JP2008133746A - Turbo compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbo compressor which has high efficiency and a reduced size by devising the arrangement of each component. <P>SOLUTION: The turbo compressor is equipped with a first rotating shaft connected to an output shaft 4 of a drive motor 3, a second rotating shaft which is disposed in parallel to the first rotating shaft and has a first impeller, a third rotating shaft which is disposed in parallel to the first rotating shaft and has a second impeller, a first cooling part 41 for cooling a working gas A compressed by the first impeller, a second cooling part 45 for cooling the working gas A compressed by the second impeller, and a casing 8 which houses these parts and has a gas flow passage which introduces the working gas A from the first impeller to the second cooling part 45. The first and second impellers are disposed at the opposite side of the drive motor, and the first and second cooling parts 41, 45 are disposed along the direction substantially orthogonal to the first rotating shaft. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

The present invention relates to a turbo compressor.
About.

2. Description of the Related Art As an industrial turbo compressor, a two-stage turbo compressor that discharges a fluid compressed by a first stage compressor after further compression by a second stage compressor is known. In this turbo compressor, an impeller (impeller) of a first stage compressor and an impeller of a second stage compressor are connected by a rotation shaft, and the rotation shaft is rotated by a drive motor through a gear train. Yes.
JP-A-8-93685

Industrial turbo compressors are required to reduce power consumption and installation area.
In a so-called single-shaft two-stage turbo compressor, the impeller of the first-stage compressor and the impeller of the second-stage compressor are connected to the same rotating shaft, so that each impeller is driven at an optimum rotational speed. I can't. Therefore, it is difficult to achieve efficient operation at the highest efficiency point of each impeller.
Also, as high-efficiency turbo compressors, so-called two-shaft three-stage and two-shaft four-stage turbo compressors have been proposed, but with increased equipment costs and larger equipment due to the increased number of parts. End up.

Therefore, a two-shaft two-stage turbo compressor in which the impeller of the first stage compressor and the impeller of the second stage compressor are provided on different rotating shafts has been proposed. This two-shaft two-stage turbo compressor can improve efficiency (reduction of power consumption, etc.) while suppressing an increase in apparatus cost.
However, in the two-shaft two-stage turbo compressor, the installation area has to be increased due to the fact that the number of rotating shafts is increased as compared with the single-shaft two-stage type.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to propose a turbo compressor that is highly efficient and has been made compact by devising the arrangement of each component.

The turbo compressor according to the present invention employs the following means in order to solve the above problems.
According to a first aspect of the present invention, a first rotating shaft connected to the output shaft of the drive motor and having a first gear, a second rotating shaft having a second gear meshing with the first gear, and the second rotating shaft A first impeller mounted, a third gear meshing with the first gear and a third rotating shaft disposed substantially parallel to the second rotating shaft; and attached to the third rotating shaft A second impeller, a first cooling part for cooling the working gas compressed by the first impeller, a second cooling part for cooling the working gas compressed by the second impeller, and the first to A gas flow that houses the third rotating shaft and the first and second cooling units and guides the working gas from the first impeller to the second cooling unit through the first cooling unit and the second impeller. And a casing having a passage, wherein the first and second blades Place the non-drive motor side relative to the first gear, and characterized in that it is arranged along a direction substantially perpendicular to said first and second cooling portion relative to the first rotation axis.

  According to a second aspect of the present invention, a first rotating shaft connected to the output shaft of the drive motor and having a first gear, a second rotating shaft having a second gear meshing with the first gear, and the second rotating shaft A first impeller mounted, a third gear meshing with the first gear and a third rotating shaft disposed substantially parallel to the second rotating shaft; and attached to the third rotating shaft A second impeller, a first cooling part for cooling the working gas compressed by the first impeller, a second cooling part for cooling the working gas compressed by the second impeller, and the first to A gas flow that houses the third rotating shaft and the first and second cooling units and guides the working gas from the first impeller to the second cooling unit through the first cooling unit and the second impeller. And a casing having a passage, wherein the first and second blades Was placed on the drive motor side relative to the first gear, and characterized in that it is arranged along a direction substantially perpendicular to said first and second cooling portion relative to the first rotation axis.

  According to a third aspect of the invention, there is provided a first rotary shaft connected to the output shaft of the drive motor and having a first gear, a second rotary shaft having a second gear meshing with the first gear, and the second rotary shaft. A first impeller mounted, a third gear meshing with the first gear and a third rotating shaft disposed substantially parallel to the second rotating shaft; and attached to the third rotating shaft A second impeller, a first cooling part for cooling the working gas compressed by the first impeller, a second cooling part for cooling the working gas compressed by the second impeller, and the first to A gas flow that houses the third rotating shaft and the first and second cooling units and guides the working gas from the first impeller to the second cooling unit through the first cooling unit and the second impeller. And a casing having a path, wherein the first impeller is The second impeller is disposed on the drive motor side on the side opposite to the drive motor with respect to one gear, and the first and second cooling units are arranged in a direction substantially parallel to the first rotation shaft. It is arranged.

  According to a fourth aspect of the invention, there is provided a first rotating shaft connected to the output shaft of the drive motor and having a first gear, a second rotating shaft having a second gear meshing with the first gear, and the second rotating shaft. A first impeller mounted, a third gear meshing with the first gear and a third rotating shaft disposed substantially parallel to the second rotating shaft; and attached to the third rotating shaft A second impeller, a first cooling part for cooling the working gas compressed by the first impeller, a second cooling part for cooling the working gas compressed by the second impeller, and the first to A gas flow that houses the third rotating shaft and the first and second cooling units and guides the working gas from the first impeller to the second cooling unit through the first cooling unit and the second impeller. And a casing having a path, wherein the first impeller is The second impeller is arranged on the drive motor side with respect to one gear, and the first and second cooling parts are arranged in a direction substantially parallel to the first rotation shaft. It is arranged.

In addition, the first and second cooling units are disposed below the first and second impellers.
Further, the first cooling part and the second cooling part have a coolant inlet / outlet on the same end face side.

The casing includes an oil storage chamber that is disposed substantially parallel to the first and second cooling sections and that contains oil for lubricating the first to third gears.
The oil storage chamber may be disposed on the low temperature side of the first or second cooling unit.

Further, the casing is integrally formed of a casting.
Further, a lubricating oil device is disposed on the oil storage chamber.
Further, the drive motor is attached to the casing so as to be positioned in an installation area of the casing.

According to the present invention, the following effects can be obtained.
According to the turbo compressor according to the first to fourth inventions, the first impeller of the first stage compressor and the second impeller of the second stage compressor are different from each other in the rotation shaft (second rotation shaft, third Therefore, the first impeller and the second impeller can be driven at optimum rotational speeds, respectively, and the working gas can be compressed with high efficiency.

  Moreover, according to the turbo compressor which concerns on 1st-4th invention, according to arrangement | positioning of a 1st impeller and a 2nd impeller, seeing arrangement | positioning of a 1st cooling part and a 2nd cooling part from upper direction, An optimal gas flow path can be formed by arranging along a direction substantially orthogonal to the axial direction of the first to third rotation shafts or arranging along a direction substantially parallel to the first to third rotation axes. The gas flow path has characteristics such as a short flow path length, no large bending portion in the flow path, and easy formation as a casting.

Moreover, since the oil storage chamber is arranged on the low temperature part side of the first cooling part or the second cooling part, there is no possibility that the oil is heated, and good lubrication can be realized.
In addition, since the first cooling unit, the second cooling unit, and the oil storage chamber are arranged side by side, the installation area of the turbo compressor can be reduced to a substantially square shape and can be made compact. And since these were integrally molded with the casting, the cost reduction of an apparatus can be achieved.

Embodiments of a turbo compressor according to the present invention will be described below with reference to the drawings.
[First embodiment]
FIG. 1 is a top view (partially sectional view) schematically showing a schematic configuration of a turbo compressor 1 according to the first embodiment.
FIG. 2 is a cross-sectional view showing the configuration of the gear device 10.
FIG. 3 is a schematic cross-sectional view including the first stage compressor 6 (PP cross-sectional view in FIG. 1). FIG. 4 is a schematic cross-sectional view including the second stage compressor 7 (QQ cross-sectional view of FIG. 1).

  The turbo compressor 1 includes a drive motor 3, a gear device 10 connected to the output shaft 4 of the drive motor 3, and a first stage compressor 6 having a first impeller 21 rotated at an increased speed by the gear device 10. , A second stage compressor 7 having a second impeller 22 rotated at a higher speed by the gear unit 10, a casing 8 for housing these components, and the like.

In the casing 8, a gas flow path 30 for guiding the air A sucked from the outside to the second stage compressor 7 from the first stage compressor 6 and further to the outside from the second stage compressor 7 for discharge. Is formed. The gas flow path 30 is provided with an intercooler 41 that cools the air A compressed by the first stage compressor 6, an aftercooler 45 that cools the air A compressed by the second stage compressor 7, and the like.
The casing 8 is also provided with an oil storage chamber 50 that stores the oil L to be lubricated by the gear unit 10.

The drive motor 3 is attached to a gear case 9 that houses the gear device 10 via a flange (not shown) or the like. The output shaft 4 is connected to the first rotating shaft 11 of the gear device 10 via a joint. The gear case 9 is integrally formed with the casing 8.
The drive motor 3 is attached to the casing 8 so as to be located within the installation area of the casing 8. That is, when the turbo compressor 1 is viewed from above, the drive motor 3 is prevented from projecting sideways from the casing 8. Thereby, the installation area of the turbo compressor 1 becomes substantially equal to the installation area of the casing 8, and the turbo compressor apparatus 1 as a whole can be made compact.

As shown in FIG. 2, the first rotating shaft 11 is rotatably supported by the gear case 9, and the output shaft 4 of the drive motor 3 is connected to one end via a bearing, and the other end side has a large diameter. A first gear 14 is attached.
The first gear 14 meshes with a small-diameter second gear 15 provided at one end of the second rotary shaft 12 and a small-diameter third gear 16 provided at one end of the third rotary shaft 13. .
The gear device 10 accelerates the rotation of the output shaft 4 of the drive motor 3 and transmits it to the second rotating shaft 12 and the third rotating shaft 13, respectively.

The second rotating shaft 12 and the third rotating shaft 13 are parallel to the first rotating shaft 11 and are respectively rotatable about the gear case 9 at substantially symmetrical positions across the first rotating shaft 11. Be supported. And the 1st impeller 21 and the 2nd impeller 22 are provided in the other end of the 2nd rotating shaft 12 and the 3rd rotating shaft 13, respectively.
The first impeller 21 and the second impeller 22 are disposed on the opposite side of the drive motor 3 with the gear device 10 interposed therebetween. That is, the second rotary shaft 12 and the third rotary shaft 13 are supported so as to extend from the gear device 10 on the opposite side to the drive motor 3, and the first impeller 21, A second impeller 22 is arranged.

The first impeller 21 is accommodated in a cylindrical recess 23 formed on the side of the gear case 9. The second impeller 22 is accommodated in a cylindrical recess 24 formed on the opposite side of the gear case 9 across the first rotating shaft 11.
Blocks 25 and 26 having spiral chambers and intake passages 31 and 34 are inserted into the recesses 23 and 24, respectively, and diffusers are formed between the blocks 25 and 26 and the recesses 23 and 24, respectively.
In addition, the gear case 9 can be divided | segmented up and down in a horizontal cross section, and inspection of the 1st-3rd rotating shafts 11-13, the 1st-3rd gearwheels 14-16 is carried out by removing an upper cover. It is possible.

Below the first stage compressor 6, the second stage compressor 7, and the gear unit 10, two substantially rectangular parallelepiped spaces (cooling chambers 42, 46) integrally formed with the gear case 9 are formed. Yes.
One cooling chamber 42 is provided with a heat exchanger 43 for an intercooler 41 that cools the air A discharged from the first stage compressor 6 and guides it to the second stage compressor 7. The other cooling chamber 46 is provided with a heat exchanger 47 for an aftercooler 45 that cools and exhausts the air A discharged from the second stage compressor 7.

The heat exchangers 43 and 47 are formed to be elongated along the longitudinal direction of the cooling chambers 42 and 46, and are arranged in the center of the cooling chambers 42 and 46, respectively, and the insides of the cooling chambers 42 and 46 are respectively at the inlet side and the outlet side. It is divided into the side.
The cooling chambers 42 and 46 are each provided with an inlet at one end in the longitudinal direction on the inlet side and a discharge port at the other end in the longitudinal direction on the outlet side.
The inlet of the cooling chamber 42 of the intercooler 41 is connected to the spiral chamber of the first stage compressor 6 via the first communication passage 32, and the discharge port is the intake air of the second stage compressor 7 via the second communication passage 33. Connected to the passage 34.
The inlet of the cooling chamber 46 of the aftercooler 45 is connected to the swirl chamber of the second stage compressor 7 through the third communication passage 35, and the discharge port itself becomes an exhaust port 36 for discharging the air A to the outside. ing.
The first communication passage 32 extends from the spiral chamber of the first stage compressor 6 to the cooling chamber 42 in an obliquely downward direction in substantially the same direction as the second rotary shaft 12. The second communication passage 33 extends from the cooling chamber 42 to the intake passage 34 of the second stage compressor 7 in an obliquely upward direction in substantially the same direction as the third rotating shaft 13. The third communication passage 33 extends from the spiral chamber of the second stage compressor 6 to the cooling chamber 46 substantially downward.

The heat exchangers 43 and 47 include a plurality of fin plates arranged orthogonal to the longitudinal direction thereof, a plurality of water pipes provided through the fin plates, seal baffles provided above and below the fin plates, And a seal member provided on the seal baffle (both not shown).
The seal baffle guides air A from one side of the heat exchangers 43 and 47 to the other side, and the seal member seals between the seal baffle and the inner surfaces of the cooling chambers 42 and 46, 46 is divided into an inlet side and an outlet side.
Moreover, the heat exchangers 43 and 47 are each provided with the cooling water inlet / outlet 49 which introduce | transduces and discharges cooling water to the water pipe mentioned above. The cooling water inlet / outlet 49 is provided at one end in the longitudinal direction of the heat exchangers 43 and 47.

When viewed from above, the intercooler 41 and the aftercooler 45 are disposed along a direction substantially orthogonal to the axial direction of the first to third rotating shafts 11 to 13 of the gear device 10. Further, the aftercooler 45 and the intercooler 41 are arranged side by side in the direction away from the drive motor 3.
The cooling water inlet / outlet ports 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface of the casing 8 of the turbo compressor 1.

On the side of the cooling chambers 42 and 46, an oil storage chamber 50 is provided substantially in parallel. The oil storage chamber 50 is adjacent to the outlet side (low temperature side) of the cooling chamber 46. That is, the oil storage chamber 50, the cooling chamber 46 (aftercooler 45), and the cooling chamber 42 (intercooler 41) are arranged side by side in the direction away from the drive motor 3.
The oil storage chamber 50 stores oil for lubricating the bearings that support the first to third rotating shafts 11 to 13 of the gear device 10 and the first to third gears 14 to 16.
A lubricating oil device (not shown) (oil pump, oil pipe, oil cooler, etc.) is provided in the oil storage chamber 50, and the oil pumped up by the oil pump and cooled by the oil cooler is passed through the oil pipe. Thus, oil is supplied to the first to third gears 14 to 16. The supplied oil is collected in the oil storage chamber 50.
Note that the above-described lubricating oil device may be installed in the upper part of the oil storage chamber 50.

The two cooling chambers 42 and 46 and the oil storage chamber 50 are cast integrally with the gear case 9 to constitute the casing 8.
The casing 8 has a substantially quadrangular shape when viewed from above, and is shaped to match the projected area of the turbo compressor 1.

  In the turbo compressor 1 having the above configuration, the first impeller 21 of the first stage compressor 6 sucks the air A from the intake passage 31 and boosts it radially outward. The pressurized air A is decelerated through the diffuser and the swirl chamber, and the speed is converted into pressure, whereby the static pressure further increases and is guided to the intercooler 41 through the first communication passage 32. The air A cooled by the intercooler 41 is guided to the intake passage 34 of the second stage compressor 7 through the second communication passage 33.

Further, the second impeller 22 of the second stage compressor 7 sucks the air A from the intake passage 34 and accelerates it radially outward. The accelerated air A is decelerated through the diffuser and the spiral chamber, the speed is converted into pressure, and is guided to the aftercooler 45 through the third communication passage 35. The air A cooled by the aftercooler 45 is discharged from the exhaust port 36 formed in the casing 8 to the outside (an external connection pipe (not shown)).
In this manner, the turbo compressor 1 can efficiently obtain air A having a desired amount and a desired pressure.

  As described above, according to the turbo compressor 1 of the first embodiment, the first impeller 21 of the first stage compressor 6 and the second impeller 22 of the second stage compressor 7 are different from each other. Since the first impeller 21 and the second impeller 22 can be driven at optimum rotational speeds, respectively, the air compression process can be performed with high efficiency. Can do.

Further, the intercooler 41 and the aftercooler 45 are arranged along a direction substantially orthogonal to the axial direction of the first to third rotating shafts 11 to 13 of the gear device 10 when viewed from above. For this reason, the optimal gas flow path 30 can be formed. That is, the gas flow path 30 (particularly, the first communication path 32, the second communication path 33, and the third communication path 35) has a short flow path length, no large bending portion in the flow path, and is formed as a casting. It has features such as being easy to do.
Further, since the oil storage chamber 50 is disposed adjacent to the outlet side (low temperature side) of the cooling chamber 46, there is no possibility that the oil L is heated by the air heated by the compressor.

Further, since the intercooler 41, the aftercooler 45, and the oil storage chamber 50 are arranged side by side, the installation area of the turbo compressor 1 is substantially rectangular and compact.
Further, since the intercooler 41 and the aftercooler 45 are arranged so that the gas inlet sides (high temperature sides) thereof are adjacent to each other, the gas cooled by the intercooler 41 is heated by the aftercooler 45 or cooled by the aftercooler 45. The heated gas can be prevented from being heated by the intercooler 41.

Further, in the turbo compressor 1, the cooling water inlets / outlets 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface of the casing 8. it can.
Although the cooling water inlet / outlet 49 is provided on the side surface of the casing 8 on the second compressor 7 side, it may be provided on the side surface of the casing 8 on the first compressor 6 side.
In addition, by arranging the control panel 60 of the turbo compressor 1 on the same side as the cooling water inlet / outlet 49, it becomes easy to secure a maintenance space.

[Second Embodiment]
FIG. 5 is a top view (partially sectional view) schematically showing a schematic configuration of the turbo compressor 101 according to the second embodiment.
FIG. 6 is a schematic cross-sectional view including the first stage compressor 6 (PP cross-sectional view in FIG. 5). FIG. 7 is a schematic cross-sectional view including the second stage compressor 7 (QQ cross-sectional view of FIG. 5).

The turbo compressor 101 has the same configuration as the turbo compressor 1 according to the first embodiment, but the arrangement of main components is different.
In the following description, parts different from the turbo compressor 1 will be described, and the same parts will be denoted by the same reference numerals and description thereof will be omitted.

As with the turbo compressor 1, the turbo compressor 101 includes first to third rotating shafts 11 to 13. The second rotating shaft 12 and the third rotating shaft 13 are parallel to the first rotating shaft 11 and are rotatably supported by the gear case 9 at symmetrical positions with the first rotating shaft 11 in between. Is done.
And the 1st impeller 21 and the 2nd impeller 22 are provided in the other end of the 2nd rotating shaft 12 and the 3rd rotating shaft 13, respectively. The first impeller 21 and the second impeller 22 are arranged on the same side as the drive motor 3 with respect to the gear device 10. That is, the second rotating shaft 12 and the third rotating shaft 13 are supported so as to extend from the gear device 10 toward the drive motor 3, and the first impeller 21 and the second impeller 21 are provided at one end (drive motor side). An impeller 22 is arranged.

Further, similarly to the turbo compressor 1, the intercooler 41 and the aftercooler 45 are substantially orthogonal to the axial directions of the first to third rotating shafts 11 to 13 of the gear device 10 when viewed from above. It is arranged along the direction. The intercooler 41 and the aftercooler 45 are arranged in this order in the direction away from the drive motor 3.
The cooling water inlet / outlet ports 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface of the casing 8 of the turbo compressor 1.

The oil storage chamber 50 is provided substantially parallel to the sides of the cooling chambers 42 and 46. The oil storage chamber 50 is adjacent to the outlet side (low temperature side) of the cooling chamber 46. That is, the cooling chamber 42 (intercooler 41), the cooling chamber 46 (aftercooler 45), and the oil storage chamber 50 are arranged in this order in a direction away from the drive motor 3.
The two cooling chambers 42 and 46 and the oil storage chamber 50 are cast integrally with the gear case 9 to constitute the casing 8. Further, the casing 8 has a substantially rectangular shape when viewed from above, and is formed in a size that matches the projected area of the turbo compressor 1.

  Also in the turbo compressor 101 of the second embodiment, the first impeller 21 of the first stage compressor 6 and the second impeller 22 of the second stage compressor 7 are different from each other in rotating shafts (second rotating shaft 12, first Since the three impellers 13) are provided, the first impeller 21 and the second impeller 22 can be driven at optimum rotational speeds, respectively, so that the air can be compressed with high efficiency.

Also in the turbo compressor 101, the intercooler 41 and the aftercooler 45 are arranged along a direction substantially orthogonal to the axial direction of the first to third rotating shafts 11 to 13 of the gear device 10 when viewed from above. Therefore, an optimal gas flow path 130 can be formed. That is, the gas flow path 130 (particularly, the first communication path 132, the second communication path 133, and the third communication path 135) has a short flow path length, no large bend in the flow path, and is formed as a casting. It has features such as being easy to do.
The first communication passage 132 extends from the spiral chamber of the first stage compressor 6 to the cooling chamber 42 obliquely downward in substantially the same direction as the second rotary shaft 12. The second communication passage 133 extends from the cooling chamber 42 to the intake passage 34 of the second stage compressor 7 in an obliquely upward direction in substantially the same direction as the third rotating shaft 13. The third communication passage 133 extends from the spiral chamber of the second stage compressor 6 to the cooling chamber 46 substantially downward.

Further, since the oil storage chamber 50 is disposed adjacent to the outlet side (low temperature side) of the cooling chamber 46, there is no possibility that the oil L is heated by the air heated by the compressor.
Further, since the intercooler 41, the aftercooler 45, and the oil storage chamber 50 are arranged side by side, the installation area of the turbo compressor 1 is substantially rectangular and compact. Since the first stage compressor 6, the second stage compressor 7 and the like are not arranged on the upper part of the oil storage chamber 50, various lubrication-related devices can be installed.
Further, since the intercooler 41 and the aftercooler 45 are arranged so that the gas inlet sides (high temperature sides) thereof are adjacent to each other, the gas cooled by the intercooler 41 is heated by the aftercooler 45 or cooled by the aftercooler 45. The heated gas can be prevented from being heated by the intercooler 41.

Further, in the turbo compressor 101, the cooling water inlets / outlets 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface of the casing 8, so that the piping work and the like are made efficient it can.
In addition, although the cooling water inlet / outlet was provided in the casing side surface of the 2nd compressor side, you may provide it in the casing side surface of the 1st compressor side.
Further, by arranging the control panel 60 of the turbo compressor 101 on the same side as the cooling water inlet / outlet 49, it becomes easy to secure a maintenance space.
Moreover, since there are no related parts in the upper part of the oil storage chamber 50, a lubricating oil apparatus can be installed and the whole turbo compressor apparatus 1 can be made compact.

[Third embodiment]
FIG. 8 is a top view (partially sectional view) schematically showing a schematic configuration of the turbo compressor 201 according to the third embodiment.
FIG. 9 is a schematic cross-sectional view including the first-stage compressor 6 (PP cross-sectional view in FIG. 8). FIG. 10 is a schematic cross-sectional view including the second stage compressor 7 (QQ cross-sectional view of FIG. 8).

The turbo compressor 201 has the same configuration as the turbo compressors 1 and 101 according to the first and second embodiments, but the arrangement of main components is different.
In the following description, portions different from the turbo compressors 1 and 101 will be described, and the same portions will be denoted by the same reference numerals and description thereof will be omitted.

The turbo compressor 201 includes first to third rotating shafts 11 to 13, similarly to the turbo compressors 1 and 101. The second rotating shaft 12 and the third rotating shaft 13 are parallel to the first rotating shaft 11 and are rotatably supported by the gear case 9 at symmetrical positions with the first rotating shaft 11 in between. Is done.
And the 1st impeller 21 and the 2nd impeller 22 are provided in the other end of the 2nd rotating shaft 12 and the 3rd rotating shaft 13, respectively. The first impeller 21 is disposed on the opposite side of the drive motor 3 with the gear device 10 interposed therebetween. On the other hand, the second impeller 22 is disposed on the same side as the drive motor 3 with respect to the gear device 10.
In other words, the second rotary shaft 12 is supported so as to extend from the gear device 10 on the side opposite to the drive motor 3, and the first impeller 21 is disposed at one end thereof (on the side opposite to the drive motor). Moreover, the 3rd rotating shaft 13 is supported so that it may extend toward the drive motor 3 from the gear apparatus 10, and the 2nd impeller 22 is arrange | positioned at the end (drive motor side).

Further, the turbo compressor 201 is different from the turbo compressors 1 and 101, and the intercooler 41 and the aftercooler 45 are viewed from above with respect to the axial directions of the first to third rotating shafts 11 to 13 of the gear device 10. It arrange | positions along the substantially parallel direction. The intercooler 41 and the aftercooler 45 are arranged side by side in the direction away from the second rotating shaft 12 (first impeller 21).
The cooling water inlets / outlets 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface (opposite side of the drive motor 3) of the casing 8 of the turbo compressor 1.

The oil storage chamber 50 is provided on the side of the cooling chambers 42 and 46. The oil storage chamber 50 is adjacent to the side of the cooling chambers 42 and 46 opposite to the cooling water inlet / outlet 49. That is, the oil storage chamber 50, the cooling chamber 42, and the cooling chamber 46 (intercooler 41 and aftercooler 45) are arranged side by side in the direction away from the drive motor 3.
The two cooling chambers 42 and 46 and the oil storage chamber 50 are cast integrally with the gear case 9 to constitute the casing 8. Further, the casing 8 has a substantially rectangular shape when viewed from above, and is formed in a size that matches the projected area of the turbo compressor 1.

  Also in the turbo compressor 201 of the third embodiment, the first impeller 21 of the first stage compressor 6 and the second impeller 22 of the second stage compressor 7 are made to have different rotation shafts (second rotation shaft 12, first rotation shaft 12). Since the three impellers 13) are provided, the first impeller 21 and the second impeller 22 can be driven at optimum rotational speeds, respectively, so that the air can be compressed with high efficiency.

In the turbo compressor 201, the intercooler 41 and the aftercooler 45 are disposed along a direction substantially parallel to the axial direction of the first to third rotating shafts 11 to 13 of the gear device 10 when viewed from above. Therefore, an optimal gas flow path 230 can be formed. That is, the gas flow path 230 (particularly, the first communication path 232, the second communication path 233, and the third communication path 235) has a short flow path length, no large bent portion in the flow path, and is formed as a casting. It has features such as being easy to do.
The first communication passage 232 extends from the spiral chamber of the first stage compressor 6 to the cooling chamber 42 substantially downward. The second communication passage 233 extends from the cooling chamber 42 to the intake passage 34 of the second stage compressor 7 in an obliquely upward direction in a direction substantially orthogonal to the third rotation shaft 13. The third communication passage 233 extends from the spiral chamber of the second stage compressor 6 to the cooling chamber 46 substantially downward.

In addition, since the intercooler 41, the aftercooler 45, and the oil storage chamber 50 are optimally arranged, the installation area of the turbo compressor 1 is substantially rectangular and compact.
Further, in the turbo compressor 201, the cooling water inlets / outlets 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface of the casing 8, so that the piping work and the like are made efficient it can.
Further, since the intercooler 41 and the aftercooler 45 are arranged so that the gas inlet sides (high temperature sides) thereof are adjacent to each other, the gas cooled by the intercooler 41 is heated by the aftercooler 45 or cooled by the aftercooler 45. The heated gas can be prevented from being heated by the intercooler 41.
Further, since the control panel 60 of the turbo compressor 201 can be disposed on both side surfaces of the casing 8 with the first rotating shaft 11 interposed therebetween, the flexibility of layout is increased.

[Fourth embodiment]
FIG. 11 is a top view (partially sectional view) schematically showing a schematic configuration of a turbo compressor 301 according to the fourth embodiment.
FIG. 12 is a schematic sectional view including the first stage compressor 6 (PP sectional view of FIG. 11). FIG. 13 is a schematic cross-sectional view including the second stage compressor 7 (QQ cross-sectional view of FIG. 11).

The turbo compressor 301 has the same configuration as the turbo compressors 1, 101, and 201 according to the first to third embodiments, but the arrangement of main components is different.
In the following description, parts different from the turbo compressors 1, 101, 201 will be described, and the same parts will be denoted by the same reference numerals and the description thereof will be omitted.

The turbo compressor 301 includes first to third rotating shafts 11 to 13, similarly to the turbo compressors 1, 101, and 201. The second rotating shaft 12 and the third rotating shaft 13 are parallel to the first rotating shaft 11 and are rotatably supported by the gear case 9 at symmetrical positions with the first rotating shaft 11 in between. Is done.
And the 1st impeller 21 and the 2nd impeller 22 are provided in the other end of the 2nd rotating shaft 12 and the 3rd rotating shaft 13, respectively. The first impeller 21 is disposed on the same side as the drive motor 3 with respect to the gear device 10. On the other hand, the second impeller 22 is disposed on the opposite side of the drive motor 3 with the gear device 10 interposed therebetween.
That is, the second rotating shaft 12 is supported so as to extend from the gear device 10 toward the drive motor 3, and the first impeller 21 is disposed at one end (drive motor side) thereof. Moreover, the 3rd rotating shaft 13 is supported so that it may extend on the opposite side to the drive motor 3 from the gear apparatus 10, and the 2nd impeller 22 is arrange | positioned at the end (counter drive motor side).

Further, the turbo compressor 301 is similar to the turbo compressor 201 (unlike the turbo compressors 1 and 101), and the intercooler 41 and the aftercooler 45 are the first to third rotating shafts of the gear device 10 when viewed from above. It arrange | positions along the direction substantially parallel with respect to the axial direction of 11-13. The intercooler 41 and the aftercooler 45 are arranged side by side in the direction away from the second rotating shaft 12 (first impeller 21).
The cooling water inlets / outlets 49 of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 are arranged so as to be exposed on the same side surface (opposite side of the drive motor 3) of the casing 8 of the turbo compressor 1.

The oil storage chamber 50 is provided on the side of the cooling chambers 42 and 46. The oil storage chamber 50 is adjacent to the side of the cooling chambers 42 and 46 opposite to the cooling water inlet / outlet 49. That is, the oil storage chamber 50, the cooling chamber 42, and the cooling chamber 46 (intercooler 41 and aftercooler 45) are arranged side by side in the direction away from the drive motor 3.
The two cooling chambers 42 and 46 and the oil storage chamber 50 are cast integrally with the gear case 9 to constitute the casing 8. Further, the casing 8 has a substantially rectangular shape when viewed from above, and is formed in a size that matches the projected area of the turbo compressor 1.

  Also in the turbo compressor 301 of the fourth embodiment, the first impeller 21 of the first stage compressor 6 and the second impeller 22 of the second stage compressor 7 are different from each other in the rotation shaft (second rotation shaft 12, first rotation shaft 12). Since the three impellers 13) are provided, the first impeller 21 and the second impeller 22 can be driven at optimum rotational speeds, respectively, so that the air can be compressed with high efficiency.

Further, in the turbo compressor 301, the intercooler 41 and the aftercooler 45 are arranged along a direction substantially parallel to the axial direction of the first to third rotating shafts 11 to 13 of the gear device 10 when viewed from above. Therefore, an optimal gas flow path 330 can be formed. That is, the gas flow path 330 (particularly, the first communication path 332, the second communication path 333, and the third communication path 335) has a short flow path length, no large bending portion in the flow path, and is formed as a casting. It has features such as being easy to do.
The first communication passage 232 extends from the spiral chamber of the first stage compressor 6 to the cooling chamber 42 substantially downward. The second communication passage 233 extends from the cooling chamber 42 to the intake passage 34 of the second stage compressor 7 in an obliquely upward direction in a direction substantially orthogonal to the third rotation shaft 13. The third communication passage 233 extends from the spiral chamber of the second stage compressor 6 to the cooling chamber 46 substantially downward.

In addition, since the intercooler 41, the aftercooler 45, and the oil storage chamber 50 are optimally arranged, the installation area of the turbo compressor 1 is substantially rectangular and compact.
Further, in the turbo compressor 301, the cooling water inlet / outlet 49 of each of the heat exchangers 43 and 47 of the intercooler 41 and the aftercooler 45 is disposed so as to be exposed on the same side surface of the casing 8, so that the piping work and the like become efficient it can.
Further, since the intercooler 41 and the aftercooler 45 are arranged so that the gas inlet sides (high temperature sides) thereof are adjacent to each other, the gas cooled by the intercooler 41 is heated by the aftercooler 45 or cooled by the aftercooler 45. The heated gas can be prevented from being heated by the intercooler 41.
Further, since the control panel 60 of the turbo compressor 301 can be disposed on both side surfaces of the casing 8 with the first rotating shaft 11 interposed therebetween, the flexibility of layout is increased.

  The various shapes and combinations of the constituent members shown in the above-described embodiments are merely examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.

1 is a top view schematically showing a schematic configuration of a turbo compressor 1 according to a first embodiment. 2 is a cross-sectional view showing the configuration of the gear device 10. FIG. It is a cross-sectional schematic diagram (PP sectional drawing of FIG. 1) containing the 1st stage compressor 6. FIG. It is a cross-sectional schematic diagram (QQ sectional drawing of FIG. 1) including the 2nd stage compressor 7. FIG. It is a top view which shows typically schematic structure of the turbo compressor 101 which concerns on 2nd embodiment. It is a cross-sectional schematic diagram (PP sectional drawing of FIG. 5) containing the 1st stage compressor 6. FIG. It is a cross-sectional schematic diagram (QQ sectional drawing of FIG. 5) including the 2nd stage compressor 7. FIG. It is a top view which shows typically schematic structure of the turbo compressor 201 which concerns on 3rd embodiment. It is a cross-sectional schematic diagram (PP sectional drawing of FIG. 8) containing the 1st stage compressor 6. FIG. It is a cross-sectional schematic diagram (QQ sectional drawing of FIG. 8) containing the 2nd stage compressor 7. FIG. It is a top view which shows typically schematic structure of the turbo compressor 301 which concerns on 4th embodiment. It is a cross-sectional schematic diagram (PP sectional drawing of FIG. 11) containing the 1st stage compressor 6. FIG. It is a cross-sectional schematic diagram (QQ sectional drawing of FIG. 11) including the 2nd stage compressor 7. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,101,201,301 ... Turbo compressor 3 ... Drive motor 6 ... First stage compressor 7 ... Second stage compressor 8 ... Casing 10 ... Gear apparatus 11 ... First rotating shaft 12 ... Second rotating shaft 13 ... 3rd rotating shaft 14 ... 1st gear 15 ... 2nd gear 16 ... 3rd gear 21 ... 1st impeller 22 ... 2nd impeller 30, 130, 230, 330 ... Gas flow path 31 ... Intake passage 32,132, 232, 332 ... first communication passage 33, 133, 233, 333 ... second communication passage 34 ... intake passage 35, 135, 235, 335 ... third communication passage 36 ... exhaust port 41 ... intercooler (first cooling section)
42 ... Cooling chamber 43 ... Heat exchanger 45 ... Aftercooler (second cooling part)
46 ... Cooling chamber 47 ... Heat exchanger 49 ... Cooling water inlet / outlet port 50 ... Oil reservoir chamber 60 ... Control panel A ... Air (working gas)
L ... oil

Claims (11)

A first rotating shaft connected to the output shaft of the drive motor and having a first gear;
A second rotating shaft having a second gear meshing with the first gear;
A first impeller attached to the second rotating shaft;
A third rotating shaft having a third gear meshing with the first gear and disposed substantially parallel to the second rotating shaft;
A second impeller attached to the third rotating shaft;
A first cooling section for cooling the working gas compressed by the first impeller;
A second cooling section for cooling the working gas compressed by the second impeller;
The first to third rotating shafts and the first and second cooling units are accommodated and working gas is transferred from the first impeller to the second cooling unit through the first cooling unit and the second impeller. A casing having a gas flow path leading to
In a turbo compressor comprising:
The first and second impellers are disposed on the side opposite to the driving motor with respect to the first gear, and the first and second cooling parts are along a direction substantially orthogonal to the first rotation axis. A turbo compressor characterized by being arranged. A first rotating shaft connected to the output shaft of the drive motor and having a first gear;
A second rotating shaft having a second gear meshing with the first gear;
A first impeller attached to the second rotating shaft;
A third rotating shaft having a third gear meshing with the first gear and disposed substantially parallel to the second rotating shaft;
A second impeller attached to the third rotating shaft;
A first cooling section for cooling the working gas compressed by the first impeller;
A second cooling section for cooling the working gas compressed by the second impeller;
The first to third rotating shafts and the first and second cooling units are accommodated and working gas is transferred from the first impeller to the second cooling unit through the first cooling unit and the second impeller. A casing having a gas flow path leading to
In a turbo compressor comprising:
The first and second impellers are arranged on the drive motor side with respect to the first gear, and the first and second cooling parts are arranged along a direction substantially orthogonal to the first rotation axis. A turbo compressor characterized by that. A first rotating shaft connected to the output shaft of the drive motor and having a first gear;
A second rotating shaft having a second gear meshing with the first gear;
A first impeller attached to the second rotating shaft;
A third rotating shaft having a third gear meshing with the first gear and disposed substantially parallel to the second rotating shaft;
A second impeller attached to the third rotating shaft;
A first cooling section for cooling the working gas compressed by the first impeller;
A second cooling section for cooling the working gas compressed by the second impeller;
The first to third rotating shafts and the first and second cooling units are accommodated and working gas is transferred from the first impeller to the second cooling unit through the first cooling unit and the second impeller. A casing having a gas flow path leading to
In a turbo compressor comprising:
The first impeller is disposed on the side opposite to the drive motor with respect to the first gear, the second impeller is disposed on the drive motor side, and the first and second cooling portions are disposed on the first rotation shaft. The turbo compressor is arranged along a substantially parallel direction. A first rotating shaft connected to the output shaft of the drive motor and having a first gear;
A second rotating shaft having a second gear meshing with the first gear;
A first impeller attached to the second rotating shaft;
A third rotating shaft having a third gear meshing with the first gear and disposed substantially parallel to the second rotating shaft;
A second impeller attached to the third rotating shaft;
A first cooling section for cooling the working gas compressed by the first impeller;
A second cooling section for cooling the working gas compressed by the second impeller;
The first to third rotating shafts and the first and second cooling units are accommodated and working gas is transferred from the first impeller to the second cooling unit through the first cooling unit and the second impeller. A casing having a gas flow path leading to
In a turbo compressor comprising:
The first impeller is disposed on the drive motor side with respect to the first gear, the second impeller is disposed on the counter drive motor side, and the first and second cooling units are disposed on the first rotation shaft. The turbo compressor is arranged along a substantially parallel direction.   The turbo compressor according to any one of claims 1 to 4, wherein the first and second cooling units are disposed below the first and second impellers.   The turbo compressor according to claim 5, wherein the first cooling unit and the second cooling unit have a coolant inlet / outlet on the same end face side.   2. The casing according to claim 1, wherein the casing has an oil reservoir chamber that is disposed substantially parallel to the first and second cooling sections and that contains oil for lubricating the first to third gears. The turbo compressor according to claim 2.   The turbo compressor according to claim 7, wherein the oil storage chamber is disposed on a low temperature part side of the first or second cooling part.   The turbo compressor according to any one of claims 1 to 8, wherein the casing is integrally formed of a casting.   The turbo compressor according to claim 2, wherein a lubricating oil device is disposed on the oil storage chamber.   11. The turbo compressor according to claim 1, wherein the drive motor is attached to the casing so as to be positioned in an installation area of the casing.

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