JP5197157B2 - Screw fluid machine - Google Patents

Screw fluid machine Download PDF

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JP5197157B2
JP5197157B2 JP2008138033A JP2008138033A JP5197157B2 JP 5197157 B2 JP5197157 B2 JP 5197157B2 JP 2008138033 A JP2008138033 A JP 2008138033A JP 2008138033 A JP2008138033 A JP 2008138033A JP 5197157 B2 JP5197157 B2 JP 5197157B2
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seal
rotor
screw
space
bearing
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JP2009287413A (en
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正樹 松隈
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Kobe Steel Ltd
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Kobe Steel Ltd
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Priority to KR1020090032548A priority patent/KR20090123775A/en
Priority to CN2009101418413A priority patent/CN101592151B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、スクリュ流体機械に関する。   The present invention relates to a screw fluid machine.

ロータ室内に収容された雌雄咬合するスクリュロータで対象気体を圧縮するスクリュ圧縮機や、対象気体の膨張を回転エネルギに変換するスクリュエキスパンダなどのスクリュ流体機械は、対象気体を系内に封止、或いは、対象気体に外気などが混入するのを防止するために、ロータ軸のスクリュロータと軸受との間に軸封構造が設けられる。   Screw fluid machines, such as a screw compressor that compresses the target gas with a screw rotor that engages the male and female in the rotor chamber, and a screw expander that converts the expansion of the target gas into rotational energy, seal the target gas in the system. Alternatively, a shaft seal structure is provided between the screw rotor of the rotor shaft and the bearing in order to prevent outside air from being mixed into the target gas.

特許文献１に記載されているように、従来のスクリュ圧縮機では、吸込側の軸封装置としてリップシールが用いられ、吐出側の軸封装置としてメカニカルシールが用いられている。   As described in Patent Document 1, in the conventional screw compressor, a lip seal is used as a suction side shaft seal device, and a mechanical seal is used as a discharge side shaft seal device.

リップシールは安価で省スペースの軸封装置であるが、一般に、封止可能な最大圧力が０．０３ＭＰａ程度である。このため、リップシールは、高圧となる吐出側では軸封が不十分になったり耐久性が著しく低下するおそれがあるので、低圧の吸込側の軸封にのみ使用可能である。一方、メカニカルシールは、高圧の軸封が可能であるが、非常に高価であると共に設置のためのスペースが大きいという問題がある。   The lip seal is an inexpensive and space-saving shaft seal device, but generally the maximum pressure that can be sealed is about 0.03 MPa. For this reason, the lip seal can be used only for the shaft seal on the suction side of the low pressure because the shaft seal may be insufficient on the discharge side where the pressure is high or the durability may be significantly reduced. On the other hand, the mechanical seal is capable of high-pressure shaft sealing, but has a problem that it is very expensive and requires a large space for installation.

特許文献２には、スクリュロータと軸受との間に、スクリュロータ側にラビリンスシールのような非接触シールを設け、軸受側にリップシールを設け、非接触シールとリップシールとの間の空間を低圧空間に連通させることで、リップシールに過大な圧力が加わらないようにした発明が記載されている。   In Patent Document 2, a non-contact seal such as a labyrinth seal is provided on the screw rotor side between the screw rotor and the bearing, a lip seal is provided on the bearing side, and a space between the non-contact seal and the lip seal is provided. An invention is described in which excessive pressure is not applied to the lip seal by communicating with a low pressure space.

しかしながら、特許文献２の発明でも、対象気体の温度が高い場合、僅かに漏出した高温の対象気体によりリップシールの温度が上昇する。リップシールは、一般に熱膨張率が大きく、シール空間の圧力が上昇しなくても、温度上昇によってロータ軸に対する接触圧力が高くなり、損傷し易くなるという問題がある。
特開２０００−４５９４８号公報 特開２００７−１３２２４３号公報 However, even in the invention of Patent Document 2, when the temperature of the target gas is high, the temperature of the lip seal rises due to the slightly leaked high temperature target gas. Lip seals generally have a large coefficient of thermal expansion, and even if the pressure in the seal space does not rise, there is a problem that the contact pressure against the rotor shaft increases due to temperature rise and is easily damaged.
JP 2000-45948 A JP 2007-132243 A

前記問題点に鑑みて、本発明は、ロータ軸の高圧側に安価で省スペース、且つ、シールが確実な軸封構造を有するスクリュ流体機械を提供することを課題とする。   In view of the above problems, an object of the present invention is to provide a screw fluid machine having a shaft seal structure that is inexpensive, space-saving, and has a reliable seal on the high-pressure side of a rotor shaft.

前記課題を解決するために、本発明によるスクリュ流体機械は、前記スクリュロータと前記スクリュロータのロータ軸の高圧側の軸受との間に、前記スクリュロータ側から順に、第１非接触シールと、第２非接触シールと、リップシールとを配設し、前記リップシールは、前記軸受側から、前記第２非接触シールと前記リップシールとの間の第２シール空間への潤滑油の流出を防ぐ向きに設けられ、前記第１非接触シールと前記第２非接触シールとの間の第１シール空間に潤滑流体を供給する潤滑流体供給流路と、前記第２シール空間を、前記リップシールの前記軸受側の圧力以下の圧力の空間に連通させる連通孔とを設けたものとする。 In order to solve the above-described problem, a screw fluid machine according to the present invention includes a first non-contact seal between the screw rotor and a bearing on a high-pressure side of a rotor shaft of the screw rotor, in order from the screw rotor side, A second non-contact seal and a lip seal are provided, and the lip seal causes the lubricating oil to flow out from the bearing side to a second seal space between the second non-contact seal and the lip seal. provided in the direction preventing the first and the first supplies lubricating fluid to the seal space lubricating fluid supply flow path between the non-contact seal with the second non-contact seal, a pre-Symbol second sealing space, the lip It is assumed that a communication hole that communicates with a space having a pressure equal to or lower than the pressure on the bearing side of the seal is provided.

この構成によれば、第１シール空間に潤滑流体が供給されるので、第１非接触シールおよび第２非接触シールのシール性を向上させることができる。また、第２シール空間を低圧の空間に連通させたことで、リップシールに過剰な圧力が加わらず、軸受側への圧縮ガスや潤滑流体の侵入を防止できる。さらに、第１シール間に供給される潤滑流体が第２シール空間に漏出し、リップシールを冷却するので、第１リップシールを長寿命化、および、ロータの高回転化が可能である。   According to this configuration, since the lubricating fluid is supplied to the first seal space, the sealing performance of the first non-contact seal and the second non-contact seal can be improved. Further, since the second seal space communicates with the low-pressure space, excessive pressure is not applied to the lip seal, and intrusion of compressed gas or lubricating fluid to the bearing side can be prevented. Further, since the lubricating fluid supplied between the first seals leaks into the second seal space and cools the lip seal, it is possible to extend the life of the first lip seal and increase the rotation of the rotor.

また、本発明のスクリュ流体機械において、前記第１非接触シールおよび前記第２非接触シールは、前記ロータ軸の回転力によって前記潤滑流体を前記ロータ室側に移動させる螺旋状の溝または突起を有してもよい。   Further, in the screw fluid machine according to the present invention, the first non-contact seal and the second non-contact seal have a spiral groove or protrusion for moving the lubricating fluid to the rotor chamber side by the rotational force of the rotor shaft. You may have.

この構成によれば、潤滑流体がロータ室側に移動する圧力によって対象気体を封止することができる。   According to this configuration, the target gas can be sealed by the pressure at which the lubricating fluid moves to the rotor chamber side.

以上のように、本発明によれば、第２非接触シールとリップシールとの間の第２シール空間を低圧空間に連通させる連通孔を設けたことで、リップシールに過大な圧力が加わらず、第１非接触シールと第２非接触シールとの間に潤滑流体を供給することで、第２シール空間に漏出した潤滑流体がリップシールを冷却するので、リップシールの寿命を延ばすことができる。   As described above, according to the present invention, by providing the communication hole that communicates the second seal space between the second non-contact seal and the lip seal with the low pressure space, excessive pressure is not applied to the lip seal. By supplying the lubricating fluid between the first non-contact seal and the second non-contact seal, the lubricating fluid leaking into the second seal space cools the lip seal, so that the life of the lip seal can be extended. .

これより、本発明の実施形態について、図面を参照しながら説明する。
図１は、本発明のスクリュ流体機械の第１実施形態であるスクリュ圧縮機１を示す。スクリュ圧縮機１は、ハウジング２のロータ室３内に収容された雌雄咬合する一対のスクリュロータ４で、低圧（たとえば大気圧）の蒸気（対象気体）を（例えば０．５ＭＰａＧに）圧縮して吐出するものである。 Embodiments of the present invention will now be described with reference to the drawings.
FIG. 1 shows a screw compressor 1 which is a first embodiment of a screw fluid machine of the present invention. The screw compressor 1 compresses low-pressure (for example, atmospheric pressure) steam (target gas) (for example, to 0.5 MPaG) with a pair of screw rotors 4 that engage in male and female, housed in the rotor chamber 3 of the housing 2. To be discharged.

ハウジング２には、ロータ室３に圧縮すべき蒸気を供給する吸込流路５と、ロータ室３内でスクリュロータ４によって圧縮された蒸気を排出する吐出流路６と、スクリュロータ４のロータ軸７を吸込側および吐出側で、それぞれ、支持および軸封する構造を設置するための軸受軸封空間８，９が設けられている。   The housing 2 includes a suction flow path 5 for supplying steam to be compressed to the rotor chamber 3, a discharge flow path 6 for discharging steam compressed by the screw rotor 4 in the rotor chamber 3, and a rotor shaft of the screw rotor 4. Bearing shaft sealing spaces 8 and 9 are provided for installing a structure for supporting and sealing the shaft 7 on the suction side and the discharge side, respectively.

ロータ軸７は、吸込側の軸受軸封空間８内に設置されたころ軸受１０と、吐出側の軸受軸封空間９内に設置された２つの玉軸受１１とで回転可能に支持され、吸込側の軸受軸封空間９を貫通して延伸し、不図示のモータに接続される。   The rotor shaft 7 is rotatably supported by a roller bearing 10 installed in the suction-side bearing shaft sealing space 8 and two ball bearings 11 installed in the discharge-side bearing shaft sealing space 9, The bearing shaft sealing space 9 on the side is extended and connected to a motor (not shown).

ころ軸受１０の前記モータ側には、モータ側への異物（ころ軸受１０のグリスなど）の浸入を防ぐリップシール１２が設置され、ころ軸受１０のスクリュロータ４側には、ころ軸受１０のグリスがスクリュロータ４側に流出しないように封止するリップシール１３と、吸込流路５からころ軸受１０側に蒸気や潤滑流体が浸入しないように封止するリップシール１４とが設けられている。   A lip seal 12 is installed on the motor side of the roller bearing 10 to prevent foreign substances (such as grease on the roller bearing 10) from entering the motor side. On the screw rotor 4 side of the roller bearing 10, grease on the roller bearing 10 is installed. Is provided with a lip seal 13 for sealing so as not to flow out to the screw rotor 4 side, and a lip seal 14 for sealing so that steam and lubricating fluid do not enter the roller bearing 10 side from the suction flow path 5.

スクリュロータ４と玉軸受１１との間の吐出側の軸受軸封空間９には、スクリュロータ４側から順に、第１ラビリンスシール１５、第２ラビリンスシール１６およびリップシール１７が設けられている。第１ラビリンスシール１５は、ロータ軸７に嵌合してロータ軸７とともに回転するロータと、該ロータと接触しないように軸受軸封室９の内壁に嵌合して固定されたステータとからなる公知の非接触シールであり、少しずつ蒸気を漏出させながら、蒸気圧力を低減するものである。リップシール１７は、玉軸受１１からの潤滑用油の流出を防止する向きに設置され、その耐用圧力は、０．０３ＭＰａＧ程度である。   A first labyrinth seal 15, a second labyrinth seal 16, and a lip seal 17 are provided in the bearing shaft seal space 9 on the discharge side between the screw rotor 4 and the ball bearing 11 in order from the screw rotor 4 side. The first labyrinth seal 15 includes a rotor that is fitted to the rotor shaft 7 and rotates together with the rotor shaft 7, and a stator that is fitted and fixed to the inner wall of the bearing shaft sealing chamber 9 so as not to contact the rotor. This is a known non-contact seal that reduces the vapor pressure while gradually leaking the vapor. The lip seal 17 is installed in a direction that prevents the lubricating oil from flowing out of the ball bearing 11, and its withstand pressure is about 0.03 MPaG.

軸受軸封空間９は、第２ラビリンスシール１６とリップシール１７とによって区分され、第１ラビリンスシール１５と第２ラビリンスシール１６との間の第１シール空間１８、第２ラビリンスシール１６とリップシール１７との間の第２シール空間１９、および、第２シール空間１９より玉軸受１１側の封油空間２０に分割されている。   The bearing shaft seal space 9 is divided by a second labyrinth seal 16 and a lip seal 17, and a first seal space 18 between the first labyrinth seal 15 and the second labyrinth seal 16, a second labyrinth seal 16 and a lip seal. The second seal space 19 between the second seal space 17 and the oil seal space 20 closer to the ball bearing 11 than the second seal space 19 is divided.

また、ハウジング２には、リップシール１３とリップシール１４との間の空間を大気に開放する開放孔２１と、第１第１ラビリンスシール１５と第２ラビリンスシール１６との間の第１シール空間１８に潤滑流体（例えばスクリュ圧縮機が吐出した蒸気の凝縮水）を供給する潤滑流体供給流路２２と、第２ラビリンスシール１６とリップシール１７との間の第２シール空間１９を大気（低圧空間）に開放する連通路２３とを有する。   Further, the housing 2 has an opening hole 21 that opens the space between the lip seal 13 and the lip seal 14 to the atmosphere, and a first seal space between the first first labyrinth seal 15 and the second labyrinth seal 16. A lubricating fluid supply flow path 22 for supplying a lubricating fluid (for example, condensed water of steam discharged by a screw compressor) 18 and a second seal space 19 between the second labyrinth seal 16 and the lip seal 17 are opened to the atmosphere (low pressure). And a communication passage 23 opened to the space.

第１シール空間１８に供給された潤滑流体は、第１シール空間１８に漏出した蒸気と共に第２ラビリンスシール１６を通過して第２シール空間１９に漏出する。このとき、潤滑流体は、第２ラビリンスシール１６の隙間を小さくするので、蒸気の漏出量を低減する。   The lubricating fluid supplied to the first seal space 18 passes through the second labyrinth seal 16 together with the steam leaked to the first seal space 18 and leaks to the second seal space 19. At this time, the lubricating fluid reduces the gap between the second labyrinth seals 16, thereby reducing the amount of steam leakage.

第２シール空間１９は、連通路２２によって大気開放されているので、第２ラビリンスシール１６から漏出した蒸気は大気に放出され、リップシール１７に過剰な圧力を加えることがない。また、第２シール空間１９に漏出した潤滑流体は、リップシール１７からロータ軸７との摩擦によって生じた熱を奪い、連通孔２３から流出する。これにより、リップシール１７の過熱を防止して劣化や損傷を防止でき、ロータ軸７の回転速度を高速化（例えば、ロータ軸７の周速を４０から５０ｍ／ｓまで上昇）することも可能になる。   Since the second seal space 19 is opened to the atmosphere by the communication passage 22, the steam leaked from the second labyrinth seal 16 is released to the atmosphere, and an excessive pressure is not applied to the lip seal 17. Further, the lubricating fluid leaking into the second seal space 19 takes heat generated by friction with the rotor shaft 7 from the lip seal 17 and flows out from the communication hole 23. As a result, overheating of the lip seal 17 can be prevented to prevent deterioration and damage, and the rotational speed of the rotor shaft 7 can be increased (for example, the peripheral speed of the rotor shaft 7 is increased from 40 to 50 m / s). become.

図２および３に、本発明のスクリュ流体機械の第２実施形態であるスクリュエキスパンダ３１の高圧側の軸受軸封構造を示す。スクリュエキスパンダ３１は、ハウジング３２に形成されたロータ室３３にスクリュロータ３４が収容され、スクリュロータ３４のロータ軸３５を、ハウジング３２に保持された軸受３６で回転可能に支持している。スクリュエキスパンダ３１では、スクリュロータ３４と軸受３６との間に、スクリュロータ３４側から順に、第１ビスコシール（非接触シール）３７、第２ビスコシール３８およびリップシール３９が配設されている。   2 and 3 show a bearing shaft seal structure on the high pressure side of a screw expander 31 which is a second embodiment of the screw fluid machine of the present invention. In the screw expander 31, a screw rotor 34 is accommodated in a rotor chamber 33 formed in a housing 32, and a rotor shaft 35 of the screw rotor 34 is rotatably supported by a bearing 36 held in the housing 32. In the screw expander 31, a first visco seal (non-contact seal) 37, a second visco seal 38, and a lip seal 39 are disposed between the screw rotor 34 and the bearing 36 in order from the screw rotor 34 side. .

第１ビスコシール３７および第２ビスコシール３８は、ハウジング３２に嵌装されたスリーブからなり、波ばね４０によってハウジング３２およびハウジング３２に気密に取り付けた固定部材３２ａに軸方向に押圧され、結果的にハウジング３２に気密に保持されている。第１ビスコシール３７は、ロータ軸３５との間の隙間が数十μｍ以下になるように保持され、第２ビスコシール３８は、ロータ軸３５に嵌装されてロータ軸３５と共に回転するシャフトスリーブ４１との間の隙間が数十μｍ以下になるように保持されている。さらに、第１ビスコシール３７および第２ビスコシール３８は、その内面に螺旋状の溝４２，４３が形成されており、ロータ軸３５またはシャフトスリーブ４１の回転に随伴して回転する流体に、ロータ室３３に向かう圧力を付与するようになっている。   The first visco seal 37 and the second visco seal 38 are sleeves fitted in the housing 32, and are pressed in the axial direction by the wave spring 40 to the housing 32 and the fixing member 32a that is airtightly attached to the housing 32. The housing 32 is airtightly held. The first visco seal 37 is held so that the gap between the first visco seal 37 and the rotor shaft 35 is several tens of μm or less, and the second visco seal 38 is fitted to the rotor shaft 35 and rotates with the rotor shaft 35. 41 is held so that the gap between it and 411 is several tens of μm or less. Further, the first visco seal 37 and the second visco seal 38 have spiral grooves 42 and 43 formed on the inner surfaces thereof, so that the rotor rotates as the rotor shaft 35 or the shaft sleeve 41 rotates. A pressure toward the chamber 33 is applied.

ハウジング３２には、第１ビスコシール３７と第２ビスコシール３８との間の、波ばね４０が配設された第１シール空間４４に潤滑流体を供給する潤滑流体供給流路４５が設けられている。また、ハウジング３２には、第２ビスコシール３８とリップシール３９との間の第２シール空間４６を大気に開放する連通路４７が設けられている。   The housing 32 is provided with a lubricating fluid supply passage 45 for supplying a lubricating fluid to a first seal space 44 between the first visco seal 37 and the second visco seal 38 in which the wave spring 40 is disposed. Yes. The housing 32 is provided with a communication passage 47 that opens the second seal space 46 between the second Bisco seal 38 and the lip seal 39 to the atmosphere.

リップシール３９は、シャフトスリーブ４１に摺接するように、ハウジング３２に保持され、軸受３６が保持された封油空間４８から潤滑油等が第２シール空間４６に漏出するのを防止する方向に取り付けられている。   The lip seal 39 is held by the housing 32 so as to be in sliding contact with the shaft sleeve 41, and is attached in a direction that prevents lubricating oil and the like from leaking from the sealed oil space 48 in which the bearing 36 is held to the second sealed space 46. It has been.

本実施形態において、第１シール空間４４に供給される潤滑流体は、例えば、ボイラからスチームエキスパンダ３１に供給され、スチームエキスパンダ３１から吐出された蒸気の熱を熱交換器で２次利用する際に発生した凝縮水の一部を、スチームトラップを介し潤滑流体供給流路４５から供給することで利用できる。   In the present embodiment, for example, the lubricating fluid supplied to the first seal space 44 is supplied from the boiler to the steam expander 31, and the heat of the steam discharged from the steam expander 31 is secondarily used in the heat exchanger. A part of the condensed water generated at this time can be used by supplying it from the lubricating fluid supply flow path 45 via the steam trap.

本実施形態では、ロータ軸３５の回転によって第１ビスコシール３７および第２ビスコシール３８が発生する流体圧によって蒸気をロータ室３３内に封止するものであるが、潤滑流体供給流路４５を介して第１シール空間４４に水を供給しているので、蒸気のような気体だけが存在する場合に比べて、第１ビスコシール３７および第２ビスコシール３８において発生する流体圧が格段に大きくなる。これによって、蒸気の確実な封止ができ、第２シール空間４６に漏出した潤滑流体によってリップシール３９を冷却することもできる。   In this embodiment, the steam is sealed in the rotor chamber 33 by the fluid pressure generated by the first visco seal 37 and the second visco seal 38 by the rotation of the rotor shaft 35. Since the water is supplied to the first seal space 44 through the first seal space 44, the fluid pressure generated in the first visco seal 37 and the second visco seal 38 is remarkably larger than when only a gas such as steam is present. Become. Accordingly, the vapor can be surely sealed, and the lip seal 39 can be cooled by the lubricating fluid leaked into the second seal space 46.

図３に、本発明の第３実施形態のスクリュ流体機械であるスクリュ圧縮機３１ａの高圧側の軸受け構造を示す。本実施形態の説明では、第２実施形態と同じ構成要素には同じ符号を付して重複する説明を省略する。本実施形態のスクリュ圧縮機３１ａにおいて、第１ビスコシール３７ａおよび第２ビスコシール３８ａは、ロータ軸３５に一体に形成した螺旋状の突起４９，５０からなる。この第１ビスコシール３７ａおよび第２ビスコシール３８ａも、ロータ軸３５の回転によって、ハウジング３２との隙間に存在する流体をロータ室３３側に移動させる流体圧を生じるものである。   FIG. 3 shows a bearing structure on the high-pressure side of a screw compressor 31a which is a screw fluid machine of a third embodiment of the present invention. In the description of this embodiment, the same components as those of the second embodiment are denoted by the same reference numerals, and redundant description is omitted. In the screw compressor 31a of the present embodiment, the first visco seal 37a and the second visco seal 38a are formed of helical protrusions 49 and 50 formed integrally with the rotor shaft 35. The first visco seal 37a and the second visco seal 38a also generate fluid pressure that moves the fluid existing in the gap with the housing 32 to the rotor chamber 33 side by the rotation of the rotor shaft 35.

本発明の第１実施形態のスクリュ圧縮機の概略断面図。1 is a schematic sectional view of a screw compressor according to a first embodiment of the present invention. 本発明の第２実施形態のスクリュエキスパンダの軸受構造の概略断面図。The schematic sectional drawing of the bearing structure of the screw expander of 2nd Embodiment of this invention. 本発明の第３実施形態のスクリュエキスパンダの軸受構造の概略断面図。The schematic sectional drawing of the bearing structure of the screw expander of 3rd Embodiment of this invention.

符号の説明Explanation of symbols

１…スクリュ圧縮機（スクリュ流体機械）
２…ハウジング
３…ロータ室
４…スクリュロータ
５…吸込流路
６…吐出流路
７…ロータ軸
９…軸受軸封空間
１１…玉軸受
１５…第１ラビリンスシール（第１非接触シール）
１６…第２ラビリンスシール（第２非接触シール）
１７…リップシール
１８…第１シール空間
１９…第２シール空間
２０…封油空間
２２…潤滑流体供給流路
２３…連通路 1 ... Screw compressor (screw fluid machine)
DESCRIPTION OF SYMBOLS 2 ... Housing 3 ... Rotor chamber 4 ... Screw rotor 5 ... Suction flow path 6 ... Discharge flow path 7 ... Rotor shaft 9 ... Bearing shaft sealing space 11 ... Ball bearing 15 ... 1st labyrinth seal (1st non-contact seal)
16 ... 2nd labyrinth seal (2nd non-contact seal)
DESCRIPTION OF SYMBOLS 17 ... Lip seal 18 ... 1st seal space 19 ... 2nd seal space 20 ... Seal oil space 22 ... Lubricating fluid supply flow path 23 ... Communication path

Claims (2)

ハウジングに形成したロータ室内に収容された雌雄咬合するスクリュロータにより対象気体を圧縮、または、前記対象気体の膨張力を回転力に変換するスクリュ流体機械において、
前記スクリュロータと前記スクリュロータのロータ軸の高圧側の軸受との間に、前記スクリュロータ側から順に、第１非接触シールと、第２非接触シールと、リップシールとを配設し、
前記リップシールは、前記軸受側から、前記第２非接触シールと前記リップシールとの間の第２シール空間への潤滑油の流出を防ぐ向きに設けられ、
前記第１非接触シールと前記第２非接触シールとの間の第１シール空間に潤滑流体を供給する潤滑流体供給流路と、
前記第２シール空間を、前記リップシールの前記軸受側の圧力以下の圧力の空間に連通させる連通孔とを設けたことを特徴とするスクリュ流体機械。 In a screw fluid machine that compresses a target gas by a male and female screw rotor housed in a rotor chamber formed in a housing, or converts an expansion force of the target gas into a rotational force,
Between the screw rotor and the bearing on the high-pressure side of the rotor shaft of the screw rotor, a first non-contact seal, a second non-contact seal, and a lip seal are disposed in order from the screw rotor side,
The lip seal is provided in a direction to prevent outflow of lubricating oil from the bearing side to the second seal space between the second non-contact seal and the lip seal,
A lubricating fluid supply flow path for supplying a lubricating fluid to a first seal space between the first non-contact seal and the second non-contact seal;
Before Symbol a second sealing space, the screw fluid machine is characterized by providing a communicating hole for communicating the space of the bearing-side pressure below the pressure of the lip seal. 前記第１非接触シールおよび前記第２非接触シールは、前記ロータ軸の回転力によって前記潤滑流体を前記ロータ室側に移動させる螺旋状の溝または突起を有することを特徴とする請求項１に記載のスクリュ流体機械。   The said 1st non-contact seal and the said 2nd non-contact seal have a helical groove | channel or protrusion which moves the said lubricating fluid to the said rotor chamber side with the rotational force of the said rotor shaft | axis. The described screw fluid machine.
JP2008138033A 2008-05-27 2008-05-27 Screw fluid machine Expired - Fee Related JP5197157B2 (en)

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