JP2016156282A - Compressor system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor system capable of restraining an interval between an impeller and a housing from being excessively narrowed.SOLUTION: A compressor system 10 includes: a motor 3 having a rotor 31 rotating around an axis O, and a stator 32 arranged on an outer peripheral side of the rotor 31; a compressor 2 having an impeller 22 rotating with the rotor 31 and thereby compressing a working fluid, and a housing 23 covering the impeller 22 from an outer peripheral side; and a heat exchange flow passage 600 which allows the fluid flowing through an inside of the stator 32 or a gap between the stator 32 and the rotor 31 to circulate so that heat exchange can be performed between the fluid and the housing 23.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor system.

  A compressor system in which a motor and a compressor are integrated includes a compressor that compresses a gas such as air or gas, and a motor that drives the compressor. In the compressor system, a rotating shaft that extends from the casing of the compressor and a rotating shaft of the motor that similarly extends from the casing of the motor are connected, and the rotation of the motor is transmitted to the compressor. The rotating shafts of the motor and the compressor are stably rotated by being supported by a plurality of bearings.

  Such a compressor system is, for example, a subsea production system such as Non-Patent Document 1 or a floating production storage and offloading facility such as Non-Patent Document 2 (FPSO). used. When used in a submarine production system, the compressor system is installed on the bottom of the sea and sends out a production fluid mixed with crude oil, natural gas, etc. from a production well drilled to a depth of several thousand meters from the bottom of the sea. . Further, when used in a floating marine oil storage facility, the compressor system is installed in a marine facility such as a ship.

Mitsubishi Heavy Industries Technical Report Vol. 34 No. 5 P310-P313 Turbomachinery International September / October 2014 P18-P24

  By the way, in the compressor of a compressor system, the temperature of each part which comprises compressors, such as an impeller and a housing, differs in the case where it has stopped and the case where it is carrying out steady operation. Particularly, the impeller and the housing are different in the degree of temperature change when starting and stopping because the volume difference between the members is large. For this reason, depending on the operating condition of the compressor system, the temperature difference between the impeller and the housing becomes large, so that the amount of thermal expansion is greatly deviated and the clearance between the impeller and the housing varies. As a result, at the time of starting or stopping, the distance between the impeller and the housing becomes too narrow and may come into contact.

  The present invention has been made to solve the above-described demand, and provides a compressor system capable of suppressing the interval between the impeller and the housing from becoming too narrow.

In order to solve the above problems, the present invention proposes the following means.
A compressor system according to a first aspect of the present invention compresses a working fluid by rotating with a rotor having a rotor that rotates about an axis, a stator that is disposed on an outer peripheral side of the rotor, and the rotor. A compressor having an impeller and a housing that covers the impeller from the outer peripheral side; and a fluid that flows through a gap in the stator or between the stator and the rotor, and between the fluid and the housing. And a heat exchange flow path that enables heat exchange.

  According to such a configuration, the temperature of the fluid flowing in the stator or in the gap between the stator and the rotor rises by cooling the stator and the rotor. The housing can be efficiently and quickly heated by causing the fluid whose temperature has risen to exchange heat with the housing through the heat exchange channel. As a result, the housing can be quickly warmed in accordance with the temperature change of the impeller at the time of start and stop, and the deviation between the thermal elongation amount of the impeller and the thermal elongation amount of the housing can be reduced.

  In the compressor system, the fluid may be a working fluid compressed by the impeller.

  According to such a configuration, the working fluid can be further heated before being supplied to the housing by cooling the rotor and the stator with the working fluid whose temperature has been increased by being compressed by the impeller. Therefore, the housing can be effectively warmed.

  The compressor system further includes a flow rate adjusting unit that adjusts the flow rate of the fluid flowing through the heat exchange flow path when a temperature difference between the housing and the impeller satisfies a predetermined criterion. May be.

  According to such a configuration, when the temperature difference between the housing and the impeller satisfies a predetermined standard, the fluid adjustment unit adjusts the flow rate of the fluid so that the fluid is exchanged by a necessary amount. Can be distributed. Therefore, for example, when the temperature difference between the housing and the impeller becomes small and it is not necessary to heat the housing, it is possible to prevent the fluid from continuing to flow through the heat exchange flow path. Therefore, the fluid can be efficiently circulated through the heat exchange channel.

  According to the compressor system of the present invention, the housing can be heated by using the fluid whose temperature has been increased by cooling the rotor and the stator, and the interval between the impeller and the housing is prevented from becoming too narrow. can do.

It is a mimetic diagram explaining the compressor system in a first embodiment of the present invention. It is a schematic diagram explaining the compressor system in 2nd embodiment of this invention. It is a schematic diagram explaining the compressor system in 3rd embodiment of this invention. It is a schematic diagram explaining the compressor system in 4th embodiment of this invention.

<First embodiment>
Hereinafter, a first embodiment according to the present invention will be described with reference to FIG.
The compressor system 10 is used in a subsea production system (Subsea Production System), which is one of the development systems of an offshore oil and gas field, and is provided on the seafloor, or a floating production storage and offloading (FPSO). It is used in the sea and is provided on the sea. The compressor system 10 pumps, as a working fluid, a production fluid such as oil and gas collected from a production well of an oil and gas field existing at several hundred to several thousand m in the seabed.

  As shown in FIG. 1, the compressor system 10 includes a compressor 2 having a shaft 21 that extends in the axis O direction (left and right direction in FIG. 1) as a rotation axis, and a rotor 31 that is directly connected to the shaft 21. Heat which heats the housing 23 of the compressor 2 by heat-exchanging with the motor 3 which has, the bearing part 4 which supports the shaft 21, the casing 5 which accommodates the motor 3 and the compressor 2, and the fluid which distribute | circulates an inside. The exchange flow path 600 and the flow rate adjusting unit 7 that adjusts the flow rate of the fluid flowing through the heat exchange flow path 600 are provided.

  The compressor 2 is accommodated in the casing 5, and the working fluid is compressed by rotating the shaft 21 around the axis O together with the rotor 31. The compressor 2 of the present embodiment includes a shaft 21 extending in the direction of the axis O, an impeller 22 that is fixed to the outer peripheral surface of the shaft 21 and rotates together with the rotor 31, and compresses the impeller 22 from the outside. And a housing 23 for covering.

  The shaft 21 is a rotating shaft extending in the direction of the axis O, and is supported by the casing 5 so as to be rotatable around the axis O. The shaft 21 passes through the housing 23 in the direction of the axis O, and both ends extend from the housing 23. The shaft 21 extends in the direction of the axis O in the casing 5 described later.

  The impeller 22 rotates together with the shaft 21 and compresses the working fluid passing through the impeller 22 to generate a compressed fluid. A plurality of impellers 22 are fixed to the outer peripheral surface of the shaft 21 side by side in the direction of the axis O.

  The housing 23 is an exterior of the compressor 2 and accommodates the impeller 22 therein. The housing 23 is accommodated in the casing 5. The housing 23 is provided with a plurality of internal spaces 23a that repeat the contraction and expansion. The impellers 22 are accommodated in the internal spaces 23a. In the internal space 23 a, the impeller 22 is disposed at a predetermined interval with respect to the housing 23. The housing 23 has an impeller 22 disposed on the upstream side (right side in FIG. 1) on one side in the axis O direction and the impeller 22 adjacent to the downstream side (left side in FIG. 1) on the other side in the axis O direction. A flow path (not shown) through which the working fluid flows is formed.

  The motor 3 is accommodated in the casing 5 with an interval in the direction of the axis O with respect to the compressor 2. The motor 3 includes a rotor 31 fixed so as to be integrated with the shaft 21 and a stator 32 disposed on the outer peripheral side of the rotor 31.

  The rotor 31 can rotate about the axis O together with the shaft 21. The rotor 31 is directly connected to the outer peripheral side of the shaft 21, which is the outer side in the circumferential direction with respect to the axis O, so as to rotate integrally with the shaft 21 of the compressor 2 without using a gear or the like. Has been. The rotor 31 has, for example, a rotor core (not shown) through which an induced current flows when the stator 32 generates a rotating magnetic field.

  The stator 32 is provided with a gap 33 in the circumferential direction so as to cover the rotor 31 from the outer peripheral side. The stator 32 has, for example, a plurality of stator cores (not shown) arranged along the circumferential direction of the rotor 31, and a stator winding (not shown) wound around the stator core. The stator 32 rotates the rotor 31 by generating a rotating magnetic field when an electric current flows from the outside. The stator 32 is fixed in the casing 5.

  The bearing part 4 is accommodated in the casing 5, and supports the shaft 21 rotatably. The bearing portion 4 of this embodiment includes a plurality of journal bearings 41 and thrust bearings 42.

  The journal bearing 41 supports a load that acts on the shaft 21 in the radial direction with respect to the axis O. The journal bearings 41 are disposed at both ends of the shaft 21 in the axis O direction so as to sandwich the motor 3 and the compressor 2 from the axis O direction. The journal bearing 41 is disposed between the area where the compressor 2 is provided and the area where the motor 3 is provided, and is also arranged closer to the motor 3 than a seal member 51 described later.

  The thrust bearing 42 supports a load that acts on the shaft 21 in the direction of the axis O via a thrust collar 21 a formed on the shaft 21. The thrust bearing 42 is disposed between the area where the compressor 2 is provided and the area where the motor 3 is provided, and is disposed closer to the compressor 2 than a seal member 51 described later.

  The casing 5 accommodates the compressor 2 and the motor 3 therein. The casing 5 has a cylindrical shape along the axis O. The inner surface of the casing 5 protrudes toward the shaft 21 between the compressor 2 and the motor 3 in the direction of the axis O. The casing 5 is provided in a protruding portion of a seal member 51 that seals between a region where the compressor 2 is provided and a region where the motor 3 is provided.

  The heat exchange flow path 600 allows fluid to flow between the housing 23 and the fluid that has been circulated. The heat exchange flow path 600 of the present embodiment cools the rotor 31 and the stator 32 by circulating a fluid inside the stator 32. The heat exchange channel 600 circulates the fluid whose temperature has been increased by cooling the rotor 31 and the stator 32 inside the housing 23. The heat exchange flow path 600 supplies the fluid that has flowed through the housing 23 to the heat exchanger 601, cools it, and makes it flow through the stator 32 again. The heat exchange flow path 600 of this embodiment is a closed loop flow path that circulates fluid between the motor 3 and the compressor 2.

  In addition, as a fluid in this embodiment, it is preferable to use the cooling medium using gas, such as air and helium, for example. By using a gas such as air or helium, the metal material constituting the heat exchange channel 600 is prevented from being oxidized and reduced in strength compared to a gas containing a large amount of liquid such as liquid or water vapor. can do.

  The heat exchange channel 600 of the first embodiment includes a heat exchanger 601 that cools the fluid after flowing through the inside of the housing 23, and an introduction channel 602 that introduces the fluid cooled by the heat exchanger 601 into the stator 32. A stator internal flow path 603 that is connected to the introduction flow path 602 and allows the fluid to flow inside the stator 32; a first connection flow path 604 that is connected to the stator internal flow path 603 and supplies the fluid to the housing 23; A first housing flow path 605 that is connected to one connection flow path 604 and distributes fluid inside the housing 23, and is connected to the first housing flow path 605 and discharges fluid from the inside of the housing 23 and supplies it to the heat exchanger 601. And a first discharge channel 606.

  The heat exchanger 601 cools the fluid that has flowed through the stator 32 and the housing 23. The heat exchanger 601 of this embodiment is disposed outside the casing 5. The heat exchanger 601 cools the fluid to a temperature suitable for cooling the motor 3 by exchanging heat between the surrounding secondary cooling medium and the fluid.

  As the secondary cooling medium, when the compressor system 10 is used in a seabed production system and is provided on the seabed, surrounding seawater is preferably used. By using the surrounding seawater, the fluid can be cooled to a temperature at which the motor 3 can be sufficiently cooled by simply exchanging heat with low-temperature seawater on the seabed without newly preparing a secondary cooling medium for the heat exchanger 601. Can be cooled.

  Further, as the secondary cooling medium, when the compressor system 10 is used for FPSO and is provided in a marine facility such as a ship, ambient air or fresh water stored in the marine facility should be used. Is preferred. By using ambient air or fresh water, it is not necessary to newly prepare a secondary cooling medium for the heat exchanger 601, and the motor 3 can be sufficiently used while suppressing the influence of corrosion of the piping. The fluid can be cooled to a temperature that can be cooled to a low temperature.

  The introduction flow path 602 introduces fluid from the heat exchanger 601 into the stator 32 on the upstream side in the axis O direction. The introduction flow path 602 is a pipe connected from the heat exchanger 601 to the inside of the stator 32 on the upstream side of the stator 32 in the axis O direction. The introduction channel 602 is provided with a pump 601a that pumps fluid in the middle.

  The stator internal flow path 603 is arranged inside the stator 32, thereby allowing fluid to flow through the stator 32. The stator internal flow path 603 of this embodiment is connected to the introduction flow path 602 and allows fluid to flow from the upstream side in the direction of the axis O toward the downstream side. The stator internal channel 603 is a pipe extending in the direction of the axis O at a portion close to the radial rotor 31 inside the stator 32. The stator internal flow path 603 extends from a position upstream of the rotor 31 in the axis O direction to a position downstream of the rotor 31 in the axis O direction within the stator 32. The stator internal flow path 603 is connected to the introduction flow path 602 at the upstream end in the axis O direction.

  The first connection channel 604 circulates through the stator internal channel 603 and supplies the fluid whose temperature has risen from the inside of the stator 32 to the outside of the casing 5 to the inside of the housing 23. The first connection channel 604 of the present embodiment is a pipe that extends from the downstream side of the stator 32 in the axis O direction to the outside of the casing 5 and is connected to the upstream side of the housing 23 in the axis O direction. The first connection channel 604 is connected to the downstream end of the stator internal channel 603 in the axis O direction.

  The first housing channel 605 is disposed inside the housing 23, thereby allowing fluid to flow through the housing 23. The first housing flow path 605 of this embodiment is connected to the first connection flow path 604 and allows fluid to flow from the upstream side in the axis O direction toward the downstream side. The first housing flow path 605 is a pipe extending in the axis O direction on the radially outer side than the internal space 23 a in which the impeller 22 inside the housing 23 is disposed. The first housing flow path 605 is connected to the first connection flow path 604 at the upstream end in the axis O direction.

  The first discharge channel 606 discharges the fluid flowing through the first housing channel 605 from the inside of the housing 23 to the outside of the casing 5 and supplies the fluid to the heat exchanger 601. The first discharge channel 606 is a pipe connected from the inside of the housing 23 to the heat exchanger 601 on the downstream side in the axis O direction of the housing 23. The first discharge channel 606 is connected to the downstream end of the first housing channel 605 in the axis O direction.

  The flow rate adjusting unit 7 adjusts the flow rate of the fluid flowing through the heat exchange flow path 600 when the temperature difference between the housing 23 and the impeller 22 satisfies a predetermined criterion. In the flow rate adjusting unit 7 of the present embodiment, when the temperature difference between the housing 23 and the impeller 22 becomes smaller than a predetermined reference, the flow rate of the fluid flowing through the first connection channel 604 is reduced. In the flow rate adjusting unit 7, the temperature of the fluid flowing through the first discharge channel 606 is measured without directly measuring the temperatures of the housing 23 and the impeller 22, and the temperature difference between the housing 23 and the impeller 22 is confirmed.

  The flow rate adjustment unit 7 of the present embodiment includes a temperature measurement unit 71 that measures the temperature of the fluid that has flowed through the first discharge channel 606, a valve unit 72 that is provided in the middle of the first connection channel 604, and a temperature. And a control unit 73 that sends a signal to adjust the opening degree to the valve unit 72 based on the measurement result of the measurement unit 71.

  The temperature measuring unit 71 is provided in the middle of the first discharge channel 606. The temperature measuring unit 71 is a thermometer that measures the temperature of the fluid flowing through the first discharge channel 606. The temperature measurement unit 71 sends the measured temperature information of the fluid to the control unit 73 as a measurement result.

  The valve part 72 switches the flow state of the fluid flowing through the first connection channel 604. The valve part 72 of the present embodiment is an electromagnetic valve that closes so as to restrict the first connection channel 604 by receiving a signal from the control part 73.

  The control unit 73 sends a signal to close the valve unit 72 when the measurement result obtained by the temperature measurement unit 71 satisfies a predetermined criterion.

  The predetermined reference in the present embodiment is, for example, a temperature difference that can be considered that there is no possibility of contact between the housing 23 and the impeller 22. Specifically, the temperature difference that can be considered that there is no risk of contact between the housing 23 and the impeller 22 is the difference between the housing 23 and the impeller 22 in a state where the housing 23 and the impeller 22 are sufficiently warmed as in the steady operation. Temperature difference.

  The control unit 73 of the present embodiment is based on the input unit 731 to which the measurement result is input from the temperature measurement unit 71 and the result input to the input unit 731, and whether the measured measurement result satisfies a predetermined standard. It has the determination part 732 which determines whether or not, and the output part 733 which sends a signal to the valve part 72 according to the determination result in the determination part 732.

  According to the compressor system 10 as described above, when an external device such as a generator (not shown) supplies current to the stator 32, a rotating magnetic field is generated based on the supplied current, and the rotor 31 of the motor 3. Starts rotating together with the shaft 21. By rotating the shaft 21 at a high speed, in the compressor 2, the impeller 22 that rotates together with the shaft 21 compresses the working fluid flowing into the compressor 2 from the upstream side in the axis O direction and compresses from the downstream side in the axis O direction. Drain the compressed fluid.

  In the motor 3, the fluid cooled by the heat exchanger 601 is introduced into the stator 32 through the introduction flow path 602 and flows through the stator internal flow path 603. Thereby, the part near the rotor 31 of the stator 32 is cooled. Therefore, the rotor 31 and the stator 32 heated by the heat generated between the rotor 31 and the stator 32 can be cooled.

  Further, the fluid whose temperature has been increased by cooling the rotor 31 and the stator 32 is once discharged from the stator internal channel 603 to the outside of the casing 5 via the first connection channel 604 and supplied to the first housing channel 605. Is done. When the fluid whose temperature has increased flows through the first housing channel 605, heat exchange is performed between the fluid and the housing 23, and the housing 23 is warmed. That is, the housing 23 can be efficiently and quickly heated using the exhaust heat generated when the rotor 31 and the stator 32 are cooled. As a result, the housing 23 can be quickly warmed in accordance with the temperature change of the impeller 22 when the compressor system 10 is started or stopped, and the deviation between the thermal elongation amount of the impeller 22 and the thermal elongation amount of the housing 23 is reduced. can do. Thereby, it can suppress that the space | interval of an impeller and a housing becomes too narrow at the time of starting and a stop.

  In addition, the fluid that has flowed through the first housing flow path 605 is supplied to the heat exchanger 601 through the first discharge flow path 606, cooled, and supplied again from the introduction flow path 602 to the stator internal flow path 603. Thus, since the heat exchange flow path 600 is formed as a closed loop flow path, it is not necessary to supply a new fluid, so that the flow rate of the fluid flowing through the heat exchange flow path 600 can be suppressed.

  Further, by cooling the fluid with the heat exchanger 601, the fluid can be efficiently cooled to a temperature at which the rotor 31 and the stator 32 can be sufficiently cooled. That is, the fluid whose temperature has risen too much to cool the rotor 31 and the stator 32 by flowing through the stator internal flow path 603 and the first housing flow path 605 is exchanged with the secondary cooling medium by the heat exchanger 601. And the temperature of the fluid can be lowered efficiently.

  Further, by allowing the fluid sufficiently cooled by the heat exchanger 601 to flow through the stator internal flow path 603, the fluid capable of cooling the rotor 31 and the stator 32 with high accuracy in the direction of the axis O is passed through the stator 32. Can do. Therefore, when the rotor 31 rotates, the rotor 31 and the stator 32 heated by the heat generated between the rotor 31 and the stator 32 can be efficiently cooled in the direction of the axis O. Thereby, it can suppress that the area | region where temperature is high locally arises in the rotor 31 and the stator 32, and can suppress the efficiency fall of the motor 3 or can improve the lifetime.

  Further, the temperature of the fluid flowing through the first discharge channel 606 is measured by the temperature measurement unit 71, and the measurement result is sent to the input unit 731 of the control unit 73. In the control unit 73, the measurement result input from the input unit 731 to the determination unit 732 is sent. The determination unit 732 determines whether or not the temperature difference is such that the housing 23 and the impeller 22 are not likely to contact each other by determining whether or not the measured temperature satisfies a predetermined standard. When the determination unit 732 determines that the standard is satisfied, a signal is sent from the output unit 733 to the valve unit 72 so that the flow rate of the fluid flowing through the first connection channel 604 is reduced. Close.

  Therefore, as in the steady operation, the determination unit 732 can check whether the housing 23 and the impeller 22 are sufficiently warmed and the temperature difference is small. That is, it can be confirmed whether or not the housing 23 is sufficiently warmed and the deviation between the thermal elongation amount of the impeller 22 and the thermal elongation amount of the housing 23 is small.

  When the determination unit 732 determines that the standard is satisfied, the fluid can be circulated through the heat exchange channel 600 by a necessary amount by closing the valve unit 72. Therefore, for example, when the temperature difference between the housing 23 and the impeller 22 becomes sufficiently small and the housing 23 does not need to be heated, it is possible to prevent the fluid from continuing to flow through the heat exchange channel 600. it can. Therefore, the fluid can be efficiently circulated through the heat exchange channel 600.

<Second embodiment>
Next, the compressor system 12 of the second embodiment will be described with reference to FIG.
In the second embodiment, the same components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. The compressor system 12 of the second embodiment is different from the first embodiment in the configuration of the heat exchange flow path 620.

  That is, in the heat exchange flow path 620 of the compressor system 12 of the second embodiment, a compressed fluid that is a working fluid compressed by the impeller 22 is used as the fluid, and the gap 33 (hereinafter referred to as the gap between the stator 32 and the rotor 31). , Simply referred to as gap 33). Specifically, as shown in FIG. 2, the heat exchange flow path 620 of the second embodiment is a middle stage bleed air introduction flow path 622 that bleeds compressed fluid from the middle stage of the compressor 2 and introduces it into the gap 33 of the motor 3. A second connection channel 624 that supplies the compressed fluid that has passed through the gap 33 to the housing 23; a second housing channel 625 that is connected to the second connection channel 624 and distributes the compressed fluid inside the housing 23; A second discharge flow path 626 that is connected to the second housing flow path 625 and discharges the compressed fluid from the housing 23 to the outside of the casing 5.

  The gap 33 in this embodiment is a space formed between the stator 32 and the rotor 31, and an outer peripheral surface facing the radially outer side of the rotor 31 and an inner peripheral surface facing the radially inner side of the stator 32. It is a space sandwiched between surfaces facing each other in the radial direction.

  The middle stage bleed introduction passage 622 bleeds the compressed fluid compressed by the impeller 22 from the middle stage of the compressor 2 and supplies it to the upstream side of the gap 33 in the direction of the axis O. The middle stage bleed introduction passage 622 of the present embodiment is a pipe connected from the middle stage of the compressor 2 to the upstream side in the direction of the axis O of the motor 3 inside the casing 5. The middle stage bleed introduction flow path 622 is connected to the upstream side in the axis O direction from the rotor 31 and the stator 32 inside the casing 5. That is, the middle extraction air introduction channel 622 supplies the compressed fluid from the upstream side in the direction of the axis O to the gap 33. A valve portion 72 is provided in a portion located outside the casing 5 in the middle extraction air introduction flow path 622.

  The second connection channel 624 bleeds the compressed fluid that has passed through the gap 33 from the upstream side toward the downstream side in the direction of the axis O, and supplies the compressed fluid to the second housing channel 625. The second connection channel 624 is a pipe connected from the housing 23 to the downstream side in the axis O direction of the motor 3 inside the casing 5. The second connection channel 624 is connected to the downstream side in the axis O direction from the rotor 31 and the stator 32 inside the casing 5. That is, the second connection channel 624 bleeds the compressed fluid from the downstream side of the gap 33 in the axis O direction.

  The second housing channel 625 is disposed inside the housing 23, thereby allowing fluid to flow through the housing 23. The second housing flow path 625 is connected to the second connection flow path 624 and allows the compressed fluid to flow from the upstream side toward the downstream side in the direction of the axis O. The second housing flow path 625 is a pipe extending in the axis O direction on the outer side in the radial direction than the internal space 23 a in which the impeller 22 inside the housing 23 is disposed. The second housing channel 625 is connected to the second connecting channel 624 at the upstream end in the axis O direction.

  The second discharge channel 626 is connected to the second housing channel 625 and discharges the compressed fluid flowing through the housing 23 from the downstream side in the direction of the axis O to the outside of the casing 5. The second discharge channel 626 is a pipe connected from the inside of the housing 23 to the outside of the casing 5 on the downstream side in the axis O direction of the housing 23. The second discharge channel 626 is connected to the downstream end of the second housing channel 625 in the axis O direction. The second discharge channel 626 is provided with a temperature measurement unit 71 at a portion located outside the casing 5.

  According to the compressor system 12 as described above, the compressed fluid, which is the working fluid compressed by the impeller 22, is extracted from the middle stage of the compressor 2 through the middle stage bleed air introduction flow path 622, and the gap 33 is moved in the direction of the axis O. Supplied upstream. Therefore, the compressed fluid flows through the gap 33 from the upstream side in the axis O direction toward the downstream side, and the periphery of the gap 33 is cooled over the axis O direction. Thereby, the rotor 31 and the stator 32 heated by the heat generated by the rotation of the rotor 31 can be cooled.

  Further, the compressed fluid that has flowed through the gap 33 is extracted from the downstream side in the direction of the axis O of the gap 33 via the second connection flow path 624 and supplied to the second housing flow path 625, whereby the rotor 31 and the stator 32. By cooling the housing 23, the housing 23 can be warmed by the compressed fluid whose temperature has increased. That is, the housing 23 can be efficiently and quickly heated using the exhaust heat generated when the rotor 31 and the stator 32 are cooled. As a result, the housing 23 can be quickly warmed in accordance with the temperature change of the impeller 22 when the compressor system 10 is started or stopped, and the deviation between the thermal elongation amount of the impeller 22 and the thermal elongation amount of the housing 23 is reduced. can do. Thereby, it can suppress that the space | interval of an impeller and a housing becomes too narrow at the time of starting and a stop.

  In addition, by extracting a part of the working fluid compressed by the compressor 2 and using it as a fluid flowing through the heat exchange channel 620, the inside of the heat exchange channel 620 can be used without using a device such as a pump 601a. Can be distributed. Furthermore, by cooling the rotor 31 and the stator 32 with the working fluid whose temperature has been increased by being compressed by the impeller 22, the working fluid can be further warmed and then supplied to the housing 23. Therefore, the housing 23 can be effectively warmed with a simple configuration.

<Third embodiment>
Next, the compressor system 13 of 3rd embodiment is demonstrated with reference to FIG.
In 3rd embodiment, the same code | symbol is attached | subjected to the component similar to 1st embodiment and 2nd embodiment, and detailed description is abbreviate | omitted. The compressor system 13 of the third embodiment is different from the first embodiment and the second embodiment regarding the configuration of the heat exchange flow path 630.

  That is, in the heat exchange flow path 630 of the compressor system 13 of the third embodiment, unlike the second embodiment, the fluid is not supplied to the motor 3 side while using the compressed fluid as the fluid. Specifically, as shown in FIG. 3, the heat exchange flow path 630 of the third embodiment bleeds the compressed fluid compressed from the middle stage of the compressor 2 and supplies it to the second housing flow path 625. A middle bleed introduction passage 632 is provided. Moreover, the heat exchange flow path 630 of 3rd embodiment has the 2nd housing flow path 625 and the 2nd discharge flow path 626 similarly to 2nd embodiment.

  The second middle stage bleed air introduction flow path 632 bleeds the compressed fluid compressed by the impeller 22 from the middle stage of the compressor 2 and supplies it to the second housing flow path 625. The second middle stage bleed introduction passage 632 of the present embodiment is a pipe connected from the middle stage of the compressor 2 to the upstream side of the second housing passage 625 in the axis O direction. A valve portion 72 is provided in a portion located outside the casing 5 in the second middle stage extraction air introduction channel 632.

  According to the compressor system 13 as described above, a device that pumps out a fluid such as the pump 601a by extracting a part of the working fluid compressed by the compressor 2 and using it as a fluid flowing through the heat exchange channel 620. It can be made to circulate in the heat exchange flow path 620 without using. Furthermore, the working fluid whose temperature has been increased by being compressed by the impeller 22 can be supplied to the housing 23. Therefore, the housing 23 can be effectively warmed with a simple configuration.

<Fourth embodiment>
Next, the compressor system 14 of the fourth embodiment will be described with reference to FIG.
In the fourth embodiment, the same components as those in the first embodiment to the third embodiment are denoted by the same reference numerals, and detailed description thereof is omitted. The compressor system 14 of the fourth embodiment is different from the first embodiment in the configuration of the heat exchange flow path 640 from the first embodiment.

  When a compressed fluid is used as the fluid flowing through the heat exchange channel 640, the compressed fluid is not limited to the configuration extracted from the middle stage of the compressor 2 as in the second embodiment or the third embodiment. It is only necessary that the working fluid compressed by the impeller 22 can be extracted. Therefore, for example, the compressed fluid may be extracted from the last stage of the compressor 2.

  That is, the compressed fluid is extracted from the last stage of the compressor 2 in the heat exchange flow path 640 of the compressor system 14 of the fourth embodiment. Specifically, as shown in FIG. 4, the heat exchange flow path 640 of the fourth embodiment is a subsequent stage for extracting the compressed fluid compressed from the last stage of the compressor 2 and supplying it to the second housing flow path 625. A bleed air introduction channel 642 is provided.

  The rear stage bleed air introduction flow path 642 bleeds the compressed fluid that has been most compressed by the impeller 22 from the last stage of the compressor 2 and supplies it to the second housing flow path 625. The rear stage bleed introduction flow path 642 of the present embodiment is a pipe connected from the last stage of the compressor 2 to the upstream side of the second housing flow path 625 in the axis O direction. The rear stage bleed air introduction flow path 642 is connected to a discharge port (not shown) that discharges the compressed fluid provided in the last stage of the compressor 2 to the outside of the housing 23. A valve portion 72 is provided in a portion located outside the casing 5 in the rear stage bleed air introduction flow path 642.

  According to the compressor system 14 as described above, the housing 23 can be warmed by the compressed fluid having a temperature higher than that of the third embodiment.

  Although the embodiments of the present invention have been described in detail with reference to the drawings, the configurations and combinations of the embodiments in the embodiments are examples, and the addition and omission of configurations are within the scope not departing from the gist of the present invention. , Substitutions, and other changes are possible. Further, the present invention is not limited by the embodiments, and is limited only by the scope of the claims.

  Note that the heat exchanger 601 is not limited to being disposed outside the casing 5 as in the first embodiment, and it is sufficient that the fluid can be cooled. For example, the heat exchanger 601 may be disposed inside the casing 5. Moreover, the heat exchanger 601 is not limited to one as in the present embodiment, and a plurality of heat exchangers 601 may be provided.

  Further, the temperature difference between the housing 23 and the impeller is not limited to measuring and confirming the temperature of the fluid flowing through the first housing flow path 605 and the second housing flow path 625 as in the present embodiment. Alternatively, the temperature of the housing 23 and the impeller 22 may be directly measured and confirmed, and the relationship between the temperature difference between the housing 23 and the impeller 22 and the rotational speed of the shaft 21 is determined in advance, and depending on the rotational speed of the shaft 21 You may check.

  Further, the first housing flow path 605 and the second housing flow path 625 for supplying fluid to the housing 23 are not limited to the structure extending in the direction of the axis O inside the housing 23 as in the present embodiment. Any structure that allows heat exchange between the fluid to be circulated and the housing 23 may be used. For example, the first housing channel 605 and the second housing channel 625 may be provided between the housing 23 and the casing 5. In this case, the first housing flow path 605 and the second housing flow path 625 may be spirally wound around the outer periphery of the housing 23, and may be arranged extending linearly along the axis O direction. .

DESCRIPTION OF SYMBOLS 10, 12, 13, 14 ... Compressor system O ... Axis 2 ... Compressor 21 ... Shaft 21a ... Thrust collar 22 ... Impeller 23 ... Housing 23a ... Internal space 3 ... Motor 31 ... Rotor 32 ... Stator 33 ... Gap 4 ... Bearing Part 41 ... Journal bearing 42 ... Thrust bearing 5 ... Casing 51 ... Seal member 600, 620, 630, 640 ... Heat exchange flow path 601 ... Heat exchanger 601a ... Pump 602 ... Introduction flow path 603 ... Stator internal flow path 604 ... First One connection flow path 605 ... first housing flow path 606 ... first discharge flow path 7 ... flow rate adjustment section 71 ... temperature measurement section 72 ... valve section 73 ... control section 731 ... input section 732 ... determination section 733 ... output section 622 ... Middle stage bleed introduction flow path 624 ... second connection flow path 625 ... second housing flow path 626 ... second exhaust Outlet flow path 632... Second middle extraction air introduction flow path 642...

Claims (3)

A motor having a rotor that rotates about an axis, and a stator that is disposed on an outer peripheral side of the rotor;
A compressor having an impeller that compresses the working fluid by rotating together with the rotor, and a housing that covers the impeller from an outer peripheral side;
A heat exchange flow path that allows a fluid that has flowed through the gap between the stator or the rotor and the stator to exchange heat between the fluid and the housing;
A compressor system comprising:   The compressor system according to claim 1, wherein the fluid is a working fluid compressed by the impeller.   3. The flow rate adjusting unit according to claim 1, further comprising: a flow rate adjusting unit configured to adjust a flow rate of the fluid flowing through the heat exchange flow path when a temperature difference between the housing and the impeller satisfies a predetermined reference. Compressor system.

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