JP5616866B2 - Turbo compressor - Google Patents

Description

  The present invention relates to a gear built-in type multi-stage turbo compressor in which a rotating shaft of an impeller is driven from a drive shaft via a drive gear.

  First, a multistage turbo compressor according to a conventional example will be described below with reference to FIGS. 6 is a plan view of a centrifugal compressor according to prior art 1, FIG. 7 is a sectional view taken along arrows IV-IV in FIG. 6, FIG. 8 is a side sectional view of a turbo compressor according to prior art 2, and FIG. It is an example of the cooling water piping system diagram at the time of installing a plurality of turbo compressors concerning.

  The compressor main body 44 of the centrifugal compressor according to the prior art 1 includes a compressor base 45 having a hollow structure, a gear box housing part 46, a first stage scroll part 47, a second stage scroll part 48, and a motor attachment. The base 49 is provided, and these parts are integrally formed by casting.

  A lubricating oil storage chamber 52 for storing lubricating oil is formed in a portion near the one end A side inside the compressor base 45, and a portion near the other end B side inside the compressor base 45 is heated. An intercooler chamber 50 that houses an exchange element (not shown) and an aftercooler chamber 51 that houses another heat exchange element (not shown) are formed.

  Opening covers 59 and 60 are attached to the end of the compressor base 45 close to one end A so as to cover the openings 56 and 57 of the lubricating oil storage chamber 52 separately. An opening cover 58 is attached to the end of the other end B side so as to integrally cover the openings 54 and 55 of the intercooler chamber 50 and the aftercooler chamber 51.

  The opening cover 58 is provided with a pipe (not shown) for transferring a cooling medium to and from the heat exchange elements built in the cooler chambers 50 and 51. By circulating a cooling medium from the outside to each heat exchange element, heat is exchanged between the cooling medium and the gas inside the cooler chambers 50 and 51 to cool the gas. . The aftercooler chamber 51 is provided with a gas outlet (not shown) that opens to the outside.

  The gear box housing portion 46 is provided on the upper portion of the compressor base 45, and a speed increasing gear mechanism (not shown) having an input shaft and an output shaft is housed therein. A gear box cover 61 that covers the speed increasing gear mechanism is attached to the upper end of the gear box housing portion 46, while the lubricating oil is stored in the gear box housing portion 46 from the speed increasing gear installation portion. A lubricating oil recovery flow path 75 extending to the chamber 52 is formed.

  Further, a first-stage discharge passage 66 extending from the scroll chamber 62 to the vicinity of the end portion near the one end A side of the intercooler chamber 50 inside the compressor base 45 is formed inside the first-stage scroll portion 47. The gas compressed by flowing into the first scroll portion 47 from the gas inlet 65 by the rotation of the impeller (not shown) flows into the intercooler chamber 50 through the first discharge channel 66. It has become.

  Further, in the second stage scroll portion 48, a second stage suction passage 70 extending from the vicinity of the other end B side end portion of the intercooler chamber 50 inside the compressor base 45 to the scroll chamber 67, and the scroll A second-stage discharge flow channel 71 extending from the other end B side of the aftercooler chamber 51 inside the compressor base 45 to the vicinity of the end portion is formed from the chamber 67, and the second-stage intake flow channel is formed by rotating the impeller. The gas that flows into the second-stage scroll portion 48 from 70 and is compressed flows into the aftercooler chamber 51 through the second-stage discharge passage 71 (see, for example, Patent Document 1).

  However, the centrifugal compressor according to the prior art 1 is a compressor main body 44, an intercooler chamber 50 and an after cooler chamber 51, and a pipe (not shown) connecting the compressor main body 44 and the cooler chambers 50, 51. Since the bottom part 61a is formed at the bottom of the gear box housing part 61 that houses the speed increasing gear, the lubricating oil injected into the gear box housing part 61 hits the bottom board 61a. Bounces and collides with the speed increasing gear, increasing the mechanical loss. As a result, the performance of the centrifugal compressor is reduced.

  On the other hand, in the related art 2, a compressor body including a gear case 81 that houses a speed increasing gear (not shown), a first stage compressor 85, and a second stage compressor 86, a first gas cooling unit 82, and a second stage. The gas cooling unit 83 and a part of the pipe connecting the compressor main body to the first gas cooling unit 82 and the second gas cooling unit 83 (for example, the first-stage compressed air flow path 88 and the second-stage compressed air flow path 89 ) Is the same as the prior art 1, but as shown in FIG. 8, the bottom plate of the gear case 81 is eliminated, and the lubricating oil is directly collected in the lubricating oil tank 87. (See Patent Document 2). Therefore, unlike the prior art 1, the lubricating oil hits the bottom plate 61a and rebounds, increasing the mechanical loss and causing no deterioration in the performance of the centrifugal compressor.

  However, the turbo compressor according to the prior art 2 is similar to the centrifugal compressor according to the prior art 1, the first gas cooling unit 82 and the second gas cooling unit 83 (in the prior art 1, the intercooler chamber 50 and The axial direction of the aftercooler chamber 51) (longitudinal direction of the first gas cooling unit 82 and the second gas cooling unit 83) is orthogonal to a drive shaft (not shown) arranged in parallel with the pinion shaft 84 of the compressor. Arranged in the direction. Also, since the drive motor for driving the drive shaft is naturally mounted in the same direction as the drive shaft, the external dimension of such a compressor is relatively long in the direction parallel to the drive shaft, and the direction perpendicular to the drive shaft. It will be short. In addition, the water supply joint and the drain joint for the cooling water of the first gas cooling section 82 and the second gas cooling section 83 are arranged at the end portions in the axial direction of the first gas cooling section 82 and the second gas cooling section 83. Is done.

  When a plurality of turbo compressors according to the related art 2 are installed, the plurality of turbo compressors are arranged so that the drive shafts of the compressors are arranged in parallel as shown in FIG. 9 for convenience of maintenance. As a result, the water supply inlet 91 and the drainage outlet 92 to each cooling part 82 and 83 are arrange | positioned at the side surface (surface mutually opposed among the surfaces of an adjacent compressor).

  When arranged in this manner, the water supply pipe 91a and the drainage pipe 92a connected to the water supply joint 91 and the drainage joint 92 are both bent with respect to the water supply main pipe 91b and the drainage main pipe 92b (that is, the water supply main pipe). After extending substantially vertically from 91b and the drainage main pipe 92b, it is necessary to bend the pipe in a substantially perpendicular direction so as to extend substantially parallel to the water supply main pipe 91b and the drainage main pipe 92b and connect to each compressor. Yes, piping work is complicated and difficult. Moreover, since it is necessary to ensure sufficient space between each compressor for the maintenance of each drive system and the operation | work of extraction of a cooler main body, a wide installation space is needed.

JP-A-7-103162 Japanese Patent No. 4048078

  Accordingly, it is an object of the present invention to provide a turbo compressor that does not increase mechanical loss due to rebound of lubricating oil, reduces the installation space of the compressor, and facilitates piping work for cooling water.

In order to achieve the above object, means adopted by the turbo compressor according to claim 1 of the present invention includes an input shaft and at least one pinion shaft to which rotation of the input shaft is transmitted via a gear. A first stage compressor driven by the pinion shaft is provided on one side surface of the gear case, and a second stage compressor driven by the pinion shaft is provided on the other side surface. In the turbo compressor provided with gas coolers for cooling the gas discharged from the compressor and the second stage compressor, a lubricating oil tank is disposed below the gear case, and the first stage compressor The gas coolers are respectively disposed below the second stage compressor and on both side surfaces of the lubricating oil tank, and the axes of the lubricating oil tank and the respective gas coolers and the input shaft are disposed in parallel. Before An inner partition plate that vertically defines an oil reservoir portion in the tank is provided in the lubricating oil tank, and the upper and lower portions defined by the end portion of the inner partition plate and the inner wall of the lubricating oil tank are provided. An opening for communicating with the oil reservoir is formed .

The turbo compressor according to claim 2 of the present invention employs the turbo compressor according to claim 1 , wherein the gas cooler housing is penetrated to insert a heat exchanger in the axial direction of the gas cooler. A hole is formed.

According to the turbo compressor according to claim 1 of the present invention, the pinion is provided on one side surface of a gear case having an input shaft and at least one pinion shaft to which rotation of the input shaft is transmitted via a gear. A first-stage compressor driven by a shaft, and a second-stage compressor driven by the pinion shaft on the other side surface, and from these first-stage compressor and second-stage compressor In each of the turbo compressors each provided with a gas cooler for cooling the discharged gas, a lubricating oil tank is disposed below the gear case, and below the first stage compressor and the second stage compressor, and wherein the said gas cooler is respectively arranged on both sides of the lubricating oil tank, the lubricating oil tank and Ri Na disposed parallel to said input shaft and each of the axis of the gas cooler of the respective said lubricating oil tank, this In the tank A partition plate that vertically defines the reservoir portion is provided, and an opening that communicates the defined upper and lower oil reservoir portions is formed by the end portion of the partition plate and the inner wall of the lubricating oil tank. Being done .

As a result, it is possible to connect to each main pipe without increasing the mechanical loss of the turbo compressor and without bending the water supply / drain pipe to the gas cooler. Therefore, the piping work is simple and the installation space can be reduced, and these water supply and drainage pipes do not interfere with the maintenance of the compressor. Furthermore, the storage time in the lubricating oil tank becomes longer, and bubbles in the lubricating oil can be eliminated. As a result, it is possible to prevent the gears and bearings from being lubricated and lowered in cooling capacity, and corrosion. Further, since the amount of lubricating oil used can be reduced and the capacity of the lubricating oil tank can be reduced, there is an advantage that the size of the entire compressor can be reduced.

In the turbo compressor according to claim 2 of the present invention, the housing of the gas cooler is formed with a through hole for inserting a heat exchanger in the axial direction of the gas cooler. The core can be supported at both ends, and the gas cooler can be securely sealed.

1 is a schematic system diagram of a three-stage turbo compressor according to an embodiment of the present invention. FIG. 3 is a schematic plan view in which the motor of the three-stage turbo compressor according to the embodiment of the present invention is omitted. It is an AA arrow line view of FIG. It is a BB arrow line view of FIG. It is an example of the systematic diagram of the cooling water piping at the time of installing two or more units | sets of the three-stage type turbo compressor which concerns on embodiment of this invention. It is a top view of the centrifugal compressor which concerns on the prior art 1. FIG. It is the IV-IV arrow line view of FIG. It is a sectional side view of the turbo compressor which concerns on the prior art 2. FIG. It is an example of the system diagram of a cooling water piping at the time of installing the multiple turbo compressor which concerns on the prior art 2. FIG.

  First, a turbo compressor according to an embodiment of the present invention will be described as an example of an aspect applied to a three-stage turbo compressor with reference to FIGS. FIG. 1 is a schematic system diagram of a three-stage turbo compressor according to an embodiment of the present invention. FIG. 2 is a schematic plan view in which the motor of the three-stage turbo compressor according to the embodiment of the present invention is omitted. 3 is a view taken along the line AA in FIG. 2, FIG. 4 is a view taken along the line BB in FIG. 2, and FIG. 5 is a case where a plurality of three-stage turbo compressors according to the embodiment of the present invention are installed. It is an example of the systematic diagram of cooling water piping.

  As shown in FIG. 1, this three-stage turbo compressor includes a twin-pinion type speed increaser (gear) 4 formed by meshing an input gear 6 with a 1-2-stage pinion gear 7 and a 3-stage pinion gear 8. I have. The gearbox 4 is accommodated in a gearbox housing (gear case) 5. And the said input gear 6 is connected to the input shaft 6a in the center part. The input shaft 6a is rotatably supported by a bearing or the like (not shown) built in the gearbox housing (gear case) 5.

  At the same time, one end of the input shaft 6 a protrudes from the gearbox housing 5 and is connected to the output shaft 6 b of the electric motor M. The input shaft 6a and the output shaft 6b are connected via a coupling 23 so that a rotational force can be transmitted without generating vibration and noise even when the shaft center is displaced. The gearbox housing 5 includes a gearbox lower housing 5a at the lower part of the housing and a gearbox upper housing 5b at the upper part of the housing. And the gearbox lower housing 5a is connected above the lubricating oil tank 13 mentioned later.

  A 1-2 stage pinion gear 7 and a 3 stage pinion gear 8 are meshed with the input gear 6. The 1-2 stage pinion gear 7 is connected to a pinion shaft 7a, and the 3rd stage pinion gear 8 is further connected to a pinion shaft 8a. Is supported rotatably. That is, in other words, the three-stage turbo compressor according to the embodiment of the present invention includes a pinion shaft 7a in which the rotation of the input shaft 6a is transmitted via the input gear 6 and the first-second pinion gear 7, and the input It can be said that the shaft 6a has a pinion shaft 8a to which the rotation of the shaft 6a is transmitted via the input gear 6 and the three-stage pinion gear 8.

  The first stage impeller 1a is connected to one end on the counter-motor M side of the pinion shaft 7a of the 1-2 stage pinion gear 7 when viewed from the speed increaser 4, and the first stage impeller 1a is connected to the first stage compressor casing. 1b is provided around. On the other hand, a second stage impeller 2a is connected to the other end of the pinion shaft 7a of the 1-2 stage pinion gear 7 on the electric motor M side as viewed from the speed increaser 4, and a second stage compressor is connected to the second stage impeller 2a. A casing 2b is provided around the casing. The turbo compressor has a third-stage impeller 3a connected to one end of the pinion shaft 8a of the three-stage pinion gear 8 on the counter-motor M side as viewed from the speed increaser 4, and the third-stage impeller 3a is connected to the third-stage impeller 3a. A compressor casing 3b is provided around the compressor casing 3b.

  The first stage impeller 1a, the second stage impeller 2a, and the third stage impeller 3a are all swirl chambers in the first stage compressor casing 1b, the second stage compressor casing 2b, and the third stage compressor casing 3b ( 1st stage compressor 1, 2nd stage compressor 2, and 3rd stage compressor 3 are constituted, respectively.

  That is, the three-stage turbo compressor includes a first stage compressor 1 driven by a pinion shaft 7a on one side surface of a speed increaser housing (gear case) 5, and the speed increaser housing (gear case). A second stage compressor driven by the pinion shaft 7a is also provided on the other side surface of 5). The three-stage turbo compressor is provided with a third-stage compressor 3 driven by a pinion shaft 8a on one side surface of a gearbox housing (gear case) 5, and a gearbox housing ( A third stage compressor 3 driven by a pinion shaft 8a is provided on one side surface of the gear case) 5.

  Air A0 sucked in through a suction filter (not shown) is compressed by the first stage compressor 1, and as the first stage compressed air, the discharge port of the first stage compressor 1 and the suction port of the second stage compressor 2 Are guided to the first-stage compressed air flow path 21 communicating with each other. And this 1st stage compressed air is the 1st stage intercooler interposed between the 1st stage compressor discharge piping 21a which comprises the 1st stage compressed air flow path 21, and the 2nd stage compressor suction piping 21b. (Gas cooler) 11 is introduced into second stage compressor 2.

  The first stage compressed air introduced into the second stage compressor 2 is further compressed by the second stage compressor 2, and the second stage compressor 2 discharge port and the third stage compressor 3 serve as the second stage compressed air. To the second-stage compressed air flow path 22 communicating with the suction port. The second-stage compressed air is a second-stage intercooler interposed between the second-stage compressor discharge pipe 22a constituting the second-stage compressed air flow path 22 and the third-stage compressor suction pipe 22b. (Gas cooler) 12 is introduced into the third stage compressor 3. And it is comprised so that the 3rd stage compressed air A3 compressed by this 3rd stage compressor 3 may be supplied to the demand destination of compressed air. Here, the code | symbol 20 is a pipe joint which connects each piping.

  The turbo compressor according to the embodiment of the present invention is an increase formed by meshing the input gear 6 with the 1-2 stage pinion gear 7 and the 3 stage pinion gear 8 in the above-described 3-stage turbo compressor. A lubricating oil tank 13 is disposed below the speed machine 4 and thus below the speed increaser housing (gear case) 5, while the first stage compressor 1, the second stage compressor 2, and the third stage compression. A first-stage intercooler 11 and a second-stage intercooler 12 each having a cylindrical shape are disposed below the machine 3 and on both sides of the lubricating oil tank 13.

  At the same time, when the turbo compressor is viewed in plan (see FIG. 2), the lubricating oil tank axis C3, the first stage intercooler axis C1, the second stage intercooler axis C2, and the input shaft 6a of the compressor are arranged in parallel. . Here, the first stage intercooler body (housing) 11a constituting the outer shell of the first stage intercooler 11, the second stage intercooler body (housing) 12a constituting the outer shell of the second stage intercooler 12, and both the intercooler bodies 11a. , 12a, the lubricating oil tank 13 is integrally formed of a casting.

  The first-stage and second-stage intercooler bodies 11a, 12a constituting the first-stage and second-stage intercoolers 11, 12 respectively have substantially cylindrical shapes in which through holes are formed in the directions of the respective intercooler axes C1, C2. Those are preferred. The heat exchangers 11b and 12b are inserted in the through-holes of the first-stage and second-stage intercooler bodies 11a and 12a and stored in the directions of the respective intercooler axes C1 and C2.

  Further, cooling water is supplied to the tube nests 11c and 12c constituting the heat exchangers 11b and 12b in the first and second stage intercoolers 11 and 12, or from the tube nests 11c and 12c (after the compressed air is cooled). The cooling water is discharged so that the first-stage compressed air and the second-stage compressed air can be cooled. Reference numeral 13a denotes a lubricating oil tank lid, reference numerals 19a and 19b denote intercooler lids, and reference numerals 18 and 18 denote seal portions of the first and second stage intercoolers 11 and 12, respectively.

  The cooling water supply / drain joint (reference numerals 31 and 32 shown in FIG. 5) is either one of both end sides of the first and second stage intercooler bodies 11a and 12a in the direction of each intercooler axis C1 and C2, for example, on the side of the counter-motor M The first stage and the second stage intercooler lids 19a and 19a are preferably provided for the reasons described later. Then, by removing the intercooler lids 19b, 19b on the side where the water supply / drainage connection port is not attached, the heat exchangers 11b, 12b can be inserted in the first and second intercooler axis C1, C2 directions. It is configured.

  In this manner, the first and second stage intercoolers 11 and 12 for gas cooling are provided below the first to third stage compressors 1, 2 and 3 and in the spaces on both sides of the lubricating oil tank 13. By providing the compressor, the entire compressor can be made compact. Further, since the heat exchangers 11b and 12b can be inserted in the first and second stage intercooler axis C1 and C2 directions, the first and second stage intercoolers 11 of the heat exchangers 11b and 12b can be inserted. , 12 can be easily attached and detached, and maintenance of each intercooler 11, 12 is facilitated. Furthermore, since the end face of the lubricating oil tank 13 on the lubricating oil tank lid 13a side is not obstructed by the electric motor, the lubricating oil tank 13 can be supplied easily.

  In addition, the first and second stage intercooler bodies 11a and 12a constituting the first and second stage intercoolers 11 and 12 are formed with through holes in the direction of the first and second stage intercooler axes C1 and C2. Therefore, when casting the intercooler bodies 11a, 12a, the core is firmly supported at both ends thereof, and the processing accuracy at the time of casting the intercooler bodies 11a, 12a can be improved, and the first and second intercoolers 11 can be improved. , 12 can be reliably sealed.

  Furthermore, the gearbox housing 5 in which the gearbox 4 is housed is composed of a gearbox lower housing 5a at the lower part of the housing and a gearbox upper housing 5b at the upper part of the housing. A first stage and second stage intercoolers 11 and 12 are provided in the space on both sides of the lubricating oil tank 13 formed at the lower part of the lower speed machine housing 5a. By adopting such a configuration, the turbo compressor according to the present invention can be made compact, and in particular, the first stage and second stage intercoolers are not located under the lubricating oil tank 13 but in the spaces on both sides thereof. 11 and 12 can increase the distance between the gears 6 to 8 constituting the speed increaser 4 and the lubricating oil surface of the lubricating oil tank 13, thereby reducing mechanical loss due to the rebound of the lubricating oil. It can be resolved.

  That is, in FIG. 4, the lubricating oil 14 stored in the lubricating oil tank 13 is sucked up by an oil pump 17 from an oil supply port (not shown) provided in the lubricating oil tank lid 13 a, and the shower nozzle 9 for the 1-2 stage pinion gear 7. Are injected from the shower nozzle 10 for the three-stage pinion gear 8 toward the input gear 6, the first-second stage pinion gear 7 and the third-stage pinion gear 8, and are used for lubrication and cooling of the speed increaser 4, but rotate at high speed. Even if the lubricating oil 14a bounced off the input gear 6 and the three-stage pinion gear 8 of the speed increasing gear 4 bounces off from the lubricating oil surface 14b, the lubricating oil 14a does not reach the speed increasing gear 4, and the lubricating oil 14a rebounds. Mechanical loss can be eliminated. Here, reference numeral 24 denotes the rotation direction of the input gear 6.

  In addition, as shown in FIG. 5, the turbo compressor according to the embodiment of the present invention includes the first and second intercoolers 11 and 12, the water supply connection ports 31 and 31 and the drainage connection ports 32 and 32, Since it is provided on the intercooler lid on the side of the counter-motor M in the direction of the second stage intercooler axis C1, C2, it is connected to the water supply inlet 31 and the drainage inlet 32 when a plurality of the turbo compressors are installed. Both the water supply pipe 31a and the drainage pipe 32a can be connected to the water supply main pipe 31b and the drainage main pipe 32b without being bent.

  That is, the water supply pipe 31a and the drainage pipe 32a extend substantially perpendicularly from the water supply main pipe 31b and the drainage main pipe 32b, and then are not bent, and are arranged substantially coaxially with the water supply pipe 31a and the drainage pipe 32a. Connected to the joint 31 and the drain joint 32. Therefore, the piping work is simple and the installation space can be reduced, and these pipes do not become an obstacle to the maintenance of the compressor.

  Further, as shown in FIGS. 2 and 4, the turbo compressor according to the embodiment of the present invention has a partition plate 16 that vertically defines an oil reservoir 15 in the tank 13 in the lubricating oil tank 13. Is provided. An opening 16 a that communicates with the upper and lower oil reservoirs 15 defined by the intermediate partition plate 16 is formed by the end of the intermediate partition plate 16 and the inner wall of the tank 13.

  The lubricating oil 14 splashed off by the speed increaser 4 and stored in the oil reservoir 15 is sucked up by an oil pump 17 from an oil supply port (not shown) provided in the lubricating oil tank lid 13a, and again input gears 6 and 1- Lubricating oil 14a which is used for lubricating and cooling the second-stage pinion gear 7 and the third-stage pinion gear 8 and a bearing (not shown) but is sputtered by the gears 6 to 8 rotating at high speed is air (bubbles). Is returned to the oil reservoir 15 in the lubricating oil tank 13. The lubricating oil 14 still containing bubbles may cause a reduction in the ability to lubricate and cool the gears 6 to 8 and the bearing, and may cause corrosion.

  As a method of eliminating bubbles, the capacity of the lubricating oil tank 13 is increased, the time until the returned lubricating oil 16 is reused is lengthened, and the bubbles are floated and scattered on the oil surface. In general, a large amount of lubricating oil 14 is required. By providing the partition plate 16 as described above, the lubricating oil 14 that has been splashed by the gears 6 to 8 and dropped onto the lubricating oil surface 14 b of the oil reservoir 15 before the lubricating oil 14 is sucked into the oil pump 17. Passes through the opening 16 a along the flow of the lubricating oil 14 in the upper oil reservoir 15 defined in the partition plate 16, and then the lower oil reservoir defined in the partition plate 16. Along the flow of the lubricating oil 14 in the portion 15, the lubricating oil tank lid 13 a is directed.

  Therefore, a long path is surely taken until the lubricating oil 14 is sucked into the oil pump 17, and the time until the lubricating oil 14 is reused becomes longer, and the bubbles in the lubricating oil 14 rise to the oil surface. Can be scattered to the gas phase portion in the gearbox housing 5.

  When there is no intermediate partition plate 16, the lubricating oil 14 that has fallen from the speed increaser 4 to the lubricating oil surface 14b of the lubricating oil tank 13 is directed to the lubricating oil tank lid 13a through the shortest path. In the case of the embodiment of the present invention in which the plate 16 is provided, the lubricating oil 14 that has fallen on the lubricating oil surface 14b of the lubricating oil tank 13 leaves the lubricating oil tank 13 via a distance that is approximately three times longer. It will be.

  As described above, according to the turbo compressor according to the embodiment of the present invention, it is possible to eliminate bubbles in the lubricating oil 14 that cause a reduction in lubrication and cooling capacity of the speed increaser 4 and the bearing. Furthermore, since the amount of the lubricating oil 14 used can be reduced and the capacity of the lubricating oil tank 13 can be reduced, there is an advantage that the overall size of the compressor can be reduced.

  In addition, although the example of the aspect applied to the three-stage turbo compressor was described about the turbo compressor which concerns on embodiment of this invention, the turbo compressor which concerns on this invention is limited to a three-stage turbo compressor. Of course, this is also effective in a two-stage turbo compressor or a multistage turbo compressor having four or more stages.

A0: Air,
A3: Third stage compressed air,
C1: first intercooler axis,
C2: first intercooler axis,
C3: lubricating oil tank axis,
M: electric motor,
1: 1st stage compressor, 1a: 1st stage impeller, 1b: 1st stage compressor casing,
2: 2nd stage compressor, 2a: 2nd stage impeller, 2b: 2nd stage compressor casing,
3: Third stage compressor, 3a: Third stage impeller, 3b: Third stage compressor casing,
4: gearbox (gear),
5: Gearbox housing (gear case),
5a: Housing below the gearbox, 5b: Housing above the gearbox,
6: input gear, 6a: input shaft, 6b: output shaft,
7: 1-2 stage pinion gear, 7a: pinion shaft,
8: Three-stage pinion gear, 8a: Pinion shaft,
9, 10: Shower nozzle,
11: First stage intercooler (gas cooler), 11a: First stage intercooler fuselage,
11b: heat exchanger, 11c: tube nest,
12: Second stage intercooler (gas cooler), 12a: Second stage intercooler fuselage,
12b: heat exchanger, 12c: tube nest,
13: Lubricating oil tank, 13a: Lubricating oil tank lid,
14, 14a: Lubricating oil, 14b: Lubricating oil surface,
15: Oil reservoir
16: Middle partition plate, 16a: Opening part,
17: Oil pump,
18: seal part,
19a, 19b: Intercooler lid,
20: Pipe fitting,
21: First stage compressed air flow path, 21a: First stage compressor discharge pipe,
21b: second stage compressor suction pipe,
22: Second stage compressed air flow path, 22a: Second stage compressor discharge pipe,
22b: Third stage compressor suction pipe,
23: Coupling, 24: Direction of rotation,
31: Water supply joint, 31a: Water supply piping, 31b: Water supply main piping,
32: Drainage joint, 32a: Drainage pipe, 32b: Drainage main pipe

Claims (2)

A first stage compressor driven by the pinion shaft is provided on one side surface of a gear case having an input shaft and at least one pinion shaft to which rotation of the input shaft is transmitted via a gear.
And a second stage compressor driven by the pinion shaft is provided on the other side surface,
In each of the turbo compressors provided with gas coolers for cooling the gas discharged from the first stage compressor and the second stage compressor,
A lubricating oil tank is disposed below the gear case,
The gas coolers are respectively disposed below the first stage compressor and the second stage compressor and on both sides of the lubricating oil tank,
The lubricating oil tank and Ri name is the input shaft is arranged parallel to the respective axes of the gas cooler of the respective said lubricating oil tank, the partition plate is provided in defining an oil reservoir in the tank in the vertical The turbocompressor is characterized in that an opening for communicating the defined upper and lower oil reservoirs is formed by an end portion of the partition plate and an inner wall of the lubricating oil tank . The turbo compressor according to claim 1, wherein a through hole for inserting a heat exchanger is formed in the housing of the gas cooler in an axial direction of the gas cooler.

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