Rotating Machinery

Abstract

A rotating machine capable of preventing the influence of heat from high-temperature gas or low-temperature gas on a pinion gear is provided. [Solution] The turbo compressor includes a working part that compresses gas, and a transmission mechanism that transmits power to the working part. The transmission mechanism includes a bull gear and a pinion gear 15. The working part includes an impeller 10, a casing cover 12, and an intermediate member 19. The pinion gear 15 is formed using chrome molybdenum steel or nickel chrome molybdenum steel. The casing cover 12 is arranged so that a gap G is formed between the casing cover 12 and a back surface 10a of the impeller. The intermediate member 19 is inserted into a hole 12a of the casing cover 12, and is interposed between an accommodation space 13a in a gear case 13 in which the pinion gear 12 is accommodated, and the gap G. The intermediate member 19 is formed of a metal material that is more heat resistant than the material from which the pinion gear 15 is formed.

Description

[Technical field]

[0001] The present invention relates to a centrifugal rotating machine. [Background technology]

[0002] Conventionally, as a centrifugal rotary machine, a geared type rotary machine in which a gear is arranged in a power transmission path is known. Patent Document 1 discloses a turbo compressor as an example of a centrifugal rotary machine. In the turbo compressor of Patent Document 1, a first impeller and a second impeller are fixed to a gear shaft portion of a pinion gear. The pinion gear is integrally formed with a rod-shaped gear shaft portion and a gear body portion having teeth.

[0003] The pinion gear disclosed in Patent Document 2 is formed, for example, using chrome-molybdenum steel having high rigidity. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 4876867 [Patent Document 2] JP 2011-196327 A Summary of the Invention [Problem to be solved by the invention]

[0005] However, pinion gears made of chrome molybdenum steel or nickel chrome molybdenum steel are not suitable for use with hot or cold gases. Due to the thermal effects of This may result in a decrease in durability. Therefore, when using high-temperature or low-temperature gas in a rotating machine, Due to the thermal effects of these gases Pinion Gear Suppress deterioration of durability It is necessary.

[0006] The present invention has been made in consideration of the above problems. 、 Thermal effects of hot or cold gas Prevents deterioration of pinion gear durability due to The purpose is to [Means for solving the problem]

[0007] A rotary machine according to one aspect of the present invention includes an actuating unit and a transmission mechanism. Operation The actuator compresses or expands the gas. The transmission mechanism transmits power to the actuator.

[0008] The transmission mechanism includes a bull gear and a pinion gear. The pinion gear is made of chrome-molybdenum steel or nickel-chrome-molybdenum steel and meshes with the bull gear.

[0009] The actuation unit includes an impeller, a casing cover, and an intermediate member. The casing cover is disposed so as to form a gap between the casing cover and a rear surface of the impeller. The intermediate member is inserted into a hole in the casing cover and is interposed between an accommodation space in which the pinion gear is accommodated and the gap.

[0010] In the rotating machine according to this aspect, the intermediate member is formed of a metal material that has higher heat resistance or cold resistance than chromium-molybdenum steel or nickel-chromium-molybdenum steel. In addition, in the rotary machine according to this aspect, the intermediate member is interposed between the pinion gear and the impeller so as to be able to transmit rotation of the pinion gear to the impeller, and is coupled to both the pinion gear and the impeller. Further, according to this embodiment The rotary machine further includes a seal portion disposed between the intermediate member and an inner circumferential surface surrounding the hole portion of the casing cover.

[0011] In the rotary machine according to the above aspect, by interposing the intermediate member made of the above-mentioned highly heat-resistant or highly cold-resistant metal material between the accommodation space and the gap, the pinion gear accommodated in the accommodation space is directly exposed to the high-temperature gas or the low-temperature gas present in the gap. Be Therefore, in the rotating machine, 、 Thermal effects of hot or cold gas This can prevent the deterioration of the pinion gear's durability due to can.

[0013] Also, In the rotary machine according to the above aspect, the intermediate member can have a power transmission function between the pinion gear and the impeller. Furthermore, in the rotary machine, a seal portion is provided between the intermediate member and the inner circumferential surface, which is further advantageous in suppressing leakage of high-temperature gas or low-temperature gas from the gap into the accommodation space.

[0014] In the rotating machine according to the above aspect, the intermediate member may include a first intermediate toothing portion and a second intermediate toothing portion. The first intermediate toothing portion may mesh with impeller teeth provided on the impeller at one end surface. The second intermediate toothing portion may mesh with gear teeth provided on the pinion gear at the other end surface. In this case, the intermediate member may be coupled to both the pinion gear and the impeller by meshing between the first intermediate toothing portion and the impeller teeth portion and meshing between the second intermediate toothing portion and the gear teeth portion.

[0015] In the rotary machine according to the above aspect, the intermediate member is coupled to the impeller and the pinion gear by meshing between the impeller teeth portion and the first intermediate teeth portion and between the gear teeth portion and the second intermediate teeth portion, so that the coupling between the intermediate member and the impeller and the pinion gear can be easily released, for example, during maintenance, etc. Therefore, in the rotary machine according to the above aspect, high maintainability can be ensured compared to a case in which the intermediate member is coupled to the impeller and the pinion gear by shrink fitting or the like.

[0016] In the rotating machine according to the above aspect, the intermediate member may have a sleeve shape, and the impeller may have an impeller hole formed so that a rotation shaft of the impeller passes through. The rotating machine may further include a tension bolt inserted into the intermediate member hole and the impeller hole of the intermediate member. In this case, a male thread portion formed on one end of the tension bolt may be fastened to a nut in a state where the male thread portion protrudes on the opposite side to the back surface of the impeller, and another male thread portion formed on the other end may be fastened to a female thread portion formed on the pinion gear. The intermediate member may be clamped between the impeller and the pinion gear by fastening both male thread portions of the tension bolt to the nut and the female thread portion of the pinion gear.

[0017] In the rotary machine according to the above aspect, the intermediate member is clamped between the impeller and the pinion gear by fastening both male and female threads of the tension bolt to the nut and the female thread. By using the intermediate member, a longer tension bolt can be used. This ensures the amount of elongation of the tension bolt, and prevents the nut from loosening. of can be suppressed more reliably.

[0018] In the rotating machine according to the above aspect, the impeller may have an impeller hole formed so that a rotation shaft of the impeller passes through. The rotating machine may further include a tension bolt inserted into the impeller hole. In this case, a male thread portion formed on one end of the tension bolt may be fastened to a nut in a state where the male thread portion protrudes on the opposite side to the back surface of the impeller, and another male thread portion formed on the other end of the tension bolt may be fastened to a female thread portion formed on the intermediate member.

[0019] In the rotary machine according to the above aspect, since the intermediate member has a non-sleeve shape that does not have a through hole therein, high temperature gas or low temperature gas is prevented from entering the pinion gear side. restraint can.

[0020] In the rotary machine according to the above aspect, The pinion gear may have a gear body portion that meshes with the bull gear, and a gear shaft portion that is formed integrally with the gear body portion. The intermediate member may have a sleeve shape and be fitted onto the gear shaft portion. An end portion of the intermediate member on the impeller side and a back surface of the impeller may each be provided with teeth that mesh with each other. In this case, the pinion gear and the impeller may be spaced apart from each other in a direction in which a rotation shaft of the impeller extends, and the intermediate member may be fitted onto the gear shaft portion, and the teeth of the intermediate member may mesh with the teeth of the impeller, thereby connecting the pinion gear and the impeller to be capable of transmitting power therebetween.

[0022] The rotary machine according to the above aspect may further include a vent portion that discharges gas leaked between the intermediate member and an inner circumferential surface of the casing cover that surrounds the hole to the outside.

[0023] In the rotary machine according to the above aspect, since the rotary machine includes the vent portion, the high-temperature gas or the low-temperature gas leaking from the gap between the intermediate member and the inner circumferential surface can be discharged to the outside via the vent portion. Therefore, in the rotary machine, the high-temperature gas or the low-temperature gas leaking from the gap can be discharged to the accommodation space in which the pinion gear is accommodated. Leak more effectively restraint It is possible.

[0024] In the rotary machine according to the above aspect, the working section may be a compression section that compresses gas, and the rotary machine may be used as a centrifugal compressor.

[0025] The rotary machine according to the above aspect is used as a centrifugal compressor, and gas heated by compression is present in the gap. However, by interposing the intermediate member between the accommodation space and the gap, the pinion gear is not directly exposed to high-temperature gas or low-temperature gas. Be This suppresses the Effect of the Invention

[0026] In the rotary machine according to each of the above aspects, 、 Thermal effects of hot or cold gas Prevents deterioration of pinion gear durability due to It is possible. [Brief description of the drawings]

[0027] [Figure 1] 1 is a cross-sectional view showing a partial configuration of a turbo compressor according to a first embodiment of the present invention. [Diagram 2] FIG. 2 is a cross-sectional view showing an intermediate member and its surrounding structure in the turbo compressor. [Diagram 3] FIG. 6 is a cross-sectional view showing a coupling structure between an intermediate member and an impeller in a turbo compressor according to a second embodiment of the present invention. [Figure 4] FIG. 4 is a cross-sectional view showing a coupling structure between an intermediate member and a pinion gear in the turbo compressor. [Diagram 5] FIG. 4 is a cross-sectional view showing a partial configuration of a turbo compressor according to a third embodiment of the present invention. [Figure 6] FIG. 11 is a cross-sectional view showing a partial configuration of a turbo compressor according to a fourth embodiment of the present invention. [Figure 7] FIG. 11 is a cross-sectional view showing a partial configuration of a turbo compressor according to a fifth embodiment of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0028] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Note that the embodiment described below is an example of the present invention, and the present invention is not limited to the embodiment described below except for the essential configuration.

[0029] [First embodiment] 1. Structure of turbo compressor 1 The structure of a turbo compressor 1 according to a first embodiment of the present invention will be described with reference to Fig. 1. The turbo compressor (centrifugal compressor) 1 according to this embodiment is an example of a rotating machine.

[0030] 1, the turbo compressor 1 includes a working unit 1a that compresses gas and a transmission mechanism 1b that transmits power to the working unit 1a. The working unit 1a includes an impeller 10, a casing 11, a casing cover 12, and an intermediate member 19. The transmission mechanism 1b includes a gear case 13, a bull gear 16, and a pinion gear 15.

[0031] The gear case 13 of the transmission mechanism 1b is a case member having an accommodation space 13a that accommodates the bull gear 16 and the pinion gear 15. A casing cover 12 of the operating part 1a is fastened to the gear case 13 by fastening members (not shown).

[0032] The gear case 13 has a through hole 13b that communicates the accommodation space 13a with the outside. The casing cover 12 has a hole portion (through hole) 12a that is provided so that the center line of the hole coincides with the through hole 13b of the gear case 13 and penetrates in the plate thickness direction. The gear case 13 and the casing cover 12 are fastened together so that the through hole 13b of the gear case 13 communicates with the hole portion 12a of the casing cover 12.

[0033] The casing 11 is attached to the casing cover 12 on a side opposite to the side attached to the gear case 13. The casing 11 is also attached to the casing cover 12 using fastening members (not shown). The impeller 10 is housed in a space (impeller housing space) 1c defined by the casing cover 12 and the casing 11.

[0034] As shown in the enlarged portion of FIG. 1, the casing cover 12 is disposed so as to form a gap G with respect to the rear surface (impeller rear surface) 10a of the impeller 10 housed in the space 1c.

[0035] In the turbo compressor 1, kinetic energy is imparted to the gas by the rotation of the impeller 10 in the space 1c defined by the casing cover 12 and the casing 11. Then, the gas to which the kinetic energy has been imparted is decelerated and pressurized by a diffuser vane (not shown) that is arranged between the casing cover 12 and the casing 11 (a portion radially outward of the impeller 10 in the space 1c).

[0036] The bull gear 16 housed in the housing space 13a of the gear case 13 is connected to a motor or a turbine (not shown) The bull gear 16 receives a rotational driving force from the motor or the turbine and rotates.

[0037] The pinion gear 15 has a gear body 15a having teeth that mesh with the bull gear 16, and a rod-shaped gear shaft 15b formed integrally with the gear body 15a. In this embodiment, the pinion gear 15 is formed using chrome molybdenum steel or nickel chrome molybdenum steel having high rigidity.

[0038] A gear body portion 15 a of the pinion gear 15 is accommodated in the accommodation space 13 a of the gear case 13 . The gear shaft portion 15b of the pinion gear 15 is disposed so as to pass through the through hole 13b and extend from the accommodation space 13a of the gear case 13 toward the casing cover 12. The gear shaft portion 15b is rotatably supported by a bearing 14 attached to the inner periphery of the gear case 13 that forms the through hole 13b. The impeller 10 receives the rotational force of the pinion gear 15 and rotates.

[0039] The intermediate member 19 is cylindrical and is inserted into a hole (through hole) 12a formed in the casing cover 12. Inside To That is, the intermediate member 19 is disposed in the hole 12a of the casing cover 12. As a result, the intermediate member 19 is positioned between a space on one side (the gear case 13 side) of the casing cover 12 and a space on the other side (the casing 11 side) of the casing cover 12. A gear shaft portion 15b of the pinion gear 15 is accommodated in a space on the gear case 13 side with respect to the casing cover 12.

[0040] Although detailed illustration is omitted in Fig. 1 etc., the turbo compressor 1 according to this embodiment is a multi-stage compressor having a plurality of working sections 1a, and is configured so that the temperature of the gas increases toward the rear stage. In this embodiment, the working section 1a shown in Fig. 1 is the working section 1a on the rear stage side.

[0041] 2. Intermediate member 19 and its surrounding structure The intermediate member 19 and its surrounding structure in the turbo compressor 1 will be described with reference to Fig. 2. Note that in Fig. 2, the gear case 13 is not shown.

[0042] 2, the casing cover 12 is disposed such that a gap G is formed between the surface 12c facing the space 1c and the back surface (impeller back surface 10a) of the impeller 10. The hole 12a of the casing cover 12 is provided so as to communicate with both the accommodation space 13a of the gear case 13 and the gap G. The intermediate member 19 is inserted into the hole 12a and disposed so as to be interposed between the gap G and the accommodation space 13a. The pinion gear 15 is accommodated on the accommodation space 13 a side of the gear case 13 relative to the casing cover 12 . As a result, the pinion gear 15 accommodated in the accommodation space 13a is exposed to the heat of the high-temperature gas or the low-temperature gas present in the gap G. direct exposure This will prevent the content from being used.

[0043] In this embodiment, the intermediate member 19 is disposed as a member in a power transmission path between the impeller 10 and the pinion gear 15. Specifically, the intermediate member 19 has a cylindrical shape. The intermediate member 19 does not have a through hole inside in the axial direction. One end face (impeller side end face) 19a of the intermediate member 19 is connected to the impeller back face 10a of the impeller 10 so that the axis coincides with the rotation center of the impeller 10.

[0044] Moreover, the intermediate member 19 has the other end face (gear shaft side end face) 19b joined to an end face (intermediate member side end face) 15c of the gear shaft portion 15b of the pinion gear 15 such that the axis of the other end face (gear shaft side end face) 19b coincides with the axis of the gear shaft portion 15b. Note that various joining means such as a coupling structure based on meshing of gears, shrink fitting, or a key may be used to join the intermediate member 19 to the impeller 10 and to join the intermediate member 19 to the gear shaft portion 15b.

[0045] The intermediate member 19 and the impeller 10 are fixed together using a tension bolt 17 and a nut 18. Specifically, the tension bolt 17 is disposed so as to pass through an impeller hole 10b formed so as to penetrate the rotation shaft of the impeller 10. One end and the other end of the tension bolt 17 are each formed with a male thread (one end male thread 17a, the other end male thread 17b).

[0046] The intermediate member 19 has a female thread portion 19c formed on the rotation axis from the impeller side end face 19a inward. The other end male thread portion 17b of the tension bolt 17 inserted into the impeller hole portion 10b from the opposite side to the intermediate member 19 is screwed into the female thread portion 19c of the intermediate member 19. At this time, the one end male thread portion 17a of the tension bolt 17 protrudes from the impeller hole portion 10b to the opposite side to the intermediate member 19. The intermediate member 19 is joined to the impeller 10 by screwing the nut 18 onto the one end male thread portion 17a of the tension bolt 17 protruding as described above.

[0047] In this way, by connecting the intermediate member 19 and the impeller 10 using the tension bolt 17 and the nut 18, loosening is less likely to occur between the intermediate member 19 and the impeller 10, even when power is transmitted from the pinion gear 15 to the impeller 10 via the intermediate member 19.

[0048] 2, the casing cover 12 has a vent portion 12b which is a gas passage connecting the hole portion 12a with the outside of the casing cover 12. The vent portion 12b exhausts gas leaked into the hole portion 12a (the gap between the outer circumferential surface of the intermediate member 19 and the inner circumferential surface surrounding the hole portion 12a) to the outside of the casing cover 12. The casing cover 12 may be provided with a scavenging portion which is a gas passage for supplying a seal gas into the hole portion 12a (the gap between the outer circumferential surface of the intermediate member 19 and the inner circumferential surface surrounding the hole portion 12a).

[0049] A cylindrical seal portion 20 having a labyrinth structure is disposed between the outer peripheral surface of the intermediate member 19 and the inner peripheral surface surrounding the hole portion 12a of the casing cover 12. The seal portion 20 prevents gas from leaking from the gap G between the surface 12c of the casing cover 12 and the impeller back surface 10a into the accommodation space 13a in which the pinion gear 15 and the like are accommodated. This prevents the pinion gear 15 accommodated in the accommodation space 13a from leaking from the gap G between the surface 12c of the casing cover 12 and the impeller back surface 10a. but Hot or cold gas Reduces direct exposure to heat It is even more advantageous to

[0050] 3. Materials of construction of the impeller 10, the pinion gear 15, and the intermediate member 19 In the turbo compressor 1 according to this embodiment, the pinion gear 15 is made of chrome molybdenum steel or nickel chrome molybdenum steel. In contrast, when high-temperature gas is processed, the intermediate member 19 is made of a metal material that is more heat resistant than the material (chrome molybdenum steel or nickel chrome molybdenum steel) that the pinion gear 15 is made of.

[0051] Specifically, the intermediate member 19 is formed using a metal material that has a higher heat resistance than the tempering temperature of the material forming the pinion gear 15. In this embodiment, the intermediate member 19 is formed using austenitic stainless steel, precipitation hardened stainless steel, or a titanium alloy.

[0052] On the other hand, when low-temperature gas, specifically gas at or below -100°C, is processed, the intermediate member 19 is formed of a metal material having higher cold resistance than the material (chrome molybdenum steel or nickel chrome molybdenum steel) from which the pinion gear 15 is made. In this embodiment, the intermediate member 19 is formed using austenitic stainless steel, aluminum alloy, nickel chrome alloy, or titanium alloy.

[0053] The impeller 10, like the intermediate member 19, is made of a metal material that has higher heat resistance than the material from which the pinion gear 15 is made.

[0054] 4.Effects In the turbo compressor 1 according to this embodiment, an intermediate member 19 made of a metal material having a higher heat resistance than the material of the pinion gear 15 is interposed between the gap G and the accommodation space 13a, so that the pinion gear 15 accommodated in the accommodation space 13a is protected from the heat of the high-temperature gas or low-temperature gas present in the gap G. direct exposure Therefore, in the turbo compressor 1, 、 Thermal effects of hot or cold gas This can suppress the deterioration of the durability of the pinion gear 15 due to the can.

[0055] In the turbo compressor 1 according to the present embodiment, an intermediate member 19 is interposed as a member in the power transmission path between the pinion gear 15 and the impeller 10, and the presence of the intermediate member 19 reduces the gap G. From Heat from hot or cold gas This prevents the pinion gear 15 from being directly exposed to the It is possible.

[0056] Furthermore, in the turbo compressor 1 according to this embodiment, the intermediate member 19 does not have a through hole therein, so high temperature gas or low temperature gas can be prevented from passing through the interior of the intermediate member 19 and entering the pinion gear side.

[0057] In addition, in the turbo compressor 1 according to this embodiment, a seal portion 20 is provided between the outer peripheral surface of the intermediate member 19 and the inner peripheral surface surrounding the hole portion 12a in the casing cover 12, so that leakage of high-temperature gas or low-temperature gas from the gap G between the surface 12c of the casing cover 12 and the impeller back surface 10a into the accommodation space 13a of the gear case 13 is prevented. restraint It is even more advantageous to

[0058] Furthermore, in the turbo compressor 1 according to this embodiment, the casing cover 12 is provided with the vent portion 12b, so even if high-temperature gas or low-temperature gas leaks from the gap G between the casing cover 12 and the impeller back surface 10a between the outer circumferential surface of the intermediate member 19 and the inner circumferential surface surrounding the hole portion 12a in the casing cover 12, the high-temperature gas or low-temperature gas can be discharged to the outside via the vent portion 12b. Therefore, in the turbo compressor 1, even if high-temperature gas or low-temperature gas leaks from the gap G, the high-temperature gas or low-temperature gas can be discharged to the outside via the vent portion 12b. Leaking of restraint The pinion gear 15 accommodated in the accommodation space 13a is heated by the high-temperature gas or the low-temperature gas. The durability of the product decreases due to the effects of heat. It is advantageous in suppressing the

[0059] Furthermore, in this embodiment, the above structure is adopted for the turbo compressor 1, which is a centrifugal compressor. As a result, even if high-temperature gas or low-temperature gas leaks from the gap G, the intermediate member 19 is interposed between the gap G and the accommodation space 13a, thereby preventing the pinion gear 15 from being directly exposed to the high-temperature gas or low-temperature gas.

[0060] As described above, in the turbo compressor 1 of this embodiment, 、 Thermal effects of hot or cold gas Suppresses deterioration of the durability of the pinion gear 15 due to It is possible.

[0061] [Second embodiment] The configuration of a turbo compressor 1 according to a second embodiment of the present invention will be described with reference to Figures 3 and 4. Note that the turbo compressor 1 according to this embodiment has the same configuration as the turbo compressor 1 according to the first embodiment described above, except for the configuration described below.

[0062] 3, impeller teeth 10c are formed around the openings of impeller holes 10b on impeller back surface 10a of impeller 10. Impeller teeth 10c are portions having gear-shaped projections and recesses.

[0063] A first intermediate tooth portion 19d is formed around the opening of the female thread portion 19c on the impeller side end surface 19a of the intermediate member 19. The first intermediate tooth portion 19d is a portion having gear-shaped projections and recesses formed to mesh with the impeller teeth portion 10c.

[0064] 4, a gear tooth portion 15d is formed around the rotation axis on an end face (intermediate member side end face) 15c on the intermediate member 19 side of the gear shaft portion 15b of the pinion gear 15. The gear tooth portion 15d is a portion having gear-shaped projections and recesses.

[0065] A second intermediate toothed portion 19e is formed around the rotation shaft on a gear shaft side end face 19b opposite to the impeller side end face 19a of the intermediate member 19. The second intermediate toothed portion 10e is a member having gear-shaped projections and recesses formed to mesh with the gear tooth portion 15d.

[0066] The turbo compressor 1 according to this embodiment has the same structure as the turbo compressor 1 according to the first embodiment described above, except for the connection structure between the intermediate member 19 and the impeller 10 and the gear shaft portion 15b, and can therefore obtain the same effects as the turbo compressor 1 according to the first embodiment described above.

[0067] Furthermore, in the turbo compressor 1 according to this embodiment, the intermediate member 19 is coupled to the impeller 10 and the pinion gear 15 by meshing between the impeller tooth portion 10c and the first intermediate tooth portion 19d and between the gear tooth portion 15d and the second intermediate tooth portion 19e (coupled using a so-called tooth structure), so that the coupling between the intermediate member 19 and the impeller 10 and the pinion gear 15 can be easily released, for example, during maintenance. Therefore, with the turbo compressor 1, high maintainability can be ensured compared to a case in which the intermediate member 19 is coupled to the impeller 10 and the pinion gear 15 by shrink fitting or the like.

[0068] Although not shown in Figures 3 and 4, in this embodiment in which the intermediate member 19 is connected to the impeller 10 and the gear shaft portion 15b using a double tooth structure, it is also possible to clamp the intermediate member 19 between the impeller 10 and the pinion gear 15 using a tension bolt 17.

[0069] [Third embodiment] The configuration of a turbo compressor 1 according to a third embodiment of the present invention will be described with reference to Fig. 5. Note that the turbo compressor 1 according to this embodiment has the same configuration as the turbo compressor 1 according to the above-described first embodiment, except for the configuration described below.

[0070] 5, in the turbo compressor 1 according to this embodiment, the gear shaft portion 15b of the pinion gear 15 and the intermediate member 19 are joined by shrink fitting. Specifically, a shrink-fit recess 19f is formed on the gear shaft side end face 19b of the intermediate member 19, the shrink-fit recess 19f being centered on the rotation axis.

[0071] An intermediate member side end surface 15c of the gear shaft portion 15b of the pinion gear 15 has a shrink-fit protrusion 15e centered on the rotation axis and protruding toward the intermediate member 19. The shrink-fit protrusion 15e of the gear shaft portion 15b is fitted into a shrink-fit recess 19f of the intermediate member 19 whose diameter has been expanded by increasing the temperature, and is fastened to the shrink-fit recess 19f by decreasing the temperature of the intermediate member 19.

[0072] The turbo compressor 1 according to this embodiment has the same structure as the turbo compressor 1 according to the first embodiment or the second embodiment, except for the connection structure between the intermediate member 19 and the gear shaft portion 15b, and therefore can obtain the same effects as the first embodiment or the second embodiment.

[0073] As for the method of joining the intermediate member 19 and the impeller 10, the same method as in the first and second embodiments can be adopted, or a joining method by shrink fitting can also be adopted.

[0074] It is also possible to provide a shrink-fit recess on the intermediate member side end face 15c of the gear shaft portion 15b and a shrink-fit protrusion on the gear shaft side end face 19b of the intermediate member 19, and to join them by shrink fitting. In this case, however, the temperature of the gear shaft portion 15b is raised to expand the diameter of the shrink-fit recess. In this embodiment, the intermediate member 19 is also formed of a metal material having a higher heat resistance than the pinion gear 15 including the gear shaft portion 15b, so from the viewpoint of suppressing a decrease in durability of the pinion gear 15, it is preferable to provide a shrink-fit recess 19f in the intermediate member 19 and a shrink-fit protrusion 15e in the gear shaft portion 15b as in this embodiment.

[0075] [Fourth embodiment] The configuration of a turbo compressor 1 according to a fourth embodiment of the present invention will be described with reference to Fig. 6. The turbo compressor 1 according to this embodiment has the same configuration as the turbo compressor 1 according to the first embodiment, except for the configuration described below. Also, in Fig. 6, the gear case 13 is omitted from illustration.

[0076] As shown in FIG. 6, in the turbo compressor 1 according to this embodiment, the intermediate member 19 is also inserted into a hole 12a formed in the casing cover 12 and is interposed between the gap G (the gap between the casing cover 12 and the impeller back surface 10a) and the accommodation space 13a.

[0077] In this embodiment, the intermediate member 19 has a sleeve shape. An intermediate member hole 19g is formed in the center of the intermediate member 19, penetrating in the axial direction between an impeller side end face 19a and a gear shaft side end face 19b. The intermediate member hole 19g is continuous with the impeller hole 10b on the impeller 10 side.

[0078] The gear shaft portion 15b of the pinion gear 15 has a female thread portion 15f formed on the rotation axis from the intermediate member side end face 15c. The female thread portion 15f is continuous with an intermediate member hole portion 19g of the intermediate member 19.

[0079] In the turbo compressor 1 according to this embodiment, the tension bolt 17 is formed to be longer than that in the first embodiment. The other end male thread portion 17b of the tension bolt 17, which is inserted so as to pass through the impeller hole portion 10b and the intermediate member hole portion 19g from the opposite side to the intermediate member 19, is screwed into the female thread portion 15f of the gear shaft portion 15b. At this time, the one end male thread portion 17a of the tension bolt 17 protrudes from the impeller hole portion 10b to the opposite side to the intermediate member 19. A nut 18 is screwed into the one end male thread portion 17a of the tension bolt 17 that protrudes. As a result, the intermediate member 19 is sandwiched between the gear shaft portion 15b and the impeller 10 in the power transmission path from the pinion gear 15 to the impeller 10.

[0080] In the turbo compressor 1 according to this embodiment, an intermediate member 19 is sandwiched between the gear shaft portion 15b and the impeller 10 in the power transmission path from the pinion gear 15 to the impeller 10. The presence of the intermediate member 19 allows a longer tension bolt 17 to be used in accordance with the length of the intermediate member 19. This ensures that the tension bolt 17 can stretch, and the nut 18 can be more reliably prevented from loosening.

[0081] Although detailed description will be omitted, a tooth structure can be used for the connection between the impeller back surface 10a of the impeller 10 and the impeller side end face 19a of the intermediate member 19, and between the gear shaft side end face 19b of the intermediate member 19 and the intermediate member side end face 15c of the gear shaft portion 15b, as in the second embodiment, or shrink fitting can be used as in the third embodiment. When a tooth structure is used for each connection, excellent maintainability can be achieved while ensuring high connectability between the members, as in the second embodiment.

[0082] Moreover, the turbo compressor 1 according to this embodiment can also obtain the same effects as those of the first embodiment.

[0083] [Fifth embodiment] The configuration of a turbo compressor 1 according to a fifth embodiment of the present invention will be described with reference to Fig. 7. The turbo compressor 1 according to this embodiment has the same configuration as the turbo compressor 1 according to the first embodiment, except for the configuration described below. Also, in Fig. 7, the gear case 13 is omitted from illustration.

[0084] As shown in FIG. 7, in the turbo compressor 1 according to this embodiment, the intermediate member 19 is also inserted into a hole 12a formed in the casing cover 12 and is interposed between the gap G and the accommodation space 13a.

[0085] In this embodiment, the gear shaft portion 15b is directly coupled to the impeller 10. The intermediate member 19 is fitted onto the gear shaft portion 15b such that an inner periphery 19h is in close contact with an outer periphery 15g of the gear shaft portion 15b.

[0086] As described above, in this embodiment, a structure is adopted in which the gear shaft portion 15b is directly coupled to the impeller 10. For this reason, a female thread portion 15f is formed on the impeller 10 side of the gear shaft portion 15b. The other end male thread portion 17b of the tension bolt 17 inserted into the impeller hole portion 10b from the opposite side to the gear shaft portion 15b is screwed into the female thread portion 15f of the gear shaft portion 15b. At this time, the one end male thread portion 17a of the tension bolt 17 protrudes from the impeller hole portion 10b to the opposite side to the gear shaft portion 15b. The nut 18 is screwed into the one end male thread portion 17a of the protruding tension bolt 17, thereby coupling the impeller 10 and the gear shaft portion 15b.

[0087] In this embodiment, the intermediate member 19 is fitted onto the gear shaft portion 15b, and therefore does not function as a member for transmitting power from the pinion gear 15 to the impeller 10.

[0088] Although detailed description is omitted, a tooth structure can be adopted for the connection between the impeller 10 and the gear shaft portion 15b, as in the second embodiment. In this case, as in the second embodiment, it is possible to realize excellent maintainability while ensuring high connection between them. Also, a connection means such as shrink fitting or a key may be used to connect the intermediate member 19 and the impeller 10.

[0089] Furthermore, the turbo compressor 1 according to this embodiment differs from the first embodiment in that no intermediate member 19 is disposed in the power transmission path from the pinion gear 15 to the impeller 10. However, since the other configurations are the same, it is possible to obtain the same effects as in the first embodiment.

[0090] [Variations] In the first to fifth embodiments, the turbo compressor (centrifugal compressor) 1 is used as an example of a rotary machine, but the present invention can also be applied to a centrifugal turbine.

[0091] In the first to fifth embodiments, the turbo compressor 1 is configured to include a plurality of working sections 1a such that the temperature of the gas increases as it moves toward the rear stage, and each working section 1a is a rear-stage working section, but the present invention is not limited to this. For example, the turbo compressor 1 does not have to be a multi-stage compressor, and even if it is a multi-stage compressor, the configuration of the present invention can be adopted for the working sections 1a on the front stage side.

[0092] In the first to fifth embodiments, the intermediate member 19 is formed using austenitic stainless steel, precipitation hardened stainless steel, or titanium, but the present invention is not limited to this in terms of the material for the intermediate member 19. That is, when handling gas with a temperature higher than the tempering temperature of the chromium-molybdenum steel or nickel-chromium-molybdenum steel from which the pinion gear 15 is formed, the intermediate member 19 can be formed using various metal materials that have heat resistance to that temperature.

[0093] Similarly, in the case where low-temperature gas is used, the intermediate member 19 may be made of various metal materials having higher cold resistance than chrome molybdenum steel or nickel chrome molybdenum steel.

[0094] In the above second embodiment, a tooth structure is adopted for both the connection between the pinion gear 15 and the intermediate member 19 and the connection between the intermediate member 19 and the impeller 10, but in the present invention, a tooth structure can also be adopted for only one of the connections.

[0095] In the third embodiment, the pinion gear 15 and the intermediate member 19 are joined by shrink fitting, but the intermediate member 19 and the impeller 10 can also be joined by shrink fitting. In addition, when a sleeve-shaped intermediate member 19 is used as in the fifth embodiment, the pinion gear 15 and the impeller 10 can also be joined by shrink fitting.

[0096] In the above-described fifth embodiment, the intermediate member 19 may come into contact with the impeller 10. In this case, the end of the intermediate member 19 on the impeller side 10 and the back surface of the impeller 10 may be provided with teeth that mesh with each other, so that power can be transmitted to the impeller 10 via the intermediate member 19. The gear shaft portion 15b does not necessarily have to be directly connected to the impeller 10.

[0097] In the first to fifth embodiments, the casing 11 and the casing cover 12 may be integrally formed. Also, the seal portion 20 is provided in the hole 12a of the casing cover 12, but the provision of the seal portion 20 is not essential in the present invention.

[0098] In the first to fifth embodiments, the casing cover 12 is provided with the vent portion 12b penetrating from the hole portion 12a to the outside, but in the present invention, it is not essential to provide the vent portion 12b on the casing cover 12. There is no particular limit to the number of vent portions 12b provided on the casing cover 12, and it may be one or more.

[0099] In the first, second, fourth and fifth embodiments, tension bolts 17 are used to secure the members together more firmly, but the present invention does not require the use of tension bolts 17. Other configurations (such as a coupling) may be used to prevent the joint portions from coming apart when the pinion gear 15 and the impeller 10 rotate. [Explanation of symbols]

[0100] 1. Turbo compressor (rotary machine) 10 Impeller 10a Impeller back 11 Casing 12 Casing cover 12a Hole (through hole) 13 Gear case 13a Containment Space 15 Pinion gear 15b Gear shaft 17 Tension bolt 18 Nut 19 Intermediate parts 20 Seal part G Gap

Claims

1. A rotating machine, A working part that compresses or expands a gas; A transmission mechanism that transmits power to the operating unit; Equipped with The transmission mechanism is Brugia and a pinion gear formed of chrome molybdenum steel or nickel chrome molybdenum steel and meshing with the bull gear; Equipped with The actuation unit is The impeller, A casing cover is arranged so that a gap is formed between the casing cover and a back surface of the impeller; an intermediate member that is inserted into a hole of the casing cover and is interposed between an accommodation space in which the pinion gear is accommodated and the gap; Equipped with The intermediate member is formed of a metal material having higher heat resistance or higher cold resistance than chromium-molybdenum steel or nickel-chromium-molybdenum steel, the intermediate member is interposed between the pinion gear and the impeller so as to be capable of transmitting rotation of the pinion gear to the impeller, and is coupled to both the pinion gear and the impeller, The rotary machine further includes a seal portion disposed between the intermediate member and an inner circumferential surface surrounding the hole of the casing cover. Rotating machinery.

2. The intermediate member is a first intermediate tooth portion that meshes with an impeller tooth portion provided on the impeller at one end surface; a second intermediate tooth portion that meshes with a gear tooth portion provided on the pinion gear at the other end surface; Equipped with the intermediate member is coupled to both the pinion gear and the impeller by meshing of the first intermediate tooth portion with the impeller tooth portion and meshing of the second intermediate tooth portion with the gear tooth portion; The rotary machine according to claim 1 .

3. The intermediate member has a sleeve shape, The impeller has an impeller hole formed so that a rotation shaft of the impeller passes through the impeller hole, a tension bolt inserted into an intermediate member hole of the intermediate member and into the impeller hole, A male threaded portion formed on one end of the tension bolt is fastened to a nut in a state where the male threaded portion protrudes on the opposite side of the back surface of the impeller, and another male threaded portion formed on the other end of the tension bolt is fastened to a female threaded portion formed on the pinion gear, The intermediate member is sandwiched between the impeller and the pinion gear by fastening both male threaded portions of the tension bolt to the nut and the female threaded portion of the pinion gear. The rotary machine according to claim 2 .

4. The impeller has an impeller hole formed so that a rotation shaft of the impeller passes through the impeller hole, A tension bolt is further provided to be inserted into the impeller hole. A male threaded portion formed on one end of the tension bolt is fastened to a nut in a state where the male threaded portion protrudes on the opposite side to the back surface of the impeller, and another male threaded portion formed on the other end of the tension bolt is fastened to a female threaded portion formed on the intermediate member. The rotary machine according to claim 1 .

5. The pinion gear has a gear body portion that meshes with the bull gear and a gear shaft portion that is integrally formed with the gear body portion, the intermediate member has a sleeve shape and is fitted onto the gear shaft portion, The end of the intermediate member on the impeller side and the back surface of the impeller are provided with teeth that mesh with each other. The pinion gear and the impeller are spaced apart from each other in a direction in which a rotation shaft of the impeller extends, and the intermediate member is fitted onto the gear shaft portion, and the teeth of the intermediate member mesh with the teeth of the impeller, thereby allowing power transmission between the pinion gear and the impeller. The rotary machine according to claim 1 .

6. a vent portion for discharging gas leaked between the intermediate member and an inner circumferential surface surrounding the hole of the casing cover to the outside, 5. A rotary machine according to claim 1.

7. The working unit is a compression unit that compresses gas and is used as a centrifugal compressor. A rotary machine according to any one of claims 1 to 4.

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