• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A screw compressor rotatably accommodates, inside a housing 20 comprising a suction office and a discharge port 3, a pair of female and male rotors 1,2 in the meshed state and compresses gas. in the state where a liquid is mixed by pouring the liquid onto the gas confined in a working chamber 8 formed by the two rotors 1, 2 and the casing 20. A recessed portion 10 is provided on the wall surface of the casing 20 opposite to the discharge end of the rotors. The working chamber 8 is brought into communication with the recessed portion 10 immediately prior to being isolated from the discharge port 3 and this communication is maintained until the volume of the working chamber 8 becomes substantially zero. It is thus possible to control the increase in power consumption, vibration and noise of the screw compressor.
    公开号:BE1018907A3
    申请号:E2007/0403
    申请日:2007-08-23
    公开日:2011-11-08
    发明作者:Kohtaro Chiba；Hirotaka Kameya；Hideharu Tanaka
    申请人:Hitachi Ind Equipment Sys；
    IPC主号:
    专利说明:

    "Screw compressor"
    Background of the invention (1) Field of the invention
    The present invention relates to a screw compressor and more specifically to a screw compressor for compressing gas in the state where liquid is mixed with the gas.
    (2) Description of the Related Art
    A general screw compressor in the related art will be explained with reference to FIG. 5 and in FIG. 6. FIG. 5 is a cross-sectional view of a discharge end in the state immediately preceding completion of the discharge of a general screw compressor in the related art. Fig. 6 is an enlarged cross-sectional view of the discharge end in the state at the completion of delivery in FIG. 5.
    In the screw compressor, a pair consisting of a female rotor 1 and a male rotor 2 are housed in a bore 21 of a housing 20 indicated by dashed lines to turn respectively in the direction indicated by the arrow marks. and are intermeshed in each other as shown in FIG. 5. As the rotation of the two rotors 1 and 2 progresses, gas in a groove functioning as a working chamber is compressed and delivered to a discharge chamber (not shown) through a discharge port 3.
    In the gear zone of the two rotors 1 and 2, a working chamber 7 and a working chamber 8 are formed and respectively comprise a contact point 4 and a contact point 5, a contact point 4 and a point of contact. contact 6 at both ends.
    A working chamber 7 is formed in a suitable groove shape while these volumes are enlarged in association with the rotation of the rotors 1 and 2. This working chamber 7 is placed in communication with a suction port (not shown) to the other ends of the rotors 1, 2.
    The other working chamber 8 is formed in an adequate groove shape while gradually decreasing in volume. This working chamber 8 becomes a closed space with respect to the outside, with the exception of the discharge orifice 3, immediately with the completion of the discharge. Liquid is poured into the working chamber 8 to cool the gas during the compression process and seal a clearance of the working chamber which would result in internal leakage, and the gas mixed with the liquid is compressed in the chamber 8. As part of the reprocessing process, since the gas having a lower density than that of the liquid is discharged beforehand, the working chamber 8 is filled with liquid immediately before completion of the discharge, and the gas is practically excluded.
    When the rotors 1, 2 continue to rotate, the working chamber 8 transforms into a closed working chamber 9 because it is isolated from the discharge port 3 as shown in FIG. 6. Even when the volume of the closed working chamber 9 is further reduced after the rotors 1, 2 have continued to rotate, an outlet of the liquid is not provided therein. Therefore, not only is the pressure inside the closed working chamber 9 likely to rise rapidly and vibrations and noises are likely to be generated but there is also a risk of damage to the rotors and shortening the life of a bearing.
    Therefore, Japanese Examined Patent Application Publication No. S62-358 (Patent Document 1) discloses another compressor. This screw compressor eliminates liquid confinement and reduces the level of vibration and noise by providing a recessed portion on an inner wall surface opposite an end of a casing on the discharge side of the rotors, forming a contour area of the rotor. recessed portion in a shape substantially conforming to the shape of a previous flank of a groove forming a closed working chamber of a female rotor when the working chamber is isolated from the discharge port to form the working chamber closed, and communicating the closed working chamber and the recessed portion after the working chamber has been isolated from the discharge port and transformed into the closed working chamber.
    [Patent Document 1] Japanese Patent Examined
    In the screw compressor of patent document 1, the closed working chamber and the recessed portion are in communication with each other after the working chamber has been isolated from the discharge port and has been transformed. in the closed working area, regardless of the fact that an internal pressure of the working chamber becomes very high immediately before the working chamber is isolated from the discharge port.
    In fact, since the gas having a density which is lower than that of the liquid is discharged previously in the discharge process, the working chamber is filled with liquid immediately before being isolated from the discharge orifice and consequently gas is virtually excluded. Therefore, since the liquid is discharged by an extremely narrow communication region between the discharge port having a reduced area and the working chamber immediately before the working chamber is isolated from the discharge port, it becomes It is obvious that several problems are caused by the sudden increase in the internal pressure of the working chamber, the intermittent increase in torque to drive the rotors, and the increase in power consumption, vibrations and resulting noise.
    Here, the screw compressor in patent document 1 has only been limited to a screw compressor where the closed working chamber is formed because the working chamber is isolated from the discharge port immediately before completion of the delivery. . Therefore, such a screw compressor has a problem because it can not be applied to the screw compressor where a volume of the working chamber becomes essentially zero when the working chamber is isolated from the discharge port. .
    Summary of the invention
    An object of the present invention is therefore to provide a screw compressor to control the increase in power consumption, vibration and noise.
    In order to achieve the object described above, the present invention provides a screw compressor rotatably housing a pair of male and female rotors in the interlocked state within a housing including a suction port and a discharge port for compressing gas in the state of mixing with a liquid by pouring the liquid on the gas confined in a working chamber formed by the two rotors and the housing, wherein a recessed portion is formed on a surface of wall opposite one end of the casing on the discharge side of the rotors, the working chamber is placed in communication with the recessed portion immediately before being isolated from the discharge orifice, and the communication is maintained until a volume of the working chamber becomes essentially zero.
    More preferable examples of the structure of the present invention are as follows.
    (1) The working chamber is isolated from the discharge port before a volume of it becomes essentially zero.
    (2) An area which is first in contact with a contour of the male rotor in association with rotation of the rotors along the contour of the recessed portion is formed into a shape which corresponds to a leading edge of the male rotor when the working chamber is isolated from the discharge port.
    (3) The volume of the working chamber becomes essentially zero when the working chamber is isolated from the discharge port.
    (4) A final discharge zone of the discharge port is fixed at a point where the discharge port and the working chamber are isolated from each other in an advanced position of the angle of rotation, and the area corresponding to the leading edge of the male rotor in the contour of the recessed portion is set according to the leading edge of the male rotor in a more advanced position.
    According to the screw compressor of the present invention explained herein, an intermittent increase in torque can be reduced by preventing overcompression of a liquid until a volume of the working chamber becomes essentially zero from the moment immediately preceding the completion of the liquid discharge. As a result, it is possible to save energy and reduce vibration and noise.
    Brief description of the drawings
    Fig. 1 is a cross-sectional view at the discharge end in the state immediately preceding completion of the screw compressor discharge as the first embodiment of the present invention.
    Fig. 2 is a cross-sectional view taken along A-Asurlafig. 1.
    Fig. 3 is a cross-sectional view at the discharge end in the state where the rotation angle of the screw compressor of FIG. is 0 degrees.
    Fig. 4 is a cross-sectional view at the discharge end in the state immediately preceding completion of the screw compressor discharge as a second embodiment of the present invention.
    Fig. 5 is a cross-sectional view at the discharge end in the state immediately preceding completion of the discharge of a general screw compressor of the related art.
    Fig. 6 is an enlarged transverse cross-sectional view at the discharge end in the state at the time of completion of the discharge in FIG. 5.
    Detailed Description of the Preferred Embodiments
    A plurality of preferred embodiments of the present invention will be explained below with reference to the accompanying drawings. The like reference numerals in each of the embodiments and the related art refer to like elements in the drawings.
    (First embodiment)
    A screw compressor of a first embodiment of the present invention will be explained with reference to FIG. 1 to fig. 3. FIG. 1 is a cross-sectional view of the discharge end in the state immediately preceding completion of the screw compressor discharge in the first embodiment of the present invention. Fig. 2 is a cross-sectional view taken along A-A in FIG. 1. FIG. 3 is a cross-sectional view of the discharge end in the state where the rotation angle of the screw compressor of FIG. is 0 degrees.
    The screw compressor of this embodiment is an oil cooled screw compressor using ordinary oil as a liquid to be poured into a working chamber. In addition, in this embodiment, a state of FIG. 3 where a lobe tip of the male rotor 2 is located on a line connecting the centers of the two rotors 1, 2 is defined as the zero degree in terms of rotation angles of the female rotor 1 and the male rotor 2, and the directions indicated by the arrow marks in fig. 1 and FIG. 3 are defined as the positive directions of rotation. Furthermore, in the case of the male rotor 2, a contour among those coupling the tips and the bases of a pair of lobe flanks where the normal direction line of the sidewall is in the direction of rotation is defined by the terms " flank of attack ". In the case of the female rotor 1, a contour where the normal direction line of the sidewall is in the direction opposite to the direction of rotation is defined by the terms "leading edge".
    In the screw compressor, a pair consisting of a female rotor and a male rotor are housed inside a bore 21 of a housing 20 indicated by dashed lines to turn respectively in the direction indicated by the arrow marks and are intermeshed in one another as shown in FIG. 1. As the rotation of the two rotors 1 and 2 progresses, gas in a groove functioning as a working chamber is compressed and is forced to a discharge chamber (not shown) by a discharge port 3.
    In the state shown in FIG. 1, the two rotors 1, 2 are theoretically in contact with each other at the three locations of points 4, 5 and 3 on the discharge side. In general, the contact points 4, 5 and 6 are respectively provided with a small clearance in a measure that does not result in a large internal leak to achieve a smooth rotation of the two rotors 1 and 2. At the gear zone of the two rotors 1 and 2, the working chamber 7 and the working chamber 8 are formed and include the contact point 4 and the contact point 5, the contact point 4 and the point of contact. contact 6 at both ends.
    A working chamber 7 is formed in a suitable groove shape while these volumes are enlarged in association with the rotation of the rotors 1 and 2. This working chamber 7 is placed in communication with a suction port (not shown) to the other ends of the rotors 1,2.
    The other working chamber 8 is formed in a suitable groove shape whose volume is gradually reduced. The oil is poured into this working chamber 8 to cool the gas during the compression process and to seal the play of the working chamber which is considered a cause of internal leakage. As a result, the gas mixed with the oil is compressed in the working chamber 8. During the discharge process, since the gas having a lower density than the oil is discharged previously, the working chamber 8 is filled with oil immediately before completion of the discharge and the gas is virtually excluded.
    A final discharge zone 12 of the discharge orifice 3 is fixed in the zone on the line connecting the centers of the two rotors 1, 2 or in the zone a little lower than the connecting line of FIG. In addition, a recessed portion 10 is provided on the wall surface 13 of the housing 20 opposite the discharge end of the rotor. An area of the contour of the recessed portion 10 (i.e., a curve connecting the points 6 and 11) is fixed in correspondence with the leading edge of the male rotor 2 at the location corresponding to minus 10 degrees in terms of rotation of the male rotor 2. This contour of the other recessed portion 10 is fixed in correspondence with an arc having a diameter which is the diameter of the base of the lobes of the female rotor 1, the leading edge of the female rotor being at the location corresponding to 60 degrees in terms of the angle of rotation of the female rotor 1 and an arc having a diameter which is the diameter of the tip of the lobes of the female rotor 1. Therefore, the working chamber 8 is placed in communication smoothly with the recessed portion 10 and resistance to the flow of the oil to be discharged can be reduced.
    The working chamber 8 is brought into communication with the recessed portion 10 immediately before being isolated from the delivery port 3. In other words, the working chamber 8 is in communication with the discharge port 3 and the recessed portion immediately prior to completion of the backflow. The communication between the working chamber 8 and the recessed portion 10 is maintained until the volume of the working chamber 8 becomes substantially zero.
    In the state shown in FIG. 2, the discharge port 3 is in communication with the working chamber 8, the working chamber 8 with the recessed portion 10 and the recessed portion 10 with the suction side, respectively.
    Next, the operation of the screw compressor of this embodiment will be explained. With the rotation of the two rotors 1 and 2, the working chamber 8 draws gas (air) from the atmosphere and then compresses the gas in combination with a volume reduction. The oil is poured into the working chamber 8 at the initial stage of the compression process. The working chamber 8 is then placed in communication with the discharge port 3 to discharge the compressed air. In addition, the working chamber 8 is brought into communication, immediately before completion of the discharge, with the recessed portion 10 via the line connecting the points 6 and 11 of the contour of the recessed portion 10, while maintaining communication with the In addition, the working chamber 8 delivers the fluid inside the latter to the discharge orifice 3 and the recessed portion 10 as a function of the reduction in its volume. In this case, since the fluid inside the working chamber 8 is practically only oil because of the reason explained in the related art section, there is hardly any of air that is forced to the suction side by the recessed portion 10. Therefore, there is no increase in internal leakage due to the structure of this embodiment of the present invention and the operating efficiency. is not likely to be reduced.
    The working chamber 8 is always in communication, in the process of reducing its volume, with at least any one of the discharge port 3 and the recessed portion 10 to stably acquire an oil discharge zone. Therefore, it is possible to prevent a rapid increase in resistance when the oil is pumped back. Therefore, since the oil in the working chamber 8 is forced towards the suction side without overcompression, it is possible to prevent a significant increase in the drive torque of the rotors due to the overcompression of the oil. As a result, it is possible not only to save energy but also to prevent an increase in the level of vibrations and noise.
    Here, the first embodiment of the present invention has been explained subject to the fact that the recessed portion 10 is in communication with the suction side. However, in the case where the volume of the recessed portion 10 is sufficiently larger than that of the working chamber 8 immediately before being isolated from the discharge orifice 3, the communication of the recessed portion 10 with the suction side is not always required, when the working chamber 8 is in communication with the recessed portion 10.
    In addition, the structure of this first embodiment can also be applied to the screw compressor where the volume of the working chamber becomes essentially zero at the moment the working chamber is isolated from the discharge port.
    (Second embodiment)
    Next, the screw compressor as a second embodiment of the present invention will be explained with reference to FIG. 4. FIG. 4 is a cross-sectional view at the discharge end in the state immediately preceding completion of the screw compressor discharge as a second embodiment of the present invention. Since this second embodiment is different from the first embodiment in what is explained below but is basically the same as the first embodiment in the rest, a duplicate explanation is eliminated here.
    In this second embodiment, the final discharge zone 12 of the discharge orifice 3 is fixed at the point where the discharge orifice is isolated from the working chamber 8, at a location corresponding to minus 10 degrees in In addition, an area of the contour of the recessed portion 10, namely a curve connecting the points 6 and 11 is fixed in correspondence with the leading edge of the male rotor 2 to the rotor. corresponding place at minus 20 degrees. Immediately before completion of the discharge, the discharge port 3 is brought into communication with the working chamber 8, the working chamber with the recessed portion 10 and the recessed portion 10 with the suction side, respectively.
    According to the second embodiment, the time required for the communication between the working chamber 7 in communication with the suction side and the discharge port 3 can be further reduced, during the rotational process of the rotors 1, 2, that the time required in the first embodiment. After the working chamber 8 has been isolated from the discharge port 3, the oil remaining in the working chamber 8 is discharged to the suction side by the recessed portion 10. Therefore, this not only prevents overcompression of the oil in the working chamber 8 but also to reduce the amount of air delivered to the working chamber 7 in communication with the suction side through the discharge port 3. Therefore, it is possible to improve the operating efficiency of the screw compressor.
    权利要求:
    Claims (5)
    [1]
    A screw compressor rotatably housing a pair of male and female rotors in the interlocked state within a housing including a suction port and a discharge port for compressing gas in the mixing state. with a liquid by pouring the liquid on the gas confined in a working chamber formed by the two rotors and the housing, wherein a recessed portion is formed on a wall surface opposite an end of the casing on the discharge side of the rotors, the The working chamber is communicated with the recessed portion immediately prior to being isolated from the discharge port, and communication is maintained until a volume of the working chamber becomes essentially zero.
    [2]
    The screw compressor according to claim 1, wherein the working chamber is isolated from the discharge port before the volume of the working chamber becomes essentially zero;
    [3]
    The screw compressor according to claim 1, wherein an area which is first in contact with a contour of the male rotor in association with rotation of the rotors along the contour of the recessed portion is formed into a shape which corresponds at a leading edge of the male rotor when the working chamber is isolated from the discharge port.
    [4]
    The screw compressor according to claim 1, wherein the volume of the working chamber becomes essentially zero at the moment the working chamber is isolated from the discharge port.
    [5]
    A screw compressor as claimed in claim 3, wherein a final discharge area of the discharge port is fixed at a location where the discharge port and the working chamber are isolated from each other in a position less than one rotation angle, and an area corresponding to the leading edge of the male rotor in the contour of the recessed portion is set according to the leading edge of the male rotor in the position less than the angle of rotation.
    类似技术:
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    同族专利:
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    JP2008082273A|2008-04-10|
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    引用文献:
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    JP3823573B2|1998-11-19|2006-09-20|株式会社日立製作所|Screw fluid machinery|JP5422260B2|2009-05-28|2014-02-19|株式会社日立製作所|Oil-free screw compressor|
    JP5695995B2|2011-07-25|2015-04-08|株式会社神戸製鋼所|Gear pump|
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    JP6184837B2|2013-10-30|2017-08-23|株式会社日立産機システム|Screw compressor|
    EP3245405B1|2015-01-15|2019-09-04|Atlas Copco Airpower|Oil-injected vacuum pump element|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    JP2006264232A|JP5000962B2|2006-09-28|2006-09-28|Screw compressor|
    JP2006264232|2006-09-28|
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