Patent Description:
Disclosed in, for example, Patent Document <NUM> is a transmission (integrally geared compressor) including a drive small gear (drive gear) driven by a steam turbine, a large gear as an intermediate gear meshing with the drive small gear and a turbo machine rotor (compression unit), and a driven small gear connected to a main compressor in a state of meshing with the drive gear.

By the way, the number of compression units may be increased in order to improve the output of an integrally geared compressor. However, due to constraints on the installation of a gear for compression unit rotation, it may be necessary to provide a new intermediate gear between the gear and a drive gear or an existing intermediate gear. Accordingly, the space occupied by the integrally geared compressor may increase as the output of the integrally geared compressor is improved.

The present disclosure provides an integrally geared compressor capable of suppressing an increase in occupied space while improving output.

Provided is an lntegrally geared compressor according to claim <NUM>.

According to the present disclosure, it is possible to provide an integrally geared compressor capable of suppressing an increase in occupied space while improving output.

Hereinafter, an integrally geared compressor according to an embodiment of the present disclosure will be described with reference to the drawings.

The integrally geared compressor compresses a process gas as a working fluid generated in, for example, a chemical plant. The integrally geared compressor supplies the boosted process gas to reaction equipment provided in the chemical plant.

As shown in <FIG> and <FIG>, an integrally geared compressor <NUM> has a multi-axis multi-stage configuration driving a compression unit <NUM> having a plurality of impellers. The integrally geared compressor <NUM> includes a motor <NUM>, a compression unit drive mechanism <NUM>, the compression unit <NUM>, a uniaxial multi-stage compressor <NUM>, and a shaft joint <NUM>.

The motor <NUM> is a drive source generating power for driving the integrally geared compressor <NUM>. The motor <NUM> has an output shaft <NUM> and a motor main body <NUM> rotating the output shaft <NUM>. The output shaft <NUM> is a cylindrical drive shaft extending about an output axis O1 extending in the horizontal direction and rotatable around the output axis O1.

The motor main body <NUM> is fixed in a state of being placed on a foundation B such as the ground, a pedestal, and a base plate. The motor main body <NUM> has, for example, a motor stator (not shown) as a stator and a motor rotor (not shown) as a rotor integrally fixed to the output shaft <NUM>.

The motor stator is electrically connected to, for example, an external electric power system. By an electric current flowing through a coil of the motor stator, an electromagnetic force rotating the motor rotor in the circumferential direction of the output shaft <NUM> is generated. In other words, the output shaft <NUM> rotates when electric power is input from the outside to the motor stator of the motor main body <NUM>.

The compression unit drive mechanism <NUM> rotates an apparatus compressing a working fluid G supplied from the outside by the power (torque) generated by the motor <NUM> being transmitted. The compression unit drive mechanism <NUM> has a gear case <NUM>, a drive gear <NUM>, a first drive side pinion <NUM>, a second drive side pinion <NUM>, an intermediate gear <NUM>, a first intermediate side pinion <NUM>, a second intermediate side pinion <NUM>, and a bearing <NUM>.

The gear case <NUM> is a casing for accommodating a plurality of gears inside.

The drive gear <NUM> is a gear accommodated in the gear case <NUM> and rotated by the rotation of the motor <NUM>. The drive gear <NUM> has a drive support shaft <NUM> and a drive gear main body <NUM>. The drive support shaft <NUM> has a cylindrical shape extending about a drive axis O2 extending in the horizontal direction.

The drive support shaft <NUM> in the present embodiment is integrally connected to the output shaft <NUM> of the motor <NUM> via a flexible coupling C. Accordingly, the drive support shaft <NUM> is rotated with the rotation of the output shaft <NUM>.

Here, the output axis O1 on the output shaft <NUM> and the drive axis O2 on the drive support shaft <NUM> are on the same straight line. The output shaft <NUM> and the drive support shaft <NUM> share an axis O as a center line. The axis O is configured by the output axis O1 and the drive axis O2.

In the present embodiment, the direction in which the axis O extends (up-down direction in <FIG>) is simply referred to as "axial direction Da". In addition, one of both sides in the axial direction Da (upper side in <FIG>, first side) is simply referred to as "one side Dab", and the opposite side (lower side in <FIG>, second side) is simply referred to as "the other side Daf".

The drive gear main body <NUM> is a helical gear fixed to the drive support shaft <NUM> from the outer peripheral side and spreading about the drive support shaft <NUM>. The drive gear main body <NUM> spreads in a direction perpendicular to the axis O. The drive support shaft <NUM> protrudes from the drive gear main body <NUM> to the one side Dab and the other side Daf.

Hereinafter, for convenience of description, the direction in which a virtual surface X spreading in the direction perpendicular to the axis O (direction in which the drive gear main body <NUM> spreads) and bisecting the drive gear <NUM> in the axial direction Da spreads will be referred to as "in-plane direction Pi". At this time, the axial direction Da corresponds to "out-of-plane direction Po" with respect to the virtual surface X.

The first drive side pinion <NUM> is a gear accommodated in the gear case <NUM> and rotating with the rotation of the drive gear <NUM>. The first drive side pinion <NUM> has a first drive side pinion support shaft <NUM>, a first drive side pinion main body <NUM>, and a first thrust bearing <NUM>. The first drive side pinion support shaft <NUM> has a cylindrical shape extending about a first axis A1 parallel to the axis O.

The first drive side pinion main body <NUM> is fixed to the first drive side pinion support shaft <NUM> from the outer peripheral side. The first drive side pinion main body <NUM> is a helical gear spreading about the first drive side pinion support shaft <NUM>. The first drive side pinion main body <NUM> spreads in a direction perpendicular to the first axis A1. The first drive side pinion support shaft <NUM> protrudes from the first drive side pinion main body <NUM> to the one side Dab and the other side Daf.

The first drive side pinion main body <NUM> meshes with the drive gear main body <NUM> in a state of being adjacent to the drive gear main body <NUM> in the in-plane direction Pi. The first drive side pinion main body <NUM> in the present embodiment meshes only with a drive gear upper half portion 211a in the drive gear main body <NUM>.

The outer diameter of the first drive side pinion main body <NUM> in the present embodiment is smaller than the outer diameter of the drive gear main body <NUM>. Accordingly, the number of teeth of the first drive side pinion main body <NUM> is smaller than the number of teeth of the drive gear main body <NUM>.

The drive gear upper half portion 211a in the drive gear main body <NUM> in the present embodiment means the drive gear main body <NUM> in the region above the axis O in the vertical direction (up-down direction in <FIG>) when the drive gear main body <NUM> is viewed from the axial direction Da.

In addition, a drive gear lower half portion 211b in the drive gear main body <NUM> means the drive gear main body <NUM> in the region below the axis O in the vertical direction when the drive gear main body <NUM> is viewed from the axial direction Da.

In addition, the tooth bottom circle diameter, the tooth tip circle diameter, the pitch circle diameter, or the like that can be measured as the distance (dimension) from the central axis of each gear is adopted as "outer diameter" of the gear in the present embodiment.

The first thrust bearing <NUM> is a pair of thrust bearings fixed so as to surround the first drive side pinion support shaft <NUM> of the first drive side pinion <NUM> from the outer peripheral side. The first thrust bearing <NUM> is disposed closer to each of the one side Dab and the other side Daf than the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The first thrust bearing <NUM> is formed larger in diameter than the first drive side pinion main body <NUM>. The first thrust bearing <NUM> comes into sliding contact from the axial direction Da with, for example, a thrust collar (not shown) spreading in a disk shape from the first drive side pinion support shaft <NUM> toward the outer peripheral side integrally with the first drive side pinion support shaft <NUM>. As a result, displacement of the first drive side pinion main body <NUM> in the axial direction Da is regulated.

The second drive side pinion <NUM> is a gear accommodated in the gear case <NUM> and rotating with the rotation of the drive gear <NUM>. The second drive side pinion <NUM> has a second drive side pinion support shaft <NUM>, a second drive side pinion main body <NUM>, and a second thrust bearing <NUM>. The second drive side pinion support shaft <NUM> has a cylindrical shape extending about a second axis A2 parallel to the axis O.

The second drive side pinion main body <NUM> is a helical gear spreading about the second drive side pinion support shaft <NUM>. The second drive side pinion main body <NUM> spreads in a direction perpendicular to the second axis A2. The second drive side pinion support shaft <NUM> protrudes from the second drive side pinion main body <NUM> to the one side Dab and the other side Daf.

The second drive side pinion main body <NUM> meshes with the drive gear main body <NUM> at a position separated in the in-plane direction Pi from the first drive side pinion main body <NUM> of the first drive side pinion <NUM>. The second drive side pinion main body <NUM> is adjacent to the drive gear main body <NUM> in the in-plane direction Pi. The second drive side pinion main body <NUM> in the present embodiment meshes only with the part of the drive gear main body <NUM> where the drive gear upper half portion 211a and the drive gear lower half portion 211b are switched.

The outer diameter of the second drive side pinion main body <NUM> in the present embodiment is equal to the outer diameter of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>. Accordingly, the number of teeth of the second drive side pinion main body <NUM> is equal to the number of teeth of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The second thrust bearing <NUM> is a pair of thrust bearings fixed so as to surround the second drive side pinion support shaft <NUM> of the second drive side pinion <NUM> from the outer peripheral side. The second thrust bearing <NUM> is disposed on each of the one side Dab and the other side Daf with respect to the second drive side pinion main body <NUM> of the second drive side pinion <NUM>.

The second thrust bearing <NUM> is formed larger in diameter than the second drive side pinion main body <NUM>. The second thrust bearing <NUM> comes into sliding contact with, for example, a thrust collar (not shown) from the axial direction Da. The thrust collar spreads in a disk shape from the second drive side pinion support shaft <NUM> toward the outer peripheral side integrally with the second drive side pinion support shaft <NUM>. As a result, displacement of the second drive side pinion main body <NUM> in the axial direction Da is regulated.

The intermediate gear <NUM> is a gear accommodated in the gear case <NUM> and rotating with the rotation of the drive gear <NUM>. The intermediate gear <NUM> has an intermediate support shaft <NUM> and an intermediate gear main body <NUM>. The intermediate support shaft <NUM> has a cylindrical shape extending about an intermediate axis O3 parallel to the axis O.

The intermediate gear main body <NUM> is a helical gear fixed to the intermediate support shaft <NUM> from the outer peripheral side and spreading about the intermediate support shaft <NUM>. The intermediate gear main body <NUM> spreads in a direction perpendicular to the intermediate axis <NUM>. The intermediate support shaft <NUM> protrudes from the intermediate gear main body <NUM> to the one side Dab and the other side Daf.

The intermediate gear main body <NUM> meshes with the drive gear main body <NUM> at a position separated in the in-plane direction Pi from the first drive side pinion main body <NUM> of the first drive side pinion <NUM> and the second drive side pinion main body <NUM> of the second drive side pinion <NUM>. The intermediate gear main body <NUM> is adjacent to the drive gear main body <NUM> in the in-plane direction Pi.

As shown in <FIG>, the intermediate gear main body <NUM> in the present embodiment meshes with the drive gear upper half portion 211a in the drive gear main body <NUM>. Accordingly, the intermediate axis O3 is positioned above the axis O in the vertical direction.

The first intermediate side pinion <NUM> is a gear accommodated in the gear case <NUM> and rotating with the rotation of the intermediate gear <NUM>. The first intermediate side pinion <NUM> has a first intermediate side pinion support shaft <NUM>, a first intermediate side pinion main body <NUM>, and a third thrust bearing <NUM>. The first intermediate side pinion support shaft <NUM> has a cylindrical shape extending about a third axis A3 parallel to the axis O.

The first intermediate side pinion main body <NUM> is fixed to the first intermediate side pinion support shaft <NUM> from the outer peripheral side. The first intermediate side pinion main body <NUM> is a helical gear spreading about the first intermediate side pinion support shaft <NUM>. The first intermediate side pinion main body <NUM> spreads in a direction perpendicular to the third axis A3. The first intermediate side pinion support shaft <NUM> protrudes from the first intermediate side pinion main body <NUM> to the one side Dab and the other side Daf.

The first intermediate side pinion main body <NUM> meshes with the intermediate gear main body <NUM> in a state of being adjacent to the intermediate gear main body <NUM> in the in-plane direction Pi. The first intermediate side pinion main body <NUM> in the present embodiment meshes only with an intermediate gear upper half portion 241a in the intermediate gear main body <NUM>.

The intermediate gear upper half portion 241a in the intermediate gear main body <NUM> in the present embodiment means the intermediate gear main body <NUM> in the region above the intermediate axis O3 in the vertical direction when the intermediate gear main body <NUM> is viewed from the axial direction Da.

In addition, an intermediate gear lower half portion 241b in the intermediate gear main body <NUM> means the intermediate gear main body <NUM> in the region below the intermediate axis O3 in the vertical direction when the intermediate gear main body <NUM> is viewed from the axial direction Da.

The outer diameter of the first intermediate side pinion main body <NUM> in the present embodiment is equal to the outer diameter of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>. Accordingly, the number of teeth of the first intermediate side pinion main body <NUM> is equal to the number of teeth of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The third thrust bearing <NUM> is a pair of thrust bearings fixed so as to surround the first intermediate side pinion support shaft <NUM> of the first intermediate side pinion <NUM> from the outer peripheral side. The third thrust bearing <NUM> is disposed closer to the one side Dab and the other side Daf than the first intermediate side pinion main body <NUM> of the first intermediate side pinion <NUM>.

The third thrust bearing <NUM> is formed larger in diameter than the first intermediate side pinion main body <NUM>. The third thrust bearing <NUM> comes into sliding contact with, for example, a thrust collar (not shown) from the axial direction Da. The thrust collar spreads in a disk shape from the first intermediate side pinion support shaft <NUM> toward the outer peripheral side integrally with the first intermediate side pinion support shaft <NUM>. As a result, displacement of the first intermediate side pinion main body <NUM> in the axial direction Da is regulated.

The second intermediate side pinion <NUM> is a gear accommodated in the gear case <NUM> and rotating with the rotation of the drive gear <NUM>. The second intermediate side pinion <NUM> has a second intermediate side pinion support shaft <NUM>, a second intermediate side pinion main body <NUM>, and a fourth thrust bearing <NUM>. The second intermediate side pinion support shaft <NUM> has a cylindrical shape extending about a fourth axis A4 parallel to the axis O.

The second intermediate side pinion main body <NUM> is fixed to the second intermediate side pinion support shaft <NUM> from the outer peripheral side. The second intermediate side pinion main body <NUM> is a helical gear spreading about the second intermediate side pinion support shaft <NUM>. The second intermediate side pinion main body <NUM> spreads in a direction perpendicular to the fourth axis A4. The second intermediate side pinion support shaft <NUM> protrudes from the second intermediate side pinion main body <NUM> to the one side Dab and the other side Daf.

The second intermediate side pinion main body <NUM> meshes with the intermediate gear main body <NUM> at a position separated in the in-plane direction Pi from the first intermediate side pinion main body <NUM> of the first intermediate side pinion <NUM>. The second intermediate side pinion main body <NUM> is adjacent to the intermediate gear main body <NUM> in the in-plane direction Pi.

The second intermediate side pinion main body <NUM> in the present embodiment meshes only with the intermediate gear lower half portion 241b in the intermediate gear main body <NUM>. Specifically, the second intermediate side pinion main body <NUM> is disposed directly below the intermediate gear main body <NUM>.

The outer diameter of the second intermediate side pinion main body <NUM> in the present embodiment is equal to the outer diameter of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>. Accordingly, the number of teeth of the second intermediate side pinion main body <NUM> is equal to the number of teeth of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The fourth thrust bearing <NUM> is a pair of thrust bearings fixed so as to surround the second intermediate side pinion support shaft <NUM> of the second intermediate side pinion <NUM> from the outer peripheral side. The fourth thrust bearing <NUM> is disposed closer to the one side Dab and the other side Daf than the second intermediate side pinion main body <NUM> of the second intermediate side pinion <NUM>.

The fourth thrust bearing <NUM> is formed larger in diameter than the second intermediate side pinion main body <NUM>. The fourth thrust bearing <NUM> comes into sliding contact from the axial direction Da with, for example, a thrust collar (not shown) spreading in a disk shape from the second intermediate side pinion support shaft <NUM> toward the outer peripheral side integrally with the second intermediate side pinion support shaft <NUM>. As a result, displacement of the second intermediate side pinion main body <NUM> in the axial direction Da is regulated.

The compression unit <NUM> compresses the working fluid G supplied from the outside by being rotated by the rotation of each of the first drive side pinion <NUM>, the second drive side pinion <NUM>, and the first intermediate side pinion <NUM>. The compression unit <NUM> is configured by a first compression unit <NUM>, a second compression unit <NUM>, a third compression unit <NUM>, a fourth compression unit <NUM>, a fifth compression unit <NUM>, and a sixth compression unit <NUM>.

The first compression unit <NUM> is connected to the first drive side pinion <NUM> and compresses the working fluid G by being rotated by the rotation of the first drive side pinion <NUM>. The first compression unit <NUM> has a first rotor <NUM> and a first compression unit casing <NUM>. The first rotor <NUM> has a first rotating shaft 310a and a first impeller 310b.

The first rotating shaft 310a is a cylindrical member extending about the first axis A1 and rotatable around the first axis A1. The first rotating shaft 310a is integrally connected from the one side Dab to the first drive side pinion support shaft <NUM> of the first drive side pinion <NUM> and protrudes from the gear case <NUM> to the one side Dab.

The first impeller 310b is fixed so as to cover the part of the first rotating shaft 310a protruding from the gear case <NUM> to the one side Dab from the outer peripheral side. The first impeller 310b has a plurality of blades arranged in the circumferential direction of the first rotating shaft 310a when fixed to the first rotating shaft 310a.

The first compression unit casing <NUM> covers the first impeller 310b from the outer peripheral side and forms a first compression passage inside together with the first impeller 310b. The first compression unit casing <NUM> in the present embodiment is formed integrally with the gear case <NUM>.

The first compression unit casing <NUM> has a first gas introduction port 311a for introducing the working fluid G from the outside into the first compression passage and a first gas discharge port 311b for discharging the compressed working fluid G from the first compression passage to the outside. A pipe (not shown) through which the working fluid G flows is connected to the first gas introduction port 311a and the first gas discharge port 311b.

In the present embodiment, a one-stage compression mechanism is configured by the first rotor <NUM> and the first compression unit casing <NUM> in the first compression unit <NUM>. The first compression unit <NUM> has the single first impeller 310b.

The second compression unit <NUM> is connected to the first intermediate side pinion <NUM> and compresses the working fluid G by being rotated by the rotation of the first intermediate side pinion <NUM>. The second compression unit <NUM> has a second rotor <NUM> and a second compression unit casing <NUM>. The second rotor <NUM> has a second rotating shaft 320a and a second impeller 320b.

The second rotating shaft 320a is a cylindrical member extending about the third axis A3 and rotatable around the third axis A3. The second rotating shaft 320a is integrally connected from the one side Dab to the first intermediate side pinion support shaft <NUM> of the first intermediate side pinion <NUM>. Accordingly, the second rotating shaft 320a protrudes from the gear case <NUM> to the one side Dab.

The second impeller 320b is fixed so as to cover the part of the second rotating shaft 320a protruding from the gear case <NUM> to the one side Dab from the outer peripheral side. The second impeller 320b has a plurality of blades arranged in the circumferential direction of the second rotating shaft 320a when fixed to the second rotating shaft 320a.

The second compression unit casing <NUM> covers the second impeller 320b and forms a second compression passage inside together with the second impeller 320b. The second compression unit casing <NUM> in the present embodiment is formed integrally with the gear case <NUM>.

The second compression unit casing <NUM> has a second gas introduction port 321a for introducing the working fluid G from the outside into the second compression passage and a second gas discharge port 321b for discharging the compressed working fluid G from the second compression passage to the outside. A pipe through which the working fluid G flows is connected to the second gas introduction port 321a and the second gas discharge port 321b.

In the present embodiment, a one-stage compression mechanism is configured by the second rotor <NUM> and the second compression unit casing <NUM> in the second compression unit <NUM>. The second compression unit <NUM> has the single second impeller 320b.

The second compression unit <NUM> compresses the working fluid G supplied from the outside in a stage ahead of the first compression unit <NUM>. Accordingly, the working fluid G compressed in the second compression passage in the second compression unit <NUM> is introduced into the first compression passage in the first compression unit <NUM> through a pipe and further compressed.

The outer diameter of the second impeller 320b of the second rotor <NUM> in the second compression unit <NUM> is larger than the outer diameter of the first impeller 310b of the first rotor <NUM> in the first compression unit <NUM>. In other words, each blade of the first impeller 310b is formed larger than each blade of the second impeller 320b.

The third compression unit <NUM> is connected to the second drive side pinion <NUM> and compresses the working fluid G by being rotated by the rotation of the second drive side pinion <NUM>. The third compression unit <NUM> has a third rotor <NUM> and a third compression unit casing <NUM>. The third rotor <NUM> has a third rotating shaft 330a and a third impeller 330b.

The third rotating shaft 330a is a cylindrical member extending about the second axis A2 and rotatable around the second axis A2. The third rotating shaft 330a is integrally connected from the one side Dab to the second drive side pinion support shaft <NUM> of the second drive side pinion <NUM> and protrudes from the gear case <NUM> to the one side Dab.

The third impeller 330b is fixed so as to cover the part of the third rotating shaft 330a protruding from the gear case <NUM> to the one side Dab from the outer peripheral side. The third impeller 330b has a plurality of blades arranged in the circumferential direction of the third rotating shaft 330a when fixed to the third rotating shaft 330a.

The third compression unit casing <NUM> covers the third impeller 330b and forms a third compression passage inside together with the third impeller 330b. The third compression unit casing <NUM> in the present embodiment is formed integrally with the gear case <NUM>.

The third compression unit casing <NUM> has a third gas introduction port 331a for introducing the working fluid G from the outside into the third compression passage and a third gas discharge port 331b for discharging the compressed working fluid G from the third compression passage to the outside. A pipe through which the working fluid G flows is connected to the third gas introduction port 331a and the third gas discharge port 331b.

In the present embodiment, a one-stage compression mechanism is configured by the third rotor <NUM> and the third compression unit casing <NUM> in the third compression unit <NUM>. The third compression unit <NUM> has the single third impeller 330b.

The third compression unit <NUM> compresses the working fluid G in a stage behind the first compression unit <NUM>. Accordingly, the working fluid G compressed in the first compression passage in the first compression unit <NUM> is introduced into the third compression passage in the third compression unit <NUM> through a pipe and further compressed.

The outer diameter of the third impeller 330b of the third rotor <NUM> in the third compression unit <NUM> is smaller than the outer diameter of the first impeller 310b of the first rotor <NUM> in the first compression unit <NUM>. In other words, each blade of the third impeller 330b is formed smaller than each blade of the first impeller 310b.

The fourth compression unit <NUM> is connected to the first intermediate side pinion <NUM> and compresses the working fluid G by being rotated by the rotation of the first intermediate side pinion <NUM>. The fourth compression unit <NUM> has a fourth rotor <NUM> and a fourth compression unit casing <NUM>. The fourth rotor <NUM> has a fourth rotating shaft 340a and a fourth impeller 340b.

The fourth rotating shaft 340a is a cylindrical member extending about the third axis A3 and rotatable around the third axis A3. The fourth rotating shaft 340a is integrally connected from the other side Daf to the first intermediate side pinion support shaft <NUM> of the first intermediate side pinion <NUM>. Accordingly, the fourth rotating shaft 340a protrudes from the gear case <NUM> to the other side Daf.

The fourth impeller 340b is fixed so as to cover the part of the fourth rotating shaft 340a protruding from the gear case <NUM> to the other side Daf from the outer peripheral side. The fourth impeller 340b has a plurality of blades arranged in the circumferential direction of the fourth rotating shaft 340a when fixed to the fourth rotating shaft 340a.

The fourth compression unit casing <NUM> covers the fourth impeller 340b and forms a fourth compression passage inside together with the fourth impeller 340b. The fourth compression unit casing <NUM> in the present embodiment is formed integrally with the gear case <NUM>.

The fourth compression unit casing <NUM> has a fourth gas introduction port 341a for introducing the working fluid G from the outside into the fourth compression passage and a fourth gas discharge port 341b for discharging the compressed working fluid G from the fourth compression passage to the outside. A pipe through which the working fluid G flows is connected to the fourth gas introduction port 341a and the fourth gas discharge port 341b.

In the present embodiment, a one-stage compression mechanism is configured by the fourth rotor <NUM> and the fourth compression unit casing <NUM> in the fourth compression unit <NUM>. The fourth compression unit <NUM> has the single fourth impeller 340b. The fourth compression unit <NUM> in the present embodiment compresses the working fluid G in a stage behind the second compression unit <NUM> and ahead of the first compression unit <NUM>.

Accordingly, the working fluid G compressed in the second compression passage in the second compression unit <NUM> is introduced into the fourth compression passage in the fourth compression unit <NUM> through a pipe and further compressed. The working fluid G compressed in the fourth compression passage in the fourth compression unit <NUM> is introduced into the first compression passage in the first compression unit <NUM> through a pipe and further compressed.

The outer diameter of the fourth impeller 340b of the fourth rotor <NUM> in the fourth compression unit <NUM> is smaller than the outer diameter of the second impeller 320b of the second rotor <NUM> in the second compression unit <NUM>. In addition, the outer diameter of the fourth impeller 340b is larger than the outer diameter of the first impeller 310b in the first compression unit <NUM>. In other words, each blade of the fourth impeller 340b is formed smaller than each blade of the second impeller 320b. In addition, each blade of the fourth impeller 340b is formed larger than each blade of the first impeller 310b.

The fifth compression unit <NUM> is connected to the first drive side pinion <NUM> and compresses the working fluid G by being rotated by the rotation of the first drive side pinion <NUM>. The fifth compression unit <NUM> has a fifth rotor <NUM> and a fifth compression unit casing <NUM>. The fifth rotor <NUM> has a fifth rotating shaft 350a and a fifth impeller 350b.

The fifth rotating shaft 350a is a cylindrical member extending about the first axis A1 and rotatable around the first axis A1. The fifth rotating shaft 350a is integrally connected from the other side Daf to the first drive side pinion support shaft <NUM> of the first drive side pinion <NUM>. The fifth rotating shaft 350a protrudes from the gear case <NUM> to the other side Daf.

The fifth impeller 350b is fixed so as to cover the part of the fifth rotating shaft 350a protruding from the gear case <NUM> to the other side Daf from the outer peripheral side. The fifth impeller 350b has a plurality of blades arranged in the circumferential direction of the fifth rotating shaft 350a when fixed to the fifth rotating shaft 350a.

The fifth compression unit casing <NUM> covers the fifth impeller 350b and forms a fifth compression passage inside together with the fifth impeller 350b. The fifth compression unit casing <NUM> in the present embodiment is formed integrally with the gear case <NUM>.

The fifth compression unit casing <NUM> has a fifth gas introduction port 351a for introducing the working fluid G from the outside into the fifth compression passage and a fifth gas discharge port 351b for discharging the compressed working fluid G from the fifth compression passage to the outside. A pipe through which the working fluid G flows is connected to the fifth gas introduction port 351a and the fifth gas discharge port 351b.

In the present embodiment, a one-stage compression mechanism is configured by the fifth rotor <NUM> and the fifth compression unit casing <NUM> in the fifth compression unit <NUM>. The fifth compression unit <NUM> has the single fifth impeller 350b. The fifth compression unit <NUM> in the present embodiment compresses the working fluid G in a stage behind the first compression unit <NUM> and ahead of the third compression unit <NUM>.

Accordingly, the working fluid G compressed in the first compression passage in the first compression unit <NUM> is introduced into the fifth compression passage in the fifth compression unit <NUM> through a pipe and further compressed. The working fluid G compressed in the fifth compression passage in the fifth compression unit <NUM> is introduced into the third compression passage in the third compression unit <NUM> through a pipe and further compressed.

The outer diameter of the fifth impeller 350b of the fifth rotor <NUM> in the fifth compression unit <NUM> is smaller than the outer diameter of the first impeller 310b of the first rotor <NUM> in the first compression unit <NUM>. In addition, the outer diameter of the fifth impeller 350b is larger than the outer diameter of the third impeller 330b in the third compression unit <NUM>. In other words, each blade of the fifth impeller 350b is formed smaller than each blade of the first impeller <NUM>10b. In addition, each blade of the fifth impeller 350b is formed larger than each blade of the third impeller 330b.

The sixth compression unit <NUM> is connected to the second drive side pinion <NUM> and compresses the working fluid G by being rotated by the rotation of the second drive side pinion <NUM>. The sixth compression unit <NUM> has a sixth rotor <NUM> and a sixth compression unit casing <NUM>. The sixth rotor <NUM> has a sixth rotating shaft 360a and a sixth impeller 360b.

The sixth rotating shaft 360a is a cylindrical member extending about the second axis A2 and rotatable around the second axis A2. The sixth rotating shaft 360a is integrally connected from the other side Daf to the second drive side pinion support shaft <NUM> of the second drive side pinion <NUM>. The sixth rotating shaft 360a protrudes from the gear case <NUM> to the other side Daf.

The sixth impeller 360b is fixed so as to cover the part of the sixth rotating shaft 360a protruding from the gear case <NUM> to the other side Daf from the outer peripheral side. The sixth impeller 360b has a plurality of blades arranged in the circumferential direction of the sixth rotating shaft 360a when fixed to the sixth rotating shaft 360a.

The sixth compression unit casing <NUM> covers the sixth impeller 360b and forms a sixth compression passage inside together with the sixth impeller 360b. The sixth compression unit casing <NUM> in the present embodiment is formed integrally with the gear case <NUM>.

The sixth compression unit casing <NUM> has a sixth gas introduction port 361a for introducing the working fluid G from the outside into the sixth compression passage and a sixth gas discharge port 361b for discharging the compressed working fluid G from the sixth compression passage to the outside.

In the present embodiment, a one-stage compression mechanism is configured by the sixth rotor <NUM> and the sixth compression unit casing <NUM> in the sixth compression unit <NUM>. The sixth compression unit <NUM> has the single sixth impeller 360b.

The sixth compression unit <NUM> in the present embodiment compresses the working fluid G in a stage behind the third compression unit <NUM>. Accordingly, the working fluid G compressed in the third compression passage in the third compression unit <NUM> is introduced into the sixth compression passage in the sixth compression unit <NUM> through a pipe and further compressed.

The outer diameter of the sixth impeller 360b of the sixth rotor <NUM> in the sixth compression unit <NUM> is smaller than the outer diameter of the third impeller 330b of the third rotor <NUM> in the third compression unit <NUM>. In other words, each blade of the sixth impeller 360b is formed smaller than each blade of the third impeller 330b.

Accordingly, the working fluid G supplied from the outside to the compression unit <NUM> is introduced in the order of the second compression unit <NUM>, the fourth compression unit <NUM>, the first compression unit <NUM>, the fifth compression unit <NUM>, the third compression unit <NUM>, and the sixth compression unit <NUM> and is sequentially compressed (boosted).

In addition, the size of the impeller in each compression unit <NUM> (first impeller 310b to sixth impeller 360b) decreases in the order of the second compression unit <NUM>, the fourth compression unit <NUM>, the first compression unit <NUM>, the fifth compression unit <NUM>, the third compression unit <NUM>, and the sixth compression unit <NUM>.

The uniaxial multi-stage compressor <NUM> performs boosting by further compressing the working fluid G compressed by the compression unit <NUM>. The uniaxial multi-stage compressor <NUM> in the present embodiment further compresses the working fluid G compressed by the sixth compression unit <NUM>. The uniaxial multi-stage compressor <NUM> has a compressor rotor <NUM> and a compressor casing <NUM>.

The compressor rotor <NUM> is connected to the second intermediate side pinion <NUM> and is rotated with the rotation of the second intermediate side pinion <NUM>. The compressor rotor <NUM> has a compressor rotating shaft 40a and a plurality of compressor impellers 40b. The compressor rotating shaft 40a has a cylindrical shape extending about the fourth axis A4.

The plurality of compressor impellers 40b are arranged on the compressor rotating shaft 40a so as to be lined up in the axial direction Da and rotate around the fourth axis A4 integrally with the compressor rotating shaft 40a. Each compressor impeller 40b has a plurality of blades arranged in the circumferential direction of the compressor rotating shaft 40a when fixed to the compressor rotating shaft 40a. The compressor rotor <NUM> in the present embodiment has three compressor impellers 40b.

The compressor impellers 40b are formed to have the same size. The outer diameter of each compressor impeller 40b is smaller than the outer diameter of the sixth impeller 360b in the sixth compression unit <NUM>. In other words, each blade of each compressor impeller 40b is formed smaller than each blade of the sixth impeller 360b.

The compressor casing <NUM> forms the outer shell of the uniaxial multi-stage compressor <NUM>. The compressor casing <NUM> is fixed in a state of being placed on the foundation B such as the ground, a pedestal, and a base plate. The foundation B in the present embodiment is positioned below the drive gear <NUM> and the intermediate gear <NUM> in the vertical direction.

The compressor casing <NUM> has a casing main body 41a, a suction port 41b formed in the casing main body 41a, and a discharge port 41c formed in the casing main body 41a. A pipe through which the working fluid G flows is connected to the suction port 41b and the discharge port 41c.

The casing main body 41a forms a compressor passage compressing the working fluid G inside together with the compressor rotor <NUM>. The working fluid G compressed by the sixth compression unit <NUM> is suctioned into the casing main body 41a via the suction port 41b after flowing through the pipe.

The working fluid G suctioned into the casing main body 41a is gradually compressed (boosted) by the plurality of compressor impellers 40b in the compressor passage. The working fluid G compressed in the casing main body 41a is discharged to the outside via the discharge port 41c.

The working fluid G compressed by the uniaxial multi-stage compressor <NUM> is supplied to, for example, reaction equipment provided outside the integrally geared compressor <NUM>. In the present embodiment, a multi-stage (three-stage) compression mechanism is configured by the compressor rotor <NUM> and the compressor casing <NUM> of the uniaxial multi-stage compressor <NUM>.

The shaft joint <NUM> is a shaft joint connecting the second intermediate side pinion support shaft <NUM> of the second intermediate side pinion <NUM> and the compressor rotating shaft 40a of the uniaxial multi-stage compressor <NUM>. The shaft joint <NUM> in the present embodiment is, for example, a diaphragm shaft joint. By the shaft joint <NUM> connecting the second intermediate side pinion support shaft <NUM> and the compressor rotating shaft 40a, the uniaxial multi-stage compressor <NUM> rotates integrally with the second intermediate side pinion <NUM>.

The shaft joint <NUM> is flexible. The shaft joint <NUM> is elastically deformed when the second intermediate side pinion support shaft <NUM> and the compressor rotating shaft 40a are misaligned during the operation of the integrally geared compressor <NUM>. As a result, the shaft joint <NUM> suppresses a loss of torque transmitted from the second intermediate side pinion support shaft <NUM> to the compressor rotating shaft 40a.

Here, the bearing <NUM> of the compression unit drive mechanism <NUM> rotatably supports each of the drive support shaft <NUM> of the drive gear <NUM>, the intermediate support shaft <NUM> of the intermediate gear <NUM>, the second intermediate side pinion support shaft <NUM> in the second intermediate side pinion <NUM>, the first rotating shaft 310a in the first compression unit <NUM>, the second rotating shaft 320a in the second compression unit <NUM>, the third rotating shaft 330a in the third compression unit <NUM>, the fourth rotating shaft 340a in the fourth compression unit <NUM>, the fifth rotating shaft 350a in the fifth compression unit <NUM>, and the sixth rotating shaft 360a in the sixth compression unit <NUM>.

The bearing <NUM> is configured by a drive gear bearing <NUM>, an intermediate gear bearing <NUM>, a pinion support shaft bearing <NUM>, a first compression unit bearing <NUM>, a second compression unit bearing <NUM>, a third compression unit bearing <NUM>, a fourth compression unit bearing <NUM>, a fifth compression unit bearing <NUM>, and a sixth compression unit bearing <NUM>.

A pair of the drive gear bearings <NUM> are fixed to the gear case <NUM>. The drive gear bearing <NUM> is a radial bearing rotatably supporting the drive support shaft <NUM> of the drive gear <NUM> closer to the one side Dab and the other side Daf than the drive gear main body <NUM>.

A pair of the intermediate gear bearings <NUM> are fixed to the gear case <NUM>. The intermediate gear bearing <NUM> is a radial bearing rotatably supporting the intermediate support shaft <NUM> of the intermediate gear <NUM> closer to the one side Dab and the other side Daf than the intermediate gear main body <NUM>.

The pinion support shaft bearing <NUM> is fixed to the gear case <NUM>. The pinion support shaft bearing <NUM> is a radial bearing rotatably supporting the second intermediate side pinion support shaft <NUM> of the second intermediate side pinion <NUM> closer to the one side Dab than the second intermediate side pinion main body <NUM>.

The first compression unit bearing <NUM> is fixed to the gear case <NUM>. The first compression unit bearing <NUM> is a radial bearing rotatably supporting the first rotating shaft 310a of the first rotor <NUM> in the first compression unit <NUM>. The first compression unit bearing <NUM> is disposed closer to the one side Dab than the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The second compression unit bearing <NUM> is fixed to the gear case <NUM>. The second compression unit bearing <NUM> is a radial bearing rotatably supporting closer to the one side Dab than the first intermediate side pinion main body <NUM> of the first intermediate side pinion <NUM>. The second compression unit bearing <NUM> is disposed closer to the one side Dab than the first intermediate side pinion main body <NUM> of the first intermediate side pinion <NUM>.

The third compression unit bearing <NUM> is fixed to the gear case <NUM>. The third compression unit bearing <NUM> is a radial bearing rotatably supporting the third rotating shaft 330a of the third rotor <NUM> in the third compression unit <NUM>. The third compression unit bearing <NUM> is disposed closer to the one side Dab than the second drive side pinion main body <NUM> of the second drive side pinion <NUM>.

The fourth compression unit bearing <NUM> is fixed to the gear case <NUM>. The fourth compression unit bearing <NUM> is a radial bearing rotatably supporting the fourth rotating shaft 340a of the fourth rotor <NUM> in the fourth compression unit <NUM>. The fourth compression unit bearing <NUM> is disposed closer to the other side Daf than the first intermediate side pinion main body <NUM> of the first intermediate side pinion <NUM>.

The fifth compression unit bearing <NUM> is fixed to the gear case <NUM>. The fifth compression unit bearing <NUM> is a radial bearing rotatably supporting the fifth rotating shaft 350a of the fifth rotor <NUM> in the fifth compression unit <NUM>. The fifth compression unit bearing <NUM> is disposed closer to the other side Daf than the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The sixth compression unit bearing <NUM> is fixed to the gear case <NUM>. The sixth compression unit bearing <NUM> is a radial bearing rotatably supporting the sixth rotating shaft 360a of the sixth rotor <NUM> in the sixth compression unit <NUM>. The sixth compression unit bearing <NUM> is disposed closer to the other side Daf than the second drive side pinion main body <NUM> of the second drive side pinion <NUM>.

In the integrally geared compressor <NUM> according to the above embodiment, the uniaxial multi-stage compressor <NUM> having the plurality of compressor impellers 40b is used. Accordingly, the compression efficiency of the integrally geared compressor <NUM> can be improved as compared with another compression unit <NUM> compressing with one impeller. As a result, the output of the integrally geared compressor <NUM> can be improved.

In addition, the drive gear <NUM> and the second intermediate side pinion <NUM> are connected via one intermediate gear <NUM>. Accordingly, on condition that the gear diameters of the drive gear <NUM> and the second intermediate side pinion <NUM> are not changed, the relationship between the rotational speed of the drive gear <NUM> and the rotational speed of the second intermediate side pinion <NUM> can be maintained constant no matter how the gear diameter of the intermediate gear <NUM> is changed.

As a result, it is possible to dispose the uniaxial multi-stage compressor <NUM> at any position, without reducing the rotational speed of the uniaxial multi-stage compressor <NUM>, simply by changing the gear diameter of the intermediate gear <NUM>. Further, the relationship between the rotational speed of the drive gear <NUM> and the rotational speed of the second intermediate side pinion <NUM> is maintained constant. Accordingly, it is possible to suppress a gear-attributable loss when the uniaxial multi-stage compressor <NUM> is driven by the drive gear <NUM>.

In addition, there is no need to dispose a new intermediate gear for driving the uniaxial multi-stage compressor <NUM> so as to mesh with the drive gear <NUM> or the intermediate gear <NUM>. In other words, there is no need to add a new intermediate gear. In other words, it is possible to suppress an increase in dimension in the in-plane direction Pi as compared with a configuration in which an intermediate gear for the uniaxial multi-stage compressor <NUM> is added. Accordingly, it is possible to suppress an increase in the occupied space of the integrally geared compressor <NUM>.

In addition, the uniaxial multi-stage compressor <NUM> having the plurality of compressor impellers 40b is larger in size than the compression unit <NUM> configured by one impeller. In a case where the second intermediate side pinion <NUM> to which the uniaxial multi-stage compressor <NUM> is connected is configured to directly mesh with the drive gear <NUM>, the motor <NUM> for rotating the drive gear <NUM> and the uniaxial multi-stage compressor <NUM> interfere with each other. However, it is possible to suppress the interference between the motor <NUM> and the uniaxial multi-stage compressor <NUM> via the intermediate gear <NUM>. Further, the size of the integrally geared compressor <NUM> can be reduced as compared with a case where every compression unit <NUM> is a uniaxial multi-stage compressor.

In addition, in the integrally geared compressor <NUM> according to the above embodiment, the first drive side pinion <NUM>, the first intermediate side pinion <NUM>, and the second intermediate side pinion <NUM> are smaller in outer diameter than the drive gear <NUM>. As a result, the first drive side pinion <NUM>, the first intermediate side pinion <NUM>, and the second intermediate side pinion <NUM> are smaller in number of teeth than the drive gear <NUM>. Accordingly, the first drive side pinion <NUM>, the first intermediate side pinion <NUM>, and the second intermediate side pinion <NUM> are higher in rotation speed than the drive gear <NUM>.

In other words, the first compression unit <NUM> connected to the first drive side pinion <NUM>, the second compression unit <NUM> connected to the first intermediate side pinion <NUM>, and the uniaxial multi-stage compressor <NUM> connected to the second intermediate side pinion <NUM> are higher in rotation speed than the drive gear <NUM>. Accordingly, the output of the integrally geared compressor <NUM> can be improved.

Further, the dimension in the in-plane direction Pi can be reduced as compared with a configuration in which the first drive side pinion <NUM>, the first intermediate side pinion <NUM>, and the second intermediate side pinion <NUM> are equal to or larger than the drive gear <NUM> in outer diameter. Accordingly, it is possible to further suppress an increase in occupied space while further improving the output of the integrally geared compressor <NUM>.

In addition, in the integrally geared compressor <NUM> according to the above embodiment, the second compression unit <NUM> is configured to compress the working fluid G in a stage ahead of the first compression unit <NUM>. Here, in order to further compress the working fluid G compressed by the second compression unit <NUM> by rotation, the first impeller 310b in the first compression unit <NUM> needs to be smaller than the second impeller 320b in the second compression unit <NUM> in a stage ahead of the first compression unit <NUM>. In other words, the second impeller 320b in the second compression unit <NUM> needs to be larger than the first impeller 310b in the first compression unit <NUM>.

According to the above configuration, the first intermediate side pinion <NUM> to which the second compression unit <NUM> having the second impeller 320b larger than the first impeller 310b in the first compression unit <NUM> is connected meshes with the intermediate gear <NUM>. Accordingly, it is possible to avoid the second compression unit <NUM> interfering with the first compression unit <NUM> and the motor <NUM> as compared with, for example, a configuration in which the first intermediate side pinion <NUM> meshes with the drive gear <NUM>.

In addition, in the integrally geared compressor <NUM> according to the above embodiment, the motor <NUM> and the uniaxial multi-stage compressor <NUM> are configured to be placed on the foundation B with the intermediate gear <NUM> meshing with the drive gear <NUM> in the drive gear upper half portion 211a of the drive gear <NUM> and the second intermediate side pinion <NUM> meshing with the intermediate gear <NUM> in the intermediate gear lower half portion 241b of the intermediate gear <NUM>. As a result, the dimension in the in-plane direction Pi can be reduced as compared with, for example, a configuration in which the drive gear <NUM>, the intermediate gear <NUM>, and the second intermediate side pinion <NUM> mesh so as to be lined up in a row. Accordingly, the integrally geared compressor <NUM> can be made compact.

In addition, the uniaxial multi-stage compressor <NUM> is disposed on the foundation B where the motor <NUM> is placed at a lower position as compared with, for example, a configuration in which the second intermediate side pinion <NUM> meshes with the intermediate gear upper half portion 241a of the intermediate gear <NUM>. Accordingly, the uniaxial multi-stage compressor <NUM> can be stably driven.

In addition, in the integrally geared compressor <NUM> according to the above embodiment, the shaft joint <NUM> connects the second intermediate side pinion support shaft <NUM> of the second intermediate side pinion <NUM> and the compressor rotating shaft 40a of the uniaxial multi-stage compressor <NUM>. As a result, even in a case where misalignment occurs between the second intermediate side pinion support shaft <NUM> and the compressor rotating shaft 40a, the effect of the misalignment can be suppressed by the shaft joint <NUM>. As a result, the rotor dynamics between the second intermediate side pinion support shaft <NUM> and the compressor rotating shaft 40a can be reduced.

Further, the rotor dynamics generated in the second intermediate side pinion support shaft <NUM> and the compressor rotating shaft 40a can be further reduced by the shaft joint <NUM> being elastically deformed. Accordingly, torque can be smoothly transmitted between the second intermediate side pinion support shaft <NUM> and the compressor rotating shaft 40a.

In addition, in the integrally geared compressor <NUM> according to the above embodiment, the third compression unit <NUM> connected to the second drive side pinion <NUM> meshing with the drive gear <NUM> compresses the working fluid G in a stage behind the first compression unit <NUM> and ahead of the uniaxial multi-stage compressor <NUM>. As a result, the third compression unit <NUM> further compresses the working fluid G compressed by the first compression unit <NUM>. Accordingly, the pressure of the working fluid G is further increased. Accordingly, the output of the integrally geared compressor <NUM> can be further improved.

Further, the first intermediate side pinion <NUM> and the second intermediate side pinion <NUM> mesh with the intermediate gear <NUM>. In addition, the first drive side pinion <NUM> and the second drive side pinion <NUM> mesh with the drive gear <NUM>. In other words, many pinions do not mesh with only one of the drive gear <NUM> and the intermediate gear <NUM>. As a result, it is possible to suppress the magnitude of the load applied to the teeth of each of the drive gear <NUM> and the intermediate gear <NUM> being biased.

Although an embodiment of the present disclosure has been described in detail with reference to the drawings, the specific configuration is not limited to the configuration of the embodiment and the invention is not limited by the embodiment and is limited only by the claims.

It should be noted that the outer diameter of each pinion main body of the second drive side pinion <NUM>, the first intermediate side pinion <NUM>, and the second intermediate side pinion <NUM> (second drive side pinion main body <NUM>, first intermediate side pinion main body <NUM>, and second intermediate side pinion main body <NUM>) may not be equal to the outer diameter of the first drive side pinion main body <NUM> of the first drive side pinion <NUM>.

The outer diameters of the pinion main bodies of the first drive side pinion <NUM>, the second drive side pinion <NUM>, the first intermediate side pinion <NUM>, and the second intermediate side pinion <NUM> (first drive side pinion main body <NUM>, second drive side pinion main body <NUM>, first intermediate side pinion main body <NUM>, and second intermediate side pinion main body <NUM>) may be mutually different.

In addition, the outer diameter of the intermediate gear main body <NUM> in the above embodiment may be equal to the outer diameter of the drive gear main body <NUM>. In addition, the outer diameter of the intermediate gear main body <NUM> may be larger than the outer diameter of the drive gear main body <NUM>. In addition, the outer diameter of the intermediate gear main body <NUM> may be smaller than the outer diameter of the drive gear main body <NUM>.

In addition, the first intermediate side pinion main body <NUM> of the first intermediate side pinion <NUM> may mesh with the intermediate gear lower half portion 241b in the intermediate gear main body <NUM>.

Further, although a configuration in which the working fluid G compressed by the second compression unit <NUM> is introduced into the fourth compression unit <NUM> has been described in the above embodiment, the present disclosure is not limited to this configuration. For example, in an alternative configuration, the working fluid G supplied from the outside may be simultaneously supplied to the second compression unit <NUM> and the fourth compression unit <NUM>, be compressed by each of the second compression unit <NUM> and the fourth compression unit <NUM>, and then merge to be introduced into the first compression unit <NUM>. At this time, the outer diameter of the second impeller 320b in the second compression unit <NUM> and the outer diameter of the fourth impeller 340b in the fourth compression unit <NUM> may be equal to each other.

In addition, although a configuration in which the working fluid G supplied to the compression unit <NUM> is introduced in the order of the second compression unit <NUM>, the fourth compression unit <NUM>, the first compression unit <NUM>, the fifth compression unit <NUM>, the third compression unit <NUM>, and the sixth compression unit <NUM> and sequentially compressed has been described in the above embodiment, the present disclosure is not limited to this configuration. The working fluid G may be introduced in any order with respect to the first compression unit <NUM>, the second compression unit <NUM>, the third compression unit <NUM>, the fourth compression unit <NUM>, the fifth compression unit <NUM>, and the sixth compression unit <NUM>. At this time, the size of the impeller in each compression unit <NUM> (first impeller 310b to sixth impeller 360b) may be smaller in the order in which the working fluid flows.

In addition, although a configuration in which the output axis O1 on the output shaft <NUM> and the drive axis O2 on the drive gear <NUM> are on the same straight line has been described in the above embodiment, the case of a slight deviation as well as the case of being completely on the same straight line is included.

In addition, although a configuration in which the second drive side pinion main body <NUM> meshes with the part of the drive gear main body <NUM> where the drive gear upper half portion 211a and the drive gear lower half portion 211b are switched has been described in the above embodiment, the present disclosure is not limited to this configuration. The second drive side pinion main body <NUM> may mesh with the drive gear upper half portion 211a in the drive gear main body <NUM>. In addition, the second drive side pinion main body <NUM> may mesh with the drive gear lower half portion 211b in the drive gear main body <NUM>.

In addition, although a configuration in which the outer diameter of each compressor impeller 40b in the uniaxial multi-stage compressor <NUM> is smaller than the outer diameter of the sixth impeller 360b in the sixth compression unit <NUM> has been described in the above embodiment, the present disclosure is not limited to this configuration. The outer diameter of each compressor impeller 40b in the uniaxial multi-stage compressor <NUM> may be larger than the outer diameter of the sixth impeller 360b in the sixth compression unit <NUM>.

In addition, although a configuration in which the compressor rotor <NUM> of the uniaxial multi-stage compressor <NUM> has three compressor impellers 40b has been described in the above embodiment, the number is not limited to three.

In addition, the compressor casing <NUM> of the uniaxial multi-stage compressor <NUM> may be formed integrally with the gear case <NUM> of the compression unit drive mechanism <NUM>.

In addition, the present disclosure is not limited to the configuration in which the shaft joint <NUM> is a diaphragm shaft joint. The shaft joint <NUM> may be, for example, a flange-shaped shaft joint, a gear-type shaft joint, a rubber shaft joint, a metal spring shaft joint, a roller chain shaft joint, or the like.

Claim 1:
An integrally geared compressor (<NUM>) comprising:
a drive gear (<NUM>) configured to rotate by rotation of a motor (<NUM>) ;
an intermediate gear (<NUM>) meshing with the drive gear (<NUM>);
a first drive side pinion (<NUM>) meshing with the drive gear (<NUM>) at a position away from the intermediate gear (<NUM>);
a first intermediate side pinion (<NUM>) meshing with the intermediate gear (<NUM>) at a position away from the drive gear (<NUM>) ;
a second intermediate side pinion (<NUM>) meshing with the intermediate gear (<NUM>) at a position away from the drive gear (<NUM>) and the first intermediate side pinion (<NUM>);
a first compression unit (<NUM>) connected to the first drive side pinion (<NUM>) and configured to compress a working fluid (G) supplied from an outside by rotation of the first drive side pinion (<NUM>);
a second compression unit (<NUM>) connected to the first intermediate side pinion (<NUM>) and configured to compress a working fluid supplied from an outside by rotation of the first intermediate side pinion; characterized in that the integrally geared compressor further comprises
a uniaxial multi-stage compressor (<NUM>) connected to the second intermediate side pinion (<NUM>) and configured to further compress the working fluid (G) compressed by at least one of the first compression unit (<NUM>) and the second compression unit (<NUM>),
and in that the intermediate gear (<NUM>) meshes with the drive gear (<NUM>) in an upper half portion of the drive gear (<NUM>),
the second intermediate side pinion (<NUM>) meshes with the intermediate gear (<NUM>) in a lower half portion of the intermediate gear (<NUM>), and
the motor (<NUM>) and the uniaxial multi-stage compressor are placed on a foundation (G) positioned below the drive gear (<NUM>) and the intermediate gear (<NUM>).