Hydrostatic guideway performance testing device and testing method

Abstract

The application discloses a hydrostatic guide working performance testing device and a testing method. The hydrostatic guide working performance testing device comprises a workbench, a pressing plate, an oil supply mechanism and a testing module. The pressing plate is fixedly arranged on the workbench and surrounds the first surface of the workbench to form a testing space, a hydrostatic slide to be tested is arranged in the testing space, and a first hydrostatic cavity is arranged opposite to the pressing plate and a second hydrostatic cavity is arranged opposite to the first surface. The oil supply mechanism comprises an oil tank, a throttling element and a pressure regulating element. The testing module is used for calculating the working performance of the hydrostatic slide. The hydrostatic guide working performance testing method is used for executing the hydrostatic guide working performance testing device. The application solves the problems that the weight loading mode in the testing method of the prior art has low loading efficiency, the load change is discontinuous, and factors such as the weight placement position, the dial gauge dialing position, the testing device assembly effect and the throttling consistency make the hydrostatic guide working performance testing result inaccurate.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of hydrostatic guideway testing, in particular to a hydrostatic guideway working performance testing device and testing method. BACKGROUND

[0002] A hydrostatic guideway is a high-precision linear guideway that provides support force through liquid with certain pressure. It has been widely applied in industrial automation, semiconductor production, precision machining and other fields due to its high precision, high rigidity, low friction, low wear and other advantages. The working performance of a hydrostatic guideway is usually evaluated by testing performance indicators such as guideway load capacity, support gap and oil film stiffness.

[0003] At present, the performance of a hydrostatic guideway is mostly tested after the completion of the assembly of the whole machine by loading weights and then measuring the change in the support gap with a micrometer. This testing method has the following disadvantages: first, the loading method of changing the weight amount to control the external load size needs manual loading and unloading, which is low in efficiency, and the load change is discontinuous, and the load center is affected by the weight placement position, which can result in inaccurate test results; second, the measurement with a micrometer only measures the support gap at a certain point rather than the overall average support gap, that is, the measurement position can affect the measurement results; third, the test is performed after the assembly of the whole machine, and the accuracy of the test results is affected by factors such as the assembly effect and the consistency of the restrictor. SUMMARY

[0004] The main purpose of the present application is to provide a hydrostatic guideway working performance testing device and testing method to at least solve the problems of low loading efficiency, discontinuous load change and inaccurate test results of the hydrostatic guideway working performance caused by factors such as the weight placement position, the micrometer measurement position, the assembly effect of the testing device and the consistency of the restrictor in the prior art testing method.

[0005] According to one aspect of the present application, a hydrostatic guideway working performance testing device is provided, the hydrostatic guideway comprising a hydrostatic slide block, the hydrostatic slide block comprising a first hydrostatic cavity and a second hydrostatic cavity, the first hydrostatic cavity being arranged on a first side of the hydrostatic slide block, the second hydrostatic cavity being arranged on a second side of the hydrostatic slide block opposite to the first side, and the hydrostatic guideway working performance testing device comprising:

[0006] a workbench;

[0007] a pressing plate, the pressing plate being fixedly arranged on the workbench and surrounding the first surface of the workbench to form a testing space, the hydrostatic slide block to be tested being installed in the testing space, and the first hydrostatic cavity being arranged opposite to the pressing plate and the second hydrostatic cavity being arranged opposite to the first surface;

[0008] The oil supply mechanism comprises an oil tank, a throttling element and a pressure regulating element, the throttling element is connected between the oil tank and the second static pressure cavity, and the pressure regulating element is connected between the oil tank and the first static pressure cavity to regulate the load of the static pressure slide block.

[0009] The test module calculates the working performance of the static pressure slide block according to the current oil pressure of the first static pressure cavity, the current oil flow in the second static pressure cavity and the current oil pressure in the second static pressure cavity.

[0010] Further, the workbench comprises a support arranged on the first surface of the workbench, and the pressing plate is fixedly arranged on the support and forms a test space with the first surface.

[0011] Further, the static pressure guide rail working performance test device further comprises a thrust rod arranged on the workbench for applying a thrust to the static pressure slide block, the direction of the thrust being consistent with the sliding direction of the static pressure slide block.

[0012] Further, the workbench comprises at least two spaced supports, and the two ends of the pressing plate are fixedly arranged on the two supports, respectively. The support is provided with an avoiding opening along the sliding direction of the static pressure slide block, and the thrust rod applies a thrust to the static pressure slide block through the avoiding opening.

[0013] Further, the static pressure guide rail working performance test device further comprises:

[0014] The first channel is in communication with the oil tank and the first static pressure cavity at two ends, respectively;

[0015] The second channel is in communication with the oil tank and the second static pressure cavity at two ends, respectively;

[0016] The pressure detection element is two, one of the two pressure detection elements is arranged on the first channel and located between the first static pressure cavity and the pressure regulating element, and the other of the two pressure detection elements is arranged on the second channel and located between the second static pressure cavity and the throttling element;

[0017] The flow detection element is arranged on the second channel and located between the second static pressure cavity and the throttling element;

[0018] The test module is electrically connected with the pressure detection element and the flow detection element to calculate the working performance of the static pressure slide block.

[0019] Further, the throttling element comprises a throttling device; and / or, the pressure regulating element comprises a pressure regulating valve.

[0020] On the other hand, the application further provides a static pressure guide rail working performance test method for the static pressure guide rail working performance test device, and the static pressure guide rail working performance test method comprises:

[0021] The detection step: real-time detection of the pressure P1 of the current oil in the first static pressure cavity, the pressure P2 of the current oil in the second static pressure cavity, and the flow Q2 of the current oil in the second static pressure cavity, followed by the calculation step;

[0022] The calculation step: calculating the current load F of the static pressure slider according to the pressure P1 of the current oil in the first static pressure cavity and the effective load area S1 of the first static pressure cavity; calculating the supporting gap h of the second static pressure cavity according to the pressure P2 of the current oil in the second static pressure cavity, the flow Q2 of the current oil, the viscosity μ of the oil, and the oil cavity flow coefficient K of the static pressure slider ; calculating the stiffness j of the current oil film in the second static pressure cavity according to the current load F and the supporting gap h u , and then executing the judgment step;

[0023] The judgment step: judging whether the supporting gap h is greater than 0: if the supporting gap h is greater than 0, gradually adjusting the pressure regulating element to increase the pressure P1 of the current oil in the first static pressure cavity, and executing the detection step again until the supporting gap h is just 0, at which time the current load F is the maximum load F of the static pressure slider max , and stopping the test; if the supporting gap h is equal to 0, gradually adjusting the pressure regulating element to reduce the pressure P1 of the current oil in the first static pressure cavity, and executing the detection step again until the supporting gap h is just not 0, and the current load F calculated in the last calculation step is the maximum load F of the static pressure slider max , and stopping the test.

[0024] Further, the current load F of the static pressure slider is calculated by the following formula:

[0025] F=S1×P1

[0026] Wherein, S1 represents the effective load area of the first static pressure cavity;

[0027] P1 represents the pressure of the current oil in the first static pressure cavity.

[0028] Further, the supporting gap h of the second static pressure cavity is calculated by the following formula:

[0029]

[0030] Wherein, μ represents the viscosity of the oil;

[0031] K represents the oil cavity flow coefficient of the static pressure slider;

[0032] Q2 represents the flow of the current oil in the second static pressure cavity;

[0033] P2 represents the pressure of the current oil in the second static pressure cavity.

[0034] Further, the rigidity j of the current oil film in the second hydrostatic cavity u The rigidity j of the current oil film in the second hydrostatic cavity is calculated by the following formula:

[0035]

[0036] Wherein, represents the partial differential of the current load F of the hydrostatic slide;

[0037] represents the partial differential of the support gap h of the second hydrostatic cavity.

[0038] Compared with the prior art, the hydrostatic guide rail performance testing device in the application uses the load provided by the oil to replace the way of controlling the external load size by using the weight, so that stepless adjustment of the load can be realized. At the same time, the test module can directly calculate the working performance indicators such as the support gap, and the whole test process does not need to use the dial gauge to mark points. Further, in the application, only the hydrostatic guide rail needs to be installed in the test space when testing the performance of the hydrostatic guide rail, and no test element needs to be installed on the hydrostatic guide rail. This means that the test results are not easily affected by factors such as assembly effect and consistency of the throttling device, which affect the accuracy of the test results. BRIEF DESCRIPTION OF DRAWINGS

[0039] The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiments of the application and serve to explain the principles of the application, and do not limit the application. In the drawings:

[0040] Figure 1 It is a structural schematic diagram of the hydrostatic guide rail performance testing device disclosed in the application;

[0041] Figure 2 It is a front view of the hydrostatic guide rail performance testing device disclosed in the application;

[0042] Figure 3 It is a working principle diagram of the hydrostatic guide rail performance testing device disclosed in the application;

[0043] Figure 4 It is a structural schematic diagram of the hydrostatic slide in the first perspective view disclosed in the application;

[0044] Figure 5 It is a structural schematic diagram of the hydrostatic slide in the second perspective view disclosed in the application;

[0045] Figure 6 It is a flowchart of the hydrostatic guide rail performance testing method disclosed in the application.

[0046] Among the above drawings, the following reference signs are included:

[0047] 10, workbench; 20, pressing plate; 40, first channel; 50, second channel; 60, pressure detecting element; 70, flow detecting element; 80, static pressure slider; 90, slide rail; 11, support; 21, test space; 31, oil tank; 32, throttling element; 33, pressure regulating element; 34, oil filtering element; 35, oil pump; 36, driving element; 37, overflow valve; 81, first static pressure cavity; 82, second static pressure cavity; 83, connecting hole; 111, avoiding opening. DETAILED DESCRIPTION

[0048] It should be noted that the embodiments and features of the embodiments in the present application can be combined with each other without conflict. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0049] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should be understood that, when the term "comprising" and / or "including" is used in the specification, it means that the features, steps, operations, devices, components and / or combinations thereof are present.

[0050] The relative arrangement of the components and steps, numerical expressions and values set forth in these embodiments do not limit the scope of the present application, unless otherwise specifically stated. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in proportion to the actual proportions. Techniques, methods and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as part of the authorized specification, if appropriate. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference numbers and letters represent similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0051] Reference is made to Figures 1 to 5 As shown, according to the embodiments of the present application, a static pressure guide rail performance testing device is provided for testing the performance of a static pressure guide rail.

[0052] In the drawings: Figure 4 As shown in Figure 5As shown, the static pressure guide rail in the present application comprises a static pressure slider 80, which comprises a first static pressure cavity 81 and a second static pressure cavity 82, the first static pressure cavity 81 is arranged on the first side of the static pressure slider 80, and the second static pressure cavity 82 is arranged on the second side of the static pressure slider 80 opposite to the first side.

[0053] As shown in the accompanying drawings, Figure 1 to the accompanying drawings, Figure 2 As shown, the static pressure guide rail performance testing device in the present application comprises a workbench 10, a pressing plate 20, an oil supply mechanism and a testing module. The pressing plate 20 is fixedly arranged on the workbench 10 and surrounds the first surface of the workbench 10 to form a test space 21, the static pressure slider 80 to be tested is installed in the test space 21, and the first static pressure cavity 81 is arranged opposite to the pressing plate 20, and the second static pressure cavity 82 is arranged opposite to the first surface. The oil supply mechanism comprises an oil tank 31, a throttling element 32 and a pressure regulating element 33, the throttling element 32 is connected between the oil tank 31 and the second static pressure cavity 82, and the pressure regulating element 33 is connected between the oil tank 31 and the first static pressure cavity 81 to adjust the load of the static pressure slider 80. The testing module is used for calculating the working performance of the static pressure slider 80 according to the current oil pressure in the first static pressure cavity 81, the current oil flow and pressure in the second static pressure cavity 82.

[0054] In the present embodiment, as shown in the accompanying drawings, Figure 3 The oil supply mechanism further comprises a filter element 34, an oil pump 35 and an overflow valve 37, the filter element 34 is connected with the oil tank 31 to filter the oil. The oil pump 35 is connected with the oil tank 31, and the oil pump 35 is further provided with a driving element 36, which can pump the oil in the oil tank 31 into the static pressure slider 80. The overflow valve 37 is arranged between the oil pump 35 and the static pressure slider 80 to prevent the oil pumped by the oil pump 35 from having too high pressure.

[0055] When it is necessary to test the working performance of the static pressure guide rail, the static pressure slider 80 is installed in the test space 21, and the oil pump 35 works to pump the oil in the oil tank 31 into the first static pressure cavity 81 and the second static pressure cavity 82 of the static pressure slider 80, so that there is an oil film in the first static pressure cavity 81 and the second static pressure cavity 82. At the same time, the pressing plate 20 can support the oil film to prevent the oil from being depressurized on the first static pressure cavity 81. By adjusting the pressure regulating element 33, the current oil pressure in the first static pressure cavity 81 is changed continuously, so that different loads are applied to the static pressure slider 80. By adjusting the throttling element 32, the oil flow in the second static pressure cavity 82 can be changed at any time to test more performance parameters, and then the testing module is used to calculate the working performance indexes of the static pressure slider 80.

[0056] Compared to existing technologies, the hydrostatic guide rail performance testing device in this embodiment utilizes the load provided by oil instead of weights to control the external load during hydrostatic guide rail performance testing, enabling stepless load adjustment. Simultaneously, the testing module can directly calculate performance indicators such as support clearance, eliminating the need for dial indicator marking during the entire testing process. Furthermore, in this embodiment, when testing the hydrostatic guide rail performance, only the hydrostatic guide rail needs to be installed in the testing space 21, without the need to install testing elements on the hydrostatic guide rail. This means that the accuracy of the test results is less affected by factors such as assembly quality and throttle consistency.

[0057] Further, in this embodiment, the workbench 10 includes a support member 11, which is disposed on a first surface of the workbench 10, and the pressure plate 20 is fixedly disposed on the support member 11, forming the aforementioned test space 21 between the pressure plate 20 and the first surface. Specifically, the support member 11 allows for a certain gap between the hydrostatic guide rail and the pressure plate 20, so that the support member 11, the pressure plate 20, and the workbench 10 form the aforementioned test space, and the hydrostatic guide rail can be installed in the test space. Optionally, the support member 11 can be a support block, and the support block is fixedly connected to the pressure plate 20 by bolts.

[0058] Furthermore, the hydrostatic guide rail performance testing device also includes a thrust rod (not shown in the figure). The thrust rod is mounted on the worktable 10 to apply a thrust to the hydrostatic slider 80, and the direction of the thrust is consistent with the sliding direction of the hydrostatic slider 80. The thrust rod is used to manually check whether the load applied to the hydrostatic slider 80 has exceeded the maximum load when the hydrostatic guide rail performance testing device is in operation. Specifically, as shown in the attached... Figure 3 As shown, the hydrostatic guide rail also includes a slide rail 90, and a hydrostatic slider 80 is disposed on the slide rail 90. The slider 80 slides on the slide rail 90 via an oil film on its second hydrostatic chamber 82. In this embodiment, a very small force is typically applied to the push rod. Since the coefficient of friction of the oil film is between 0.0005 and 0.001, and the frictional force on the hydrostatic slider 80 is equal to the product of the coefficient of friction of the oil film and the load force on the hydrostatic slider, the frictional force between the hydrostatic slider and the oil film is typically a very small value, usually between 1N and 100N. The thrust applied to the push rod is typically between 60N and 100N, causing the hydrostatic slider 80 to move in its sliding direction. However, when there is no oil film in the lower oil chamber of the hydrostatic slider 80, the frictional force on the hydrostatic slider 80 increases dramatically, and the force applied by the push rod cannot push the hydrostatic slider 80. In this case, it can be considered that the load applied to the hydrostatic slider 80 exceeds its maximum load value.

[0059] In some embodiments, the workbench 10 comprises at least two spaced-apart supports 11, and the two ends of the pressing plate 20 are fixedly arranged on the two supports 11, respectively. The supports 11 are provided with a clearance opening 111 along the sliding direction of the static pressure slider 80, and the thrust rod applies a thrust force to the static pressure slider 80 through the clearance opening 111. Specifically, in order to ensure that the force applied by the thrust rod to the static pressure slider 80 is parallel to the sliding direction of the static pressure slider 80, the clearance opening 111 is provided along the sliding direction of the static pressure slider 80. The thrust rod applies a thrust force inwardly through the clearance opening 111, and manual detection is completed. The support 11 and the pressing plate 20 are fixedly connected by a plurality of bolts, which to some extent ensures that the test space 21 will not be deformed by the test, thereby affecting the test effect of the static pressure guide rail.

[0060] Optionally, the static pressure slider 80 is provided with a connecting hole 83 on one side for connecting with the thrust rod. During manual detection, the thrust rod can be connected with the connecting hole 83 through the clearance opening 111, so that the thrust rod will not slip when pushing the slider. Further, the connecting hole 83 is arranged at the center of the side of the static pressure slider, which can make the force transmission of the thrust rod more uniform when applying force to the static pressure slider 80.

[0061] Further, the static pressure guide rail performance test device further comprises a first channel 40, a second channel 50, a pressure detection element 60 and a flow detection element 70. The two ends of the first channel 40 are respectively communicated with the oil tank 31 and the first static pressure cavity 81. The two ends of the second channel 50 are respectively communicated with the oil tank 31 and the second static pressure cavity 82. The pressure detection element 60 is two, one of the two pressure detection elements 60 is arranged on the first channel 40 and located between the first static pressure cavity 81 and the pressure regulating element 33, and the other of the two pressure detection elements 60 is arranged on the second channel 50 and located between the second static pressure cavity 82 and the throttling element 32. The flow detection element 70 is arranged on the second channel 50 and located between the second static pressure cavity 82 and the throttling element 32. The test module is electrically connected with the pressure detection element 60 and the flow detection element 70 to calculate the working performance of the static pressure slider 80. In this embodiment, the load of the static pressure slider 80 can be adjusted by adjusting the pressure regulating element 33. At the same time, the two pressure detection elements 60 can detect the pressure of the oil in the first static pressure cavity 81 and the second static pressure cavity 82, respectively. Moreover, the flow detection element 70 can detect the flow of the oil in the second static pressure cavity 82. One advantage of this structure is that before testing different models of static pressure guide rails, only different models of static pressure guide rails need to be installed in the test space 21, and then the first channel 40 is communicated with the first static pressure cavity 81 of the static pressure slider 80, and the second channel 50 is communicated with the second static pressure cavity 82 of the static pressure slider 80, so that the assembly is completed, and there is no need to connect the test elements such as the pressure detection element 60 and the flow detection element 70 to the static pressure slider 80.

[0062] Further, the throttling element 32 comprises a throttle; and / or, the pressure regulating element 33 comprises a pressure regulating valve. It is to be noted that "the throttling element 32 comprises a throttle; and / or, the pressure regulating element 33 comprises a pressure regulating valve" means one of the following three cases: the throttling element 32 comprises a throttle, the pressure regulating element 33 comprises a pressure regulating valve, the throttling element 32 comprises a throttle and the pressure regulating element 33 comprises a pressure regulating valve. In this embodiment, the throttling element 32 is a throttle, and the pressure regulating element 33 is a pressure regulating valve. Specifically, the pressure regulating valve is a manual stepless pressure regulating valve, and the oil pressure in the first static pressure chamber 81 of the static pressure slide block 80 can be continuously adjusted by twisting the knob on the pressure regulating valve.

[0063] Further, the present application also provides a static pressure guide rail working performance testing method, which is used for executing the static pressure guide rail working performance testing device, and comprises a detection step, a calculation step and a judgment step, which will be described in detail below.

[0064] Step S1: detection step

[0065] In this step, the pressure detection element 60 and the flow detection element 70 are used to detect the current oil pressure P1 in the first static pressure chamber 81, the current oil pressure P2 in the second static pressure chamber 82 and the current oil flow Q2 in the second static pressure chamber 82 in real time, and the detection data is transmitted to the testing module, and then the calculation step is executed.

[0066] Step S2: calculation step

[0067] The current load F of the static pressure slide block 80 is calculated according to the current oil pressure P1 in the first static pressure chamber 81 detected by the pressure detection element 60 and the effective load area S1 of the first static pressure chamber 81 input in advance; the current oil film stiffness j of the second static pressure chamber 82 is calculated according to the current oil pressure P2 in the second static pressure chamber 82, the current oil flow Q2 in the second static pressure chamber 82, the oil viscosity μ and the oil cavity flow coefficient The supporting gap h of the second static pressure chamber 82 is calculated; the current oil film stiffness j of the second static pressure chamber 82 is calculated according to the current load F and the supporting gap h calculated above. u Then, the judgment step is executed. Specifically, when testing different models of static pressure guide rails, the oil viscosity μ, the effective load area S1 of the first static pressure chamber 81 and the oil cavity flow coefficient of the static pressure guide rail need to be input in the testing module in advance, wherein the oil viscosity μ is related to the oil temperature and the oil model, and the effective load area S1 of the first static pressure chamber 81 and the oil cavity flow coefficient are related to the model of the static pressure guide rail.

[0068] Step S3: Determine the step

[0069] Determine if the support clearance h is greater than 0: If the support clearance h is greater than 0, gradually adjust the pressure regulating element 33 to increase the pressure P1 of the current oil in the first static pressure chamber 81, and repeat the detection step until the support clearance h is exactly 0. At this time, the current load F is the maximum load F of the static pressure slider 80. max The test is stopped. If the support clearance h is equal to 0, the pressure regulating element 33 is gradually adjusted to reduce the pressure P1 of the current oil in the first static pressure chamber 81, and the test step is executed again until the support clearance h is just not 0, and the current load F calculated in the previous calculation step is the maximum load F of the static pressure slider 80. max At that time, the test was stopped.

[0070] Specifically, when the support clearance h is greater than 0, the detection module will prompt the operator to adjust the pressure regulating element 33 to increase the current oil pressure P1 in the first static pressure chamber 81. Similarly, when the support clearance h is equal to 0, the detection module will prompt the operator to adjust the pressure regulating element 33 to decrease the current oil pressure P1 in the first static pressure chamber 81. In the above judgment, "if the support clearance h is greater than 0, the pressure regulating element 33 is gradually adjusted to increase the current oil pressure P1 in the first static pressure chamber 81, and the detection steps are executed again until the support clearance h is exactly 0. At this time, the current load F is the maximum load F of the static pressure slider 80." max In the two judgment steps, "If the support clearance h is equal to 0, then gradually adjust the pressure regulating element 33 to reduce the current oil pressure P1 in the first static pressure chamber 81, and repeat the detection step until the support clearance h is just not 0", the current load F ignores the error. Therefore, the current load F can be regarded as the maximum load F of the static pressure slider 80. max Alternatively, the current load F calculated in the previous calculation step can be considered as the maximum load F of the static pressure slider 80. max .

[0071] In actual operation of the hydrostatic slider 80, the first hydrostatic chamber 81 typically provides the load, while a support clearance between the second hydrostatic chamber 82 and the guide rail is essential. That is, the hydrostatic slider 80 cannot function properly if there is no support clearance between the second hydrostatic chamber 82 and the guide rail 90. Therefore, only the support clearance h of the second hydrostatic chamber 82 needs to be calculated, without considering the support clearance of the first hydrostatic chamber 81.

[0072] The current load F of the static pressure slider 80 is calculated using the following formula:

[0073] F = S1 × P1

[0074] Wherein, S1 represents the effective load area of ​​the first static pressure chamber 81;

[0075] P1 represents the pressure of the current oil in the first static pressure cavity 81.

[0076] Wherein, the support gap h of the second static pressure cavity 82 is calculated by the following formula:

[0077]

[0078] Wherein, μ represents the viscosity of the oil;

[0079] represents the oil cavity flow coefficient of the static pressure slider 80;

[0080] Q2 represents the flow of the current oil in the second static pressure cavity 82;

[0081] P2 represents the pressure of the current oil in the second static pressure cavity 82.

[0082] Wherein, the stiffness j of the current oil film in the second static pressure cavity 82 is calculated by the following formula: u

[0083]

[0084] Wherein, represents the partial differential of the current load F of the static pressure slider 80;

[0085] represents the partial differential of the support gap h of the second static pressure cavity 82. When the stiffness j of the current oil film in the second static pressure cavity 82 is calculated, u When calculating, the current load F of the static pressure slider 80 and the support gap h of the second static pressure cavity 82 are usually specific numbers, so numerical calculation is carried out by using numerical solution methods of ordinary differential equations, such as Euler method, Runge-Kutta method, etc.

[0086] After the current load F of the static pressure slider 80, the support gap h of the second static pressure cavity 82 and the stiffness j of the current oil film in the second static pressure cavity 82 are calculated, u Then, the maximum load F of the static pressure slider 80 is found by the judging step max To ensure that the load applied to the static pressure slider 80 in actual work is not greater than the maximum load F of the static pressure slider 80 max At the same time, the working range of the support gap of the second static pressure cavity 82 can be obtained by the theoretical calculation method, that is, when the support gap h of the second static pressure cavity 82 exceeds the working range of the support gap, the static pressure slider 80 cannot work normally.

[0087] In one specific embodiment in the embodiment, the oil temperature is 20℃, the oil type is VG46, the oil viscosity μ is 0.1075, and the oil cavity flow coefficient of the static pressure slider 80 ​The current oil pressure P1 in the first static pressure chamber 81 is 0.7387 MPa, and the current oil pressure P2 in the first static pressure chamber 81 is 0.3365 MPa. The current oil flow rate Q2 in the second static pressure chamber 82 is 11.87 ml / min, and the effective load area S1 of the first static pressure chamber 81 is 0.005394 m². 2 According to theoretical calculations, the specific range of the support clearance h of the second static pressure chamber 82 is 0 to 18 μm. After calculation, ignoring errors, the current load F of the static pressure slider 80 is 4000 N, the support clearance h of the second static pressure chamber 82 is 26.27 μm, and the stiffness j of the current oil film in the second static pressure chamber 82 is... u The value is 1250.75 N / µm. At this time, the support clearance h of the second static pressure chamber 82 exceeds the working range of the support clearance, and it is necessary to adjust the pressure regulating element 33 to increase the current load F of the static pressure slider 80.

[0088] In this embodiment, a hydrostatic guide rail performance testing device and method are designed. The load provided by the oil replaces the method of controlling the external load using weights. A manual stepless pressure regulating valve is selected, allowing continuous adjustment of the load on the hydrostatic slider 80. Furthermore, in this embodiment, when testing is required, only the hydrostatic guide rail needs to be installed in the test space 21, and the first channel 40 and the second channel 50 are connected to the first hydrostatic chamber 81 and the second hydrostatic chamber 82, respectively, to begin the test, without needing to connect test components to the first and second hydrostatic chambers 81 and 82. Compared to existing technologies, the advantages of this embodiment are that it eliminates the need for weights and dial indicators, the load on the hydrostatic slider can be continuously varied, the method provided in this embodiment can directly calculate the working performance of the hydrostatic slider through test parameters, and the device in this embodiment is easy to assemble during testing and is less susceptible to the accuracy of test results being affected by factors such as assembly effects and throttle consistency.

[0089] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0090] In addition, it should be noted that the use of the terms "first", "second", etc. to qualify parts is only intended to facilitate the distinction of the corresponding parts, and in the absence of a further declaration, the above terms do not have a special meaning and therefore cannot be understood as limiting the scope of protection of the present application.

[0091] The above only is the preferred embodiment of the present application, and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A hydrostatic guideway performance testing device, a hydrostatic guideway comprising a hydrostatic slide (80), the hydrostatic slide (80) comprising a first hydrostatic chamber (81) and a second hydrostatic chamber (82), the first hydrostatic chamber (81) being arranged at a first side of the hydrostatic slide (80), the second hydrostatic chamber (82) being arranged at a second side of the hydrostatic slide (80) opposite to the first side, characterized in that, include: Workbench (10); A pressure plate (20) is fixedly disposed on the workbench (10) and surrounds the first surface of the workbench (10) to form a test space (21). The static pressure slider (80) to be tested is installed in the test space (21), and the first static pressure cavity (81) is directly opposite to the pressure plate (20), and the second static pressure cavity (82) is directly opposite to the first surface. The oil supply mechanism includes an oil tank (31), a throttling element (32), and a pressure regulating element (33). The throttling element (32) is connected between the oil tank (31) and the second static pressure chamber (82), and the pressure regulating element (33) is connected between the oil tank (31) and the first static pressure chamber (81) to adjust the load of the static pressure slider (80). The testing module calculates the working performance of the static pressure slider (80) based on the current oil pressure in the first static pressure chamber (81), the current oil flow rate in the second static pressure chamber (82), and the current oil pressure in the second static pressure chamber (82).

2. The static pressure guideway performance testing device of claim 1, wherein, The workbench (10) includes a support member (11), which is disposed on a first surface of the workbench (10), and the pressure plate (20) is fixedly disposed on the support member (11) and forms the test space (21) between the pressure plate (20) and the first surface.

3. The static pressure guideway performance testing device of claim 1 wherein, The hydrostatic guide rail performance testing device also includes a thrust rod, which is set on the worktable (10) to apply a thrust to the hydrostatic slider (80), and the direction of the thrust is consistent with the sliding direction of the hydrostatic slider (80).

4. The static pressure guideway performance testing device of claim 3 wherein, The workbench (10) includes at least two spaced support members (11). The two ends of the pressure plate (20) are respectively fixed on the two support members (11). The support member (11) has a clearance opening (111) through it along the sliding direction of the static pressure slider (80). The thrust rod applies the thrust to the static pressure slider (80) through the clearance opening (111).

5. The static pressure guideway performance testing device of claim 4 wherein, The hydrostatic guide rail performance testing device also includes: The first channel (40) is connected at both ends to the oil tank (31) and the first static pressure chamber (81), respectively. The second channel (50) is connected at both ends to the oil tank (31) and the second static pressure chamber (82), respectively. Pressure detection element (60), there are two pressure detection elements (60), one of the two pressure detection elements (60) is disposed on the first channel (40) and located between the first static pressure chamber (81) and the pressure regulating element (33), and the other of the two pressure detection elements (60) is disposed on the second channel (50) and located between the second static pressure chamber (82) and the throttling element (32); A flow detection element (70) is arranged on the second channel (50) and located between the second static pressure cavity (82) and the throttling element (32); The test module is electrically connected with the pressure detection element (60) and the flow detection element (70) to calculate the working performance of the static pressure slider (80).

6. The static pressure guideway performance testing device of claim 1 wherein, The throttling element (32) comprises a throttling device; and / or, the pressure regulating element (33) comprises a pressure regulating valve.

7. A hydrostatic guideway performance testing method, characterized by, The static pressure guide rail working performance test method is used for the static pressure guide rail working performance test device in any one of claims 1 to 6, and the static pressure guide rail working performance test method comprises: A detection step: real-time detection of the pressure P1 of the current oil in the first static pressure cavity (81), the pressure P2 of the current oil in the second static pressure cavity (82), and the flow Q2 of the current oil in the second static pressure cavity (82), and then a calculation step is performed; Computing step: calculating the current load F of the static pressure slide (80) according to the pressure P1 of the current oil in the first static pressure cavity (81) and the effective load area S1 of the first static pressure cavity (81); calculating the current oil film stiffness j in the second static pressure cavity (82) according to the current load F and the support gap h of the second static pressure cavity (82) Computing the support gap h of the second static pressure cavity (82); calculating the current oil film stiffness j in the second static pressure cavity (82) according to the current load F and the support gap h u , and then, performing a judging step; Judging step: judging whether the supporting gap h is greater than 0: if the supporting gap h is greater than 0, then gradually adjusting the pressure regulating element (33), increasing the pressure P1 of the current oil in the first hydrostatic cavity (81), and executing the detecting step again until the supporting gap h is just 0, at which time the current load F is the maximum load F of the hydrostatic slide (80) and the test is stopped; if the supporting gap h is equal to 0, then gradually adjusting the pressure regulating element (33), decreasing the pressure P1 of the current oil in the first hydrostatic cavity (81), and executing the detecting step again until the supporting gap h is just not 0 and the current load F calculated in the last calculating step is the maximum load F of the hydrostatic slide (80) and the test is stopped. max max Judging step: judging whether the supporting gap h is greater than 0: if the supporting gap h is greater than 0, then gradually adjusting the pressure regulating element (33), increasing the pressure P1 of the current oil in the first hydrostatic cavity (81), and executing the detecting step again until the supporting gap h is just 0, at which time the current load F is the maximum load F of the hydrostatic slide (80) and the test is stopped; if the supporting gap h is equal to 0, then gradually adjusting the pressure regulating element (33), decreasing the pressure P1 of the current oil in the first hydrostatic cavity (81), and executing the detecting step again until the supporting gap h is just not 0 and the current load F calculated in the last calculating step is the maximum load F of the hydrostatic slide (80) and the test is stopped. max max Judging step: judging whether the supporting gap h is greater than 0: if the supporting gap h is greater than 0, then gradually adjusting the pressure regulating element (33), increasing the pressure P1 of the current oil in the first hydrostatic cavity (81), and executing the detecting step again until the supporting gap h is just 0, at which time the current load F is the maximum load F of the hydrostatic slide (80) and the test is stopped; if the supporting gap h is equal to 8. The static pressure guideway performance testing method of claim 7 wherein, The current load F of the static pressure slider (80) is calculated by the following formula: F=S1×P1 Wherein, S1 represents the effective load area of the first static pressure cavity (81); P1 represents the pressure of the current oil in the first static pressure cavity (81).

9. The static pressure guideway performance testing method of claim 7 wherein, The bearing gap h of the second static pressure cavity (82) is calculated by the following formula: Wherein, μ represents the viscosity of the oil; represents the oil cavity flow coefficient of the hydrostatic slide (80); Q2 represents the flow of the current oil in the second static pressure cavity (82); P2 represents the pressure of the current oil in the second static pressure cavity (82).

10. The static pressure guideway performance testing method of claim 7 wherein, the stiffness j of the current oil film in the second hydrostatic chamber (82) u is calculated by the following formula: wherein, represents the partial differential of the current load F of the hydrostatic slide (80); represents the partial derivative of the support gap h of the second hydrostatic chamber (82).

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