Anti-overturning design method for sliding assembly

Abstract

The application relates to an anti-overturning design method of a sliding assembly. The design method is based on a sliding block adopting a planar gap throttling feedback self-adaptive adjustment model, reference overturning force value and variable overturning force value of the sliding block are obtained, and reference size parameter groups and variable size parameter groups of the sliding block and quantitative data in the sliding assembly are selected. First spacing difference value and second spacing difference value of the sliding block are calculated and obtained based on the above steps, the first spacing difference value and the second spacing difference value are compared to select a target size parameter group from the variable size parameter groups, the target size parameter group is a target size parameter group of the sliding block, and finally, the anti-overturning sliding block is designed and generated based on the target size parameter group. Therefore, the anti-overturning design method of the sliding assembly can make the sliding assembly have the anti-overturning capability, so that the precision machine tool provided with the sliding assembly designed according to the design method has higher precision.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of precision machine tools, in particular to an anti-overturning design method of a sliding assembly. BACKGROUND

[0002] A precision machine tool is a machine tool that can perform high-precision machining. Its machining precision is usually much higher than that of ordinary machine tools, and can reach micron or even nanometer level precision. The sliding assembly (such as a guide rail) of the precision machine tool provides precise guidance for the moving parts, and a high-quality sliding assembly helps to maintain the precision of the machine tool.

[0003] In related technologies, the machine body of the precision machine tool is provided with a sliding groove, a sliding block of a sliding assembly is arranged in the sliding groove, and a sliding carrier in the sliding assembly is fixedly connected with the sliding block, so that the sliding carrier moves along the extension direction of the sliding groove by moving the sliding block along the sliding groove. The sliding carrier is used to load the tool (for example, a turning tool, a milling tool, and a grinding head) of the machine tool, and the tool is arranged on one side of the sliding carrier in the sliding direction of the sliding carrier. In this way, the tool can be moved by driving the sliding carrier to move.

[0004] However, the tool is arranged on one side of the sliding carrier in the sliding direction of the sliding carrier, which also causes the sliding assembly to be subjected to unbalanced load. Under normal circumstances, the friction between the sliding assemblies is uniformly distributed, but unbalanced load can cause excessive local pressure. When the precision machine tool is machining, the movement trajectory of the tool depends on the precise guidance of the sliding assembly. When the sliding assembly is subjected to unbalanced load, the moving parts will deviate from the normal movement path, and the service life and precision of the sliding assembly will also be affected. SUMMARY

[0005] Therefore, it is necessary to provide an anti-overturning design method of a sliding assembly in view of the problem of unbalanced load of the sliding assembly.

[0006] An anti-overturning design method of a sliding assembly includes the following steps:

[0007] S1, obtaining a reference overturning force value of each prototype sliding block, and obtaining a variable overturning force value of each prototype sliding block;

[0008] S2, selecting quantitative data in the sliding assembly;

[0009] S3, selecting a reference size parameter group and a plurality of variable size parameter groups based on each of the prototype sliding blocks;

[0010] S4, obtaining a first interval difference value and a second interval difference value, wherein step S4 includes:

[0011] S41, obtaining a first reference interval and a second reference interval of each prototype slider, the first reference interval and the second reference interval being obtained according to the reference overturning component force value and the reference size parameter group,

[0012] S42, obtaining a plurality of first variable intervals and a plurality of second variable intervals of each prototype slider, the first variable interval and the second variable interval being obtained according to the variable overturning component force value and the variable size parameter group,

[0013] S43, obtaining a plurality of first interval differences based on the first reference interval and each first variable interval, each first variable interval being operated with the first reference interval to obtain a corresponding first interval difference,

[0014] S44, obtaining a plurality of second interval differences based on the second reference interval and each second variable interval, each second variable interval being operated with the second reference interval to obtain a corresponding second interval difference;

[0015] S5, comparing the first interval difference of each prototype slider, comparing the second interval difference of each prototype slider, and selecting a target size parameter group from the plurality of variable size parameter groups obtained.

[0016] In one embodiment, step S1 includes:

[0017] S11, determining the position of the center of gravity of the mobile load carrier in the sliding direction of the mobile load carrier;

[0018] S12, determining the center of gravity interval of each prototype slider and the mobile load carrier in the sliding direction;

[0019] S13, selecting a reference gravity value of the mobile load carrier and a plurality of variable gravity values;

[0020] S14, obtaining each reference overturning component force value based on the reference gravity value, and obtaining each variable overturning component force value based on the variable gravity value.

[0021] In one embodiment, step S13 satisfies the relationship: the variable gravity value is greater than the reference gravity value.

[0022] In one embodiment, in step S2, the quantitative data includes the upper working groove area, the lower working groove area, the oil sealing edge size, the dynamic viscosity of the pressure oil in the sliding assembly, and the oil source pressure value based on the prototype slider.

[0023] In one embodiment, in step S3, the size parameters based on the prototype slider include the throttle edge of the working groove, the throttle edge of the throttle, and the throttle edge of the pressure oil groove in the throttle, and the size parameters are divided into a reference size parameter group and a variable size parameter group.

[0024] In one of the embodiments, the variable dimension parameter group of the throttle edge of the working groove of the lower end surface is greater than the reference dimension parameter group,

[0025] the variable dimension parameter group of the throttle edge of the throttle of the upper end surface is greater than the reference dimension parameter group,

[0026] the variable dimension parameter group of the throttle edge of the pressure oil groove of the upper end surface is less than the reference dimension parameter group.

[0027]

[0028] In one of the embodiments, the throttle edge of the working groove includes a first throttle edge, a second throttle edge, a third throttle edge, and a fourth throttle edge, and the throttle edge of the throttle includes a fifth throttle edge and a sixth throttle edge.

[0029] In one of the embodiments, in step S5, a first interval difference value that is close to the same for each of the plurality of prototype sliders is selected from the plurality of first interval difference values of the plurality of prototype sliders, and a target dimension parameter group is selected from the plurality of variable dimension parameter groups based on the first interval difference value.

[0030] In one of the embodiments, the anti-overturning design method further includes the following steps:

[0031] S6, the plurality of anti-overturning sliders designed based on the target dimension parameter group are arranged on the slide rail of the sliding assembly, and the relative positional relationship between the anti-overturning sliders and the moving load body in the sliding direction is equivalent to the relative positional relationship between the sliders and the moving load body in the sliding direction.

[0032] The anti-overturning design method of the sliding assembly described above, which is based on a slider using a planar gap throttle feedback self-adaptive adjustment model, obtains a reference overturning force value and a variable overturning force value of the slider, and selects quantitative data in the sliding assembly and a reference dimension parameter group and a variable dimension parameter group of the slider. After the above steps, a first interval difference value and a second interval difference value of the slider are calculated and obtained, a target dimension parameter group is selected from the plurality of variable dimension parameter groups by comparing the first interval difference value and the second interval difference value, and an anti-overturning slider designed based on the target dimension parameter group has the ability to resist overturning. Therefore, the anti-overturning design method of the sliding assembly described above can enable the sliding assembly to have the ability to resist overturning, so that the precision machine tool equipped with the sliding assembly designed according to the design method of the present application has higher precision. BRIEF DESCRIPTION OF DRAWINGS

[0033] Figure 1 Flowchart of the anti-overturning design method of the sliding assembly according to an embodiment of the present application.

[0034] Figure 2 ​A schematic diagram of force analysis of the slider in the sliding assembly according to an embodiment of the present application.

[0035] Figure 3 A schematic diagram of the structure of the slider according to an embodiment of the present application.

[0036] Figure 4 A top view of a precision machine tool equipped with a sliding assembly according to an embodiment of the present application (part of the structure is not shown).

[0037] Reference signs:

[0038] 1, prototype slider; 1a, first slider; 1b, second slider; 10, anti-overturning slider; 10a, first anti-overturning slider; 10b, second anti-overturning slider; 11, throttle; 110, oil delivery groove; 120, pressure oil groove; 12, working groove; 2, moving load body; 21, sliding load body; 22, tool;b i3 , first throttle edge;b i4 , second throttle edge;l i2 , third throttle edge;l i3 , fourth throttle edge;l i1 , fifth throttle edge;b i1 , sixth throttle edge;b i2 , seventh throttle edge;100, upper boundary; 200, lower boundary. DETAILED DESCRIPTION

[0039] In order to make the above objectives, features and advantages of the present application more obvious and easy to understand, the specific embodiments of the present application are described in detail below in conjunction with the drawings. In the following description, a large number of specific details are set forth in order to facilitate a full understanding of the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without departing from the spirit of the present application, so the present application is not limited to the specific embodiments disclosed below.

[0040] In the description of the present application, it should be understood that if these terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like appear, these terms indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the purpose of facilitating the description of the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0041] In addition, if there are terms such as "first", "second", these terms are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the features defined as "first", "second" can be explicitly or implicitly included at least one feature. In the description of the present application, if the term "multiple" appears, the meaning of "multiple" is at least two, such as two, three, etc., unless otherwise explicitly specified.

[0042] In the present application, unless otherwise explicitly specified and limited, if the terms "mounting", "connecting", "connecting", "fixing" and the like appear, these terms should be interpreted broadly. For example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the internal communication of two elements or the interaction relationship between two elements, unless otherwise explicitly limited. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0043] In the present application, unless otherwise explicitly specified and limited, if the first feature is described as "on" or "below" the second feature, etc. The meaning can be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature "above", "above" and "above" the second feature can be the first feature directly above or obliquely above the second feature, or only indicates that the first feature is higher than the second feature in horizontal height. The first feature "below", "below" and "below" the second feature can be the first feature directly below or obliquely below the second feature, or only indicates that the first feature is lower than the second feature in horizontal height.

[0044] It should be noted that if an element is referred to as "fixed to" or "provided on" another element, it can be directly on another element or there can be a middle element. If an element is considered to be "connected" to another element, it can be directly connected to another element or there can be a middle element. If present, the terms "vertical", "horizontal", "up", "down", "left", "right" and similar expressions used in the present application are only for illustrative purposes and do not represent the only implementation.

[0045] Referring to Figures 1 to 3 As shown, the structure of the prototype slider used in the anti-overturning design method of the sliding assembly according to some embodiments of the present application is designed based on a planar gap throttling feedback self-adaptive adjustment model. The pressure bearing mode of the prototype slider is closed hydrostatic pressure bearing. The prototype slider can independently adjust the oil film stiffness of the pressure bearing surface according to the corresponding prototype slider load, thereby realizing the anti-overturning capability of the sliding assembly. It should be understood that:

[0046] 1. Planar gap throttling feedback adaptive regulation model: a kind of liquid static pressure throttling mode, the gap throttling function between planes is used to hinder liquid from flowing out of the oil cavity, form a bearing oil film, so that the liquid in the oil cavity maintains a certain pressure, and the supporting function is realized. In the slider based on the planar gap throttling feedback adaptive regulation model, the oil cavity is communicated in the thickness direction of the slider, so that the pressure change of one side oil cavity is transmitted to the associated oil cavity to adjust the oil cavity pressure, to balance the load, and achieve the effect of self-feedback regulation. For example, refer to Figure 2 As shown, the prototype slider 1 is formed with a gap with the upper boundary 100 and the lower boundary 200, and oil under pressure flows in the gap. It is also understood that the distance between the upper end surface of the prototype slider 1 and the upper boundary 100 is the upper oil film thickness of the prototype slider 1 (which can also be understood as the upper throttling gap of the prototype slider 1), and the distance between the lower end surface of the prototype slider 1 and the lower boundary 200 is the lower oil film thickness of the prototype slider 1 (which can also be understood as the lower throttling gap of the prototype slider 1).

[0047] 2. Closed liquid static pressure bearing: oil cavities are provided in all directions except the moving direction of the slider, forming a geometric closure to constrain the degree of freedom in the non-moving direction, and ensure smooth operation of the moving part.

[0048] 3. Oil film stiffness: the ability of the oil film in the planar gap to resist load changes when bearing load. That is, the change rate of the oil film thickness relative to the load change.

[0049] For example, refer to Figure 1 As shown, the anti-overturning design method of the sliding assembly according to some embodiments of the application includes the following steps S1, S2, S3, S4 and S5.

[0050] Among them, step S1 is to obtain the reference overturning component value of each prototype slider, and to obtain the variable overturning component value of each prototype slider. In step S1, the following steps are also included, such as step S11 for determining the position of the center of gravity of the moving load body in the sliding direction of the moving load body, step S12 for determining the center of gravity distance between each prototype slider and the moving load body in the sliding direction, step S13 for selecting a reference gravity value and a plurality of variable gravity values of the moving load body, step S13 for obtaining each reference overturning component value based on the reference gravity value, and obtaining each variable overturning component value based on the variable gravity value, step S13 for obtaining each reference overturning component value based on the reference gravity value, and obtaining each variable overturning component value based on the variable gravity value.

[0051] It needs to be supplemented that, in combination with Figure 2 and Figure 4As shown, the movable load body 2 may include a sliding carrier 21 in the sliding assembly and a cutting tool 22 of a precision machine tool. In the moving direction of the sliding carrier 21, the relationship between the sliding carrier 21 and the multiple prototype sliders 1 is a non-eccentric loading state. This can also be understood as follows: when the cutting tool 22 is not mounted on the sliding carrier 21, the sliding assembly is in an ideal non-eccentric loading state; after the cutting tool 22 is mounted on the sliding carrier 21, the sliding assembly is in an unideal eccentric loading state. Therefore, the relative position of the cutting tool 22 and the prototype slider carrier 21 affects the center of gravity position of the movable load body 2 in its sliding direction. In the embodiments of this application, the center of gravity position of the movable load body 2 is fixed; this can also be understood as the center of gravity of the movable load body 2 being a fixed parameter that will not change.

[0052] However, when the set tool mass changes, the gravity value of the moving load (i.e., the reference gravity value and the variable gravity value) will change. In this application, a reference gravity value and a variable gravity value of the moving load are selected, and the reference gravity value can be compared with different variable gravity values. It is worth noting that in step S13, the following relationship must be satisfied: the selected variable gravity value must be greater than the reference gravity value. For example, if the reference gravity value is selected as 100 N (Newtons), then the variable gravity value can be selected as 101 N, 110 N, 120 N, 130 N, etc., which are force values ​​greater than 100 N.

[0053] Combination Figure 2 and Figure 4 As shown, along the sliding direction of the moving load body 2 (i.e. Figure 2 As shown in the X direction, multiple prototype sliders 1 are arranged sequentially. Since each prototype slider 1 is fixedly connected to the sliding carrier 21 of the moving load body, the relative positional relationship between each prototype slider 1 and the moving load body 2 is fixed in the sliding direction. Furthermore, as mentioned above, the center of gravity of the moving load body 2 is a fixed parameter. Therefore, step S12 can be completed through calculation, that is, the distance between the centers of gravity of each prototype slider 1 and the moving load body 2 in the sliding direction can be determined. For example, see [reference needed]. Figure 2 As shown, in some embodiments of this application, taking the sliding component with two prototype sliders 1 as an example, one prototype slider 1 is the first slider 1a, and the other prototype slider 1 is the second slider 1b. From Figure 2 It can be seen that the center-of-gravity distance D1 between the first slider 1a and the moving load body 2 in the sliding direction is equal to the center-of-gravity distance D2 between the second slider 1b and the moving load body 2 in the sliding direction. Furthermore, after selecting a reference gravity value and multiple variable gravity values, the overturning force component value corresponding to each prototype slider is calculated. Each overturning force component value is a value required for subsequent calculations.

[0054] The step S2 is selecting quantitative data in the sliding assembly, the quantitative data in the sliding assembly includes the upper working groove area, the lower working groove area, the oil sealing edge size of the prototype slider, the dynamic viscosity of the pressure oil in the sliding assembly, and the oil source pressure value.

[0055] As shown in Figure 2 and Figure 2 In the prototype slider 1 of the present application, the upper end face and the lower end face of the prototype slider 1 are respectively provided with a throttle 11 and a working groove 12 along the thickness direction of the prototype slider 1, wherein the throttle 11 has an oil delivery groove 110 and a pressure oil groove 120, and the pressure oil groove 120 is located in the oil delivery groove 110. More specifically, as shown in Figure 3 and Figure 2 The pressure oil groove 120 in the throttle 11 provided on the upper end face is in communication with the working groove 12 provided on the lower end face, and the pressure oil groove 120 in the throttle 11 provided on the lower end face is in communication with the working groove 12 provided on the upper end face. In this way, the oil pump can deliver pressure oil to the oil delivery groove 110 of the throttle 11 provided on the upper end face, and then the pressure oil located in the oil delivery groove 110 flows into the pressure oil groove 120 located in the oil delivery groove 110, and then flows along the pipeline arranged inside the prototype slider 1 to the working groove 12 provided on the lower end face through the pressure oil groove 120. At the same time, the oil pump can also deliver pressure oil to the oil delivery groove 110 of the throttle 11 provided on the lower end face, and then the pressure oil located in the oil delivery groove 110 flows into the pressure oil groove 120 located in the oil delivery groove 110, and then flows along the pipeline arranged inside the prototype slider 1 to the working groove 12 provided on the upper end face through the pressure oil groove 120. As shown in Figure 3 , Figure 3 The area of the working groove 12 shown in

[0056] The step S3 is selecting a reference size parameter group and a plurality of variable size parameter groups based on each prototype slider, and the reference size parameter group and the variable size parameter group are both size parameters of the prototype slider, except that the reference size parameter group and the variable size parameter group are the relative relationship of the reference group and the control group, wherein the reference size parameter group corresponds to the reference group, and the variable size parameter group corresponds to the control group, that is, the variable size parameter group is a variable reference of the reference size parameter group. The size parameters of the prototype slider include the throttle edge of the working groove, the throttle edge of the throttle, and the throttle edge of the pressure oil groove in the throttle. It can also be understood that both the reference size parameter group and the variable size parameter group have data about the throttle edge of the working groove, and the difference between the two groups of data is that the specific parameter values in the two groups of data are different.

[0057] And based on the prototype slider, the following relationships should be met when selecting the size parameters: 1. The variable size parameter group of the throttle edge of the working groove about its lower end surface is greater than the reference size parameter group. 2. The variable size parameter group of the throttle edge of the throttle about its upper end surface is greater than the reference size parameter group. 3. The variable size parameter group of the throttle edge of the pressure oil groove about its upper end surface is less than the reference size parameter group.

[0058] Referring to Figure 3 illustrated, in some embodiments of the present application, the throttle edge of the working groove 12 includes a first throttle edge b i3 , a second throttle edge b i4 , a third throttle edge l i2 , a fourth throttle edge l i3 , the throttle edge of the throttle 11 includes a fifth throttle edge l i1 and a sixth throttle edge b i1 , and the throttle edge of the pressure oil groove 110 is a seventh throttle edge b i2 .

[0059] For example, in combination with Figure 3 illustrated, when the gravity value G of the moving load body increases, the moving load body as a whole moves downward, that is Figure 2 h11, h12 in have a trend of increasing.

[0060] According to the following formulas (1), (2), (3), (4)

[0061] (1)

[0062] Then take the derivative of q and Pi respectively, where for the working groove, , then:

[0063] (2)

[0064] (3)

[0065] For the throttle, , is a constant, then:

[0066] (4)

[0067] It should be noted that:

[0068] q: the flow rate of pressure oil flowing into the working groove; ΔP: the pressure difference between the upper and lower ends of the pressure oil groove and the working groove; P: the pressure in the pressure oil groove; L: the length of the working groove; bi: the width of the working groove; h: the gap height between the upper end surface of the prototype slider and the rail end surface; u: the dynamic viscosity of the pressure oil.

[0069] From the above formulas (2) and (3), it can be seen that for the working groove set on the lower end face of the prototype slider, the rate of change of h relative to q and P is negatively correlated, that is, the greater the flow rate and pressure, the smaller the rate of change of oil film thickness, that is, the greater the oil film stiffness. Furthermore, when the gravity value G increases, the entire moving load body shifts downwards, leading to... Figure 2 h 11 h 12 As the size increases, the throttling capacity of the working surface on the upper end face of the prototype slider decreases, thereby increasing the flow rate of the throttle in the upper end face of the prototype slider into the working groove on the lower end face of the prototype slider through the internal oil passage, resulting in increased oil film stiffness on the lower end face of the prototype slider.

[0070] And as shown in equation (4), for the throttle located on the upper surface of the prototype slider, h is positively correlated with the rate of change of P, that is, the larger h is, the larger P is. (Refer to...) Figure 2 As shown, due to h 11 h 12 As the size increases, the pressure P in the pressure oil groove 120 of the throttle 11 located on the upper end face of the prototype slider 1 also increases. Since the pressure oil groove 120 is connected to the working groove 12 located on the lower end face of the prototype slider 1, the pressure in the working groove 12 located on the lower end face of the prototype slider 1 also increases, which means that the oil film stiffness of the working groove 12 on the lower end face of the prototype slider 1 increases.

[0071] Based on the above working principle, by reasonably increasing the size of the throttling edge of the working groove on the lower end face and the size of the throttling edge of the throttling device on its opposite side (i.e., the upper end face), while simultaneously decreasing the size of the throttling edge of the pressure oil groove in the throttling device, the throttling capacity of the throttling chamber and the working groove can be optimized, thereby increasing the oil film stiffness of the prototype slider working groove. Therefore, when selecting the reference dimension parameter set and the variable dimension parameter set, the above relationship must be satisfied, that is, the variable dimension parameter set of the working groove throttling edge on the lower end face is greater than the reference dimension parameter set, the variable dimension parameter set of the throttling edge of the throttling device on the upper end face is greater than the reference dimension parameter set, and the variable dimension parameter set of the pressure oil groove throttling edge on the upper end face is less than the reference dimension parameter set.

[0072] The step S4 is acquiring the first interval difference and the second interval difference. In the step S4, the following steps are included, such as the step S41 is acquiring the first reference interval and the second reference interval of each prototype slider. It is understood that the first reference interval and the second reference interval are calculated according to the reference overturning component force value and the reference size parameter group. The step S42 is acquiring the first variable interval and the second variable interval of each prototype slider. It is understood that the first variable interval and the second variable interval are calculated according to the variable overturning component force value and the variable size parameter group. After the first reference interval and the second reference interval, the first variable interval and the second variable interval are acquired, the step S43 and the step S44 are performed.

[0073] The step S43 is acquiring the first interval difference based on the first reference interval and each first variable interval. It is understood that since the first variable interval is calculated, each first variable interval is operated with the first reference interval to obtain a corresponding first interval difference. Therefore, in the step S43, the first interval difference can be acquired. Similarly, the step S44 is acquiring the second interval difference based on the second reference interval and each second variable interval, that is, each second variable interval is operated with the second reference interval to obtain a corresponding second interval difference.

[0074] After the step S43 and the step S44 are processed, the first interval difference (i.e. Δh i1 ) and the second interval difference (i.e. Δh i2 ) are acquired. It is understood that i represents the number of prototype sliders, such as i is 1, which represents the value of the first slider. Each Δh i1 in the plurality of prototype sliders is compared, and the similar Δh i1 is selected from the Δh i1 of the plurality of prototype sliders, such as Δh 11 ≈ Δh 21 . Similarly, Δh i2 is also selected in this way.

[0075] After the first interval difference and the second interval difference are selected, the variable size parameter group for calculating the first interval difference and the second interval difference is found, that is, the variable size parameter group is the target size parameter group in the plurality of variable size parameter groups. Finally, the corresponding anti-overturning slider is designed based on the target size parameter group. Each anti-overturning slider can independently adjust the oil film stiffness according to the corresponding load, so as to realize the anti-overturning ability of the anti-overturning slider. It is necessary to supplement that the size parameters in the target size parameter group include the size of the throttle edge of the working groove, the size of the throttle edge of the throttle, and the size of the throttle edge of the pressure oil groove in the throttle.

[0076] The specific calculation formula is based on the following formulas (5), (6), (7), and in combination with Bernoulli's principle of mechanics.

[0077] (5)

[0078] (6)

[0079] (7)

[0080] F i is the overturning component force of the system i slider; ΔP is the pressure difference between the two ends of the throttling edge of the i slider; A i is the effective area of the oil chamber, A i ≈L i *B i , (see Figure 2 ); L i , b i are the size parameters of the throttling edge of the i slider; q i is the flow size through one oil sealing edge in the i slider; h i is the throttling gap of the i slider. The above formula is applicable to the size parameter calculation of the throttling device and the size parameter calculation of the working groove.

[0081] By analyzing the force of the sliding assembly and combining the above formula, the size parameters of the throttling device and the size parameters of the working groove in each prototype slider are calculated for the moving load body, that is, the target size parameter group. Based on the target size parameter group, the anti-overturning slider designed in the application has a throttling gap h i1 with a similar change amount Δh i1 self-adapting adjustment, and the throttling gap h i2 of the anti-overturning slider is self-adapting adjustment with a similar change amount Δh i2 , so that the entire sliding assembly can be in an anti-overturning state for the moving load body. It can also be understood that the sliding load body of the moving load body is in a horizontal state when loaded with a tool, achieving the purpose of anti-overturning of the sliding assembly.

[0082] In some embodiments of the present application, in combination with Figure 3 , the anti-overturning design method of the sliding assembly further includes step S6, and step S6 is that a plurality of anti-overturning sliders designed and manufactured based on the target size parameter group are arranged on the slide rail of the sliding assembly. The relative positional relationship of the anti-overturning sliders and the moving load body in the sliding direction is equivalent to the relative positional relationship of the prototype slider and the moving load body in the sliding direction. In this way, it is ensured that the anti-overturning sliders can play a role in anti-overturning in actual application.

[0083] In some embodiments of the present application, referring to Figure 1 , and Figure 4A top view of a precision machine equipped with the sliding assembly according to the design method of the present application is shown. The precision machine is equipped with two sets of sliding block groups, which are arranged side by side in the width direction of the precision machine, wherein each set of sliding block groups comprises two anti-overturning sliding blocks 10. It is worth noting that, referring to Figure 4 Figure 4 It is shown that, in the width direction of the precision machine, the first anti-overturning sliding block 10a in the first set of sliding block groups is arranged opposite to the first anti-overturning sliding block 10a in the second set of sliding block groups, and the second anti-overturning sliding block 10b in the first set of sliding block groups is arranged opposite to the second anti-overturning sliding block 10b in the second set of sliding block groups. It needs to be added that, for the precision machine equipped with the sliding assembly according to the design method of the present application, the number of sliding assemblies equipped in the precision machine can not be limited to one set, two sets, three sets, or even ten sets, etc., but it is necessary to ensure that the sliding blocks in each set are arranged correspondingly.

[0084] The technical features of the above embodiments can be combined in any manner. In order to make the description concise, not all possible combinations of the technical features in the above embodiments are described, however, as long as the combinations of the technical features do not exist contradictions, they should be considered as the scope of the present application.

[0085] The above embodiments only express several implementation manners of the present application, and the description is relatively specific and detailed, but it should not be understood as a limitation on the patent scope of the present application. It should be pointed out that, for ordinary skilled in the art, without departing from the concept of the present application, a number of modifications and improvements can be made, which are all within the protection scope of the present application. Therefore, the patent protection scope of the present application should be subject to the appended claims.

Claims

1. A method for anti-overturning design of a sliding component, characterized in that, The method comprises the following steps: S1, obtaining a reference overturning component value of each prototype slider, and obtaining a variable overturning component value of each prototype slider; S2, selecting quantitative data in the sliding assembly; S3, selecting a reference size parameter group and a plurality of variable size parameter groups based on each prototype slider; S4, obtaining a first interval difference value and a second interval difference value, wherein the step S4 comprises: S41, obtaining a first reference interval and a second reference interval of each prototype slider, the first reference interval and the second reference interval being calculated according to the reference overturning component value and the reference size parameter group, S42, obtaining a plurality of first variable intervals and a plurality of second variable intervals of each prototype slider, the first variable interval and the second variable interval being calculated according to the variable overturning component value and the variable size parameter group, S43, obtaining a plurality of first interval difference values based on the first reference interval and each first variable interval, each first variable interval being operated with the first reference interval to obtain a corresponding first interval difference value, S44, obtaining a plurality of second interval difference values based on the second reference interval and each second variable interval, each second variable interval being operated with the second reference interval to obtain a corresponding second interval difference value; S5, comparing the first interval difference value of each prototype slider, comparing the second interval difference value of each prototype slider, and selecting a target size parameter group from the plurality of variable size parameter groups obtained.

2. The anti-overturning design method of a sliding assembly according to claim 1, wherein, The step S1 comprises: S11, determining the position of the center of gravity of the mobile load carrier in the sliding direction of the mobile load carrier; S12, determining the center of gravity interval of each prototype slider and the mobile load carrier in the sliding direction; S13, selecting a reference gravity value and a plurality of variable gravity values of the mobile load carrier; S14, obtaining each reference overturning component value based on the reference gravity value, and obtaining each variable overturning component value based on the variable gravity value.

3. The anti-overturning design method of a sliding assembly according to claim 2, wherein, The step S13 satisfies the relationship: the variable gravity value is greater than the reference gravity value.

4. The method of designing a roll-over resistant slide assembly according to claim 1, wherein, In the step S2, the quantitative data comprises the upper working groove area, the lower working groove area, the oil sealing edge size of the prototype slider, the dynamic viscosity of the pressure oil in the sliding assembly, and the oil source pressure value.

5. The method of designing a roll-over resistant slide assembly according to claim 1, wherein, In the step S3, the size parameters of the prototype slider comprise the throttle edge of the working groove, the throttle edge of the throttle, and the throttle edge of the pressure oil groove in the throttle, and the size parameters are divided into the reference size parameter group and the variable size parameter group.

6. The anti-overturning design method of a sliding assembly according to claim 5, wherein, When selecting the size parameters based on the prototype slider, the following relationships are satisfied: the variable size parameter group of the throttle edge of the working groove with respect to the lower end surface is greater than the reference size parameter group, the variable size parameter group of the throttle edge of the throttle with respect to the upper end surface is greater than the reference size parameter group, and the variable size parameter group of the throttle edge of the pressure oil groove with respect to the upper end surface is less than the reference size parameter group.

7. The anti-overturning design method of a sliding assembly according to claim 5, wherein, The throttle edges of the working groove include a first throttle edge, a second throttle edge, a third throttle edge and a fourth throttle edge, and the throttle edges of the throttle device include a fifth throttle edge and a sixth throttle edge.

8. The method of designing a roll-over resistant slide assembly according to claim 1, wherein, In the step S5, a same first interval difference is selected for each of the plurality of prototype sliders from the plurality of first interval difference values, and the target size parameter group is selected from the plurality of variable size parameter groups based on the first interval difference.

9. The anti-overturning design method of a sliding assembly according to claim 1, wherein, Further comprising the following steps: S6, a plurality of anti-overturning sliders designed based on the target size parameter group are arranged on the slide rail of the sliding assembly, and a relative position relationship between the anti-overturning sliders and the moving load body in a sliding direction is equivalent to a relative position relationship between the prototype sliders and the moving load body in the sliding direction.

Images