Design method of lifting table board, coil spring part and gas spring

Abstract

The application discloses a lifting table plate, comprising: a support assembly; a guide rail assembly fixedly connected to the support assembly; a lifting mechanism assembly connected to the guide rail assembly in a vertically movable manner; a panel assembly connected to the lifting mechanism assembly through a turnover assembly, the panel assembly being capable of being converted between a folded position and an unfolded position relative to the lifting mechanism assembly; a first buffer mechanism provided at a bottom region of the lifting mechanism assembly, the first buffer mechanism providing a buffer damping action during lifting or falling of the lifting mechanism assembly along the guide rail assembly, so that the lifting or falling movement of the lifting mechanism assembly tends to be uniform; and a second buffer mechanism having one end connected to the turnover assembly and the other end connected to the lifting mechanism assembly, the second buffer mechanism providing a buffer damping action when the panel assembly is converted between the unfolded position and the folded position, so that the movement of the panel assembly tends to be uniform.

Description

Technical Field

[0001] This application relates to the field of vehicle-mounted table technology, and more specifically to a design method for a lifting table, a coil spring, and a gas spring. Background Technology

[0002] Existing vehicle-mounted lifting tables typically include a lifting mechanism that can be raised and lowered vertically, and a panel that can be flipped relative to the lifting mechanism.

[0003] In practical use, the lifting mechanism often experiences significant end-stage impact when descending to the low position due to gravitational acceleration, and sudden speed changes are prone to occur during the rising process, resulting in an uneven overall lifting motion. Simultaneously, during the opening or closing of the panel, changes in its own gravitational torque and uneven user operation force often lead to rapid descent or upward bouncing, affecting the user experience, generating significant impact noise, and accelerating wear on related moving parts. Therefore, how to ensure that the lifting and flipping movements of the adjustable table are both uniform and smooth, effectively reducing impact and noise, is a pressing technical problem that needs to be solved in this field. Summary of the Invention

[0004] The purpose of this application is to provide a design method for a lifting table, a coil spring, and a gas spring, so as to reduce the impact caused by excessive speed during the lifting and flipping movement of the table in the vehicle.

[0005] To achieve the above objectives, the technical solution adopted in this application is as follows: A height-adjustable tabletop is provided, comprising: a support assembly; a guide rail assembly fixedly connected to the support assembly; a lifting mechanism assembly connected to the guide rail assembly in a vertically movable manner; a panel assembly connected to the lifting mechanism assembly via a flipping component, the panel assembly being able to switch between a folded position and an unfolded position relative to the lifting mechanism assembly; a first buffer mechanism disposed in the bottom region of the lifting mechanism assembly, providing buffering damping during the lifting mechanism assembly's rise or fall along the guide rail assembly, thereby making the rising and falling motion of the lifting mechanism assembly tend to be smooth; and a second buffer mechanism, one end of which is connected to the flipping component and the other end of which is connected to the lifting mechanism assembly, the second buffer mechanism providing buffering damping when the panel assembly switches between the unfolded and folded positions, thereby making the movement of the panel assembly tend to be smooth.

[0006] Furthermore, the lifting mechanism assembly includes a coil spring, which drives the lifting mechanism assembly to lift. The first buffer mechanism includes a coil spring damper, and the coil spring is tractively connected to the coil spring damper. The coil spring provides a driving force to move the lifting mechanism assembly from the retracted position to the extended position. The force change of the coil spring matches the torque change of the coil spring damper, and the torque change of the coil spring damper suppresses the pop-out speed of the lifting mechanism assembly.

[0007] Preferably, the second buffer mechanism includes a gas spring mounting base and a gas spring, the gas spring being disposed within the gas spring mounting base, one end of the gas spring being connected to the gas spring mounting base, and the other end being connected to the lifting mechanism assembly; the flipping assembly includes a flipping plate, one end of the flipping plate being rotatably connected to the panel assembly, and the other end of the flipping plate being rotatably connected to the gas spring mounting base to form a movable end, the lifting mechanism assembly being provided with a sliding groove, and the movable end being located within the sliding groove and moving as the panel assembly rotates and opens.

[0008] Preferably, the sliding groove includes a first end and a second end distributed in a vertical direction. The end of the panel assembly is directly connected to it in a manner that allows it to rotate relative to the lifting mechanism assembly. When the panel assembly is in the retracted position, the movable end is located at the first end within the sliding groove, at which time the panel assembly, the flip plate, and the gas spring fixing seat are arranged parallel to each other. When the panel assembly is in the unfolded position, the movable end is located at the second end within the sliding groove, at which time the panel assembly, the flip plate, and the gas spring fixing seat form a triangular linkage structure.

[0009] Preferably, the flipping assembly further includes a stop mechanism, which is disposed between the second buffer mechanism and the lifting mechanism assembly. The stop mechanism has multiple limit positions. When the panel assembly switches between the closed position and the open position, the stop mechanism can be located at different limit positions, so as to keep the panel assembly in different predetermined positions.

[0010] Preferably, the stop mechanism includes a slot and a locking member that cooperate with each other; the slot is disposed on the lifting mechanism assembly, and the locking member is disposed on the second buffer member; the end of the locking member is provided with an elastic member, so that the locking member can elastically engage or disengage from the slot when the panel assembly changes position, so as to realize the switching and positioning of different gears.

[0011] Furthermore, the first buffer mechanism also includes a first buffer spring, which is disposed between the lower bottom of the lifting mechanism assembly and the support assembly, to prevent the lifting mechanism assembly from directly impacting the lower bottom of the support assembly and causing abnormal noise under bumpy conditions; the second buffer mechanism also includes a base connected to the guide rail assembly and a second buffer spring, which is connected to the base to provide a buffering effect to the lifting mechanism assembly and avoid the lifting mechanism assembly from impacting the base and causing abnormal noise.

[0012] Furthermore, this application also provides a design method for a coil spring component in a lifting table, which is applicable to the aforementioned lifting table, and includes: Step S10: Determining the overall load mass of the lifting mechanism assembly and the panel assembly as... m The unit is kilograms, so the total weight is... mg Unit: Newton, the total stroke of the lifting mechanism assembly is s Unit: kilogram, total time: t 总 The unit is seconds, then the target uniform speed of the lifting mechanism is... Step S20: Select a coil spring damper of a specified calibration specification; Step S30: Calculate the rotational speed of the coil spring damper, wherein... ; The radius of the coil spring damper, in meters. The rotational speed of the coil spring damper, in units of: The constant 60 represents 60 seconds; Step S40: Calculate the torque value of the coil spring damping, where , The torque value of the coil spring damping, in units of: , Therefore, the first specific constant corresponding to the coil spring damping under the specified calibration is determined. Therefore, the second specific constant corresponding to the coil spring damping under the specified calibration is determined; Step S50: Calculate the equivalent damping force of the coil spring damping on the load side, where , This is the equivalent damping force of the coil spring on the load side, in Newtons (N). The radius of the coil spring is in meters; Step S60: Calculate the ideal constant reference tension of the coil spring, i.e. , The ideal constant reference tension of the coil spring, in Newtons; Step S70: According to the... The value is used to select a coil spring with a suitable tension value.

[0013] Furthermore, after step S70, step S71 is included: calculating the nonlinear tension of the coil spring to optimize the selection of the coil spring based on the nonlinear tension of the coil spring, wherein, ,in The time point during the lifting process of the lifting mechanism assembly is expressed in seconds. This refers to the nonlinear tension of the coil spring, measured in Newtons (N). Parameter P is the instantaneous tension compensation coefficient for the coil spring during startup, parameter Q is the exponential decay time constant, and parameter R is the linear decay coefficient of the tension.

[0014] Furthermore, this application also provides a design method for a gas spring in a height-adjustable tabletop, which is applicable to the aforementioned height-adjustable tabletop, and includes: Step S100: Determining the mass of the panel assembly as... m 1 The weight of the panel assembly is... m 1 g Step S200: Calculate the gravitational torque of the panel assembly at any flip angle, that is... ,in, This refers to the flip angle of the panel assembly. When the angle is 0 degrees, the panel assembly is in a vertical folded position. When the angle is 90 degrees, the panel assembly is in a horizontal unfolded position. The gravitational torque of the panel assembly at any flip angle, in Newtons. rice, The distance from the center of gravity of the panel assembly to the gas spring mounting base and its connected rotating end when the panel assembly is in the unfolded position, in meters; Step S300: Calculate the lever arm of the gas spring when the panel assembly is at any flip angle, i.e. = ,in, The lever arm of the gas spring is the distance between the movable end of the panel assembly and the end directly connected to the lifting mechanism assembly when the panel assembly is in the retracted position, expressed in meters. When the panel assembly is in the unfolded position, the distance from the movable end to the end of the rotating plate rotatably connected to the panel assembly is the lever arm of the gas spring. , here unit: rad Step S400: The uniform rotation of the panel assembly requires that the resultant torque be 0 at any given time, thus... , that is ,in, That is, the gas spring force of the panel assembly at any flip angle, in Newtons; Step S500: Based on the gas spring force The value is used to select a gas spring with an appropriate force value.

[0015] Compared with the prior art, the beneficial effects of this application are as follows: The first buffer mechanism located at the bottom of the lifting mechanism assembly effectively solves the end-impact problem during the lifting mechanism's descent and suppresses sudden speed changes during the lifting process, improving the smoothness and safety of the lifting motion. The second buffer mechanism connected between the flipping component and the lifting mechanism assembly effectively controls the speed of the panel assembly during the flipping process, preventing rapid descent or rebound caused by uneven gravity or operating force, ensuring a smooth and uniform flipping motion. The synergistic effect of the two buffer mechanisms significantly improves the overall operating experience of the lifting table, reduces noise and wear, and extends the product's service life. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the panel assembly of the lifting table in the folded position.

[0017] Figure 2 This is a schematic diagram of the structure of the lifting table with the panel assembly in the folded position and the bracket assembly removed.

[0018] Figure 3 This is a structural schematic diagram of the panel assembly in the folded position, excluding the bracket assembly, from a side view.

[0019] Figure 4 This is a structural diagram of the panel assembly in the unfolded position of the lifting table.

[0020] Figure 5 This is a structural diagram of the panel assembly in the unfolded position with the bracket assembly removed.

[0021] Figure 6 for Figure 5 A magnified view of a portion of point A in the middle.

[0022] Figure 7 This is a graph showing the rotational speed of the coil spring damping mechanism.

[0023] Figure 8 Speed ​​curves at key time points during the lifting and lowering mechanism assembly and panel assembly of the coiled spring component.

[0024] Figure 9 This is a structural schematic diagram of the panel assembly in the unfolded position, excluding the support assembly, from a side view.

[0025] Figure 10 for Figure 9 A magnified view of a section at point B.

[0026] Figure 11 This is a structural diagram showing the position of the flip component when the panel assembly is in the folded position.

[0027] Figure 12 A schematic diagram of the positioning mechanism.

[0028] Figure 13 for Figure 12 A magnified view of a section at point C.

[0029] Figure 14 This is a schematic diagram of the structure of the first buffer spring in the first buffer mechanism.

[0030] Figure 15 This is a schematic diagram of the structure of the base and the second buffer spring in the second buffer mechanism.

[0031] In the diagram: 1. Lifting table; 10. Bracket assembly; 20. Guide rail assembly; 30. Lifting mechanism assembly; 31. Spring coil; 32. Sliding groove; 321. First end; 322. Second end; 40. Panel assembly; 50. Flip assembly; 51. Flip plate; 52. Movable end; 60. First buffer mechanism; 61. Spring coil damping; 62. First buffer spring; 70. Second buffer mechanism; 71. Gas spring fixing seat; 72. Gas spring; 73. Base; 74. Second buffer spring; 80. Stop mechanism; 81. Slot; 811. Guide slope; 82. Engaging part; 83. Elastic part. Detailed Implementation

[0032] The present application will be further described below with reference to specific embodiments. It should be noted that, without conflict, the various embodiments or technical features described below can be arbitrarily combined to form new embodiments.

[0033] In the description of this application, it should be noted that the directional terms such as "center", "lateral", "longitudinal", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", and "counterclockwise" indicate the orientation and positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. They should not be construed as limiting the specific protection scope of this application.

[0034] It should be noted that the terms "first," "second," etc., in the specification and claims of this application are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence.

[0035] The terms “comprising” and “having”, and any variations thereof, in the specification and claims of this application are intended to cover non-exclusive inclusion, for example, a process, method, system, product, or device that includes a series of steps or units is not necessarily limited to those steps or units that are explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to such process, method, product, or device.

[0036] In a preferred embodiment, see Figures 1 to 13 This application provides a height-adjustable table 1, comprising: a support assembly 10; a guide rail assembly 20 fixedly connected to the support assembly 10; a lifting mechanism assembly 30 connected to the guide rail assembly 20 in a vertically movable manner; a panel assembly 40 connected to the lifting mechanism assembly 30 via a flip assembly 50, the panel assembly 40 being able to switch between a folded position and an unfolded position relative to the lifting mechanism assembly 30; a first buffer mechanism 60 disposed in the bottom area of ​​the lifting mechanism assembly 30, providing buffering damping during the lifting or lowering of the lifting mechanism assembly 30 along the guide rail assembly 20, so that the lifting and lowering movement of the lifting mechanism assembly 30 tends to be smooth; and a second buffer mechanism 70, one end of which is connected to the flip assembly 50. One end is connected to the lifting mechanism assembly 30. When the panel assembly 40 transitions between the unfolded and retracted positions, the second buffer mechanism 70 provides a buffering and damping effect, making the movement of the panel assembly 40 more gradual. This gradual movement means that during the lifting and lowering motion of the lifting mechanism assembly 30 and the flipping motion of the panel assembly 40, the rate of change of speed is limited to a range that does not cause noticeable impact or vibration to the user. Specifically, the speed curve during the middle of the movement is smooth and without abrupt changes, and the overall movement exhibits near-uniform speed or near-uniform acceleration / deceleration characteristics. The first buffer mechanism 60 and the second buffer mechanism 70 ensure that the above-mentioned movement characteristics are achieved by providing appropriate damping force.

[0037] For details, please refer to Figures 1 to 4The first buffer mechanism 60 is located in the bottom region of the lifting mechanism assembly 30. The bottom region refers to the area near the lower stop point when the lifting mechanism assembly 30 is in its lowest position, or the end of the lifting mechanism assembly 30 facing the downward direction. During the lifting or lowering process of the lifting mechanism assembly 30 along the guide rail assembly 20, the first buffer mechanism 60 provides a buffering and damping effect, making the lifting and lowering motion of the lifting mechanism assembly 30 tend to be uniform. Specifically, when the lifting mechanism assembly 30 falls from a high position to a low position, gravity will cause it to accelerate downwards. The first buffer mechanism 60 generates a damping force in the opposite direction of motion, absorbing the kinetic energy during the descent, slowing down the descent speed, and preventing the lifting mechanism assembly 30 from hitting the lower stop point at too high a speed, thus preventing impact and noise. When the lifting mechanism assembly 30 rises from a low position to a high position, if there are fluctuations in the driving force, the first buffer mechanism 60 can also suppress sudden acceleration changes, keeping the upward speed stable.

[0038] One end of the second buffer mechanism 70 is connected to the flipping assembly 50, and the other end is connected to the lifting mechanism assembly 30. When the panel assembly 40 switches between the unfolded and retracted positions, the second buffer mechanism 70 provides a buffering and damping effect, making the movement of the panel assembly 40 tend to be uniform. Specifically, when the panel assembly 40 flips from the retracted position to the unfolded position, under the action of gravitational torque, the panel assembly 40 tends to accelerate downwards. The second buffer mechanism 70 applies an appropriate damping torque to the panel assembly 40 through the flipping assembly 50 to balance the changes in gravitational torque or driving torque, making the flipping speed of the panel assembly 40 uniform and controllable. Similarly, when the panel assembly 40 retracts from the unfolded position to the retracted position, the second buffer mechanism 70 prevents the panel assembly 40 from falling back quickly due to gravity or elasticity, ensuring a smooth retraction action.

[0039] As a preferred embodiment, the lifting mechanism assembly 30 includes a coil spring 31, which drives the lifting mechanism assembly 30 to lift. The first buffer mechanism 60 includes a coil spring damper 61, which is tractively connected to the coil spring 31. The coil spring 31 provides a driving force to move the lifting mechanism assembly 30 from the retracted position to the extended position. The force change of the coil spring 31 is matched with the torque change of the coil spring damper 61, and the torque change of the coil spring damper 61 is used to suppress the pop-out speed of the lifting mechanism assembly 30.

[0040] Specifically, when the lifting mechanism assembly 30 descends, the coil spring 31 is gradually stretched, and the coil spring damper 61 rotates accordingly, generating a damping torque. When the lifting mechanism assembly 30 ascends, the coil spring 31 retracts, and the coil spring damper 61 also provides a reverse damping torque. The torque of the coil spring damper 61 is related to the rotational speed. By properly matching the parameters of the coil spring 31 and the coil spring damper 61, the lifting mechanism assembly 30 can achieve an approximately constant speed during the ascent. Specifically, the coil spring 31 provides the greatest tension at its initial position, that is, at the lowest point of the lifting mechanism assembly 30. To overcome the gravity of the lifting mechanism assembly 30 and the panel assembly 40; as the lifting mechanism assembly 30 rises, the gravitational potential energy is gradually converted into kinetic energy, the tension of the coil spring 31 decreases, and at the same time the resistance torque of the coil spring damper 61 increases with the increase of rotational speed. The two work together to stabilize the speed. The coil spring 31 and the coil spring damper 61 have a compact matching structure, and uniform speed movement can be achieved during the lifting process without a complicated control system. At the same time, the coil spring 31 can provide driving force, reducing the operating force when the user manually raises it, which is especially suitable for lifting table panels 1 with large size or heavy panel.

[0041] Further, see Figures 5 to 6 The ideal constant reference tension of the coil spring 31 is determined based on the equivalent damping force of the coil spring damper 61 on the load side and the load weight of the lifting mechanism assembly 30 and the panel assembly 40; wherein, the overall load mass of the lifting mechanism assembly 30 and the panel assembly 40 is determined as follows: m The unit is kilograms, so the total weight is... mg Unit: Newtons, the total stroke of the lifting mechanism assembly 30 is... s Unit: kilogram, total time: t 总 The unit is seconds. The target uniform speed of the lifting mechanism is... ; that is, This is the torque value of the coil spring damper 61, in units of: , For the first specific constant, ,unit: , It is the second specific constant; ; The radius of the coil spring damper 61 is in meters; thus, the equivalent damping force on the load side is... , The radius of the coil spring is in meters, therefore the ideal constant reference tension of the coil spring is... .

[0042] The aforementioned parameter relationships provide engineers with a basis for selecting the first buffer mechanism 60 and the drive mechanism such as the coil spring 31. Therefore, in a specific embodiment, the overall load mass of the lifting mechanism assembly 30 and the panel assembly 40 is set. m=3 kg, at which point the total weight is . mg= 29.4 cows, g Select 9.8 m / s 2 The radius of the coil spring 31 is taken as follows r s = The radius of the coil spring damper 61 is 0.02 meters. =0.0045 meters, at this time the transmission ratio i= / r s = 0.225; The total stroke of the lifting mechanism assembly 30 is set to... s= 0.305 meters, total operating time of lifting mechanism assembly 30 t 总 = 2 seconds, therefore the target has a uniform speed =0.1525 m / s; Since the coil spring damper 61 is a calibration component, it has 100 200 400 Different models of the coil spring damper 61 have different values ​​for the first specific constant and the second specific constant, which vary with the model of the coil spring damper 61. These are calibration values; see [link to relevant documentation]. Figure 7 In this embodiment, a coil spring damper 61 with a diameter of 400 is selected. Let's take an example to illustrate this. =203.86×(2122 ) 0.300 Therefore, the lifting mechanism assembly 30 has different torque values ​​of the coil spring damping 61 under different load linear velocities, thus enabling it to adjust according to... Wait until a damping curve is found. The above The unit is After unit conversion 1 =9.8×10 -5 N m, therefore in this embodiment = ×9.8×10 -5 0.02= Therefore, under ideal conditions, that is, if the lifting mechanism assembly 30 and the panel assembly 40 are moving at a constant speed... If the lifting is completed at a speed of 0.1525 m / s, then the ideal uniform tension (constant) that the coil spring 31 can provide under ideal conditions is... =29.4 N + =29.4 N +5.78 N= 35.18 N Furthermore, based on this, select or customize the coil spring 31 so that its average tension output within the working stroke is close to... Furthermore, it should be noted that the actual output tension of the coil spring 31 inevitably fluctuates. This serves as a benchmark value to guide selection. Through quantitative formula derivation, the uniform motion requirement of the lifting mechanism assembly 30 is transformed into a calculable parameter for selecting the tension of the coil spring 31, avoiding the inefficiency of relying on repeated trial and error based on experience in traditional design. At the same time, the formula considers the superposition effect of load gravity and damping force, and can accurately match the needs of lifting table 1 with different weights and strokes, thus having wide applicability.

[0043] Furthermore, the actual lifting speed of the lifting mechanism assembly 30 under the ideal tension value selected by the actual speed measuring device was detected. See the following verification table of core performance indicators for spring selection. Figure 8 :

[0044] In time t= At 0.0 seconds, the actual speed of the lifting mechanism assembly 30 during movement. 实际 =0 m / s, in time t= At 0.5 seconds, the actual speed of the lifting mechanism assembly 30 during movement. 实际 =0.102 m / s, at this time the relative velocity to the target 目标 The deviation is -33.1%. The lifting mechanism assembly accelerates at 30 seconds relative to 0 seconds. t= At 0.1 seconds, the actual speed of the lifting mechanism assembly 30 during movement. 实际 =0.154 m / s, relative target speed 目标 The deviation is +0.98%, and the lifting mechanism assembly 30 is in an accelerated convergence state until time... t= At 0.2 seconds, the actual speed of the lifting mechanism assembly 30 during movement. 实际 =0.153 m / s, at this time the lifting speed of the lifting mechanism assembly 30 relative to the target speed 目标The deviation is +0.33%, and the speed is stable and uniform. The lifting is completed from 0.2 seconds to 2 seconds. During this period, the motion of the lifting mechanism assembly 30 is stable and uniform. Therefore, the speed phased characteristics can be obtained. In the instantaneous starting phase (0~0.1 seconds), the speed rises rapidly from 0 and converges to the vicinity of the target value in only 0.1 seconds. The maximum overshoot is only +0.98%, with no obvious impact. In the stable uniform speed phase (0.1~2.0 seconds), the speed is stable in the range of 0.151~0.154 m / s throughout the entire process. The fluctuation is less than ±1.5%, which almost coincides with the ideal uniform speed line.

[0045] Furthermore, as shown in the following core performance indicator verification table:

[0046] For the displacement-time curve, the total displacement of the lifting mechanism assembly 30 within 2 seconds is approximately 0.306 meters, with an error of only 0.39% compared to the target of 0.305 meters. The displacement curve is approximately linear, perfectly matching the characteristics of uniform motion. As for the acceleration-time curve, the acceleration remains within ±0.3 m / s after 0.1 seconds. 2 The fluctuation within the range is almost zero, which is better than maintaining a constant speed. Therefore, it can be concluded that the selection of spring component 31 is correct.

[0047] Furthermore, preferably, the nonlinear tension of the coil spring 31 is calculated, so as to optimize the selection of the coil spring 31 under the above-mentioned ideal force value based on the nonlinear tension of the coil spring 31. ;in The time point of the lifting mechanism assembly 30 during the lifting process is in seconds. Parameter P is the instantaneous tension compensation coefficient of the starting spring component 31, parameter Q is the exponential decay time constant, and parameter R is the linear decay coefficient of the tension.

[0048] Based on the selected coil spring 31 under the aforementioned ideal force value, since the damping force provided by the coil spring damper 61 at the moment of coil spring 31 activation is relatively large, a certain compensation force needs to be provided during the initial activation of the coil spring 31. In this embodiment, according to the selection of 400... The compensation coefficient for the instantaneous tension of the coil spring damper 61 is approximately 1.60~1.65. The optimal value obtained through fitting is 1.62. Since the lifting speed of the lifting mechanism assembly 30 reaches a near-uniform state within 0.1~0.15 seconds, the exponential decay time constant Q is approximately 0.10~0.15. The optimal value obtained through fitting is 0.12. Simultaneously, since the force of the coil spring 31 gradually decreases with the stroke, for the coil spring 31 with an ideal force of 35.18N in this embodiment, the decrease is approximately 0.5~0.6N during a 2-second lifting stroke. Therefore, the decay slope is between 0.25~0.3, and the optimal value obtained through fitting is 0.28. Therefore, for the nonlinear tension of the coil spring 31 in this embodiment… It can calculate the tension value that the coiled spring 31 can provide at any point in time, such as during instantaneous start-up. =0.05 seconds, at this time = =35.18 At the end of the lifting stroke, =1.5 seconds, at this time = =35.18 .

[0049] Therefore, in the actual lifting process of the lifting mechanism assembly 30, since the tension of the coil spring 31 is non-linear, the tension of the coil spring 31 at different lifting time points can be obtained based on the ideal tension of the coil spring 31. The nonlinear tension curve of the coil spring 31 is obtained. By introducing a nonlinear tension model, the actual output characteristics of the coil spring 31 can be described more accurately, providing a theoretical basis for simulation analysis and parameter optimization, and further selecting a coil spring 31 with a more optimal force value. At the same time, the model reveals the dynamic matching mechanism of the coordinated work of the coil spring 31 and the coil spring damper 61, which helps designers adjust the design parameters of the coil spring 31 for different working conditions, so as to achieve smooth start-up and stable operation of the lifting process.

[0050] Preferred, see Figures 9 to 11 The second buffer mechanism 70 includes a gas spring fixing seat 71 and a gas spring 72. The gas spring 72 is disposed in the gas spring fixing seat 71. One end of the gas spring 72 is connected to the gas spring fixing seat 71, and the other end is connected to the lifting mechanism assembly 30. The flipping assembly 50 includes a flipping plate 51. One end of the flipping plate 51 is rotatably connected to the panel assembly 40, and the other end of the flipping plate 51 is rotatably connected to the gas spring fixing seat 71 to form a movable end 52. The lifting mechanism assembly 30 is provided with a sliding groove 32. The movable end 52 is located in the sliding groove 32 and moves as the panel assembly 40 rotates and opens.

[0051] In this embodiment, the gas spring mounting base 71 is designed as a housing with an inner cavity, in which the body of the gas spring 72 is housed. By utilizing the cooperation between the sliding groove 32 and the movable end 52, the motion conversion between the flipping motion of the panel assembly 40 and the linear damping motion of the gas spring 72 is realized, resulting in a simple and reliable structure. At the same time, the flipping plate 51, as part of the transmission mechanism, can change the lever arm according to the flipping angle of the panel assembly 40, thereby optimizing the output characteristics of the damping force.

[0052] Preferably, the sliding groove 32 includes a first end 321 and a second end 322 distributed in a vertical direction. The end of the panel assembly 40 is directly connected to it in a manner that allows it to rotate relative to the lifting mechanism assembly 30. When the panel assembly 40 is in the retracted position, the movable end 52 is located at the first end 321 in the sliding groove 32. At this time, the panel assembly 40, the flip plate 51, and the gas spring fixing seat 71 are arranged parallel to each other. When the panel assembly 40 is in the unfolded position, the movable end 52 is located at the second end 322 in the sliding groove 32. At this time, the panel assembly 40, the flip plate 51, and the gas spring fixing seat 71 form a triangular linkage structure.

[0053] The aforementioned triangular linkage structure has high geometric stability and can withstand the vertical load when items are placed on the panel assembly 40. When the panel assembly 40 is in the folded position, the parallel stacking structure minimizes the storage space. When the panel assembly 40 is in the unfolded position, the triangular linkage structure uses the principle of geometric locking to enhance the rigidity of the panel assembly 40 in the horizontal position, preventing the panel from sagging due to insufficient rigidity of the gas spring 72 itself. At the same time, the position change of the movable end 52 in the sliding groove 32 changes the lever arm of the gas spring 72, so that the damping characteristics of the gas spring 72 match the change of gravitational torque during the flipping process of the panel assembly 40.

[0054] Preferably, the mass of the panel assembly 40 is determined to be... m 1 Gravity is m 1 g The center of gravity of the panel assembly is 40. G The distance between the gas spring fixing seat 71 and its connected rotating end is L G The sliding stroke of the sliding groove 32 is s. 滑 The uniform rotation of the panel assembly 40 requires that the net torque be zero at any given moment, thus... Among them, gravitational torque Unit: cow rice; For gas spring force, This refers to a 40° rotation angle for the panel assembly. When the angle is 0 degrees, the panel assembly 40 is in a vertical folded position. When the angle is 90 degrees, the panel assembly 40 is in a horizontal unfolded position. The gas spring lever arm, measured in meters, is the distance between the movable end 52 and the end directly connected to the lifting mechanism assembly 30 and the panel assembly 40 when the panel assembly 40 is in the retracted position. When the panel assembly 40 is in the unfolded position, the distance from the movable end 52 to the end of the rotating plate rotatably connected to the panel assembly 40 is the gas spring lever arm. ; = , here Unit: rad.

[0055] Therefore, in one specific embodiment, the mass of the panel assembly 40 m 1 =2 kg, the gravity is . m 1 g= 19.6 cows, g Select 9.8 m / s 2 When the panel assembly 40 is in the unfolded position, the distance from the center of gravity of the panel assembly 40 to the gas spring mounting base 71 and its connected rotating end is... L G The rotation target of the panel assembly 40 is set to 0.17 meters, which means it rotates 90 degrees at a constant speed from a vertically folded position to a horizontally unfolded position, with angular acceleration of 0 and resultant torque of 0. The sliding stroke of the sliding groove 32 is set. s 滑 =0.029583 meters. When the panel assembly 40 is in the retracted position, the distance between the movable end 52 and the end directly connected to the lifting mechanism assembly 30 and the panel assembly 40 is the gas spring lever arm. =0.028383 meters. When the panel assembly 40 is in the unfolded position, the distance from the movable end 52 to the end of the rotating plate rotatably connected to the panel assembly 40 is the gas spring lever arm. =0.073383 meters. Meanwhile, uniform rotation requires torque balance, which means the net torque must be zero at any given moment, i.e. , gas spring lever arm As the panel assembly 40 rotates at different angles, its movement is determined by the triangular linkage structure and the sliding stroke of the movable end 52 within the sliding groove 32. =0 corresponds to =0.028383 meters, When =90, the corresponding =0.073383 meters, therefore =19.6×0.17× / (0.02838+0.028648) ), The value is in radians (rad). In a physical sense, the numerator is the gravitational torque, which decreases with the cosine of the angle, and the denominator is the lever arm of the gas spring, which increases linearly with the angle. The two are matched in real time to ensure that the resultant torque is 0, so as to achieve uniform rotation.

[0056] Furthermore, please refer to the table below for the numerical parameters of the gas spring force at key angles during the panel assembly flipping process:

[0057] At the critical flipping angle of the panel assembly 40, when the panel assembly 40 is in a vertical position, i.e., in the folded position, the panel assembly 40 does not undergo relative displacement. The movable end 52 of the flip plate 51 is located within the sliding groove 32 and does not undergo displacement. The gas spring lever arm... = =0.028383 meters, gas spring force = =117.32N. When the panel assembly 40 is rotated 22.5 degrees, the movable end 52 moves upward 0.0074 mm within the sliding groove 32. At this time, the gas spring lever arm... = =0.039729 meters, gas spring force = =97.31N, and so on. When the panel assembly 40 is horizontal, that is, in the unfolded position, the movable end 52 is located at the top of the sliding groove 32, and the gas spring lever arm... = =0.073383 meters, gas spring force = =0N, at this time the gas spring 72 does not provide force.

[0058] Furthermore, from the curve characteristics, in the initial segment (0°~22.5°), the gas spring force slowly decreases from 117.32N, compensating for the slow decay of the gravitational torque and the slight increase in the lever arm; in the middle segment (22.5°~67.5°), the gas spring force decreases rapidly, matching the rapid decay of the gravitational torque, while the lever arm continues to increase; in the final segment (67.5°~90°), the gas spring force approaches 0, because the gravitational torque is 0 at 90°, only the friction of the mechanism needs to be overcome (which is negligible); the force value changes smoothly throughout the entire range without abrupt changes, perfectly offsetting the gravitational torque and achieving uniform rotation. Therefore, in this embodiment, the gas spring can be selected accordingly based on the above-mentioned gas spring force values.

[0059] For further optimization, see [link to relevant documentation]. Figures 12 to 13The flipping assembly 50 also includes a stop mechanism 80, which is located between the second buffer mechanism 70 and the lifting mechanism assembly 30. The stop mechanism 80 has multiple limit positions. When the panel assembly 40 switches between the closed position and the open position, the stop mechanism 80 can be located at different limit positions, which can keep the panel assembly 40 in different predetermined positions.

[0060] Preferably, the stop mechanism 80 includes a slot 81 and a locking member 82 that cooperate with each other; the slot 81 is disposed on the lifting mechanism assembly 30, and the locking member 82 is disposed on the second buffer member; the end of the locking member 82 is provided with an elastic member 83, so that the locking member 82 can elastically engage or disengage from the slot 81 when the panel assembly 40 changes position, so as to realize the switching and positioning of different gears.

[0061] Specifically, the slot 81 and the engaging member 82 constitute an elastic positioning mechanism. The slot 81 can be a series of recesses or grooves arranged along the direction of the sliding groove 32, with each recess corresponding to a limit position. These slots 81 are directly formed on the side wall of the lifting seat of the lifting mechanism assembly 30. The engaging member 82 is a positioning pin or positioning ball, mounted on the second buffer member, such as the gas spring fixing seat 71. The end of the engaging member 82 extends towards the lifting seat and is aligned with the position of the slot 81. The elastic member 83 can be a compression spring or a spring sheet, with one end abutting against the tail end of the engaging member 82 and the other end abutting against the spring seat on the second buffer member.

[0062] In its free state, the elastic element 83 pushes the engaging element 82 towards the slot 81, causing the end of the engaging element 82 to embed into one of the slots 81, thereby preventing the second buffer from moving relative to the lifting mechanism assembly 30. When the panel assembly 40 flips, the elastic element 83 is compressed, causing the engaging element 82 to disengage from the current slot 81. As the second buffer continues to move, the end of the engaging element 82 falls into the next slot 81 under the action of the elastic element 83, producing a clear positioning feel. The mechanical positioning method using the slots 81 and the engaging element 82 is simple in structure, low in cost, and highly reliable. The presence of the elastic element 83 ensures that the engaging element 82 can automatically reset without additional user operation. At the same time, the limiting effect of the engaging element 82 and the slot 81 provides a stop function when the panel assembly 40 is closed and opened, ensuring the stability of the panel assembly 40 when closed and opened.

[0063] Preferably, the slot 81 is a triangular slot with a guide slope 811 on its wall; the end of the engaging member 82 that engages with the slot 81 is set with an arc-shaped end so that the engaging member 82 can smoothly enter or exit the slot 81 under the action of the elastic member 83.

[0064] The triangular slot refers to the cross-section of the slot 81 being approximately V-shaped or triangular, with a sharp corner or small arc at the bottom and inclined planes on both sides. The guide ramps 811 are these two inclined planes, which are at a certain angle relative to the center line of symmetry of the slot, such as 45 degrees or 60 degrees. When the engaging component 82 exits the slot 81, the arc-shaped end of the engaging component 82 first contacts the guide ramps 811. Since the ramps decompose the vertical pressure on the engaging component 82 into a thrust along the ramp direction, this thrust helps overcome the preload of the elastic component 83, allowing the engaging component 82 to slide out smoothly. Conversely, when the engaging component 82 enters the slot 81, the arc-shaped end slides smoothly into the bottom of the slot along the guide ramps 811 without jamming.

[0065] The arc-shaped end can be achieved by rounding the spherical, hemispherical, or cylindrical end. The inclination angle of the guide slope 811 should not be too large or too small. If it is too large, it will result in excessive pull-out force; if it is too small, it will result in unstable positioning. It is usually chosen to be between 30 and 60 degrees. In addition, the depth of the slot 81 matches the radius of the end of the engaging part 82, so that after the engaging part 82 is completely in the slot 81, the second buffer cannot be pulled out by itself without external force. The combination of the triangular slot and the arc-shaped end has both guiding and self-locking properties. On the one hand, it reduces friction and wear during movement and extends service life; on the other hand, it provides a stable holding force in the positioning state to prevent accidental disengagement due to vibration or slight external force. At the same time, this shape is easy to mass-produce through injection molding or machining, which has high economic and processability.

[0066] Further, see Figure 14 and Figure 15 The first buffer mechanism 60 also includes a first buffer spring 62, which is disposed between the lower bottom of the lifting mechanism assembly 30 and the support assembly 10, and is used to prevent the lifting mechanism assembly 30 from directly impacting the lower bottom of the support assembly 10 and causing abnormal noise under bumpy conditions; the second buffer mechanism 70 also includes a base 73 connected to the guide rail assembly 20, and a second buffer spring 74, which is connected to the base 73 to provide a buffering effect to the lifting mechanism assembly 30 and avoid the lifting mechanism assembly 30 from impacting the base 73 and causing abnormal noise.

[0067] The basic principles, main features, and advantages of this application have been described above. Those skilled in the art should understand that this application is not limited to the above embodiments. The embodiments and descriptions in the specification are merely the principles of this application. Various changes and modifications can be made to this application without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claims. The scope of protection claimed by this application is defined by the appended claims and their equivalents.

Claims

1. A height-adjustable tabletop, characterized in that, include: Bracket assembly; The guide rail assembly is fixedly connected to the bracket assembly; The lifting mechanism assembly is connected to the guide rail assembly in a manner that allows it to move vertically. The panel assembly is connected to the lifting mechanism assembly via a flip component, and the panel assembly can switch between a folded position and an unfolded position relative to the lifting mechanism assembly; The first buffer mechanism is located in the bottom area of ​​the lifting mechanism assembly and provides a buffering and damping effect during the lifting mechanism assembly's rise or fall along the guide rail assembly, so that the lifting mechanism assembly's rising and falling motion tends to be smooth. The second buffer mechanism is connected at one end to the flipping component and at the other end to the lifting mechanism assembly. When the panel assembly switches between the unfolded position and the retracted position, the second buffer mechanism provides a buffering and damping effect, making the movement of the panel assembly more gradual.

2. The lifting table as described in claim 1, characterized in that, The lifting mechanism assembly includes a coil spring, which drives the lifting mechanism assembly to lift. The first buffer mechanism includes a coil spring damper, and the coil spring is throttle connected to the coil spring damper. The coil spring provides a driving force to move the lifting mechanism assembly from the retracted position to the extended position. The force change of the coil spring is matched with the torque change of the coil spring damping, and the ejection speed of the lifting mechanism assembly is suppressed by the torque change of the coil spring damping.

3. The lifting table as described in claim 1, characterized in that, The second buffer mechanism includes a gas spring mounting base and a gas spring. The gas spring is disposed in the gas spring mounting base. One end of the gas spring is connected to the gas spring mounting base, and the other end is connected to the lifting mechanism assembly. The flipping assembly includes a flipping plate, one end of which is rotatably connected to the panel assembly, and the other end of which is rotatably connected to the gas spring fixing seat to form a movable end. The lifting mechanism assembly is provided with a sliding groove, and the movable end is located in the sliding groove and moves as the panel assembly rotates and opens.

4. The lifting table as described in claim 3, characterized in that, The sliding groove includes a first end and a second end distributed in a vertical direction. The end of the panel assembly is directly connected to it in a manner that allows it to rotate relative to the lifting mechanism assembly. When the panel assembly is in the retracted position, the movable end is located at the first end in the sliding groove. At this time, the panel assembly, the flip plate, and the gas spring fixing seat are arranged parallel to each other. When the panel assembly is in the unfolded position, the movable end is located at the second end within the sliding groove. At this time, the panel assembly, the flip plate, and the gas spring fixing seat form a triangular linkage structure.

5. The lifting table as described in any one of claims 1-4, characterized in that, The flipping assembly also includes a stop mechanism, which is located between the second buffer mechanism and the lifting mechanism assembly. The stop mechanism has multiple limit positions. When the panel assembly switches between the closed position and the open position, the stop mechanism can be located at different limit positions to keep the panel assembly in different predetermined positions.

6. The lifting table as described in claim 5, characterized in that, The stop mechanism includes a slot and a locking element that cooperate with each other; The slot is provided on the lifting mechanism assembly, and the engaging member is provided on the second buffer member; the end of the engaging member is provided with an elastic member, so that the engaging member can elastically engage or disengage from the slot when the panel assembly changes position, so as to realize the switching and positioning of different gears.

7. The lifting table as described in claim 1, characterized in that, The first buffer mechanism further includes a first buffer spring, which is disposed between the lower bottom of the lifting mechanism assembly and the support assembly, and is used to prevent the lifting mechanism assembly from directly impacting the lower bottom of the support assembly and producing abnormal noise in a bumpy state; The second buffer mechanism further includes a base connected to the guide rail assembly and a second buffer spring connected to the base to provide a buffering effect to the lifting mechanism assembly and prevent the lifting mechanism assembly from impacting the base and causing abnormal noise.

8. A design method for a coil spring component in a lifting table, wherein the design method for the coil spring component in a lifting table is applicable to the lifting table as described in claim 2, characterized in that, include: Step S10: Determine the overall load mass of the lifting mechanism assembly and the panel assembly as follows: m The unit is kilograms, so the total weight is... mg Unit: Newton, the total stroke of the lifting mechanism assembly is s Unit: kilogram, total time: t 总 The unit is seconds, then the target uniform speed of the lifting mechanism is... ; Step S20: Select a coil spring damper of the specified calibration specifications; Step S30: Calculate the rotational speed of the coil spring damper, where ; The radius of the coil spring damper, in meters. The rotational speed of the coil spring damper, in units of: The constant 60 represents 60 seconds; Step S40: Calculate the torque value of the coil spring damping, where , The torque value of the coil spring damping, in units of: , Therefore, the first specific constant corresponding to the coil spring damping under the specified calibration is determined. Therefore, the second specific constant corresponding to the coil spring damping under the specified calibration is determined; Step S50: Calculate the equivalent damping force of the coil spring on the load side, where , This is the equivalent damping force of the coil spring on the load side, in Newtons (N). The radius of the coiled spring is in meters. Step S60: Calculate the ideal constant reference tension of the coil spring, that is... , The ideal constant reference tension of the coil spring, in Newtons; Step S70: According to the above The value is used to select a coil spring with a suitable tension value.

9. The design method of the lifting table as described in claim 8, characterized in that, Following step S70, step S71 is further included: calculating the nonlinear tension of the coil spring to optimize the selection of the coil spring based on the nonlinear tension of the coil spring, wherein, ,in The time point during the lifting process of the lifting mechanism assembly is expressed in seconds. This refers to the nonlinear tension of the coil spring, measured in Newtons (N). Parameter P is the instantaneous tension compensation coefficient for the coil spring during startup, parameter Q is the exponential decay time constant, and parameter R is the linear decay coefficient of the tension.

10. A design method for a gas spring in a height-adjustable tabletop, wherein the design method for the gas spring in a height-adjustable tabletop is applicable to the height-adjustable tabletop as described in claim 4, characterized in that... include: Step S100: Determine the mass of the panel assembly as follows: m 1 The weight of the panel assembly is... m 1 g ; Step S200: Calculate the gravitational torque of the panel assembly at any flip angle, that is... ,in, This refers to the flip angle of the panel assembly. When the angle is 0 degrees, the panel assembly is in a vertical folded position. When the angle is 90 degrees, the panel assembly is in a horizontal unfolded position. The gravitational torque of the panel assembly at any flip angle, in Newtons. rice, The distance from the center of gravity of the panel assembly to the gas spring mounting base and its connected rotating end when the panel assembly is in the unfolded position, in meters; Step S300: Calculate the lever arm of the gas spring when the panel assembly is at any flip angle, that is... = ,in, The lever arm of the gas spring is the distance between the movable end of the panel assembly and the end of the lifting mechanism assembly directly connected to the panel assembly when the panel assembly is in the retracted position. The unit is meters. When the panel assembly is in the unfolded position, the distance from the movable end to the end of the rotating plate rotatably connected to the panel assembly is the lever arm of the gas spring. , here unit: rad ; Step S400: The uniform rotation of the panel assembly requires that the resultant torque be 0 at any given time, thus... , that is ,in, This refers to the gas spring force of the panel assembly at any flip angle, measured in Newtons (N). Step S500: Based on the gas spring force The value is used to select a gas spring with an appropriate force value.

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