Closed swash plate vane orifice heat balance hydraulic damper

Abstract

This invention discloses a closed-type gyratory blade throttling orifice type thermal balance hydraulic damper, which is less affected by temperature changes and has high damping efficiency. This is achieved through the following technical solution: a spring cylinder equipped with a hydraulic thrust spring divides the outer cylinder damping cavity into a high-pressure chamber and a low-pressure chamber with symmetrical left and right gyratory blades; the working medium in the compensation chamber D1 flows through the stepped annular groove D2 in the front end cover, enters the radial oil hole D4 of the piston neck cylinder along the end oil hole D3, connects to the oil supply path D5 and the variable throttling orifice D6 and damping hole D7, and supplements the gyratory blade oil supply path D8; the oil supply path formed by D1 to D8 flows through the symmetrical left oblique diameter oil path C1-C2 of the drum cylinder in the middle of the blade, flows into the first annular groove C3, connects to the variable damping hole C4, enters the second annular groove C5, and then enters the right oblique diameter oil path C6-C7 of the rotating gyratory shaft, flowing into the low-pressure chamber; balancing the damping pressure of thermal expansion and contraction in the low and high pressure chambers, the damper performance remains stable when the ambient temperature changes.

Description

Technical Field

[0001] This invention relates to a closed-type oscillating blade throttling orifice type thermal balance hydraulic damper that can be widely used in various industries such as aviation, aerospace, automobile, nuclear power, thermal power, steel, petrochemical construction, road and bridge railway and mechanical engineering, ground moving vehicles, and aircraft control systems. Background Technology

[0002] Many mechanical mechanisms experience vibrations and impacts during operation, leading to reduced system efficiency, shortened lifespan, and in severe cases, damage to the mechanical structure. Some mechanisms, due to their low damping, suffer from poor or unstable motion, even resonance, resulting in mechanism failure. To mitigate these effects, damping devices are typically incorporated into the mechanism to effectively protect it and improve system efficiency. A damper is a device that provides resistance to motion and dissipates kinetic energy. Various frictional and other hindering effects caused by vibration attenuation are called damping. A "special" component placed on a structural system to provide resistance to motion and dissipate kinetic energy is called a damper. The working process of a damper is a dissipation process, converting mechanical energy into heat energy to reduce vibration or suppress excessively rapid motion in the mechanical system.

[0003] Currently, commonly used dampers mainly include eddy current dampers, viscoelastic dampers, viscous dampers, and hydraulic dampers. The main advantages of eddy current dampers are their simple structure, high reliability, lack of electromagnetic pollution (excluding electromagnetic contamination), and convenient adjustment. Their main disadvantages are insufficient damping force, large product size and weight, and the risk of jamming. Viscoelastic dampers primarily offer simple structure and high reliability. Their disadvantages include a larger size and difficulty in adjusting the matching relationship between damping force and elastic force.

[0004] Viscous dampers are made based on the principle of fluid motion, particularly the viscous resistance generated when fluid passes through a throttling orifice. They are a type of damper related to stiffness and velocity. Generally, they consist of a cylinder, piston, piston rod, bushing, medium, and pin. The piston reciprocates within the cylinder, which has a damping structure. The cylinder is filled with a fluid damping medium. When the fluid passes through the damping orifice, viscous resistance is generated, causing relative motion between the cylinder and piston. The volume on the left side of the piston decreases, forcing the viscous damping medium to flow through the damping orifice to the right chamber. The shear flow generates damping force, causing the fluid to move to the right under a certain resistance. The fluid can only flow through the throttling valve under pressure differential. During the flow, energy loss occurs due to viscous friction, dissipating externally input mechanical energy. The key component of this hydraulic damper is the damping orifice on the piston. If a Newtonian fluid is used as the damping medium, and local losses are not considered, the pressure difference across the damping orifice is Δp.

[0005] A hydraulic damper is a device used to absorb and convert impact energy during the application of impact loads, limiting the speed and displacement of the load. It is also a speed-sensitive vibration reduction device that uses a specially structured valve to control the movement of a rotating pivot to suppress the effects of periodic and impact loads on pipelines or equipment. Its function is to utilize a hydraulic cylinder filled with hydraulic oil, through a damping control valve or damping throttle orifice, to create a pressure difference between the two chambers of the hydraulic cylinder, thereby generating a damping force on the load and improving the dynamic performance of the system. It is mainly used to prevent damage to pipelines or equipment caused by earthquakes, water hammer, steam hammer, wind loads, safety valve exhaust, and other impact loads. When the movement caused by the force exceeds the permissible speed, the damper will lock, bear the load, and limit the speed to a value called the lock-up speed or leakage rate. The advantage of hydraulic dampers is that they are commonly used to control impact fluid vibrations (such as rapid closure of the main steam valve, safety valve discharge, water hammer, pipe rupture, etc.) and pipeline vibrations caused by earthquakes. Compared to other dampers, hydraulic dampers are small in size, light in weight, simple in structure, have large damping force, are easy to adjust the damping coefficient, have a long service life, and good heat dissipation, thus they are widely used. Hydraulic dampers are classified into linear dampers and rotary dampers according to their motion. Existing linear dampers generally utilize the volume change of a fluid (liquid or gas) and the movement of a one-way valve to generate damping force. Essentially, they utilize the viscosity of the fluid. Although simple in structure and low in cost, they are affected by temperature. They are also affected in a vacuum. They are very sensitive to changes in speed and acceleration, making it difficult to produce stable and controllable linear damping.

[0006] Rotary dampers can directly provide dampers for rotating motion components. They have small installation dimensions, complex structures, and require high precision in component machining.

[0007] The function of a hydraulic damper is to utilize a hydraulic cylinder filled with hydraulic oil. Through a damping control valve or damping throttle orifice, a pressure difference is generated between the two chambers of the hydraulic cylinder, thereby generating a damping force on the load and improving the dynamic performance of the system. Hydraulic dampers primarily utilize the principle of fluid resistance for vibration reduction and can be used in various gear and torque-sensitive equipment. The damper generates torque due to the rotation of the damping oil. The resistance value is determined by the viscosity and contact area of ​​the damping oil. Higher viscosity and a larger contact area result in higher resistance; conversely, lower viscosity and a smaller contact area result in lower resistance. However, the torque also varies with the rotational speed (torque is directly proportional to speed, increasing or decreasing with speed; the static torque at startup differs from the standard value) and with ambient temperature (torque decreases as ambient temperature increases, and increases as ambient temperature decreases). Due to the different applications of hydraulic dampers, various performance and functional requirements are imposed on the product, and the shape can be selected according to customer needs. Existing hydraulic dampers have the following problems: The damping coefficient is related to the oil density, flow coefficient, damper structural parameters, and damping orifice, and is inversely proportional to the fourth power of the damping orifice diameter d. Commonly used hydraulic dampers have unadjustable damping coefficients and performance, and limited applicability. Therefore, once other parameters are determined, the damping coefficient is generally achieved by adjusting the damping orifice diameter. Increasing the orifice diameter decreases the damping coefficient, while decreasing it increases it. However, if the orifice is too small, oil contamination can cause blockage. The piston cylinder stepped shaft seal is positioned via two grooves on the end cover. When the piston rod reciprocates at high frequency, the seal is prone to axial movement between the two grooves, leading to oil leakage in existing hydraulic dampers. Due to the low pressure resistance of the seal, the existing hydraulic dampers can only output a relatively small damping force. Hydraulic dampers used in the aerospace field require small installation size, light weight, high reliability and environmental adaptability, stable performance, and in some cases, adjustable damping performance and low starting friction torque.

[0008] Rotary dampers are commonly seen in daily life and work, serving as devices suitable for various mechanical movements requiring buffering. The torque of a rotary damper changes with the ambient temperature. The pattern is: torque decreases as ambient temperature increases and increases as ambient temperature decreases. This is because the viscosity of the viscous oil in the damper changes with ambient temperature. Hydraulic rotary dampers are divided into unidirectional dampers with resistance in either clockwise or counterclockwise directions, and bidirectional dampers with resistance in both directions. This product offers both unidirectional and bidirectional resistance options. Hydraulic dampers come in various forms, such as pulsating dampers, magnetorheological hydraulic dampers, rotary dampers, and other hydraulic dampers. Different hydraulic dampers may have different methods, but their basic principles are the same. Rotary dampers often use annular slot throttling elements. Their damping performance is significantly affected by the slot height and temperature changes. The annular slot height of the damper needs to be individually machined, and temperature compensation elements need to be designed. Unstable damping performance: Temperature compensation elements have a significant impact on damper performance, with overcompensation and undercompensation occurring frequently across different temperature ranges. Rotary dampers suffer from high precision requirements, increasing manufacturing costs, complex structures, and significantly reduced reliability. Hydraulic dampers using damping orifices face significant design and manufacturing challenges, making it difficult to guarantee stability under working loads. Furthermore, rotary dampers require high reliability and strong environmental adaptability; existing rotary dampers urgently need improvements in starting friction torque, reliability, and environmental adaptability. The throttling orifice of a small-orifice throttling damper undergoes temperature deformation under long-term circulation of viscous fluid, leading to a decrease in damping performance and affecting its service life. Summary of the Invention

[0009] The purpose of this invention is to address the shortcomings of existing technologies by providing a small-hole throttling rotary damper that is compact in structure, less affected by temperature changes, has high damping efficiency, stable performance, adjustable damping performance, and can balance the pressure of the damper cavity in response to the thermal expansion and contraction of the working medium.

[0010] The technical solution adopted by this invention to solve the technical problem is: a closed-type oscillating blade 10 throttling orifice type thermal balance hydraulic damper, comprising: a rear end cover 1 and a front end cover 5 axially fixed by screws at both ends, annularly sealed in the inner annular holes at both ends of the outer cylinder shell 2, and a piston cylinder rotating in the inner annular cylinder at the center of the outer cylinder damping cavity; and oscillating blades 10 mounted on symmetrically rotating swing shafts 9. The feature is that: the inner wall of the outer cylinder damping cavity is provided with concave arc-shaped spring seats facing each other and pointing towards the central bulging cylinder of the oscillating blade 10; the spring cylinders are radially symmetrically mounted with hydraulic thrust springs 3. The outer cylinder damping cavity is divided into a high-pressure chamber A1 on the upper left, a low-pressure chamber B1 on the upper right, a low-pressure chamber B2 on the lower right, and a high-pressure chamber A2 on the lower left, with symmetrical upper and lower oscillating blades 10 at both ends. The front end face of the oil replenishing piston 4 is provided with an oil compensation cavity D1 that provides replenishing oil pressure to the right low-pressure chamber B1 and the lower left low-pressure chamber B2 relative to the front end cover 5. The working medium in D1 flows through the stepped annular groove D2 in the front end cover 5, enters the radial oil hole D4 of the piston neck cylinder along the end oil hole D3, and connects the stepped hole of the piston cylinder with the piston rod neck to form a loop replenishing oil passage D5. D5 connects to the variable throttle orifice D6 and the replenishing oil passage. The damping hole D7 at the rod end of valve core 12 replenishes the oil supply passage D8 of the gyratory blade 10, which connects the right low-pressure chamber B1 and the lower left low-pressure chamber B2, supplying the working medium from D1 to the high-pressure chambers A1 and A2. The oil supply passage formed by D1 to D8 flows into the first annular groove C3 formed by the radially symmetrical left oblique diameter oil passages C1-C2 of the drum cylinder in the middle of the blade, and then into the conical necked hollow cavity on the rotating body of the gyratory shaft 9. This forms the second annular groove C5, which connects to the adjacent variable damping hole C4. The oil then enters the right oblique diameter oil passages C6-C7 of the radially symmetrical gyratory shaft 9 and flows into the low-pressure chamber B1. B2; The rotating pendulum shaft 9 rotates relative to the outer cylinder 2 via the rocker arm assembly 6. When the rotating pendulum shaft 9 rotates clockwise, the pressure in the low-pressure chambers B1 and B2 is low, and the damping orifice D7 is opened. The volume of the working medium in the low-pressure chambers B1 and B2 is compressed, and the working medium in the oil compensation chamber D1 is replenished to the high-pressure chambers A1 and A2. It is connected to the right inclined diameter oil passage C6-C7 through the second circulation groove C5 oil passage, which balances the damper chamber pressure due to the thermal expansion and contraction of the working medium in the low-pressure chambers B1 and B2 and the high-pressure chambers A1 and A2, so as to achieve stable damper performance when the ambient temperature changes.

[0011] Compared with the prior art, the present invention has the following beneficial effects:

[0012] This invention utilizes a piston cylinder that rotates within the inner annular holes at both ends of the outer cylinder shell 2, axially fixed by screws at both ends, and a piston cylinder that rotates within the inner annular cylinder at the center of the outer cylinder damping cavity. A symmetrically rotating pendulum blade 10 is assembled on the pendulum shaft 9. The invention integrates the small-hole damping element, the manually adjustable damping element, and the oil compensation inside the outer cylinder blade, thus maximizing the use of space to design a temperature-compensated pendulum damper with a compact structure and minimal impact from temperature changes.

[0013] This invention uses a piston cylinder to divide the vertical plane of the outer cylinder damping cavity into upper and lower symmetrical spring cylinders. The spring cylinders, equipped with hydraulic thrust springs 3, further divide the outer cylinder damping cavity into left high-pressure chamber A1, right low-pressure chamber B1, right lower low-pressure chamber B2, and left lower high-pressure chamber A2, each with symmetrical upper and lower rotating blades 10 at both ends. Utilizing the characteristic that the V-shaped conical ring groove of the variable throttling orifice D6, symmetrically coupled to the rotating plane of the rotating shaft 9, ensures stable performance at low flow rates, the damper's performance is guaranteed. Analysis shows that with multiple small-orifice throttling methods, the damping performance is less affected by temperature and remains stable. The damping effect of the variable throttling orifice D6 decreases significantly with the reduction in the damping effect of the V-shaped conical ring groove.

[0014] In this invention, the rotating pendulum shaft 9 rotates relative to the outer cylinder 2. When the pressure in the low-pressure chambers B1 and B2 is low, the damping hole D7 at the rod end of the oil replenishing valve core 13 is opened. The working medium in the oil compensation chamber D1 flows through the stepped annular groove D2 in the front end cover 5, along the end oil hole D3, into the radial oil hole D4 of the piston neck cylinder, connecting the piston cylinder stepped hole and the loop oil replenishing passage D5 formed by the necking of the rotating pendulum shaft 9, connecting the variable throttle orifice D6 and the damping hole D7 at the rod end of the oil replenishing valve core 13, and replenishing the oil replenishing passage D8 of the pendulum blade 10 connected to the right low-pressure chamber B1 and the lower left low-pressure chamber B2; the working medium flows through the oil compensation chamber D1...

[0015] D2→D3→D4→D5→D6→D7→D8 supplements the low-pressure chambers B1 and B2. By using a small orifice throttling method, the damping performance is less affected by temperature, resulting in high damping efficiency and stable performance.

[0016] This invention employs an oil compensation chamber to balance the damper cavity pressure during thermal expansion and contraction of the working medium. During high-frequency rotation of the damper, low-pressure oil replenishment prevents oil and gas from precipitating and forming cavities that could negatively impact damper performance. This overcomes the significant impact of temperature compensation elements on damper performance, which often results in overcompensation or undercompensation across different temperature ranges. A Y-type dynamic seal ring with a rotary dynamic seal design, utilizing its lip seal and low compression force, reduces the damper's starting friction torque. A highly balanced piston head and piston rod, coupled with an absolutely leak-proof design, prevents axial movement between the two grooves during high-frequency reciprocating piston rod motion, thus avoiding oil leakage problems in hydraulic dampers and the low pressure resistance of the seal ring, which results in low output damping force.

[0017] In this invention, when the rotating pendulum shaft 9 rotates at a relatively high clockwise speed relative to the outer cylinder 2, the volume of the working medium in the low-pressure chambers B1 and B2 is compressed. The working medium in the oil compensation chamber D1 replenishes the high-pressure chambers A1 and A2, maintaining a constant pressure in the controlled system or circuit, thus achieving pressure stabilization, regulation, or limiting. When the hydraulic pressure acting on the valve core is greater than the spring force, the valve opens. Adjusting the spring preload adjusts the overflow pressure, thereby controlling the magnitude of the damping force. The forces at both ends of the valve core return to equilibrium, and the pressure difference Δp across the valve remains essentially constant, ensuring the stability of the working load. When the piston moves with the structure, it forces the damping medium from the high-pressure chamber into the low-pressure chamber. During the flow, it overcomes internal friction, converting the fluid's kinetic energy into heat energy, which is then transferred to the outside. This damper uses a damping orifice to dampen and dissipate energy, thereby dissipating externally input mechanical energy and improving the stress condition of the damper under conditions such as creep and low speed. It can ensure that it has a strong energy dissipation capacity under different external excitations and maintain a stable damping force generated under strong excitation.

[0018] This invention employs a working medium that flows through the replenishing oil passages formed by D1 to D8, then through the left oblique diameter oil passages C1 and C2 of the radially symmetrical rotating pendulum shaft 9 at the center of the blade, into the first annular groove C3 formed by the conical necked hollow cavity on the rotating body of the rotating pendulum shaft 9. This connects to the adjacent variable damping orifice C4, flowing into the second annular groove C5, and then into the oil passages C6 and C7 of the radially symmetrical rotating pendulum shaft 9, flowing into the low-pressure chambers B1 and B2. The high-pressure chambers A1 and A2 are connected to the first annular groove C3 via the left oblique diameter oil passages C1 and C2, while the low-pressure chambers B1 and B2 are connected to the oil passages C6 and C7 via the second annular groove C5. This balances the pressure in the low-pressure chambers B1 and B2, the high-pressure chambers A1 and A2, and the pressure in the damper cavity due to the thermal expansion and contraction of the working medium. When the pendulum blade 10 rotates clockwise at a certain angular velocity, the pressure in the left volume chamber increases due to the decrease in volume. The right volume chamber, due to the increase in volume, forms a partial vacuum, causing the hydraulic oil to flow from the high-pressure chamber to the low-pressure chamber. The rotation of the moving blades pressurizes the hydraulic oil in the left chamber, creating a pressure difference that acts on the moving blades and generates a damping torque M. Under the action of the damping orifice, the damping torque generated by the damper is proportional to the angular velocity of the output shaft within a certain range. This results in a damping force proportional to the velocity, which, by consuming energy, suppresses oscillations in the control system, reducing the number of oscillations and allowing the system to stabilize quickly. This ensures stable damper performance despite changes in ambient temperature.

[0019] This invention uses a metal rotating shaft 9 and a plastic material with a high coefficient of thermal expansion for the manual adjustment valve core 14. By rotating the manual adjustment valve core 14 to change its position relative to the rotating shaft 9, the damping coefficient can be manually adjusted. The rate of change of the length of the manual adjustment valve core 14 is greater than that of the rotating shaft 9 when the temperature changes, thus ensuring stable damping performance under temperature variations.

[0020] The working process of the hydraulic damper of this invention can be described as a combination of rigidity and flexibility. During normal thermal expansion of the pipeline or equipment, it moves slowly, exhibiting almost no damping force, which is considered "flexible." When the load changes instantaneously, the valve of the hydraulic damper is activated, generating a reverse resistance equal to the vibration force, thus suppressing larger vibrations in the pipeline or equipment, reducing the amplitude, and protecting the pipeline or equipment, which is considered "rigid." The orifice throttling damping element generates damping force independent of the working medium viscosity, meaning it is insensitive to temperature changes. Utilizing a highly balanced piston head and piston rod, coupled with absolute oil leakage prevention, it avoids axial movement between the two grooves during high-frequency reciprocating motion of the piston rod, thus preventing oil leakage faults, low pressure resistance of the sealing ring, and small output damping force in hydraulic dampers.

[0021] The present invention can change the flow area of ​​the damping orifice formed by the rotating pendulum shaft 9 and the manual adjusting screw 14 as needed, and steplessly adjust the damping coefficient.

[0022] Examples of applications of this invention include industries such as aviation, aerospace, automotive, construction, road and bridge railways, mechanical engineering, ground moving vehicles, and aircraft control systems. Attached Figure Description

[0023] Figure 1 This is a front view of the closed-type gyratory blade throttling orifice type thermal balance hydraulic damper of the present invention;

[0024] Figure 2 yes Figure 1 Top view;

[0025] Figure 3 yes Figure 1 Sectional view along axis AA;

[0026] Figure 4 yes Figure 3 A partially enlarged schematic diagram of the rotating pivot F towards the middle of the main body;

[0027] Figure 5 yes Figure 2 BB-direction sectional view;

[0028] Figure 6 yes Figure 1 CC-direction sectional view;

[0029] Figure 7 yes Figure 1 DD section view;

[0030] Figure 8 yes Figure 1 Assembly breakdown diagram;

[0031] Figure 9 yes Figure 1 Assembly breakdown diagram.

[0032] In the diagram: 1. Rear end cover; 2. Outer cylinder shell; 3. Hydraulic thrust spring; 4. Oil replenishing piston; 5. Front end cover; 6. Rocker arm assembly; 7. Y-type dynamic seal ring; 8. Angular contact ball bearing; 9. Rotary swing shaft; 10. Swing blade; 11. Stepped spring shaft; 12. Oil replenishing spring; 13. Oil replenishing valve core; 14. Manual adjusting valve core; 15. Oil filling fixture; 16. Needle roller bearing; 17. Dynamic seal ring; 18. Elastic retaining ring; M. Oil filling port; A1. Upper left high-pressure chamber. A2 Lower left high-pressure chamber, B1 Upper right low-pressure chamber, B2 Lower right low-pressure chamber, C1 Radial oil passage, C3 First annular groove, C4 Variable damping orifice, C5 Second annular groove, C6 Oil passage channel, C7 Damping oil passage, D1 Oil compensation chamber, D1, D3 Cantilever cylinder end oil holes, D4 Piston necking cylinder radial oil hole, D5 Circulation oil replenishment oil passage, D6 Variable throttle orifice, D7 Rod end damping orifice, D8 Swing blade oil replenishment oil passage. Implementation

[0033] See Figures 1 to 7In the embodiments described below, a closed-type oscillating blade 10 throttling orifice type thermal balance hydraulic damper includes: a rear end cover 1 and a front end cover 5, which are axially fixed by screws at both ends and annularly sealed in the inner annular holes at both ends of an outer cylinder shell 2, and rotate in the inner annular cylinder at the center of the outer cylinder damping cavity; and oscillating blades 10 mounted on symmetrically rotating oscillating shafts 9. The outer cylinder damping cavity is characterized by: a spring seat body with concave arcs pointing towards the central bulging cylinder of the oscillating blade 10 and apex opposite each other on the inner wall of the outer cylinder damping cavity; and a spring cylinder body equipped with a hydraulic thrust spring 3, which is radially symmetrical, dividing the outer cylinder damping cavity into... The left and right ends of the symmetrically rotating blades 10 have an upper left high-pressure chamber A1, an upper right low-pressure chamber B1, a lower right low-pressure chamber B2, and a lower left high-pressure chamber A2. The front end face of the oil replenishing piston 4 is provided with an oil compensation chamber D1, which provides oil replenishment pressure to the right low-pressure chamber B1 and the lower left low-pressure chamber B2 relative to the front end cover 5. The working medium in D1 flows through the stepped annular groove D2 in the front end cover 5, enters the radial oil hole D4 of the piston neck cylinder along the end oil hole D3, and connects the piston cylinder stepped hole and the piston rod neck to form a loop oil replenishment oil passage D5. D5 connects the variable throttle hole D6 and the damping hole at the rod end of the oil replenishing valve core 12. D7, supplements the oil supply path D8 of the gyratory blade 10 connected to the right low-pressure chamber B1 and the left lower low-pressure chamber B2, replenishing the working medium of D1 to the high-pressure chambers A1 and A2; the oil supply path formed by D1 to D8 flows through the radially cross-symmetrical rotating gyratory shaft 9 of the central drum cylinder of the blade, and the left oblique diameter oil paths C1 and C2 flow into the conical necked hollow cavity on the rotating body of the gyratory shaft 9 to form the first annular groove C3, which connects to the adjacent variable damping orifice C4 and flows into the second annular groove C5, entering the oil passages C6 and C7 of the radially symmetrical rotating gyratory shaft 9 and flowing into the low-pressure chambers B1 and B2; the rotating gyratory shaft 9... The rocker arm assembly 6 rotates relative to the outer cylinder 2. When the rotating pendulum shaft 9 rotates clockwise, the pressure in the low-pressure chambers B1 and B2 is low, and the damping orifice D7 is opened. The volume of the working medium in the low-pressure chambers B1 and B2 is compressed, and the working medium in the oil compensation chamber D1 is replenished to the high-pressure chambers A1 and A2. The low-pressure chambers B1 and B2 are connected to the oil passages C6 and C7 through the second circulation groove C5, which balances the damper chamber pressure due to thermal expansion and contraction of the working medium in the low-pressure chambers B1 and B2 and the high-pressure chambers A1 and A2, thus achieving stable damper performance when the ambient temperature changes.

[0034] When the rotating pendulum 9 rotates at a relatively high clockwise speed relative to the outer cylinder 2, the working medium in the low-pressure chambers B1 and B2 is compressed, and the working medium in the oil compensation chamber D1 of the oil replenishment chamber is replenished to the high-pressure chambers A1 and A2, and the pressure is maintained constant.

[0035] When the pendulum blade 10 rotates clockwise at a certain angular velocity, the pressure in the left volume chamber increases due to the decrease in volume, while the pressure in the right volume chamber increases due to the increase in volume, forming a partial vacuum. This promotes the flow of hydraulic oil from the high-pressure chamber to the low-pressure chamber. The pendulum blade 10's pendulum motion causes the hydraulic oil in the left chamber to be pressurized, generating a pressure difference that acts on the moving blade, forming a damping torque M.

[0036] The rotating pivot shaft 9 houses the stepped cylinders at both ends of the receiving cylinder, which are connected to the Y-type dynamic seal ring 7 via an angular contact ball bearing 8 mounted in the blind hole bearing of the central ring of the front end cover 5. The lip of the seal ring seals the piston cylinder output shaft and extends out of the outer cylinder shell 2 to connect to the rocker arm assembly 6. By designing the Y-type dynamic seal ring through a rotary dynamic seal, and utilizing the lip seal of the Y-type dynamic seal ring, which has the characteristics of low compression force, the starting friction torque of the damper can be reduced.

[0037] At both ends of the stepped cylinder of the piston rod receiving cylinder assembled in the outer cylinder damping cavity, there are oil replenishing springs 12 that are constrained between the stepped spring shaft 11 and the oil replenishing valve core 13 and provide pre-pressure for the oil replenishing valve core 13. The extended end of the oil replenishing valve core 13 has a V-shaped conical ring groove that is symmetrically coupled to the rotating surface of the rotating swing shaft 9 with the variable throttling orifice D6.

[0038] A V-shaped oblique groove is opened on the manually adjustable valve core 14 part connected to the rocker arm connecting shaft. The flow cross section formed by it and the rotating swing shaft 9 is closer to the circular variable cross section throttling orifice. By changing the axial relative position of it and the relative rotating swing shaft 9 and the flow area of ​​the damping orifice formed by the manually adjusting screw, the opening of the V-shaped oblique groove is changed, so as to realize the stepless adjustment of the damping performance in the external field over a large range, and the damping performance is more stable.

[0039] See Figure 8 The rear end cover 1 encapsulates the needle roller bearing 17 in the end cover annular groove with a flanged ring by the circumferential screws 16 on the cover plate. The sealing ring in the outer annular groove of the rear end cover 1 is sealed in the stepped hole inside the outer cylinder shell 2. The front end cover 5 is sealed in the oil injection hole of the stepped M inside the outer cylinder shell 2 by the sealing ring in the outer annular groove. The outer cylinder shell 2 between the rear end cover 1 and the front end cover 5 forms a damping cavity.

[0040] The damper is filled with oil as follows: the rear end cover 1 is tightened and fixed to the outer cylinder 2 with screws 16; the angular contact ball bearing 8, the Y-type dynamic seal ring 7, the needle roller bearing 16, and the rotating swing shaft 9 are installed; the front end cover 5 is installed and tightened to the outer cylinder shell 2 with screws; the hydraulic thrust spring 3 and the oil replenishing piston 4 are installed in the oil replenishing chamber D1 of the outer cylinder shell 2; the manual adjusting screw 14 with the dynamic seal ring 17 is screwed in; the elastic retaining ring 18 is installed and the oil filling fixture 15 is removed.

[0041] To ensure that the damper cavity is filled with oil, and that the oil in the replenishment chamber and the oil storage in the compensation chamber D1 are adequate, an oil filling fixture 15 is provided on the outer shell 2 at one end of the adjacent front end cover 5. This fixture is radially connected to the spring cylinder. After the oil filling piston 4 at one end is started and compressed to its limit, it is positioned by the oil filling fixture 15, keeping the extended end of the rotating swing shaft 9 vertically upward. The working medium is filled through the oil filling port M, and any excess working medium is discharged from the oil drain port N. The pressure in the two replenishment chambers is balanced, and the spring compression lengths are equal, allowing them to jointly replenish oil to the damping chamber.

[0042] See Figure 9 The manual adjusting valve core 14, equipped with a sealing ring 17 and an elastic retaining ring 18 on the rod body, is assembled into the front oil drain port N hole via the rotating swing shaft 9 through the assembly hole. An adjustable damping hole is formed between the end faces of the rotating swing shaft 9 and the front face of the manual adjusting valve core 14. A V-shaped conical ring groove is provided at the front end of the manual adjusting valve core 14. Rotating the manual adjusting valve core 14 changes the opening of the V-shaped conical ring groove, achieving stepless adjustment of the damping performance over a wide range in the external field, ensuring the stability of the working load. The rotating swing shaft 9 is made of metal, while the manual adjusting valve core 14 is made of plastic with a high coefficient of thermal expansion. Rotating the manual adjusting valve core 14 changes its position relative to the rotating swing shaft 9, allowing for manual adjustment of the damping coefficient. The rate of change of the length of the manual adjusting valve core 14 is greater than that of the rotating swing shaft 9 when the temperature changes, ensuring stable damping performance under temperature variations.

[0043] The damping orifice described in the above embodiments is mainly used to control the pressure change of the oil to achieve the required control pressure, and the throttling orifice is mainly used to control the flow rate of the oil to achieve the required control flow rate.

[0044] During operation, the mechanical system, through the movement of the oil-replenishing piston 4 in the damper, forces the liquid in the damping cylinder to flow through the small holes or gaps of the compensation chambers D1 to D8, or a combination of both, into the damping element. When an instantaneous impact load occurs, the speed V of the rotating pendulum shaft 9 increases to the locking speed v. At this point, the hydraulic oil pushes the valve core 13 to close, allowing the hydraulic oil to flow only through the damping holes of the throttle valve, forming a damping force FN. The damper locks in, causing the liquid molecules to squeeze and rub against each other, generating a damping effect and converting mechanical energy into heat energy for dissipation, thus achieving vibration reduction and anti-vibration. Under normal operating conditions, the piston rod speed V < the locking speed v, and the force on the pipeline is very small, f < 1-2% FN.

[0045] The embodiments of the present invention have been described in detail above. Specific implementation methods have been used to illustrate the present invention. The description of the above embodiments is only for the purpose of helping to understand the method and device of the present invention. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the ideas of the present invention. Therefore, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A closed-type gyratory blade throttling orifice type thermal balance hydraulic damper, comprising: The rear end cap (1) and front end cap (5) are axially fixed by screws at both ends, and are sealed in the inner annular holes at both ends of the outer cylinder shell (2). The piston cylinder rotates in the inner annular cylinder at the center of the outer cylinder damping cavity. The symmetrically rotating pendulum shaft (9) is equipped with a pendulum blade (10). The outer cylinder damping cavity is characterized by: the inner wall of the outer cylinder damping cavity is provided with a spring seat body with concave arcs pointing towards the middle of the bulging cylinder of the pendulum blade (10) and the spring cylinder body equipped with the hydraulic thrust spring 3 is radially symmetrical, dividing the outer cylinder damping cavity into the upper left high pressure cavity A of the symmetrical upper and lower pendulum blades (10) at both ends.

1. Right upper low-pressure chamber B1, right lower low-pressure chamber B2, left lower high-pressure chamber A2; the front end face of the oil replenishing piston (4) is provided with an oil compensation chamber D1 that provides oil replenishment pressure to the right low-pressure chamber B1 and the left lower low-pressure chamber B2 relative to the front end cover (5). The working medium in D1 flows through the stepped annular groove D2 in the front end cover (5), enters the radial oil hole D4 of the piston neck cylinder along the end oil hole D3, and connects the piston cylinder stepped hole and the piston rod neck to form a loop oil replenishment oil passage D5. D5 connects the variable throttle hole D6 and the damping hole D7 at the rod end of the oil replenishing valve core (12) to replenish the right low-pressure chamber B1.

1. The oil supply path D8 of the rotary blade (10) connected to the lower left low-pressure chamber B2 replenishes the working medium of D1 to the high-pressure chambers A1 and A2; the oil supply path formed by D1 to D8 flows into the first circulation groove C3 formed by the radially cross-symmetrical left oblique diameter oil passages C1-C2 of the drum cylinder in the middle of the blade, and then into the conical necked hollow cavity on the rotating body of the rotary shaft (9), which connects to the adjacent variable damping hole C4, flows into the second circulation groove C5, and then enters the right oblique diameter oil passages C6-C7 of the radially symmetrical rotary shaft (9), flowing into the low-pressure chambers B1 and B2; the rotary shaft (9) By rotating and swinging the rocker arm assembly (6) relative to the outer cylinder (2), when the rotating pendulum shaft (9) rotates clockwise, the damping hole D7 is opened when the pressure in the low-pressure chambers B1 and B2 is low. The working medium in the low-pressure chambers B1 and B2 is compressed, and the working medium in the oil compensation chamber D1 is replenished to the high-pressure chambers A1 and A2. The oil circuit of the second circulation groove C5 is connected to the right inclined diameter oil circuit C6-C7 to balance the damper chamber pressure due to thermal expansion and contraction of the working medium in the low-pressure chambers B1 and B2 and the high-pressure chambers A1 and A2, so as to achieve stable damper performance when the ambient temperature changes.

2. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: When the rotating pendulum shaft (9) rotates clockwise at a relatively high speed relative to the outer cylinder (2), the working medium in the low-pressure chambers B1 and B2 is compressed, and the working medium in the oil compensation chamber D1 of the oil replenishment chamber is replenished to the high-pressure chambers A1 and A2, and the pressure is kept constant.

3. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: When the pendulum blade (10) rotates clockwise at a certain angular velocity, the pressure in the left volume chamber increases due to the decrease in volume, while the pressure in the right volume chamber increases due to the increase in volume, forming a partial vacuum. This promotes the flow of hydraulic oil from the high-pressure chamber to the low-pressure chamber. The rotation of the blade causes the hydraulic oil in the left chamber to be pressurized, generating a pressure difference that acts on the blade, forming a damping torque M.

4. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: The stepped cylinders at both ends of the piston rod receiving cylinder are connected to the Y-type dynamic seal ring (7) through the angular contact ball bearing (8) assembled in the blind hole bearing of the center ring of the front end cover (5). The lip of the seal ring seals the piston cylinder output shaft and extends out of the outer cylinder shell (2) to connect to the rocker arm assembly (6).

5. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: The rear end cover (1) encapsulates the needle roller bearing (16) in the end cover ring groove with a flange ring by the circumferential screws on the cover plate. The sealing ring in the outer ring groove of the rear end cover (1) is sealed in the stepped hole in the outer cylinder shell (2). The front end cover (5) is sealed in the oil injection hole of the step M in the outer cylinder shell (2) by the sealing ring in the outer ring groove. The outer cylinder shell (2) between the rear end cover (1) and the front end cover (5) forms a damping cavity.

6. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: The damper is filled with oil as follows: the rear end cover (1) is tightened and fixed to the outer cylinder (2) with screws; angular contact ball bearing (8), Y-type dynamic seal ring (7) is installed and needle roller bearing (16) and rotating swing shaft (9) are installed; the front end cover (5) is installed and tightened to the outer cylinder shell (2) with screws; hydraulic thrust spring (3) and oil replenishing piston (4) are installed in the oil replenishing chamber D1 of the outer cylinder shell (2); a manual adjusting screw (14) with dynamic seal ring (17) is screwed in; after the elastic retaining ring (18) is installed, the oil filling fixture (15) is removed.

7. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: An oil injection fixture (15) is provided on the outer shell (2) of the adjacent front end cover (5) and the cylinder body of the spring cylinder that is radially connected to the cylinder body. After the oil replenishing piston (4) is started and compressed to the limit, the oil injection fixture (15) is used to position it and keep the extended end of the rotating swing shaft (9) vertically upward. The working medium is filled through the oil injection port M and the excess working medium is discharged from the oil discharge port N. The pressure of the two oil replenishing chambers is balanced and the spring compression length is equal, so they jointly replenish the damping chamber with oil.

8. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: A V-shaped oblique groove is opened on the manual adjustment valve core (14) part connected to the rocker arm connecting shaft. The flow cross section formed by the rotating swing shaft (9) is closer to the circular variable cross section throttling orifice. The axial relative position of the valve core (9) and the flow area of ​​the damping orifice formed by the manual adjustment screw are changed, thereby changing the opening of the V-shaped oblique groove and realizing the stepless adjustment of the damping performance in the external field.

9. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: The manual adjustment valve core (14) is fitted with a sealing ring (17) and an elastic retaining ring, and is assembled in the mounting hole of the rotating swing shaft (9) through the front oil drain port N hole, forming an adjustable damping hole on the end face of the rotating swing shaft (9).

10. The closed-type gyratory blade throttling orifice type thermal balance hydraulic damper as described in claim 1, characterized in that: During the movement of the mechanical system, the movement of the oil replenishing piston (4) in the damper forces the liquid in the damping cylinder to flow through the small holes or gaps of the compensation chamber D1 to D8, or a combination of both. When an instantaneous impact load occurs, the speed V of the rotating pendulum shaft (9) increases to the locking speed v. When the locking speed v is closed, the hydraulic oil pushes the oil replenishing valve core (13) to close. The hydraulic oil can only flow through the damping small hole of the throttle valve, forming a damping force FN. The damper locks, causing the liquid molecules to squeeze and rub against each other, generating a damping effect, converting mechanical energy into heat energy and dissipating it, thus achieving vibration reduction and anti-vibration.

Images