KR102320557B1 - Apparatus for Testing Air Foil Bearings - Google Patents

Abstract

The present invention relates to a bearing test apparatus capable of evaluating the performance of an airfoil bearing using a commercial turbocharger, and relates to a rotational drive unit that generates rotational force by hydraulic pressure of a gas, a bearing test unit that measures the torque of the test bearing, and the bearing a load applying unit for applying an axial load to the test unit, wherein the bearing test unit includes a rotating part on which the test bearing is disposed, a shaft extending in the rotational axis direction of the rotating part, a plurality of radial bearings supporting the shaft, and It relates to an air foil bearing test apparatus comprising a torque measuring unit for measuring the torque of the test bearing.

Description

Air Foil Bearing Testing Apparatus {Apparatus for Testing Air Foil Bearings}

The present invention relates to an airfoil bearing testing apparatus, and more particularly, to a testing apparatus for evaluating the floating characteristics and durability of an axial airfoil bearing.

In general, a bearing is used as a means for fixing a rotating shaft and supporting a load applied to the shaft.

A thrust bearing is a bearing for supporting a load applied in an axial direction, and a journal bearing is a bearing for supporting a side of the shaft. In general, journal bearings have a shaft hole formed in the center and inserted into the bearing housing, and the shaft is inserted and supported in the shaft hole of the journal bearing. At this time, the supplied oil is applied between the shaft hole and the shaft to form an oil film, whereby the shaft can rotate smoothly with respect to the journal bearing.

However, with the development of machinery, the rotational speed required for the shaft is gradually increasing at a high speed, and as a bearing supporting the rotational shaft of a high-speed rotating device such as a compressor, a turbine, a supercharger, etc., it does not use oil and is a fluid in the air or gas state. The use of so-called 'gas bearing', which uses as a working fluid, is expanding.

An air foil bearing is a type of gas bearing that uses air as a lubricant to support rotation, and supports a rotating body and a load by dynamic pressure generated by relative motion between a rotating body and a foil. Airfoil bearings maintain a non-contact state with the shaft during high-speed rotation to minimize friction and wear, and they do not require lubricating means such as oil, so they are easy to manage, have a simple structure, and produce less heat and noise.

Since the airfoil bearing can rotate at a high speed, it can be used as a bearing for a small or light turbo machine, and can be used in various fields such as a turbocharger, a gas compressor, a turbo blower, and an air cycle machine.

However, due to the relatively low load bearing capacity compared to rolling elements and oil-lubricated bearings, performance analysis and experimental performance verification are essential for application to high-speed rotating equipment.

Accordingly, the development of a device capable of evaluating the performance of an airfoil bearing is requested, and the prior art (Korean Patent Registration No. 10-1408330) rotates a rotating part with a motor to simulate an airfoil bearing in an actual high-temperature turbine-like environment. A test apparatus for airfoil bearings to evaluate the lubrication and cooling performance of airfoil bearings was proposed.

However, in the prior art, it is impossible to evaluate the performance of one axial bearing, and it is difficult to obtain sufficient data because the evaluation of the lubrication performance of the bearing depends only on temperature.

That is, an economical and reliable test apparatus for evaluating the floating speed and durability of an airfoil bearing used in a device that rotates at a high speed has not yet been developed.

Korean Patent Registration 10-1408330

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An object of the present invention is to provide a test apparatus capable of evaluating the levitation characteristics and durability of one axial airfoil bearing in order to solve the above problems.

Another object of the present invention is to provide an airfoil bearing testing apparatus having a structure for accurately measuring the torque of a bearing.

The problems of the present invention are not limited to the problems mentioned above, and other problems not mentioned will be clearly understood by those skilled in the art from the following description.

In order to achieve the above object, the airfoil bearing testing apparatus according to the present invention includes a rotational driving part that generates a rotational force by hydraulic pressure of a gas, a bearing test part and a load applying part for applying an axial load to the bearing test part, The bearing test part is composed of a rotating part in which the test bearing is disposed, a shaft extending in the direction of the rotation axis of the rotating part, a plurality of radial bearings supporting the shaft, and a torque measuring part measuring the torque of the test bearing.

An airfoil bearing testing apparatus according to the present invention includes a rotational driving unit corresponding to a turbine unit of a turbocharger.

The airfoil bearing test apparatus according to the present invention includes a bearing test part corresponding to the impeller part of a turbocharger.

The airfoil bearing testing apparatus according to the present invention includes a radial bearing composed of a static pressure bearing symmetrically disposed around a torque measuring unit.

The airfoil bearing test apparatus according to the present invention includes a housing forming the exterior of the rotating part, a thrust runner mounted inside the housing and connected to the rotation shaft of the rotating driving unit, and a test bearing mounted inside the housing to contact the test bearing. and a rotating part configured as a bearing support.

The test bearing of the airfoil bearing testing apparatus according to the present invention is an air foil disposed between a bearing support and a thrust runner, and comprising a disk-shaped bearing disk, a back foil attached to the bearing disk, and a top foil covering the back foil. It consists of bearings.

The airfoil bearing test apparatus according to the present invention includes a bearing support in which a cooling hole is formed for lowering the temperature of the bearing test part by injecting an external gas into the side surface.

The airfoil bearing test apparatus according to the present invention includes a housing in which a supply hole for supplying an external gas to a cooling hole and a sensor hole in which a gap sensor is installed, the sensor hole is disposed closer to the rotational driving part than the supply hole do.

The airfoil bearing test apparatus according to the present invention includes a load cell, a torque head that comes into contact with the load cell and applies pressure to the load cell, and a torque arm having one end connected to the torque head and the other end inserted into the shaft and fixed. includes wealth.

The airfoil bearing test apparatus according to the present invention includes a load cell having one surface attached to the load cell support and a torque box extending from the center of the shaft to the center of the load cell in a radial direction.

The airfoil bearing test apparatus according to the present invention includes a speed sensor for measuring the rotational speed of the rotational driving unit.

The airfoil bearing test apparatus according to the present invention further includes a control unit for obtaining torque information of the test bearing according to the rotational speed of the rotary driving unit.

The details of other embodiments are included in the detailed description and drawings.

According to an embodiment of the present invention, there are one or more of the following effects.

First, by arranging the axial airfoil bearing in the rotating part, there is an effect of enabling the performance evaluation of one bearing.

Second, as the length of the rotating shaft is reduced, the rotating shaft can be rotated at a higher speed.

Third, by implementing the radial bearing through the static pressure bearing, the torque of the bearing can be measured more accurately.

Effects of the present invention are not limited to the effects mentioned above, and other effects not mentioned will be clearly understood by those skilled in the art from the description of the claims.

1 is a view illustrating a compressor to which an airfoil bearing is applied.
2A to 2B are views illustrating a journal bearing and a thrust bearing.
3 is a diagram illustrating a typical turbocharger.
4A to 4D are views showing an airfoil bearing testing apparatus according to an embodiment of the present invention.
5 is a view showing the floating characteristics of the test bearing according to an embodiment of the present invention.
6 to 7D are views showing a rotating part according to an embodiment of the present invention.
8A to 9B are views showing a torque measuring unit according to an embodiment of the present invention.
10 is a diagram illustrating a load application unit according to an embodiment of the present invention.
11 is a view for explaining that the pulley changes the direction of the force according to an embodiment of the present invention.
12A to 12B are diagrams illustrating movement of a moving unit according to an embodiment of the present invention.
13 is a block diagram of a control unit of an airfoil bearing testing apparatus according to an embodiment of the present invention.

Advantages and features of the present invention and methods of achieving them will become apparent with reference to the embodiments described below in detail in conjunction with the accompanying drawings. However, the present invention is not limited to the embodiments disclosed below, but may be implemented in various different forms, and only these embodiments allow the disclosure of the present invention to be complete, and common knowledge in the art to which the present invention pertains It is provided to fully inform those who have the scope of the invention, and the present invention is only defined by the scope of the claims. Like reference numerals refer to like elements throughout.

Spatially relative terms "below", "beneath", "lower", "above", "upper", etc. It can be used to easily describe the correlation between components and other components. Spatially relative terms should be understood as terms including different orientations of components in use or operation in addition to the orientation shown in the drawings. For example, when a component shown in the drawings is turned over, a component described as “beneath” or “beneath” of another component may be placed “above” of the other component. can Accordingly, the exemplary term “below” may include both directions below and above. Components may also be oriented in other orientations, and thus spatially relative terms may be interpreted according to orientation.

The terminology used herein is for the purpose of describing the embodiments and is not intended to limit the present invention. As used herein, the singular also includes the plural unless specifically stated otherwise in the phrase. As used herein, "comprises" and/or "comprising" means that a referenced component, step and/or action excludes the presence or addition of one or more other components, steps and/or actions. I never do that.

Unless otherwise defined, all terms (including technical and scientific terms) used herein may be used with the meaning commonly understood by those of ordinary skill in the art to which the present invention belongs. In addition, terms defined in a commonly used dictionary are not to be interpreted ideally or excessively unless clearly specifically defined.

In the drawings, the thickness or size of each component is exaggerated, omitted, or schematically illustrated for convenience and clarity of description. In addition, the size and area of each component do not fully reflect the actual size or area.

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.

Hereinafter, the present invention will be described with reference to the drawings for explaining the bearing test apparatus according to the embodiments of the present invention.

1 is a view illustrating a compressor to which an airfoil bearing is applied.

Airfoil bearings 50 and 60 according to an embodiment of the present invention are installed in a mechanical device provided with a rotating shaft rotating at high speed. The airfoil bearings 50 and 60 are a concept including a journal bearing 50 installed in a radial direction with respect to the rotation shaft 20 and a thrust bearing 60 installed in an axial direction.

In this specification, for convenience, the airfoil bearings 50 and 60 are installed to support the rotation shaft 20 of the compressor 10 as an example. However, this description is only one example, and may be applied to any machine having a rotating shaft.

Referring to FIG. 1 , the compressor 10 according to the embodiment may function as a part of a chiller system.

The chiller system includes a compressor (10) formed to compress a refrigerant, a condenser for condensing the refrigerant by exchanging heat with the refrigerant compressed in the compressor (10), an expander for expanding the refrigerant condensed in the condenser, and the refrigerant expanded from the expander and cold water. and an evaporator configured to cool the cold water with evaporation of the refrigerant by heat exchange.

The compressor 10 according to FIG. 1 includes one or more impellers 40 for sucking refrigerant in the axial direction (Ax) and compressing it in the centrifugal direction, a rotation shaft 20 to which a motor 30 for rotating the impeller 40 is connected; A plurality of journal bearings 50 supporting the rotary shaft 20 to be rotatable in the air, bearing housings 52 and 54 supporting the journal bearing 50, and a gap sensor (not shown) for detecting the distance between the rotary shaft 20 time) and the rotation shaft 20 may include a thrust bearing 60 for limiting vibration in the axial direction Ax.

The impeller 40 is generally composed of one stage or two stages, and may be composed of a plurality of stages. It rotates by the rotating shaft 20 and compresses the refrigerant flowing in the axial direction (Ax) by rotation in the centrifugal direction, thereby making the refrigerant high pressure.

The motor 30 may include a stator (not shown) and a rotor 22 to rotate the rotating shaft 20 . The rotating shaft 20 is connected to the impeller 40 and the motor 30 , and the rotating shaft 20 may extend in the left and right directions of FIG. 1 . Hereinafter, the axial direction Ax of the rotation shaft 20 means a left-right direction.

A plurality of journal bearings 50 are provided to surround the rotary shaft 20 with the rotary shaft 20 as a center, and the thrust bearing 60 is a rotary shaft blade 21 provided to extend in a rotational radial direction of the rotary shaft 20 . It may be provided adjacent to.

When the rotary shaft 20 rotates, the journal bearing 50 can rotate without friction in a state suspended in the air. To this end, at least two or more journal bearings 50 may be provided around the rotation shaft 20 .

A plurality of journal bearings 50 are provided, and may be installed with a gap so as not to contact the rotation shaft 20 . Referring to FIG. 1 , the first journal bearing 51 and the second journal bearing 53 may be installed to be spaced apart from each other about the rotation shaft 20 .

The journal bearing 50 may be installed at at least two points of the rotation shaft 20 . The two points correspond to different points along the longitudinal direction of the rotation shaft 20 . Since the rotation shaft 20 corresponds to a straight line, it is necessary to support the rotation shaft 20 at at least two points to prevent vibration in the circumferential direction.

Meanwhile, the compressor 10 may further include bearing housings 52 and 54 supporting the journal bearing 50 . The first bearing housing 52 may support the first journal bearing 51 , and the second bearing housing 54 may support the second journal bearing 53 .

The thrust bearing 60 may have a constant area in a plane perpendicular to the axial direction Ax in order to prevent vibration in the axial direction Ax (left and right direction) of the rotation shaft 20 .

Specifically, the rotary shaft 20 may further include a rotary shaft blade 21 capable of moving the rotary shaft 20 by the thrust of the thrust bearing 60 . The rotary shaft blade 21 may have a larger area than the cross-sectional area of the rotary shaft 20 in a plane perpendicular to the axial direction Ax. The rotary shaft blade 21 may be formed to extend in a rotational radial direction of the rotary shaft 20 .

The thrust bearing 60 limits the movement of the rotary shaft 20 in the axial direction (Ax) vibration, and when the surge occurs, the rotary shaft 20 moves in the impeller 40 direction, and the other configuration of the compressor 10 and It is possible to prevent the rotation shaft 20 from moving.

Specifically, the thrust bearing 60 includes a first thrust bearing 61 and a second thrust bearing 62 , and is disposed to surround the rotary shaft wing 21 in the axial direction Ax of the rotary shaft 20 . can That is, in the axial direction Ax of the rotating shaft 20 , the first thrust bearing 61 , the rotating shaft blade 21 , and the second thrust bearing 62 may be disposed in this order.

The first thrust bearing 61 is located closer to the impeller 40 than the second thrust bearing 62, and the second thrust bearing 62 is located farther from the impeller 40 than the first thrust bearing, and At least a portion of the rotation shaft 20 may be positioned between the first thrust bearing 61 and the second thrust bearing 62 . Preferably, the rotary shaft blade 21 may be positioned between the first thrust bearing 61 and the second thrust bearing 62 .

Therefore, the first thrust bearing 61 and the second thrust bearing 62 have an effect of minimizing the vibration of the rotary shaft 20 in the direction of the rotary shaft 20 by the operation of the rotary shaft blade 21 and thrust.

On the other hand, looking at the flow of the refrigerant, the refrigerant introduced into the compressor 10 from the evaporator through the inlet passage 70 is compressed in the circumferential direction by the action of the impeller 40 and then discharged to the condenser through the discharge passage 80 . can be The inflow passage 70 may be connected to the compressor 10 so that the refrigerant may be introduced in a direction perpendicular to the rotation direction of the impeller 40 .

2A to 2B are views illustrating a journal bearing and a thrust bearing.

2A is a cross-sectional view of a journal bearing 50 which is a bearing for supporting the side of the shaft among the airfoil bearings. That is, the journal bearing 50 may support the radial load of the rotating shaft.

Referring to FIG. 2A , the journal bearing 50 includes a hollow bearing housing 55 into which a rotation shaft 20 or a shaft is inserted, and between the inner surface of the bearing housing 55 and the rotation shaft 20 . foils 56 and 57 may be included.

The foils 56 and 57 are made of a top foil 56 on the inner circumference side and a back foil on the outer circumference side, and the back foil may be a bump foil 57 formed by forming a thin plate into a corrugated plate shape. In addition, one end of the top foil 56 and the bump foil 57 may be fixed to the inner surface of the bearing housing 55 to prevent dropping, and the other end may be configured as a free end.

When the rotating shaft 20 rotates, a fluid lubricating film is formed between the rotating shaft 20 and the foils 56 and 57 , so that the journal bearing 50 may rotatably support the rotating shaft 20 .

When the rotating shaft 20 rotates, a fluid lubricating film is formed between the top foil 56 and the rotating shaft 20, and the load acting on the rotating shaft 20 pushes the top foil 56 through the fluid lubricating film and tries to deform it, Since the top foil 56 is elastically supported by the bump foil 57, the amount of deformation thereof may be appropriately limited.

In addition, when the top foil 56 deforms, the bump foil 57 deforms to widen the pitch of the individual waves, thereby causing a slip between the top foil 56 and the bump foil 57, but the rotation shaft 20 Since vibration energy is dispersed and disappears due to friction caused by the sliding when vibration occurs, there is an effect of suppressing vibration of the rotating shaft 20 .

According to FIG. 2A , the journal bearing 50 in the present invention has been specified to include a bearing housing 55 , a top foil 56 and a bump foil 57 , but is not limited thereto. In addition, various known structures It can be adopted as any one of the journal bearings with

2B is a perspective view of the thrust bearing 60, which is a bearing for supporting a load applied in the axial direction among the airfoil bearings.

Referring to FIG. 2B , the thrust bearing 60 may have a form in which a back foil is attached to a disk-shaped bearing disk 64 and covered with a top foil 66 again. The back foil may be a bump foil 67 formed by forming a thin plate into a corrugated plate shape. A circular hole into which the rotation shaft 20 is inserted may be formed in the center of the thrust bearing 60 .

The top foil 66 may be formed as a free end having one end fixed to the bearing disk 64 and the other end being spaced apart from the bearing disk 64 and deformed. The bump foil 67 may be formed in a fan-shaped plate shape, and may be in contact with the top foil 66 between a fixed end and a free end of the top foil 66 .

Hereinafter, the principle of the thrust bearing 60 supporting the axial load is the same as the journal bearing 50 of FIG. 2A .

Airfoil bearings 50 and 60 can be used in small or light high-speed rotating machines due to their advantages such as high high-speed stability, low operating friction loss, and the need for a separate oil refueling system. , can be used in various fields such as an air cycle machine.

However, due to its relatively low load bearing capacity compared to rolling elements and oil-lubricated bearings, performance analysis and experimental performance verification are essential for application to high-speed rotating equipment.

A typical airfoil bearing test device uses a motor that can rotate at high speed for performance evaluation. However, when a high-speed motor is used, the rotation drive unit and the rotation unit are separately configured, thereby increasing the total length of the total rotation shaft. As a result, as the total length of the rotating shaft increases, the bending mode of the rotating shaft occurs at a low speed, making it difficult to rotate at a high speed. Also, if a high-speed motor is used, the device configuration is expensive.

Therefore, by configuring the bearing test apparatus 100 using a commercial turbocharger, it is possible to minimize the length of the total rotation shaft and reduce the cost when configuring the apparatus.

Hereinafter, the specification describes an airfoil bearing testing apparatus using a turbocharger, in particular a thrust bearing testing apparatus.

3 is a diagram illustrating a typical turbocharger.

Referring to FIG. 3 , the turbocharger 300 according to an embodiment of the present invention may include a body 310 and a rotating body 320 .

The main body 310 includes a compression chamber 311 for compressing the introduced air, a turbine chamber 312 for sucking the high-temperature and high-pressure exhaust gas burned in the engine E, a compression chamber 311 and a turbine chamber 312 . It may include an installation pipe 313 in which the rotating body 320 and the bearing 322 are installed.

The rotating body 320 may include a rotating shaft 321 , an impeller 323 , and a turbine 324 .

The rotating shaft 321 is installed in the installation pipe 313 of the main body 310 by connecting the impeller 323 and the turbine 324 and inserting the bearing 322 .

The turbine 324 is installed at one end of the rotating shaft 321 and installed in the turbine chamber 312 of the main body 310 , the high-temperature and high-pressure exhaust gas burned in the engine E rotates the turbine 324 , the rotating shaft The impeller 323 installed at the other end of the 321 is rotated.

The impeller 323 is installed at the other end of the rotating shaft 321 and installed in the compression chamber 311 of the main body 310 , and the impeller 323 rotates while the turbine 324 rotates. Accordingly, air is introduced through the intake port, the air is compressed by the rotation of the impeller 323, the compressed air is supplied to the engine (E).

Accordingly, the engine (E) supplied with the compressed air increases the output. A detailed description thereof will be omitted since the description thereof is well-known.

The A-foil bearing test apparatus 100 according to an embodiment of the present invention may be configured through the rotating body 320 of the turbocharger 300 . That is, the airfoil bearing test apparatus 100 uses the turbine 324 as the rotational driving unit 110, and installs the bearing test unit 120 instead of the impeller 323 to transmit the rotational force by the rotating shaft 116. have.

4A to 4D are views showing an airfoil bearing testing apparatus according to an embodiment of the present invention.

4A to 4B are perspective views of an airfoil bearing testing apparatus 100 according to an embodiment of the present invention.

4A to 4B , the airfoil bearing testing apparatus 100 according to an embodiment of the present invention includes a rotational driving unit 110 that generates a rotational force by hydraulic pressure of a gas, a torque of the test bearing 121 and It may include a bearing test part 120 for measuring the temperature and a load part 140 for applying an axial load to the bearing test part 120 .

The rotation driving unit 110 may correspond to the turbine unit of the turbocharger. The rotary driving unit 110 may use the turbine 324 of the turbocharger 300 as shown in FIG. 3 as it is. In other words, the rotation driving unit 110 may include the turbine 324 of the turbocharger 300 . In addition, the rotation driving unit 110 may further include a rotation shaft 321 of the turbocharger 300 .

The bearing test unit 120 may correspond to the impeller unit of the turbocharger. The bearing test unit 120 may remove the impeller of the turbocharger and be disposed to correspond to the position of the impeller. That is, the bearing test unit 120 may be disposed at the position of the impeller 323 in the turbocharger 300 as shown in FIG. 3 .

In other words, the airfoil bearing test apparatus 100 utilizes the rotating body 320 of the commercial turbocharger 300 , and uses the turbine 324 of the turbocharger 300 as the rotational driving unit 110 , and the impeller The bearing test unit 120 located instead of 323 may be used.

The bearing test unit 120 may measure the torque and temperature of the test bearing 121 disposed therein. Specifically, the bearing test unit 120 includes a rotating unit 600 on which the test bearing 121 is disposed, a shaft 126 extending in a direction of a rotation axis of the rotating unit 600 , and a plurality of radii supporting the shaft 126 . It may include a radial bearing 128 and a torque measuring unit 130 measuring the torque of the test bearing 121 . A temperature sensor for measuring the temperature of the test bearing 121 may be attached to one surface of the test bearing 121 .

The load applying unit 140 is disposed to be spaced apart from the bearing test unit 120 , and may apply a load to the bearing test unit 120 in an axial direction. Specifically, the load-applying unit 140 includes an axial bearing (thrust bearing, 141) disposed to be spaced apart from the bearing test unit 120, a supporting unit 143 supporting the axial bearing 141, and the supporting unit ( It may include a moving unit 144 for moving the 143).

The airfoil bearing testing apparatus 100 according to an embodiment of the present invention may further include a base 150 supporting the rotational driving unit 110 , the bearing testing unit 120 , and the load applying unit 140 . . An LM guide may be installed on the base 150 , and the load-applying unit 140 may move in the axial direction through the LM guide.

The airfoil bearing test apparatus 100 according to an embodiment of the present invention may further include a cooling pipe 160 that prevents the temperature of the bearing test unit 120 from rising due to frictional heat. The cooling pipe 160 may lower the temperature of the bearing test part 120 by injecting an external cold gas into the bearing test part 120 .

4C is a cross-sectional view of an airfoil bearing testing apparatus 100 according to an embodiment of the present invention.

Referring to FIG. 4C, the rotary drive unit 110 includes a turbine 111 that generates rotational force by hydraulic pressure, an inlet pipe 112 through which external gas is introduced, and a discharge pipe 113 through which the introduced gas is discharged. can

Looking at the inflow of gas, the gas is introduced into the inlet pipe 112 through a blower or the like from the outside, and the introduced gas turns the turbine 111 and is discharged to the outside through the discharge pipe 113 . The turbine 111 generates rotational force by the introduced gas, and the rotational force is transmitted to the rotation shaft 116 to rotate the bearing test unit 120 .

The rotation driving unit 110 may further include a pipe support unit 115 for supporting the discharge pipe 113 . A speed sensor 114 for measuring the rotational speed of the turbine 111 may be located in the discharge pipe 113 . For example, the speed sensor 114 may be a tachometer.

Referring to FIG. 4C , the bearing test unit 120 includes a rotating unit 600 in which the test bearing 121 is disposed, a shaft 126 extending in the direction of the rotation axis of the rotating unit 600 , and supporting the shaft 126 . A plurality of radial bearings 128 and a torque measuring unit 130 for measuring the torque of the test bearing 121 may be included.

The rotation unit 600 includes a housing 124 forming an exterior, a thrust runner 122 mounted inside the housing 124 and connected to the rotation shaft 116 of the rotation driving unit 110, the housing 124 It may include a bearing support 123 mounted therein to contact the test bearing 121 .

That is, the test bearing 121 may be disposed between the thrust runner 122 and the bearing support 123 . Specifically, the test bearing 121 is a thrust bearing, and one surface of the bearing support 123 may contact a bearing disk of the test bearing 121 . The trust runner 122 may be spaced apart from the test bearing 121 at a predetermined distance when it rotates at a predetermined speed or more while in contact with the top foil of the test bearing 121 .

The thrust runner 122 may include a hollow, and may be connected to the rotation shaft 116 of the rotation driving unit 110 through the hollow. When the rotating shaft 116 is rotated by the turbine 111 , the thrust runner 122 connected to the rotating shaft 116 may rotate. When the rotational speed of the trust runner 122 exceeds a certain speed, an air gap is created between the trust runner 122 and the test bearing 121 , and the trust runner 122 is spaced apart from the test bearing 121 . can

The shaft 126 may have a cylindrical structure that is connected to the rotation shaft 125 of the rotation unit 600 and extends in the direction of the rotation shaft 125 . At the center of the shaft 126 , a torque measuring unit 130 that measures a torque according to the rotation of the shaft 126 may be located. Shaft 126 may be supported by a plurality of radial bearings 128 .

The radial bearing 128 may be configured as a static pressure bearing, and may be symmetrically disposed around the torque measuring unit 130 to support the shaft 126 . The radial bearing 128 may not contact the shaft 126 and affect the rotation of the shaft 126 . That is, since the radial bearing 128 is a static pressure bearing, it can help the torque measuring unit 130 to accurately measure the torque.

The bearing test unit 120 may further include a rotating plate 127 disposed at one end of the shaft 126 and extending wider than a cross-sectional area of the shaft 126 in a rotational radius direction of the shaft 126 . The rotating plate 127 is connected to one end of the shaft 126, and may have a disk shape. The rotating part 600 may be present at the other end of the shaft 126 .

Referring to FIG. 4C , the load applying unit 140 includes an axial bearing 141 spaced apart from the bearing test unit 120 , a support unit 143 supporting the axial bearing 141 and the It may include a moving part 144 for moving the support part 143 .

The axial bearing 141 may be configured as a static pressure bearing. One surface of the axial bearing 141 may be spaced apart from one surface of the rotating plate 127 with a predetermined gap to face each other. That is, an air gap may exist between the axial bearing 141 and the rotating plate 127 , and the axial bearing 141 may be spaced apart from the rotating plate 127 by the air gap.

The axial bearing 141 may be connected to the support 143 by a ball screw 142 . The ball screw 142 may be connected to the axial bearing 141 through the upper end of the support part 143 .

A connection part 145 with the wire 146 may be located in the support part 143 . The connection part 145 may be disposed on the inner surface of the support part 143 . In the drawing, the connection part 145 is recessed into the support part 143 , but the present invention is not limited thereto. That is, the connection part 145 may have a structure derived from the support part 143 .

A moving part 144 may be disposed at a lower end of the support part 143 . The moving part 144 may be connected to the LM guide of the base 150 to move the support part 143 in the axial direction. Through the axial movement of the support part 143 through the moving part 144 , the load applying part 140 may apply a load to the bearing test part 120 in the axial direction.

FIG. 4D is a cross-sectional view of the rotational driving unit 110 according to an embodiment of the present invention as viewed from a plane A-A' in FIG. 4C.

Referring to FIG. 4D , an inlet pipe 112 is positioned at the lower end of the rotation driving unit 110 , and the gas introduced through the inlet pipe 112 may rotate the turbine 111 . The gas rotating the turbine 111 may be discharged to the outside through the discharge pipe 113 .

The airfoil bearing testing apparatus 100 according to an embodiment of the present invention may further include a speed sensor 114 for measuring the rotational speed of the rotational driving unit 110 . The speed sensor 114 may be installed on a portion of the rotation driving unit 110 to measure the rotation speed of the rotation driving unit 110 . For example, the speed sensor 114 may be a tachometer.

The airfoil bearing testing apparatus 100 according to an embodiment of the present invention may further include a control unit 170 electrically connected to the speed sensor 114 . The control unit 170 may be electrically connected to the torque measuring unit 130 as well as the speed sensor 114 .

The control unit 170 may receive rotation speed information of the rotation driving unit 110 from the speed sensor 114 . The control unit 170 may receive torque information of the test bearing 121 from the torque measuring unit 130 .

The control unit 170 may obtain information on the torque of the test bearing 121 according to the rotational speed of the rotational driving unit 110 based on the information obtained from the speed sensor 114 and the torque measuring unit 130 . .

5 is a view showing the floating characteristics of the test bearing according to an embodiment of the present invention.

When the rotation driving unit 110 rotates, the bearing test unit 120 may rotate by the rotating shaft 116 . Specifically, when the rotation driving unit 110 rotates, the trust runner 122 connected to the rotation shaft 116 rotates, and when the trust runner 122 rotates at a predetermined speed or higher, the trust runner 1220 is a test bearing 121 . At this time, the rotational speed of the rotational driving unit 110 is the floating speed of the test bearing 121 .

When the thrust runner 122 rotates at a speed lower than a certain speed, the thrust runner 122 generates frictional force on the contacting test bearing 121 . Torque of the test bearing 121 may be generated by frictional force generated while the thrust runner 122 rotates. That is, the torque of the test bearing 121 may be defined as a force that prevents rotation of the thrust runner 122 .

When the thrust runner 122 rotates at a speed lower than a predetermined speed, the test bearing 121 generates a torque, and the torque may be transmitted to the shaft 126 by the rotation shaft 125 . The torque transmitted to the shaft 126 may be transmitted to the load cell 133 through the torque arm 131 inserted into the shaft 126 .

A detailed description of the torque measuring unit 130 will be described later with reference to FIGS. 8A to 9B .

The control unit 170 may obtain information on the torque of the test bearing 121 according to the rotational speed of the rotational driving unit 110 based on the information obtained from the speed sensor 114 and the torque measuring unit 130 . .

The control unit 170 may output information about the torque of the test bearing 121 according to the obtained rotation speed of the rotational driving unit 110 . The rotation speed 510 of the rotation driving unit 110 may continuously increase. The torque 520 of the test bearing 121 may vary according to the rotation speed 510 .

Referring to FIG. 5 , as the rotation speed 510 increases, the torque 520 may increase and then decrease. In addition, the torque 520 is constant after a certain speed while decreasing, the control unit 170 may determine the rotational speed 510 at this time (540) as the floating speed (550). For example, in FIG. 5 , the controller 170 may determine the floating speed 550 of the test bearing 121 as 125 Hz.

As described above, in order to accurately measure the floating speed 550, it is necessary to make the load applied in the axial direction constant. Referring to FIG. 5 , the axial load 530 is constant. In order to apply a constant axial load, the load-applying part 140 may be used. The structure of the load-applying unit 140 will be described later with reference to FIG. 10 .

6 to 7D are views showing a rotating part according to an embodiment of the present invention.

Referring to FIG. 6 , the rotating unit 600 includes a housing 124 forming an exterior, and a thrust runner 122 mounted inside the housing 124 and connected to the rotating shaft 116 of the rotating driving unit 110 . , may include a bearing support 123 mounted inside the housing 124 to contact the test bearing 121 .

The test bearing 121 may be disposed between the thrust runner 122 and the bearing support 123 . The test bearing 121 may include an airfoil bearing including a disk-shaped bearing disk, a back foil attached to the bearing disk, and a top foil covering the back foil.

One surface of the bearing support 123 may be in contact with one surface of the bearing disk. When one surface of the bearing support 123 and one surface of the bearing disk come into contact to generate frictional force, the torque of the test bearing 121 may be transmitted to the shaft 126 .

A cooling hole 610 for lowering the temperature of the bearing test unit 120 by injecting an external gas may be formed on a side surface of the bearing support unit 123 . A plurality of cooling holes 610 may exist along the side surface of the bearing support 123 .

A supply hole 620 for supplying an external gas to the cooling hole 610 and a sensor hole 630 in which a gap sensor is installed may be formed on a side surface of the housing 124 . The sensor hole 630 may be disposed closer to the rotation driving unit 110 than the supply hole 620 .

A gap sensor may be installed in the sensor hole 630 . The gap sensor may measure the vibration of the trust runner 122 .

7A to 7D are exploded views of the rotating part 600 .

Referring to FIG. 7A , the bearing support 123 may have a cylindrical shape. Concave-convex portions 710 for heat generation may be formed on a side surface of the bearing support 123 . The concavo-convex portion 710 may have a larger cross-sectional area in contact with the air of the bearing support 123 to be effective in heat generation.

Referring to FIG. 7B , the test bearing 121 may include a disk-shaped bearing disk 720 , a back foil (not shown) attached to the bearing disk 720 , and a top foil 730 covering the back foil. can The bearing disk 720 may include a fastener 740 capable of being coupled to the bearing support 123 . In addition, a temperature sensor capable of measuring the temperature of the test bearing 121 may be attached to the bearing disk 720 .

Referring to FIG. 7C , the trust runner 122 may have a disk shape. A cylindrical protrusion 750 into which the rotation shaft 126 of the rotation driving unit 110 can be inserted may be formed in the center of the thrust runner 122 . The protrusion 750 includes a hollow, and the rotating shaft 126 may be inserted into the hollow.

Referring to FIG. 7D , a portion of the housing 124 may have a structure surrounded by a connection member 760 connected to the cooling pipe 160 . The connection member 710 may be disposed to surround the supply hole 620 of the housing 124 . The supply hole 620 may be disposed closer to the shaft 126 than the sensor hole 630 .

The cooling pipe 160 may inject an external gas into the housing 124 through the supply hole 620 . The external gas injected into the housing 124 may be introduced into the bearing support 123 through the cooling hole 610 . The cooling pipe 160 may be coupled to the fastener 720 of the connecting member 710 .

8A to 9B are views showing a torque measuring unit according to an embodiment of the present invention.

Referring to FIG. 8A , the torque measuring unit 130 includes a load cell 133 , a torque head 132 that comes into contact with the load cell 133 to apply pressure to the load cell 133 , and one end of the torque head 132 . It may include a torque arm 131 that is connected and the other end is inserted into the shaft 126 and fixed.

One side of the load cell 133 is attached and fixed to the load cell support 134 . The torque arm 131 extends from the center of the shaft 126 to the center of the load cell 133 in a radial direction. A torque head 132 is coupled to one end of the torque arm 131 , and the torque head 132 applies a force to the load cell 133 in a vertical direction.

The load cell 133 may measure the force applied by the torque head 132 by the rotation of the torque arm 131 . The torque applied to the test bearing 121 is transmitted to the shaft 126 , and the torque arm 131 rotates by the torque. Accordingly, the torque head 132 may transmit the force while pressing the load cell 133 .

The load cell 133 may convert the measured force into an electrical signal and transmit it to the controller 170 . The controller 170 may be electrically connected to the load cell 133 , and may calculate a torque by obtaining force information from the load cell 133 .

Referring to FIG. 8B , the torque may be calculated as the product of the force F measured by the load cell 133 and the distance L from the center of the shaft 126 to the center of the load cell 133 . The distance L from the center of the shaft 126 to the center of the load cell 133 may be the same as or different from the length l of the torque arm 131 .

The length l of the torque arm 131 is a constant value. Therefore, if the length l of the torque arm 131 is equal to the distance L from the center of the shaft 126 to the center of the load cell 133 , the torque is equal to the force F measured by the load cell 133 and It may be calculated as a product of the length l of the torque arm 131 .

9A to 9B show exploded views of the torque arm 131 and the torque head 132 . A hole 920 capable of being coupled to one end of the torque arm 131 may exist on each surface of the torque head 132 . One surface 910 of the torque head 132 may be coupled to one end of the torque arm 131 through the hole 920 , and the other surface 930 may be in contact with the load cell 133 to apply a force to the load cell 133 . can

10 is a diagram illustrating a load application unit according to an embodiment of the present invention.

Referring to FIG. 10 , the load applying unit 140 includes an axial bearing 141 spaced apart from the bearing test unit 120 , a support unit 143 supporting the axial bearing 141 , and the It may include a moving part 144 for moving the support part 143 .

The axial bearing 141 may be configured as a static pressure bearing. One surface of the axial bearing 141 may be spaced apart from one surface of the rotating plate 127 with a predetermined gap to face each other. An air gap may exist between the axial bearing 141 and the rotating plate 127 , and the axial bearing 141 may be spaced apart from the rotating plate 127 by the air gap. The axial bearing 141 may not contact the rotating plate 127 and may not affect rotation of the rotating plate 127 . This may help the torque measuring unit 130 to accurately measure the torque.

The axial bearing 141 may be connected to the support 143 by a ball screw 142 . The ball screw 142 may be connected to the axial bearing 141 through the upper end of the support part 143 .

The load applying unit 140 should be applied to the wire 146 connected to the inner surface of the support unit 143 , the weight 147 connected to the wire 146 in the direction of gravity 1010 and the wire 146 . may further include pulleys 148 and 149 for changing the direction of the force.

The pulleys 148 and 149 may change the direction of the force applied to the wire 146 in the direction of gravity 1010 by the weight 147 to the axial direction 1020 . Although the direction of the force is changed using two pulleys in FIG. 10, one pulley may be used. In this case, a portion of the base 150 may have a hole through which the wire 146 may pass.

In other words, the number of pulleys is not limited to FIG. 10 , and the pulley may serve to change the direction of the force applied to the wire 146 from the gravitational direction 1010 to the axial direction 1020 .

Hereinafter, the specification will be described on the basis of changing the direction of the force using two pulleys (148, 149).

The wire 146 may be connected to the inner surface of the support 143 to pass through the bearing support 129 . A through hole 1030 through which the wire 146 passes is installed in the bearing support 129 , and the wire 146 passes through the through hole 1030 to the inner surface of the support 143 and the axial direction 1020 . can be connected The wire 146 may apply a force to the support 143 in the axial direction 1020 through the through hole 1030 .

The support 143 may receive a force in the axial direction 1020 by the tension of the wire 146 . The support 143 may be pulled to the inner side by the wire 146 . A moving part 144 is installed at the lower end of the support part 143, and the moving part 144 can move the support part 143 in the axial direction 1020 when the support part 143 receives a force by the wire 146. have.

11 is a view for explaining that the pulley changes the direction of the force according to an embodiment of the present invention.

Referring to FIG. 11 , a plurality of pulleys 148 and 149 may be configured. The pulleys 148 and 149 change the direction of the force applied to the wire 146 by the weight 147 from the first direction 1110 to the second direction 1120. The first pulley 148 and the second It may include a second pulley 149 that changes from the direction to the third direction.

The first direction 1110 may be a direction of gravity in a direction of a force applied by the weight 147 to the wire 146 . The third direction 1130 may be an axial direction in a direction of a force applied by the wire 146 to the support 143 . The second direction 1120 may be a direction perpendicular to the first direction 1110 and the third direction 1130 .

The first pulley 148 changes the direction of the force applied in the first direction 1110 to the second direction 1120 , and the second pulley 149 changes the direction of the force applied in the second direction 1120 . It may change in the third direction 1130 . Accordingly, the support 143 is subjected to a force in the axial direction by the gravity of the weight 147 , and the load applying unit 140 may apply a load to the bearing test unit 120 .

A connection part 145 connecting the support part 143 and the wire 146 may be positioned in the support part 143 . The connection part 145 may be disposed on the inner surface of the support part 143 . The connection part 145 may have a structure that is recessed from the inner surface of the support part 143 or a structure that protrudes from the inner surface of the support part 143 . The wire 146 may be connected to the connection part 145 to transmit tension to the support part 143 .

The connection part 145 may be located in the middle of the total height of the support part 143 and the moving part 144 . In other words, when the height of the support part 143 is H and the height of the movable part 144 is h, the connection part 145 is (H+h)/2 from the base 150 on the inner surface of the support part 143 . can be placed in the position of

The position of (H+h)/2 from the base 150 is half the height of the load-applying unit 140 , and may be a position that can most efficiently transmit the tension of the wire 146 .

As shown in FIG. 11 , by configuring the axial load unit 140 using the pulleys 148 and 149 and the weight 147 , an axial load can be applied to the test bearing 121 without an existing pneumatic system. . That is, it is possible to reduce the space occupied by the airfoil bearing testing apparatus 100 and to economically evaluate the durability of the airfoil bearing.

12A to 12B are diagrams illustrating movement of a moving unit according to an embodiment of the present invention.

The moving unit 144 is disposed at the lower end of the supporting unit 143, and at the lower end of the moving unit 144, an LM guide may be arranged to move the supporting unit 143 as a weight 147 is added. . In other words, a rail for the LM guide is installed on the base 150 , and the moving unit 144 may move along the rail.

Referring to FIG. 12A , the first weight m may apply a first axial force 1210 to the support 143 using a wire 146 and a pulley 1230 . Referring to FIG. 12B , the second weight M may apply a second axial force 1220 to the support 143 using the wire 146 and the pulley 1230 .

The first weight (m) may have a smaller mass than the second weight (M). The mass of the second weight M may be greater than the mass of the first weight m. The gravity of the second weight (M) is greater than the gravity of the first weight (m), and the tension by the second weight (M) and the wire (146) is the first weight (m) and the wire (146) may be greater than the tension caused by

The second axial force 1220 may be greater than the first axial force 1210 . Accordingly, the moving distance of the moving part 144 may be increased, and the distance between the load applying part 140 and the bearing test part 120 may be narrowed.

The axial bearing 141 of the load-applying unit 140 may face the rotating plate 127 of the bearing test unit 120 with a predetermined gap therebetween. The predetermined gap may be referred to as an air gap. When the moving unit 144 receives a force by a wire, the moving unit 144 moves the supporting unit 143 by tension, and the axial bearing 141 may also move therewith.

When the moving part 144 moves inward by tension, the air gap between the axial bearing 141 and the rotating plate 127 may be reduced. 12A to 12B , the length of the air gap d2 may be smaller than d1. However, even in this case, the axial bearing 141 and the rotating plate 127 may not contact each other.

Since the axial bearing 141 is configured as a static bearing, the axial bearing 141 and the rotating plate 127 may not contact even if the load applied by the load applying unit 140 to the bearing test unit 120 increases. This may allow the load-applying unit 140 to apply a large load, and may broaden the durability evaluation range of the test bearing 121 . In addition, by not affecting the rotation of the shaft 126, it can help the torque measuring unit 130 to accurately measure the torque.

As shown in FIG. 12b, when the mass of the second weight M increases and the tension by the wire 146 increases and the air gap decreases to d2, the pressure applied by the axial bearing 141 to the rotating plate 127 can be increased. have. When the pressure applied to the rotating plate 127 by the axial bearing 141 increases, the axial load applied to the bearing test unit 120 may increase.

In other words, by adjusting the mass of the weight 147 , the load applied by the load applying unit 140 to the bearing test unit 120 may be adjusted. The mass of the weight 147 is easily adjustable, and accordingly, the load applied by the load applying unit 140 to the bearing test unit 120 is also easily adjustable.

According to an embodiment, a pressure sensor or a force sensor may be installed on the rotating plate 127 . The pressure sensor or the force sensor may measure the load applied by the load applying unit 140 to the bearing test unit 120 .

As described above, by configuring the axial load part 140 using the pulleys 148 and 149 and the weight 147, it is possible to apply an accurate load, thereby ensuring test repeatability and reproducibility.

13 is a block diagram of a control unit of an airfoil bearing testing apparatus according to an embodiment of the present invention.

The controller 170 may be electrically connected to at least one of a speed sensor 114 , a load cell 133 , a temperature sensor (not shown), a pressure sensor, or a force sensor. The control unit 170 may receive rotation speed information of the rotation driving unit 110 from the speed sensor 114 . The controller 170 may receive force information applied by the torque head 132 to the load cell 133 from the load cell 133 . The controller 170 may receive temperature information of the test bearing 121 from the temperature sensor. The control unit 170 may receive load information applied to the bearing test unit 120 by the load application unit 140 from a pressure sensor or a force sensor.

The controller 170 may acquire information on the torque of the test bearing 121 according to the rotational speed of the rotational driving unit 110 based on information obtained from the speed sensor 114 and the load cell 133 . The torque may be calculated as the product of the force F measured by the load cell 133 and the distance L from the center of the shaft 126 to the center of the load cell 133 .

Referring to FIG. 13 , the control unit 170 may include at least one of a processor 171 , an input unit 172 , an output unit 173 , a memory 174 , an interface unit 175 , or a power supply unit 176 . can At least one of the processor 171 , the input unit 172 , the output unit 173 , the memory 174 , the interface unit 175 , and the power supply unit 176 may be electrically connected to the printed circuit board.

The processor 171 may be electrically connected to the input unit 172 , the output unit 173 , the memory 174 , the interface unit 175 , and the power supply unit 176 to exchange signals. The processor 171 is ASICs (application specific integrated circuits), DSPs (digital signal processors), DSPDs (digital signal processing devices), PLDs (programmable logic devices), FPGAs (field programmable gate arrays), processors (processors), controller It may be implemented using at least one of controllers, micro-controllers, microprocessors, and other electrical units for performing functions.

The processor 171 may be driven by power provided from the power supply 176 . The processor 171 may receive data, process data, generate a signal, and provide a signal while power is supplied by the power supply unit 176 .

The processor 171 may acquire information on the torque of the test bearing 121 according to the rotational speed of the rotational driving unit 110 based on information obtained from the speed sensor 114 and the load cell 133 .

The input unit 172 is for receiving information from a user, and the data collected by the input unit 172 may be processed as a user's control command. The input unit 172 may include at least one of a voice input unit, a gesture input unit, a touch input unit, and a mechanical input unit.

The input unit 172 may receive user input information on the target rotation speed of the rotation driving unit 110 . The setting value for the rotation speed may be determined by the user's input information, and the rotation speed of the rotation driving unit 110 may be controlled according to the setting value.

The input unit 172 may receive user input information regarding the length of the torque arm 131 . The processor 171 may calculate the torque of the test bearing 121 based on the user's input information on the length of the torque arm 131 and the force information received from the load cell 133 . The torque may be calculated as the product of the force F measured by the load cell 133 and the distance L from the center of the shaft 126 to the center of the load cell 133 .

The output unit 173 is for generating an output related to visual, auditory or tactile sense, and may include at least one of a display unit, a sound output unit, and a haptic output unit.

The output unit 173 may output at least one of speed measurement information measured by the speed sensor 114 , torque information calculated by the processor 171 , and load information measured by a pressure sensor or a force sensor. The output unit 173 may provide sensor information to a user through a display and enable the user to monitor.

For example, the output unit 173 may output a graph and provide it to the user as shown in FIG. 5 . In this case, the controller 170 may determine the levitation speed 550 of the test bearing 121 as 125Hz, and display the levitation speed 550 to the user.

The memory 174 is electrically connected to the processor 171 . The memory 174 may store basic data for the unit, control data for operation control of the unit, and input/output data. The memory 174 may store data processed by the processor 171 . The memory 174 may be configured as at least one of ROM, RAM, EPROM, flash drive, and hard drive in terms of hardware. The memory 174 may store various data for the overall operation of the controller 170 , such as a program for processing or controlling the processor 171 . The memory 174 may be implemented integrally with the processor 171 . According to an embodiment, the memory 174 may be classified into a sub-configuration of the processor 171 .

The interface unit 175 may exchange signals with at least one electronic device provided in the bearing testing apparatus 100 in a wired or wireless manner. The interface unit 175 may transmit/receive a signal to/from at least one of a speed sensor 114 , a load cell 133 , a pressure sensor, or a force sensor. The interface unit 175 may be configured of at least one of a communication module, a terminal, a pin, a cable, a port, a circuit, an element, and a device.

The power supply unit 176 may supply power to the control unit 170 . The power supply unit 176 may receive power from a power source (eg, a battery) included in the bearing testing apparatus 100 to supply power to each unit of the bearing testing apparatus 100 . The power supply unit 176 may be operated according to a control signal provided from the control unit 170 . The power supply unit 176 may be implemented as a switched-mode power supply (SMPS).

In the above, preferred embodiments of the present invention have been shown and described, but the present invention is not limited to the specific embodiments described above, and in the technical field to which the present invention pertains without departing from the gist of the present invention as claimed in the claims. Various modifications may be made by those of ordinary skill in the art, and these modifications should not be individually understood from the technical spirit or perspective of the present invention.

10: Compressor
100: airfoil bearing test device
110: rotation drive unit
111: turbine 112: inlet pipe 113: discharge pipe
114: speed sensor 115: pipe support 116: rotation shaft
120: bearing test unit
121: test bearing 122: thrust runner 123: bearing support
124: housing 125: rotation shaft 126: shaft
127: rotary plate 128: radial bearing 129: bearing support
130: torque measuring unit
131: torque arm 132: torque head 133: load cell
134: load cell support
140: load or not
141: axial bearing 142: ball screw 143: support
144: moving part 145: connecting part 146: wire
147: weight 148: first pulley 149: second pulley
150: base
160: cooling pipe
170: control unit

Claims (15)

a rotational driving unit that generates rotational force by hydraulic pressure of the gas;
A test bearing is disposed, a rotating unit axially connected to the rotating driving unit, a shaft extending in a direction of a rotation axis of the rotating unit, a plurality of radial bearings supporting the shaft, and a torque of the test bearing positioned on the shaft a bearing test unit comprising a torque measuring unit that measures and
Including; a load-applying part for applying an axial load to the bearing test part;
The load-bearing part is
an axial bearing spaced apart from the bearing test unit;
a support for supporting the axial bearing; and
It includes a moving part for moving the support part,
The radial bearing is composed of a static pressure bearing,
The static pressure bearing is
An air foil bearing test apparatus disposed symmetrically with respect to the torque measuring unit. delete According to claim 1,
The rotating part,
a housing forming an exterior of the rotating part;
a thrust runner mounted inside the housing and connected to the rotation shaft of the rotation driving unit; and
and a bearing support part mounted inside the housing and contacting the test bearing. 4. The method of claim 3,
The test bearing is
Airfoil bearing testing apparatus, characterized in that it is disposed between the bearing support and the thrust runner. 5. The method of claim 4,
The test bearing is
An air foil bearing comprising a disk-shaped bearing disk, a back foil attached to the bearing disk, and a top foil covering the back foil,
The bearing support part,
Air foil bearing testing apparatus, characterized in that in contact with one surface of the bearing disk. 4. The method of claim 3,
On the side of the bearing support,
Air foil bearing test apparatus, characterized in that a cooling hole for lowering the temperature of the bearing test part by injecting an external gas is formed. 7. The method of claim 6,
On the side of the housing,
A supply hole for supplying an external gas to the cooling hole and a sensor hole in which a gap sensor is installed are formed,
The sensor hole is
Air foil bearing test apparatus, characterized in that it is disposed closer to the rotational driving part than the supply hole. According to claim 1,
The torque measuring unit,
Air foil bearing testing apparatus comprising a load cell, a torque head contacting the load cell to apply pressure to the load cell, and a torque arm having one end connected to the torque head and the other end inserted into the shaft and fixed. 9. The method of claim 8,
One side of the load cell is attached to the load cell support and fixed,
The torque arm is an air foil bearing test apparatus, characterized in that extending from the center of the shaft to the center of the load cell in a radial direction. 10. The method of claim 9,
The load cell is
Air foil bearing testing apparatus, characterized in that the force applied by the torque head by the rotation of the torque arm is measured. According to claim 1,
The rotary drive unit,
An airfoil bearing testing apparatus corresponding to a turbine part of a turbocharger. 12. The method of claim 11,
The bearing test unit,
Airfoil bearing test apparatus, characterized in that it corresponds to the impeller of the turbocharger. 12. The method of claim 11,
The rotary drive unit,
Airfoil bearing test apparatus comprising a speed sensor for measuring the rotational speed of the rotational driving unit. 14. The method of claim 13,
The rotary drive unit,
Further comprising an inlet pipe through which the gas is introduced and a discharge pipe through which the introduced gas is discharged,
The speed sensor is an air foil bearing test apparatus, characterized in that installed in the discharge pipe. 14. The method of claim 13,
Electrically connected to the torque measuring unit and the speed sensor,
Air foil bearing testing apparatus further comprising a; a control unit for obtaining torque information of the test bearing according to the rotational speed of the rotary driving unit.

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