Hydraulic dynamic balancing device

Abstract

The present application relates to the technical field of engine, disclose a kind of hydraulic dynamic balancing device, including piston, locating seat, screw plug, dynamic balancing shaft, bushing and limit screw plug;The both ends of the dynamic balancing shaft are respectively machined with step hole, outer surface is respectively provided with the oil port communicated with the step hole, the surface of the step hole is machined with thread;Screw plug is arranged in the step hole of the one end of the dynamic balancing shaft, piston is arranged in the step hole of the other end, and limit screw plug is arranged;The end of the limit screw plug is against the end surface of the piston;Bushing is arranged on the outer surface of the dynamic balancing shaft and located on the oil port, locating seat is arranged on the outer surface of the dynamic balancing shaft and located on the bushing.The present application is by injecting hydraulic oil in dynamic balancing shaft, and by adjusting the tightening degree of limit screw plug, the outer diameter of bushing is uniformly expanded, the close cooperation of disc rotor and dynamic balancing device is realized, the overall structure is simple, easy to operate, improves the dynamic balancing precision and efficiency of disc rotor.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of turbine engine, more particularly, it is a kind of hydraulic dynamic balancing device. BACKGROUND

[0002] I, II turbine rotor assembly is a key part of turbine engine, it is a typical shafting disc type part, because the working speed of engine is very high, close to 40000rpm, therefore the dynamic balance precision of I, II turbine rotor assembly is required to be higher, and the dynamic balance effect directly affects the vibration performance of engine. During dynamic balance, horizontal dynamic balancing machine is generally used for dynamic balance, and vertical dynamic balancing machine cannot guarantee the balance precision requirement. In order to realize the connection between disc type rotor and dynamic balancing machine, I, II turbine rotor assembly needs to be assembled on dynamic balancing tool, and then the two are supported on the roller of horizontal dynamic balancing machine, the belt is pressed tightly, and dynamic balance detection is carried out. In order to guarantee the dynamic balance quality, dynamic balancing tool and rotor need to adopt interference fit. Because the matching length of existing turbine rotor assembly positioning hole and dynamic balancing tool is very small, the design difficulty of tool is very great.

[0003] The dynamic balance method of disc type rotor assembly is that the disc type rotor is hot assembled on the process shaft (tool), and then the two are supported on the horizontal dynamic balancing machine for dynamic balance. Another kind is that the disc type rotor is assembled on the taper face matching expansion sleeve type dynamic balancing tool, and then the two are supported on the horizontal dynamic balancing machine for dynamic balance, and the tool is composed of compression nut and dynamic balancing shaft.

[0004] When using process shaft (tool) for dynamic balance, because the process shaft and disc type rotor are interference fit, hot assembly and hot disassembly process method needs to be used, and about 4h is needed for heating and heat preservation each time, which leads to low balance efficiency. In addition, the assembly and disassembly of product and tool are realized by using hot assembly and hot disassembly process method, which is generally suitable for rotors with large thermal expansion coefficient such as aluminum. Because the material of turbine rotor is high-temperature alloy, and the thermal expansion coefficient is similar to that of process shaft, hot disassembly is difficult, so the process shaft is not suitable for turbine rotor. In order to balance multiple parts at the same time, the number of process shafts is large, which leads to high cost of tool production and management, and is not conducive to batch production of turbine engine disc type parts.

[0005] The taper face matching expansion sleeve type tool and rotor are linear contact matching. Because the matching length of turbine rotor assembly positioning hole and dynamic balancing tool is very short, generally only 4mm, the taper face matching expansion sleeve type tool is not easy to expand tightly, and the radial and axial positioning accuracy cannot be guaranteed, so the dynamic balance quality cannot be guaranteed. SUMMARY

[0006] The present application aims at the technical problems existing in the prior art, and provides a hydraulic dynamic balancing device, which has simple structure, reliable function, and can improve the dynamic balance precision and efficiency of disc type rotor with narrow matching surface.

[0007] To address the problems mentioned above, the technical solution adopted by this invention is as follows:

[0008] This invention provides a hydraulic dynamic balancing device, comprising a piston, a positioning seat, a screw plug, a dynamic balancing shaft, a bushing, and a limiting screw plug;

[0009] The dynamic balancing shaft has stepped holes machined at both ends, and oil ports communicating with the stepped holes are provided on its outer surface. The stepped holes are threaded. A screw plug is installed in the stepped hole at one end of the dynamic balancing shaft, and a piston is installed in the stepped hole at the other end, with a limiting screw plug provided. The end of the limiting screw plug abuts against the end face of the piston and is threadedly engaged with the screw plug and the dynamic balancing shaft. A bushing is provided on the outer surface of the dynamic balancing shaft and on the oil port, and a positioning seat is provided on the dynamic balancing shaft and on the outer surface of the bushing.

[0010] Furthermore, a nut is also provided in the stepped hole at the other end of the dynamic balancing shaft, and the end of the limiting plug passes through the nut and presses against the piston.

[0011] Furthermore, a stepped through hole is formed on the positioning seat, and the seat is fitted onto the outer surface of the dynamic balance shaft through the stepped through hole. The larger diameter end of the stepped through hole is located on the outer surface of the bushing, and the stepped surface abuts against the end of the bushing. The smaller diameter end of the stepped through hole corresponds to the position of the stepped hole where the screw plug is located.

[0012] Furthermore, the surface of the positioning seat is also provided with a mounting hole communicating with the stepped through hole. The mounting hole corresponds to the position of the smaller end of the diameter of the stepped through hole and is provided with a positioning pin. The positioning pin is connected to a hole provided on the surface of the dynamic balance shaft.

[0013] Furthermore, the area of ​​the inner surface of the bushing is 3.2 times the surface area of ​​the piston; the thickness of the bushing is 0.85 mm.

[0014] Furthermore, the inner surface of the dynamic balance shaft corresponding to the nut and the piston is set as an inclined plane.

[0015] Furthermore, an O-ring rubber seal is provided between the screw plug and the mating surface of the dynamic balance shaft.

[0016] Furthermore, an O-ring rubber seal is provided on the surface of the piston that faces the inner wall of the dynamic balance shaft.

[0017] Furthermore, the outer surface of the moving horizontal shaft forms a stepped shaft, with the size of the middle stepped shaft being larger than that of the two ends, and the bushing is located on the middle stepped shaft.

[0018] Furthermore, the coaxiality and perpendicularity of the dynamic balancing device are between 0.005 mm and 0.01 mm.

[0019] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0020] The hydraulic dynamic balancing device provided by this invention injects hydraulic oil into the dynamic balancing shaft and adjusts the tightening of the limit plug to hydraulically expand the outer diameter of the bushing, thereby achieving a tight fit between the disc rotor and the dynamic balancing device. It also has high axial and radial positioning accuracy of the rotor, simple overall structure, and easy operation, improving the dynamic balancing accuracy and efficiency of the disc rotor. Furthermore, it enables rapid installation and disassembly between the dynamic balancing device and the disc rotor, making it particularly suitable for disc rotors with narrow mating surfaces. Attached Figure Description

[0021] To more clearly illustrate the solutions in this invention, a brief introduction to the accompanying drawings used in the description of the embodiments will be provided below. Obviously, the drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without any creative effort. Wherein:

[0022] Figure 1 This is a schematic diagram of the hydraulic dynamic balancing device of the present invention.

[0023] Figure 2 This is a schematic diagram of the installation of the hydraulic dynamic balancing device and the disc rotor of the present invention.

[0024] The reference numerals in the attached drawings are explained as follows: 1-nut; 2-piston; 3-positioning seat; 4-positioning pin; 5-screw plug; 6-dynamic balance shaft; 7-bulb; 8-limiting screw plug; 9-disc rotor; 10-first oil port; 11-second oil port; 61-sloping surface; 31-protrusion. Detailed Implementation

[0025] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. For example, terms such as “length,” “width,” “upper,” “lower,” “left,” “right,” “front,” “rear,” “vertical,” “horizontal,” “top,” “bottom,” “inner,” and “outer” indicate orientations or positions based on the orientations or positions shown in the accompanying drawings and are for ease of description only, and should not be construed as limiting the technical solution.

[0026] The terms "comprising" and "having," and any variations thereof, in the specification, claims, and accompanying drawings of this invention are intended to cover non-exclusive inclusion; the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this invention are used to distinguish different objects, not to describe a particular order. In the specification, claims, and accompanying drawings of this invention, when an element is referred to as "fixed to," "mounted to," "disposed of," or "connected to" another element, it may be directly or indirectly located on that other element. For example, when an element is referred to as "connected to" another element, it may be directly or indirectly connected to that other element.

[0027] Furthermore, the reference to "embodiment" herein means that a particular feature, structure, or characteristic described in connection with an embodiment may be included in at least one embodiment of the invention. The appearance of this phrase in various places throughout the specification does not necessarily refer to the same embodiment, nor is it a separate or alternative embodiment mutually exclusive with other embodiments. It will be explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0028] See Figure 1 As shown, the present invention provides a hydraulic dynamic balancing device, including a piston 2, a positioning seat 3, a screw plug 5, a dynamic balancing shaft 6, a bushing 7, and a limiting screw plug 8.

[0029] The dynamic balancing shaft 6 has stepped holes machined at both ends, and oil ports communicating with the stepped holes are respectively provided on the surface of the stepped holes. Threads are machined on the surface of the stepped holes. A screw plug 5 is installed in the stepped hole at one end of the dynamic balancing shaft 6, and a piston 2 is installed in the stepped hole at the other end, with a limiting screw plug 8 provided. The limiting screw plug 8 is threadedly engaged with the dynamic balancing shaft 6, and its end abuts against the end face of the piston 2. A bushing 7 is provided on the outer surface of the dynamic balancing shaft 6 and located on the oil port, and a positioning seat 3 is provided on the dynamic balancing shaft 6 and located on the outer surface of the bushing 7.

[0030] Specifically, the surface of the dynamic balancing shaft 6 is provided with a first oil port 10 and a second oil port 11, which are respectively connected to the bottom of the corresponding stepped hole and form a first oil passage and a second oil passage. The bushing 7 is located on the first oil port 10 and the second oil port 11, that is, the hydraulic oil in the first oil passage and the second oil passage can act on the inner surface of the bushing 7.

[0031] Furthermore, a nut 1 is also provided in the stepped hole at the other end of the dynamic balancing shaft 6. The end of the limiting screw plug 8 passes through the central hole of the nut 1 and presses against the piston 2. Specifically, by providing the nut 1, the limiting screw plug 8 is guided and the piston 2 is axially limited. Even if the limiting screw plug 8 can only act on the piston 2 axially, the piston 2 transmits the clamping force of the limiting screw plug 8 to the hydraulic oil in the stepped hole.

[0032] Specifically, the stepped holes at both ends of the dynamic balance shaft 6 are respectively provided with threads for threaded connection with the limit plug 8, the plug 5 and the nut 1, so as to facilitate connection and mating.

[0033] Furthermore, the inner surface of the dynamic balance shaft 6 corresponding to the nut 1 and the piston 2 is set as an inclined surface 61 for axially limiting the nut 1.

[0034] Furthermore, an O-ring rubber seal is provided between the mating surfaces of the screw plug 5 and the dynamic balance shaft 6 to provide a seal.

[0035] Furthermore, an O-ring is provided on the surface of the piston 2 that is opposite to the inner wall of the dynamic balance shaft 6 to provide a sealing function.

[0036] Furthermore, a stepped through hole is formed on the positioning seat 3, and the seat is fitted onto the outer surface of the dynamic balance shaft 6 through the stepped through hole. The larger end of the stepped through hole is located on the outer surface of the bushing 7, and the stepped surface abuts against the end of the bushing 7. The smaller end of the stepped through hole corresponds to the position of the stepped hole where the screw plug 5 is located.

[0037] Furthermore, the surface of the positioning seat 3 is also provided with a mounting hole communicating with the stepped through hole. The mounting hole corresponds to the smaller end of the diameter of the stepped through hole, and a positioning pin 4 is provided therein. The positioning pin 4 is connected to a hole on the surface of the dynamic balance shaft 6, so that the positioning seat 3 and the dynamic balance shaft 6 are reliably connected, which plays a role in axial positioning of the disc rotor and can well ensure the axial positioning accuracy of the rotor. Specifically, the limiting pin 4 is a cylindrical pin, which has a simple structure and is easy to connect and install.

[0038] Furthermore, the area of ​​the inner surface of the bushing 7 is 3.2 times the surface area of ​​the piston 2, which can transmit the clamping force of the limiting screw 8 to the hydraulic oil through the piston 2, and then to the inner surface of the bushing 7 through the hydraulic oil, so that the outer diameter of the bushing 7 can be reliably and uniformly expanded, which can well ensure the radial positioning accuracy of the rotor.

[0039] Furthermore, the bushing 7 has a thickness of 0.85 mm, which ensures that the disc rotor 9 and the dynamic balancing device can be effectively tightened and meets the required tightening amount within the rotor manufacturing tolerance range.

[0040] Furthermore, the dynamic balancing shaft 6 and bushing 7 are welded using a method that minimizes deformation. After the positioning seat 3 is installed, the entire assembly is precision machined to ensure that the coaxiality and perpendicularity of the dynamic balancing device are within 0.005mm to 0.01mm. This ensures the assembly accuracy of the rotor and the dynamic balancing device, thereby guaranteeing the dynamic balancing accuracy.

[0041] In this embodiment, for ease of installation, the outer surface of the dynamic balancing shaft 6 is axially stepped, with each step meeting strict coaxiality requirements. The steps at both ends are used to connect with the support rollers of the horizontal rigid support dynamic balancing machine. The size of the middle step shaft is larger than that of the two ends. The bushing 7 is welded to the middle step shaft of the dynamic balancing shaft 6, and the dynamic balancing machine belt is installed on the dynamic balancing shaft 6 and located on one side of the bushing 7. The outer surface of the positioning seat 3 has a protrusion 31 for axial positioning with the disc rotor 9.

[0042] In this embodiment, the clamping force generated by tightening the limiting screw 8 is transmitted to the hydraulic oil in the stepped hole through the piston 2, and then acts on the inner surface of the bushing 7, causing the outer surface of the bushing 7 and the disc rotor to expand uniformly, thereby making the dynamic balancing device and the disc rotor fit together without gap, ensuring the dynamic balancing accuracy.

[0043] See Figure 2 As shown, the hydraulic dynamic balancing device provided by the present invention is installed on a disc rotor and its working process is as follows: When the tooling is used, the disc rotor assembly is installed on the dynamic balancing tooling.

[0044] 1) First install piston 2, then install nut 1, and install limit plug 8, but do not tighten it. Use an oiler to inject hydraulic oil into the stepped hole at the right end of the dynamic balance shaft 6. When the hydraulic oil flows out from the bottom, tighten the limit plug 8 while injecting oil to ensure that the oil no longer flows out.

[0045] 2) Turn the dynamic balance shaft 6 over and tighten the mounting plug 5, then wipe away any excess hydraulic oil from the surface of the dynamic balance shaft 6;

[0046] 3) The disc rotor 9 is installed on the dynamic balancing shaft 6 of the dynamic balancing device. The inner diameter of the positioning hole of the disc rotor 9 is in contact with the outer surface of the bushing 7, and the end face is close to the positioning seat 3. The positioning seat 3 performs axial positioning of the disc rotor 9, which improves the dynamic balancing accuracy of the disc rotor 9.

[0047] 4) Tighten the limit plug 8. The hydraulic oil acts on the bushing 7 through the first oil circuit and the second oil circuit respectively, which will evenly expand the outer diameter of the bushing 7, so that the disc rotor 9 and the bushing 7 are evenly tightened, thereby ensuring that the disc rotor 9 and the bushing 7 are in a clearance-free fit.

[0048] In this embodiment, before dynamic balancing, the radial and end face runout of the disc rotor 9 is detected to ensure that the disc rotor is properly aligned with the dynamic balancing device and to ensure the detection accuracy of the dynamic balancing device.

[0049] 5) The 180° overturning compensation method is used to support both the dynamic balancing device and the disc rotor 9 on a horizontal dynamic balancing machine for dynamic balancing.

[0050] In this embodiment, during dynamic balancing, the 180° flip compensation method is used to eliminate the influence of the unbalance of the dynamic balancing device itself on the balancing result, which can well ensure the quality of dynamic balancing.

[0051] 6) After the dynamic balancing is completed, loosen the limit plug 8, release the pressure, and remove the disc rotor 9 from the dynamic balancing device. This avoids hot fitting, press fitting and other process methods, making the operation simple and the balancing efficiency high.

[0052] The hydraulic dynamic balancing device provided by this invention is applicable to disc rotors, especially disc rotors with narrow mating surfaces. By injecting hydraulic oil into the dynamic balancing shaft 6 and acting on the bushing 7 through the first and second oil passages respectively, the outer diameter of the bushing 7 can be uniformly expanded by using hydraulic means, thereby achieving a tight fit between the disc rotor with narrow mating surfaces and the dynamic balancing device, and ensuring the radial and axial positioning accuracy of the rotor, thus ensuring the accuracy of the rotor's dynamic balance detection.

[0053] Furthermore, by adjusting the tightening degree of the limiting screw plug 8, the dynamic balancing device and the disc rotor can be assembled and disassembled within 1 minute, which is simple to operate and has high dynamic balancing efficiency.

[0054] The above embodiments are preferred embodiments of the present invention, but the embodiments of the present invention are not limited to the above embodiments. Any changes, modifications, substitutions, combinations, or simplifications made without departing from the spirit and principle of the present invention shall be considered equivalent substitutions and shall be included within the protection scope of the present invention.

Claims

1. A hydraulic dynamic balancing device, characterized in that: Includes piston, positioning seat, screw plug, dynamic balance shaft, bushing and limit screw plug; The dynamic balancing shaft has stepped holes machined at both ends, and oil ports communicating with the stepped holes are respectively provided on its outer surface. The stepped holes are threaded. A screw plug is installed in the stepped hole at one end of the dynamic balancing shaft, and a piston is installed in the stepped hole at the other end, with a limiting screw plug provided. The end of the limiting screw plug abuts against the end face of the piston and is threadedly engaged with the screw plug and the dynamic balancing shaft. A bushing is provided on the outer surface of the dynamic balancing shaft and on the oil port, and a positioning seat is provided on the dynamic balancing shaft and on the outer surface of the bushing. A nut is also provided in the stepped hole at the other end of the dynamic balancing shaft, and the end of the limiting screw plug passes through the nut and presses against the piston; The positioning seat has a stepped through hole, through which the dynamic balance shaft is fitted onto the outer surface. The larger diameter end of the stepped through hole is located on the outer surface of the bushing, and the stepped surface abuts against the end of the bushing. The smaller diameter end of the stepped through hole corresponds to the position of the stepped hole where the screw plug is located. The surface of the positioning seat is also provided with a mounting hole that communicates with the stepped through hole. The mounting hole corresponds to the position of the smaller end of the diameter of the stepped through hole and is provided with a positioning pin. The positioning pin is connected to a hole provided on the surface of the dynamic balance shaft.

2. The hydraulic dynamic balancing device according to claim 1, characterized in that: The area of ​​the inner surface of the bushing is 3.2 times the surface area of ​​the piston; the thickness of the bushing is 0.85 mm.

3. The hydraulic dynamic balancing device according to claim 1, characterized in that: The inner surface of the dynamic balance shaft corresponding to the nut and the piston is set as an inclined plane.

4. The hydraulic dynamic balancing device according to claim 1, characterized in that: An O-ring rubber seal is provided between the screw plug and the mating surface of the dynamic balance shaft.

5. The hydraulic dynamic balancing device according to claim 1, characterized in that: An O-ring is provided on the surface of the piston that is opposite to the inner wall of the dynamic balance shaft.

6. The hydraulic dynamic balancing device according to claim 1, characterized in that: The outer surface of the dynamic balancing shaft forms a stepped shaft, with the size of the middle stepped shaft being larger than that of the two ends, and the bushing is located on the middle stepped shaft.

7. The hydraulic dynamic balancing device according to claim 1, characterized in that: The coaxiality and perpendicularity of the dynamic balancing device are between 0.005 mm and 0.01 mm.

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