Anti-overturning design method of sliding assembly

Abstract

The invention relates to an anti-overturning design method for a sliding assembly. The design method is based on a sliding block adopting a plane gap throttling feedback self-adaptive adjustment model, and comprises the following steps: acquiring a reference overturning component force value and a variable overturning component force value of the sliding block, and selecting quantitative data in a sliding assembly and a reference size parameter group and a variable size parameter group of the sliding block; a first spacing difference value and a second spacing difference value of the sliding block are obtained through calculation based on the steps, a target size parameter set is selected from the variable size parameter sets by comparing the first spacing difference value with the second spacing difference value, and the target size parameter set is the target size parameter set of the sliding block. And finally, designing and generating an anti-overturning sliding block based on the target size parameter group. Therefore, by means of the anti-overturning design method of the sliding assembly, the sliding assembly can have the anti-overturning capacity, and therefore for the precision machine tool provided with the sliding assembly designed according to the design method, the precision machine tool has higher precision.

Description

Technical Field

[0001] The present application relates to the technical field of precision machine tools, and in particular to an anti-overturning design method for a sliding component. Background Art

[0002] Precision machine tools are machine tools that can perform high-precision processing. Their processing accuracy is usually much higher than that of ordinary machine tools, and can reach micron or even nanometer levels of accuracy. The sliding components (such as guide rails, etc.) of precision machine tools provide precise guidance for moving parts, and high-quality sliding components help maintain the accuracy of machine tools.

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

[0004] However, the tool is set on one side of the sliding direction of the sliding carrier, which also causes the sliding component to be overloaded. Under normal circumstances, the friction between the sliding components is evenly distributed, but overload will cause excessive local pressure. When the precision machine tool is processing, the movement trajectory of the tool depends on the precise guidance of the sliding component. When the sliding component is overloaded, it will cause the moving parts to deviate from the normal movement path, and it will also affect the service life and precision of the sliding component. Summary of the invention

[0005] Based on this, it is necessary to provide an anti-overturning design method for the sliding assembly to address the problem of overload of the sliding assembly.

[0006] A method for anti-overturning design of a sliding assembly comprises the following steps:

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

[0008] S2, select the quantitative data in the sliding component;

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

[0010] S4, obtaining a first spacing difference and a second spacing difference;

[0011] S5, comparing the first spacing difference of each prototype slider and the second spacing difference of each prototype slider to select a target size parameter group from the obtained multiple variable size parameter groups.

[0012] In one embodiment, step S1 comprises:

[0013] S11, determining the position of the center of gravity of the mobile load body in the sliding direction of the mobile load body;

[0014] S12, determining the distance between the center of gravity of each prototype slider and the mobile load in the sliding direction;

[0015] S13, selecting a reference gravity value and a plurality of variable gravity values ​​of the mobile load body;

[0016] S14. Obtain each reference overturning component force value based on the reference gravity value, and obtain each variable overturning component force value based on the variable gravity value.

[0017] In one embodiment, step S13 satisfies the relationship: the variable gravity value is greater than the reference gravity value.

[0018] In one embodiment, in step S2, the quantitative data includes an upper working groove area, a lower working groove area, an oil sealing edge size, a dynamic viscosity of the pressure oil in the sliding assembly, and an oil source pressure value based on the prototype slider.

[0019] In one of the embodiments, in step S3, the dimensional parameters based on the prototype slider include the throttling edge of the working groove, the throttling edge of the throttling device and the throttling edge of the pressure oil groove in the throttling device, and the dimensional parameters are divided into a reference dimensional parameter group and a variable dimensional parameter group.

[0020] In one embodiment, the size parameters are selected based on the prototype to satisfy the relationship:

[0021] The variable size parameter set of the throttling edge of the working groove on its lower end surface is greater than the reference size parameter set.

[0022] The variable size parameter set of the throttling edge of the throttling device on its upper end surface is greater than the reference size parameter set,

[0023] And the variable size parameter group of the throttling edge of the pressure oil groove on its upper end surface is smaller than the reference size parameter group.

[0024] In one embodiment, the throttling edge of the working groove includes a first throttling edge, a second throttling edge, a third throttling edge, and a fourth throttling edge, and the throttling edge of the throttler includes a fifth throttling edge and a sixth throttling edge.

[0025] In one embodiment, step S4 comprises:

[0026] S41, obtaining a first reference spacing and a second reference spacing of each prototype slider;

[0027] S42, obtaining a plurality of first variable spacings and a plurality of second variable spacings of each prototype slider;

[0028] S43, acquiring a plurality of first interval differences based on the first reference interval and each first variable interval;

[0029] S44. Acquire a plurality of second interval differences based on the second reference interval and each second variable interval.

[0030] In one embodiment, in step S5, a first spacing difference value that is close to the same for each prototype slider is selected from a plurality of first spacing differences of a plurality of prototype sliders, and a target size parameter group is selected from a plurality of variable size parameter groups based on the first spacing difference value.

[0031] In one embodiment, the anti-overturning design method further comprises the following steps:

[0032] S6. Multiple anti-overturning sliders designed and manufactured based on the target size parameter group are arranged on the slide rails of the sliding assembly, and the relative position relationship between the anti-overturning slider and the mobile load in its sliding direction is equivalent to the relative position relationship between the slider and the mobile load in the sliding direction.

[0033] The anti-overturning design method of the sliding assembly is based on a slider adopting a plane gap throttling feedback adaptive adjustment model, by obtaining the reference overturning component force value and variable overturning component force value of the slider, and selecting the quantitative data in the sliding assembly and the reference size parameter group and variable size parameter group of the slider. Based on the above steps, the first spacing difference and the second spacing difference of the slider are calculated and obtained, and the target size parameter group is selected from multiple variable size parameter groups by comparing the first spacing difference and the second spacing difference. The anti-overturning slider designed and manufactured based on the target size parameter group has the ability to resist overturning. Therefore, the anti-overturning design method of the sliding assembly can make the sliding assembly have the ability to resist overturning, so that for the precision machine tool equipped with the sliding assembly according to the design method of the present application, the precision machine tool has higher precision. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] FIG. 1 is a flow chart of an anti-overturning design method for a sliding assembly according to an embodiment of the present application.

[0035] FIG. 2 is a schematic diagram of force analysis of a slider in a sliding assembly according to an embodiment of the present application.

[0036] FIG. 3 is a schematic structural diagram of a slider according to an embodiment of the present application.

[0037] FIG. 4 is a top view of a precision machine tool equipped with a sliding assembly according to an embodiment of the present application (partial structure is not shown).

[0038] Reference numerals:

[0039] 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 tank; 120. Pressure oil tank; 12. Working tank; 2. Moving load body; 21. Sliding carrier; 22. Tool; b i3 , the first flow edge; b i4 , the second flow edge; l i2 , the third section flow edge; l i3 , Section 4 Flow Edge; l i1 , the fifth section flow edge; b i1 , Section 6 Flow Edge; b i2 , the seventh flow edge; 100, the upper boundary; 200, the lower boundary. DETAILED DESCRIPTION

[0040] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific implementation methods of the present application are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth 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 violating the connotation of the present application, so the present application is not limited by the specific embodiments disclosed below.

[0041] In the description of the present application, it should be understood that if the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. appear, the orientation or position relationship indicated by these terms is based on the orientation or position relationship shown in the accompanying drawings, which is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present application.

[0042] In addition, if the terms "first" or "second" appear, these terms are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the description of this application, if the term "plurality" appears, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0043] In this application, unless otherwise clearly specified and limited, if the terms "installed", "connected", "connected", "fixed" and the like appear, these terms should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integrated connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0044] In the present application, unless otherwise clearly specified and limited, if there is a description that a first feature is "above" or "below" a second feature, etc., or similar descriptions appear, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium. Moreover, the first feature being "above", "above" and "above" the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. The first feature being "below", "below" and "below" the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0045] It should be noted that if an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. If an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. If any, the terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used in this application are for illustrative purposes only and do not represent the only implementation method.

[0046] Referring to FIGS. 1 to 3 , 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 the plane gap throttling feedback adaptive adjustment model, the pressure bearing mode of the prototype slider is closed liquid static pressure bearing, and the prototype slider can independently and adaptively adjust the oil film stiffness of the pressure bearing surface according to the corresponding prototype slider load, thereby realizing the anti-overturning ability of the sliding assembly. It should be understood that:

[0047] 1. Plane gap throttling feedback adaptive adjustment model: a liquid static pressure throttling method, through the gap throttling function between the planes, hinders the liquid from flowing out of the oil chamber, forms a bearing oil film, so that the liquid in the oil chamber maintains a certain pressure and realizes the supporting function. In the slider whose structure is based on the plane gap throttling feedback adaptive adjustment model, there are connected oil chambers in the thickness direction of the slider, so that the pressure change of the oil chamber on one side will be transmitted to the connected oil chamber to adjust the oil chamber pressure to balance the load and achieve the self-feedback adjustment effect. For example, referring to FIG2, the prototype slider 1 and the upper boundary 100 and the lower boundary 200 are formed with gaps, and oil pressure oil flows in these gaps. 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 (it 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 (it can also be understood as the lower throttling gap of the prototype slider 1).

[0048] 2. Closed liquid static pressure bearing: Except for the moving direction of the slider, oil chambers are set in other directions to form a geometric closure to constrain the degree of freedom in the non-moving direction and ensure the smooth operation of the moving parts.

[0049] 3. Oil film stiffness: When the oil film in the plane gap is under load, when the load changes, the oil film's ability to resist the load change. That is, the rate of change of the oil film thickness relative to the load change.

[0050] 1 , the anti-overturning design method of the sliding assembly according to some embodiments of the present application includes the following steps S1 , S2 , S3 , S4 , and S5 .

[0051] Wherein step S1 is to obtain the reference overturning force component value of each prototype slider, and obtain the variable overturning force component value of each prototype slider. In step S1, the following multiple steps are also included, such as step S11 is to determine the position of the center of gravity of the mobile load body in the sliding direction of the mobile load body, step S12 is to determine the distance between the center of gravity of each prototype slider and the mobile load body in the sliding direction, step S13 is to select the reference gravity value of the mobile load body and multiple variable gravity values, step S13 is to obtain each reference overturning force component value based on the reference gravity value, and obtain each variable overturning force component value based on the variable gravity value, step S13 is to obtain each reference overturning force component value based on the reference gravity value, and obtain each variable overturning force component value based on the variable gravity value.

[0052] It should be supplemented that, in combination with FIG. 2 and FIG. 4 , the mobile load body 2 may include a sliding carrier 21 in a sliding assembly and a tool 22 of a precision machine tool, wherein in the moving direction of the sliding carrier 21, the relationship between the sliding carrier 21 and the plurality of prototype sliders 1 is in a non-biased load state, which can also be understood as, when the tool 22 is not loaded on the sliding carrier 21, the sliding assembly is in an ideal non-biased load state, and after the tool 22 is assembled on the sliding carrier 21, the sliding assembly is in a non-ideal biased load state. It can be seen that the relative position of the tool 22 and the prototype slider carrier 21 will affect the center of gravity position of the mobile load body 2 in its sliding direction. In the embodiment of the present application, the center of gravity position of the mobile load body 2 is fixed, which can also be understood as the center of gravity of the mobile load body 2 is a fixed parameter and will not change.

[0053] However, when the set tool mass changes, the gravity value of the mobile load body (i.e., the reference gravity value and the variable gravity value) will change. In the present application, the reference gravity value and the variable gravity value of the mobile load body are selected, and the reference gravity value and the different variable gravity values ​​can be used for reference comparison. It is worth noting that in step S13, the 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 100N (Newton), the variable gravity value can be selected as 101N, 110N, 120N, 130N, etc., which are greater than 100N.

[0054] As shown in FIG. 2 and FIG. 4 , along the sliding direction of the mobile load 2 (i.e., the X direction shown in FIG. 2 ), a plurality of prototype sliders 1 are arranged in sequence, and since each prototype slider 1 is in a fixed connection relationship with the sliding carrier 21 of the mobile load, the relative position relationship between each prototype slider 1 and the mobile load 2 in the sliding direction is fixed, and it can be known from the above content that the center of gravity of the mobile load 2 is a fixed parameter, so that step S12 can be completed by calculation, that is, the center of gravity distance between each prototype slider 1 and the mobile load 2 in the sliding direction can be determined. Exemplarily, referring to FIG. 2 , in some embodiments of the present application, two prototype sliders 1 are provided in the sliding assembly as an example, wherein one prototype slider 1 is a first slider 1a, and the other prototype slider 1 is a second slider 1b. As can be seen from FIG. 2 , the center of gravity distance D1 between the first slider 1a and the mobile load 2 in the sliding direction, and the center of gravity distance D2 between the second slider 1b and the mobile load 2 in the sliding direction. After selecting a reference gravity value and multiple variable gravity values, a calculation is performed to obtain the overturning force component value corresponding to each prototype slider. Each overturning force component value is a value required for subsequent calculations.

[0055] Wherein step S2 is to select quantitative data in the sliding component, and the quantitative data in the sliding component includes the upper working groove area, the lower working groove area, the oil sealing edge size based on the prototype slider, the dynamic viscosity of the pressure oil in the sliding component, and the oil source pressure value.

[0056] For example, referring to FIG. 2 and FIG. 3 , in the prototype slider 1 of the present application, along the thickness direction of the prototype slider 1, 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, 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, in combination with FIG. 2 and FIG. 3 , the pressure oil groove 120 arranged in the throttle 11 on the upper end face is in a state of communication with the working groove 12 on the lower end face, and the pressure oil groove 120 arranged in the throttle 11 on the lower end face is in a state of communication with the working groove 12 on the upper end face. In this way, the oil pump can deliver the pressure oil to the oil delivery groove 110 of the throttle 11 on the upper end face, and then the pressure oil in the oil delivery groove 110 flows into the pressure oil groove 120 in the oil delivery groove 110, and flows through the pressure oil groove 120 along the pipeline arranged inside the prototype slider 1 to the working groove 12 arranged on the lower end face. At the same time, the oil pump can also deliver the pressure oil to the oil delivery groove 110 of the lower end throttle 11, and then the pressure oil in the oil delivery groove 110 flows into the pressure oil groove 120 in the oil delivery groove 110, and flows through the pressure oil groove 120 along the pipeline arranged inside the prototype slider 1 to the working groove 12 arranged on the upper end surface. For example, referring to FIG3, the area of ​​the working groove 12 shown in FIG3 is approximately the product of the length of the working groove 12 and its width. The pressure value output by the oil pump for driving the pressure oil is the oil source pressure value, the dynamic viscosity of the pressure oil is related to its own characteristics, and the oil sealing edge size of the prototype slider 1 is the side length of the prototype slider 1.

[0057] Wherein step S3 is to select a reference dimension parameter group and multiple variable dimension parameter groups based on each prototype slider, the reference dimension parameter group and the variable dimension parameter group are both dimension parameters of the prototype slider, the difference is that the reference dimension parameter group and the variable dimension parameter group are the relative relationship between the reference group and the control group, wherein the reference dimension parameter group is equivalent to the reference group, and the variable dimension parameter group is equivalent to the control group, that is, the variable dimension parameter group is the variable reference of the reference dimension parameter group. The dimension parameters of the prototype slider include the throttling edge of the working groove, the throttling edge of the throttling device, and the throttling edge of the pressure oil groove in the throttling device. It can also be understood that both the reference dimension parameter group and the variable dimension parameter group have data on the throttling edge of the working groove, and the difference is that there are differences in the specific parameter values ​​in the two sets of data.

[0058] And the following relationship must be satisfied when selecting the size parameters based on the prototype slider: 1. The variable size parameter group of the throttling edge of the working groove on its lower end face is greater than the reference size parameter group. 2. The variable size parameter group of the throttling edge of the throttling device on its upper end face is greater than the reference size parameter group. 3. The variable size parameter group of the throttling edge of the pressure oil groove on its upper end face is less than the reference size parameter group.

[0059] Referring to FIG. 3 , in some embodiments of the present application, the throttling edge of the working slot 12 includes a first throttling edge b i3 , the second throttling edge b i4 、The third section flow edge l i2 、The fourth section flow edge l i3 The throttling edge of the throttling device 11 includes the fifth throttling edge l i1 and the sixth flow edge b i1 The throttling edge of the pressure oil groove 110 is the seventh throttling edge b i2 .

[0060] Exemplarily, as shown in FIG. 2 , when the gravity value G of the mobile load increases, the mobile load moves downward as a whole, that is, h11 and h12 in FIG. 2 tend to increase.

[0061] According to the following formulas (1), (2), (3), (4)

[0062] (1)

[0063] Then take the derivative of q and Pi respectively, where for the working slot, , then:

[0064] (2)

[0065] (3)

[0066] For the throttle, , is a constant, then:

[0067] (4)

[0068] It should be noted that:

[0069] q: flow rate of pressure oil flowing into the working groove; ΔP: pressure difference between the pressure oil groove and the upper and lower ends of the working groove; P: pressure in the pressure oil groove; L: length of the working groove; bi: width of the working groove; h: gap height between the upper end face of the prototype slider and the end face of the guide rail; u: dynamic viscosity of the pressure oil.

[0070] From the above formulas (2) and (3), it can be seen that for the working groove set on the lower end surface of the prototype slider, the change rate of h relative to q and P is negatively correlated, that is, the greater the flow rate and pressure, the smaller the change rate of the oil film thickness, that is, the greater the oil film stiffness. In addition, when the gravity value G becomes larger, the moving load body shifts downward as a whole, resulting in h in Figure 2 11 、h 12The throttling capacity of the working surface arranged on the upper end face of the prototype slider decreases, thereby increasing the flow rate of the throttle arranged in the upper end face of the prototype slider flowing into the working groove in the lower end face of the prototype slider through the internal oil channel, thereby enhancing the oil film stiffness of the lower end face of the prototype slider.

[0071] And from formula (4), it can be seen that for the throttle set on the upper end surface of the prototype slider, the change rate of h relative to P is positively correlated, that is, the larger h is, the larger P is. As shown in Figure 2, due to h 11 、h 12 It becomes larger, resulting in that the pressure P of the pressure oil groove 120 in the throttle 11 arranged 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 arranged on the lower end face of the prototype slider 1, the pressure of the working groove 12 arranged on the lower end face of the prototype slider 1 also increases, that is, the oil film stiffness of the working groove 12 on the lower end face of the prototype slider 1 increases.

[0072] Through the above working principle, the size of the throttling edge of the working groove set in the lower end face and the size of the throttling edge of the throttling device set on the opposite side (i.e., the upper end face) are reasonably increased, and the size of the throttling edge of the pressure oil groove in the throttling device needs to be reduced at the same time, so that the throttling capacity of the throttling cavity and the working groove can be optimized, thereby achieving the purpose of increasing the oil film stiffness of the working groove of the prototype slider. Therefore, when selecting the reference size parameter group and the variable size parameter group, the above relationship must be satisfied, that is, the variable size parameter group of the throttling edge of the working groove on its lower end face is greater than the reference size parameter group, the variable size parameter group of the throttling edge of the throttling device on its upper end face is greater than the reference size parameter group, and the variable size parameter group of the throttling edge of the pressure oil groove on its upper end face is less than the reference size parameter group.

[0073] Wherein step S4 is to obtain the first spacing difference and the second spacing difference. Step S4 also includes the following multiple steps, such as step S41 is to obtain the first reference spacing and the second reference spacing of each prototype slider. It should be understood that the first reference spacing and the second reference spacing are calculated and obtained according to the reference overturning component value and the reference size parameter group. Step S42 is to obtain multiple first variable spacings and multiple second variable spacings of each prototype slider. It should be understood that the first variable spacing and the second variable spacing are calculated and obtained according to the variable overturning component value and the variable size parameter group. After obtaining the first reference spacing and the second reference spacing, the first variable spacing and the second variable spacing, step S43 and step S44 are performed.

[0074] Among them, step S43 is to obtain multiple first spacing differences based on the first reference spacing and each first variable spacing. It should be understood that since multiple first variable spacings are calculated, each first variable spacing is calculated once with the first reference spacing to obtain a corresponding first spacing difference. Therefore, multiple first spacing differences can be obtained in step S43. Similarly, step S44 is to obtain multiple second spacing differences based on the second reference spacing and each second variable spacing, that is, each second variable spacing is calculated once with the second reference spacing to obtain a corresponding first spacing difference.

[0075] After step S43 and step S44 are completed, multiple first spacing differences (i.e., ∆h i1 ) and multiple second spacing differences (i.e. ∆h i2 ). It should be understood that i represents the number of prototype sliders. If i is 1, it means that the value is the value of the first slider. i1 Compare the ∆h of multiple prototype sliders. i1 Filter out similar ∆h i1 , for example, select ∆h from the two prototype sliders 11 ≈∆h 21 Similarly, ∆h i2 Also selected in this way.

[0076] After selecting the first spacing difference and the second spacing difference, find out the variable size parameter group for calculating the first spacing difference and the second spacing difference, that is, the variable size parameter group is the target size parameter group among the multiple 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 and adaptively adjust the oil film stiffness according to the corresponding load to achieve the anti-overturning slider's anti-overturning ability. It should be added that the size parameters in the target size parameter group include the size of the throttling edge of the working groove, the size of the throttling edge of the throttling device, and the size of the throttling edge of the pressure oil groove in the throttling device.

[0077] The specific calculation formula is based on the following formulas (5), (6), (7), and combined with the Bernoulli mechanics principle.

[0078] (5)

[0079] (6)

[0080] (7)

[0081] F i is the overturning force of the system i slider; ∆P 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 , (as shown in Figure 3); L i 、b i is the throttling edge size parameter of the i slider; q i is the flow rate through an oil sealing edge in the slider i; h i is the throttling gap of the slider. The above formula is applicable to the calculation of the size parameters of the throttling device and the working groove.

[0082] For the force analysis of the sliding component, the above formulas are combined to calculate the size parameters of the throttle and the working groove in each prototype slider for the moving load body, that is, the target size parameter group. In the application of the anti-overturning slider designed based on the target size parameter group, the throttling gap h of the anti-overturning slider is i1 With similar change ∆h i1 Adaptive adjustment and throttling gap h of the anti-overturning slider i2 With similar change ∆h i2 Adaptive adjustment allows the entire sliding assembly to be in an anti-overturning state for the mobile load body. It can also be understood as ensuring that the sliding carrier of the mobile load body is in a horizontal state when loaded with a tool, thereby achieving the purpose of anti-overturning of the sliding assembly.

[0083] In some embodiments of the present application, in combination with FIG. 1 , the anti-overturning design method of the sliding assembly further includes step S6, in which 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, and the relative position relationship between the anti-overturning slider and the mobile load in the sliding direction is equal to the relative position relationship between the prototype slider and the mobile load in the sliding direction. This ensures that the anti-overturning slider can play an anti-overturning role in practical applications.

[0084] In some embodiments of the present application, refer to FIG. 4, which shows a top view of a sliding assembly using the design method of the present application applied to a precision machine tool. The precision machine tool is equipped with two groups of slider groups, which are arranged side by side in the width direction of the precision machine tool, wherein each group of slider groups includes two anti-overturning sliders 10. It is worth noting that, as shown in FIG. 4, in the width direction of the precision machine tool, the first anti-overturning slider 10a in the first group of slider groups is arranged opposite to the first anti-overturning slider 10a in the second group of slider groups, and the second anti-overturning slider 10b in the first group of slider groups is arranged opposite to the second anti-overturning slider 10b in the second group of slider groups. It should be supplemented that, for a precision machine tool equipped with a sliding assembly according to the design method of the present application, the sliding assembly equipped in the precision machine tool may not be limited to one group, two groups, three groups, or even ten groups, but it is necessary to ensure that the sliders in each group are arranged correspondingly.

[0085] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0086] The above embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the patent application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent application shall be subject to the attached claims.

Claims

1. A method for anti-overturning design of a sliding assembly, characterized in that: The following steps are involved: S1, obtaining a reference overturning force component value of each prototype slider, and obtaining a variable overturning force component value of each prototype slider; S2, selecting quantitative data in the sliding component; S3, selecting a reference size parameter group and a plurality of variable size parameter groups based on each of the prototype sliders; S4, obtaining a first spacing difference and a second spacing difference; S5. Compare the first spacing difference of each of the prototype sliders and compare the second spacing difference of each of the prototype sliders to select a target size parameter group from the multiple variable size parameter groups obtained.

2. The anti-overturning design method of a sliding assembly according to claim 1, characterized in that: The step S1 comprises: S11, determining the position of the center of gravity of the mobile load in the sliding direction of the mobile load; S12, determining the distance between the center of gravity of each prototype slider and the mobile load body in the sliding direction; S13, selecting a reference gravity value and a plurality of variable gravity values ​​of the mobile load body; S14. Obtain each of the reference overturning component force values ​​based on the reference gravity value, and obtain each of the variable overturning component force values ​​based on the variable gravity value.

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

4. The anti-overturning design method of a sliding assembly according to claim 1, characterized in that: In the 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.

5. The anti-overturning design method of a sliding assembly according to claim 1, characterized in that: In the step S3, based on the dimensional parameters of the prototype slider including the throttling edge of the working groove, the throttling edge of the throttling device and the throttling edge of the pressure oil groove in the throttling device, the dimensional parameters are divided into the reference dimensional parameter group and the variable dimensional parameter group.

6. The anti-overturning design method of a sliding assembly according to claim 5, characterized in that: Based on the prototype slider, the relationship is satisfied when selecting the size parameters: The variable dimension parameter set of the throttling edge of the working groove with respect to its lower end surface is greater than the reference dimension parameter set, The variable size parameter set of the throttling edge of the throttling device with respect to its upper end surface is greater than the reference size parameter set, And the variable size parameter group of the throttling edge of the pressure oil groove with respect to its upper end surface is smaller than the reference size parameter group.

7. The anti-overturning design method of a sliding assembly according to claim 5, characterized in that: The throttling edges of the working groove include a first throttling edge, a second throttling edge, a third throttling edge, and a fourth throttling edge, and the throttling edges of the throttler include a fifth throttling edge and a sixth throttling edge.

8. The anti-overturning design method of a sliding assembly according to claim 1, characterized in that: The step S4 comprises: S41, obtaining a first reference spacing and a second reference spacing of each of the prototype sliders; S42, obtaining a plurality of first variable spacings and a plurality of second variable spacings of each of the prototype sliders; S43, acquiring a plurality of first interval differences based on the first reference interval and each of the first variable intervals; S44. Acquire a plurality of second interval differences based on the second reference interval and each of the second variable intervals.

9. The anti-overturning design method of a sliding assembly according to claim 1, characterized in that: In the step S5, the first spacing difference value that each of the prototype sliders approaches is selected from the multiple first spacing differences of the multiple prototype sliders, and the target size parameter group is selected from the multiple variable size parameter groups based on the first spacing difference value.

10. The anti-overturning design method of a sliding assembly according to claim 1, characterized in that: The following steps are also included: S6. Multiple anti-overturning sliders designed and manufactured based on the target size parameter group are arranged on the slide rails of the sliding assembly, and the relative position relationship between the anti-overturning slider and the mobile load body in its sliding direction is equivalent to the relative position relationship between the prototype slider and the mobile load body in the sliding direction.

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