷媒を高圧室に向けて吐出する吐出ポートが形成される端板を有する固定スクロールと、を備え、
前記吐出ポートは、
前記圧縮室に連なり、開口面積A1である上流ポート部と、
前記上流ポート部に連なり、開口面積A2が前記上流ポート部の前記開口面積A1より大きい下流ポート部、とからなり、前記上流ポート部と前記下流ポート部の境界には、振動モードの腹が生じ、
前記下流ポート部の前記開口面積A2は、前記上流ポート部の前記開口面積A1との関係で前記振動モードの前記腹が生じるように設定される、
ことを特徴とするスクロール型圧縮機。 An orbiting scroll rotatably connected to the eccentric shaft portion of the main shaft,
A fixed scroll having an end plate that forms a compression chamber that compresses the refrigerant by facing the orbiting scroll and that has a discharge port that discharges the compressed refrigerant toward the high-pressure chamber;
The discharge port is
An upstream port portion connected to the compression chamber and having an opening area A1,
Continuous with the upstream port portion, the opening area A1 is greater than the downstream port of the opening area A2 is the upstream port section consists city, a boundary of the said downstream ports and the upstream port unit, antinodes of vibration mode raw Flip,
The opening area A2 of the downstream port portion is set so that the antinode of the vibration mode occurs in relation to the opening area A1 of the upstream port portion.
A scroll compressor characterized by that.
前記開口面積A2が、前記冷媒の流れる向きで一定である、
請求項1に記載のスクロール型圧縮機。 The downstream port portion is
The opening area A2 is constant in the direction in which the refrigerant flows .
The scroll compressor according to claim 1.
前記開口面積A2が、段階的に又は連続的に拡大する、 The opening area A2 expands stepwise or continuously,
請求項1に記載のスクロール型圧縮機。The scroll compressor according to claim 1.
開口形状が円形又は扇形である、 The opening shape is circular or fan-shaped,
請求項1〜3のいずれか一項に記載のスクロール型圧縮機。The scroll type compressor according to any one of claims 1 to 3.
開口形状が円形である、 The opening shape is circular,
請求項1〜4のいずれか一項に記載のスクロール型圧縮機。The scroll type compressor according to any one of claims 1 to 4.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012257840A JP5951456B2 (en) | 2012-11-26 | 2012-11-26 | Scroll compressor |
CN201380056491.5A CN104755762B (en) | 2012-11-26 | 2013-09-17 | Scroll compressor |
EP13856394.5A EP2918841A4 (en) | 2012-11-26 | 2013-09-17 | Scroll compressor |
PCT/JP2013/005482 WO2014080553A1 (en) | 2012-11-26 | 2013-09-17 | Scroll compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012257840A JP5951456B2 (en) | 2012-11-26 | 2012-11-26 | Scroll compressor |
Publications (3)
Publication Number | Publication Date |
---|---|
JP2014105606A JP2014105606A (en) | 2014-06-09 |
JP2014105606A5 true JP2014105606A5 (en) | 2016-03-17 |
JP5951456B2 JP5951456B2 (en) | 2016-07-13 |
Family
ID=50775751
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2012257840A Active JP5951456B2 (en) | 2012-11-26 | 2012-11-26 | Scroll compressor |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2918841A4 (en) |
JP (1) | JP5951456B2 (en) |
CN (1) | CN104755762B (en) |
WO (1) | WO2014080553A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP4043729A4 (en) * | 2019-10-11 | 2023-01-25 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Electric compressor |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5342183A (en) | 1992-07-13 | 1994-08-30 | Copeland Corporation | Scroll compressor with discharge diffuser |
JPH07269485A (en) * | 1994-03-31 | 1995-10-17 | Mitsubishi Heavy Ind Ltd | Compressor |
JPH08319963A (en) * | 1995-03-22 | 1996-12-03 | Mitsubishi Electric Corp | Scroll compressor |
JP2009167983A (en) * | 2008-01-18 | 2009-07-30 | Daikin Ind Ltd | Scroll compressor |
CN102016319B (en) * | 2008-04-22 | 2013-11-06 | 松下电器产业株式会社 | Scroll compressor |
JP2010065560A (en) * | 2008-09-09 | 2010-03-25 | Daikin Ind Ltd | Scroll compressor |
JP4775494B2 (en) * | 2010-02-15 | 2011-09-21 | ダイキン工業株式会社 | Scroll compressor |
JP5758112B2 (en) * | 2010-12-07 | 2015-08-05 | 三菱重工業株式会社 | Scroll compressor |
-
2012
- 2012-11-26 JP JP2012257840A patent/JP5951456B2/en active Active
-
2013
- 2013-09-17 WO PCT/JP2013/005482 patent/WO2014080553A1/en active Application Filing
- 2013-09-17 CN CN201380056491.5A patent/CN104755762B/en active Active
- 2013-09-17 EP EP13856394.5A patent/EP2918841A4/en not_active Withdrawn
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