• 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 comprising: a low pressure stage of the compressor body, a high pressure stage of the compressor body which further compresses the compressed air which has been compressed by the low pressure stage of the compressor body, gear gears for example respectively provided, for example, on a male rotor of the low pressure stage of the compressor body and, for example on a male rotor of the high pressure stage of the compressor body, a motor, a main ring for example provided on a rotating shaft of the motor, and an intermediate shaft rotatably supported and provided with a gear pinion which meshes with the main ring gear, and a main ring gear which meshes with the gear pinions. Therefore, it is possible to make the motor have a relatively low rotational speed while preventing the toothed wheels from increasing in diameter, thereby achieving a reduction in cost.
    公开号:BE1019083A5
    申请号:E2006/0314
    申请日:2006-06-08
    公开日:2012-03-06
    发明作者:Hiroshi Ohta；Hitoshi Nishimura；Tomoo Suzuki
    申请人:Hitachi Ind Equipment Sys；
    IPC主号:
    专利说明:

    "Screw compressor"
    Prior art of the invention
    The present invention relates to a screw compressor, and more particularly to a large capacity screw compressor that generates compressed air.
    The screw compressors comprise a male rotor and a female rotor whose rotating shafts are parallel to each other and which rotate so that spiral teeth thereof meshing with each other, and a housing which houses in its within the male rotor and the female rotor. A plurality of compression working chambers are defined by tooth grooves of the male rotor and the female rotor and an inner wall of the housing. Compression work chambers are reduced in volume to compress the air while moving in an axial direction as the male rotor and the female rotor rotate.
    Conventionally, the construction of a two-stage type screw compressor is disclosed by way of example and comprises: a low pressure stage of the compressor body, an intercooler which cools the compressed air from the body of the compressor; compressor low pressure stage, a high pressure stage of the compressor body which further compresses the compressed air cooled by the intercooler, and a final cooler which cools the compressed air from the high pressure stage of the compressor body ( for example, see JP-A-2002-155879). According to the related art, gear wheels are respectively mounted on the rotor shafts (either of a male rotor or a female rotor) of the low pressure stage of the compressor body and the high pressure stage. of the compressor body. The gear wheels engage respectively in a main ring which is mounted on a rotary shaft of a motor (electric motor). When the motor is actuated, a rotational power of the motor is transmitted and multiplied by the main ring gear and the gear wheels, whereby the low pressure stage of the compressor body and the high pressure stage of the compressor body are respectively driven. .
    However, the related art leaves the next room for improvement.
    That is, according to the related art, a multiplication ratio is determined by a ratio of a primitive operating diameter of the main crown of a motor side to the pitch diameter of the gear pinion on one side compressor body, and a power of the motor is multiplied in a stage according to the multiplication ratio for respectively driving the low pressure stage of the compressor body and the high pressure stage of the compressor body. Therefore, in order to obtain a predetermined multiplication ratio in a large compressor unit generating, for example, several hundred kilowatts (kW), it is necessary to increase the diameter of the main ring of the motor side corresponding to the Gear pinion on the compressor body side, or decrease a gear ratio to increase the engine rotational speed. In the case where the toothed wheel must be of large diameter, the manufacture sometimes becomes difficult in terms of manufacturing means (for example, limiting a working range performed by a machine tool). As a result, the cost of the gears or the motor increases.
    Brief summary of the invention
    An object of the present invention is to provide a screw compressor by ensuring that its motor has a relatively low rotational speed while avoiding increasing the diameter of the toothed wheels, which provides a reduction in costs.
    (1) In order to achieve this object, the invention provides a screw compressor comprising: a compressor body, a rotor side gear on a rotor shaft of the compressor body, a motor, a gear wheel on the side motor provided on a rotary shaft of the motor, and a rotatably supported intermediate shaft provided with a first multiplier which meshes with the toothed wheel on the motor side, and a second multiplier which meshes with the toothed wheel on the opposite side. rotor.
    According to the invention, there is provided an intermediate shaft with a first multiplier which meshes with the toothed wheel on the motor side, and a second multiplier which meshes with the toothed wheel on the rotor side. A multiplication ratio of the engine side gear to the first multiplier, and a multiplication ratio of the second multiplier to the rotor side gear makes the rotor side gear at the first multiplier and a second multiplication ratio of the second multiplier. at the rotor-side toothed wheel rotational power of the rotary shaft of the motor is multiplied in two stages and transmits it, thereby rotating the rotor shaft of the compressor body.
    Therefore, by comparison for example with the case where the toothed wheel on the motor side and the gear wheel on the rotor side mesh with each other to achieve an increase in speed in a stage, it is possible to to ensure that the motor has a relatively low speed of rotation while avoiding to increase the diameter of the gears, which makes it possible to obtain a reduction of the costs.
    (2) In order to achieve this object, the invention provides a screw compressor comprising: a low pressure stage of the compressor body, a high pressure stage of the compressor body which further compresses the compressed air by the low pressure stage of the compressor body, a plurality of rotor side gears respectively provided on the rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body, a motor, a gear wheel on the motor on a rotary shaft of the motor, and a rotatably supported intermediate shaft provided with a first multiplier which meshes with the toothed wheel on the motor side and a second multiplier which meshes with the plurality of toothed wheels on the opposite side. rotor.
    (3) In (1) and (2), the rotary shaft of the motor and the rotor shaft of the compressor body are preferably arranged parallel to each other, and the motor and the compressor body are arranged up and down on one side in axial directions of these.
    Therefore, by comparison for example with the case where a motor is arranged on one side in an axial direction and a compressor body is disposed on the other side in the axial direction, the entire axial dimension composed of the motor, the compressor body, etc., can be shortened. Therefore, an arrangement of the compressor unit can be improved by the freedom of layout.
    (4) In (3), the rotary shaft of the motor and the rotor shaft of the compressor body are preferably arranged with their axial directions oriented in a direction of the small width of the compressor unit.
    (5) In order to achieve the objective, the invention also provides a screw compressor comprising: a low pressure stage of the compressor body, a high pressure stage of the compressor body which further compresses the compressed air by the stage low pressure of the compressor body, a plurality of rotor side gears respectively provided on the rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body, a motor, a gear wheel on the motor side provided on a rotary shaft of the motor, a rotatably supported intermediate shaft provided with a first multiplier which meshes with the toothed wheel on the motor side, and a second multiplier which meshes with the plurality of wheels. toothed on the rotor side, a gearbox which houses within it the toothed wheel on the motor side, the first multiplier, the intermediate shaft, the second multip rotor and the gears on the rotor side, a first cooling device which cools the compressed air coming from the low pressure stage of the compressor body, and a second cooling device which cools the compressed air coming from the upper stage compressor body pressure, wherein the motor, the gearbox, the low pressure stage of the compressor body and the high pressure stage of the compressor body are arranged at the center of the compressor unit, the first device The cooling device is arranged on one side in a direction of the large width of the compressor unit and the second device is disposed on the other side in a direction of the large width of the compressor unit.
    As described in (3), for example, when the rotary shaft of the motor and the rotor shaft of the high pressure stage of the compressor body are arranged parallel to one another and the motor, the low pressure stage of the compressor body and the high pressure stage of the compressor body are arranged upwardly and downwardly on one side in axial directions thereof, the entire axial dimension composed of the motor, the low pressure stage the compressor body, the high pressure stage of the compressor body, etc. can be shortened. As a result, the axial directions of the rotary shaft of the motor and the rotor shaft of the low pressure stage of the compressor body and the high pressure stage of the compressor body can be arranged in the direction of the small width of the compressor unit. The engine, the gearbox, the low pressure stage of the compressor body, the high pressure stage of the compressor body are arranged at the center of the compressor unit, and sandwiching them, the first and second devices. are respectively arranged on one side and the other in the direction of the large width of the compressor unit. Therefore, it is possible to arrange the elements in the compressor unit efficiently and well balanced, which allows to give a small size to the entire unit.
    (6) In (5), the rotary shaft of the motor and the rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body are arranged parallel to each other with their directions. axially oriented in a direction of the small width of the compression unit, and the motor, the low pressure stage of the compressor body and the high pressure stage of the compressor body are arranged upwardly and downwardly. one side in the axial directions.
    (7) In (6), the low pressure stage of the compressor body is disposed on one side in a direction of the large width of the compressor unit in the gearbox, and the high pressure stage of the compressor body is arranged on the other side in the direction of the large width of the compressor unit in the gearbox.
    As a result, it is possible to shorten a connecting pipe between the low pressure stage of the compressor body and the first cooling device, and a connecting pipe between the high pressure stage of the compressor body and the second cooling device. cooling.
    (8) In any one of (5) to (7), the first and second cooling devices preferably comprise respectively: a conduit provided in a substantially vertical direction, a fan provided in the conduit for generating a current of cooling air, and a heat exchanger for compressed air, provided upstream of the fan in the duct for exchanging heat with a cooling air stream to cool the compressed air from the low pressure stage of the body of compressor or the high pressure stage of the compressor body.
    (9) In (8), the conduit is preferably connected to an air intake port and an exhaust port of the compression unit, an inlet space is formed between the port of air intake and the heat exchanger for compressed air, and an exhaust space is formed between the fan and the exhaust port.
    Therefore, by comparison for example with the case where no intake space is formed between the air inlet and the heat exchanger for compressed air, and the case where no exhaust space is formed between the fan and the exhaust port, it is possible to reduce the noise leak generated in the compressed air heat exchanger, etc.
    (10) In (8), one or both of the first and second cooling devices are provided with a plurality of compressed air heat exchangers, and the plurality of compressed air heat exchangers are arranged in a juxtaposed manner. to the flow of the cooling air stream.
    In a large capacity compressor unit, for example, a compressed air heat exchanger is large, and sometimes becomes difficult to manufacture in existing production facilities (for example, because of a size problem). oven or the like). According to the invention, a plurality of compressed air heat exchangers are provided and they are arranged juxtaposed with the flow of the cooling air stream in the conduit. As a result, the individual compressed air heat exchanger is small and therefore it is possible to facilitate its manufacture even if its size is limited by an existing production facility or the like. In addition, the pressure loss is reduced compared to the case where, for example, a plurality of compressed air heat exchangers are arranged in series, so that the power required for a fan can be reduced.
    (11) In (10), the fans are preferably provided in the plural so as to mate with the plurality of heat exchangers and are arranged juxtaposed with each other.
    (12) In (10), the plurality of compressed air heat exchangers are preferably arranged juxtaposed with each other in the direction of the small width of the compressor unit.
    (13) In (8), the compressed air heat exchanger is preferably provided so as to be inclined with respect to. a vertical flow of the cooling air stream in the conduit.
    In this way, by tilting the compressed air heat exchanger, it is possible to shorten a dimension in the direction of the small width of the compressor unit.
    (14) In (8), one or both of the first and second cooling devices are preferably provided with a plurality of compressed air heat exchangers, and the plurality of compressed air heat exchangers are inclined relative to the vertical flow of a cooling air stream in the duct and are arranged side by side therewith, and oil heat exchangers are provided between the plurality of compressed air heat exchangers .
    According to the invention, it is possible to manufacture a motor with a relatively low speed of rotation while avoiding increasing the diameter of the gears, which makes it possible to achieve a reduction in costs.
    Other objects, elements and advantages of the invention will become apparent from the following description of the embodiments of the invention taken in conjunction with the accompanying drawings.
    Brief description of several views of the drawings Figure 1 is a plan view showing the construction of a first embodiment of a screw compressor according to the invention; Figure 2 is a side view as seen in the direction of the arrow II in Figure 1; Figure 3 is a side view as seen in the direction of the arrow III in Figure 1; Figure 4 is a side view, in cross section taken along a cross-section IV - IV in Figure 1; Figure 5 is a side view, in cross-section taken along a V-V cross-section in Figure 1; Figure 6 is a plan view, in perspective, showing the construction of a second embodiment of a screw compressor according to the invention; Figure 7 is a plan view, in perspective, showing in a side view the construction of the second embodiment of a screw compressor according to the invention; Fig. 8 is a perspective side view showing the compressor unit as viewed in the direction of arrow VIII in Fig. 6; Fig. 9 is a perspective side view showing the compressor unit as viewed in the direction of arrow IX in Fig. 6; Fig. 10 is a perspective side view showing a first cooling device as viewed in the direction of arrow X in Fig. 6; and Fig. 11 is a perspective side view showing a second cooling device as seen in the direction of arrow XI in Fig. 6.
    Detailed description of the invention
    Embodiments of the invention will be described below with reference to the drawings.
    A first embodiment of the invention will be described with reference to Figures 1 to 5.
    Figure 1 is a plan view showing the construction of a screw compressor according to the invention. FIG. 2 is a side view as seen in a direction indicated by an arrow II in FIG. 1. FIG. 3 is a side view as seen in a direction indicated by an arrow III in FIG. 4 is a side view, in cross-section taken along a cross-section IV - IV in FIG. 1, and FIG. 5 is a side view, in cross-section taken along a V - V cross section. in Figure 1 (only one inside of a box is shown).
    In FIGS. 1 to 5, there is provided: a low pressure stage 2 of the compressor body which compresses the air sucked therein through an intake butterfly valve 1 (not shown in the drawings but illustrated in the drawings) subsequent) at an intermediate pressure, a high pressure stage 3 of the compressor body which further compresses the compressed air which has been compressed by the low pressure stage 2 of the compressor body to a predetermined discharge pressure, a motor ( electric motor) 4 and a gearbox 5 housing therein a gear mechanism (the details of which are described below) which transmits a rotational power of the engine 4 to the low pressure stage of the compressor body 2 and to the high pressure stage 3 of the compressor body. In addition, an oil reservoir (not shown) is provided in a lower region inside the gearbox 5.
    The motor 4 is fixed on a motor frame 6. The motor frame 6 is mounted on a base 7 with a plurality of vibration-resistant rubber parts therebetween. A rotary shaft 4a of the motor 4 is rotatably supported via, for example, a radial bearing 4b provided on a loaded side (on the right in FIG. 2 and on the left in FIG. 3) and, for example , a thrust bearing 4c provided on an unloaded side (left in Figure 2 and right in Figure 3) to be rotated. A flange 4d of the motor 4 is fixed to a lateral surface of one side (of a lower side in FIG. 1, on the left in FIG. 2 and on the right in FIG. 3) of the gearbox 5 by means of of bolts 9. An opening is formed on said lateral surface of the gearbox 5 to correspond to the flange 4d of the engine 4, and a main ring 10 is mounted on the leading end of the rotary shaft 4a of the engine 4 in the gearbox 5, which is inserted through the opening.
    The low pressure stage 2 of the compressor body is a screw compressor of a type, for example, oil-free (operating with a compression working chamber interior in an oil-free state) comprising a male rotor 2a and a female rotor 2b whose rotation shafts are parallel to each other and which rotate so that their spiral teeth intermesh in one another. On one end (on the lower side in Figure 1 and on the left in Figure 2) of the male rotor 2a and the female rotor 2b are respectively mounted synchronization gears (not shown). As a result, the male rotor 2a and the female rotor 2b rotate in a contact and oil free state. A flange 2c of the low pressure stage 2 of the compressor body is fixed on a lateral surface of the gearbox 5 by means of bolts 11 so as to be positioned above (on the upper side in FIGS. 4) of the flange 4d of the motor 4. The male rotor 2a is disposed on the inside (on the left in FIG. 4) and the female rotor 2b is placed on the outside (on the right in FIG. 4) so as to be parallel to the rotary shaft 4a of the engine 4. An opening is formed on a side surface of the gearbox 5 to correspond to the flange 2c of the low pressure stage 2 of the compressor body, and a gear pinion 12 is mounted on a head end of the male rotor 2a on the other side (on an upper side in FIG. 1 and on the right in FIG. 2), the leading end being inserted through the opening.
    Similarly, the high pressure stage 3 of the compressor body is a screw compressor of a type, for example, oil-free comprising a male rotor 3a and a female rotor 3b whose rotation shafts are parallel to each other and which rotate in such a way that their spiral teeth intermesh with each other. On one end (on the lower side in FIG. 1 and on the left in FIG. 2) of the male rotor 3 a and the female rotor 3 b are respectively synchronizing gears (not shown). As a result, the male rotor 3a and the female rotor 3b rotate in a contact and oil free state. A flange 3c of the high pressure stage 3 of the compressor body is fixed on a lateral surface of the gearbox 5 by means of bolts 13 so as to be positioned above the flange 4d of the engine 4. The male rotor 2a is disposed inside (on the right in FIG. 4) and the female rotor 3b is placed on the outside (on the left in FIG. 4) so as to be made parallel to the rotary shaft 4a of the motor 4. An opening is formed on a side surface of the gearbox 5 to correspond to the flange 3c of the compressor body of the high-pressure stage 3, and a gear gear 14 is mounted on a head end of the male rotor 3a. on the other side (on an upper side in Figure 1 and on the left in Figure 2), the leading end being inserted through the opening.
    An intermediate shaft 16 is provided in the gearbox 5 and is rotatably supported, for example, by a thrust bearing 15A and a radial bearing 15B, the intermediate shaft 16 being made parallel to the rotary shaft 4a of the motor 4, the male rotor 2a of the low pressure stage 2 of the compressor body, the male rotor 3a of the high pressure stage 3 of the compressor body, and the like. The radial bearing 15B is provided, for example, on one side of the gearbox, and the thrust bearing 15A is provided, for example, on a bearing support 17 mounted on the opposite side (on the upper side of the gearbox). Figure 1, on the right in Figure 2, and on the left in Figure 3) of the gearbox 5. A cover 18 is mounted on the bearing support 17.
    Mounted on the intermediate shaft 16 a gear pinion 19 (first multiplier) which meshes with the main ring gear 10 on the rotary shaft 4a of the engine 4, and a main ring 20 (second multiplier) which meshes in the pinion gear 12 on the male rotor 2a of the low pressure stage 2 of the compressor body and in the pinion 14 on the male rotor 3a of the high pressure stage 3 of the compressor body. A pitch diameter of operation of the pinion gear 19 on the intermediate shaft 16 is smaller than that of the main ring gear 10 on the rotary shaft 4a of the engine 4, so that the rotary power of the rotary shaft 4a of the motor 4 is increased in speed and is transmitted to the intermediate shaft 16 via the main ring gear 10 and pinion 19. A primitive operating diameter of the main ring 20 on the intermediate shaft 16 is more large than that of the pinion gear 12 on the male rotor 2a of the low pressure stage 2 of the compressor body and that of the pinion gear 14 on the male rotor 3a of the high pressure stage 3 of the compressor body , so that a rotational power of the intermediate shaft is multiplied and is respectively transmitted to the male rotor 2a of the low pressure stage 2 of the compressor body and to the male rotor 3a of the high press stage 3 of the compressor body via the main ring gear 20 and pinions 12, 14.
    Thus, according to the embodiment, the intermediate shaft 16 is provided to include the gear pinion 19 which meshes with the main ring gear 10 on the rotary shaft 4a of the engine 4, and the main ring gear 20 which engages in the gear pinion 12 provided on the male rotor 2a of the low pressure stage 2 of the compressor body and in the pinion gear 14 provided on the male rotor 3a of the high pressure stage 3 of the compressor body . A multiplication ratio of the main crown 10 and the gear pinion 19, and a multiplication ratio of the main ring 20 and the gear pinion 12 (or the main ring 20 and the gear pinion 14) makes that a rotational power of the rotary shaft 4a of the motor 4 is multiplied in two stages and transmits it, thereby rotating the male rotor 2a of the low pressure stage 2 of the compressor body (or the male rotor 3a of the high pressure stage 3 of the compressor body).
    Therefore, in comparison with the case where, for example, the main ring provided on the rotary shaft 4a of the motor 4 meshes respectively with the gear gears provided on the male rotors 2a, 2a to provide an increase of speed in a stage, the motor 4 can have a relatively low rotational speed while avoiding that the gears increase in diameter. That is, it is even possible to respond to the case where, for example, the gears in a large capacity compressor unit generating several hundred kilowatts are limited in size in terms of manufacturing capability, and facilitate their manufacture. In addition, a quadrupole motor can, for example, be used for the motor 4 which has a relatively low rotational speed. Therefore, it is possible to achieve a reduction in costs.
    In addition, by preventing an increase in diameter of the gears, it is possible to prevent the gearbox 5 from being large. By decreasing the rotational speed of the motor 4, this reduces the load and it is possible to increase the reliability of parts such as bearings, etc.
    Moreover, by providing the motor 4, the low pressure stage 2 of the compressor body and the high pressure stage 3 of the compressor body on one side (in other words, one side of the rotary shaft 4a and male rotors 2a, 3a in an axial direction) of the gearbox 5, the entire axial dimension composed of the motor 4, the low pressure stage 2 of the compressor body, the high pressure stage 3 of the body of the compressor, etc. can be shortened by comparison with the case where, for example, the motor is disposed on one side of the gearbox 5, and the low pressure stage 2 of the compressor body and the high pressure stage 3 of the compressor body are arranged on the other side. Therefore, an arrangement of a compressor unit (see a second embodiment) described later can be improved by freedom of arrangement.
    Figures 6 to 11 show a second embodiment of the invention. The embodiment is that of a compressor unit on which the first embodiment is mounted.
    Fig. 6 is a perspective plan view showing a compressor unit representative of the construction of a screw compressor according to the embodiment (a fan, a fan motor and an oil cooler are not shown for convenience) and showing a compressed air system. Fig. 7 is a perspective plan view showing the compressor unit representative of the construction of a screw compressor according to the embodiment (an inlet butterfly valve, a fan and a fan motor are not not shown for convenience) and showing an oil system. Fig. 8 is a perspective side view showing the compressor unit as viewed in a direction indicated by arrow VIII in Fig. 6 and showing the compressed air system and the oil system. Fig. 9 is a perspective side view showing the compressor unit as viewed in a direction indicated by arrow IX in Fig. 6 (an inlet butterfly valve is not shown for convenience) ) and showing the compressed air system. FIG. 10 is a perspective side view showing a first cooling device as seen in a direction indicated by the arrow X in FIG. 6, and FIG. 11 is a perspective side view showing a second cooling device as seen in a direction indicated by the arrow XI in Figure 6 (a feed pipe is not shown for convenience). In Figs. 6 to 11, parts equivalent to those in the first embodiment are indicated by the same reference numerals as in this and an explanation is therefore omitted as appropriate.
    In the embodiment, a large capacity compressor unit 21 (a production of the order of several hundred kilowatts) is a monoblock type compressor unit covered by an acoustic insulation cover 22 or the like. The motor 4, the gearbox 5, the low-pressure stage 2 of the compressor body, and the high-pressure stage 3 of the compressor body are mounted in the center of the base 7. As described in the first embodiment , since the entire axial dimension composed of the motor 4, the low pressure stage 2 of the compressor body, the high pressure stage 3 of the compressor body, etc. is relatively short, the axial directions of the rotary shaft 4a of the motor 4, the male rotor 2a and the female rotor 2b of the low pressure stage 2 of the compressor body, and the male rotor 3a and the female rotor 3b of the the high pressure stage 3 of the compressor body are oriented in a direction of the small width (a vertical direction in FIGS. 6 and 7 of the compressor unit 21. That is to say that this arrangement makes it possible to shorten a W dimension of the compressor unit in the direction of the small width.
    A first cooling device 23 which cools the compressed air from the low pressure stage 2 of the compressor body is mounted on the base 7 on one side (right in FIGS. 6 to 8 and on the left in FIG. 9 ) of the compressor unit 21 in a small width direction with the motor 4, the gearbox 5, the low pressure stage 2 of the compressor body, and the high pressure stage 3 of the compressor body placed In the center. A second cooling device 24 which cools the compressed air from the high pressure stage 3 of the compressor body is mounted on the base 7 on the other side (left in FIGS. 6 to 8 and on the right in FIG. 9) of the compressor unit 21 in the direction of the large width. In this way, by arranging the first cooling device 23 and the second cooling device 24 independently and separately, it is possible to arrange the elements in the compressor unit 21 in an efficient and well-balanced manner.
    The low pressure stage 2 of the compressor body is disposed in the gearbox 5 on one side of the compressor unit 21 in the large width direction. As a result, it is possible to shorten a connecting pipe (a discharge pipe 25, etc. described later) between the low pressure stage 2 of the compressor body and the first cooling device 23. The high pressure stage 3 of the compressor body is disposed in the gearbox on the other side of the compressor unit 21 in the long width direction. As a result, it is possible to shorten a connecting pipe (a discharge pipe 26, etc. described later) between the high pressure stage 3 of the compressor body and the second cooling device 24.
    The first cooling device 23 comprises: a duct 27 disposed in a substantially vertical direction (a vertical direction in FIGS. 8 to 10) and connected to a first exhaust port 22a provided on an upper surface of the soundproofing cover 22, respectively 29A, 29B, upward (upwardly in FIGS. 8-10) fan motors in the conduit 27 and provided with fans 28A, 28B which generate a cooling air stream (represented by FIG. arrows in FIG. 10) directed upwards, intermediate coolers, respectively 30A, 30B, provided upstream (upwards in FIG. 10) of the fan motors 29A, 29B in the duct 27 to cool the air compressed from the low pressure stage 2 of the compressor body by heat exchange with a cooling air stream, and an air intake duct 31 connected to a lower side 27 of the duct 27 and connected to a first air inlet 22b provided on lower parts of the sides of the soundproofing cover 22.
    When the fans 28A, 28B are rotated when the motors 29A, 29B are actuated, outside air from the first air inlet 22b is introduced as the cooling air stream into the intake duct. air 31 and a cooling air stream in the conduit 27 flows upward to be discharged from the first exhaust port 22a through the intermediate coolers 30A, 30B and the fans 28A, 28B. At this time, the air intake duct 31 defines an intake passage 32 (inlet space) between the first air intake port 22b and the intermediate coolers 30A, 30B and an exhaust passage 33 (exhaust space) is also defined between the fans 28A, 28B in the duct 27 and the first exhaust port 22a. Therefore, by comparison, for example, with the case where the intake passage 32 and the exhaust passage 33 are not defined (more specifically, the case where the intermediate coolers are intended to be abutted against the first air inlet 22b and the case where the fans are intended to be abutted against the first exhaust port 22a), it is possible to reduce the noise leak generated by the intermediate coolers 30A, 30B, etc.
    The fans 28A, 28B are arranged juxtaposed with each other in the short width direction (a left and right direction in FIG. 10) of the compressor unit 21, and the intermediate coolers 30A, 30B are arranged juxtaposed with each other in the direction of the small width of the compressor unit 21 so as to mate respectively with the fans 28A, 28B (in other words, the intermediate coolers 30A , 30B are arranged juxtaposed with each other with respect to the flow of a cooling air stream in the conduit 27). The intermediate coolers 30A, 30B are respectively connected to the branch pipes 25a, 25b of the discharge pipe 25 connected to a discharge side of the low pressure stage 2 of the compressor body and are also connected to the branch pipes 34a, 34b a suction pipe 34 connected to a suction side of the high pressure stage 3 of the compressor body. The intermediate coolers 30A, 30B respectively use a cooling air stream which pass through fins 30a to cool the compressed air from the low pressure stage 2 of the compressor body, and supplies the cooled compressed air to the compressor. high pressure stage 3 of the compressor body. In this way, by providing the intermediate coolers 30A, 30B in two systems, it is possible to give a small size to the individual intercooler 30A or 30B and to facilitate the manufacture thereof even in the case where its size is restricted, for example, by existing manufacturing components, etc. By arranging the intermediate coolers 30A, 30B juxtaposed with the flow of a cooling air stream, the pressure loss is reduced by comparison, for example, with the case where the intermediate coolers are arranged in series, if although it is possible to reduce the energy required for the fan motors 29A, 29B.
    The intermediate coolers 30A, 30B are provided to be inclined with respect to the flow of a cooling air stream in a vertical direction within the conduit 27 (more specifically, they are provided to be inclined towards the outside and up in the short width direction of the compressor unit 21 and are arranged in a V configuration). As a result, it is possible to reduce a width dimension of the first cooling device, i.e. a W dimension of the compressor unit in the short width direction. The intercoolers may be provided to be inclined upwards in the short width direction of the compressor unit 21 and be placed parallel to each other.
    For purposes of efficient disposal, a jacket system oil cooler 35 is provided between the intermediate coolers 30A, 30B. Oil supplied by an oil pipe 37a from the oil reservoir into the gearbox 5 by an oil pump 36 is fed through the jacketed oil cooler 35 to exchange heat with a cooling air stream for cooling, and the cooled oil is supplied by an oil pipe 37b to a liquid cooled liner 1d of the low pressure stage of the compressor body 2. The oil having cooled the fluid circulation cooled jacket 1d of the low pressure stage 2 of the compressor body is introduced by an oil pipe 37c into the fluid circulation cooled jacket 3d of the high pressure stage 3 of the compressor body to be cooled, and is then returned by an oil pipe 37d to the oil reservoir in the gearbox 5.
    The second cooling device 24 is constructed in the same manner as the first cooling device 23 and comprises: a duct 38 disposed in a substantially vertical direction (a vertical direction in FIGS. 8, 9 and 11) and connected to a second orifice 22c exhaust provided on the upper surface of the sound insulation cover 22, respectively 40A, 40B, fan motors provided upward (upwards in Figures 8, 9 and 11) in the conduit 38 and provided with fans 39A, 39B which generate a cooling air stream (represented by arrows in Figure 11) directed upwards, final coolers, respectively 41A, 41B, provided upstream (downwards on the 11) of the fans 39A, 39B in the duct 38 for cooling the compressed air coming from the high pressure stage 3 of the compressor body by heat exchange with a cooling air stream. oidissement, and an air intake duct 42 connected to a lower side of the duct 38 and connected to a second air intake port 22d provided on the lower part of the side of the soundproofing cover 22.
    When the fans 39A, 39B are rotated when the motors 40A, 40B are actuated, outside air from the second air inlet 22d is introduced as a cooling air stream into the intake duct. air 42 and a cooling air stream in the conduit 38 flows upward to be discharged from the second exhaust port 22c through the final coolers 41A, 41B and the fans 39A, 39B. At this time, the air intake duct 42 defines an intake passage 43 (intake space) between the second air intake port 22d and the final coolers 41A, 41B and an air passage. Exhaust 44 (exhaust space) is also defined between the fans 39A, 39B in the duct 38 and the second exhaust port 22c. Therefore, compared with the case where, for example, the intake passage 43 and the exhaust passage 44 are not defined (more specifically, the case where the intermediate coolers are intended to be abutted against the second air inlet 22d and the case where the fans are intended to be abutted against the first exhaust port 22c), it is possible to reduce the noise leak generated by the final coolers 41A, 41B, etc.
    The fans 39A, 39B are arranged side by side in the direction of the small width (a left and right direction in FIG. 10) of the compressor unit 21, and the final coolers 41A, 41B are arranged juxtaposed with each other in the direction of the small width of the compressor unit 21 so as to mate respectively with the fans 39A, 39B (in other words, the final coolers 41A, 41B are arranged juxtaposed with each other with respect to the flow of a cooling air stream in the conduit 38). The final coolers 41A, 41B are respectively connected by non-return valves 45 to the branch pipes 26a, 26b of the discharge pipe 26 connected to a discharge side of the high pressure stage 3 of the compressor body and are also connected to branch pipes 46a, 46b of a supply pipe 46 which supplies compressed air to a user's side. The final coolers 41A, 41B respectively use a cooling air stream which passes through fins 41a for cooling compressed air from the high pressure stage 3 of the compressor body, and supplies the cooled compressed air to the compressor side. an user. In this way, by providing the final coolers 41A, 41B in two systems, it is possible to give a small size to the individual final cooler 41A or 41B and to facilitate the manufacture thereof even in the case where its size is restricted for example, by existing manufacturing components, etc. By arranging the final coolers 41A, 41B juxtaposed with the flow of a cooling air stream, the pressure loss is reduced compared to the case where, for example, the intermediate coolers are arranged in series, so that it is possible to reduce the energy required for the fan motors 40A, 40B.
    The final coolers 41A, 41B are provided to be inclined with respect to the flow of a cooling air stream in a vertical direction within the conduit 38 (more specifically, they are intended to be inclined towards the outside. outside and up in the direction of the small width of the compressor unit 21 and are arranged in a V configuration). As a result, it is possible to reduce a width dimension of the second cooling device 24, that is to say a dimension W of the compressor unit 21 in the small width direction. In addition, the final coolers 41A, 41B may be provided to be inclined upwards, for example, in the small width direction of the compressor unit 21 and be placed parallel to each other.
    For purposes of efficient disposal, an oil cooler of the lubrication system 47 is provided between the final coolers 41A, 41B. Oil supplied by an oil pipe 48a from the oil tank into the gearbox 5 by an oil pump 36 is fed through the oil cooler of the lubrication system 35 to exchange heat with a cooling air stream to be cooled, and the cooled oil is supplied by the oil pipes 48b, 48c to the carrier parts of the synchronous gear of the low pressure stage 2 of the compressor body and the high pressure stage 3 of the compressor body. The oil having cooled the carrier parts of the synchronization pinion of the low pressure stage 2 of the compressor body and the high pressure stage 3 of the compressor body is then brought back by an oil pipe 48d to the reservoir of the compressor. oil in the gearbox 5.
    As described above, according to the embodiment, it is possible to give a small size to the whole unit and it is possible to greatly produce the effect, in particular, in the compressor unit 21 of a type high capacity. In addition, the compressor unit 21 is made to be small, which consequently makes it possible to give the transport means a small size.
    It should further be understood by those skilled in the art that, although the foregoing description has been made on the basis of embodiments of the invention, the invention is not limited to these and various changes and modifications. modifications may be made without departing from the spirit of the invention and the scope of the appended claims.
    权利要求:
    Claims (20)
    [1]
    A screw compressor comprising: a compressor body, a rotor-side gear on a rotor shaft of the compressor body, a motor, a motor-side gear on a rotating shaft of the motor, and an intermediate shaft. rotatably supported and provided with a first multiplier which meshes with the toothed wheel on the motor side, and a second multiplier which meshes with the toothed wheel on the rotor side.
    [2]
    2. A screw compressor comprising: a low pressure stage of the compressor body, a high pressure stage of the compressor body which further compresses the compressed air which has been compressed by the low pressure stage of the compressor body, a plurality of gears on the rotor side respectively provided on rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body, a motor, a toothed gear on the motor side provided on a rotary shaft of the motor and a rotatably supported intermediate shaft provided with a first multiplier which meshes with the toothed wheel on the motor side, and a second multiplier which meshes with the plurality of toothed wheels on the rotor side.
    [3]
    A screw compressor according to claim 1, wherein the rotary shaft of the motor and the rotor shaft of the compressor body are arranged parallel to one another, and the motor and the compressor body are arranged upwards and down one side in an axial direction thereof.
    [4]
    The screw compressor according to claim 3, wherein the rotary shaft of the motor and the rotor shaft of the compressor body are arranged with their axial directions oriented in a direction of the small width of the compressor unit.
    [5]
    A screw compressor comprising: a low pressure stage of the compressor body, a high pressure stage of the compressor body which further compresses the compressed air which has been compressed by the low pressure stage of the compressor body, a plurality of wheels. rotor side teeth respectively provided on rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body, a motor, a motor-side gear on a rotary shaft of the motor, and a rotatably supported intermediate shaft provided with a first multiplier which meshes with the toothed wheel on the motor side, and a second multiplier which meshes with the plurality of toothed wheels on the rotor side, a gearbox which houses the gear wheel on the engine side, the first gearbox, the intermediate shaft, the second gearbox and the gears on the side a rotor, a first cooling device which cools the compressed air from the low pressure stage of the compressor body, and a second cooling device which cools the compressed air from the high pressure stage of the compressor body, wherein the motor, the gearbox, the low pressure stage of the compressor body, and the high pressure stage of the compressor body are centrally located in the compressor unit, the first cooling device is disposed of. one side in a large width direction of the compressor unit, and the second cooling device is disposed on the other side in the large width direction of the compressor unit.
    [6]
    A screw compressor according to claim 5, wherein the rotary shaft of the motor and the rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body are arranged in parallel between them with their axial directions oriented in a direction of the small width of the compressor unit, and the motor, the low pressure stage of the compressor body and the high pressure stage of the compressor body are arranged upwards and down on one side in the axial directions.
    [7]
    The screw compressor according to claim 6, wherein the low pressure stage of the compressor body is disposed at one side in the direction of the large width of the compressor unit in the compressor. gearbox, and the high pressure stage of the compressor body is disposed on the other side in the direction of the large width of the compressor unit in the gearbox.
    [8]
    The screw compressor according to claim 5, wherein the first and second cooling devices respectively comprise: a duct provided in a substantially vertical direction, a fan provided in the duct for generating a cooling air stream, and a heat exchanger for compressed air, provided upstream of the fan in the duct for exchanging heat with a current cooling air apparatus for cooling the compressed air from the low pressure stage of the compressor body or the high pressure stage of the compressor body.
    [9]
    The screw compressor according to claim 8, wherein the conduit is connected to an air intake port and an exhaust port of the compressor unit, an intake space is formed between the air inlet port and the exhaust port of the compressor unit. air intake and the heat exchanger for compressed air, and an exhaust space is formed between the fan and the exhaust port.
    [10]
    A screw compressor according to claim 8, wherein one or both of the first and second cooling devices are provided with a plurality of compressed air heat exchangers, and the plurality of compressed air heat exchangers are disposed juxtaposed with the flow of a cooling air stream.
    [11]
    The screw compressor according to claim 10, wherein the fans are plural provided to mate with the plurality of heat exchangers and are arranged juxtaposed to one another.
    [12]
    A screw compressor according to claim 10, wherein the plurality of compressed air heat exchangers are arranged juxtaposed with each other in the small width direction of the compressor unit.
    [13]
    The screw compressor according to claim 8, wherein the compressed air heat exchanger is provided to be inclined with respect to the vertical flow of a cooling air stream in the conduit.
    [14]
    The screw compressor according to claim 8, wherein one or both of the first and second cooling devices are provided with a plurality of compressed air heat exchangers, and the plurality of compressed air heat exchangers are inclined relative to the vertical flow of a cooling air stream in the duct and arranged in a juxtaposed manner thereto, and oil heat exchangers are provided between the plurality of compressed air heat exchangers .
    [15]
    A screw compressor comprising: a motor having a motor casing and a rotary shaft, a low pressure stage of the compressor body, driven by the motor, overlying a portion of the motor casing and having a rotor shaft parallel to the rotary shaft of the engine; a high pressure stage of the compressor body, which further compresses the compressed air by the low pressure stage of the compressor body, the high pressure stage of the compressor body being driven by the engine, being overlying a part of the compressor body; the motor casing and having a rotor shaft parallel to the rotary shaft of the motor and parallel to the rotor shaft of the low pressure stage of the compressor body; a plurality of rotor side gears respectively provided on the rotor shafts of the low pressure stage of the compressor body and the high pressure stage of the compressor body; a toothed gear on the motor side provided on a rotary shaft of the motor; and a rotatably supported intermediate shaft provided with a first multiplier which meshes with the toothed gear of the motor side and a second multiplier which meshes with the plurality of toothed wheels on the rotor side, wherein an axis longitudinal axis of the intermediate shaft is disposed in a radial position between a radial position of a longitudinal axis of the rotary shaft of the motor and radial positions of the longitudinal axes of the rotor shafts of the low pressure stage of the compressor body and of the high pressure stage of the compressor body.
    [16]
    The screw compressor according to claim 15, further comprising a gearbox housing the first rotor side gearwheel, the second rotor side gearwheel, the motorwheel gear, the first multiplier and the second multiplier.
    [17]
    The screw compressor according to claim 16, wherein the assembly of the rotary shaft of the motor, the motor casing and the rotor shafts of each of the low pressure stage of the compressor body and the stage. High pressure of the compressor body are arranged on one side of the gearbox.
    [18]
    A screw compressor according to claim 15, wherein the first rotor side gear is provided on the male rotor shaft of the low pressure stage of the compressor body and the second rotor side gear is provided on the rotor. male rotor shaft of the high pressure stage of the compressor body.
    [19]
    The screw compressor according to claim 15, further comprising a base and a motor frame mounted on the base, wherein the motor housing attaches the motor casing to the base and is not directly connected to the stage. low pressure of the compressor body or the high pressure stage of the compressor body.
    [20]
    The screw compressor according to claim 15, wherein a diameter of the first multiplier is smaller than a diameter of the second multiplier.
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    同族专利:
    公开号 | 公开日
    US20090123302A1|2009-05-14|
    JP4673136B2|2011-04-20|
    US20120251372A1|2012-10-04|
    US8734126B2|2014-05-27|
    US20060280626A1|2006-12-14|
    CN100520071C|2009-07-29|
    US8231363B2|2012-07-31|
    CN101349268A|2009-01-21|
    US8221094B2|2012-07-17|
    CN101576082B|2012-10-10|
    CN101349268B|2013-02-06|
    JP2006342742A|2006-12-21|
    CN1877127A|2006-12-13|
    CN101576082A|2009-11-11|
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