Loading control system for rotating part in semi-closed cavity

Abstract

The invention belongs to the field of engine assembly, and particularly relates to a loading control system for a rotating part in a semi-closed cavity, which comprises a bearing system and a spring system, the spring system is connected into the bearing system, and the spring system can be pushed and pulled by moving the bearing system; the spring system comprises a blind hole shaft, a large spring and a small spring; the small spring is coaxially connected into a blind hole of the blind hole shaft, and the large spring is coaxially connected to the outer wall of the blind hole shaft. One ends of the large spring and the small spring are free ends, and the other ends are fixed ends; the free ends and the fixed ends of the large spring and the small spring are positioned in the same direction; the device is small, light, easy to operate, simple in structure and low in machining cost. The device can adapt to the axial force loading operation of a rotating part in a semi-closed cavity with a small internal space, a narrow outlet and a low visual degree, and can also be used in an open space to replace similar equipment with similar functions but complex structures.

Description

TECHNICAL FIELD

[0001] The present application belongs to the field of engine assembly, and particularly relates to a loading control system for a rotating part in a semi-closed cavity. BACKGROUND

[0002] In the process of assembling an aero-engine, the meshing condition of gears therein often needs to be checked. For the meshing check of a bevel gear pair, the meshing clearance and color mark of the gear pair are generally checked on the premise that a certain axial force is applied to the bevel gear to eliminate bearing play. However, due to the existence of many semi-closed cavity structures in the structure of an aero-engine, the meshing condition of some bevel gear pairs after final assembly needs to be checked in such a semi-closed cavity.

[0003] When checking the meshing condition of gears in a relatively open space, a complex tool fixture and a special force measuring instrument can be used to control the loading state of the gears. However, when the above operation is performed in a cavity, due to the small internal mechanism space and the narrow entrance and exit, a complex tool fixture with a large volume cannot enter the cavity for operation. In addition, the light in the cavity is poor, and the line of sight is blocked in most areas, so it is also difficult to operate a conventional force measuring instrument in the cavity.

[0004] In this case, the posture of the parts is usually adjusted so that the axis of one gear is perpendicular to the horizontal plane, and the axial loading and the load size are controlled by means of gravity through the suspension of a weight. Due to the included angle between the axes of the two gears of a bevel gear pair, the axis of the other gear cannot be perpendicular to the horizontal plane at the same time, so other methods need to be used for axial loading. Since the conventional tool fixture and force measuring instrument cannot operate normally in the cavity, the operator usually needs to try to simulate the operation on the model outside the cavity, measure the approximate hand feeling at the specified load, and then load the parts manually in the cavity according to the hand feeling.

[0005] has the following disadvantages:

[0006] The existing loading method by means of the experience and hand feeling of the operator cannot accurately control the loading force, and the operation error is large. In addition, the change of the operator may cause a large change in the loading force error, and such error and change are difficult to detect. If the operator can be loaded in an open space by changing the structure, the design and manufacturing difficulty and cost may be greatly improved. However, the development of a special automatic control robot device to enter the narrow cavity for operation is difficult and costly due to the complex structure of the cavity and the parts.

[0007] Therefore, how to accurately control the loading force is a problem to be solved. SUMMARY

[0008] In order to solve the above problems, the application provides a loading control system for a rotating part in a semi-closed cavity to solve the problem that the loading force cannot be accurately controlled during assembly in the prior art.

[0009] The technical scheme of the application is as follows: a loading control system for a rotating part in a semi-closed cavity, comprising a bearing system and a spring system.

[0010] The spring system is connected to the bearing system and can push and pull the spring system by moving the bearing system; the spring system comprises a blind hole shaft, a large spring and a small spring.

[0011] The small spring is coaxially connected to the blind hole of the blind hole shaft, and the large spring is coaxially connected to the outer wall of the blind hole shaft.

[0012] One end of the large spring and the small spring is a free end, and the other end is a fixed end; the free end and the fixed end of the large spring and the small spring are in the same direction; by applying a pushing force to the free end of the large spring, the free end of the large spring can be moved to be flush with the free end of the small spring in the free state, so that the force transmitted to the part through the fixed end of the large spring reaches the lower limit of the specified size; by continuously applying a pushing force to the large spring and the small spring, the free ends of the large spring and the small spring can be moved to the upper limit position of the loading force at the same time.

[0013] Preferably, the relative relationship between the free ends of the large spring and the small spring is as follows:

[0014] Let the planes where the free ends of the large spring and the small spring are located in the free state be represented by solid line a and solid line b respectively, and the positions where the free end of the large spring is located when the loading force reaches the lower limit and the upper limit be represented by dashed line c and dashed line d respectively.

[0015] The distance between the solid line a and the solid line b (or the dashed line c) is L1=F1÷k1.

[0016] The distance between the solid line b and the dashed line d is L2=(F2-F1)÷(k1+k2).

[0017] Wherein, F1 and F2 are the maximum and minimum values of the loading force respectively, k1 and k2 are the elastic coefficients of the large spring and the small spring respectively, a is the position where the free end of the large spring is located in the free state, and b is the position where the free end of the small spring is located in the free state.

[0018] Preferably, the free ends of the large spring and the small spring are between the lower limit and the upper limit of the loading force; by controlling the position of the fixed end of the small spring, the dashed line c can coincide with the solid line b.

[0019] Preferably, a threaded hole is provided at the bottom of the blind hole of the blind hole shaft and a countersunk screw is installed, and the fixed end of the small spring is attached to the countersunk screw during loading; by turning the countersunk screw, the position of the fixed end of the small spring can be adjusted.

[0020] The outlet position of the blind hole is provided with a thimble, and the thimble and the blind hole are fixed by a radial pin. The pin hole of the blind hole wall surface is an oblong hole along the axial direction, and the radial pin can freely move in the oblong hole.

[0021] Preferably, the end of the blind hole shaft is provided with a cover, the length of the radial pin exceeds the diameter of the blind hole shaft, the large spring is installed between the shaft shoulder of the blind hole shaft and the cover, the fixed end of the large spring is flush with the shaft shoulder on the blind hole shaft, and the large spring and the blind hole shaft are tightly attached to the same installation flange when the spring system is installed; the cover is a bowl-shaped structure, the bottom of the bowl faces the large spring, and the radial pin is in the cover.

[0022] Preferably, the bowl-shaped upper part of the cover corresponds to the plane represented by the solid line a, the end of the thimble corresponds to the plane represented by the solid line b, and the end of the blind hole shaft corresponds to the plane represented by the dashed line d.

[0023] Preferably, the bearing system comprises a shaft sleeve, a first bearing, a housing, and a second bearing.

[0024] The shaft sleeve, the first bearing, the housing, and the second bearing are coaxially arranged, the first bearing and the second bearing are arranged in front and back, and the housing is connected to the outer side of the first bearing and the second bearing; the shaft sleeve is arranged on the inner side of the first bearing and the second bearing; the housing is provided with a force transmission structure connected to the loading force system and a torque transmission interface;

[0025] The end of the shaft sleeve is provided with a bearing baffle, and a fixing screw is connected between the bearing baffle and the spring system.

[0026] The application has the following advantages:

[0027] It is small, light, simple to operate, simple in structure, and low in processing cost. It can adapt to the axial force loading operation of the rotating part in the semi-closed cavity with small internal space, narrow outlet, and low visibility, and can also be used in open space to replace similar devices with similar functions but complex structure. Compared with the existing loading method relying on the feeling of the operator, the application can strictly control the size of the loading force within the specified range, and can adjust the size of the loading force by adjusting the threaded parts and inserting shims, etc., and has strong adaptability. BRIEF DESCRIPTION OF DRAWINGS

[0028] Figure 1 It is a schematic diagram of the spring system structure of the application;

[0029] Figure 2 It is a relationship diagram of the large spring and the small spring of the application;

[0030] Figure 3 It is a schematic diagram of the blind hole shaft structure of the application;

[0031] Figure 4 Figure 1 is a schematic diagram of the radial pin installation of the present application;

[0032] Figure 5 Figure 2 is a schematic diagram of the bearing system structure of the present application;

[0033] Figure 6 Figure 3 is a schematic diagram of the loading system structure of the present application;

[0034] Figure 7 Figure 4 is a schematic diagram of the loading system in the inner cavity of the present application;

[0035] Figure 8 Figure 5 is an enlarged view of the loading system in the inner cavity of the present application.

[0036] 1, blind hole shaft; 2, large spring; 3, countersunk screw; 4, small spring; 5, cover; 6, thimble; 7, radial pin; 8, rectangular hole; 9, shaft sleeve; 10, first bearing; 11, shell; 12, force transmission interface; 13, second bearing; 14, torque transmission interface; 15, bearing baffle; 16, fixing screw. DETAILED DESCRIPTION

[0037] In order to make the purpose, technical scheme and advantages of the present application clearer, the technical scheme of the present application will be described in more detail below in combination with the drawings in the embodiments of the present application. In the drawings, the same or similar reference numerals represent the same or similar elements or elements with the same or similar functions throughout. The described embodiments are part of the embodiments of the present application, not all of the embodiments. The embodiments described below by referring to the drawings are exemplary and are intended to explain the present application, and cannot be understood as a limitation of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application. The embodiments of the present application will be described in detail below in combination with the drawings.

[0038] The first aspect of the present application provides a loading control system for a rotating part in a semi-closed cavity, such as Figure 1 , comprising a bearing system and a spring system.

[0039] The spring system is connected to the bearing system and can push and pull the spring system by moving the bearing system; the spring system comprises a blind hole shaft 1, a large spring 2 and a small spring 4.

[0040] The small spring 4 is coaxially connected to the blind hole of the blind hole shaft 1, and the large spring 2 is coaxially connected to the outer wall of the blind hole shaft 1.

[0041] The one end of the big spring 2 and the small spring 4 is free end, the other end is fixed end; the free end and the fixed end of the big spring 2 and the small spring 4 are in the same direction; by applying the pushing force to the free end of the big spring 2, the free end of the big spring 2 can be moved to be flush with the free end of the small spring 4 in the free state, then the force transmitted to the part through the fixed end of the big spring 2 reaches the lower limit of the specified size; continue to push and apply the pushing force to the big spring 2 and the small spring 4, the free end of the big spring 2 and the small spring 4 can be moved to the upper limit position of the loading force at the same time.

[0042] In operation, the big spring 2 and the small spring 4 are compressed through the bearing system, and in the pushing process, if the palm can contact the end of the blind hole shaft 1, it represents that the loading force has reached the upper limit of the allowable loading force. The operator adjusts the size of the pushing force applied by the palm, so that the palm contacts the thimble 6 without contacting the blind hole shaft 1, which can ensure that the loading force is within a fixed range, thereby realizing precise control of the loading force.

[0043] Preferably, according to Hooke's law, the relative relationship of the positions (i.e. solid line a, b and dashed line c, d) of the free ends of the two springs in the above states can be determined as follows:

[0044] As Figure 2 The upper part is the big spring 2, and the lower part is the small spring 4; let the solid line a and the solid line b be the planes where the free ends of the big spring 2 and the small spring 4 are located in the free state respectively, and the dashed line c and the dashed line d be the positions of the free end of the big spring 2 when the loading force reaches the lower limit and the upper limit respectively.

[0045] The distance between the solid line a and the solid line b (or the dashed line c) is: L1=F1÷k1;

[0046] The distance between the solid line b and the dashed line d is L2=(F2-F1)÷(k1+k2);

[0047] Wherein, F1 and F2 are the maximum and minimum values of the allowable loading force respectively, k1 and k2 are the elastic coefficients of the big spring 2 and the small spring 4 respectively, and a is the position of the free end of the big spring 2 in the free state, and b is the position of the free end of the small spring 4 in the free state.

[0048] In operation, the free end of the large spring 2 is controlled between the dashed lines c and d, so that the loading force meets the requirements. In design, the solid line b (the plane where the free end of the small spring 4 is located in the free state) and the dashed line c (the plane where the free end of the large spring 2 is located when the loading force reaches the lower limit), and the fixed ends of the large and small springs 4 are fixed to the rotating parts (such as bevel gears, etc.), and by applying a pushing force to the free end of the large spring 2, the free end of the large spring 2 is moved to be flush with the free end of the small spring 4 in the free state (the position of the dashed line c), so that the force transmitted to the parts through the fixed end of the large spring 2 reaches the lower limit of the specified size. Continue to move forward while applying a pushing force to the large and small springs 4, so that the free ends of the two springs are moved to the upper limit position (the position of the dashed line d) of the loading force at the same time, and at this time, the force transmitted to the parts through the fixed ends of the two springs reaches the upper limit of the specified size.

[0049] In use, the free ends of the large spring 2 and the small spring 4 are between the lower limit and the upper limit of the loading force, so that the pushing force applied to the rotating parts meets the requirements; by controlling the position of the fixed end of the small spring 4, the dashed line c can coincide with the solid line b.

[0050] Preferably, a threaded hole is provided at the bottom of the blind hole of the blind hole shaft 1, and a countersunk screw 3 is installed, and the fixed end of the small spring 4 is attached to the countersunk screw 3 during loading; by turning the countersunk screw 3, the position of the fixed end of the small spring 4 can be adjusted.

[0051] In combination Figure 3 , the outlet position of the blind hole is provided with a thimble 6, and the thimble 6 and the blind hole are fixed by a radial pin 7, and the pin hole of the blind hole wall surface is an oblong hole 8 along the axial direction, and the radial pin 7 can freely move in the oblong hole 8, so that the thimble 6 limited by the pin and the oblong hole 8 can freely move along the axis of the blind hole.

[0052] Preferably, the end of the blind hole shaft 1 is provided with a cover 5, and the length of the radial pin 7 exceeds the diameter of the blind hole shaft 1, so that the outer end protrudes from the outer wall of the blind hole shaft 1, and blocks the cover 5 sleeved on the blind hole shaft 1 (such as Figure 4 ), so that the cover 5 cannot be pulled out from this side. The large spring 2 is installed between the shaft shoulder of the blind hole shaft 1 and the cover 5, and the fixed end of the large spring 2 is kept flush with the shaft shoulder on the blind hole shaft 1, and the large spring 2 and the blind hole shaft 1 are tightly attached to the same installation flange during installation of the spring system, and the free end is limited by the cover 5 to ensure that it will not come out of the blind hole shaft 1; the cover 5 is in the shape of a bowl, with the bottom of the bowl facing the large spring 2, and the radial pin 7 is located in the cover 5.

[0053] After the size of the large spring 4 and the blind hole shaft 1 is determined, the axial length of the plunger 6 and the cover 5 is adjusted so that the relationship between the upper edge of the cover 5, the end of the plunger 6 and the end of the blind hole shaft 1 conforms to the position relationship of the solid line a, b and the dashed line c, d, wherein the upper edge of the cover 5 corresponds to the plane represented by the solid line a, the end of the plunger 6 corresponds to the plane represented by the solid line b (and the dashed line c), and the end of the blind hole shaft 1 corresponds to the plane represented by the dashed line d.

[0054] In order to shorten the size of the spring system, the axial length of the rectangular hole 8 on the blind hole shaft 1 is shortened so that, in the unloaded state, the large spring 2 and the cover 5 are limited by the rectangular hole 8 through the radial pin 7 and cannot be elongated to the position where the pressure is completely zero (i.e. the solid line a), but only to the position a' between the solid lines a and b in the figure. Limiting the cover 5 at the position a' is equivalent to generating a pre-pressure smaller than the minimum value d of the loading force inside the spring system in the state where no loading force is applied. After the large spring 2 is compressed by the pre-pressure, the length is shortened, and the size of the entire spring system is correspondingly shortened. Since the pre-pressure is an internal force of the spring system, it will not be transmitted to the parts outside the system, i.e. it will not affect the size of the loading force.

[0055] Preferably, as Figure 5 , the bearing system comprises a sleeve 9, a first bearing 10, a housing 11 and a second bearing 13;

[0056] The sleeve 9, the first bearing 10, the housing 11 and the second bearing 13 are coaxially arranged, the first bearing 10 and the second bearing 13 are arranged in front of and behind each other, and the housing 11 is connected to the outer sides of the first bearing 10 and the second bearing 13; the sleeve 9 is arranged inside the first bearing 10 and the second bearing 13; the housing 11 is provided with a force transmission structure connected to the loading force system and a torque transmission interface 14;

[0057] In combination Figure 6 The end of the sleeve 9 is provided with a bearing baffle 15, and the bearing baffle 15 is connected to the spring system through a fixing screw 16.

[0058] The double bearing has radial positioning and axial thrusting capability, and the housing 11 can rotate freely relative to the sleeve 9. On the side of the housing 11 close to the mounting flange, a force transmission interface 12 and a torque transmission interface 14 connected to the rotating part are arranged to determine the correct position relationship between the loading force system and the rotating part and fix them together, wherein the force transmission interface 12 transmits the loading force of the loading system to the rotating part, and the torque transmission interface 14 limits the relative rotation between the housing 11 of the loading system and the rotating part. The force transmission interface 12 and the torque transmission interface 14 are designed according to the actual shape of the interface part of the rotating part.

[0059] The whole mechanism is integrated, small and portable, and the operator can hold the end of the shell 11 with one hand, with the palm facing the cover 5. According to the actual size of the palm and the mechanism, the palm can press the cover 5 or not be in contact with it. The mechanism is sent into the cavity through the inner cavity entrance, and the interface on the shell 11 is connected to the corresponding position of the rotating part. When the interface is connected, the cover 5 is pushed along the loading mechanism with the palm, and the holding of the shell 11 is released at the same time. The operator spreads the palm and pushes the cover 5 of the loading mechanism forward. When the pushing force exceeds the pre-pressure inside the spring system, the cover 5 starts to move. When the palm moves with the cover 5 to contact the ejector pin 6, it means that the loading force has exceeded the lower limit of the allowed loading force. Continue to push forward, and the palm contacts the end of the blind hole shaft 1, which means that the loading force has reached the upper limit of the allowed loading force. The operator adjusts the size of the pushing force applied by the palm to ensure that the loading force is within a fixed range. Figure 7 、 Figure 8 When the interface is connected, the cover 5 is pushed along the loading mechanism with the palm, and the holding of the shell 11 is released at the same time. The operator spreads the palm and pushes the cover 5 of the loading mechanism forward. When the pushing force exceeds the pre-pressure inside the spring system, the cover 5 starts to move. When the palm moves with the cover 5 to contact the ejector pin 6, it means that the loading force has exceeded the lower limit of the allowed loading force. Continue to push forward, and the palm contacts the end of the blind hole shaft 1, which means that the loading force has reached the upper limit of the allowed loading force. The operator adjusts the size of the pushing force applied by the palm to ensure that the loading force is within a fixed range.

[0060] The above is only a specific embodiment of the present application, but the protection scope of the present application is not limited thereto. Any changes or replacements within the technical scope disclosed in the present application can be easily thought of by those skilled in the art, and should be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A loading control system for a rotating part in a semi-enclosed cavity, characterized in that, The bearing system and the spring system are connected, and the spring system can be pushed and pulled by moving the bearing system. The spring system comprises a blind hole shaft (1), a large spring (2) and a small spring (4). The small spring (4) is coaxially connected in the blind hole of the blind hole shaft (1), and the large spring (2) is coaxially connected on the outer wall of the blind hole shaft (1). One end of the large spring (2) and the small spring (4) is a free end, and the other end is a fixed end.

2. The load control system for a rotating part in a semi-enclosed cavity as recited in claim 1, wherein, The free end and the fixed end of the large spring (2) and the small spring (4) are in the same direction. The free end of the large spring (2) is moved to be flush with the free end of the small spring (4) in the free state by applying a pushing force to the free end of the large spring (2), so that the force transmitted to the part through the fixed end of the large spring (2) reaches the lower limit of the specified size. The relative relationship between the free ends of the large spring (2) and the small spring (4) is as follows: The solid line a and the solid line b respectively represent the planes where the free ends of the large spring (2) and the small spring (4) are located in the free state, and the dashed line c and the dashed line d respectively represent the positions of the free end of the large spring (2) when the load reaches the lower limit and the upper limit. The distance between the solid line a and the solid line b (or the dashed line c) is L1=F1÷k1.

3. The load control system for a rotating part in a semi-enclosed cavity of claim 2, wherein, The distance between the solid line b and the dashed line d is L2=(F2-F1)÷(k1+k2).

4. The load control system for a rotating part in a semi-enclosed cavity of claim 2, wherein, Wherein F1 and F2 are the maximum and minimum values of the allowable load, k1 and k2 are the elastic coefficients of the large spring (2) and the small spring (4), and a is the position of the free end of the large spring (2) in the free state, and b is the position of the free end of the small spring (4) in the free state. The free ends of the large spring (2) and the small spring (4) are between the lower limit and the upper limit of the load.

5. The load control system for a rotating part in a semi-enclosed cavity of claim 4, wherein, The position of the fixed end of the small spring (4) can be adjusted by screwing the countersunk screw (3) to make the dashed line c coincide with the solid line b. The blind hole of the blind hole shaft (1) is provided with a threaded hole at the bottom, and a countersunk screw (3) is installed. The outlet position of the blind hole is provided with a thimble (6), and the thimble (6) and the blind hole are fixed by a radial pin (7). The end of the blind hole shaft (1) is provided with a cover (5), the length of the radial pin (7) exceeds the diameter of the blind hole shaft (1), the large spring (2) is installed between the shaft shoulder of the blind hole shaft (1) and the cover (5), the fixed end of the large spring (2) is flush with the shaft shoulder of the blind hole shaft (1), and the large spring (2) and the blind hole shaft (1) are tightly attached to the same installation flange during installation of the spring system. The cover (5) is in the shape of a bowl, the bottom of the bowl faces the large spring (2), and the radial pin (7) is located in the cover (5).

6. The load control system for a rotating part in a semi-enclosed cavity of claim 5, wherein, The upper edge of the bowl-shaped cover (5) corresponds to the plane represented by solid line a, the end of the thimble (6) corresponds to the plane represented by solid line b, and the end of the blind hole shaft (1) corresponds to the plane represented by dotted line d.

7. The load control system of claim 1 wherein the controller is configured to determine the load control signal based on the load control signal and the load control signal. The bearing system comprises a sleeve (9), a first bearing (10), a housing (11) and a second bearing (13); The sleeve (9), the first bearing (10), the housing (11) and the second bearing (13) are coaxially arranged, the first bearing (10) and the second bearing (13) are arranged in front of and behind each other, the housing (11) is connected to the outer sides of the first bearing (10) and the second bearing (13); the sleeve (9) is arranged on the inner sides of the first bearing (10) and the second bearing (13); the housing (11) is provided with a force transmission structure connected to the load system and a torque transmission interface (14); The end of the sleeve (9) is provided with a bearing baffle (15), and a fixing screw (16) is connected between the bearing baffle (15) and the spring system.

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