JP5207822B2 - Screw compressor - Google Patents

Screw compressor Download PDF

Info

Publication number
JP5207822B2
JP5207822B2 JP2008126784A JP2008126784A JP5207822B2 JP 5207822 B2 JP5207822 B2 JP 5207822B2 JP 2008126784 A JP2008126784 A JP 2008126784A JP 2008126784 A JP2008126784 A JP 2008126784A JP 5207822 B2 JP5207822 B2 JP 5207822B2
Authority
JP
Japan
Prior art keywords
seal portion
screw rotor
screw
bearing
radial
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.)
Active
Application number
JP2008126784A
Other languages
Japanese (ja)
Other versions
JP2009275567A (en
Inventor
聡一 白石
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2008126784A priority Critical patent/JP5207822B2/en
Publication of JP2009275567A publication Critical patent/JP2009275567A/en
Application granted granted Critical
Publication of JP5207822B2 publication Critical patent/JP5207822B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、例えば冷凍機の冷媒圧縮に用いられるスクリュー圧縮機に関する。   The present invention relates to a screw compressor used for refrigerant compression of a refrigerator, for example.

一般に、この種のスクリュー圧縮機は、ケーシング内にスクリューロータが配置され、スクリューロータの両側に軸直角に２本のゲートロータが配置されている。これらゲートロータは、スクリューロータのスクリュー溝と噛み合い、スクリューロータの歯面に沿って追随回転し、スクリューロータのスクリュー溝とケーシングとの間の空間を遮ってこの空間内の流体（例えば冷媒ガス）を圧縮する機能を有している。また、スクリューロータの軸の一端側（高圧側）は、軸受を介して軸受箱に支持されているとともに、スクリューロータの軸の他端側が、図示しないモータに連結されている。   Generally, in this type of screw compressor, a screw rotor is disposed in a casing, and two gate rotors are disposed at right angles to both sides of the screw rotor. These gate rotors mesh with the screw grooves of the screw rotor, rotate following the tooth surfaces of the screw rotor, block the space between the screw grooves of the screw rotor and the casing, and fluid (for example, refrigerant gas) in this space It has a function to compress. One end side (high pressure side) of the shaft of the screw rotor is supported by a bearing box via a bearing, and the other end side of the shaft of the screw rotor is connected to a motor (not shown).

したがって、モータの駆動によりスクリューロータが回転すると、スクリュー溝内に冷媒ガスが吸引され、吸引された冷媒ガスは、スクリューロータの歯面に沿って追随回転するゲートロータによりスクリュー溝に沿って圧縮され、圧縮機内部の吐出流路に吐出される。   Accordingly, when the screw rotor is rotated by driving the motor, the refrigerant gas is sucked into the screw groove, and the sucked refrigerant gas is compressed along the screw groove by the gate rotor that rotates following the tooth surface of the screw rotor. Then, it is discharged into a discharge flow path inside the compressor.

ところで、スクリュー圧縮機においては、運転時にスクリューロータのスクリュー溝が開口される吐出流路（外周部高圧域）側が高圧、軸受側がそれよりも低圧となり、それらの間に差圧が発生する。そのため、スクリューロータと軸受箱との間にシール部が設けられている。例えば、スクリューロータと軸受箱との間に、螺旋溝からなるスラストシール部および複数個の環状溝からなるラジアルシール部を備えた段付シール部を設け、吐出流路（外周部高圧域）側とそれよりも低圧の軸受側とを段付シール部によって区画するとともに、起動時等の過渡的な運転状態下で発生する逆圧現象、つまりスラストシール部の間隙圧力に対し低圧側の圧力が上昇する現象が発生しても、内外周が連続する螺旋溝により短時間のうちにスラストシール部の間隙圧力を上昇させて、逆圧に対向させ得るようにしたものがある（例えば、特許文献１参照）。   By the way, in a screw compressor, the discharge flow path (outer peripheral high-pressure region) side in which the screw groove of the screw rotor is opened during operation has a high pressure and the bearing side has a lower pressure, and a differential pressure is generated between them. Therefore, a seal portion is provided between the screw rotor and the bearing box. For example, between the screw rotor and the bearing housing, a stepped seal portion provided with a thrust seal portion made of a spiral groove and a radial seal portion made of a plurality of annular grooves is provided, and the discharge channel (outer peripheral high pressure region) side And the lower-pressure bearing side are separated by a stepped seal part, and the reverse pressure phenomenon that occurs under transient operating conditions such as startup, that is, the pressure on the low-pressure side against the gap pressure in the thrust seal part Even if the rising phenomenon occurs, there is one in which the gap pressure of the thrust seal portion can be raised in a short time by a spiral groove having continuous inner and outer peripheries to oppose the reverse pressure (for example, Patent Documents) 1).

特開平６−１０１６７２号公報（図１）JP-A-6-101672 (FIG. 1)

スクリュー圧縮機においては、スクリューロータのスクリュー溝が開口される吐出流路（外周部高圧域）側の高圧の流体がスクリューロータと軸受箱との間を通ってそれよりも低圧の軸受側に洩れだすと、圧縮機の性能が低下する。したがって、シールの目的に反するようにスラストシール部に常に吐出流路（外周部高圧域）側の圧力が作用するようにしたものにあっては、信頼性の点で難がある。   In screw compressors, high-pressure fluid on the discharge flow path (outer peripheral high-pressure region) side where the screw groove of the screw rotor is opened passes between the screw rotor and the bearing housing and leaks to the lower-pressure bearing side. If it does, the performance of a compressor will fall. Therefore, in the case where the pressure on the discharge flow channel (outer peripheral high pressure region) side is always applied to the thrust seal portion so as to be contrary to the purpose of the seal, there is a difficulty in terms of reliability.

ところで、シールの性能低下を抑制するには、スクリューロータと軸受箱との隙間を小さくすることが有効である。しかし、この場合、隙間を過度に小さくするとスクリューロータと軸受箱が焼きつく不具合が発生する可能性が高くなり、圧縮機の信頼性が低下する。このため、シール性能低下の改善が進まない状況にあった。   By the way, it is effective to reduce the gap between the screw rotor and the bearing box in order to suppress the deterioration of the seal performance. However, in this case, if the gap is excessively reduced, there is a high possibility that a problem that the screw rotor and the bearing box are burned out occurs, and the reliability of the compressor is lowered. For this reason, it was in the situation where improvement of a sealing performance fall did not progress.

本発明の技術的課題は、ラジアルシール部のシール機能を高めて、流体がスクリューロータの軸方向へ洩れだすことを防止することで、圧縮機の信頼性の向上を図ることができるようにすることにある。   The technical problem of the present invention is to improve the reliability of the compressor by enhancing the sealing function of the radial seal portion and preventing the fluid from leaking in the axial direction of the screw rotor. There is.

本発明に係るスクリュー圧縮機は、ケーシング内に回転自在に収容されたスクリューロータと、ケーシング内でスクリューロータの吐出側軸端部を囲繞し、軸受を介して支持する軸受箱と、軸受箱の開口縁とスクリューロータとの対向面に設けられてスクリューロータの外周部高圧域に対しこれよりも低圧の軸受箱の内部空間を区画するシール部とを備え、シール部に、スクリューロータと軸受箱とを径方向で対向させたラジアルシール部を設けて、このラジアルシール部の相対する面の一方に、スクリューロータの回転に伴って低圧側から外周部高圧域方向に流体を送ろうとする力を発生させる螺旋溝を設けるとともに、ラジアルシール部の相対する面の他方に、スクリューロータや軸受箱よりも軟らかい材質からなる被覆部材を設けたものである。 A screw compressor according to the present invention includes a screw rotor that is rotatably accommodated in a casing, a bearing box that surrounds a discharge-side shaft end portion of the screw rotor in the casing, and is supported via a bearing, A seal portion that is provided on the facing surface of the opening edge and the screw rotor and divides the inner space of the bearing box at a lower pressure than the high pressure region on the outer periphery of the screw rotor. And a radial seal portion that is opposed to each other in the radial direction, and a force to send a fluid from the low pressure side to the outer peripheral portion in the high pressure region along with the rotation of the screw rotor on one of the opposing surfaces of the radial seal portion. Rutotomoni provided occurrence cause spiral groove, the other opposing surface of the radial seal portion, also provided with a covering member made of soft material than the screw rotor and the bearing housing It is.

本発明に係るスクリュー圧縮機においては、スクリューロータと軸受箱とを径方向で対向させたラジアルシール部の相対する面の一方に、スクリューロータの回転に伴って低圧側から外周部高圧域方向に流体を送ろうとする力を発生させる螺旋溝を設けるとともに、ラジアルシール部の相対する面の他方に、スクリューロータや軸受箱よりも軟らかい材質からなる被覆部材を設けているので、スクリューロータが回転すると、ラジアルシール部に低圧側から外周部高圧域方向に流体を送ろうとする力が発生する。そのため、外周部高圧域側からラジアルシール部を通って低圧側へ洩れようとする流体は、低圧側の圧力に螺旋溝による流体を送ろうとする力がプラスされた圧力の抵抗を受け、その洩れる量が抑制される。また、ラジアルシール部の相対する面の他方に設けた、スクリューロータや軸受箱よりも軟らかい材質からなる被覆部材は、ラジアルシール部から流体が洩れだす隙間を小さくする。このため、洩れ量抑制効果を更に高めることができて、圧縮機の性能を一層向上させることができる。 In the screw compressor according to the present invention, the radial surface of the radial seal portion facing the screw rotor and the bearing box is opposed to one of the opposing surfaces of the radial direction from the low pressure side to the outer peripheral high pressure region. Rutotomoni provided a spiral groove which makes generating a force to send fluid, the other opposing surface of the radial seal portion, since the provided cover member made of soft material than the screw rotor and the bearing housing, the screw rotor is rotated Then, a force is generated in the radial seal portion to send the fluid from the low pressure side toward the outer peripheral portion high pressure region. Therefore, the fluid that tries to leak from the outer peripheral high-pressure region side to the low-pressure side through the radial seal portion is subjected to pressure resistance in which the force to send the fluid by the spiral groove is added to the low-pressure side pressure. The amount is suppressed. Further, the covering member made of a material softer than the screw rotor and the bearing box provided on the other of the opposing surfaces of the radial seal portion reduces a gap through which fluid leaks from the radial seal portion. For this reason, the leakage suppression effect can be further enhanced and the performance of the compressor can be further improved.

実施の形態１．
以下、図示実施形態により本発明を説明する。
図１は本発明の実施の形態１に係るスクリュー圧縮機のシール部周辺の一部断面表示を含む構造図、図２は図１のシール部Ａを拡大して示す断面図である。 Embodiment 1 FIG.
The present invention will be described below with reference to illustrated embodiments.
FIG. 1 is a structural view including a partial cross-sectional display around a seal portion of a screw compressor according to Embodiment 1 of the present invention, and FIG. 2 is an enlarged cross-sectional view showing a seal portion A in FIG.

本実施形態のスクリュー圧縮機は、図１のようにケーシング６と、ケーシング６内に配置されたスクリューロータ１と、スクリューロータ１の一端側（高圧側）の軸端部７を軸受８を介して支持する軸受箱２とを備えている。   As shown in FIG. 1, the screw compressor of the present embodiment includes a casing 6, a screw rotor 1 disposed in the casing 6, and a shaft end 7 on one end side (high pressure side) of the screw rotor 1 via a bearing 8. And a bearing box 2 to be supported.

スクリューロータ１は、複数条のスクリュー溝９を有し、これらスクリュー溝９にはスクリューロータ１の両側に軸直角に配置された２本のゲートロータ（一方のみ示す）１０が噛み合っている。ゲートロータ１０は、周知のようにスクリューロータ１の歯面に沿って追随回転し、スクリューロータ１のスクリュー溝９とケーシング６との間の空間を遮ってこの空間内の流体（例えば冷媒ガス）を圧縮する機能を有する。スクリューロータ１の他端部の軸部は、図示しないモータに連結されている。   The screw rotor 1 has a plurality of screw grooves 9, and two gate rotors (only one is shown) 10 arranged at right angles to the both sides of the screw rotor 1 are engaged with the screw grooves 9. As is well known, the gate rotor 10 rotates following the tooth surface of the screw rotor 1 to block the space between the screw groove 9 of the screw rotor 1 and the casing 6, and fluid (for example, refrigerant gas) in this space. Has a function of compressing. The shaft portion at the other end of the screw rotor 1 is connected to a motor (not shown).

また、スクリューロータ１と軸受箱２の開口縁との間にシール部Ａが設けられている。シール部Ａは、図２のようにスクリューロータ１と軸受箱２とを径方向で対向させたラジアルシール部Ｂと、ラジアルシール部Ｂに連続しスクリューロータ１と軸受箱２とを軸方向で対向させたスラストシール部Ｃとからなる段付シール状に形成されている。   Further, a seal portion A is provided between the screw rotor 1 and the opening edge of the bearing housing 2. As shown in FIG. 2, the seal part A includes a radial seal part B in which the screw rotor 1 and the bearing box 2 are opposed to each other in the radial direction, and a radial seal part B continuous with the screw rotor 1 and the bearing box 2 in the axial direction. It is formed in the shape of a stepped seal comprising an opposed thrust seal portion C.

これを更に詳述すると、ラジアルシール部Ｂは、相対する面の一方、ここでは軸受箱２側の面に、スクリューロータ１の回転に伴って低圧側（軸受８側）から外周部高圧域方向、つまり運転時にスクリューロータ１のスクリュー溝９が開口される吐出流路１１の方向に揚力を発生する螺旋溝４を設けたものである。   More specifically, the radial seal portion B is arranged on one of the opposing surfaces, here the surface on the bearing housing 2 side, from the low pressure side (bearing 8 side) to the outer peripheral portion high pressure region direction as the screw rotor 1 rotates. That is, the spiral groove 4 for generating lift is provided in the direction of the discharge flow path 11 in which the screw groove 9 of the screw rotor 1 is opened during operation.

スラストシール部Ｃは、相対する面の一方、ここでは軸受箱２側の面に、同心円状の複数個の環状溝３から成るラビリンスを設けたものである。   The thrust seal portion C is provided with a labyrinth composed of a plurality of concentric annular grooves 3 on one of the opposing surfaces, here the surface on the bearing housing 2 side.

以上のように構成された本実施形態のスクリュー圧縮機において、モータの駆動によりスクリューロータ１が回転すると、スクリュー溝９内に冷媒ガスが吸引され、吸引された冷媒ガスは、スクリューロータ１の歯面に沿って追随回転するゲートロータ１０によりスクリュー溝９に沿って圧縮され、圧縮機内部の吐出流路１１に吐出される。   In the screw compressor of the present embodiment configured as described above, when the screw rotor 1 is rotated by driving the motor, the refrigerant gas is sucked into the screw groove 9, and the sucked refrigerant gas is absorbed by the teeth of the screw rotor 1. It is compressed along the screw groove 9 by the gate rotor 10 that rotates following the surface, and is discharged to the discharge flow path 11 inside the compressor.

本実施形態に係るスクリュー圧縮機においては、スクリューロータと軸受箱とを径方向で対向させたラジアルシール部の相対する面の一方に、スクリューロータの回転に伴って低圧側から外周部高圧域方向に揚力を発生する螺旋溝４を設けているので、スクリューロータ１の回転時、ラジアルシール部Ｂでは、螺旋溝４の側壁による搬送機能によって低圧側から外周部高圧域方向に流体を送ろうとする力が発生する。そのため、外周部高圧域側からラジアルシール部Ｂを通って低圧側へ洩れようとする流体は、低圧側の圧力に螺旋溝４による揚力がプラスされた圧力の抵抗を受け、その洩れる量が抑制される。このため、圧縮機の性能が向上する。   In the screw compressor according to the present embodiment, the radial direction from the low pressure side to the outer peripheral high pressure region along with the rotation of the screw rotor on one of the opposing surfaces of the radial seal portion in which the screw rotor and the bearing housing are opposed in the radial direction. Since the spiral groove 4 for generating lift is provided in the radial seal portion B, when the screw rotor 1 rotates, the fluid is sent from the low pressure side to the outer peripheral portion high pressure region by the transfer function by the side wall of the spiral groove 4. Force is generated. Therefore, the fluid that tries to leak to the low pressure side through the radial seal portion B from the outer peripheral high pressure region side receives the resistance of the pressure obtained by adding the lift by the spiral groove 4 to the low pressure side pressure, and the amount of leakage is suppressed. Is done. For this reason, the performance of the compressor is improved.

なお、ここでは軸受箱２側の面にラジアルシール部Ｂの螺旋溝４とスラストシール部Ｃの環状溝３を設けたものを例に挙げて説明したが、これら螺旋溝４と環状溝３をスクリューロータ１側の面に設けてもよいことは言うまでもない。   Here, the description has been given by taking as an example the case where the spiral groove 4 of the radial seal portion B and the annular groove 3 of the thrust seal portion C are provided on the surface on the bearing housing 2 side. Needless to say, it may be provided on the surface of the screw rotor 1.

実施の形態２．
図３は本発明の実施の形態２に係るスクリュー圧縮機の要部であるシール部を拡大して示す断面図であり、図中、前述の実施形態１と同一部分には同一符号を付してある。なお、説明にあたっては前述の図１を参照するものとする。 Embodiment 2. FIG.
FIG. 3 is an enlarged cross-sectional view showing a seal part, which is a main part of the screw compressor according to the second embodiment of the present invention. In the figure, the same parts as those in the first embodiment are denoted by the same reference numerals. It is. In the description, reference is made to FIG.

本実施形態のスクリュー圧縮機は、図３のようにラジアルシール部Ｂの相対する面の他方、つまりスクリューロータ１側の面に、スクリューロータ１や軸受箱２よりも軟らかい材質（例えばリン酸マンガンやニッケルグラファイトなど）からなる被覆部材５を設けるとともに、スラストシール部Ｃの相対する面の他方、つまりスクリューロータ１側の面にも、連続させて被覆部材５を形成し、これらラジアルシール部Ｂ及びスラストシール部Ｃから流体が洩れだす隙間を小さくしたものである。それ以外の構成は、全て前述の実施形態１と同一であり、実施形態１の持つ機能を全て備えている。   As shown in FIG. 3, the screw compressor of the present embodiment is made of a material softer than the screw rotor 1 or the bearing housing 2 (for example, manganese phosphate) on the other side of the radial seal portion B, that is, the surface on the screw rotor 1 side. And the covering member 5 is formed continuously on the other of the opposing surfaces of the thrust seal portion C, that is, the surface on the screw rotor 1 side, and these radial seal portions B are provided. In addition, the gap through which fluid leaks from the thrust seal portion C is reduced. All other configurations are the same as those of the first embodiment described above, and all the functions of the first embodiment are provided.

本実施形態のスクリュー圧縮機においては、被覆部材５によってラジアルシール部Ｂ及びスラストシール部Ｃから流体が洩れだす隙間を小さくしているので、洩れ量抑制効果を更に高めることができて、圧縮機の性能を一層向上させることができる。   In the screw compressor of this embodiment, since the gap through which the fluid leaks from the radial seal portion B and the thrust seal portion C is reduced by the covering member 5, the effect of suppressing the leakage amount can be further enhanced. The performance can be further improved.

また、ラジアルシール部Ｂやスラストシール部Ｃの相対する面が過度に接触する場合には、被覆部材５が摩耗して焼付きによる不具合の発生を回避するので、信頼性も確保することができる。   In addition, when the opposing surfaces of the radial seal portion B and the thrust seal portion C are in contact with each other, the covering member 5 is worn and avoids the occurrence of defects due to seizure, so that reliability can be ensured. .

なお、ここではスクリューロータ１側の面に被覆部材５を設けたものを例に挙げて説明したが、この被覆部材５を軸受箱２側に設けてもよいことは言うまでもない。   Here, the example in which the covering member 5 is provided on the surface on the screw rotor 1 side has been described as an example, but it goes without saying that the covering member 5 may be provided on the bearing box 2 side.

本発明の実施の形態１に係るスクリュー圧縮機のシール部周辺の一部断面表示を含む構造図である。It is a structural diagram including a partial cross-sectional display around the seal portion of the screw compressor according to Embodiment 1 of the present invention. 図１のシール部Ａを拡大して示す断面図である。It is sectional drawing which expands and shows the seal | sticker part A of FIG. 本発明の実施の形態２に係るスクリュー圧縮機の要部であるシール部を拡大して示す断面図である。It is sectional drawing which expands and shows the seal part which is the principal part of the screw compressor which concerns on Embodiment 2 of this invention.

符号の説明Explanation of symbols

１ スクリューロータ、２ 軸受箱、３ 環状溝、４ 螺旋溝、５ 被覆部材、６ ケーシング、７ 軸端部（吐出側軸端部）、８ 軸受、１１ 吐出流路（外周部高圧域）、Ａ シール部、Ｂ ラジアルシール部、Ｃ スラストシール部。   DESCRIPTION OF SYMBOLS 1 Screw rotor, 2 Bearing box, 3 Annular groove, 4 Spiral groove, 5 Cover member, 6 Casing, 7 Shaft end part (discharge side shaft end part), 8 Bearing, 11 Discharge flow path (outer peripheral high pressure area), A Seal part, B radial seal part, C thrust seal part.

Claims (3)

ケーシング内に回転自在に収容されたスクリューロータと、
前記ケーシング内で前記スクリューロータの吐出側軸端部を囲繞し、軸受を介して支持する軸受箱と、
前記軸受箱の開口縁と前記スクリューロータとの対向面に設けられて前記スクリューロータの外周部高圧域に対しこれよりも低圧の前記軸受箱の内部空間を区画するシール部とを備え、
前記シール部に、前記スクリューロータと前記軸受箱とを径方向で対向させたラジアルシール部を設けて、このラジアルシール部の相対する面の一方に、前記スクリューロータの回転に伴って前記低圧側から前記外周部高圧域方向に流体を送ろうとする力を発生させる螺旋溝を設けるとともに、ラジアルシール部の前記相対する面の他方に、前記スクリューロータや前記軸受箱よりも軟らかい材質からなる被覆部材を設けたことを特徴とするスクリュー圧縮機。 A screw rotor rotatably accommodated in a casing;
A bearing box that surrounds the discharge-side shaft end portion of the screw rotor in the casing and supports the bearing through a bearing;
A seal portion that is provided on the opposed surface of the opening edge of the bearing box and the screw rotor and that partitions the inner space of the bearing box at a lower pressure than the high-pressure area of the outer periphery of the screw rotor;
The seal portion is provided with a radial seal portion in which the screw rotor and the bearing housing are opposed to each other in the radial direction, and the low pressure side of the radial seal portion is rotated along with the rotation of the screw rotor. the outer peripheral portion high range direction is provided a spiral groove which makes generating a force to send fluid Rutotomoni from, the other of the opposing surfaces of the radial seal portion, coating of soft material than the screw rotor and the bearing housing A screw compressor comprising a member . 前記ラジアルシール部に連続させて、前記スクリューロータと前記軸受箱とを軸方向で対向させたスラストシール部を設けて、このスラストシール部の相対する面の一方に、同心円状の複数個の環状溝からなるラビリンスを設けたことを特徴とする請求項１記載のスクリュー圧縮機。 A thrust seal portion is provided continuously to the radial seal portion so that the screw rotor and the bearing housing face each other in the axial direction. A plurality of concentric circular rings are formed on one of the opposing surfaces of the thrust seal portion. screw compressor according to claim 1 Symbol mounting, characterized in that a labyrinth consisting of the groove. 前記スラストシール部の前記相対する面の他方に、前記スクリューロータや前記軸受箱よりも軟らかい材質からなる被覆部材を設けたことを特徴とする請求項２記載のスクリュー圧縮機。 3. The screw compressor according to claim 2 , wherein a coating member made of a material softer than the screw rotor and the bearing box is provided on the other of the opposing surfaces of the thrust seal portion.
JP2008126784A 2008-05-14 2008-05-14 Screw compressor Active JP5207822B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008126784A JP5207822B2 (en) 2008-05-14 2008-05-14 Screw compressor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008126784A JP5207822B2 (en) 2008-05-14 2008-05-14 Screw compressor

Publications (2)

Publication Number Publication Date
JP2009275567A JP2009275567A (en) 2009-11-26
JP5207822B2 true JP5207822B2 (en) 2013-06-12

Family

ID=41441237

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2008126784A Active JP5207822B2 (en) 2008-05-14 2008-05-14 Screw compressor

Country Status (1)

Country Link
JP (1) JP5207822B2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015527523A (en) * 2012-06-29 2015-09-17 イートン コーポレーションＥａｔｏｎ Ｃｏｒｐｏｒａｔｉｏｎ Supercharger assembly having rotor end face seal and method of manufacturing supercharger assembly
WO2023182457A1 (en) * 2022-03-23 2023-09-28 ダイキン工業株式会社 Screw compressor and freezer

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06101672A (en) * 1992-09-18 1994-04-12 Daikin Ind Ltd Screw compressor
JPH07279678A (en) * 1994-04-15 1995-10-27 Tochigi Fuji Ind Co Ltd Screw-type supercharger
BE1010915A3 (en) * 1997-02-12 1999-03-02 Atlas Copco Airpower Nv DEVICE FOR SEALING A rotor shaft AND SCREW COMPRESSOR PROVIDED WITH SUCH DEVICE.
JP4103708B2 (en) * 2003-07-11 2008-06-18 ダイキン工業株式会社 Screw compressor
JP2006226160A (en) * 2005-02-16 2006-08-31 Hokuetsu Kogyo Co Ltd Oil-cooled screw compressor
JP2007016704A (en) * 2005-07-08 2007-01-25 Mitsubishi Heavy Ind Ltd Seal structure of rotating shaft and rotary machine having the same
JP4559343B2 (en) * 2005-11-09 2010-10-06 株式会社神戸製鋼所 Screw compressor

Also Published As

Publication number Publication date
JP2009275567A (en) 2009-11-26

Similar Documents

Publication Publication Date Title
JP4559343B2 (en) Screw compressor
JP2012017656A (en) Scroll compressor
JP2008215108A (en) Seal device and scroll type fluid machine
JP6377839B2 (en) Gas compressor
JP4833882B2 (en) Screw fluid machine
JP2009103012A (en) Screw fluid machine
US20090060767A1 (en) Axial compliance
JP5207822B2 (en) Screw compressor
US9004857B2 (en) Barrel-shaped centrifugal compressor
JP5425049B2 (en) Water jet screw compressor
JP2011236823A (en) Screw compressor
JP2003129979A (en) Sealed mechanical booster
KR102522649B1 (en) Scroll compressor
JP4103708B2 (en) Screw compressor
JP2002022033A (en) Labyrinth seal and fluid machinery
CN212225993U (en) Oil-proof and dust-proof sealing device
JP2016079877A (en) Screw compressor
JP2014145261A (en) Discharge muffler structure and rotary compressor
KR101099098B1 (en) Scroll compressor
KR20210028466A (en) Apparatus for a Formation of Back-Pressure in Electric Compressor and Method Employing the Same
JP2009138641A (en) Compressor
JP2006009614A (en) Scroll compressor
JP2006009576A (en) Scroll compressor
JP4103709B2 (en) Screw compressor
JP2009174523A (en) Screw compressor

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20110114

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20120607

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20120612

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20120807

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20130122

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20130219

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20160301

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Ref document number: 5207822

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250