WO2017203649A1 - アンバランス検出装置、および、アンバランス検出方法 - Google Patents
アンバランス検出装置、および、アンバランス検出方法 Download PDFInfo
- Publication number
- WO2017203649A1 WO2017203649A1 PCT/JP2016/065544 JP2016065544W WO2017203649A1 WO 2017203649 A1 WO2017203649 A1 WO 2017203649A1 JP 2016065544 W JP2016065544 W JP 2016065544W WO 2017203649 A1 WO2017203649 A1 WO 2017203649A1
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- WIPO (PCT)
- Prior art keywords
- sound pressure
- vibration
- rotating body
- pressure sensor
- oil supply
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/027—Arrangements for balancing
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining unbalance
- G01M1/16—Determining unbalance by oscillating or rotating the body to be tested
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/04—Antivibration arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01H—MEASUREMENT OF MECHANICAL VIBRATIONS OR ULTRASONIC, SONIC OR INFRASONIC WAVES
- G01H1/00—Measuring characteristics of vibrations in solids by using direct conduction to the detector
- G01H1/003—Measuring characteristics of vibrations in solids by using direct conduction to the detector of rotating machines
- G01H1/006—Measuring characteristics of vibrations in solids by using direct conduction to the detector of rotating machines of the rotor of turbo machines
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01H—MEASUREMENT OF MECHANICAL VIBRATIONS OR ULTRASONIC, SONIC OR INFRASONIC WAVES
- G01H11/00—Measuring mechanical vibrations or ultrasonic, sonic or infrasonic waves by detecting changes in electric or magnetic properties
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/02—Details of balancing machines or devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/334—Vibration measurements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/80—Devices generating input signals, e.g. transducers, sensors, cameras or strain gauges
- F05D2270/81—Microphones
Definitions
- the present disclosure detects an unbalance of a rotating body in a turbo cartridge including a rotating body in which a turbine wheel and a compressor wheel are coupled by a rotating shaft, and a bearing housing that houses a bearing that rotatably supports the rotating body.
- the present invention relates to an unbalance detection device and an unbalance detection method.
- a cartridge (hereinafter referred to as a turbo cartridge), which is a core part of a turbocharger, is subjected to balancing work of a rotating body constituting the turbo cartridge after assembly (for example, Patent Documents 1 to 4).
- This balancing operation includes an unbalance detection operation for detecting the unbalance of the rotating body while the rotating body is rotated. When the unbalance of the rotating body is detected, a part of the rotating body is slightly shaved. It is a series of work to balance the rotating body.
- the unbalance detection device uses two housing members to support the bearing housing from both sides while accommodating the turbine wheel or compressor wheel of the rotating body, respectively (see Patent Document 3).
- Patent Document 3 discloses that housing members on the turbine wheel side and the compressor wheel side are fixed to each other with bolts via a fixing rod.
- Patent Document 4 supports one side of the turbo cartridge by a clamp method that supports without fixing bolts, and has a natural frequency and a rotation frequency of the rotation body on the unbalance detection device side as the rotation body rotates.
- an unbalance correction device that can reduce the influence of resonance due to the coincidence and improve the accuracy of unbalance correction.
- Japanese Patent Laid-Open No. 2003-240054 Japanese Unexamined Patent Publication No. 62-135743 JP-A-3-503315 Japanese Patent No. 423241
- the support of the turbo cartridge by the clamp method is more advantageous than the bolt fixing method from the viewpoint of productivity.
- the bolt fixing method requires fastening and removal of bolts, and increases the work time and cost. Therefore, the support by the clamp method is particularly suitable for a mass-produced turbo cartridge.
- the housing member and the bearing housing of the turbo cartridge are in direct contact with each other in the clamp method as in Patent Document 4, problems as described below may occur. That is, the clamp method is inferior in stability when the turbo cartridge is supported because it is not firmly fastened with the bolt as compared with the bolt fixing method.
- the difference in how the bearing housing and the housing member come into contact (how to contact) that may occur when the turbo cartridge is supported by the unbalance detection device is the resonance point of resonance between the turbo cartridge side and the device described above. The vibration characteristics during rotation of the rotating body are greatly affected.
- the above-described effect vector is acquired in a state where the bearing housing and the housing member of the turbo cartridge are stably supported, such as being fixed with bolts. For this reason, if the vibration characteristics change depending on how both members hit, the correspondence between the individual during balancing work and the effect vector will not be appropriate, and it will be difficult to accurately calculate cutting information. This will cause the yield to deteriorate.
- the productivity of the turbo cartridge is reduced. Will bring about a decline.
- a non-contact type vibration sensor using a well-known method such as an eddy current type, a capacitance type, an optical type, or an ultrasonic type, but in these non-contact type vibration sensors, There is not enough resolution to detect vibration during rotation of the rotating body, and it is difficult to properly detect vibration signals from the rotating body.
- the present inventor has found that the vibration signal of the rotating body can be appropriately detected with a necessary resolution by using a sound pressure sensor represented by a microphone and used for sound detection.
- At least one embodiment of the present invention aims to provide an unbalance detection device that detects vibration during rotation of a rotating body of a turbo cartridge using a sound pressure sensor.
- An unbalance detection device includes: An unbalance for detecting an unbalance of the rotating body in a turbo cartridge, comprising: a rotating body in which a turbine wheel and a compressor wheel are coupled by a shaft; and a bearing housing that houses a bearing that rotatably supports the rotating body.
- a detection device A sound pressure sensor capable of detecting vibration during rotation of the rotating body by measuring a sound pressure generated by vibration during rotation of the rotating body without contact.
- the unbalance detection device detects the vibration during rotation of the rotating body using the sound pressure sensor for detecting the sound pressure (sound) such as a microphone. Composed.
- the vibration during rotation of the rotating body cannot be properly detected with the resolution of the non-contact type vibration sensor, but can be detected with the resolution of the sound pressure sensor, as will be described later. Therefore, the vibration during rotation of the rotating body can be appropriately detected by the sound pressure sensor.
- the non-contact type sound pressure sensor is attached to and detached from each of the mass-produced turbo cartridges. It can be installed without any need. For this reason, it is possible to improve the efficiency of the unbalance detection work by detecting the vibration when the rotating body is rotated by the sound pressure sensor.
- the sound pressure sensor is configured by a microphone having a directivity characteristic capable of collecting sound pressure from a specific direction, or based on sound pressures respectively collected by a plurality of microphones. It is configured to measure the sound pressure from.
- the sound pressure sensor is configured to measure the sound pressure coming from a specific direction. For example, when a microphone having an omnidirectional characteristic is used, sound pressure from other than the target is also collected, but the sound pressure from other than the target becomes a disturbance for detecting the vibration of the rotating body. For this reason, it is possible to measure the sound pressure by narrowing in a specific direction, for example, by processing the sound pressure from a microphone having directivity characteristics or a plurality of microphones. As a result, it is possible to increase the detection accuracy of vibration during rotation of the rotating body by measuring the sound pressure by reducing the sound pressure coming from the bearing housing of the turbo cartridge.
- the sound pressure sensor has a self-noise level of 50 dB or less. According to the configuration of (3) above, the vibration during rotation of the rotating body can be appropriately detected with the necessary resolution by the sound pressure sensor.
- a turbine-side housing member that houses the turbine wheel A compressor-side housing member that houses the compressor wheel; A support mechanism configured to press and hold at least one of the turbine side housing member and the compressor side housing member toward the turbo cartridge, thereby supporting the turbo cartridge sandwiched from both sides; Vibration isolation members interposed between the turbine side housing member and the turbo cartridge and between the compressor side housing member and the turbo cartridge, respectively,
- the specific direction is a direction in which the bearing housing is located.
- the turbo cartridge is supported in a state of being sandwiched from both sides by the turbine side housing member and the compressor side housing member via the vibration insulating member.
- the vibration isolation member provides vibration isolation (reduction of transmitted vibration) between the unbalance detection device side and the turbo cartridge side. Accordingly, in the unbalance detection operation, resonance on the unbalance detection device side with respect to vibration during rotation of the rotating body can be suppressed. In addition, vibrations that are not affected by resonance are detected through the measurement of sound pressure from the bearing housing by the sound pressure sensor, improving the accuracy of balancing and improving the efficiency of balancing work. Can be achieved.
- the turbo cartridge in the configuration of (4) above, is supported by the support mechanism in contact with the vibration insulating member without contacting the turbine housing member and the compressor housing member. According to the configuration of (5) above, the turbo cartridge contacts the support mechanism only through the vibration insulating member. For this reason, the vibration isolation member can more appropriately achieve vibration isolation between the unbalance detection device side and the turbo cartridge side.
- An oil supply pipe for supplying lubricating oil to the inside of the bearing housing the oil supply pipe configured to be connectable to and separated from an oil supply port formed in the bearing housing;
- the sound pressure sensor is fixed to the oil supply pipe.
- the sound pressure sensor is installed on the bearing housing. That is, the connection of the oil supply pipe to the oil supply port of the bearing housing and the installation of the sound pressure sensor are linked. As a result, the sound pressure sensor can be efficiently installed in the bearing housing, and the unbalance detection operation can be performed efficiently.
- the sound pressure sensor is fixed to the oil supply pipe so as to be separated from the bearing housing by a predetermined distance in a state where the oil supply pipe is connected to the oil supply port.
- the sound pressure sensor can be installed in a non-contact state separated from the bearing housing by connecting the oil supply pipe to the oil supply port.
- the predetermined distance is 0.5 mm to 2.0 mm.
- the sound pressure sensor can be installed in a state separated from the bearing housing by a predetermined distance suitable for vibration detection of the rotating body by connecting the oil supply pipe to the oil supply port. Vibration during body rotation can be detected with high accuracy.
- the bearing housing has a planar sensing surface that the sound pressure sensor faces, The sensing surface is provided such that the normal direction of the opening surface of the fuel filler opening and the normal direction of the sensing surface coincide.
- the sensing surface is formed in a flat shape on the bearing housing so that the normal direction of the sensing surface matches the normal direction of the opening surface of the fuel filler opening. Accordingly, the sound pressure sensor and the sensing surface can face each other in parallel with the oil supply pipe and the oil supply port connected, and the sound pressure from the bearing housing can be measured well.
- the sound pressure sensor is fixed to the oil supply pipe via a sensor side vibration insulating member.
- the vibration isolation between the sound pressure sensor side and the unbalance detection device side using the oil supply pipe as a vibration transmission path can be achieved by the sensor side vibration insulating member. Thereby, the detection accuracy of the vibration signal from the rotating body by the vibration sensor can be increased.
- the sensor side vibration insulating member is a sponge.
- the sound pressure sensor and the oil supply pipe are connected via a sponge, so that the oil supply pipe is used as a vibration transmission path between the sound pressure sensor side and the unbalance detection device side. Vibrational insulation can be achieved.
- An unbalance detection method includes: A turbo cartridge comprising: a rotating body in which a turbine wheel and a compressor wheel are coupled by a rotating shaft; and a bearing housing that houses a bearing that rotatably supports the rotating body.
- a balance detection method Vibration isolation members between the turbine-side housing member that accommodates the turbine wheel of the rotating body and the turbo cartridge, and between the compressor-side housing member that accommodates the compressor wheel of the rotating body and the turbo cartridge, respectively.
- a vibration insulating member installation step for interposing A support step of supporting at least one of the turbine-side housing member and the compressor-side housing member by sandwiching the turbo cartridge from both sides by pressing toward the turbo cartridge with the vibration insulating member interposed therebetween; , A measurement step of measuring, in a non-contact manner, a sound pressure generated by the vibration when the rotating body is rotated by a sound pressure sensor capable of detecting the vibration when the rotating body is rotating.
- the resonance on the unbalance detection device side with respect to the vibration at the time of rotation of the rotating body can be suppressed. It is possible to improve the efficiency of balancing work while improving the accuracy of balance detection.
- vibrations that are not affected by resonance are detected through the measurement of sound pressure from the bearing housing by the sound pressure sensor, improving the accuracy of balancing and improving the efficiency of balancing work. Can be achieved.
- the supporting step supports the turbo cartridge in a state where it is in contact with the vibration insulating member without contacting the turbine side housing member and the compressor side housing member.
- the vibration isolation member can more appropriately achieve vibration isolation between the unbalance detection device side and the turbo cartridge side.
- the oil supply pipe for supplying lubricating oil to the interior of the bearing housing to an oil supply port formed in the bearing housing
- the oil supply pipe is provided with a predetermined distance from the bearing housing.
- a sensor fixing step for fixing the sound pressure sensor is further provided.
- the sound pressure sensor can be installed in a non-contact state separated from the bearing housing by connecting the oil supply pipe to the oil supply port in the same manner as in the above (7).
- the predetermined distance is 0.5 mm to 2.0 mm.
- the sound pressure sensor is separated from the bearing housing by a predetermined distance suitable for vibration detection of the rotating body. Can be installed, and vibration during rotation of the rotating body can be detected with high accuracy.
- an unbalance detection device that detects vibration during rotation of a rotating body of a turbo cartridge using a sound pressure sensor.
- FIG. 6 is a reference diagram for explaining a vibration mode that occurs when a turbo cartridge is supported without using a vibration insulating member according to an embodiment of the present invention.
- an expression indicating that things such as “identical”, “equal”, and “homogeneous” are in an equal state not only represents an exactly equal state, but also has a tolerance or a difference that can provide the same function. It also represents the existing state.
- expressions representing shapes such as quadrangular shapes and cylindrical shapes represent not only geometrically strict shapes such as quadrangular shapes and cylindrical shapes, but also irregularities and chamfers as long as the same effects can be obtained. A shape including a part or the like is also expressed.
- the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of the other constituent elements.
- FIG. 1 is a diagram schematically showing an unbalance detection device 1 according to an embodiment of the present invention, and shows a state in which a turbo cartridge 7 is supported by the unbalance detection device 1.
- FIG. 2 is a diagram schematically showing a turbo cartridge 7 according to an embodiment of the present invention.
- FIG. 3 is a view for explaining that the turbo cartridge 7 of FIG. 2 is supported by being sandwiched from both sides by the housing members (2t, 2c) of the unbalance detection device 1.
- the unbalance detection device 1 is a device used for balancing the rotating body 71 of the turbo cartridge 7.
- the unbalance detecting apparatus 1 supports the turbo cartridge 7 in a state where the rotating body 71 is rotatable by a clamp method, and unbalances the rotating body 71. It is configured to be able to detect vibration during rotation caused by balance.
- the clamp method referred to here means a support method in which the turbo cartridge 7 is supported by forces (pressing forces) applied in opposite directions from both sides of the rotation axis M of the rotating body 71 in the axial direction.
- the turbo cartridge 7 is supported by the unbalance detection device 1 by the two housing members of the turbine side housing member 2t and the compressor side housing member 2c.
- the two housing members are fastened to each other with bolts, or the two housing members are fastened to the turbo cartridge 7 (bearing housing 72 described later) with bolts. There is no support in combination.
- the unbalance detection device 1 detects the vibration during rotation of the rotating body 71 while rotating the rotating body 71 at a predetermined rotation speed (unbalance detection rotation speed N).
- a vibration characteristic V is obtained by performing frequency analysis such as Fourier transform.
- the turbo cartridge 7 is a core part of the turbocharger, and includes a rotating body 71 in which the turbine wheel Wt and the compressor wheel Wc are integrally coupled by a rotation axis M, and a bearing (not shown) that rotatably supports the rotating body 71. ) And a bearing housing 72 (see FIG. 2).
- the turbo cartridge 7 When the turbo cartridge 7 is installed in, for example, an automobile engine, the turbine wheel Wt installed in the exhaust passage of the engine is rotated by the exhaust gas discharged from the engine so that it is coaxially coupled with the rotation axis M.
- the turbo cartridge 7 is configured such that the compressed compressor wheel Wc is rotated in the intake passage of the engine to compress the intake air to the engine.
- the turbo cartridge 7 is a part of a turbocharger including a radial turbine.
- the unbalance detection device 1 detects the vibration during rotation of the rotating body 71 by measuring the sound pressure P generated by the vibration during rotation of the rotating body 71 in a non-contact manner.
- a possible sound pressure sensor 4 is provided.
- the sound pressure sensor 4 is a pressure sensor.
- the sound pressure sensor 4 is a microphone. That is, the sound pressure sensor 4 is a sensor for measuring a sound in a frequency band of human audible sound (generally referred to as 20 Hz to 20 kHz).
- the frequency band of the audible sound is 20 ⁇ Pa (micropascal) to 20 Pa (pascal) when converted to sound pressure P. Note that a sound having a frequency exceeding the frequency band of the audible sound is an ultrasonic wave.
- the sound pressure sensor 4 has a self-noise level of 50B or less, it depends on the vibration of the measurement object. The smaller the self noise level, the better, but 40 dB or less is more preferable.
- the self-noise level of the microphone (sound pressure sensor 4) is about 40 dB. That is, the level of noise generated by the microphone itself is about 40 dB. With this value as the minimum value, it is possible to pick up a sound larger than this minimum value.
- Lp 20 ⁇ log (sound pressure P / reference sound pressure) using a common logarithm.
- the reference sound pressure is 20 ⁇ Pa
- this microphone is used.
- the sound pressure resolution is 0.002 ⁇ Pa.
- the resolution of a microphone having a self-noise of 40 dB is represented by the vibration speed v (m / s) of the radiation surface, the following vibration speed v (m / s) of the radiation surface and sound pressure P (Pa) near the radiation surface. Therefore, 0.005 mm / s. For this reason, the resolution is when the vibration velocity v is 0.005 mm / s or more.
- the vibration velocity v is a value calculated by using ⁇ as the density of air (1.2 kg / m 3) and c as the speed of sound in air (340 m / s).
- the vibration acceleration a during rotation of the rotating body 71 in this assumption is 0.12 (m / s 2 ).
- the vibration displacement x is 0.0002 ⁇ m.
- the sound pressure sensor 4 has a resolution capable of detecting vibrations where the vibration displacement x is about 0.0001 ⁇ m, and requires vibration when the rotating body rotates. It can be detected appropriately with high resolution.
- the resolution of existing non-contact type vibration sensors eddy current type, laser type, etc.
- Some expensive non-contact type vibration sensors have a resolution increased to 0.01 ⁇ m, but the sound pressure sensor 4 has a high resolution such as a resolution of 0.0001 ⁇ m at 4000 Hz, and is a non-contact type. Compared with this vibration sensor, it is advantageous in terms of cost and accuracy.
- the unbalance detection device 1 uses the sound pressure sensor 4 for detecting the sound pressure P (sound), such as a microphone, to detect vibration during rotation of the rotating body 71.
- the sound pressure sensor 4 can appropriately detect vibration during rotation of the rotating body 71.
- the turbo cartridge 7 is supported by the clamp method via the vibration insulating member 5, the non-contact type sound pressure sensor 4 is attached to each of the mass-produced turbo cartridges 7, It can be installed without requiring removal work. For this reason, the vibration of the rotating body 71 is detected by the sound pressure sensor 4 so that the imbalance detection work can be made more efficient.
- the sound pressure sensor 4 is composed of microphones having directivity characteristics capable of collecting sound pressure P from a specific direction, or is detected by a plurality of microphones.
- the sound pressure P from a specific direction is measured based on the sound pressure P. That is, in any method, the sound pressure sensor 4 is configured to measure the sound pressure P coming from a specific direction. For example, when a microphone having an omnidirectional characteristic is used, sound pressure P from other than the object is collected, but the sound pressure P from other than the object is a disturbance for detecting the vibration of the rotating body 71. . For this reason, it is possible to measure the sound pressure P in a specific direction by performing signal processing on the sound pressure P from a microphone having directivity or a plurality of microphones. As a result, by measuring the sound pressure P by reducing the sound pressure P coming from the bearing housing 72 of the turbo cartridge 7, it is possible to increase the detection accuracy of vibration during rotation of the rotating body.
- FIG. 4 is a diagram for explaining the vibration characteristic V in a state in which the rotating body 71 is rotated when the turbo cartridge 7 is supported via the vibration insulating member 5 according to the embodiment of the present invention.
- FIG. 5 is a reference diagram for explaining a vibration mode that occurs when the turbo cartridge 7 is supported without using the vibration insulating member 5 according to the embodiment of the present invention.
- the unbalance detection device 1 includes a turbine-side housing member 2t, a compressor-side housing member 2c, a support mechanism 3, the above-described sound pressure sensor 4, and a vibration insulating member 5. .
- the unbalance detection device 1 includes a turbine-side housing member 2t, a compressor-side housing member 2c, a support mechanism 3, the above-described sound pressure sensor 4, and a vibration insulating member 5. .
- the turbine side housing member 2t is a housing member that can accommodate the turbine wheel Wt.
- the compressor-side housing member 2c is a housing member that can accommodate the compressor wheel Wc. That is, these housing members (2t, 2c) are for internal wheels for accommodating wheels (Wt, Wc) such as turbine wheels Wt and compressor wheels Wc, and for wheels that allow the wheels to be taken in and out of the internal spaces. It has an opening Ew.
- the turbine wheel Wt is accommodated in the internal space of the turbine side housing member 2t via the wheel opening Ew as shown in FIG.
- the compressor wheel Wc is accommodated in the internal space of the side housing member 2c.
- each of the two housing members supports the turbo cartridge 7 by supporting a support receiving portion 72 p formed in the bearing housing 72 of the turbo cartridge 7.
- the support receiving portion 72p is provided in a region of the bearing housing 72 facing the edge of the wheel opening Ew of the housing member (see FIGS. 2 to 3).
- the rotating body 71 is rotated by supplying air (gas) to either the compressor wheel Wc or the turbine wheel Wt.
- the supply of air for rotating the rotating body 71 is performed through an air opening Eg formed in the housing member.
- the unbalance detection device 1 is configured to rotate the rotating body 71 by supplying air to the compressor wheel Wc accommodated in the compressor-side housing member 2c.
- the compressor side housing member 2c is formed with an inlet side air opening Egi (air opening Eg) so that air can be supplied from the radial direction to the accommodated compressor wheel Wc.
- An outlet side air opening (air opening Eg) (not shown) is formed to discharge air from the internal space of the compressor side housing member 2c.
- the imbalance detection apparatus 1 connects the air blower 12 for supplying air, and the opening side air opening Egi of the compressor side housing member 2c by the air supply piping 13, and supplies air to the compressor wheel Wc from the air blower 12. Is configured to do.
- the air supply pipe 13 and the housing member are connected via a vibration isolation member 91 for piping (for example, an elastic member such as rubber). The vibration on the unbalance detection device 1 side transmitted to the housing member (2c) as a vibration transmission path is reduced.
- the turbine side housing member 2t has an outlet side air opening Ego or an inlet side for flowing the air flow generated by the rotation of the compressor wheel Wc to the outside.
- An air opening Eg such as an air opening Egi (not shown) is formed.
- the rotating body 71 may be rotated by supplying air to the turbine wheel Wt.
- an inlet side air opening Egi and an outlet side air opening Ego are formed in the turbine side housing member 2t, and at least an outlet side air opening Ego is formed in the compressor side housing member 2c.
- the support mechanism 3 is configured to support the turbo cartridge 7 by sandwiching the turbo cartridge 7 from both sides by pressing at least one of the turbine side housing member 2t and the compressor side housing member 2c toward the turbo cartridge 7.
- the support mechanism 3 includes a compressor-side support mechanism 31 connected to the compressor-side housing member 2c and a turbine-side support mechanism 32 connected to the turbine-side housing member 2t.
- the compressor-side support mechanism 31 and the turbine-side support mechanism 32 are each fixed to a floor such as a factory so as not to move when the turbo cartridge 7 is pressed.
- both support mechanisms (31, 32) are connected to these housing members (2t, 2c) above the floor surface so that the turbine side housing member 2t and the compressor side housing member 2c do not contact the floor surface.
- connection between the compressor-side housing member 2c and the compressor-side support mechanism 31 (the pressing rod 34 of the pressing device 33 described later) and the connection between the turbine-side housing member 2t and the turbine-side support mechanism 32 are supported.
- This is performed via a mechanism vibration insulating member 92 (for example, an elastic member such as rubber), and is transmitted to the housing member (2c) using the compressor side support mechanism 31 and the turbine side support mechanism 32 as a vibration transmission path.
- the vibration on the detection device 1 side is reduced.
- a pressing device 33 is provided in the compressor side support mechanism 31, and the pressing device 33 is configured to press the compressor side housing member 2 c toward the turbo cartridge 7. Yes. More specifically, as shown in FIG. 1, the pressing device 33, the compressor-side housing member 2c, the turbo cartridge 7, the turbine-side housing member 2t, and the turbine-side support mechanism 32 are arranged side by side in the pressing direction (FIG. 1, FIG. (In the direction of arrow 3). For this reason, the pressing force by the pressing device 33 is transmitted to the turbine side support mechanism 32 by these arrangements, and the turbo cartridge 7 is caused by the pressing force from the pressing device 33 and the reaction force from the turbine side support mechanism 32. Supported. In the embodiment shown in FIGS.
- the pressing device 33 includes a pressing rod 34 connected to the housing member (2c), and a piston device 35 that pushes the pressing rod 34 toward the housing member (2c). It has.
- the piston device 35 pushes the pressing rod 34 toward the housing member (2c), whereby the housing member (2c) is pressed toward the turbo cartridge 7.
- the pressing rod 34 and the air supply pipe 13 are connected by a connecting member 15, and the air supply pipe 13 is also movable so as to expand and contract from the blower 12 as the pressing rod 34 moves in the pressing direction. It is configured.
- the sound pressure sensor 4 is as described above, and the specific direction in which the sound pressure sensor 4 collects sound is the direction in which the bearing housing 72 is located. That is, in the embodiment shown in FIGS. 1 to 3, the sound pressure sensor 4 is configured to measure the sound pressure P (sound) coming from the bearing housing 72 of the turbo cartridge 7 (see FIG. 7 described later). ).
- the bearing housing 72 supports a bearing 72b (see FIG. 2) therein, and supports the rotating body 71 via the bearing 72b. That is, the vibration at the time of rotation of the rotating body 71 caused by the unbalance of the rotating body 71 is transmitted to the bearing housing 72 via the bearing 72b.
- the sound pressure sensor 4 detects the pressure (pressure change) of the air. Then, a vibration signal S is generated based on the measured sound pressure.
- the sound pressure sensor 4 is fixed to the oil supply pipe 14 as described later.
- the present invention is not limited to this embodiment, and may be fixed to an object other than the turbo cartridge 7. For example, in some other embodiments, it may be fixed to any location other than the oil supply pipe 14 of the unbalance detection device 1. Alternatively, an object (structure) around the unbalance detection device 1 or a device for installing the sound pressure sensor 4 may be prepared and installed.
- the vibration insulating member 5 is interposed between the turbine side housing member 2t and the turbo cartridge 7 and between the compressor side housing member 2c and the turbo cartridge 7, respectively.
- the vibration insulating member 5 is a member capable of achieving vibrational insulation (reduction of vibration) between the housing members (2t, 2c) and the turbo cartridge 7, and is made of an elastic member such as rubber, for example. is there.
- the member formed with the same raw material as the vibration insulation member 91 for piping mentioned above and the vibration insulation member 92 for support mechanisms may be sufficient.
- the housing members (2 t, 2 c) support the support receiving portion 72 p of the bearing housing 72, and this is performed via the vibration insulating member 5.
- the vibration insulating members 5 are respectively installed at the edge portions of the wheel openings Ew of the two housing members (see FIG. 3). Then, when the wheel is accommodated in each housing member and the turbo cartridge 7 is sandwiched between the two housing members, the vibration insulating member 5 provided at the edge of the wheel opening Ew of the housing member becomes the bearing housing 72. It contacts the support receiving portion 72p.
- the shape of the wheel opening Ew is circular.
- the vibration insulating member 5 has an annular shape having a diameter larger than the wheel opening Ew, and the support receiving portion 72p has a circular shape in accordance with this.
- the turbo cartridge 7 is supported via the vibration insulating member 5, so that the vibration when the rotating body 71 is rotated at the unbalance detection rotation speed N described above includes the housing member (2t, 2c). It is possible to suppress (avoid) resonance of the balance detection device 1 side. This point will be described with reference to FIGS.
- the horizontal axis represents the frequency (Hz), and the vertical axis represents the vibration response (vibration magnitude).
- the natural frequency on the unbalance detection device 1 side including the housing members (2t, 2c) in the present embodiment is between the lower limit frequency F1 and the upper limit frequency F2 that is larger than the lower limit frequency F1.
- the vibration characteristic V (vibration frequency characteristic) shown by a thick line in FIG. 4 corresponds to the case where the turbo cartridge 7 is supported via the vibration insulating member 5 as in the above-described embodiment. As shown by the thick line in FIG. 4, when the rotating body 71 is rotated at the unbalance detection rotation speed N, the vibration component having the vibration frequency Vp becomes the peak of the vibration response.
- the peak frequency Vp is smaller than the lower limit frequency F1 (Vp ⁇ F1) and deviates from the natural frequency range (range between F1 and F2) on the unbalance detection device 1 side.
- the vibration response in the range of the natural frequency is small, and the influence on the unbalance detection operation is so small that it can be ignored.
- the vibration characteristic Vr indicated by a thin line as a comparative example in FIG. 4 shows that the two housing members (2t, 2c) and the support receiving portion 72p on the turbo cartridge 7 side do not pass through the vibration insulating member 5. It corresponds to the case where the turbo cartridge 7 is supported by direct contact.
- the vibration component having the vibration frequency Vpr has a peak vibration response.
- the peak frequency Vrp of this comparative example is located between the lower limit frequency F1 and the upper limit frequency F2 (F1 ⁇ Vrp ⁇ F2).
- the turbo cartridge 7 is supported by being sandwiched from both sides by the turbine side housing member 2t and the compressor side housing member 2c through the vibration insulating member 5.
- the vibration isolation member 5 provides vibration isolation between the imbalance detection device 1 side and the turbo cartridge 7 side. Accordingly, in the unbalance detection operation, resonance on the unbalance detection device 1 side with respect to vibration during rotation of the rotating body 71 can be suppressed. Further, the vibration in a state where it is not affected by resonance is detected through the measurement of the sound pressure P from the bearing housing 72 by the sound pressure sensor 4, thereby improving the detection accuracy of the unbalance of the rotating body 71 and balancing. Work efficiency can be improved.
- the turbo cartridge 7 is not in contact with the turbine side housing member 2t and the compressor side housing member 2c, and the vibration insulating member 5 and In the contact state, it is supported by the support mechanism 3.
- the turbo cartridge 7 contacts the support mechanism 3 only through the vibration insulating member 5.
- the vibration isolation member 5 can more appropriately achieve vibration isolation between the unbalance detection device 1 side and the turbo cartridge 7 side.
- FIG. 6A is a schematic side view showing a state in which the sound pressure sensor 4 according to one embodiment of the present invention is fixed to the oil supply pipe 14, and shows a state in which the sound pressure sensor 4 is removed from the bearing housing 72. is there.
- FIG. 6B is a schematic side view showing a state in which the sound pressure sensor 4 according to one embodiment of the present invention is fixed to the oil supply pipe 14, and shows a state in which the sound pressure sensor 4 is installed in the bearing housing 72. is there.
- FIG. 7 is a schematic diagram for explaining the positional relationship between the sound pressure sensor 4 and the bearing housing 72 according to an embodiment of the present invention.
- the unbalance detection device 1 is an oil supply pipe 14 for supplying lubricating oil to the inside of the bearing housing 72.
- the fuel supply pipe 14 is further provided so as to be connected to and separated from the fuel supply port 73 formed in the reference numeral 72.
- the sound pressure sensor 4 is fixed to the oil supply pipe 14.
- the oil supply pipe 14 is supported on the tip side of a support arm 36 extending from the upper part of the turbine side support mechanism 32 toward the compressor side support mechanism 31. Further, in a state where the turbo cartridge 7 is supported by the support mechanism 3, the oil supply port 73 of the bearing housing 72 faces upward in the vertical direction, and the oil supply pipe 14 is positioned above the turbo cartridge 7. (See FIG. 1).
- the support arm 36 can move the oil supply pipe 14 up and down along the vertical direction.
- a fuel filler 73 is connected.
- a vibration insulating member 93 for the oil supply pipe is provided at a portion of the oil supply pipe 14 that contacts the oil supply port 73, and the unbalance detection device 1 side that is transmitted to the turbo cartridge 7 using the oil supply pipe 14 as a vibration transmission path.
- the sound pressure sensor 4 is installed on the bearing housing 72. That is, the connection of the oil supply pipe 14 to the oil supply port 73 of the bearing housing 72 and the installation of the sound pressure sensor 4 are interlocked. Thereby, the sound pressure sensor 4 can be efficiently installed in the bearing housing 72, and the unbalance detection operation can be performed efficiently.
- the sound pressure sensor 4 is separated from the bearing housing 72 by a predetermined distance L when the oil supply pipe 14 is connected to the oil supply port 73 (installed state).
- the oil supply pipe 14 is fixed.
- the sound radiation surface (sensing surface 72v) formed of the bearing housing 72 vibrates at a vibration velocity v (m / s), and the sound propagates through the air by this vibration.
- the sound collection surface 42 of the sound collection unit 41 of the sound pressure sensor 4 is located at a position separated from the sensing surface 72v by a predetermined distance L.
- the sound pressure sensor 4 measures the sound that has reached the sound collection surface 42. Accordingly, the sound pressure sensor 4 can be installed in a non-contact state separated from the bearing housing 72 by connecting the oil supply pipe 14 to the oil supply port 73.
- the predetermined distance L is determined so as to be a distance suitable for detecting the vibration of the rotating body. For example, if the sound pressure sensor 4 (sound collecting surface 42) is too far from the sensing surface 72v to be measured, the sound pressure P due to vibrations of other radiation surfaces may be picked up or the sound may be diffused radially. Accurate measurement of the sound radiated from the sensing surface 72v becomes difficult, for example, the sound pressure P collected becomes small and the problem of the phase delay of the sound transmitted through the air occurs. For this reason, it is necessary to measure the sound (sound pressure P) as close as possible. In some embodiments, the predetermined distance L is 0.5 mm to 2.0 mm.
- the bearing housing 72 has a planar sensing surface 72v facing the sound pressure sensor 4, and the sensing surface 72v is It is provided so that the normal direction of the opening surface of the fuel filler port 73 and the normal direction of the sensing surface 72v coincide.
- the sound collection surface 42 of the sound pressure sensor 4 is formed in a planar shape, and the sensing surface 72v having the planar shape is defined by the normal direction of the sensing surface 72v and the fuel filler port. It is formed in the bearing housing 72 so that the normal direction of the opening surface of 73 coincides.
- the sound pressure sensor 4 when the sound pressure sensor 4 is installed in the bearing housing 72 by connecting the oil supply pipe 14 to the bearing housing 72, the sound pressure sensor 4 (sound collecting surface 42) and the sensing surface 72v face each other in parallel.
- the sound pressure P from the bearing housing 72 can be measured satisfactorily.
- the sound pressure sensor 4 is fixed to the oil supply pipe 14 via the sensor-side vibration insulating member 8.
- the sensor side vibration insulating member 8 may be a sponge.
- the periphery of the sound pressure sensor 4 is covered with the sensor-side vibration insulating member 8 except for the sound collecting surface 42 side of the sound collecting unit 41.
- the sensor side vibration insulating member 8 is bonded and fixed to the oil supply pipe 14 with an adhesive. 1 and 6A to 6B, a part of the sensor side vibration insulating member 8 that covers the sound pressure sensor 4 is omitted for convenience.
- the vibration isolation between the sound pressure sensor 4 side and the imbalance detection apparatus 1 side which made the oil supply piping 14 the vibration transmission path by the sensor side vibration insulation member 8 can be aimed at. .
- the accuracy of detection of the vibration signal S from the rotating body 71 by the sound pressure sensor 4 can be enhanced.
- the fuel filler 73 faces upward when the turbo cartridge 7 is supported by the support mechanism 3 (see FIGS. 1 to 4).
- the turbo cartridge 7 may be supported by the unbalance detection device 1 so that the oil supply port 73 of the bearing housing 72 faces in a direction other than the upward direction. If the other direction is above the horizontal direction, the lubricating oil can be supplied without receiving a component of force in the reverse direction due to gravity.
- FIG. 8 is a flowchart showing an unbalance detection method according to an embodiment of the present invention.
- the unbalance detection method includes a vibration insulating member installation step (S1), a support step (S2), and a sensor installation step (S3).
- the unbalance detection method may include a sound pressure sensor fixing step (S0) before the vibration insulating member installation step (S1).
- a rotating body rotation step (S4) a vibration detection step (S5), and a cutting information calculation step (S6) may be provided in this order.
- the unbalance detection method will be described according to the flow of FIG.
- the sound pressure sensor fixing step (S0) is a step of fixing the sound pressure sensor 4 to a part other than the turbo cartridge 7 such as the oil supply pipe 14, and is performed as a preparation for detecting an unbalance for the turbo cartridge 7. . That is, if the sound pressure sensor 4 is already installed in the oil supply pipe 14, this step can be omitted.
- this sound pressure sensor fixing step (S 0) connects the oil supply pipe 14 for supplying lubricating oil into the bearing housing 72 to the oil supply port 73 formed in the bearing housing 72.
- the sound pressure sensor 4 may be fixed to the oil supply pipe 14 so as to be separated from the bearing housing 72 by a predetermined distance L.
- the connection of the oil supply pipe 14 to the oil supply port 73 of the bearing housing 72 and the installation of the sound pressure sensor 4 to the bearing housing 72 can be interlocked.
- the oil supply pipe 14 is connected to the oil supply port 73 by setting the predetermined distance L to 1/40 or less of the vibration wavelength ⁇ when the rotating body 71 is rotated, or 0.5 to 2.0 mm.
- the sound pressure sensor 4 can be installed in a state of being separated from the bearing housing 72 by a predetermined distance L suitable for detecting the vibration of the rotating body 71, and the vibration during rotation of the rotating body 71 can be detected with high accuracy. Can do.
- the sound pressure sensor 4 is fixed to the oil supply pipe 14 via the sensor side vibration insulating member 8 (see FIGS. 1 and 6A to 6B).
- step S1 of FIG. 8 the vibration insulating member installation step is executed.
- This vibration insulating member installation step (S1) includes a compressor-side housing member that accommodates the turbine-side housing member 2t that accommodates the turbine wheel Wt of the rotating body 71 and the turbo cartridge 7, and a compressor wheel Wc of the rotating body 71.
- the vibration insulating member 5 is interposed between the 2c and the turbo cartridge 7, respectively.
- the vibration insulating member 5 is a member for achieving vibrational insulation between the two housing members (2t, 2c) and the turbo cartridge 7.
- the vibration balance member 5 is brought to the unbalance detection device 1 to support the turbo cartridge 7. Will be executed (see FIG. 3).
- the support step is executed in step S2 of FIG.
- the support step (S2) is a step of supporting the turbo cartridge 7 by sandwiching the turbo cartridge 7 from both sides in the axial direction of the rotating shaft M via the vibration insulating member 5. More specifically, in the supporting step (S2), at least one of the turbine-side housing member 2t and the compressor-side housing member 2c is pressed toward the turbo cartridge 7 with the vibration insulating member 5 interposed therebetween. The cartridge 7 is supported by being sandwiched from both sides. That is, the turbo cartridge 7 is supported by the clamp method via the vibration insulating member 5.
- the support side of the turbo cartridge 7 (such as the turbine-side housing member 2t and the compressor-side housing member 2c) can be prevented from resonating with vibration during rotation of the rotating body 71. It is possible to improve the efficiency of balancing work while improving the accuracy of balance detection.
- the turbo cartridge 7 may be supported in contact with the vibration insulating member 5 without contacting the turbine side housing member 2t and the compressor side housing member 2c. Vibration isolation from the cartridge 7 side can be achieved more appropriately.
- the sensor installation step is executed in step S3 of FIG.
- the sensor installation step (S3) is a step of installing the sound pressure sensor 4 in the bearing housing 72. More specifically, in the sensor installation step, the sound pressure sensor 4 that can detect the vibration during the rotation of the rotating body 71 by measuring the sound pressure P generated by the vibration during the rotation of the rotating body 71 in a non-contact manner, In this step, the sound pressure P from the direction in which the bearing housing 72 is located is measured.
- the sound pressure sensor 4 is composed of one or more microphones. This step is performed, for example, by connecting the oil supply pipe 14 to the oil supply port 73 when the sound pressure sensor 4 is fixed to the oil supply pipe 14 in the embodiment in which the step S0 described above is executed. . Thereby, the sound pressure sensor 4 can be installed efficiently, and the unbalance detection work can be performed more efficiently.
- step S4 in FIG. 8 a rotating body rotating step for rotating the rotating body 71 is executed.
- air is supplied from the blower 12 to the turbine-side housing member 2 t or the compressor-side housing member 2 c that supports the turbo cartridge 7 to rotate the rotating body 71.
- step S5 in FIG. 8 a vibration detection step for detecting vibration during rotation of the rotating body 71 is executed.
- the vibration signal S of the vibration generated due to the unbalance of the rotating body 71 is detected by the sound pressure sensor 4 installed in the turbo cartridge 7.
- the phase of the rotating body 71 may be detected at the same time as the vibration signal S is detected by the sound pressure sensor 4.
- the phase (rotation position) in one rotation of the rotating body 71 is obtained by irradiating light on a reflector plate installed on the blade of the turbine wheel Wt or the compressor wheel Wc and detecting the reflected light (signal). It is done.
- the sound pressure sensor 4 that can detect the vibration when the rotating body 71 is rotated by the above steps S3 to S5 measures the sound pressure generated by the vibration when the rotating body 71 is rotated in a non-contact manner. A measurement step is being executed.
- a cutting information calculation step for calculating cutting information is executed.
- the cutting information is information including a weight amount and a position optimum for balancing of the rotating body 71, which are calculated based on the signal detected in the vibration detection step (S5).
- the rotating body 71 is balanced by cutting the rotating body 71 based on the cutting information.
- This cutting information is calculated using the vibration signal S detected by the sound pressure sensor 4, the phase of the rotating body, and the effect vector.
- the effect vector is information indicating the relationship between the mass to be shaved (unit weight) and the change in the vibration magnitude associated therewith, and is obtained by conducting an experiment in advance on the same product as the turbo cartridge 7 during the balancing operation.
- the present invention is not limited to the above-described embodiments, and includes forms obtained by modifying the above-described embodiments and forms obtained by appropriately combining these forms.
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Abstract
Description
タービンホイールとコンプレッサホイールとをシャフトで結合した回転体と、前記回転体を回転可能に支持するベアリングを収容するベアリングハウジングと、からなるターボカートリッジにおける前記回転体のアンバランスを検出するためのアンバランス検出装置であって、
前記回転体の回転時における振動により生じる音圧を非接触で計測することにより、前記回転体の回転時における振動を検出可能な音圧センサを備える。
上記(1)の構成によれば、アンバランス検出装置は、マイクロフォンなどの音圧(音)の検出を行うための音圧センサを利用して、回転体の回転時の振動を検出するように構成される。回転体の回転時の振動は、非接触型の振動センサの有する分解能では適切に検出できないが、後述するように、音圧センサの有する分解能であれば検出が可能である。したがって、音圧センサによって、回転体の回転時の振動を適切に検出することができる。また、後述するように、振動絶縁部材を介してターボカートリッジをクランプ方式で支持した場合において、非接触型の音圧センサは、大量生産品のターボカートリッジの各々に対して取り付け、取り外しの作業を要せずに設置可能である。このため、音圧センサによって回転体の回転時に振動を検出することにより、アンバランス検出作業の効率化を図ることができる。
前記音圧センサは、特定方向からの音圧を収音することが可能な指向特性を有するマイクロフォンで構成されるか、あるいは、複数のマイクロフォンによりそれぞれ収音される音圧に基づいて前記特定方向からの音圧を計測するよう構成される。
上記(2)の構成によれば、音圧センサは、特定方向から到来する音圧を計測するように構成される。例えば、無指向特性のマイクロフォンを使用した場合には対象物以外からの音圧も収音してしまうが、これら対象物以外からの音圧は回転体の振動の検出にとっては外乱となる。このため、指向特性を有するマイクロフォンや、複数のマイクロフォンからの音圧を信号処理するなどにより、特定方向に絞って音圧を計測することができる。これによって、ターボカートリッジのベアリングハウジングから到来する音圧に絞って音圧を計測することで、回転体の回転時の振動の検出精度を高めることができる。
前記音圧センサの自己雑音レベルは50dB以下である。
上記(3)の構成によれば、音圧センサによって、回転体の回転時の振動を必要な分解能をもって適切に検出することができる。
前記タービンホイールを収容するタービン側ハウジング部材と、
前記コンプレッサホイールを収容するコンプレッサ側ハウジング部材と、
前記タービン側ハウジング部材および前記コンプレッサ側ハウジング部材の少なくとも一方を前記ターボカートリッジに向かって押圧することで、前記ターボカートリッジを両側から挟んで支持するように構成された支持機構と、
前記タービン側ハウジング部材と前記ターボカートリッジとの間、および、前記コンプレッサ側ハウジング部材と前記ターボカートリッジとの間にそれぞれ介在される振動絶縁部材と、をさらに備え、
前記特定方向は、前記ベアリングハウジングの位置する方向である。
上記(4)の構成によれば、ターボカートリッジは、振動絶縁部材を介して、タービン側ハウジング部材およびコンプレッサ側ハウジング部材によって両側から挟んだ状態で支持される。換言すれば、振動絶縁部材によって、アンバランス検出装置側とターボカートリッジ側との振動的な絶縁(伝達される振動の低減)が図られる。これによって、アンバランス検出作業において、回転体の回転時の振動に対するアンバランス検出装置側の共振を抑制することができる。また、共振の影響を受けていない状態の振動が、音圧センサによるベアリングハウジングからの音圧の計測を通して検出されることで、回転体のアンバランスの検出精度を高めつつ、バランシング作業の効率化を図ることができる。
前記ターボカートリッジは、前記タービン側ハウジング部材および前記コンプレッサ側ハウジング部材とは接触せずに、前記振動絶縁部材と接触した状態で、前記支持機構によって支持される。
上記(5)の構成によれば、ターボカートリッジは振動絶縁部材を介してのみ支持機構に接触する。このため、振動絶縁部材によって、アンバランス検出装置側とターボカートリッジ側との振動的な絶縁をより適切に図ることができる。
前記ベアリングハウジングの内部に潤滑油を供給するための給油配管であって、前記ベアリングハウジングに形成された給油口に対して接続および離間可能に構成された給油配管を、さらに備え、
前記音圧センサは、前記給油配管に固定される。
上記(6)の構成によれば、ベアリングハウジングの給油口に給油配管を接続した状態とした時には、ベアリングハウジングに対して音圧センサが設置された状態となるよう構成される。すなわち、ベアリングハウジングの給油口への給油配管の接続と、音圧センサの設置が連動する。これによって、ベアリングハウジングに音圧センサを効率良く設置することができ、アンバランス検出作業を効率良く行うことができる。
前記音圧センサは、前記給油配管が前記給油口に接続された状態において、前記ベアリングハウジングから所定距離だけ離間されるように、前記給油配管に固定される。
上記(7)の構成によれば、給油配管を給油口に接続することにより、ベアリングハウジングから離間した非接触の状態で音圧センサを設置することができる。
前記所定距離は、0.5mm~2.0mmである。
上記(8)の構成によれば、給油配管を給油口に接続することにより、回転体の振動検出に適した所定距離だけベアリングハウジングから離間した状態で音圧センサを設置することができ、回転体の回転時の振動を精度良く検出することができる。
前記ベアリングハウジングは、前記音圧センサが対面する平面状のセンシング面を有し、
前記センシング面は、前記給油口の開口面の法線方向と前記センシング面の法線方向とが一致するように設けられる。
上記(9)の構成によれば、センシング面の法線方向と給油口の開口面の法線方向とが一致するように、ベアリングハウジングにセンシング面が平面状に形成される。これによって、給油配管と給油口とが接続された状態にいて、音圧センサとセンシング面とを平行に対面させることができ、ベアリングハウジングからの音圧を良好に計測することができる。
前記音圧センサは、センサ側振動絶縁部材を介して前記給油配管に固定される。
上記(10)の構成によれば、センサ側振動絶縁部材によって、給油配管を振動伝達経路とした、音圧センサ側とアンバランス検出装置側との間の振動的な絶縁を図ることができる。これによって、振動センサによる回転体からの振動信号の検出精度を高めることができる。
前記センサ側振動絶縁部材はスポンジである。
上記(11)の構成によれば、音圧センサと給油配管とをスポンジを介して接続することで、給油配管を振動伝達経路とした、音圧センサ側とアンバランス検出装置側との間の振動的な絶縁を図ることができる。
タービンホイールとコンプレッサホイールとを回転軸で結合した回転体と、前記回転体を回転可能に支持するベアリングを収容するベアリングハウジングと、からなるターボカートリッジにおける前記回転体のアンバランスを検出するためのアンバランス検出方法であって、
前記回転体の前記タービンホイールを収容するタービン側ハウジング部材と前記ターボカートリッジとの間、および、前記回転体の前記コンプレッサホイールを収容するコンプレッサ側ハウジング部材と前記ターボカートリッジとの間にそれぞれ振動絶縁部材を介在させる振動絶縁部材設置ステップと、
前記タービン側ハウジング部材と前記コンプレッサ側ハウジング部材との少なくとも一方を、前記振動絶縁部材を介在させて、前記ターボカートリッジに向かって押圧することで、前記ターボカートリッジを両側から挟んで支持する支持ステップと、
前記回転体の回転時における振動を検出可能な音圧センサによって、前記回転体の回転時における振動により生じる音圧を非接触で計測する計測ステップと、を備える。
前記支持ステップは、前記タービン側ハウジング部材および前記コンプレッサ側ハウジング部材とは接触せずに、前記振動絶縁部材と接触した状態で前記ターボカートリッジを支持する。
上記(13)の構成によれば、上記(5)と同様に、振動絶縁部材によって、アンバランス検出装置側とターボカートリッジ側との振動的な絶縁をより適切に図ることができる。
前記ベアリングハウジングに形成された給油口に、前記ベアリングハウジングの内部に潤滑油を供給するための給油配管を接続することで、前記ベアリングハウジングから所定距離だけ離間されるように、前記給油配管に前記音圧センサを固定するセンサ固定ステップを、さらに備える。
上記(14)の構成によれば、上記(7)と同様に、給油配管を給油口に接続することにより、ベアリングハウジングから離間した非接触の状態で音圧センサを設置することができる。
前記所定距離は、0.5mm~2.0mmである。
上記(15)の構成によれば、上記(8)と同様に、給油配管を給油口に接続することにより、回転体の振動検出に適した所定距離だけベアリングハウジングから離間した状態で音圧センサを設置することができ、回転体の回転時の振動を精度良く検出することができる。
例えば、「ある方向に」、「ある方向に沿って」、「平行」、「直交」、「中心」、「同心」或いは「同軸」等の相対的或いは絶対的な配置を表す表現は、厳密にそのような配置を表すのみならず、公差、若しくは、同じ機能が得られる程度の角度や距離をもって相対的に変位している状態も表すものとする。
例えば、「同一」、「等しい」及び「均質」等の物事が等しい状態であることを表す表現は、厳密に等しい状態を表すのみならず、公差、若しくは、同じ機能が得られる程度の差が存在している状態も表すものとする。
例えば、四角形状や円筒形状等の形状を表す表現は、幾何学的に厳密な意味での四角形状や円筒形状等の形状を表すのみならず、同じ効果が得られる範囲で、凹凸部や面取り部等を含む形状も表すものとする。
一方、一の構成要素を「備える」、「具える」、「具備する」、「含む」、又は、「有する」という表現は、他の構成要素の存在を除外する排他的な表現ではない。
図1~図3に示されるように、アンバランス検出装置1は、タービン側ハウジング部材2tと、コンプレッサ側ハウジング部材2cと、支持機構3と、上述した音圧センサ4と、振動絶縁部材5と、を備える。これらの、アンバランス検出装置1が備える構成について、それぞれ説明する。
以下、図8のフローに従って、アンバランス検出方法を説明する。
12 送風機
13 空気供給配管
14 給油配管
15 連結部材
2c コンプレッサ側ハウジング部材
2t タービン側ハウジング部材
3 支持機構
31 コンプレッサ側支持機構
32 タービン側支持機構
33 押圧装置
34 押圧ロッド
35 ピストン装置
36 支持アーム
4 音圧センサ
41 収音部
42 収音面
5 振動絶縁部材
7 ターボカートリッジ
71 回転体
72 ベアリングハウジング
72b ベアリング
72p 支持受部
72v センシング面
73 給油口
8 センサ側振動絶縁部材
91 配管用振動絶縁部材
92 支持機構用振動絶縁部材
93 給油配管用振動絶縁部材
Wc コンプレッサホイール
Wt タービンホイール
M 回転軸
Ew ホイール用開口
Eg 空気用開口
Egi 入口側空気用開口
Ego 出口側空気用開口
N アンバランス検出回転数
V 振動特性
Vp ピーク振動数
Vr 振動特性(比較例)
Vrp ピーク振動数(比較例)
F1 下限振動数
F2 上限振動数
L 所定距離
P 音圧
S 振動信号
v 振動速度
a 振動加速度
x 振動変位
λ 振動波長
Lp 音圧レベル
Claims (15)
- タービンホイールとコンプレッサホイールとをシャフトで結合した回転体と、前記回転体を回転可能に支持するベアリングを収容するベアリングハウジングと、からなるターボカートリッジにおける前記回転体のアンバランスを検出するためのアンバランス検出装置であって、
前記回転体の回転時における振動により生じる音圧を非接触で計測することにより、前記回転体の回転時における振動を検出可能な音圧センサを備えることを特徴とするアンバランス検出装置。 - 前記音圧センサは、特定方向からの音圧を収音することが可能な指向特性を有するマイクロフォンで構成されるか、あるいは、複数のマイクロフォンによりそれぞれ収音される音圧に基づいて前記特定方向からの音圧を計測するよう構成されることを特徴とする請求項1に記載のアンバランス検出装置。
- 前記音圧センサの自己雑音レベルは50dB以下であることを特徴とする請求項1または2に記載のアンバランス検出装置。
- 前記タービンホイールを収容するタービン側ハウジング部材と、
前記コンプレッサホイールを収容するコンプレッサ側ハウジング部材と、
前記タービン側ハウジング部材および前記コンプレッサ側ハウジング部材の少なくとも一方を前記ターボカートリッジに向かって押圧することで、前記ターボカートリッジを両側から挟んで支持するように構成された支持機構と、
前記タービン側ハウジング部材と前記ターボカートリッジとの間、および、前記コンプレッサ側ハウジング部材と前記ターボカートリッジとの間にそれぞれ介在される振動絶縁部材と、をさらに備え、
前記特定方向は、前記ベアリングハウジングの位置する方向であることを特徴とする請求項2に記載のアンバランス検出装置。 - 前記ターボカートリッジは、前記タービン側ハウジング部材および前記コンプレッサ側ハウジング部材とは接触せずに、前記振動絶縁部材と接触した状態で、前記支持機構によって支持されることを特徴とする請求項4に記載のアンバランス検出装置。
- 前記ベアリングハウジングの内部に潤滑油を供給するための給油配管であって、前記ベアリングハウジングに形成された給油口に対して接続および離間可能に構成された給油配管を、さらに備え、
前記音圧センサは、前記給油配管に固定されることを特徴とする請求項1~5のいずれか1項に記載のアンバランス検出装置。 - 前記音圧センサは、前記給油配管が前記給油口に接続された状態において、前記ベアリングハウジングから所定距離だけ離間されるように、前記給油配管に固定されることを特徴とする請求項6に記載のアンバランス検出装置。
- 前記所定距離は、0.5mm~2.0mmであることを特徴とする請求項7に記載のアンバランス検出装置。
- 前記ベアリングハウジングは、前記音圧センサが対面する平面状のセンシング面を有し、
前記センシング面は、前記給油口の開口面の法線方向と前記センシング面の法線方向とが一致するように設けられることを特徴とする請求項6~8のいずれか1項に記載のアンバランス検出装置。 - 前記音圧センサは、センサ側振動絶縁部材を介して前記給油配管に固定されることを特徴とする請求項6~9のいずれか1項に記載のアンバランス検出装置。
- 前記センサ側振動絶縁部材はスポンジであることを特徴とする請求項10に記載のアンバランス検出装置。
- タービンホイールとコンプレッサホイールとを回転軸で結合した回転体と、前記回転体を回転可能に支持するベアリングを収容するベアリングハウジングと、からなるターボカートリッジにおける前記回転体のアンバランスを検出するためのアンバランス検出方法であって、
前記回転体の前記タービンホイールを収容するタービン側ハウジング部材と前記ターボカートリッジとの間、および、前記回転体の前記コンプレッサホイールを収容するコンプレッサ側ハウジング部材と前記ターボカートリッジとの間にそれぞれ振動絶縁部材を介在させる振動絶縁部材設置ステップと、
前記タービン側ハウジング部材と前記コンプレッサ側ハウジング部材との少なくとも一方を、前記振動絶縁部材を介在させて、前記ターボカートリッジに向かって押圧することで、前記ターボカートリッジを両側から挟んで支持する支持ステップと、
前記回転体の回転時における振動を検出可能な音圧センサによって、前記回転体の回転時における振動により生じる音圧を非接触で計測する計測ステップと、を備えることを特徴とするアンバランス検出方法。 - 前記支持ステップは、前記タービン側ハウジング部材および前記コンプレッサ側ハウジング部材とは接触せずに、前記振動絶縁部材と接触した状態で前記ターボカートリッジを支持することを特徴とする請求項12に記載のアンバランス検出方法。
- 前記ベアリングハウジングに形成された給油口に、前記ベアリングハウジングの内部に潤滑油を供給するための給油配管を接続することで、前記ベアリングハウジングから所定距離だけ離間されるように、前記給油配管に前記音圧センサを固定するセンサ固定ステップを、さらに備えることを特徴とする請求項12または13に記載のアンバランス検出方法。
- 前記所定距離は、0.5mm~2.0mmであることを特徴とする請求項14に記載のアンバランス検出方法。
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JP2001074547A (ja) * | 1999-07-05 | 2001-03-23 | Nippon Densan Corp | 特性表示方法、特性表示システムおよび特性表示プログラムを記憶した記録媒体 |
EP2581553A1 (de) * | 2011-10-11 | 2013-04-17 | Schenck RoTec GmbH | Verfahren und Vorrichtung zum dynamischen Messen der Unwucht des Rotors einer Turbolader-Rumpfgruppe |
JP2014215160A (ja) * | 2013-04-25 | 2014-11-17 | トヨタ自動車株式会社 | 過給機のバランス修正装置およびバランス修正方法 |
Cited By (4)
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WO2020049680A1 (ja) * | 2018-09-06 | 2020-03-12 | 三菱重工エンジン&ターボチャージャ株式会社 | 振動絶縁保持装置 |
JPWO2020049680A1 (ja) * | 2018-09-06 | 2021-05-13 | 三菱重工エンジン&ターボチャージャ株式会社 | 振動絶縁保持装置 |
JP7045470B2 (ja) | 2018-09-06 | 2022-03-31 | 三菱重工エンジン&ターボチャージャ株式会社 | 振動絶縁保持装置 |
US11808655B2 (en) | 2018-09-06 | 2023-11-07 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Vibration isolation holding device |
Also Published As
Publication number | Publication date |
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EP3447264A4 (en) | 2019-05-08 |
CN109477424B (zh) | 2021-02-02 |
EP3447264B1 (en) | 2020-07-08 |
JP6625209B2 (ja) | 2019-12-25 |
JPWO2017203649A1 (ja) | 2019-02-21 |
US20190212220A1 (en) | 2019-07-11 |
EP3447264A1 (en) | 2019-02-27 |
US11187608B2 (en) | 2021-11-30 |
CN109477424A (zh) | 2019-03-15 |
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