• <tr id="yyy80"></tr>
  • <sup id="yyy80"></sup>
  • <tfoot id="yyy80"><noscript id="yyy80"></noscript></tfoot>
  • 99热精品在线国产_美女午夜性视频免费_国产精品国产高清国产av_av欧美777_自拍偷自拍亚洲精品老妇_亚洲熟女精品中文字幕_www日本黄色视频网_国产精品野战在线观看 ?

    Numerical investigation on damping coefficient of the integral squeeze film damper①

    2022-10-22 02:24:04LIGengHELidongJIAXingyunZHANGYipengWANGJian
    High Technology Letters 2022年3期

    LI Geng(李 耕), HE Lidong, JIA Xingyun, ZHANG Yipeng, WANG Jian

    (Engineering Research Center of Chemical Safety Ministry of Education, Beijing University of Chemical Technology, Beijing 100029, P.R.China)

    Abstract The elimination of rotor vibration is usually achieved by applying additional damping to the system. Squeeze film dampers are widely used in various aerospace and turbine equipments. The research is carried out on flow characteristics in the integral squeeze film dampers (ISFDs). The dynamic response to the operation condition is investigated through the computational fluid dynamics(CFD) model of ISFD. Due to the large pressure loss at the oil inlet, the oil film force only changes slightly with the increase of oil supply pressure, and the damping increases slightly. The vibration amplitude only affects the film force,but has no effect on the damping. The oil film force and damping show an upward tendency with the decrease of thickness of the end seal clearance.

    Key words: integral squeeze film damper (ISFD), numerical method, oil film force, damping coefficient

    0 Introduction

    With the progress of technology and increasing production requirements, the rotation speed of rotating machinery is increasing, and the vibration problem of rotors is becoming more prominent. Applying damping elements in a rotating system can effectively dissipate vibration energy and reduce vibration.

    Squeeze film dampers (SFDs) were proposed by Ref.[1]. Ref.[2] proposed an identification method suitable for nonlinear systems, and put forward a calculation model for the damping coefficient of oil film and the coefficient of inertial force. Through experiments, it was found that the damping coefficient and the coefficient of inertial force of SFD were basically consistent with model predictions.

    In the 1960s, with the application of extrusion film damping, the dynamic characteristics of oil films were studied. Ref.[3] studied the stiffness of oil films and proposed the concept of extrusion films. Ref.[4]studied the influence of cavities on oil film pressure during the motion of oil film pressure. Ref.[5] studied the motion of the oil film-rotor system of the extruded oil film damper, calculated the oil film based on the short bearing assumption, and finally obtained a calculation model of the oil film force.

    Squeeze film dampers have been used in aerospace and turbo machinery[6-10]. In application, it is gradually found that the oil films of SFDs flow circumferentially, leading to a highly nonlinear problem of oil film force[11].

    The integral squeeze film damper (ISFD) was derived from a segmented SFD proposed by Ref.[12].Ref.[13] carried out ISFD internal flow field research by using computational fluid dynamics (CFD) method.Refs[14,15] studied the vibration suppression of the ISFD rotor system and the unbalance vibration suppression of a G-type ISFD rotor system. Ref.[16] carried out ISFD vibration suppression research on gear transmission system. Ref.[17] studied the influence of end seal clearance on ISFD force coefficient.

    1 CFD model of ISFD

    The structure of an ISFD is shown in Fig.1. The inner rim and outer rim constitute the ISFDs. The inner rim and outer rim are connected by 8 S-type elastomers, which are uniformly distributed in circumferential directions. The elastomers divide the oil film into eight discontinuous separate oil films. The ISFD journal does not rotate with the rotor, and the motion form is only precession. Its equations of motion can be expressed as

    whereXandYare the precession displacement values of the ISFD journal in theXandYdirections,eis the rotor eccentricity,Ωis the rotational angular velocity of the bearing, andtis time. Derivate Eqs(1) and (2),to obtain the speed valuesuandvof the journal in theXandYdirections, i.e.,

    Fig.1 Configuration of an ISFD with bearing

    The ISFD possesses 8 segments (squeeze film lands). Long squeeze film lands are fed by oil supply nozzles, and the end seal clearance controls the outflow of the lube oil. The oil of short squeeze film lands comes from the end seal clearance. The oil enters the flow field from the oil supply nozzle and flows out from the end seal clearance. The oil flow path is shown in Fig.2.

    To reduce the calculation time, half of the model is used for calculation due to the symmetry of the model. The process arguments of the investigation ISFD are as follows. The thickness of the squeeze film is 0.2 ×10-3m, the thickness of the end seal clearance is 0.2×10-3m, the semidiameter of the oil supply nozzle is 0.5 ×10-3m, the semidiameter of the outer squeeze film land is 70 ×10-3m, the semidiameter of the inner squeeze film land is 55 ×10-3m, the length of the ISFD is 40 ×10-3m. The grade of the lube oil is ISO VG32 and the oil inlet temperature is 120 F (49 ℃).Referring to standard, the density of the lube oil is 870 kg/m3and the dynamic viscosity of the lube oil is 0.019426 Pa·s.

    Fig.2 Diagram of ISFD internal oil flow

    The CFD model meshes are shown as Fig.3. The element size of the CFD model is controlled to be smaller than 0.3 ×10-3m. The aggregate number of cells in the grid is about 1 500 000.

    Fig.3 ISFD with end seal cover

    It is assumed that the oil is an incompressible Newtonian fluid, the coefficient of the oil viscosity is constant, there is no slip between the fluid and the rim external face, and gravity is not considered in the CFD model. The cavitation phenomenon is not considered in the calculation of hydraulic pressure.

    The squeeze film Reynolds number indicates the inertia of fluid and turbulence effects in ISFDs. The Reynolds equation of the compressed oil film fluid is

    whereρis the density of the oil,μis the viscosity of the oil,Ωis the precession angular velocity of the bearing,andcis the thickness of the squeeze film land. The synchronous circular rotation frequency is 50 Hz and the semidiameter of the rotational track is 6 ×10-6m.

    According to Eq.(5), the Reynolds number is equal to 0.188 and the Reynolds number of turbulence isRe≈2000. The critical Reynolds number is much larger than the Reynolds number calculated under this condition. Therefore, the viscous model is set to laminar in Fluent software.

    The oil flows in from the oil supply nozzle, and flows out of the end seal clearance. The inner rim moves with the bearing, and there is no relative rotation between the inner rim and the outer rim. According to the working principle of ISFD, the boundary conditions (Fig.4) are defined, the oil supply nozzles are set to pressure inlet,the end seal clearances are set to pressure outlet, and other faces are set to wall.

    Fig.4 The meshes of the ISFD

    The inner walls of squeeze film lands are forced to move, so dynamic mesh is set at the inner walls of squeeze film lands. The moving speed of the inner walls of squeeze film lands is the same as the circular whirling of the journal. The outer walls of the squeeze film lands are static.Dynamic mesh model can be used to simulate the flow field since the motion of the boundary shape changes over time. Boundary movement form can be a predefined movement, which can be specified before calculating the speed or angular velocity, the boundary of sport will be decided by the calculation result of the previous step. Mesh update process by the Fluent software according to each boundary changed automatically. When using dynamic mesh model, it is necessary to first define the initial mesh,boundary movement way and specify the regions that participate in the motion.The model boundary function can be used or user defined function (UDF) can define border movements.For anyV, the integral conservation equation of general scalarΦis

    whereVis the control volume, →uis the flow velocity vector, →ugis the mesh velocity of the moving mesh, Γ is the diffusion coefficient,SΦis the source term ofΦ,?Vis the boundary of the control volumeV.

    By using a first-order backward difference formula, the time derivative term in Eq.(6) can be written as Eq.(7). In Eq.(7),n+ 1 andnrepresent different time level. The (n+1 )th time level volumeVn+1is computed from Eq.(8).

    where dV/dtis the volume time derivative of the control volumeV.In order to satisfy the mesh conservation law, the volume time derivative of the control volume is computed from Eq.(9), wherenfis the number of the faces on the control volumeV.The dot product →ug,j·→Ajon each control volume face is calculated as

    2 Results of the computational simulations

    In order to study the influence of operation condition on oil film force, a single variable numerical simulation is carried out. The variation in forces under different conditions during one period is studied. It is hereby explained that as the model used in the calculation is a scaled-down model and the procession amplitude is set to be small in order to prevent the overlap of the model boundary which will cause negative mesh,the calculation force is small.

    2. 1 Influence of the thickness of the end seal clearance on oil film force

    Oil flows out from the end seal clearance. The thickness of the end seal clearance determines how easy it is for oil to flow out. In other words, the thickness of the end seal clearance plays an important role in oil flow, and affects the oil film forces.

    Numerical simulations for different thickness of the end seal clearance are carried out. Boundary conditions: pressure inlet boundary is 0.10 MPa, pressure outlet boundary is 0, the eddy amplitude is 6 μm. The pressure distributions for four values of the thickness of the end seal clearance are depicted in Fig.5. As seen from Fig.5, it is clear that total pressure increases with the decreases in the thickness of end seal.And the oil film force increases. The pressure distribution is more uniform throughout the ISFD. Fluid flowing is more difficult with thinner end seal clearance.

    The velocity magnitude for four values of the thickness of the end seal clearance are depicted in Fig.6. The velocity magnitude decreases with the decreases in the thickness of end seal. The maximum velocity magnitude is 16. 01 m/s for 0. 25 mm of the thickness of the end seal clearance in ISFD, while the maximum velocity magnitude is 7.156 m/s for 0.1 mm of the thickness of the end seal clearance in ISFD. The thin end seal clearance severely impedes the flow of oil.

    The time history of the short oil film force in the radial and tangential directions for four values of the thickness of the end seal clearance is depicted in Fig.7.

    Fig.5 Pressure distribution under different thickness of the end seal clearance

    Fig.6 Effect of thickness of the end seal clearance on velocity distribution in ISFD

    As can be seen from Fig.7, the magnitude of oil film force changes inXdirection andYdirection increases with the end seal clearance getting thinner.The magnitude of oil film force changes inXandYdirections are 147.38 N and 146.39 N when the end seal clearance is 0.1 mm. And the magnitudes are 21.70 N and 21.23 N when the end seal clearance is 0.25 mm.This is because as the end seal thickness becomes thinner, the flow of oil becomes more difficult, the obstruction increases, and the force on the oil film also increases.

    Fig.7 Time history of oil film force in X and Y directions under different end seal clearances

    2.2 Influence of vibration amplitude on oil film force

    The whirl of the rotor is transmitted to the bearing, which in turn is transmitted to ISFD. In general,the amplitude of rotor whirl is not fixed. In order to study the influence of rotor vibration amplitude on oil film force,different vibration amplitudes are employed.

    Fig.8 Pressure distributions under different vibration amplitudes

    The simulations for four values of the vibration amplitude (6 μm,8 μm,10 μm and 12 μm) are carried out. Boundary conditions are that the pressure inlet boundary is 0.10 MPa and the pressure outlet boundary is 0. The pressure distribution in ISFD under different vibration amplitude is depicted in Fig.8. With the increase in rotor vibration amplitudes,the pressure distributions of ISFD for four values of vibration amplitudes are similar.

    The velocity magnitude in ISFD under different vibration amplitudes is depicted in Fig.9. The maximum velocity magnitudes for the 4 types of vibration amplitudes are in the range of 14.40 -14.48 m/s, therefore, the change of the vibration amplitude is not the reason of the increase in the internal flow velocity of ISFD. The time history of oil film force inXdirection is depicted in Fig.10(a) and the time history of oil film force inYdirection is depicted in Fig.10(b).

    Fig.9 Velocity under different vibration amplitudes

    Fig.10 Time history of oil film force in X and Y directions under different vibration amplitudes

    It can be seen from Fig.10(a) and 10(b) that with the increase of vibration amplitude,the fluctuation of the oil film forces in bothXdirection andYdirection increases. When the vibration amplitude is 6 μm, the magnitude of oil film force changes inXandYdirection are 33. 42 N and 32. 90 N. When the vibration amplitude is 12 μm, the changes of the magnitude of oil film force inXandYdirections are 66.11 N and 66.06 N.

    2.3 Influence of oil supply pressure on oil film force

    Fig.11 Pressure distribution under different oil supply pressures

    Numerical simulations are performed with the values of oil supply pressure changes (0.08 MPa, 0.10 MPa,0.12 MPa and 0.14 MPa). The pressure distribution is depicted in Fig.11. As seen from Fig.11, the pressure of the squeeze film on ISFD is affected by rotor whirl,and the distribution difference occurs. The pressure in the squeezed position is bigger than that in the unsqueezed position. The pressure distribution between adjacent oil films is approximately continuous, ensuring the continuity of the ISFD’s oil film forces in the circumferential region. However, with the increase of oil supply pressure, the force on the oil film does not increase significantly. This is due to the significant loss of oil pressure from the inlet to the oil film,resulting in a similar pressure distribution across the oil film.

    The velocity is depicted in Fig.12. The largest velocity magnitude increases from 12.85 m/s to 17.12 m/s as the oil supply pressure increases from 0.08 MPa to 0.14 MPa. It is obvious that the increase in velocity magnitude is caused by the enhancement of oil supply pressure. To analyze the changes in oil film force, the long squeeze film land and short squeeze film land are taken for pressure integration to obtain the oil film force. Transient analysis is used to compute the time dependence of the oil film force. The time history of oil film force inXdirection is depicted in Fig.13(a) and the time history of oil film force inYdirection is depicted in Fig.13(b).

    It can be seen from Fig.13 that the oil film force changes periodically with the rotor whirl, and the change period is the same as that of the rotor whirl.The force phase difference betweenXdirection andYdirection is π/2. Since the pressure distribution on the oil film is similar, there is no significant difference in the oil film forces under each oil supply pressure inXandYdirections.

    3 Damping coefficient calculation

    The study of oil film force of squeeze film damper is the basis of analysis and design of squeeze film damper. From the mathematical point of view, the core problem of dynamic characteristics of squeeze oil film is to solve the pressure distribution law of oil film in the Reynolds equation. The transient Reynolds equation of the squeeze film damper is

    Fig.12 Velocity under different oil supply pressures

    Fig.13 Time history of oil film force in X and Y directions under different oil supply pressures

    The Reynolds equation is binary quadratic inhomogeneous nonlinear partial differential equation with variable coefficients, which is difficult to solve. Before the computer emerging, in order to obtain the distribution of oil film pressure, people had made a lot of assumptions and simplifications on the Reynolds equation. The short bearing hypothesis and long bearing hypothesis are widely used.

    When there is no end sealing device at both ends of the damper, and the pressure at both ends of the damper is the same as the external pressure and the slender-diameter ratio is less than 0.25, the hypothesis of short bearing is in good agreement with the actual results.The change of pressure gradient along the circumference is much smaller than the change of pressure in

    According to the pressure distribution of the extruded oil film damper, eight dynamic characteristic coefficients can be derived under the condition of semi-oil film and full oil film.Under semi-oil film condition,the eight dynamic characteristic coefficients of the short bearing squeeze film damper of the concentric precession are as Eq.(13). Similarly,under the condition of full oil film, the eight dynamic characteristic parameters of concentric precession short bearing squeeze film damper are expressed as Eq.(14).

    When the mass center of the journal precession is steadily around the center of the shaft, and the trajectory of the shaft center is a standard circle, the eight dynamic parameters of the extrusion film damper can be simplified to two equivalent damping parameters.For semi-oil film condition,they are shown in Eq.(16).And under full oil film condition, they are shown as Eq.(17).

    Both short bearing hypothesis and long bearing hypothesis have their own scope of application, and their accuracy and scope of application are often inversely proportional. Both short bearing hypothesis and long bearing hypothesis do not apply to ISFDs. As seen from Fig.13, it is obvious that the thickness of end seal clearance has big effect on ISFD’s pressure distribution. This means that the end seal clearance will affect stiffness and damping, while there is no end seal clearance in Eqs(13), (14), (16) and (17). So another formula for calculating damping coefficient is proposed. The oil film’s equivalent damping coefficient is

    Numerical simulation has been performed to verify the accuracy of the Eq.(18). CFD model of ISFD fluid domain was constructed by referring to Ref.[18].

    Fig.14 CFD model of ISFD fluid domain referring to Ref.[18]

    The operation condition parameters are the same as those in Ref.[18]. The oil supply pressure is 0.14 MPa,and vibration amplitude is 6.35 μm, and the lubricant is ISO VG32 and the temperature is 49 ℃. Numerical simulation results are substituted into Eq.(18), and the average damping coefficient of the ISFD under this operation condition is 33 886.16 N·s/m. Damping coefficient in Ref.[18] under this operation condition is 37 000 N·s/m. The similarity of the calculated results is 91.58%. In another operation condition, the damping coefficient is 138 418 N·s/m, and the damping coefficient in Ref.[18] is 152 000 N·s/m. The similarity of the calculated results is 91. 06%. Some subtle structural differences in the model and slight differences in lubricant viscosity limit the higher similarity of the two damping coefficients calculated. The similarity of more than 90% proves the reliability of Eq.(18).

    3. 1 Influence of the thickness of the end seal clearance on damping coefficient

    The damping changes four times in a period of journal precession, and the damping is periodic, because the oil film is arranged symmetrically in four groups in ISFD. Increasing the oil supply pressure is an effective way to improve the ISFD damping.

    The damping coefficients of the ISFD under different thickness of the end seal clearance are depicted in Fig.15. The damping coefficient is 5620.09 N·s/m when the end seal clearance is 0.25 mm. When the end seal clearance is reduced to 0.10 mm, the damping coefficient increases to 39 226. 8 N·s/m. Thin end seal clearance causes large damping. The damping coefficients tend to increase with the decrease of end seal clearance thickness. The end seal clearance becomes thinner, the oil is difficult to flow, and the oil film hinders the precession.

    Fig.15 Damping coefficients under different end seal clearances

    3. 2 Influence of the vibration amplitude on damping coefficient

    The oil film forces calculated in subsection 2. 2 are processed and substituted into Eq.(18). The calculated results are shown in Fig.16.

    Fig.16 Damping coefficients under different vibration amplitudes

    As can be seen from Fig.16,the damping provided by ISFD does not increase with the increase of vibration amplitude. The damping coefficient is 8758.24 N·s/m when the vibration amplitude is 6 μm. And the damping coefficient rises to 8811.16 N·s/m when the vibration amplitude is 12 μm. Although the oil film force increased, the equivalent damping is inversely proportional to the vibration amplitude, and the equivalent damping is almost constant under the interaction of these 2 factors.

    3.3 Influence of the oil supply pressure on damping coefficient

    The oil film forces calculated in subsection 2. 3 are processed and substituted into Eq.(18). The damping coefficients of ISFD under different oil supply pressures are shown in Fig.17.

    Fig.17 Damping coefficients under different oil supply pressures

    As shown in Fig.17, the damping of ISFD is slightly increased with the increase of oil supply pressure. This is due to the pressure loss at inlet. When the oil supply pressure is 0.08 MPa,the average damping is 8740 N·s/m. When the oil supply pressure increases to 0.12 MPa,the average damping is 8798 N·s/m.

    4 Conclusions

    The influences of oil thickness of the end seal clearance,vibration amplitude,and oil supply pressure on the ISFD oil film force and damping are presented by numerical method in this research, and the main conclusions are as follow.

    (1) The oil film forces are very sensitive to the end seal clearance. In general, as the thickness of the end sealing clearance decreases, oil flow is obstructed within the ISFD, and internal pressure within the ISFD is increased. The tangential forces of squeeze film shows opposite trends with the decrease of end seal clearance. Damping is also very sensitive to the end seal clearance. When the end seal clearance is reduced to a half of its original size, the damping is increased by 5 times.

    (2) With the increases of the vibration amplitude,the amplitude of oil film force fluctuation inXdirection andYdirection increases. The damping of ISFD is almost constant under different vibration amplitude. In other words, the increase of vibration amplitude does not lead to the increase of the damping coefficient, but does lead to the instability of the oil film force.

    (3) With the increases of the oil supply pressure,there are more high-pressure parts in the ISFD pressure distribution. Damping is affected by tangential forces of oil film. Damping shows an increased tendency when oil supply pressure increases due to the increase of the tangential forces.

    (4) In conclusion, it is found that the necessary condition for the increase of the damping is that the oil film force needs to increase. Making the flow of oil more difficult is an effective way to increase damping.

    亚洲欧洲日产国产| 寂寞人妻少妇视频99o| 亚洲熟女精品中文字幕| 18禁在线播放成人免费| 亚洲国产最新在线播放| 女的被弄到高潮叫床怎么办| 国产伦在线观看视频一区| 永久免费av网站大全| 亚洲av成人精品一二三区| 校园人妻丝袜中文字幕| 99热这里只有是精品在线观看| videos熟女内射| 成人免费观看视频高清| 一区二区av电影网| 日日摸夜夜添夜夜爱| 国产69精品久久久久777片| 99热这里只有是精品50| 高清午夜精品一区二区三区| 中国三级夫妇交换| 美女cb高潮喷水在线观看| 在线亚洲精品国产二区图片欧美 | 日韩欧美一区视频在线观看 | 黄色视频在线播放观看不卡| 久久国产精品男人的天堂亚洲 | 80岁老熟妇乱子伦牲交| 蜜臀久久99精品久久宅男| 国产亚洲午夜精品一区二区久久| 2021少妇久久久久久久久久久| 久久精品国产鲁丝片午夜精品| 欧美老熟妇乱子伦牲交| av播播在线观看一区| 伦理电影免费视频| 啦啦啦啦在线视频资源| 成年人免费黄色播放视频 | 亚洲欧美日韩卡通动漫| 久久精品夜色国产| 国产成人一区二区在线| 国产欧美日韩综合在线一区二区 | 精品亚洲成国产av| 亚洲av日韩在线播放| 日韩大片免费观看网站| 在线 av 中文字幕| 少妇被粗大的猛进出69影院 | 涩涩av久久男人的天堂| 大话2 男鬼变身卡| 激情五月婷婷亚洲| 三级国产精品片| 少妇被粗大的猛进出69影院 | 久久国产精品男人的天堂亚洲 | 亚洲在久久综合| 亚洲精品,欧美精品| av一本久久久久| 亚洲欧美中文字幕日韩二区| 亚洲精品一二三| 亚洲av中文av极速乱| 97在线视频观看| 五月天丁香电影| 成人美女网站在线观看视频| 两个人的视频大全免费| 国产亚洲午夜精品一区二区久久| 国产中年淑女户外野战色| 久久精品熟女亚洲av麻豆精品| 中文字幕人妻丝袜制服| 亚洲欧洲日产国产| 亚洲av综合色区一区| 99国产精品免费福利视频| 国产精品无大码| 综合色丁香网| 97在线人人人人妻| 纵有疾风起免费观看全集完整版| 国产国拍精品亚洲av在线观看| 中文字幕精品免费在线观看视频 | 91精品国产九色| 一个人看视频在线观看www免费| 婷婷色麻豆天堂久久| 日韩强制内射视频| 国产欧美日韩一区二区三区在线 | 国产一区二区在线观看日韩| 免费观看无遮挡的男女| 国产一区有黄有色的免费视频| 国产男女超爽视频在线观看| 国产亚洲欧美精品永久| 麻豆乱淫一区二区| 黄色一级大片看看| 少妇人妻久久综合中文| 亚洲va在线va天堂va国产| 丝袜喷水一区| freevideosex欧美| 国产成人免费无遮挡视频| 亚洲精品国产av蜜桃| 九草在线视频观看| 亚洲av.av天堂| 啦啦啦在线观看免费高清www| 我要看日韩黄色一级片| 老司机亚洲免费影院| 久久精品久久久久久久性| 亚洲,欧美,日韩| 日本与韩国留学比较| 青春草亚洲视频在线观看| 麻豆乱淫一区二区| .国产精品久久| 99热国产这里只有精品6| 国产精品久久久久久av不卡| 成年女人在线观看亚洲视频| 久久久午夜欧美精品| 久久人人爽av亚洲精品天堂| 特大巨黑吊av在线直播| 免费看光身美女| 69精品国产乱码久久久| 亚洲欧美清纯卡通| av视频免费观看在线观看| 欧美亚洲 丝袜 人妻 在线| 综合色丁香网| 欧美精品高潮呻吟av久久| 欧美精品人与动牲交sv欧美| 国产黄片视频在线免费观看| 又黄又爽又刺激的免费视频.| 肉色欧美久久久久久久蜜桃| av天堂久久9| 香蕉精品网在线| 黄色日韩在线| 在线观看三级黄色| 一级av片app| 欧美日本中文国产一区发布| 国内揄拍国产精品人妻在线| 国内精品宾馆在线| 人妻一区二区av| 精华霜和精华液先用哪个| av卡一久久| 高清在线视频一区二区三区| 一级,二级,三级黄色视频| 久久人人爽av亚洲精品天堂| 又黄又爽又刺激的免费视频.| 亚洲欧美精品自产自拍| 多毛熟女@视频| 日韩一区二区三区影片| 亚洲成人av在线免费| 国产精品人妻久久久影院| 国产精品99久久99久久久不卡 | 美女大奶头黄色视频| 国产日韩一区二区三区精品不卡 | 中文在线观看免费www的网站| av.在线天堂| 多毛熟女@视频| 免费看av在线观看网站| 男女免费视频国产| 一级二级三级毛片免费看| 国产精品蜜桃在线观看| 边亲边吃奶的免费视频| 国产成人免费无遮挡视频| 丝袜喷水一区| 成人黄色视频免费在线看| 男男h啪啪无遮挡| 免费少妇av软件| 蜜臀久久99精品久久宅男| 日日爽夜夜爽网站| 免费人成在线观看视频色| 亚洲中文av在线| 国产精品国产三级国产av玫瑰| av不卡在线播放| 秋霞伦理黄片| 精品国产一区二区久久| 亚洲精品成人av观看孕妇| 国产欧美亚洲国产| 久久久国产一区二区| 国产69精品久久久久777片| 免费看光身美女| 日韩制服骚丝袜av| 三级国产精品片| 成人亚洲精品一区在线观看| 免费久久久久久久精品成人欧美视频 | av.在线天堂| 欧美少妇被猛烈插入视频| 免费看日本二区| 99视频精品全部免费 在线| 国产亚洲91精品色在线| 国产一级毛片在线| 欧美精品一区二区大全| 91精品国产国语对白视频| 欧美精品高潮呻吟av久久| 免费高清在线观看视频在线观看| 一区二区三区免费毛片| 赤兔流量卡办理| 欧美日韩视频精品一区| 人妻少妇偷人精品九色| 欧美最新免费一区二区三区| 国产日韩一区二区三区精品不卡 | 中文字幕人妻熟人妻熟丝袜美| 制服丝袜香蕉在线| 免费观看无遮挡的男女| 久久久欧美国产精品| 视频区图区小说| a 毛片基地| 人妻制服诱惑在线中文字幕| 久久人人爽人人爽人人片va| 亚洲图色成人| 中文欧美无线码| 最近手机中文字幕大全| 高清视频免费观看一区二区| 国产国拍精品亚洲av在线观看| 三级国产精品片| 亚洲成人av在线免费| 亚洲精品国产成人久久av| 蜜桃久久精品国产亚洲av| 黑丝袜美女国产一区| 亚洲天堂av无毛| 在线观看国产h片| 久久久久网色| 成人综合一区亚洲| 亚洲精品aⅴ在线观看| 嫩草影院新地址| 亚洲精品一区蜜桃| 国产真实伦视频高清在线观看| 嫩草影院入口| 中国美白少妇内射xxxbb| 精品一区二区免费观看| 国产日韩欧美视频二区| 国产成人精品无人区| 91在线精品国自产拍蜜月| videos熟女内射| 自拍偷自拍亚洲精品老妇| 国产黄片视频在线免费观看| 免费看不卡的av| 精品久久久久久电影网| 免费在线观看成人毛片| 国产精品久久久久久久电影| 中国国产av一级| 国产乱人偷精品视频| freevideosex欧美| 久久久久精品性色| 美女脱内裤让男人舔精品视频| 国产男女内射视频| av在线app专区| 只有这里有精品99| av不卡在线播放| 精品人妻熟女毛片av久久网站| 中国三级夫妇交换| 自线自在国产av| 亚洲精品乱码久久久久久按摩| 日日摸夜夜添夜夜爱| 久热这里只有精品99| 亚洲怡红院男人天堂| 最近的中文字幕免费完整| 大陆偷拍与自拍| 久久综合国产亚洲精品| 99久久精品一区二区三区| 日本色播在线视频| 国产淫片久久久久久久久| 女人久久www免费人成看片| 男女国产视频网站| 黄色欧美视频在线观看| 精品一区二区免费观看| 国产精品久久久久久精品古装| 熟女电影av网| 久久 成人 亚洲| 国产在线男女| 亚洲精品色激情综合| 极品教师在线视频| 高清黄色对白视频在线免费看 | 国产高清不卡午夜福利| 高清不卡的av网站| 欧美激情国产日韩精品一区| 国产亚洲午夜精品一区二区久久| 国产亚洲av片在线观看秒播厂| 亚洲av中文av极速乱| 中文字幕精品免费在线观看视频 | av专区在线播放| 成人国产麻豆网| 国产日韩欧美视频二区| 日韩av不卡免费在线播放| 99九九在线精品视频 | 日本av手机在线免费观看| 免费少妇av软件| 国内揄拍国产精品人妻在线| 青春草国产在线视频| 永久网站在线| 免费观看无遮挡的男女| 免费看光身美女| 日韩av免费高清视频| 高清在线视频一区二区三区| 亚洲欧美成人综合另类久久久| 51国产日韩欧美| 亚洲av二区三区四区| 丰满乱子伦码专区| 在线观看一区二区三区激情| 久久久久久伊人网av| 如何舔出高潮| 最新的欧美精品一区二区| 热99国产精品久久久久久7| 性高湖久久久久久久久免费观看| 午夜久久久在线观看| 乱码一卡2卡4卡精品| 街头女战士在线观看网站| 日韩亚洲欧美综合| .国产精品久久| 一级二级三级毛片免费看| 黄色欧美视频在线观看| xxx大片免费视频| 十八禁高潮呻吟视频 | 亚洲国产欧美日韩在线播放 | 三上悠亚av全集在线观看 | 建设人人有责人人尽责人人享有的| 国产av码专区亚洲av| 啦啦啦视频在线资源免费观看| 日韩电影二区| 午夜激情久久久久久久| 久久久国产欧美日韩av| 一本—道久久a久久精品蜜桃钙片| 嘟嘟电影网在线观看| 汤姆久久久久久久影院中文字幕| 亚洲国产色片| 你懂的网址亚洲精品在线观看| 嫩草影院入口| 十八禁网站网址无遮挡 | 伦精品一区二区三区| 丰满乱子伦码专区| 青春草视频在线免费观看| 亚洲怡红院男人天堂| 女的被弄到高潮叫床怎么办| 婷婷色综合大香蕉| 久久久久国产精品人妻一区二区| 国产精品一区二区性色av| 卡戴珊不雅视频在线播放| 久久精品国产亚洲av涩爱| 亚洲精品国产色婷婷电影| 成年女人在线观看亚洲视频| 国产精品免费大片| 男女无遮挡免费网站观看| 国产精品国产三级国产av玫瑰| 纯流量卡能插随身wifi吗| 中文欧美无线码| 久久精品国产亚洲网站| 亚洲真实伦在线观看| 日韩 亚洲 欧美在线| 欧美日韩一区二区视频在线观看视频在线| 王馨瑶露胸无遮挡在线观看| 夫妻性生交免费视频一级片| 99九九在线精品视频 | 亚洲va在线va天堂va国产| 亚洲av二区三区四区| 综合色丁香网| 看免费成人av毛片| 国产av国产精品国产| 亚洲,欧美,日韩| 久久久精品94久久精品| 久久毛片免费看一区二区三区| 18禁裸乳无遮挡动漫免费视频| 国产欧美日韩一区二区三区在线 | 色视频在线一区二区三区| 18+在线观看网站| 国产国拍精品亚洲av在线观看| 新久久久久国产一级毛片| 国产伦精品一区二区三区视频9| 国产精品久久久久久精品古装| 日韩av在线免费看完整版不卡| 中文字幕精品免费在线观看视频 | 欧美激情国产日韩精品一区| 丰满迷人的少妇在线观看| 蜜桃在线观看..| 91久久精品国产一区二区三区| 久久精品国产鲁丝片午夜精品| 日韩中字成人| 女的被弄到高潮叫床怎么办| 最新中文字幕久久久久| 中文字幕免费在线视频6| 自拍偷自拍亚洲精品老妇| 国产黄色视频一区二区在线观看| 中文天堂在线官网| 99热6这里只有精品| 日韩av在线免费看完整版不卡| 成年人午夜在线观看视频| 欧美区成人在线视频| 国产免费视频播放在线视频| 黑丝袜美女国产一区| 国模一区二区三区四区视频| 伊人久久精品亚洲午夜| 久久青草综合色| 欧美+日韩+精品| a级毛片免费高清观看在线播放| 日韩电影二区| 日韩强制内射视频| 在线精品无人区一区二区三| 亚洲,一卡二卡三卡| 免费大片黄手机在线观看| 中文字幕av电影在线播放| 伦理电影大哥的女人| av在线播放精品| 国产欧美亚洲国产| av国产久精品久网站免费入址| 黄色一级大片看看| 午夜福利视频精品| 你懂的网址亚洲精品在线观看| 能在线免费看毛片的网站| 在线天堂最新版资源| 亚洲国产最新在线播放| 大话2 男鬼变身卡| 国产 精品1| 亚洲一区二区三区欧美精品| 婷婷色av中文字幕| 国内揄拍国产精品人妻在线| 国产深夜福利视频在线观看| 一本—道久久a久久精品蜜桃钙片| 中文字幕人妻熟人妻熟丝袜美| 精品久久久久久电影网| 国产日韩欧美在线精品| a级毛片免费高清观看在线播放| 国产伦精品一区二区三区四那| 国产精品免费大片| 色5月婷婷丁香| 欧美性感艳星| a级一级毛片免费在线观看| 国产熟女午夜一区二区三区 | av线在线观看网站| 少妇人妻一区二区三区视频| 久久精品国产亚洲网站| 欧美日韩精品成人综合77777| 亚洲成人一二三区av| 哪个播放器可以免费观看大片| 亚洲av综合色区一区| 少妇被粗大猛烈的视频| 免费黄网站久久成人精品| 一区二区av电影网| 亚洲第一av免费看| 国产亚洲最大av| 伦精品一区二区三区| 国精品久久久久久国模美| .国产精品久久| 能在线免费看毛片的网站| 免费观看在线日韩| 欧美精品亚洲一区二区| 亚洲美女黄色视频免费看| 欧美日韩亚洲高清精品| 日本vs欧美在线观看视频 | 精品久久国产蜜桃| 蜜桃在线观看..| 日本av手机在线免费观看| 精品酒店卫生间| 一区二区三区免费毛片| 日本免费在线观看一区| 狂野欧美白嫩少妇大欣赏| 这个男人来自地球电影免费观看 | 少妇被粗大的猛进出69影院 | 男人舔奶头视频| 妹子高潮喷水视频| 国产精品秋霞免费鲁丝片| 国产色爽女视频免费观看| 大码成人一级视频| 国产精品人妻久久久久久| 久久久久人妻精品一区果冻| 黄色一级大片看看| 最后的刺客免费高清国语| a级毛片在线看网站| 最近的中文字幕免费完整| 在线观看免费日韩欧美大片 | 另类亚洲欧美激情| 日日爽夜夜爽网站| 欧美xxⅹ黑人| 久久精品国产亚洲网站| 亚洲欧洲国产日韩| 大又大粗又爽又黄少妇毛片口| 一级片'在线观看视频| 蜜桃在线观看..| 久久97久久精品| 美女脱内裤让男人舔精品视频| 大香蕉97超碰在线| 这个男人来自地球电影免费观看 | 亚洲国产精品999| 天堂8中文在线网| 亚洲经典国产精华液单| 亚洲国产精品成人久久小说| 免费高清在线观看视频在线观看| 成人二区视频| 最近最新中文字幕免费大全7| 99热这里只有是精品50| 黑人猛操日本美女一级片| 十八禁网站网址无遮挡 | 亚洲欧美一区二区三区黑人 | 亚洲av中文av极速乱| 欧美成人精品欧美一级黄| av免费在线看不卡| 国产在线男女| 午夜免费鲁丝| 美女脱内裤让男人舔精品视频| 色婷婷久久久亚洲欧美| 国产午夜精品久久久久久一区二区三区| 女的被弄到高潮叫床怎么办| 亚洲精品色激情综合| 亚洲精华国产精华液的使用体验| 国产黄片视频在线免费观看| 午夜免费男女啪啪视频观看| 国产成人免费无遮挡视频| 制服丝袜香蕉在线| 欧美3d第一页| 极品人妻少妇av视频| 午夜免费观看性视频| 久久久久久久精品精品| 精品熟女少妇av免费看| 丰满饥渴人妻一区二区三| 草草在线视频免费看| 黄色欧美视频在线观看| 校园人妻丝袜中文字幕| 免费观看在线日韩| 性色av一级| 九九久久精品国产亚洲av麻豆| av在线老鸭窝| 国产亚洲最大av| 国产黄片美女视频| 水蜜桃什么品种好| 免费播放大片免费观看视频在线观看| 国产色爽女视频免费观看| 亚洲欧洲日产国产| 性高湖久久久久久久久免费观看| 一本一本综合久久| 久久国产乱子免费精品| 涩涩av久久男人的天堂| 国产日韩一区二区三区精品不卡 | 两个人的视频大全免费| 久久精品久久久久久久性| 七月丁香在线播放| 久久av网站| 午夜老司机福利剧场| 男的添女的下面高潮视频| 91精品国产九色| 在线观看三级黄色| 国产成人freesex在线| 2021少妇久久久久久久久久久| 男人舔奶头视频| 黑人巨大精品欧美一区二区蜜桃 | www.色视频.com| 一级毛片aaaaaa免费看小| 最近中文字幕高清免费大全6| 欧美区成人在线视频| 国产成人aa在线观看| 69精品国产乱码久久久| 久久狼人影院| 卡戴珊不雅视频在线播放| 久久久久久久久久久久大奶| 中文字幕免费在线视频6| 精品午夜福利在线看| 久久亚洲国产成人精品v| 精品久久久精品久久久| 国产黄频视频在线观看| 欧美精品高潮呻吟av久久| 欧美日韩视频高清一区二区三区二| 国产男女超爽视频在线观看| 免费在线观看成人毛片| 色吧在线观看| 黄色欧美视频在线观看| 日本爱情动作片www.在线观看| 全区人妻精品视频| 午夜激情福利司机影院| 久久久久久久久大av| 赤兔流量卡办理| 黄色毛片三级朝国网站 | 韩国av在线不卡| 日韩制服骚丝袜av| 熟女av电影| 午夜福利影视在线免费观看| 欧美精品一区二区免费开放| 欧美一级a爱片免费观看看| 国产日韩一区二区三区精品不卡 | 久久久久久久久久久久大奶| 亚洲不卡免费看| 2018国产大陆天天弄谢| 性高湖久久久久久久久免费观看| 男人爽女人下面视频在线观看| 只有这里有精品99| 亚洲av成人精品一区久久| 久久久久人妻精品一区果冻| 夜夜看夜夜爽夜夜摸| 婷婷色av中文字幕| 九色成人免费人妻av| 免费看光身美女| 在现免费观看毛片| av免费观看日本| 99久久精品一区二区三区| 久久国产亚洲av麻豆专区| 亚洲欧美精品自产自拍| 国产欧美日韩一区二区三区在线 | 日韩 亚洲 欧美在线| 最新中文字幕久久久久| 秋霞伦理黄片| 欧美日韩国产mv在线观看视频| 男人舔奶头视频| 日本91视频免费播放| 最近中文字幕高清免费大全6| 国产免费福利视频在线观看| 久久久久久久国产电影| 国产视频首页在线观看| 高清午夜精品一区二区三区| 亚洲精品456在线播放app| 精品久久国产蜜桃| 国产黄片美女视频| 国产亚洲一区二区精品| 久久久国产一区二区| 国产精品一区二区在线观看99| 狂野欧美白嫩少妇大欣赏| 亚洲国产av新网站| 伦精品一区二区三区| 下体分泌物呈黄色| 久久久久久久久大av| 尾随美女入室| 中文乱码字字幕精品一区二区三区| 最黄视频免费看| 亚洲人成网站在线观看播放| 日韩免费高清中文字幕av| 少妇被粗大猛烈的视频| 人妻 亚洲 视频| 婷婷色综合www| 国产欧美日韩综合在线一区二区 | 亚洲自偷自拍三级| 国产一区二区三区综合在线观看 | 人妻人人澡人人爽人人| 国产熟女午夜一区二区三区 | 成人毛片a级毛片在线播放|