Patent Abstract:
A liquid injection type screw compressor in which, in a compression stroke of an working space formed by male and female rotors, liquids such as oil or water is prevented from leaking from the high pressure working space to a gas inlet side, suction resistance of gas sucked from the gas inlet to a rotor casing is reduced to improve volumetric efficiency, and shape forming of the casing is simplified. 
     The liquid injection screw compressor has the male and female rotor pair of screw rotors, the rotor casing ( 1   a   , 1   b ) having a bore for receiving the rotors, a gas suction opening and a gas outlet that are provided in both end sections of the casing and communicate with the bore, and a lip section ( 4 ) projected from a bore surface ( 2 ) positioned more on the upstream side than a suction seal line ( 5 ) of the casing in order to prevent a back flow of the liquid from the bore surface toward the gas inlet side. The lip section ( 4 ) is positioned in a region surrounded by the suction seal line ( 5 ) and a line separated by a distance of one screw pitch of the rotors from the suction closure line ( 5 ) to the suction opening side.

Full Description:
BACKGROUND OF THE INVENTION 
       [0001]    1. Field of the Invention 
         [0002]    The present invention relates to a liquid injection type screw compressor comprising a pair of male and female screw rotors that are installed in a space surrounded by a bore face within a casing of the compressor, while a liquid such as oil or water is injected to the bore face; whereby, a lip part is provided so as to prevent the liquid from flowing-back to a working gas inlet side, being placed on the bore face, within a range from a suction seal line (a suction closure line or a suction containment boundary locus) to a line parallel thereto apart from the suction seal line, by a distance equal to one screw pitch (a tooth groove distance in the rotor axis direction) of the rotors. 
         [0003]    In hitherto known liquid injection type screw compressors, a pair of a male screw rotor and a female screw rotor within a casing of the compressor are engaged in each other, so as to form a working/operation space inside which a liquid such as oil or water is injected whereby a working substance of a gas-liquid mixing phase is pressurized. The liquid injection brings the screw compressor a cooling function, a sealing function, and a lubricating function; thus, the compressor of the type obtains high efficiency even during a low speed operation, becoming widespread in the industry. 
         [0004]    The bore faces forming the working space within the casing of the compressor are important elements so as to secure gas/liquid tightness, when the working space is under a compression process where a gas seal across adjacent tooth spaces is required; consequently, it is a prerequisite to keep the clearance between the addendum circles of the rotors (tooth tip surfaces of the rotors) and the bore faces as small as possible. In this specification, the bore faces in the part as mentioned are called main bore faces. 
         [0005]    On the other hand, a gas leakage between adjacent tooth spaces does not effect on the performance of the compressor when working spaces are under gas suction process; therefore, the bore faces in the associated part as mentioned are expanded toward outside in comparison with the main bore faces so that a power consumption is reduced by evading useless possible friction between the bore faces and the tooth tips; thus, the bore faces in the part as mentioned are called expanded bore faces. 
         [0006]    In conventional liquid injection type screw compressors as described above, a weir (a lip part) is provided therein so as to prevent oil from scattering through a suction side end face of the rotor casing toward a gas inlet side; thus, it is intended to preserve the compressor volumetric efficiency and reduce the compressor power loss. 
         [0007]    Conventional screw compressors with such a weir as mentioned are disclosed, for instance, in a patent literature 1 (JP patent: 1967-10027), a patent literature 2 (JP: 1991-194183) and a patent literature 3 (JP: 1999-13661). 
         [0008]    The  FIGS. 1 and 2  in the patent literature 1 disclose that a lip (weir)  44  is provided between a gas inlet  24  and an expanded bore part  40  so as to lessen a heat exchange between a hot back-flow gas from a compression space formed in a rotor tooth space, and a flow-in gas from the gas inlet  24 . 
         [0009]    On the other hand, the  FIG. 1  in the patent literature  2  discloses a lip (weir)  39  that is provided at a suction side end-face of a casing  3  so that the lip  39  prevents a back-flow oil from flowing from expanded bore parts  7  and  8  back to a gas inlet side, from warming-up an inhaled gas, and also from deteriorating a charging efficiency of the inhaled gas to be charged into a rotor teeth space. 
         [0010]    Moreover, the patent literature  3  discloses that the oil injected into a working space flows back to a gas inhaling space; thereby, an oil mist generated from the back-flow oil suspends in the gas inhaling space, while the oil mist heats up the inhaled gas under a suction process; namely, a phenomenon, what is called inhaled gas heating, occurs; thus, the phenomenon increases a temperature of the gas to be compressed as well as expands a volume thereof; as a result, in a displacement type compressor that needs to inhale a gas of a constant specific volume, not only a reduction of mass-throughput but also a deterioration of volumetric efficiency are brought. 
         [0011]    In order to evade the above-mentioned difficulties, according to the patent literature  3 , as shown in  FIG. 2  of the patent literature  3  a lip part  5  is provided at a suction side end-face of a casing  3  that accommodates the rotors, so that the lip part  5  protrudes inside, i.e. toward screw rotors; further, a heat-up prevention wall (a baffle plate)  8  to close a gap between the screw rotors and the lip part  5  is provided so as to prevent an inhaled gas from leaking toward a gas inlet side. 
         [0012]      FIGS. 9   a  and  9   b  that are attached to this application shows a casing for conventional screw rotors; for explanatory convenience,  FIG. 9   a  shows a divided upper half and  FIG. 9   b  shows a divided lower half. In  FIGS. 9   a  and  9   b , a space that accommodates a male rotor and a female rotor is formed inside the casing  01 ; thereby, the boundary of the space comprises:
       a male rotor side main-bore-face  02   a  that faces a male rotor tooth tip with a slight clearance A 1 ,   a female rotor side main-bore-face  02   b  that faces a female rotor tooth tip with a slight clearance A 2 ,   a male rotor side expanded-bore-face  03   a  that faces a male rotor tooth space during a gas suction process, and a male rotor tooth tip with a clearance B 1  greater than the mentioned clearance A 1 , and   a female rotor side expanded-bore-face  03   b  that faces a female rotor tooth space during a gas suction process, and a female rotor tooth tip with a clearance B 2  greater than the mentioned clearance A 2 .         
         [0017]    Further, a lip part  04  is provided along a suction side end-face of a casing  01  so that the lip part  04  of the casing  01  protrudes inside, toward screw rotors; on the other hand, a suction seal line (a suction containment boundary locus)  05  is formed on a boundary between the male rotor side main-bore-face  02   a  and the male rotor side expanded-bore-face  03   a  as well as between the female rotor side main-bore-face  02   b  and the female rotor side expanded-bore-face  03   b.    
         [0018]    In the configuration as stated above, a working space is formed with a tooth space of the male rotor and another working space is formed with a tooth space of the female rotor, the pair of tooth spaces being independent; whereby, the tooth spaces are engraved on an outer periphery of rotors along a screw tooth spiral. While the working spaces are communicated with the expanded-bore-faces  03   a  or  03   b , the working spaces are gradually expanded to a maximum volume, inhaling a gas through a gas inlet; then, the working spaces pass through the suction seal line (the suction containment boundary locus)  05 , and the working spaces form a closed space the boundary of which includes a male rotor side main-bore-face  02   a  and a female rotor side main-bore-face  02   b . Thus, after the working space becomes a closed space, the volume of the working spaces is gradually reduced and a confined gas within the space is compressed; at a last stage of compression, the gas inside the spaces is discharged through a discharge opening. 
         [0019]    During the mentioned compression process, a liquid such as oil or water is injected into the working space, for the purpose of cooling, sealing, and lubricating. 
         [0020]      FIGS. 10   a  and  10   b  schematically depicts bore faces of a conventional screw rotor casing.  FIG. 10   a  shows a transparently perspective view seen from the top, depicting a suction seal line and a lip part.  FIG. 10   b  is a development of  FIG. 10   a.    
         [0021]    In  FIGS. 10   a  and  10   b , the reference numeral  01   a  denotes a male rotor side casing, and the numeral  01   b  does a femamale rotor side casing  01   b ; a suction seal line  05  is formed on a boundary between a male rotor side main-bore-face  02   a  and the male rotor side expanded-bore-face  03   a  as well as between the female rotor side main-bore-face  02   b  and the female rotor side expanded-bore-face  03   b ; a lip part  04  of the casing  01  protrudes inside, toward screw rotors. 
         [0022]    The working (operation) spaces formed with the male rotor and the female rotor face the male rotor side expanded-bore-face  03   a  and the female rotor side expanded-bore-face  03   b , while the working spaces gradually increase during a suction process, inhaling a gas through a gas inlet. After the volume of the working spaces reaches a maximum volume and the working spaces cross the suction seal line  05 , the spaces form a sealed space, being surrounded by the main-bore-faces  02   a  and  02   b . Subsequently, as the volume of the working spaces is reduced, the gas confined in the spaces is compressed. And the compressed gas is discharged through a discharge opening at a discharge side end face  07  of the rotor casing. 
         [0023]    In the above situation, the liquid such as oil or water injected into the working spaces leaks toward a lower pressure suction side and accumulates in the concaved expanded bore faces  03   a / 03   b . The lip part  04  prevents the liquid from leaking and scattering toward the gas suction end face  06  of the rotor casing. 
         [0024]    Patent literatures:
       Patent literature 1, JP 1967-10027;   Patent literature 2, JP 1991-194183;   Patent literature 3, JP 1999-13661.       
 
       DISCLOSURE OF THE INVENTION 
     Problem to be Solved by the Invention 
       [0028]    In spite of the disclosure according to the configuration such as in the patent literature 3, the conventional technologies are insufficient in sealing a liquid within the working spaces as well as in preventing deterioration as to volumetric efficiency; the insufficiency is caused on the ground that great distances remain between rotor tooth tips and the lip part  04  ( 04   a  and  04   b  in  FIGS. 10   a  and  10   b ) placed at the suction side end face of the rotor casings. 
         [0029]    As just mentioned above, the lip part is provided at the suction side end face of the rotor casings in conventional liquid injection screw compressors; thus, a gas inlet has to be placed outside across the suction side end face; moreover, the lip part lessens a gas inlet passage area (opening area) around the suction side end face of the rotor casings; therefore, in case of manufacturing a mono-block casting of the rotor casings and the gas inlet casing, it becomes difficult to allocate a casting core for rotor casing bores. 
         [0030]    Further, in conventional ways, only by means of lengthening rotor space in the axial direction, it is possible to secure a sufficient gas inlet passage for inhaling a gas into the working space; in addition, insufficient inlet passage area enhances suction resistance during a high-speed operation. 
         [0031]    Because of the above-mentioned situations, it is conventionally difficult to obtain a mono-block casting of the rotor casings and the gas inlet casing. That is, in casting, it is necessary to manufacture the rotor casing and the gas inlet casing separately; further, it becomes necessary to provide each casing with an essentially useless part such as an additional flange that is needed for assembling the parts. Thus, an increased whole weight and an intricate production process are brought; further, as mentioned above, in a high speed operation, there arise difficulties such as an increased gas suction resistance as well as a lessened volumetric efficiency. 
         [0032]    In view of the mentioned subjects in conventional liquid injection type screw compressors, the goals of the present invention are:
       preventing a liquid such as oil or water from leaking outside the working spaces of high compression, which are formed by screw rotors, toward the gas inlet side during a compression process, more effectively than conventional ways;   lessening a gas suction resistance of a gas flow into the rotor casings from an outside gas inlet so as to improve volumetric efficiency of the inhaled gas, as a result; and   realizing an liquid injection type screw compressors of a simplified structure so as to bring manufacturing cost reduction.       
 
         [0036]    Further, the invention aims at realizing a liquid injection type screw compressor provided with a variable compression ratio mechanism, that is, an internal volume ratio adjusting valve; wherein, the compressor has a compact structure so as to not prolong a manipulation mechanism of the internal volume ratio adjusting valve, making manufacturing cost be further reduced. 
       Means to Solve the Problem 
       [0037]    In order to attain the mentioned goals, the present invention proposes a liquid injection type screw compressor comprising of:
       a pair of a male rotor and a female rotor,   a rotor casing comprising a pair of bores that accommodate the pair of the male rotor and the female rotor,   a gas inlet and a gas outlet that are connected to the pair of the bores, the gas inlet being provided at a first end part of the rotor casing, while the gas outlet being provided at a second end part of the rotor casing, and   a lip part that is provided on a surface of the bores and protrudes inside so as to prevent the liquid on the surfaces of bores from back-flowing toward the gas inlet, the lip part being located at a gas upstream side of a suction seal line of the rotor casing;   wherein the lip part is placed within a range between the suction seal line and a line that is apart from the suction seal line, by one screw pitch distance of the screw rotors, toward the expanded-bore-face side of the male rotor side casing and/or the female rotor side casing (namely, toward the gas inlet side).       
 
         [0043]    In a screw compressor according to the present invention, a lip part for preventing liquid from back-flowing toward a gas inlet is provided on a casing bores, within a range between a suction seal line and a line that is apart from the suction seal line, by one screw pitch distance of the screw rotors, toward the expanded-bore-face side of the male rotor side casing and/or the female rotor side casing; hence, the lip part is placed nearer to the suction seal line in comparison with conventional ways; as a result, a liquid leakage from the compressed working spaces toward the gas inlet side is effectively prevented; further, the lip part placed nearer to the suction seal line makes it possible to eliminate a part of bore faces that is located at the gas inlet side from the lip part. So can be realized a simplified configuration of rotor casings with a reduced bore surface as well as a reduced suction resistance and a reduced manufacturing cost which are attributable to the simplification. 
         [0044]    A preferable configuration of the present invention may comprise:
       a straight development-line portion of the suction seal line in a development view, lying at right angles to a bore intersection line that is defined as a common generating line of a male rotor bore and a female rotor bore,   a lip-entering-edge of the lip part that is placed apart from the suction seal line toward the gas inlet side in a rotor axis direction, whereby the lip-entering-edge in response to the above-mentioned straight-line portion is bent so as to protrudes toward the suction seal line, and   a lip ending (trailing) edge of the lip part whereby the lip ending edge in response to the straight-line portion is placed parallel thereto so as to form a straight line portion of the lip ending edge in a development view, and   a thickened (wide in the rotor axis direction) lip part in response to the straight-line portion.       
 
         [0049]    The above preferable configuration can surely prevent a liquid leakage around a neighborhood along the bore intersection line. 
         [0050]    According to a further preferable aspect of the above configuration,
       the straight line portion of the suction seal line in a development view lies at right angles to the bore intersection line, and starts from a cross-point of the bore intersection and the suction seal line on the male bore surface as far as a point on the suction seal line on the female bore surface,   the lip-entering-edge of the lip part is placed apart from the suction seal line toward the gas inlet side in the rotor axis direction, and the lip-entering-edge in response to the above-mentioned straight-line portion is bent so as to protrudes toward the suction seal line; wherein, a part of the lip-entering-edge in response to the straight line portion starts from a cross-point of the bore intersection line and the lip-entering-edge on the male bore surface, as far as a point on the lip-entering-edge on the female bore surface,   the lip ending (trailing) edge of the lip part in response to the straight-line portion is placed parallel thereto so as to form the straight line portion of the lip ending edge in a development view, and   the thickened (wide in the rotor axis direction) lip part is provided in response to the straight-line portion, whereby a straight line portion of the ending edge starts from a cross-point of the bore intersection and the lip-ending-edge on the male bore surface, as far as a point on the lip-ending-edge on the female bore surface.       
 
         [0055]    The above configuration can surely prevent a liquid leakage around the bore intersection line. 
         [0056]    Another preferable aspect of the invention according to the mentioned configuration is the liquid injection type screw compressor, wherein the rotor casing with the gas inlet casing is formed in one piece or a plurality of divided-pieces from the lip ending edge toward a gas downstream side. Thus, the gas inlet side bore surface of the rotor casing can be omitted in a way that the lip part is located nearer to the suction seal line; as a result, it becomes possible to form a gas inlet casing and a rotor casing in one body. 
         [0057]    Consequently, the invention realizes a smaller rotor casing, saving an installation space; in addition, the invention greatly relieves restrictions concerning a position where a gas inlet casing is disposed in a rotor casing; in this regard, the degree of freedom as to the gas inlet casing design can be greatly expanded. 
         [0058]    According to a further preferable aspect of the invention, a labyrinth structure is embodied on the inner surface which faces rotor tooth tips in the lip part. For example, a pertinent roughness of the surface (e. g. a pertinent casting surface roughness) or an intended uneven surface can realize lesser liquid leakage. 
         [0059]    According to another preferable aspect of the invention, different outer diameters are applied to a pair of the male rotor and the female rotor so that the outer diameter of the male rotor is greater than that of the female rotor, and the number of the male rotor teeth is fewer than that of the male rotor teeth in a case when the same outer diameter is applied to a pair of the male rotor and the female rotor. 
         [0060]    In this way, a screw pitch distance of the male rotor can be shortened and the lip part can be located nearer to the suction seal line; thus, the liquid leakage can be further surely prevented; in addition, the geometry of the casings can be simplified. 
         [0061]    According to another preferable aspect of the invention, the lip part is provided at the lower side of the casing bore surfaces. In this configuration, the liquid accumulated by gravity at the bottom of the bore surfaces can be easily prevented from scattering toward the gas inlet side; thus, a simple structure can be realized. 
         [0062]    Another preferable aspect of the invention according to the mentioned configuration is a liquid injection type screw compressor comprising:
       a slide valve (capacity control valve), and   an internal volume ratio (U i ) adjusting valve; whereby, the slide valve has   a cut-out part, at a discharge end thereof, which regulates a gas discharge throat between a discharge end part (of gas discharge side) of the slide valve and an end face (of gas discharge side) of the rotor casing, and   a valve driving rod (a pushrod) that is prolonged toward the gas inlet casing on a rotor end face so that the valve driving rod protrudes across the gas inlet casing, through a storage space of the internal volume ratio adjusting valve that is provided on a side of the gas inlet casing which comes in contact with the rotor end face, the valve driving rod being connected to a drive source i.e. a hydraulic cylinder in order that the slide valve can move forward and backward along an axis of the driving rod by means of the drive source and the driving rod,   while the internal volume ratio (U i ) adjusting valve in the storage space is placed adjacent to a gas inlet side end face of the capacity control valve (a slide valve), with a positioning means that adjusts variably the position of the internal volume ratio (U i ) adjusting valve, along a direction to/from a gas discharge side,   wherein an internal volume ratio (U i ) is adjusted such that the positioning means shifts the internal volume ratio (U i ) adjusting valve to a predetermined position, while an internal gas capacity (that is equivalent to a gas density at a compression commencement) is adjusted by by-passing an inhaled gas back to the gas inlet side through a gap between the internal volume ratio (U i ) adjusting valve, and the capacity control valve (a slide valve) that slides to and fro along the driving rod direction by means of the drive source, through the driving rod.       
 
         [0069]    The installation of an internal volume ratio (U i ) adjusting valve makes a whole compressor compact, realizing a compressor of three kinds of compression ratios, namely, of lower/medium/higher compression ratios, without changing a gas inlet casing, only by replacing a rotor casing. Thus, a gas inlet casing can be applied to these kinds of compressors in common. 
         [0070]    On the other hand, conventional compressors are apt to be of a large size, as a positioning means to position the internal volume ratio (U i ) adjusting valve is prolonged toward a gas discharge side, penetrating a gas discharging casing so as to be used for setting (positioning) the valve. 
         [0071]    In order to solve the difficulty, according to a further preferable aspect of the present invention, the positioning means comprises:
       a hollow shaft which is placed concentric to the driving rod, having a screw part on an outer surface of the hollow shaft so that the screw part is engaged into a corresponding screw part inside the internal volume ratio adjusting valve, and   a rotation rod that is placed so as to intersect with the hollow shaft in order that the rod can transmit a rotational driving movement of the rod to the hollow shaft, via a connection part; whereby, the rotational movement transmitted to the hollow shaft is transformed into a to-and-fro movement of the internal volume ratio adjusting valve, through the mentioned screw engagement, so that the internal volume ratio adjusting valve is positioned to a predetermined position.       
 
         [0074]    According to the above aspect, there is no need to prolong a positioning means as in conventional approaches; a driving mechanism to position the internal volume ratio-adjusting valve can be formed as a compact one. The mentioned connection part between the hollow shaft and the rotation rod may be a bevel gear pair or a crossed helical gear pair. 
       Effect of the Invention 
       [0075]    In a screw compressor according to the disclosed invention, a lip part for preventing liquid from back-flowing toward a suction inlet is provided on a casing bores, within a range between a suction seal line and a line that is apart from the suction seal line, by one screw pitch distance of the screw rotors, toward the expanded-bore-face side of the male rotor side casing and/or the female rotor side casing. 
         [0076]    Therefore, a liquid leakage scattering during a compression process from the compressed working space formed by the screw rotors toward the gas inlet side can be effectively prevented. 
         [0077]    Moreover, the lip part placed nearer to the suction seal line makes it possible to eliminate a part of the rotor casing at the gas inlet side from the lip part. So can be realized a simplified configuration of rotor casings with a reduced bore surface as well as a reduced suction resistance of an inhaled gas and an enhanced volumetric efficiency of the compressor. 
         [0078]    Further, the lip part placed nearer to the suction seal line makes it possible to eliminate a part of the rotor bore faces at the gas inlet side from the lip part. Hence, the rotor casing can be formed in one body with a gas inlet casing. As a result, manufacturing processes can be simplified and a manufacturing cost can be reduced. Consequently, the disclosed invention greatly relieves restrictions regarding installation position of a gas inlet casing in a rotor casing. Further, the degree of freedom as to the gas inlet casing design can be greatly expanded; in addition, a compact casing can be realized and a compressor installation space can be reduced. 
         [0079]    Also as already explained, in a screw compressor according to the disclosed invention, the compressor comprises:
       a straight development-line portion of the suction seal line in a development view, lying at right angles to a bore intersection line that is defined as a common generating line of a male rotor bore and a female rotor bore,   a lip-entering-edge of the lip part that is placed apart from the suction seal line toward the gas inlet side in a rotor axis direction, whereby the lip-entering-edge in response to the above-mentioned straight-line portion is bent so as to protrudes toward the suction seal line, and   a lip ending (trailing) edge of the lip part whereby the lip ending edge in response to the straight-line portion is placed parallel thereto so as to form a straight line portion of the lip ending edge in a development view, and   a thickened (wide in the rotor axis direction) lip part in response to the straight-line portion.       
 
         [0084]    Thus, the above configuration can surely prevent a liquid leakage around a neighborhood along the bore intersection line. 
         [0085]    Further, in a screw compressor according to the disclosed invention, the compressor comprises:
       the straight line portion of the suction seal line in a development view lies at right angles to the bore intersection line, and starts from a cross-point of the bore intersection and the suction seal line on the male bore surface, as far as a point on the suction seal line on the female bore surface,   the lip-entering-edge of the lip part is placed apart from the suction seal line toward the gas inlet side in the rotor axis direction, and the lip-entering-edge in response to the above-mentioned straight-line portion is bent so as to protrudes toward the suction seal line; wherein, a part of the lip-entering-edge in response to the straight line portion starts from a cross-point of the bore intersection and the lip-entering-edge on the male bore surface, as far as a point on the lip-entering-edge on the female bore surface,   the lip ending (trailing) edge of the lip part in response to the straight-line portion is placed parallel thereto so as to form the straight line portion of the lip ending edge in a development, and   the thickened (wide in the rotor axis direction) lip part is provided in response to the straight-line portion, whereby a straight line portion of the ending edge starts from a cross-point of the bore intersection and the lip-ending-edge on the male bore surface, as far as a point on the lip-ending-edge on the female bore surface.       
 
         [0090]    Thus, the above configuration can surely prevent a liquid leakage around a neighborhood along the bore intersection line. 
         [0091]    Further, in a screw compressor according to the disclosed invention, different outer diameters are applied to a pair of the male rotor and the female rotor so that the outer diameter of the male rotor is greater than that of the female rotor, and the number of the male rotor teeth is fewer than that of the male rotor teeth in a case when the same outer diameter is applied to a pair of the male rotor and the female rotor. 
         [0092]    In this manner, a screw pitch distance of the male rotor can be shortened and the lip part can be located nearer to the suction seal line; thus, the liquid leakage can be further surely prevented; in addition, the geometry of the casings can be simplified. 
         [0093]    Further, in a screw compressor according to the disclosed invention, the compressor comprises:
       a slide valve (capacity control valve), and   an internal volume ratio (U i ) adjusting valve; whereby, the slide valve has   a slide valve (capacity control valve), and an internal volume ratio (U i ) adjusting valve; whereby, the slide valve has   a cut-out part, at a discharge end thereof, which regulates a gas discharge throat between a discharge end part (of gas discharge side) of the slide valve and an end face (of gas discharge side) of the rotor casing, and   a valve driving rod (a pushrod) that is prolonged toward the gas inlet casing on a rotor end face so that the valve driving rod protrudes across the gas inlet casing, through a storage space of the internal volume ratio adjusting valve that is provided on a side of the gas inlet casing which comes in contact with the rotor end face, the valve driving rod being connected to a drive source in order that the slide valve can move forward and backward along an axis of the driving rod by means of the drive source and the driving rod,   whereas the internal volume ratio adjusting valve in the storage space is placed adjacent to a gas inlet side end face of the capacity control valve (a slide valve), with a positioning means that adjusts variably the position of the internal volume ratio adjusting valve, along a direction to/from a gas discharge side,   wherein an internal volume ratio is adjusted such that the positioning means shifts the internal volume ratio adjusting valve to a predetermined position, while an internal gas capacity is adjusted by by-passing an inhaled gas back to the gas inlet side through a gap between the internal volume ratio adjusting valve, and the capacity control valve (a slide valve) that slides to and fro along the driving rod direction by means of the drive source, through the driving rod.       
 
         [0101]    According to the above disclosure, the installation of an internal volume ratio (U i ) adjusting valve can make a whole compressor compact, realizing a compressor of three kinds of compression ratios, namely, of lower/medium/higher compression ratios, without changing a gas inlet casing, only by replacing a rotor casing. Thus, a gas inlet casing can be applied to these kinds of compressors in common. 
         [0102]    Still further, in a screw compressor according to the disclosed invention, the compressor comprises a positioning means for positioning the internal volume ratio-adjusting valve, the positioning means comprising:
       a hollow shaft which is placed concentric to the driving rod, having a screw part on an outer surface of the hollow shaft so that the screw part is engaged into a corresponding screw part inside the internal volume ratio adjusting valve, and   a rotation rod that is placed so as to intersect with the hollow shaft in order that the rod can transmit a rotational driving movement of the rod to the hollow shaft, via a connection part; whereby, the rotational movement transmitted to the hollow shaft is transformed into a to-and-fro movement of the internal volume ratio adjusting valve, through the mentioned screw engagement, so that the internal volume ratio adjusting valve is positioned to a predetermined position.       
 
         [0105]    According to the above aspect, there is no need to prolong a positioning means as in conventional approaches; a driving mechanism to position the internal volume ratio-adjusting valve can be formed as a compact one. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS  
         [0106]    The present invention will now be described in greater detail with reference to the preferred embodiments of the invention and the accompanying drawings, wherein: 
           [0107]      FIG. 1   a  shows a transparently perspective view seen from a top as to a first embodiment of the present invention; 
           [0108]      FIG. 1   b  is a development view of  FIG. 1   a;    
           [0109]      FIG. 2   a  shows a perspective view of an upper side rotor-casing seen from the inside thereof, as to a first embodiment; 
           [0110]      FIG. 2   b  shows a perspective view of a lower side rotor-casing seen from the inside thereof, as to the first embodiment; 
           [0111]      FIG. 3  shows a perspective view of apart of a rotor casing as to the first embodiment; 
           [0112]      FIG. 4  shows a longitudinal plan view of a second embodiment of the present invention; 
           [0113]      FIG. 5  shows a longitudinal section view concerning the second embodiment; 
           [0114]      FIG. 6  explains a development view showing a suction seal line (a suction containment boundary locus) as to each of the male/female rotors that have different tip diameters; 
           [0115]      FIG. 7  gives an explanation about the male/female rotors that have different tip diameters; 
           [0116]      FIG. 8  shows a perspective view as to a variation of the second embodiment; 
           [0117]      FIG. 9   a  shows a perspective view of an upper side rotor-casing seen from the inside thereof, as to a conventional compressor; 
           [0118]      FIG. 9   b  shows a perspective view of a lower side rotor-casing seen from the inside thereof, as to a conventional compressor; 
           [0119]      FIG. 10   a  shows a transparently perspective view seen from the top as to a conventional compressor in consideration of a schematic explanation for bore faces thereof; and 
           [0120]      FIG. 10   b  is a development view of  FIG. 10   a.    
       
    
    
     REFERENCE NUMERALS  
       [0000]    
       
           01   a ,  1   a , and  11   a  a male rotor side casing; 
           01   b ,  1   b , and  11   b  a female rotor side casing; 
           02   a  and  2   a  a male rotor side main-bore-face; 
           02   b  and  2   b  a female rotor side main-bore-face; 
           03   a  and  3   a  a male rotor side expanded-bore-face; 
           03   b  and  3   b  a female rotor side expanded-bore-face; 
           04 ,  4 , and  33  a lip part; 
           4   c  and  33   c  a thickened lip part; 
           4   d  and  33   d  a lip entering edge; 
           4   e  and  33   e  a lip ending (trailing) edge 
           05 ,  5 , and  32  a suction seal line (a suction containment boundary locus) 
           5   c  and  32   c  a straight line portion of a suction seal line in a development view 
           06  and  6  a suction side end face 
           07  and  7  a discharge side end face 
           08 ,  8 , and  34  a bore intersection line (that is defined 
         as a common generating line of a male rotor bore and a female rotor bore) 
           9  and  12  a gas inlet (a suction inlet) 
           11  a rotor casing 
           13  a gas inlet casing 
           14  a male rotor shaft 
           15  a female rotor shaft 
           16  and  19  a thrust bearing 
           17 ,  18 ,  20 , and  21  a radial bearing (a journal bearing) 
           22  a male rotor 
           23  a female rotor 
           24  a mechanical seal 
           25  a discharge outlet (a gas outlet) 
           26  a gas outlet casing 
           27  and  36  a tightening bolt 
           28  a slide valve (a capacity control valve) 
           28   a  a cut-out part 
           29  a pushrod (a valve driving rod for manipulating a capacity control valve) 
           30  an oil-hydraulic cylinder (for driving a capacity /displacement-volume control valve) 
           31  an internal volume ratio (U i ) control device of a manual operation type 
           35  a casing 
           37  an internal volume ratio (U i ) adjusting valve for adjusting compression ratio U i    
           38  a hollow shaft 
           39   a  and  39   b  a bevel gear (a movement communicating part) 
           40  a rotation-rod 
           41  a discharge opening 
         “a” in  FIG. 4  an intersection point of a suction seal line and a bore intersection line 
         “b” in  FIG. 4  an intersection point of a lip entering edge and a bore intersection line 
         “c” in  FIG. 4  an intersection point of a lip ending (trailing) edge and a bore intersection line 
       
     
       DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0164]    Hereafter, the present invention will be described in detail with reference to the embodiments shown in the figures. However, the dimensions, materials, shape, the relative placement and so on of a component described in these embodiments shall not be construed as limiting the scope of the invention thereto, unless especially specific mention is placed. 
         [0165]      FIG. 1   a  shows a transparently perspective view seen from the top as to a first embodiment of the present invention;  FIG. 1   b  is a development view of  FIG. 1   a ;  FIG. 2   a  shows a perspective view of an upper side rotor-casing seen from the inside thereof, as to the first embodiment;  FIG. 2   b  shows a perspective view of a lower side rotor-casing seen from the inside thereof, as to the first embodiment;  FIG. 3  shows a perspective view of a part of a rotor casing as to the first embodiment;  FIG. 4  shows a longitudinal plan view of a second embodiment of the present invention;  FIG. 5  shows a longitudinal section view concerning the second embodiment;  FIG. 6  explains a suction seal line (a suction containment boundary locus) as to each of the male/female rotors that have different tip diameters;  FIG. 7  gives an explanation about the male/female rotors that have different tip diameters;  FIG. 8  shows a perspective view as to a variation of the second embodiment; 
       FIRST EMBODIMENT  
       [0166]      FIGS. 1   a  and  1   b  schematically depict a bore face in a rotor casing of a screw compressor according to the present invention;  FIG. 1   a  shows a perspective view as to a suction seal line (a suction containment boundary locus) and a lip part on the bore face seen transparently from a top; and,  FIG. 1   b  is a development view of  FIG. 1   a ; in  FIGS. 2   a  and  2   b , the rotor-casing is divided into an upper side part and a lower side part so that the bore face of the casing is easily explained. 
         [0167]    In a male rotor side casing la and a female rotor side casing  1   b  of  FIGS. 1   a ,  1   b ,  2   a ,  2   b , and  3 , a suction seal line (a suction containment boundary locus)  5  is formed on a boundary between main bore faces  2   a / 2   b  and expanded bore faces  3   a / 3   b , whereby the main bore faces  2   a / 2   b  are located opposite to addendum circles of the a male rotor and a female rotor, with a slight clearance, while a lip part  4  as a protruding part is provided apart from the suction seal line  5 , by a screw pitch distance to a suction side end face  6 . Here, an example of dimension data is such that a clearance between the main bore faces  2   a / 2   b  and the addendum circles of the a male rotor and a female rotor is substantially 0.05 mm to 0.125 mm (a clearance to a diameter c/D=0.8 to 1.0/1000), while a distance between the expanded bore faces  3   a / 3   b  and the addendum circles of the rotors is substantially 5 mm (a clearance to a diameter c/D=0.05 to 0.06). It is noted hereby that c and d denote a clearance and a diameter respectively. 
         [0168]    The suction seal line  5  includes a curved part  5   a  that is on a main bore face of the male rotor side casing  1   a , a curved part  5   b  that is on a main bore face of the female rotor side casing  1   b , and a curved part  5   c  that is also on the main bore face of the female rotor side casing  1   b ; whereby, in the development figures of  FIGS. 1   a  and  1   b , the curved part  5   c  is seen as a straight line which starts from a point “a” that is a cross point of the curved part  5   a  and a bore intersection line  8 ; further, in  FIGS. 1   a  and  1   b , the straight line lies at right angles to the bore intersection line  8 , while the straight line ends a point where the line intersects with the curved part  5   b.    
         [0169]    On the other hand, in response to the suction seal line  5 , the geometry of the lip part  4  comprises:
       a lip-entering-edge  4   d  of the lip part  4   c  that is placed apart from the suction seal line, within one screw pitch distance, toward the gas inlet side along a rotor axis direction, whereby the lip-entering-edge in response to the above-mentioned straight-line  5   c  is bent so as to protrudes toward the suction seal line; wherein, a part of the lip-entering-edge in response to the straight line portion starts from a cross-point “b” of the bore intersection line  8  and the lip-entering-edge on the male bore surface, as far as a point on the lip-entering-edge on the female bore surface,   a lip ending (trailing) edge  4   e  of the lip part  4   c  whereby the lip ending edge in response to the straight-line  5   c  is placed parallel thereto so as to form a straight line portion of the lip ending edge in a development view; wherein, a straight line portion of the ending edge starts from a cross-point “c” of the bore intersection line  8  and the lip-ending-edge on the male bore surface, as far as a point on the lip-ending-edge on the female bore surface, and   a thickened (wide in the rotor axis direction) lip part  4   c  in response to the straight-line portion  5   c.          
 
         [0173]    Liquid such as oil or water injected into a compression working space is apt to leak toward a lower pressure suction side and accumulates in concaved expanded bore faces  3   a / 3   b . The lip part  4  prevents the liquid from leaking and scattering toward a gas inlet side. 
         [0174]    According to the first embodiment as described above, the distance between the suction seal line  5  and the lip part  4  is substantially within one screw pitch distance; thus, the lip part  4  is provided at a location closer to the suction seal line  5  in comparison with conventional ways. Therefore, in comparison with conventional ways, is effectively prevented a liquid leakage that scatters, during a compression process, from the compressed working space which is formed by the screw rotors toward the gas inlet side. Moreover, the lip part placed nearer to the suction seal line makes it possible to eliminate a part of the rotor casing, located at the gas inlet side from the lip part. So can be realized a simplified configuration of rotor casings with a reduced bore surface as well as a reduced suction resistance of an inhaled gas and an enhanced volumetric efficiency of the compressor. 
         [0175]    Further, in the above embodiment, a straight line portion  5   c  of the suction seal line  5  is provided in the neighborhood of the bore intersection line, the line lying at right angles with the bore intersection line in a development view. In addition, a thickened lip part  4   c  is provided, comprising:
       a lip-entering-edge  4   d  of the lip part  4   c  that is placed apart from the suction seal line, within one screw pitch distance, toward the gas inlet side in a rotor axis direction, wherein the lip-entering-edge in response to the above-mentioned straight-line portion  5   c  is bent so as to protrudes toward the suction seal line; and   a lip ending (trailing) edge  4   e  of the lip part  4   c , being placed parallel to the straight line portion  5   c  so as to form a straight line portion of the lip ending edge in a development view; wherein, the straight line portion of the ending edge is vertical to the bore intersection line  8  in a development.       
 
         [0178]    In this manner, can be surely prevented a liquid leakage around the neighborhood along the bore intersection line, toward a gas inlet side, from the working (compression) spaces which are formed by the male female rotors. 
         [0179]    Moreover, it becomes possible to eliminate a part from the lip part  4  toward a side of the gas inlet  9  in the rotor casing; in addition, a simplified configuration of rotor casings can be realized. Further, since the gas inlet casing can be placed nearer to the rotor casing, the rotor casing can be formed in one body together with the gas inlet casing. As a result, manufacturing processes can be simplified and a manufacturing cost can be reduced. 
       SECOND EMBODIMENT  
       [0180]    A second embodiment of the present invention is now detailed with reference to  FIGS. 4 to 8 . As shown in  FIG. 7 , in the second embodiment a male rotor and a female rotor of different rotor sizes, namely different outer diameters, are used; where the outer diameter of the male rotor is larger than that of the female rotor, and the number of teeth as to the male rotor is  5 , while that as to the female rotor is  6 . 
         [0181]    In  FIGS. 4 and 5 , the reference numeral  11  denotes the rotor casing that accommodates both the male rotor and the female rotor, and the rotor casing  11  together with a gas inlet casing  13  that forms a gas inlet  12  is made of mono casting. The rotor casing  11  accommodates the male rotor  22  and the female rotor  23  shown in  FIG. 7 , here the detail of the rotors is omitted. The reference numeral  14  denotes a male rotor shaft that is supported by a thrust bearing  16  and radial bearings  17 / 18 , while the numeral  15  denotes a female rotor shaft that is supported by a thrust bearing  19  and radial bearings  20 / 21 . 
         [0182]    A mechanical seal  24  is provided near a shaft end part  14   a  of the male rotor shaft  14 , the shaft end part  14   a  being connected to an output shaft of a drive motor (not shown) as a power source. 
         [0183]    A gas outlet casing  26  that forms a gas outlet  25  is made of casting; however, the casing  26  is made of different casting from the rotor casing  11 , and the casing  26  is fastened thereto with tightening bolts  27 . At a lower part of the rotor casing  11 , is provided a slide valve (a capacity control valve)  28  that makes it possible to regulate a compressor capacity (an inhaled gas capacity) by means of sliding-manipulation along an axis direction of the rotors; thereby, a pushrod (a driving rod)  29  regulates a length as to the sliding-manipulation of the slide valve  28 . In addition, the pushrod  29  is operated through an oil pressure that is supplied to a left cylinder room  30   a  and a right cylinder room  30   b  in an oil-hydraulic cylinder  30 . 
         [0184]    At the middle part of the pushrod  29 , is installed a U i -control device (an internal volume ratio control device)  31  of a manual operation type; hereupon, the device  31  makes it possible to optimize the internal volume ratio U i . A casing  35  that contains the U i -control device  31  is fastened to the gas inlet casing  13  with tightening bolts  36 , while the oil-hydraulic cylinder  30  is fitted to the casing  35 . The reference numeral  37  denotes an internal volume ratio (U i ) adjusting valve; thereby, the U i -adjusting valve  37  is engaged into a screw part  38   a  that is provided on an outer face of a hollow shaft  38 . Here, the hollow shaft  38  is installed around the pushrod  29  having a round cross-section, so that a round hollow cylinder of the hollow shaft  38  and the round cross-section of the pushrod  29  are concentric, and the hollow shaft  38  can rotate freely around the pushrod  29 . Further, the U i -adjusting valve  37  moves along the rotor axes with a rotational movement of the hollow shaft  38 . 
         [0185]    On the other hand, the reference numeral  39   a  denotes a bevel gear that is fitted to a suction-side end part of the hollow shaft  38 , while the bevel gear  39   a  is engaged in a corresponding bevel gear  39   b  that is fitted to an end part of a rotation-rod  40 ; hereupon, it is noted that the axes of the hollow shaft  38  and the rotation-rod  40  lie at right angles to each other. 
         [0186]    According to the above-mentioned configuration, when the rotation-rod  40  is rotated, either clockwise or counterclockwise, a rotational movement is transmitted to the hollow shaft  38 ; as a result, the U i -adjusting valve  37  moves back and forth along an rotor axis, through an engagement of the screw part  38   a  and the U i -adjusting valve  37 . A steering wheel (not shown) or the like may be fitted to the rotation-rod  40  so as to enable an operator to turn the wheel by hand in case of manual control. 
         [0187]    When the internal volume ratio (U i ) is adjusted, the following sequence of manipulations is performed: rotating the rotation-rod  40  under a stop condition of the compressor; making the U i -adjusting valve  37  move along an rotor axis; as a result, thrusting the slide valve  28  toward the gas outlet  25 ; adjusting an opening level of a discharge opening  41  that is formed between a cut-out part  28   a  provided at a discharge-front end side of the slide valve  28 , and the gas outlet casing  26 ; thus, initializing the internal volume ratio (U i ). 
         [0188]    In addition, when a capacity of the compressor needs to be adjusted, the slide valve  28  is shifted along the axes of the rotors through a movement of the pushrod  29 ; thereby, a by-passed gas flow toward the gas inlet side from a gap between the slide valve  28  and the pushrod  29  controls the capacity (the inhaled gas flow quantity). 
         [0189]      FIG. 6  shows the male rotor  22 , the female rotor  23 , and the suction seal line  32  in the second embodiment, in which the male rotor  22  and the female rotor  23  of different rotor sizes, namely, different outer diameters, are used, where the outer diameter of the male rotor is larger than that of the female rotor; in addition, the number of teeth as to the male rotor is  5 , while the number of teeth spaces as to the female rotor is  6 . 
         [0190]    Incidentally, in  FIG. 4 , are shown the suction seal line  32  and the lip part  33 , for explanation use. Similar to  FIG. 1  as to the first embodiment, the lip part  33  is provided apart from the suction seal line  5 , by a screw pitch distance, toward the gas inlet side. 
         [0191]    As shown in  FIGS. 4 and 6 , the suction seal line  32  comprises:
       a curved part  32   a  on the bore in the male rotor casing  11   a,      a curved part  32   b  on the bore in the female rotor casing  11   b , and   a straight line portion  32   c  in a development view whereby the straight part lies at right angles to the bore intersection line  34 ; wherein, the straight line starts from a cross-point “a” of the bore intersection line  34  and the curved part  32   a , as far as a point on the curved part  32   b  on the bore in the female rotor casing  11   b.          
 
         [0195]    Further, the lip part  33  comprises a male casing side lip part  33   a  on the bore in the male rotor casing  11   a , and a female casing side lip part  33   b , while the boundary of the lip part  33  comprises a lip-entering-edge and a lip ending (trailing) edge; hereupon, the lip part  33  is away from the suction seal line, within a screw pitch distance. 
         [0196]    Still further, the lip-ending-edge comprises:
       a straight line portion  33   e , in response to the straight line  32   c  of the suction seal line  32 , and lying at right angles to the bore intersection line  34  in a development view, while the line portion  33   e  starts a cross-point “c” of the bore intersection line  8  and the lip-ending-edge on the bore in the male rotor casing  11   a , as far as a point of the lip-ending-edge on the bore in the female rotor casing  11   b ; in addition,   the lip-entering-edge comprises:   a bent curve portion  33   d , in response to the straight line portion  32   c  of the suction seal line  32 , whereby the bent curve portion  33   d  protrudes toward the straight line portion  32   c  of the suction seal line  32 , while the bent curve portion  33   d  starts a cross-point “b” of the bore intersection line  8  and the lip-entering-edge on the bore in the male rotor casing  11   a , as far as a point of the lip-entering-edge on the bore in the female rotor casing  11   b.          
 
         [0200]    In the above-mentioned manner, a thickened lip part  33   c  is formed with the bent curve portion  33   d  and the line portion  33   e , in response to the straight line portion  32   c  of the suction seal line  32 . So can be surely prevented a liquid leakage around the neighborhood along the bore intersection line, toward a gas inlet side, from the working (compression) spaces in the rotor casing  11 . 
         [0201]    According to the second embodiment, in the same way as the first embodiment, the lip part  33  is provided apart from the suction seal line  5 , by a screw pitch distance, toward the gas inlet side; thus, can be surely prevented a liquid leakage around the neighborhood along the bore intersection line, toward a gas inlet side, from the working (compression) spaces. Further, since the lip part is provided around the neighborhood along the bore intersection line as mentioned above, a liquid leakage around the bore intersection line can be surely prevented. 
         [0202]    Moreover, can be eliminated a part of the rotor casing on the gas inlet side of the lip part  33 . Thus, can be secured a satisfactory space that communicates the bore faces of the rotor casing to the gas inlet  12 , the space reducing a suction resistance of the gas inhaled from the gas inlet  12 . As a result, a volumetric efficiency of the compressor can be enhanced. 
         [0203]    On the other hand, by means of eliminating a part of the rotor casing the part which is located on the gas inlet side of the lip part, the location of the gas inlet  12  can be shifted toward the rotor casing  11 . Thus, the rotor casing  11  together with a gas inlet casing  13  that forms a gas inlet  12  can be made of mono casting. In this way, a compact casing can be realized and a compressor installation space can be reduced. Consequently, a compact casing can be realized, a compressor installation space can be reduced, a compressor manufacturing cost can be greatly lowered, and the degree of freedom as to the gas inlet casing design about the rotor axis direction can be expanded. 
         [0204]    Further, it becomes possible to design a compressor casing of the same kind compressors so that a distance L between an axis “i” of the gas inlet  12  and an axis “o” of the gas outlet  25  can be kept constant. Therefore, a manufacturing line of the compressor casings can be streamlined so as to mechanized and robotized. 
         [0205]    The installation of an internal volume ratio (U i ) adjusting valve makes a whole compressor compact, realizing a compressor with three kinds of compression ratios , namely, of lower/medium/higher compression ratios, without changing sorts of a gas inlet casing, only by replacing a rotor casing. Thus, a gas inlet casing can be applied to these kinds of compressors in common. Namely, even if the rotor-casing is replaced by another one for constituting a different kind (capacity) of the compressor, it is not necessary to exchange the gas inlet casing. 
         [0206]    Further, conventional compressors are apt to be of a large size, as a positioning means to position the internal volume ratio (U i ) adjusting valve is prolonged toward a gas discharge side, penetrating a gas outlet casing so as to be used for positioning the valve. Contrary to the above, the second embodiment comprises a positioning means for positioning the internal volume ratio-adjusting valve including: 
         [0207]    a hollow shaft  38  , and
       a rotation rod  40  that is placed so as to intersect with the hollow shaft with right angles in order that the rod can transmit a rotational driving movement of the rod to the hollow shaft, via a bevel gear pair  39   a / 39   b.          
 
         [0209]    According to the above configuration, there is no need to prolong a positioning means as in conventional approaches; a driving mechanism to position the internal volume ratio-adjusting valve  37  can be formed as a compact one. 
         [0210]    Incidentally, for the connection part between the rotation rod  40  and the hollow shaft  38 , a crossed helical gear pair may be applied instead of a bevel gear pair; a bevel gear pair tends to have a play to some extent between meeting gears, while a crossed helical gear has little play. 
       INDUSTRIAL APPLICABILITY 
       [0211]    According to the present invention regarding a liquid injection type screw compressor, a liquid leakage, such as an oil leakage or a water leakage, that flows back to a gas inlet side from a compression room which is formed screw rotors is further effectively prevented in comparison with conventional compressors of the same kind. In addition, suction resistance of the gas inhaled from the gas inlet can be lowered, and volumetric efficiency as to the inhaled gas can be improved; further, cast modeling of a rotor casing can be simplified and a manufacturing cost can be reduced. 
         [0212]    Thus, the invention greatly contributes to a practical compressor industry. 
         [0213]    This is a continuation of International Application PCT/JP2005/0020041 (published as WO 2007-0542322) having an international filing date of Oct. 31, 2005. The disclosure of the priority application, in its entirety, including the drawings, claims, and the specification thereof, is incorporated herein by reference.

Technology Classification (CPC): 5