Static pressure vibration system

Abstract

The present application relates to the field of soil testing equipment, and specifically to a static pressure vibration system, which includes: a hydraulic cylinder, a static pressure chamber and a dynamic load chamber are formed in the hydraulic cylinder, the static pressure chamber is provided with a first piston rod, the dynamic load chamber is provided with a second piston rod, the first piston rod is used to output a static load to a test surface, the output end of the second piston rod is superimposed with the output end of the first piston rod, and the second piston rod is used to output a vibration impact force to the test surface; a first oil supply device, the first oil supply device is used to provide a stable oil pressure to the static pressure chamber; a second oil supply device, the second oil supply device is used to supply oil to the dynamic load chamber according to a set frequency. The static pressure vibration system with a double-acting hydraulic cylinder can simultaneously apply a static load and a vibration impact force to the test surface, so that the test surface can be subjected to a high-frequency vibration impact force under static pressure conditions, so as to test the actual bearing capacity of the soil under the action of static and dynamic loads, and provide a solution for high-frequency vibration testing of soil.

Description

Technical Field

[0001] The present application relates to the field of soil testing equipment, and in particular, to a static pressure vibration system. Background Art

[0002] When a vehicle is driving on the road, the roadbed will not only be compressed, but also vibrated due to the vibration of the machine itself or the bumpy driving. For example, when a high-speed train is running along the track, the roadbed below the track will be subjected to pressure and vibration from the track. The existing roadbed bearing capacity test is generally a static load test. The static load test is generally to set up a steel beam on the roadbed and pile test blocks on the steel beam for loading. For safety reasons, both the test blocks and the steel beam need to be stable, and it is impossible to provide static load and vibration impact at the same time. Summary of the invention

[0003] The present application aims to provide a static pressure vibration system for conducting soil vibration tests under static load.

[0004] The embodiment of the present application is implemented as follows:

[0005] In a first aspect, an embodiment of the present application provides a static pressure vibration system, comprising:

[0006] A hydraulic cylinder, wherein a static pressure chamber and a dynamic load chamber are formed in the hydraulic cylinder, the static pressure chamber is provided with a first piston rod, the dynamic load chamber is provided with a second piston rod, the first piston rod is used to output a static load to a test surface, the output end of the second piston rod is superimposed with the output end of the first piston rod, and the second piston rod is used to output a vibration impact force to the test surface;

[0007] a first oil supply device, the first oil supply device being used to provide a stable oil pressure to the static pressure chamber;

[0008] The second oil supply device is used to supply oil to the dynamic load chamber according to a set frequency.

[0009] The present application provides a double-acting hydraulic cylinder, in which a first oil supply device outputs a stable oil pressure to a static pressure chamber to drive a first piston rod to press against a test surface, thereby subjecting the test surface to a stable static load, and a second oil supply device supplies oil to a dynamic load chamber at a set frequency. Vibrations are generated when hydraulic oil enters and exits the dynamic load chamber, and a vibration impact force is transmitted to the test surface through a second piston rod arranged in the dynamic load chamber, thereby achieving simultaneous application of a static load and a vibration impact force to the test surface. The static load and the vibration impact force are superimposed on the test surface, so that the test surface can be subjected to high-frequency vibrations under static pressure conditions, thereby achieving a soil vibration test under static load to test the actual bearing capacity of the soil under dynamic and static loads.

[0010] Optionally, in one embodiment of the present application, the static pressure chamber surrounds the dynamic load chamber, the first piston rod is in the shape of a cylinder with one end open to match the annular static pressure chamber, and the output end of the second piston rod is connected to the inner end surface of the first piston rod.

[0011] By arranging the static pressure chamber around the dynamic load chamber, the vibration impact force provided to the test surface by the second piston rod is emitted from the middle position of the first piston rod, so that the main action range of the vibration is within the static pressure range as much as possible, ensuring that the test surface is subjected to superimposed vibration impact force under the action of static load.

[0012] Optionally, in one embodiment of the present application, the hydraulic cylinder includes a first end plate, an outer cylinder and an inner cylinder coaxially installed on the first end plate, the first end plate and the inner wall of the inner cylinder form the dynamic load chamber, the first end plate, the outer wall of the inner cylinder and the inner wall of the outer cylinder form the static pressure chamber; the first end plate is provided with a dynamic load oil supply pipe connecting the second oil supply device and the dynamic load chamber.

[0013] By providing the first end plate, the outer cylinder and the inner cylinder coaxially mounted on the first end plate, a double-layer double-acting hydraulic cylinder is formed to ensure that the test surface is subjected to superimposed vibration impact force under the action of static load.

[0014] Optionally, in one embodiment of the present application, the outer wall of the inner cylinder is formed with a radially extending flange, the flange extends to the inner wall of the outer cylinder and is in contact with the first end plate; the oil inlet and outlet of the static pressure chamber passes through the outer cylinder and is located between the flange and the first piston rod.

[0015] A flange that fits the first end plate is formed on the outer wall of the inner cylinder and extends to the inner wall of the outer cylinder, so that the fitting area between the inner cylinder and the first end plate is increased, the sealing performance is improved, and the inner cylinder and the outer cylinder are guaranteed to be independent of each other.

[0016] Optionally, in an embodiment of the present application, the first oil supply device includes a first oil supply pump for supplying oil to the static pressure chamber, and a proportional valve is provided on the connection passage between the first oil supply pump and the static pressure chamber.

[0017] By providing a first oil supply pump with a proportional valve, different oil pressures can be provided to the static pressure chamber, thereby facilitating the adjustment of the static load output through the first piston rod.

[0018] Optionally, in one embodiment of the present application, the second oil supply device includes a second oil supply pump for supplying oil to the dynamic load chamber, and a vibration valve is provided on the connecting passage between the second oil supply pump and the dynamic load chamber, and the vibration valve is used to control the oil supply according to a set frequency.

[0019] By arranging the second oil supply pump and the vibration valve, vibration impact forces of different magnitudes and frequencies can be provided through the second piston rod.

[0020] Optionally, in an embodiment of the present application, the vibration valve includes a valve body, a valve sleeve and a valve core, the valve sleeve is arranged in the valve body, and the valve core is rotatably arranged in the valve sleeve; an oil inlet hole, an oil return hole and an oil supply hole are formed on the valve body, the oil supply hole is connected to the dynamic load oil supply pipe of the dynamic load chamber, and the oil inlet hole and the oil return hole are used to respectively connect to the second oil supply pump; an oil return port, a first regulating port, an oil supply port and a second regulating port are sequentially arranged on the valve sleeve along the axial direction, the oil return port is connected to the oil return port, the first regulating port and the oil supply port are respectively connected to the oil supply hole, and the second regulating port is connected to the oil inlet hole; a first shoulder and a second shoulder are formed on the valve core, the first shoulder corresponds to the first regulating port, the second shoulder corresponds to the second regulating port, a first connecting groove is formed on the circumference of the first shoulder, a second connecting groove is formed on the circumference of the second shoulder, and the projections of the first connecting groove and the second connecting groove on the radial cross section of the valve core are staggered with each other;

[0021] The valve core has an oil supply state and an oil return state. When the valve core is in the oil supply state, the first connecting groove is offset from the first regulating port to close the first regulating port, and the second connecting groove is opposite to the second regulating port to connect the second regulating port with the oil supply port; when the valve core is in the oil return state, the first connecting groove is opposite to the first regulating port to connect the first regulating port with the oil return port, and the second connecting groove is offset from the second regulating port to close the second regulating port.

[0022] The valve core rotates to switch the oil supply state and the oil return state. The frequency of the oil supply and oil return can be adjusted by adjusting the rotation frequency of the valve core, which is convenient for adjusting the output frequency of the vibration impact force, and the valve core can be quickly rotated to achieve high-frequency output vibration impact force.

[0023] Optionally, in an embodiment of the present application, a first annular groove, a second annular groove and a third annular groove are formed in the valve body and respectively surround the valve sleeve, the first annular groove is communicated with the oil return hole, the second annular groove is communicated with the oil supply hole, and the third annular groove is communicated with the oil inlet hole;

[0024] The valve sleeve comprises a plurality of oil return ports, a plurality of first regulating ports, a plurality of oil supply ports and a plurality of second regulating ports, wherein the plurality of oil return ports, the plurality of first regulating ports, the plurality of oil supply ports and the plurality of second regulating ports are respectively arranged around the circumference of the valve sleeve; the plurality of oil return ports are located within the surrounding range of the first annular groove, the plurality of first regulating ports and the plurality of oil supply ports are located within the surrounding range of the second annular groove, and the plurality of second regulating ports are located within the surrounding range of the third annular groove;

[0025] The first connecting groove includes a plurality of grooves arranged around the first shoulder, and the second connecting groove includes a plurality of grooves arranged around the second shoulder.

[0026] By arranging multiple oil return ports within the surrounding range of the first annular groove, arranging multiple first regulating ports and multiple oil supply ports within the surrounding range of the second annular groove, and arranging multiple second regulating ports within the surrounding range of the third annular groove, and correspondingly arranging multiple first connecting grooves and multiple second connecting grooves, multiple oil supply and return operations can be achieved for each rotation of the valve core, thereby improving the output frequency of the vibration impact force.

[0027] Optionally, in one embodiment of the present application, both ends of the valve core respectively pass through the valve body and form a dynamic seal with the valve body, one end of the valve core is connected to a first driving device, the first driving device is used to drive the valve core to rotate to switch between an oil supply state and an oil return state, and the other end of the valve core is connected to a core shaft adjustment device, the core shaft adjustment device is used to drive the valve core to move along its own axis so that the first adjustment port slides on the first shoulder and the second adjustment port slides on the second shoulder, thereby adjusting the overlapping area between the first adjustment port and the first connecting groove, and the overlapping area between the second adjustment port and the second connecting groove.

[0028] The overlapping area of ​​the first regulating port and the first connecting groove is the oil return port diameter, and the overlapping area of ​​the second regulating port and the second connecting groove is the oil supply port diameter. By setting the valve core as a structure that can move axially, it is convenient to adjust the oil supply port diameter and the oil return port diameter, thereby adjusting the size of the single oil supply to the dynamic load chamber and the size of the output vibration impact force.

[0029] Optionally, in an embodiment of the present application, the output end of the first driving device is connected to one end of the valve core via a coupling, and the coupling includes a first connecting portion and a second connecting portion that can slide relative to each other in the axial direction.

[0030] The first connecting part and the second connecting part which can slide relative to each other in the axial direction enable the coupling to be retracted and extended in the axial direction. The first driving device and the valve core are connected through the coupling, so that the valve core can be moved axially when the first driving device is fixed. The movement of the valve core is more labor-saving and convenient, and the energy consumption generated by the movement is lower.

[0031] Optionally, in one embodiment of the present application, the core shaft adjustment device includes a second driving device, an eccentric wheel, a first limiting ring and a second limiting ring, the eccentric wheel is connected to the output end of the second driving device, the first limiting ring and the second limiting ring are formed on the valve core, the eccentric wheel is located between the first limiting ring and the second limiting ring, and the eccentric wheel cooperates with the first limiting ring and the second limiting ring to make the valve core move along its own axis.

[0032] The eccentric wheel arranged at the output end of the second driving device cooperates with the first limiting ring and the second limiting ring arranged on the valve core. When the second driving device is working, the eccentric wheel pushes the first limiting ring or the second limiting ring to drive the valve core to move. The structure is simple and effective, with high precision, no redundant connection structure, easy installation, and not prone to failure.

[0033] Optionally, in an embodiment of the present application, the core shaft adjustment device includes a displacement meter, and the valve core is connected to the displacement meter.

[0034] A displacement meter is provided to connect the valve core so as to measure and obtain the distance the valve core moves along the axial direction, thereby obtaining the amplitude of the corresponding vibration impact force. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other related drawings can be obtained based on these drawings without paying creative work.

[0036] Figure 1 A schematic diagram of the three-dimensional structure of a hydraulic cylinder provided in an embodiment of the present application;

[0037] Figure 2 A schematic top view of a hydraulic cylinder provided in an embodiment of the present application;

[0038] Figure 3 for Figure 2 A-A section diagram;

[0039] Figure 4 for Figure 3 Enlarged view of part B;

[0040] Figure 5 A schematic diagram of the three-dimensional structure of a valve sleeve provided in an embodiment of the present application;

[0041] Figure 6 A schematic diagram of the three-dimensional structure of the valve core provided in an embodiment of the present application;

[0042] Figure 7 for Figure 3 Part C in the middle shows an enlarged view of the valve body in the fully open position;

[0043] Figure 8 for Figure 3 Part C in the middle shows an enlarged view of the valve body in the closed position;

[0044] Fig. 9 for Figure 3 Part C in the middle shows an enlarged view of the valve body in a half-open position;

[0045] Fig.10 In the vibration valve oil supply state, Figure 2 D-D section view of the middle valve sleeve and valve core;

[0046] Fig.11 In the vibration valve oil supply state, Figure 2 E-E section view of the middle valve sleeve and valve core;

[0047] Fig.12 In the oil return state of the vibration valve, Figure 2 D-D section view of the middle valve sleeve and valve core;

[0048] Fig.13 In the oil return state of the vibration valve, Figure 2 E-E section view of the middle valve sleeve and valve core.

[0049] Icons: 10 - loading beam; 20 - specimen; 30 - vibration valve; 40 - hydraulic cylinder; 100 - valve body; 110 - first annular groove; 111 - oil return hole; 120 - second annular groove; 121 - oil supply hole; 130 - third annular groove; 131 - oil inlet hole; 140 - dynamic load oil supply pipe; 200 - valve sleeve; 210 - oil return port; 220 - first regulating port; 230 - oil supply port; 240 - second regulating port; 300 - valve core; 310 - first shoulder; 311 - first connecting groove; 320 - third Second shoulder; 321 - second connecting groove; 330 - sealing groove; 340 - first driving device; 341 - coupling; 400 - spindle adjustment device; 410 - second driving device; 411 - eccentric wheel; 420 - driven wheel; 421 - first limiting ring; 422 - second limiting ring; 430 - displacement meter; 510 - first end plate; 520 - outer cylinder; 530 - inner cylinder; 540 - first piston rod; 550 - second piston rod; 560 - second end plate; 570 - static pressure chamber; 580 - dynamic load chamber. DETAILED DESCRIPTION

[0050] In order to make the purpose, technical solution and advantages of the embodiments of the present application clearer, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, rather than all the embodiments. The components of the embodiments of the present application described and shown in the drawings here can be arranged and designed in various different configurations.

[0051] Therefore, the following detailed description of the embodiments of the present application provided in the accompanying drawings is not intended to limit the scope of the present application for which protection is sought, but merely represents selected embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in the field without creative work are within the scope of protection of the present application.

[0052] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, further definition and explanation thereof is not required in subsequent drawings.

[0053] In the description of this application, it should be noted that if the terms "center", "up", "down", "left", "right", "vertical", "horizontal", "inside", "outside", etc. appear, the orientation or position relationship indicated is based on the orientation or position relationship shown in the drawings, or the orientation or position relationship in which the product of the application is usually placed when in use. It is only for the convenience of describing this 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 operate in a specific orientation, and therefore cannot be understood as a limitation on this application. In addition, if the terms "first", "second", etc. appear in the description of this application, they are only used to distinguish the description and cannot be understood as indicating or implying relative importance.

[0054] In addition, if the terms "horizontal" or "vertical" appear in the description of this application, it does not mean that the components are required to be absolutely horizontal or suspended, but can be slightly tilted. For example, "horizontal" only means that its direction is more horizontal than "vertical", and does not mean that the structure must be completely horizontal, but can be slightly tilted.

[0055] In the description of this application, it should also be noted that, unless otherwise clearly specified and limited, the terms "set", "install", "connect", and "connect" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal connection of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0056] Example

[0057] When a vehicle is driving on a road, not only will the roadbed be compressed, but the roadbed will also be vibrated due to the vibration of the machine itself or the bumpy driving. For example, when a high-speed train is running along a track, the roadbed below the track will be subjected to pressure and vibration from the track. The embodiment of the present application provides a static pressure vibration system for simultaneously providing a static load and a vibration impact force to a roadbed sample 20, so as to perform a high-frequency vibration test on the sample 20 under a certain static load pressure.

[0058] The static pressure vibration system includes a hydraulic cylinder 40 , and a first oil supply device and a second oil supply device for supplying oil to the hydraulic cylinder 40 .

[0059] like Figure 3 As shown, the hydraulic cylinder 40 is installed on the loading beam 10, and the output end faces the test surface of the sample 20 at the bottom, and the first oil supply device (not shown in the figure) and the second oil supply device (not shown in the figure) are respectively connected to the hydraulic cylinder 40.

[0060] The hydraulic cylinder 40 has a static pressure chamber 570 and a dynamic load chamber 580 formed therein. The two chambers are independent of each other. A first piston rod 540 is arranged in the static pressure chamber 570, and a second piston rod 550 is arranged in the dynamic load chamber 580. The first piston rod 540 is used to output a static load to the test surface, and the second piston rod 550 is used to output a vibration impact force to the test surface. The output end of the second piston rod 550 overlaps with the output end of the first piston rod 540.

[0061] In the present application, the output end of the second piston rod 550 overlaps with the output end of the first piston rod 540 , which means that the output end of the second piston rod 550 acts on the output end of the first piston rod 540 .

[0062] The output end of the second piston rod 550 can be separated from the output end of the first piston rod 540. The first oil supply device supplies oil to the static pressure chamber 570 to drive the first piston rod 540 to extend, and the second oil supply device drives the second piston rod 550 to reciprocate. The output end of the second piston rod 550 acts on the output end of the first piston rod 540 to provide vibration impact force.

[0063] The output end of the second piston rod 550 and the output end of the first piston rod 540 can also be interconnected. The first oil supply device supplies oil to the static pressure chamber 570 to drive the first piston rod 540 and the second piston rod 550 to extend. During the whole process, the first piston rod 540 and the second piston rod 550 always maintain a state of extending toward the test surface. The second oil supply device supplies oil to the dynamic load chamber 580 at a set frequency to make the pressure in the dynamic load chamber 580 increase and decrease regularly, and superimposes the force on the output end of the first piston rod 540 through the output end of the second piston rod 550, thereby providing a superimposed vibration impact force to the test surface.

[0064] The first oil supply device includes a first oil supply pump (not shown in the figure), which is connected to the static pressure chamber 570 of the hydraulic cylinder 40. The first oil supply pump is used to provide stable oil pressure to the static pressure chamber 570. A proportional valve is arranged on the connecting passage between the first oil supply pump and the static pressure chamber 570 to facilitate adjusting the oil supply size of the static pressure chamber 570, thereby adjusting the size of the static load.

[0065] The second oil supply device includes a second oil pump (not shown in the figure), which is connected to the dynamic load chamber 580 of the hydraulic cylinder 40. The second oil supply pump is used to supply oil to the dynamic load chamber 580 according to a set frequency. A vibration valve 30 is provided on the connection passage between the second oil supply pump and the dynamic load chamber 580. The vibration valve 30 is used to control the oil supply size and oil supply frequency of the dynamic load chamber 580 so as to adjust the output frequency and force value of the vibration impact force. Figure 1 and Figure 3 As shown, the vibration valve 30 is fixedly installed above the load beam 10 .

[0066] By setting up a hydraulic cylinder 40 with both a static pressure chamber 570 and a dynamic load chamber 580, the two chambers are supplied with oil independently, and the first oil supply device outputs a stable oil pressure to the static pressure chamber 570 to drive the first piston rod 540 and the second piston rod 550 to extend and press against the test surface, so that the test surface is subjected to a stable static load, and the second oil supply device is installed to supply oil to the dynamic load chamber 580 at a set frequency, and the hydraulic oil enters and exits the dynamic load chamber 580 to generate vibration, and the vibration impact force is transmitted to the test surface through the second piston rod 550 arranged in the dynamic load chamber 580, so as to achieve the simultaneous application of static load and vibration impact force to the test surface, so that the test surface can be subjected to high-frequency vibration under static pressure conditions to test the actual bearing capacity of the soil under the action of dynamic and static loads.

[0067] In the present embodiment, the output end of the second piston rod 550 is connected to the output end of the first piston rod 540, and the first piston rod 540 and the second piston rod 550 are always kept in a state of extending toward the test surface. The vibration impact force is provided by the high-frequency oil pressure in the dynamic load chamber 580. Compared with the reciprocating movement of the second piston rod 550 to superimpose the vibration impact force on the output end of the first piston rod 540, the static pressure vibration system provided in the present embodiment has a smaller mechanical vibration experienced by the part installed on the loading beam 10 and the whole formed by the static pressure vibration system and the loading beam 10, and the test safety is high.

[0068] The structure of the hydraulic cylinder 40 is as follows: Figure 4 As shown, it includes a first end plate 510 , an inner cylinder 530 , an outer cylinder 520 and a dynamic load oil supply pipe 140 . The second piston rod 550 is arranged in the inner cylinder 530 , and the first piston rod 540 is arranged in the outer cylinder 520 .

[0069] The inner cylinder 530 and the outer cylinder 520 are coaxially installed on the first end plate 510. The inner wall of the first end plate 510 and the inner cylinder 530 form the aforementioned dynamic load cavity 580. The outer wall of the first end plate 510, the inner cylinder 530 and the inner wall of the outer cylinder 520 form the aforementioned static pressure cavity 570.

[0070] The dynamic load chamber 580 is located in the middle, and the static pressure chamber 570 is in a ring shape surrounding the dynamic load chamber 580 .

[0071] The first piston rod 540 includes a hollow cylindrical body and a second end plate 560, and the hollow cylindrical body and the second end plate 560 form a cylindrical shape adapted to the annular static pressure chamber 570. The output end of the second piston rod 550 is connected to the inner end surface of the first piston rod 540, that is, the output end of the second piston rod 550 is connected to the center position of the second end plate 560.

[0072] To further ensure that the dynamic load chamber 580 and the static pressure chamber 570 are relatively independent, Figure 4 As shown, the outer cylinder 520 and the inner cylinder 530 are fastened to the first end plate 510 by screws respectively, and the outer wall of the inner cylinder 530 is formed with a flange extending radially, the flange is fitted with the first end plate 510, and the flange extends to the inner wall of the outer cylinder 520 and presses tightly.

[0073] Optionally, an O-ring is sleeved on the flange to further isolate and seal.

[0074] The static pressure chamber 570 is used to connect the oil inlet and outlet of the first oil supply pump, which are arranged on the outer cylinder 520. The oil inlet and outlet of the static pressure chamber 570 penetrate the outer cylinder 520 and are located between the flange and the first piston rod 540. The dynamic load chamber 580 is used to connect the dynamic load oil supply pipe 140 of the second oil supply pump, which penetrates the first end plate 510 to connect the dynamic load chamber 580 and the second oil supply device.

[0075] like Figure 3 and Figure 4 As shown, the vibration valve 30 fixed on the loading beam 10 has an oil supply hole 121 disposed on its valve body 100 , and the oil supply hole 121 is connected to the dynamic load oil supply pipe 140 .

[0076] The structure of the vibration valve 30 is shown in FIG. Figure 1 , Figure 2 and Figure 3 As shown, it includes a valve body 100, a valve sleeve 200 and a valve core 300, wherein the valve sleeve 200 is embedded in the valve body 100, the valve core 300 is rotatably arranged in the valve sleeve 200, and both ends of the valve core 300 respectively penetrate the valve body 100 and form a dynamic seal with the valve body 100, so that the valve core 300 can rotate around its own axis in the valve sleeve 200, and can also move along its own axis relative to the valve sleeve 200, and when the valve core 300 rotates or moves, oil will not leak from the connection position between the valve core 300 and the valve body 100.

[0077] The vibration valve 30 further includes a first driving device 340 and a core shaft adjusting device 400. The first driving device 340 is used to drive the core shaft to rotate around its own axis, and the core shaft adjusting device 400 is used to drive the core shaft to move along its own axis.

[0078] like Figure 3 and Figure 7 As shown, the valve body 100 is formed with an oil return hole 111, an oil supply hole 121 and an oil inlet hole 131, and the valve body 100 is formed with a first annular groove 110, a second annular groove 120 and a third annular groove 130. The oil return hole 111 is connected to the first annular groove 110 and the second oil supply pump; the oil supply hole 121 is connected to the second annular groove 120 and the dynamic load oil supply pipe 140 of the dynamic load chamber 580; and the oil inlet hole 131 is connected to the third annular groove 130 and the second oil supply pump.

[0079] The valve sleeve 200 is embedded in the valve body 100. The structure of the valve sleeve 200 is as follows: Figure 5 and Figure 7 As shown, the valve sleeve 200 is provided with an oil return port 210, a first regulating port 220, an oil supply port 230, and a second regulating port 240 in sequence along the axial direction. The number of the oil return port 210, the first regulating port 220, the oil supply port 230, and the second regulating port 240 is multiple, and the multiple oil return ports 210, the multiple first regulating ports 220, the multiple oil supply ports 230, and the multiple second regulating ports 240 are respectively arranged around the circumference of the valve sleeve 200. The number of the first regulating ports 220 and the second regulating ports 240 is the same.

[0080] The plurality of oil return ports 210 are correspondingly arranged within the surrounding range of the first annular groove 110 , the plurality of first regulating ports 220 and the plurality of oil supply ports 230 are located within the surrounding range of the second annular groove 120 , and the plurality of second regulating ports 240 are located within the surrounding range of the third annular groove 130 .

[0081] As can be seen from the above, the oil return port 210 of the valve sleeve 200 is connected to the oil return hole 111 of the valve body 100 through the first annular groove 110, the first regulating port 220 and the oil supply port 230 of the valve sleeve 200 are respectively connected to the oil supply hole 121 of the valve body 100 through the second annular groove 120, and the second regulating port of the valve sleeve 200 is connected to the oil inlet hole 131 of the valve body 100 through the third annular groove 130.

[0082] A first land 310 and a second land 320 are formed on the valve core 300 . The first land 310 corresponds to the first regulating port 220 , and the second land 320 corresponds to the second regulating port 240 .

[0083] like Figure 7As shown, the outer circumferential surfaces of the first shoulder 310 and the second shoulder 320 are respectively fitted with the inner wall of the valve sleeve 200, and the fitting parts are smooth to allow the valve core 300 to rotate in the valve sleeve 200. The first shoulder 310 is correspondingly arranged at the position of the first regulating port 220 and can close the first regulating port 220. The second shoulder 320 is correspondingly arranged at the position of the second regulating port 240 and can close the second regulating port 240.

[0084] The first shoulder 310 and the second shoulder 320 separate a relatively independent oil return chamber and an oil inlet chamber in the valve sleeve 200, wherein the left side of the first shoulder 310 is the oil return chamber, and the oil inlet chamber is between the first shoulder 310 and the second shoulder 320. The oil return port 210 provided on the valve sleeve 200 communicates with the oil return chamber and the first annular groove 110, and the oil supply port 230 provided on the valve sleeve 200 communicates with the oil inlet chamber and the second annular groove 120.

[0085] A plurality of first connecting grooves 311 are formed on the circumference of the first shoulder 310 , and a plurality of second connecting grooves 321 are formed on the circumference of the second shoulder 320 . Projections of the first connecting grooves 311 and the second connecting grooves 321 on the radial cross section of the valve core 300 are staggered.

[0086] like Figure 6 As shown, a first connecting groove 311 is formed at the left end of the first shoulder 310, and a sealing groove 330 is formed at the right end. The first connecting groove 311 extends to the left end surface of the first shoulder 310 and forms an opening to connect to the return oil chamber. The sealing groove 330 is a plurality of annular grooves arranged at the right end of the first shoulder 310, which are used to prevent the return oil chamber from connecting with the oil inlet chamber.

[0087] like Figure 6 As shown, the structure of the second shoulder 320 is the same as that of the first shoulder 310. A second connecting groove 321 is formed at the left end of the second shoulder 320. The second connecting groove 321 extends to the left end face of the second shoulder 320 and forms an opening so as to connect to the oil inlet chamber. A sealing groove 330 is formed at the right end of the second shoulder 320. The sealing groove 330 is a plurality of annular grooves at the right end of the second shoulder 320, which are used to prevent leakage from the oil inlet chamber.

[0088] The valve core 300 has an oil supply state and an oil return state, or in other words, the valve core 300 rotates to put the vibration valve 30 in the oil supply state or the oil return state.

[0089] When the valve core 300 is in the oil supply state, Fig.10 As shown, the first connection groove 311 is staggered with the first adjustment opening 220 to close the first adjustment opening 220; Fig.11 As shown, the second connecting groove 321 is opposite to the second regulating port 240 so that the second regulating port 240 is connected to the oil supply port 230 .

[0090] When the valve core 300 is in the oil return state, Fig.12 As shown, the first connecting groove 311 is opposite to the first regulating port 220 so that the first regulating port 220 is connected to the oil return port 210; Fig.13 As shown, the second connection groove 321 is staggered with the second adjustment opening 240 to close the second adjustment opening 240 .

[0091] That is, the vibration valve 30 includes an oil inlet passage and an oil return passage. When the oil inlet passage is connected, the second oil supply pump supplies oil to the dynamic load chamber 580. When the oil return passage is connected, the dynamic load chamber 580 returns oil to the second oil supply pump.

[0092] Among them, along the oil inlet direction, the oil inlet path is the second oil supply pump, the oil inlet hole 131, the third annular groove 130, the second regulating port 240, the second connecting groove 321, the oil inlet chamber, the oil supply port 230, the second annular groove 120, the oil supply hole 121, the dynamic load oil supply pipe 140, and the dynamic load chamber 580.

[0093] Among them, along the oil return direction, the oil return path is the dynamic load chamber 580, the dynamic load oil supply pipe 140, the oil supply hole 121, the second annular groove 120, the first regulating port 220, the first connecting groove 311, the oil return chamber, the oil return port 210, the first annular groove 110, the oil return hole 111, and the second oil supply pump.

[0094] Since the first connection groove 311 and the second connection groove 321 are staggered, when the valve core 300 rotates, when the first connection groove 311 is aligned with the first adjustment port 220, the second connection groove 321 and the second adjustment port 240 are necessarily staggered, and when the second connection groove 321 is aligned with the second adjustment port 240, the first connection groove 311 and the first adjustment port 220 are necessarily staggered. Therefore, when the first driving device 340 drives the valve core 300 to rotate, the oil inlet path and the oil return path can be alternately connected to achieve high-speed switching of the oil supply state and the oil return state, so that high-frequency oil can be supplied to the dynamic load chamber 580 to generate high-frequency vibration impact force.

[0095] The greater the amount of oil pumped into the dynamic load chamber 580 by the second oil supply pump each time, the greater the amplitude generated; the smaller the amount of oil pumped into the dynamic load chamber 580 by the second oil supply pump each time, the smaller the amplitude generated.

[0096] The aforementioned core shaft adjustment device 400 is used to drive the valve core 300 to move along its own axis to adjust the oil supply amount pumped into the dynamic load chamber 580 by the second oil supply pump.

[0097] When the valve core 300 moves along its own axis, the first adjustment port 220 slides on the first shoulder 310 and the second adjustment port 240 slides on the second shoulder 320 .

[0098] The valve core 300 can move to the right to put the vibration valve 30 in a fully open state with maximum oil supply, and the valve core 300 can move to the left to put the vibration valve 30 in a closed state. When the movement range of the valve core 300 is between the fully open state and the closed state, the oil supply can be adjusted.

[0099] Figure 7 The state of the vibration valve 30 shown in the figure is the fully open state with the maximum oil supply. The first regulating port 220 can be fully aligned with the first connecting groove 311. At this time, the first regulating port 220 and the first connecting groove 311 have the maximum overlapping area, thereby having the maximum oil return port 210 diameter. Similarly, the second regulating port 240 can be fully aligned with the second connecting groove 321. At this time, the second regulating port 240 and the second connecting groove 321 have the maximum overlapping area, thereby having the maximum oil inlet diameter.

[0100] exist Figure 8 The vibration valve 30 is in a closed state. No matter how the valve core 300 rotates, the first shoulder 310 always closes the first regulating port 220 , and the second shoulder 320 always closes the second regulating port 240 , and oil cannot be supplied to the dynamic load chamber 580 .

[0101] Fig. 9 A semi-open state between the fully open state and the closed state is shown, at which time a portion of the first adjustment port 220 is aligned with the first connecting groove 311 and the other portion is closed by the first shoulder 310. Similarly, at this time a portion of the second adjustment port 240 is aligned with the second connecting groove 321 and the other two portions are closed by the second shoulder 320.

[0102] Therefore, the spindle adjustment device 400 drives the valve core 300 to move along its own axis, so that the diameter of the oil inlet port and the diameter of the oil return port 210 change, so as to adjust the oil supply amount pumped into the dynamic load chamber 580 by the second oil supply pump.

[0103] Please refer to Figure 2 The spindle adjustment device 400 includes a second driving device 410 , an eccentric wheel 411 , and a driven wheel 420 .

[0104] The second driving device 410 includes a servo motor and a reducer, and the eccentric wheel 411 is connected to the output end of the reducer. The driven wheel 420 is connected to the valve core 300 through a bearing, and the two ends of the driven wheel 420 are respectively raised to form a first limit ring 421 and a second limit ring 422.

[0105] Therefore, the first limiting ring 421 and the second limiting ring 422 are coaxial with the valve core 300, and the rotation axis of the eccentric wheel 411 is perpendicular to the axis of the valve core 300. The eccentric wheel 411 is located between the first limiting ring 421 and the second limiting ring 422. When the eccentric wheel 411 rotates to contact the first limiting ring 421, the eccentric wheel 411 can push the first limiting ring 421 to the right to move the valve core 300 to the right. When the eccentric wheel 411 rotates to contact the second limiting ring 422, the eccentric wheel 411 can push the second limiting ring 422 to the left to move the valve core 300 to the left. The core shaft adjustment device 400 adjusts the vibration valve 30 between the fully open state and the closed state to adjust the force value of the vibration impact force.

[0106] The core shaft adjustment device 400 also includes a displacement meter 430, which is arranged at one end of the valve core 300 away from the first drive device 340 to measure the distance the valve core 300 moves along the axial direction, so as to obtain or observe the force value of the corresponding vibration impact force.

[0107] In this embodiment, the first driving device 340 is a servo motor. Figure 2 As shown, the output end of the servo motor is connected to the valve core 300 through a coupling 341. The coupling 341 includes a first connection part and a second connection part that can slide relative to each other in the axial direction, wherein the first connection part is connected to the output end of the servo motor, and the second connection part is connected to the valve core 300. A first flange is provided on the first connection part, and the first flange is connected to the first connection part through a key, so that the first flange can move axially on the first connection part, but cannot rotate relative to the first connection part; a second flange is provided on the second connection part, and the second flange is connected to the second connection part through a key, so that the second flange can move axially on the second connection part, but cannot rotate relative to the second connection part; the first flange and the second flange are fixedly connected.

[0108] The static pressure vibration system provided in the embodiment of the present application can simultaneously apply static load and vibration impact force to the test surface, so that the test surface can be subjected to high-frequency vibration impact force under static pressure conditions, thereby realizing the actual bearing capacity of the test soil under dynamic and static loads.

[0109] The above description is only 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 may have various modifications and variations. 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 static pressure vibration system, characterized in that: include: A hydraulic cylinder, wherein a static pressure chamber and a dynamic load chamber are formed in the hydraulic cylinder, the static pressure chamber is provided with a first piston rod, the dynamic load chamber is provided with a second piston rod, the first piston rod is used to output a static load to a test surface, the output end of the second piston rod is superimposed with the output end of the first piston rod, and the second piston rod is used to output a vibration impact force to the test surface; a first oil supply device, the first oil supply device being used to provide a stable oil pressure to the static pressure chamber; a second oil supply device, the second oil supply device being used to supply oil to the dynamic load chamber at a set frequency; The second oil supply device comprises a second oil supply pump for supplying oil to the dynamic load chamber, a vibration valve is provided on the connection passage between the second oil supply pump and the dynamic load chamber, and the vibration valve is used to control the oil supply according to a set frequency; The vibration valve comprises a valve body, a valve sleeve and a valve core, the valve sleeve is arranged in the valve body, and the valve core is rotatably arranged in the valve sleeve; an oil inlet hole, an oil return hole and an oil supply hole are formed on the valve body, the oil supply hole is connected to the dynamic load oil supply pipe of the dynamic load chamber, and the oil inlet hole and the oil return hole are used to respectively connect to the second oil supply pump; an oil return port, a first regulating port, an oil supply port and a second regulating port are sequentially arranged on the valve sleeve along the axial direction, the oil return port is connected to the oil return hole, the first regulating port and the oil supply port are respectively connected to the oil supply hole, and the second regulating port is connected to the oil inlet hole; a first shoulder and a second shoulder are formed on the valve core, the first shoulder corresponds to the first regulating port, the second shoulder corresponds to the second regulating port, a first connecting groove is formed on the circumference of the first shoulder, and a second connecting groove is formed on the circumference of the second shoulder, and the projections of the first connecting groove and the second connecting groove on the radial cross section of the valve core are staggered with each other; The valve core has an oil supply state and an oil return state. When the valve core is in the oil supply state, the first connecting groove is staggered with the first regulating port to close the first regulating port, and the second connecting groove is opposite to the second regulating port so that the second regulating port is connected to the oil supply port; when the valve core is in the oil return state, the first connecting groove is opposite to the first regulating port so that the first regulating port is connected to the oil return port, and the second connecting groove is staggered with the second regulating port to close the second regulating port; The static pressure chamber surrounds the dynamic load chamber, the first piston rod is in the shape of a cylinder with one end open to match the annular static pressure chamber, and the output end of the second piston rod is connected to the inner end surface of the first piston rod.

2. The static pressure vibration system according to claim 1, characterized in that: The hydraulic cylinder includes a first end plate, an outer cylinder and an inner cylinder coaxially mounted on the first end plate, the first end plate and the inner wall of the inner cylinder form the dynamic load chamber, the first end plate, the outer wall of the inner cylinder and the inner wall of the outer cylinder form the static pressure chamber; the first end plate is provided with a dynamic load oil supply pipe connecting the second oil supply device and the dynamic load chamber.

3. The static pressure vibration system according to claim 2, characterized in that: The outer wall of the inner cylinder is formed with a flange extending in the radial direction, and the flange extends to the inner wall of the outer cylinder and fits with the first end plate; the oil inlet and outlet of the static pressure chamber penetrates the outer cylinder and is located between the flange and the first piston rod.

4. The static pressure vibration system according to claim 1, characterized in that: The first oil supply device comprises a first oil supply pump for supplying oil to the static pressure chamber, and a proportional valve is provided on the connection passage between the first oil supply pump and the static pressure chamber.

5. The static pressure vibration system according to claim 4, characterized in that: The valve body is formed with a first annular groove, a second annular groove and a third annular groove respectively surrounding the valve sleeve, the first annular groove is communicated with the oil return hole, the second annular groove is communicated with the oil supply hole, and the third annular groove is communicated with the oil inlet hole; The valve sleeve comprises a plurality of oil return ports, a plurality of first regulating ports, a plurality of oil supply ports and a plurality of second regulating ports, wherein the plurality of oil return ports, the plurality of first regulating ports, the plurality of oil supply ports and the plurality of second regulating ports are respectively arranged around the circumference of the valve sleeve; The plurality of oil return ports are located within the surrounding range of the first annular groove, the plurality of first regulating ports and the plurality of oil supply ports are located within the surrounding range of the second annular groove, and the plurality of second regulating ports are located within the surrounding range of the third annular groove; The first connecting groove includes a plurality of grooves arranged around the first shoulder, and the second connecting groove includes a plurality of grooves arranged around the second shoulder.

6. The static pressure vibration system according to claim 5, characterized in that: The two ends of the valve core respectively pass through the valve body and form a dynamic seal with the valve body. One end of the valve core is connected to a first driving device, which is used to drive the valve core to rotate to switch between an oil supply state and an oil return state. The other end of the valve core is connected to a core shaft adjustment device, which is used to drive the valve core to move along its own axis so that the first adjustment port slides on the first shoulder and the second adjustment port slides on the second shoulder, thereby adjusting the overlapping area between the first adjustment port and the first connecting groove and the overlapping area between the second adjustment port and the second connecting groove.

7. The static pressure vibration system according to claim 6, characterized in that: The output end of the first driving device is connected to one end of the valve core through a coupling, and the coupling includes a first connecting part and a second connecting part that can slide relative to each other in the axial direction.

8. The static pressure vibration system according to claim 6, characterized in that: The core shaft adjustment device includes a second driving device, an eccentric wheel, a first limiting ring and a second limiting ring. The eccentric wheel is connected to the output end of the second driving device. The first limiting ring and the second limiting ring are formed on the valve core. The eccentric wheel is located between the first limiting ring and the second limiting ring. The eccentric wheel cooperates with the first limiting ring and the second limiting ring to enable the valve core to move along its own axis.

9. The static pressure vibration system according to claim 6, characterized in that: The core shaft adjustment device comprises a displacement meter, and the valve core is connected to the displacement meter.

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