WO2011101937A1 - テーパカップリング構造体及び回転機械 - Google Patents

テーパカップリング構造体及び回転機械 Download PDF

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Publication number
WO2011101937A1
WO2011101937A1 PCT/JP2010/006760 JP2010006760W WO2011101937A1 WO 2011101937 A1 WO2011101937 A1 WO 2011101937A1 JP 2010006760 W JP2010006760 W JP 2010006760W WO 2011101937 A1 WO2011101937 A1 WO 2011101937A1
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WO
WIPO (PCT)
Prior art keywords
hub
taper
groove
coupling structure
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2010/006760
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English (en)
French (fr)
Japanese (ja)
Inventor
栄一 柳沢
吉田　悟
藤井　正直
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to US13/320,832 priority Critical patent/US8915666B2/en
Priority to EP10846077.5A priority patent/EP2538101B1/en
Publication of WO2011101937A1 publication Critical patent/WO2011101937A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/32—Other parts
    • B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/092—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces the pair of conical mating surfaces being provided on the coupled hub and shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/32—Other parts
    • B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
    • B63H2023/342—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts comprising couplings, e.g. resilient couplings; Couplings therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D2001/0906—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using a hydraulic fluid to clamp or disconnect, not provided for in F16D1/091
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/10—Selectively engageable hub to shaft connection
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members

Definitions

  • the present invention relates to a taper coupling structure in which a shaft having a portion with a tapered outer periphery and a hub having a hollow portion with a tapered inner periphery are fitted to each other.
  • ⁇ ⁇ ⁇ Coupling is known as a mechanical element that transmits the output of the prime mover to the follower.
  • an output shaft hereinafter referred to as a taper shaft
  • a taper shaft of a prime mover in which the outer periphery of the shaft end is formed in a tapered shape, and a hub including a hollow portion in which the shaft end portion is inserted and the inner periphery is formed in a tapered shape
  • This coupling structure is used, for example, for transmission of high output such as transmission of the output of the steam turbine to the compressor and transmission of engine power to the propeller shaft.
  • the taper coupling structure (hereinafter sometimes referred to simply as the coupling structure) is a fitting between the taper shaft and the hub when the taper shaft and the hub are fitted or the taper shaft is removed from the hub.
  • the coupling structure is provided with an oil passage on the taper shaft (or hub), and an oil groove connected to the oil passage on the outer peripheral surface of the taper shaft (or the inner peripheral surface of the hub). Oil is supplied to the fitting surface through the groove.
  • the coupling structure can be fitted and pulled out by heating the hub to cause thermal expansion. However, when the hub is large, the heating operation is not easy. Therefore, the coupling structure is exclusively fitted and removed by hydraulic pressure.
  • Patent Document 1 describes that oil is scattered from an oil groove and contaminates the surroundings as a problem in a coupling structure that is fitted and removed by hydraulic pressure.
  • Patent Document 1 proposes that the inner peripheral surface of the hub is subjected to fine groove processing (depth is 5/100 mm or less). According to Patent Document 1, since the oil as a complete fluid does not exist on the inner peripheral surface of the hub by performing the fine groove processing, as a result, the taper shaft is removed and the oil is exposed to the space. However, the oil is not fluidly scattered, but is maintained in a state of being adhered to the surface layer portion.
  • the supplied oil is likely to leak from the end of the structure, so that it is difficult to obtain the pressure required for fitting or removal between the tapered shaft and the hub. If it is forcibly fitted or removed in this state, scratches will occur on the outer peripheral surface of the taper shaft and the inner peripheral surface of the hub.
  • the present invention has been made based on such a technical problem, and provides a tapered coupling structure in which the taper shaft and the hub can be easily fitted and removed without using an O-ring. Objective.
  • the coupling structure 100 is in a state where the taper shaft 110 and the hub 120 are engaged with each other as shown in FIG. (Surface pressure) P is received.
  • an oil groove 112 is provided on the outer peripheral surface of the taper shaft 110 (or the inner peripheral surface of the hub 120), and oil OL is supplied between the taper shaft 110 and the hub 120 via the oil groove 112. Due to the pressure of the supplied oil OL, the inner peripheral surface of the hub 120 is curved in a concave shape as shown in FIG. In this manner, the contact area between the tapered portion 111 and the hub 120 is reduced by widening the inner diameter of the hub 120, and the frictional resistance ⁇ N between the tapered shaft 110 and the hub 120 is lowered. That is, if the contact area CA between the taper portion 111 and the hub 120 is small as shown in FIG. 2A, the contact area CA between the taper portion 111 and the hub 120 is easily removed as shown in FIG. If it is large, it is difficult to remove.
  • the surface pressure P increases at both ends of the hub 120 in the axial direction. This is because both ends of the hub 120 in the axial direction have a large diameter of the taper shaft 110 at one end (left end in the drawing), and the radial thickness of the hub 120 is thick at the other end (right end in the drawing). This is because the radial rigidity is high. In particular, since the flange portion on the right end side of the hub 120 is thick, the surface pressure at the right end is the highest. Therefore, in order to remove the taper shaft 110, it is necessary to increase the surface pressure acting on this portion.
  • the radial rigidity of the hub or taper shaft region corresponding to the low surface pressure portion is reduced, so that the taper shaft and the hub can be easily fitted and removed even if the surface pressure is low.
  • the present invention relates to a taper coupling structure in which a taper shaft and a hub are fitted to each other.
  • the taper shaft has a first end portion and a second end portion, and includes a taper portion into which the hub is fitted on the first end portion side.
  • the tapered portion is continuously reduced in diameter from the second end portion toward the first end portion.
  • the hub has an inner periphery and an outer periphery, and the radial thickness on the first end side is thicker, and the radial thickness on the second end side is thinner than the first end side. Composed.
  • the taper coupling structure of the present invention is characterized in that a lightening portion is provided on an end surface on the first end portion side of the taper shaft or an end surface on the first end portion side of the hub.
  • This lightening portion can be provided on one or both of the taper shaft and the hub.
  • the thinned portion provided on the taper shaft is formed from a position spaced from the outer periphery of the taper shaft toward the center axis toward the center axis.
  • the lightening portion provided in the hub is formed from a position spaced from the inner periphery toward the outer periphery toward the outer periphery.
  • the above thinned portions are continuously provided in the circumferential direction on the end surface of the taper shaft or the end surface of the hub.
  • the thinned portion is provided uniformly in the radial direction on the end surface of the taper shaft or the end surface of the hub.
  • the above-described thinned portion is in a state where the tapered shaft and the hub are fitted to each other, the thinned portion formed on the tapered shaft interferes with the hub in the radial direction, and the thinned portion formed on the hub is Interference with taper shaft in radial direction.
  • the shape of the thinned portion according to the present invention is not limited as long as the radial rigidity of the tapered shaft or hub region corresponding to the low surface pressure portion can be reduced, as shown in the embodiments described later. Absent. However, in order to reduce the man-hour for processing the end face of the taper shaft or the end face of the hub, it is preferable to use an annular groove provided continuously in the circumferential direction of the thinned portion. Moreover, it is preferable to provide a lightening part in the hub from the viewpoint of ease of processing of the lightening part.
  • the present invention applies the above-described tapered coupling structure as a prime mover that outputs rotational force, a follower that is driven to rotate by the output of the prime mover, and a coupling structure that transmits the output of the prime mover to the follower. Provide rotating machinery.
  • the taper shaft and the hub can be fitted and used without using an O-ring.
  • a taper coupling structure that can be easily pulled out is provided.
  • the taper coupling structure 10 includes a taper shaft 20 and a hub 30 fitted to the taper shaft 20.
  • the taper shaft 20 constitutes an output shaft of a steam turbine (not shown), for example.
  • the hub 30 is connected to an input shaft of a compressor (not shown), for example, and functions as an element that transmits the output of the steam turbine to the compressor.
  • the taper shaft 20 includes a taper portion 21 whose diameter continuously decreases toward the tip (first end).
  • the side on which the taper shaft 20 and the hub 30 are fitted is defined as the front. That is, in FIG. 3A, the right end of the taper shaft 20 is a front end, and the left end is a rear end.
  • the left end is the front end and the right end is the rear end.
  • An axial oil passage 22 is formed along the central axis of the taper shaft 20 from the front end surface SF of the taper portion 21.
  • a radial oil passage 23 is formed in the radial direction of the tapered portion 21.
  • the radial oil passage 23 communicates with the axial oil passage 22, and both ends are open to the outer peripheral surface of the tapered portion 21. Accordingly, oil supplied from a hydraulic source (not shown) flows along the axial oil passage 22 opening in the front end surface SF of the tapered portion 21 along the axial direction, and then along the radial oil passage 23 in the radial outer periphery. Flows to the side. Thereafter, the tape is supplied to the fitting surface between the tapered portion 21 and the hub 30. An oil groove 24 is formed along the circumferential direction of the tapered portion 21 at a position on the outer peripheral surface of the tapered portion 21 where the radial oil passage 23 is opened.
  • Oil flowing out from the opening of the radial oil passage 23 flows through the oil groove 24 and permeates in the circumferential direction of the outer peripheral surface of the tapered portion 21.
  • oil passes along the fitting surface of the tapered portion 21 and the hub 30 in the axial direction.
  • the hub 30 includes a base portion 31 having a hollow portion through which the tapered portion 21 of the tapered shaft 20 passes, and a flange portion 32 having a larger outer diameter than the base portion 31 and having a high rigidity.
  • the flange portion 32 is connected by an input shaft of a compressor that receives force transmission, a bolt, and other fastening means. Since the flange portion 32 is a portion that receives a large torsional stress from the input shaft, the radial thickness is set large. Since the flange portion 32 is thicker in the radial direction than the base portion 31, the surface pressure P of the taper portion 21 received from the flange portion 32 is the surface of the taper portion 21 received from the base portion 31 as shown in FIG. It is larger than the pressure P.
  • the hollow portion of the hub 30 penetrates in the axial direction, and a taper receiving portion 33 whose diameter continuously decreases from the front end toward the rear end is formed.
  • An annular groove 34 is formed on the rear end surface HB of the hub 30.
  • the groove 34 is opened in the rear end surface HB of the hub 30, and a part of the flange portion 32 is thinned from the rear end surface HB toward the front end.
  • the groove 34 is formed from a position spaced from the inner periphery to the outer periphery of the hub 30 toward the outer periphery.
  • the groove 34 is formed continuously in the circumferential direction on the rear end surface HB of the hub 30. Further, the groove 34 has a uniform width and is formed uniformly in the radial direction.
  • the inner shell portion 35 which is a portion inside the groove 34 in the radial direction has a low rigidity in the radial direction because the groove 34 exists. Therefore, when a force is applied from the hollow portion of the flange portion 32 toward the radially outer side, the diameter is easily expanded in the direction by elastic displacement (deflection). Therefore, as shown in FIG. 3B, the surface pressure at the position corresponding to the portion where the groove 34 is formed is lowered, and the taper shaft 20 and the hub 30 can be easily fitted and removed.
  • the groove 34 formed in the hub 30 needs to interfere with the taper shaft 20 in the radial direction in a state where the taper shaft 20 and the hub 30 are completely fitted. This will be described with reference to FIG.
  • the taper shaft 20 and the hub 30 are fitted, first, as shown in FIG. 5A, the taper shaft 20 is moved into the hollow portion of the hub 30 until there is no gap between the taper shaft 20 (taper portion 21) and the hub 30. Let it enter. In this state, only the outer peripheral surface of the taper shaft 20 (taper portion 21) and the inner peripheral surface of the hub 30 are in contact with each other, and this state is referred to as an initial fitting state.
  • the front end surface SF of the taper shaft 20 recedes in the hollow portion more than the rear end surface HB of the hub 30 as shown in FIG. Is configured to do. Therefore, in FIG. 5A showing the initial stage of fitting, the groove 34 of the hub 30 does not reach the radial extension line E of the front end surface SF of the tapered shaft 20. In this state, since the inner shell portion 35 is not in contact with the tapered portion 21, the periphery of the tapered portion 21 has high rigidity. Therefore, if the taper coupling structure 10 has been fitted with the groove 34 of the hub 30 and the taper shaft 20 in the positional relationship shown in FIG. 5A, the effect of providing the groove 34 cannot be enjoyed. Become. In addition, from the above, when providing the groove
  • a condition for obtaining this state is that a part of the groove 34 of the hub 30 exceeds the direction of the rear end side of the taper shaft 20 with respect to the extension line E.
  • the relationship is defined as that the groove 34 interferes with the taper shaft 20 in the radial direction.
  • the reason why the grooves 34 are continuously formed in the circumferential direction is to equalize the surface pressure in the circumferential direction. For example, if the groove is intermittently provided in the circumferential direction, the surface pressure is high where the groove is not provided, and the surface pressure is low where the groove is provided. If the surface pressure in the circumferential direction becomes non-uniform in this way, there is a risk that oil leakage will occur from a place where the surface pressure is high. This is because the diameter of the hub 30 cannot be increased as desired.
  • the groove 34 is formed uniformly in the radial direction for the same reason.
  • the dimensions of the groove 34 are preferably set as follows (see FIG. 3A).
  • groove width W If only the elastic displacement toward the radially outer side of the inner shell portion 35 is taken into consideration, it is not necessary to set the lower limit / upper limit of the groove width W. However, the most common method for forming the groove 34 is to cut the rear end face HB after the hub element body including the base portion 31 and the flange portion 32 is manufactured. Thus, the groove width W should not be increased. Therefore, in the present invention, it is recommended that the groove width W be about several mm, for example.
  • the groove depth D is small, the inner shell portion 35 is not easily elastically displaced toward the radially outer side.
  • the groove 34 formed in the hub 30 needs to interfere with the taper shaft 20 in the radial direction when the fitting is completed, and the front end surface SF of the taper shaft 20 is more than the rear end surface HB of the hub 30.
  • the groove depth D is preferably a length including the fitting stroke.
  • Interference allowance I If the amount of interference between the groove 34 and the taper shaft 20 (interference allowance I) is too small, the inner shell portion 35 is less likely to be elastically displaced outward in the radial direction. Therefore, it is preferable to provide the interference margin I.
  • the distance L is preferably small so as not to inhibit the elastic displacement of the inner shell portion 35 toward the radially outer side.
  • groove shape In the example shown in FIG. 1 (to FIG. 5), the bottom of the groove 34 has a round shape, but the present invention is limited to this shape as long as the inner shell portion 35 is easily elastically displaced outward in the radial direction. Not. Therefore, according to the present invention, grooves having various shapes such as a groove 36 having a rectangular opening cross section as shown in FIG. 6A and a groove 37 having a triangular opening cross section as shown in FIG. Applicable.
  • the thinning part of this invention is not limited to a groove
  • a small-diameter portion 38 corresponding to the inner shell portion is provided at the rear end of the hub 30, and a portion radially outside the small-diameter portion 38 is defined as a gap (thickening portion).
  • the present invention allows. Since the small-diameter portion 38 has low rigidity, it is easily elastically displaced toward the outside in the radial direction like the inner shell portion 35.
  • the hub 30 When producing the hub 30 having the small-diameter portion 38 as in this example, forming the portion corresponding to the gap (thickening portion) radially outside the small-diameter portion 38 by cutting is from the viewpoint of the processing man-hour. It is not preferable. However, the hub 30 is usually manufactured through a procedure called cutting after forging. However, by performing forging in consideration of forming the small-diameter portion 38, the number of man-hours for cutting can be reduced. . In FIG. 6, the same components as those in FIG. 3 are denoted by the same reference numerals as those in FIG. The same applies to FIGS. 7 and 8 below.
  • the groove 39 is provided in the front end surface SF of the tapered shaft 20 as shown in FIG. You can also.
  • the groove 39 is formed from a position spaced from the outer periphery of the tapered portion 21 toward the central axis toward the central axis.
  • the radial rigidity of the outer shell portion 40 which is a portion outside the groove 39 in the radial direction, is low because the groove 39 exists.
  • the front end surface SF of the taper shaft 20 is continuous in the circumferential direction and the width thereof is set to be uniform, it is required for the groove 39 as well as the groove 34 to be formed uniformly in the radial direction. Further, the above-described groove width W, groove depth D, interference margin I, and groove shape can be similarly applied to the groove 39. Furthermore, as shown in FIG. 7B, the surface pressure can be further reduced by providing the groove 39 and the groove 34 in both the tapered shaft 20 and the hub 30.
  • the groove 39 of the taper shaft 20 has a groove depth that is less than the fact that the front end surface SF of the taper shaft 20 is retracted to the inside of the hollow portion from the rear end surface HB of the hub 30 and the fitting stroke need not be considered. D can be shallow.
  • the groove 34 thickening part
  • the groove 34 as the thinning portion is provided on the rear end surface HB of the hub 30 and the groove 39 as the thinning portion is provided on the front end surface SF of the taper shaft 20 has been shown, but as shown in FIG. It is also possible to provide a groove 41 as a thinned portion on the front end face HF.
  • the inner shell portion 42 which is the portion inside the groove 41 in the radial direction, has a low rigidity in the radial direction because the groove 41 exists. Therefore, when a force is applied from the hollow portion of the base portion 31 toward the radially outer side, the inner shell portion 42 is likely to expand in the direction due to elastic displacement (deflection). Therefore, as shown in FIG. 8B, the surface pressure at the position corresponding to the portion where the groove 41 is formed is lowered, and the taper shaft 20 and the hub 30 can be easily fitted and removed.
  • the present invention it is not essential to provide a lightening portion on the front end surface HF of the hub 30.
  • the surface pressure is large on the rear end side of the hub 30 (the front end side of the taper shaft 20)
  • by providing a thinned portion on the rear end surface HB of the hub 30 or the front end surface SF of the taper shaft 20 This is because it is possible to achieve the object of the present invention in which the taper shaft 20 and the hub 30 can be easily fitted and removed. Therefore, it is a more preferable form of the present invention to provide a thinned portion on the front end surface HF of the hub 30.
  • the taper coupling structure 10 described above is an output of the prime mover 210 in a rotary machine 200 including a prime mover 210 that outputs a rotational force and a follower 220 that is rotationally driven by the output of the prime mover. Is applied to the coupling structure 230 that transmits the motor to the follower 220.
  • one of the rotating shaft on the prime mover 210 side and the rotating shaft on the driven machine 220 side has a tapered shaft end, and a taper coupling structure 230 is configured by providing a hub on the other.
  • the prime mover 210 for example, a steam turbine, a gas turbine, an internal combustion engine, an electric motor, or the like is applied.
  • a speed increasing / variable speed device may be provided between the prime mover 210 and the follower 220 side.
  • the shaft end of the rotating shaft of the speed increasing / variable speed device may be tapered or a hub may be provided.
  • the configuration described in the above embodiment can be selected and changed to other configurations as appropriate without departing from the spirit of the present invention.
  • the oil groove 24 can be provided in the hub 30, and the oil passage can be provided in the hub 30.
  • the removal has been described, but it goes without saying that the present invention functions effectively even during fitting.
  • DESCRIPTION OF SYMBOLS 10 ... Tapered coupling structure 20 ... Tapered shaft, 21 ... Tapered part 30 ... Hub, 31 ... Base part, 32 ... Flange part, 33 ... Taper receiving part 34, 36, 37, 39, 41 ... Groove, 35, 42 ... Inner shell part, 38 ... small diameter part, 40 ... outer shell part 200 ... rotating machine, 210 ... prime mover, 220 ... follower, 230 ... coupling structure

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
PCT/JP2010/006760 2010-02-18 2010-11-18 テーパカップリング構造体及び回転機械 Ceased WO2011101937A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US13/320,832 US8915666B2 (en) 2010-02-18 2010-11-18 Taper coupling structure and rotating machine
EP10846077.5A EP2538101B1 (en) 2010-02-18 2010-11-18 Taper coupling structure and rotating machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010033523A JP5535678B2 (ja) 2010-02-18 2010-02-18 テーパカップリング構造体及び回転機械
JP2010-033523 2010-02-18

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WO2011101937A1 true WO2011101937A1 (ja) 2011-08-25

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US (1) US8915666B2 (https=)
EP (1) EP2538101B1 (https=)
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WO (1) WO2011101937A1 (https=)

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JP2020029940A (ja) * 2018-08-24 2020-02-27 イーグル工業株式会社 油圧嵌め用ハブのシール機構

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JP6607376B2 (ja) * 2015-07-01 2019-11-20 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置
JP6692070B2 (ja) * 2015-07-22 2020-05-13 パナソニックＩｐマネジメント株式会社 ターボ機械
AT521658B1 (de) * 2018-08-21 2020-12-15 Prisma Eng Maschinen Und Motorentechnik Gmbh Schwinglast zum Schwingungsprüfen einer Welle
US11525358B2 (en) 2021-02-17 2022-12-13 Pratt & Whitney Canada Corp. Interference fit control for the assembly of rotary parts

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EP2538101A1 (en) 2012-12-26
EP2538101B1 (en) 2018-01-03
US20120093579A1 (en) 2012-04-19
JP5535678B2 (ja) 2014-07-02
JP2011169395A (ja) 2011-09-01
EP2538101A4 (en) 2017-04-12

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