A high frequency breaking hammer with anti-pumping of gear oil

Abstract

This invention relates to the field of high-frequency hydraulic breakers, specifically to a high-frequency hydraulic breaker designed to prevent gear oil cavitation. The breaker includes a vibratory chamber, a circulating pump, and an anti-cavitation valve, which form a gear oil cooling circuit. The anti-cavitation valve controls the connection between its inlet and outlet according to the operating direction of the high-frequency hydraulic breaker. It connects the inlet to the outlet connected to the oil suction port below the gear oil surface in the vibratory chamber, and disconnects the inlet to the outlet connected to the oil suction port above the gear oil surface in the vibratory chamber. With the anti-cavitation valve of this invention, the high-frequency hydraulic breaker can perform upward, horizontal, downward, or vertical striking operations. Regardless of the operating posture, the gear oil in the vibratory chamber can enter the circulating pump for cooling and reflux. The operating posture of the high-frequency hydraulic breaker is no longer restricted, allowing for multi-angle striking and significantly expanding its applicability.

Description

Technical Field

[0001] This invention relates to the field of high-frequency hydraulic breakers, and specifically to a high-frequency hydraulic breaker that prevents gear oil from being sucked into the air. Background Technology

[0002] High-frequency hydraulic breakers typically consist of a shock absorber box, a vibratory chamber, and cutting tools. Their working principle involves a hydraulic motor within the vibratory chamber driving an eccentric block to rotate, generating a vibration force. This force causes the vibratory chamber to reciprocate, which in turn drives the cutting tools to strike the rock, achieving rock breaking. The applicant discovered that during prolonged use, the vibratory chamber generates significant heat due to the meshing of its internal gears. Simultaneously, the eccentric gears, operating at high speed, impact the gear oil, also generating considerable heat. If this heat raises the gear oil temperature to over 100°C, and the oil is not promptly drained from the suction port for cooling, it severely impacts lubrication, reducing the lifespan of gears and bearings. Over time, this can lead to damage or even complete failure of the entire equipment. Therefore, it is necessary to use gear oil to dissipate the heat from the vibratory chamber.

[0003] Currently, high-frequency hydraulic breakers are typically used on the ground, such as... Figure 1 As shown, in ground construction, high-frequency hydraulic breakers usually operate vertically downwards. Due to gravity, the gear oil in the vibratory box accumulates at the end near the cutter. The circulating pump can draw the gear oil out of the vibratory box through the oil suction port to dissipate heat, and then pump the cooled gear oil back into the vibratory box through the oil return port to continue lubricating and cooling the gears and bearings inside the vibratory box.

[0004] The applicant first proposed the application of high-frequency hydraulic breakers in tunnel excavation construction in Chinese invention patent application CN202210229404.2. However, in subsequent use, it was discovered that when using high-frequency hydraulic breakers for tunnel excavation, the breakers need to be operated horizontally or slightly tilted upwards. This raises a new problem, such as... Figure 2 As shown, for example, when using a high-frequency hydraulic breaker to excavate tunnels at an upward angle or to address under-excavation above a tunnel, the gear oil in the vibratory breaker box will flow to the end furthest from the cutter due to gravity. This causes the oil suction port near the cutter to be higher than the gear oil level, preventing gear oil from entering the suction port and causing the circulating pump to draw in air. The circulating pump is lubricated by the gear oil flowing through it. Because the suction port of the circulating pump is higher than the gear oil level during upward excavation, the gear oil does not flow through the pump. Prolonged idling without gear oil lubrication can lead to overheating and burnout of the circulating pump. Simultaneously, the gear oil used for cooling the circulation cannot pass through the return pipe, preventing the high-temperature gear oil in the vibratory breaker box from draining. The bearings and gears of the eccentric wheel inside the vibratory breaker box will not be cooled, leading to prolonged high temperatures that can cause equipment shutdown and, in severe cases, damage due to overheating, thus affecting the excavation efficiency of the high-frequency hydraulic breaker. Summary of the Invention

[0005] In view of this, the present invention provides a high-frequency hydraulic breaker that prevents gear oil from being sucked into the vent, aiming to solve the problem of high temperature caused by the inability of gear oil in the excitation box to enter the circulation pump when the existing high-frequency hydraulic breaker is tilted during construction, such as in a tunnel. This allows the high-frequency hydraulic breaker to have more impact angles and improves its applicability.

[0006] To solve the above technical problems, the technical solution adopted by the present invention is as follows:

[0007] A high-frequency hydraulic breaker for preventing gear oil cavitation includes a vibration chamber and a circulating pump. The vibration chamber is provided with an oil suction port and an oil return port. The circulating pump draws out the gear oil inside the vibration chamber through the oil suction port to dissipate heat, and pumps the dissipated gear oil back to the vibration chamber through the oil return port. There are N oil suction ports, with at least one oil suction port at each end along the vibration direction on the vibration chamber. The breaker also includes an anti-cavitation valve. The anti-cavitation valve has at least one outlet and N inlets. The outlet is connected to the oil return port through the circulating pump. Each inlet is connected to a corresponding oil suction port. The anti-cavitation valve controls the connection between the inlets and the outlet according to the construction direction of the high-frequency hydraulic breaker, ensuring that the inlet connected to the oil suction port below the gear oil surface in the vibration chamber is connected to the outlet, and that the inlet connected to the oil suction port above the gear oil surface in the vibration chamber is not connected to the outlet. Wherein, N is an integer ≥ 2.

[0008] In some embodiments, when N=2, the anti-vacuum valve has an inlet passage and an outlet passage that are interconnected, and the inlet passage is provided with a movable valve core; the two suction ports are respectively connected to the openings at both ends of the inlet passage; the outlet is connected to the outlet passage.

[0009] In some embodiments, the anti-air suction valve body has an oil outlet passage and N oil inlet passages, and each oil inlet passage is provided with a movable valve core; the oil inlet passages are spaced apart from each other, and each oil inlet passage is connected to the oil outlet passage; the inlet is connected to each of the oil inlet passages in a one-to-one correspondence; the outlet is connected to the oil outlet passage.

[0010] In some embodiments, the connection between the oil outlet passage and the oil inlet passage is located at a non-end portion of the oil inlet passage, so that the valve core will not block the connection between the oil outlet passage and the oil inlet passage when the oil outlet passage and the oil inlet passage are connected.

[0011] In some embodiments, the distance between the connection point of the oil outlet passage and the oil inlet passage and the end of the oil inlet passage is greater than or equal to the width of the valve core.

[0012] In some embodiments, the width of the oil outlet passage is less than the width of the valve core; or, the width of the connection between the oil outlet passage and the oil inlet passage is less than the width of the valve core.

[0013] In some embodiments, the cross-section of the oil inlet passage is circular; the valve core is a ball.

[0014] In some embodiments, a shock absorber box is also included; the excitation box is disposed inside the shock absorber box; and the anti-air suction valve is installed on the shock absorber box.

[0015] In some embodiments, the oil inlet passage in the anti-air suction valve is a straight channel, and the length direction of the oil inlet passage is parallel to the excitation direction of the excitation box.

[0016] In some embodiments, the anti-air suction valve includes an electrically controlled automatic valve and a tilt sensor; the electrically controlled automatic valve has at least one oil outlet channel and N oil inlet channels that can be individually controlled to open or close, and all the oil inlet channels are connected to the oil outlet channel; each inlet is connected to one of the oil inlet channels; the outlet is connected to the oil outlet channel; the tilt sensor is electrically connected to the electrically controlled automatic valve; the tilt sensor is used to detect the construction direction of the high-frequency breaker and feeds back to the electrically controlled automatic valve to control the opening and closing of each inlet.

[0017] In summary, compared with the prior art, the present invention has the following advantages and beneficial effects: After adopting the anti-air suction valve described in the present invention, the high-frequency breaker can perform impact operations at an upward tilt, at a horizontal angle, or at an downward tilt or vertical angle. Regardless of the orientation of the high-frequency breaker, the gear oil in its excitation box can enter the circulating pump for cooling and return. The operating orientation of the high-frequency breaker is no longer restricted, and it can perform multi-angle impacts, greatly expanding its applicability. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the structure of an existing high-frequency hydraulic breaker during vertical construction.

[0019] Figure 2 This is a schematic diagram of the structure of an existing high-frequency hydraulic breaker when operating at an upward incline.

[0020] Figure 3 This is a schematic diagram of the high-frequency hydraulic breaker described in Embodiment 1 of the present invention during upward inclined construction.

[0021] Figure 4 This is a schematic diagram of the high-frequency hydraulic breaker described in Embodiment 1 of the present invention during horizontal construction.

[0022] Figure 5 This is a schematic diagram of the high-frequency hydraulic breaker described in Embodiment 1 of the present invention during downward inclined construction.

[0023] Figure 6 This is a schematic diagram of the anti-air suction valve in the high-frequency hydraulic breaker according to Embodiment 1 of the present invention.

[0024] Figure 7 This is a schematic diagram of the high-frequency hydraulic breaker described in Embodiment 2 of the present invention during upward inclined construction.

[0025] Figure 8 This is a schematic diagram of the high-frequency hydraulic breaker described in Embodiment 2 of the present invention during horizontal construction.

[0026] Figure 9 This is a schematic diagram of the high-frequency hydraulic breaker described in Embodiment 2 of the present invention during downward inclined construction.

[0027] Figure 10 This is a schematic diagram of the anti-air suction valve in the high-frequency hydraulic breaker according to Embodiment 2 of the present invention.

[0028] The labels in the diagram are as follows: 1. Vibration box; 2. Shock absorber; 3. Gear oil; 4. Cutting tool; 5. Inherent oil suction port; 6. Oil suction pipe; 7. Circulating pump; 8. Oil return pipe; 9. Oil return port; 10. Anti-air suction valve; 101. Oil inlet passage; 102. Valve core; 103. Oil outlet passage; 11. Additional oil suction port; 12. First additional oil suction pipe; 13. Second additional oil suction pipe. Detailed Implementation

[0029] To enable those skilled in the art to better understand the technical solution of the present invention, the present invention will be further described in detail below with reference to specific embodiments.

[0030] In the description of this invention, it should be understood that the orientation descriptions, such as up, down, front, back, left, right, etc., are based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting this invention.

[0031] In the description of this invention, "several" means one or more, "multiple" means two or more, "greater than," "less than," "exceeding," etc. are understood to exclude the stated number, while "above," "below," "within," etc. are understood to include the stated number. If terms such as "first," "second," etc., are used only to distinguish technical features and should not be construed as indicating or implying relative importance, or implicitly indicating the number of indicated technical features, or implicitly indicating the order of the indicated technical features.

[0032] In the description of this invention, unless otherwise explicitly defined, terms such as "setting," "installing," and "connecting" should be interpreted broadly, and those skilled in the art can reasonably determine the specific meaning of the above terms in this invention in conjunction with the specific content of the technical solution.

[0033] Example 1

[0034] This application provides a high-frequency hydraulic breaker that prevents gear oil from sucking into the air, such as... Figures 3-5 As shown, the high-frequency hydraulic breaker includes an excitation box 1, a shock absorber box 2, a circulating pump 7, and an anti-air suction valve 10.

[0035] Among them, such as Figure 6 As shown, the anti-vacuum valve 10 described in this embodiment has two inlets and one outlet, and the anti-vacuum valve 10 body has an oil outlet passage 103 and an oil inlet control mechanism.

[0036] The oil inlet control mechanism includes an oil inlet passage 101 and a valve core 102 placed within the oil inlet passage 101 and freely movable within it. The oil outlet passage 103 is connected to the oil inlet passage 101, and the connection point between the oil outlet passage 103 and the oil inlet passage 101 is preferably located at a non-end portion of the oil inlet passage 101, so that the valve core 102 does not block the connection point when the oil outlet passage 103 is connected to the oil inlet passage 101.

[0037] The two inlets are respectively connected to the openings at both ends of the oil inlet passage 101, and the outlet is connected to the oil outlet passage 103.

[0038] like Figures 3-5 As shown, a portion of the excitation box 1 is installed inside the damping box 2, and one end of the excitation box 1 is connected to a cutting tool 4 extending outside the damping box 2. The excitation box 1 has a fixed oil suction port 5 and an oil return port 9 at its two ends along its excitation direction. For example, the fixed oil suction port 5 is located at the end of the excitation box 1 closer to the cutting tool 4, and the oil return port 9 is located at the end of the excitation box 1 away from the cutting tool 4. Furthermore, the end of the excitation box 1 away from the fixed oil suction port 5 also has an additional oil suction port 11, which, corresponding to the aforementioned description, is located at the end of the excitation box 1 away from the cutting tool 4.

[0039] The inherent oil suction port 5 and the auxiliary oil suction port 11 are respectively connected to the two inlets of the anti-vacuum valve 10 through the first auxiliary oil suction pipe 12 and the second auxiliary oil suction pipe 13. The suction port of the circulating pump 7 is connected to the outlet of the anti-vacuum valve 10 through the oil suction pipe 6, and the discharge port of the circulating pump 7 is connected to the return oil port 9 on the vibration box 1 through the return oil pipe 8.

[0040] like Figure 3 As shown, when the high-frequency hydraulic breaker strikes upwards at an angle, the gear oil 3 in the vibratory chamber 1 accumulates at the rear end of the vibratory chamber 1 (i.e., the end furthest from the cutter 4) due to gravity. At this time, the inherent oil suction port 5 cannot draw oil because it is higher than the surface of the gear oil 3, while the auxiliary oil suction port 11 is located below the surface of the gear oil 3 and can draw gear oil 3 normally. The circulating pump 7 continuously generates suction force through the suction pipe 6 to the anti-air suction valve 10. In the anti-air suction valve 10, one inlet draws air or gas from the inherent oil suction port 5 through the first auxiliary oil suction pipe 12. The air drawn in through this inlet exerts a small pressure on the valve core 102 in the oil inlet passage 101. The other inlet draws gear oil 3 from the auxiliary oil suction port 11 through the second auxiliary oil suction pipe 13. The gear oil 3 drawn in through this inlet exerts a larger pressure on the valve core 102 in the oil inlet passage 101. At this time, the valve core 102 will be pushed by the pressure difference on both sides to pass over the connection between the oil outlet passage 103 and the oil inlet passage 101 and move towards the inlet connected to the first auxiliary oil suction pipe 12 and block this inlet to prevent the continued suction of air from the inherent oil suction port 5. The gear oil 3 will enter the oil outlet passage 103 and finally enter the circulation pump 7. The circulation pump 7 will then pump the gear oil 3 back to the return port 9 of the vibration box 1.

[0041] like Figure 4 As shown, when the high-frequency hydraulic breaker performs a horizontal strike, the gear oil 3 in the vibratory chamber 1 accumulates due to gravity at the bottom of the vibratory chamber 1 along the direction of gravity. At this time, the gear oil 3 can be simultaneously drawn into the anti-vacuum valve 10 through both the inherent oil suction port 5 and the auxiliary oil suction port 11. In the oil inlet passage 101, since the pressure on both sides of the valve core 102 is basically the same, the valve core 102 may be in any position in the oil inlet passage 101 after the force is balanced. Furthermore, due to the large vibration of the high-frequency hydraulic breaker during the strike, the position of the valve core 102 will also be affected at all times, preventing it from always being in a certain position in the oil inlet passage 101. This allows the gear oil 3 to smoothly enter the circulating pump 7 from the connection between the oil outlet passage 103 and the oil inlet passage 101 and be pumped back to the return port 9 of the vibratory chamber 1.

[0042] like Figure 5As shown, when the high-frequency hydraulic breaker strikes downwards at an angle, the gear oil 3 in the vibratory chamber 1 accumulates at the front end of the vibratory chamber 1 (i.e., the end closest to the cutter 4) due to gravity. At this time, the auxiliary oil suction port 11 cannot draw oil because it is higher than the surface of the gear oil 3, while the inherent oil suction port 5 can draw gear oil 3 normally. This situation is similar to... Figure 3 The corresponding situation is the opposite: one inlet of the anti-air suction valve 10 draws in air or gas from the auxiliary suction port 11 through the second auxiliary suction pipe 13. The air drawn in through this inlet exerts a small pressure on the valve core 102 in the oil inlet passage 101. The other inlet draws in gear oil 3 from the inherent suction port 5 through the first auxiliary suction pipe 12. The gear oil 3 drawn in through this inlet exerts a large pressure on the valve core 102 in the oil inlet passage 101. At this time, the valve core 102 will be pushed by the pressure difference on both sides past the connection between the oil outlet passage 103 and the oil inlet passage 101 and move towards the inlet connected to the second auxiliary suction pipe 13, blocking this inlet to prevent further air suction or gas intake from the auxiliary suction port 11. The gear oil 3 will then smoothly enter the oil outlet passage 103 and finally enter the circulation pump 7, which will then pump the gear oil 3 back to the return port 9 of the vibration box 1. Obviously, when the high-frequency breaker strikes vertically downwards, the situation is the same as when it strikes obliquely downwards.

[0043] As can be seen, after adopting the anti-air suction valve 10 described in the embodiments of this application, the high-frequency breaker can perform upward, horizontal, downward or vertical strike operations. Regardless of the orientation of the high-frequency breaker, the gear oil 3 in its excitation box 1 can enter the circulation pump 7 for cooling and recirculation. The operating orientation of the high-frequency breaker is no longer restricted, and it can perform multi-angle strikes, greatly expanding its applicability.

[0044] As an optional implementation, both the inherent oil suction port 5 and the auxiliary oil suction port 11 are located on the side of the vibrating chamber 1 perpendicular to the excitation direction of the vibrating chamber 1, downwards along the direction of gravity. This arrangement ensures that even if the amount of gear oil 3 in the vibrating chamber 1 is relatively small, it can still be drawn into the anti-air suction valve 10 and the circulating pump 7 for cooling and return, through the inherent oil suction port 5 and the auxiliary oil suction port 11 located downwards along the direction of gravity. Additionally, the return oil port 9 can be located on the side of the vibrating chamber 1 perpendicular to the excitation direction of the vibrating chamber 1, upwards along the direction of gravity, so that cooling oil flows from top to bottom through the bearings and gears inside the vibrating chamber 1. The return oil port 9 can also be located at the bearing end cover on the vibrating chamber 1, allowing cooled gear oil to enter the bearing from the bearing end cover, thereby cooling and lubricating the bearing.

[0045] The anti-vacuum valve 10 can also be directly installed on the shock absorber 2, so that it moves together with the shock absorber 2. Especially when the oil inlet passage 101 in the anti-vacuum valve 10 is a straight channel, and the length direction of the oil inlet passage 101 is parallel to the excitation direction of the vibration box 1, the valve core 102 inside the oil inlet passage 101 will also be accelerated by its own gravity, from... Figure 3 and Figure 5 As can be seen, the valve core 102 is located at the lower end of the oil inlet passage 101. This is not only related to the specific connection positions of the first auxiliary oil suction pipe 12 and the second auxiliary oil suction pipe 13 with the two inlets of the anti-air suction valve 10, but also because this connection method can maximize the use of the gravity of the valve core 102 itself.

[0046] It should be noted that, to facilitate the assembly of the valve core 102, the oil inlet passage 101 can be designed as a hole of equal width, allowing the valve core 102 to be directly inserted through the open end of the oil inlet passage 101. In this case, to prevent the valve core 102 from detaching from the oil inlet passage 101, the first auxiliary suction pipe 12 and the second auxiliary suction pipe 13 can be connected to the inlet of the anti-vacuum valve 10 using interfaces with internal channel dimensions smaller than the width of the valve core 102. Alternatively, the end of the oil inlet passage 101 can be designed to be slightly smaller than the width of the valve core 102, and the anti-vacuum valve 10 can be designed as a modular, modular structure.

[0047] In the anti-air suction valve 10, to prevent the valve core 102 from entering the oil outlet passage 103, the width of the oil outlet passage 103 can be designed to be less than the width of the valve core 102. Alternatively, the width of the connection between the oil outlet passage 103 and the oil inlet passage 101 can be designed to be less than the width of the valve core 102, while keeping the width of the oil outlet passage 103 unchanged.

[0048] Correspondingly, to prevent the valve core 102 from blocking the connection between the oil outlet passage 103 and the oil inlet passage 101, thus preventing the gear oil 3 from entering the oil outlet passage 103, the distance between the connection between the oil outlet passage 103 and the oil inlet passage 101 and the end of the oil inlet passage 101 can be designed to be greater than or equal to the width of the valve core 102. In this way, when the valve core 102 moves within the oil inlet passage 101 due to the pressure difference, it can completely avoid the connection between the oil outlet passage 103 and the oil inlet passage 101, thereby allowing the gear oil 3 to smoothly enter the oil outlet passage 103.

[0049] As an optional implementation, the cross-section of the oil inlet passage 101 can be designed as a circle, and the valve core 102 can be designed as a sphere. This structure not only facilitates processing but also facilitates the movement of the valve core 102 within the oil inlet passage 101. Obviously, the cross-section of the oil inlet passage 101 can be designed as a polygon, such as the common rectangle, and correspondingly, the valve core 102 can also be designed as a right-angled quadrangular prism.

[0050] Example 2

[0051] like Figures 7-10 As shown, the only difference between this embodiment and Embodiment 1 is that the structure of the anti-air suction valve 10 is not exactly the same.

[0052] like Figure 10 As shown, in this embodiment of the application, the anti-air suction valve 10 still has an oil outlet passage 103, two inlets and one outlet. The main difference is that the anti-air suction valve 10 in this embodiment of the application has two oil inlet control mechanisms. The two oil inlet passages 101 in the two oil inlet control mechanisms are spaced apart from each other, and the two inlets are respectively connected to the opening ends of the two oil inlet passages 101 one by one. The oil outlet passage 103 is simultaneously connected to the two oil inlet passages 101.

[0053] Here, the two valve cores 102 in the two oil inlet passages 101 each move within their respective oil inlet passages 101. The connection between the oil outlet passage 103 and each oil inlet passage 101 is located at a non-end point of that oil inlet passage 101, so that the valve core 102 will not block the connection. The two inlets of the anti-vacuum valve 10 are still connected to the inherent oil suction port 5 and the auxiliary oil suction port 11 respectively through the first auxiliary oil suction pipe 12 and the second auxiliary oil suction pipe 13. The connection methods of other components are the same as in Embodiment 1, and will not be described again here for the sake of brevity.

[0054] like Figure 7 As shown, when the high-frequency hydraulic breaker strikes upwards at an angle, the gear oil 3 in the vibratory chamber 1 accumulates at the rear end of the vibratory chamber 1 (i.e., the end furthest from the cutter 4) due to gravity. At this time, the inherent oil suction port 5 cannot draw oil because it is higher than the surface of the gear oil 3, while the auxiliary oil suction port 11, located below the surface of the gear oil 3, can draw gear oil 3 normally. The circulating pump 7 continuously generates suction force through the oil suction pipe 6 to the anti-air suction valve 10.

[0055] In the anti-air suction valve 10, the inlet corresponding to one of the oil inlet passages 101 sucks air or gas from the inherent oil suction port 5 through the first additional oil suction pipe 12. The air sucked in from this inlet generates a small pressure on the valve core 102 in the oil inlet passage 101.

[0056] The other inlet of oil passage 101 draws gear oil 3 from the auxiliary suction port 11 through the second auxiliary suction pipe 13. The gear oil 3 drawn in through this inlet exerts a large pressure on the valve core 102 in this oil inlet passage 101, pushing the valve core 102 past the connection between this oil inlet passage 101 and the oil outlet passage 103 and moving away from the inlet. At this time, the gear oil 3 enters the oil outlet passage 103 and finally enters the circulation pump 7, which then pumps the gear oil 3 back to the return port 9 of the vibrating box 1.

[0057] At the same time, some of the gear oil 3 in the oil outlet passage 103 will also enter the oil inlet passage 101 that sucks in air or gas, and further push the valve core 102 in this oil inlet passage 101 to move toward the corresponding inlet to block the inlet, so as to prevent air from being sucked in or gas from being drawn in.

[0058] When the anti-vacuum valve 10 is directly installed on the shock absorber 2, and when the oil inlet passage 101 in the anti-vacuum valve 10 is a straight channel, and the length direction of the oil inlet passage 101 is parallel to the excitation direction of the vibration box 1, the valve core 102 in the oil inlet passage 101 will also be accelerated by its own gravity, from Figure 7 As can be seen, the valve core 102 is located at the lower end of its corresponding oil inlet passage 101. This is not only related to the specific connection positions of the first and second auxiliary oil suction pipes 12 and 13 with the two inlets of the anti-vacuum valve 10, but also because this connection method can maximize the use of the valve core 102's own gravity. Especially in the oil inlet passage 101 that sucks in air or cavitation, on the one hand, the valve core 102 moves towards the inlet end due to its own gravity; on the other hand, the pressure generated by the gear oil 3 entering from the oil outlet passage 103 on the valve core 102 can further push the valve core 102 towards the inlet end, thereby ensuring that this oil inlet passage 101 will no longer suck in air or cavitation.

[0059] like Figure 8 As shown, when the high-frequency hydraulic breaker performs a horizontal strike, the gear oil 3 in the vibratory chamber 1 accumulates due to gravity at the bottom of the vibratory chamber 1 along the direction of gravity. At this time, the gear oil 3 can be simultaneously drawn into the anti-vacuum valve 10 through the inherent oil inlet 5 and the auxiliary oil inlet 11. In the anti-vacuum valve 10, since both oil inlet passages 101 can draw in gear oil 3, the valve cores 102 in both oil inlet passages 101 will move away from the inlet under the push of the gear oil 3, thereby opening the connection between the oil outlet passage 103 and the oil inlet passage 101 so that the gear oil 3 can enter the oil outlet passage 103, and then enter the circulation pump 7 and be pumped back to the return oil port 9 of the vibratory chamber 1.

[0060] like Figure 9As shown, when the high-frequency hydraulic breaker strikes downwards at an angle, the situation is similar to... Figure 7 The situation is reversed, but the principle is the same, so I won't go into detail again. Obviously, when the high-frequency hydraulic breaker strikes vertically downwards, the situation is the same as when it strikes at an angle downwards.

[0061] As can be seen, after adopting the anti-air suction valve 10 described in the embodiments of this application, the high-frequency breaker can also perform upward tilting strikes, horizontal strikes, downward tilting strikes, or vertical strikes. Regardless of the orientation of the high-frequency breaker, the gear oil 3 in its vibration box 1 can enter the circulation pump 7 for cooling and recirculation. The operating orientation of the high-frequency breaker is no longer restricted, and it can perform multi-angle strikes, greatly expanding its applicability.

[0062] The two embodiments described above only illustrate the case where there is only one additional oil suction port 11 on the vibration box 1. However, it is obvious that multiple additional oil suction ports 11 can be provided on the vibration box 1. For ease of description, the inherent oil suction port 5 and the additional oil suction port 11 are collectively referred to as oil suction ports, since they are both for drawing gear oil from the vibration box 1. Therefore, N oil suction ports can be provided on the vibration box 1. These oil suction ports are distributed around the vibration box 1, and at least two of these oil suction ports are located at both ends of the vibration box 1 along the excitation direction, that is, each end of the vibration box 1 along the excitation direction has one oil suction port. This ensures that when the high-frequency breaker is striking at any angle, at least one additional oil suction port 11 is located below the gear oil level in the vibration box 1 to ensure that gear oil can be drawn in. Here, N is an integer ≥ 2.

[0063] Based on Embodiment 2, at least N independent oil inlet control mechanisms can be installed within the anti-vacuum valve 10 as needed (multiple oil inlet control mechanisms can be temporarily closed and not used). This means the anti-vacuum valve 10 also has at least N inlets. Furthermore, the anti-vacuum valve 10 can be designed with more than one outlet, as long as they all ultimately converge into the circulating pump 7.

[0064] The oil inlet passages 101 in these oil inlet control mechanisms are all spaced apart from each other, and each of these inlets is connected to the oil suction port of the vibration box 1. In this way, for each oil suction port, there is an oil inlet control mechanism to prevent it from sucking in air. Its working principle is similar to that of Embodiment 2, and will not be described again here.

[0065] In addition to the mechanical structure described in Embodiments 1 and 2, the anti-air suction valve 10 can also be an electrically controlled self-regulating valve, such as an electric valve or a pneumatic valve. For example, this electrically controlled self-regulating valve has at least one oil outlet channel and N oil inlet channels that can be individually controlled to open and close, and all the oil inlet channels are connected to the oil outlet channel; each inlet is connected to one of the oil inlet channels; and the outlet is connected to the oil outlet channel. It can also be equipped with, for example, a tilt sensor to detect the attitude of the high-frequency breaker in real time, and the tilt sensor is electrically connected to the electrically controlled self-regulating valve. The tilt sensor is used to detect the construction direction of the high-frequency breaker and feeds back to the electrically controlled self-regulating valve to control the opening and closing of each inlet.

[0066] Multiple electrically controlled automatic valves can also be set to connect one-to-one with the inherent oil suction port 5 and the additional oil suction port 1. The excitation direction of the excitation box 1 is detected by the tilt sensor. Finally, the electrically controlled automatic valve connected to the inlet located below the gear oil surface in the excitation box 1 is controlled to be in the open state, and the electrically controlled automatic valve connected to the inlet located below the gear oil surface in the excitation box 1 is controlled to be in the closed state.

[0067] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0068] The above preferred embodiments should not be considered as limitations on the present invention, and the scope of protection of the present invention should be determined by the scope defined in the claims. For those skilled in the art, various improvements and modifications can be made without departing from the spirit and scope of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A high-frequency hydraulic breaker for preventing gear oil from cavitating, comprising a vibratory chamber (1) and a circulating pump (7); the vibratory chamber (1) is provided with an oil suction port and an oil return port (9); the circulating pump (7) draws out the gear oil inside the vibratory chamber (1) through the oil suction port to dissipate heat, and pumps the cooled gear oil back to the vibratory chamber (1) through the oil return port (9); characterized in that: The oil suction port is provided with N, and at least one oil suction port is provided at each end along the excitation direction on the excitation box (1); It also includes an anti-vacuum valve (10); the anti-vacuum valve (10) has an oil inlet passage (101) and an oil outlet passage (103) that are interconnected, and the oil inlet passage (101) is provided with a valve core (102) that can move freely within the oil inlet passage (101); the anti-vacuum valve (10) has at least one outlet and N inlets; the outlet is connected to the return oil port (9) through the circulating pump (7), and the outlet is connected to the oil outlet passage (103); the inlets are respectively connected to the oil suction port one by one, and the inlets are connected to the oil inlet passage (101); The anti-air suction valve (10) controls the connection between the inlet and the outlet according to the construction direction of the high-frequency breaker. When the high-frequency breaker strikes upward or downward, the valve core (102) in the oil inlet passage (101) moves toward the inlet connected to the oil suction port above the gear oil surface in the excitation box (1) and passes the connection between the oil inlet passage (101) and the oil outlet passage (103), so that the inlet connected to the oil suction port below the gear oil surface in the excitation box (1) is connected to the outlet, and the inlet connected to the oil suction port above the gear oil surface in the excitation box (1) is not connected to the outlet. Where N is an integer ≥ 2.

2. The high-frequency hydraulic breaker for preventing gear oil from cavitating as described in claim 1, characterized in that: When N=2, the anti-air suction valve (10) has an oil inlet passage (101), and the two inlets are respectively connected to the openings at both ends of the oil inlet passage (101). The two oil suction ports are respectively connected to the two inlets.

3. The high-frequency hydraulic breaker for preventing gear oil from cavitating as described in claim 1, characterized in that: The anti-air suction valve (10) has N oil inlet passages (101), and each oil inlet passage (101) is provided with a valve core (102) that can move freely within the oil inlet passage (101). The oil inlet passages (101) are spaced apart from each other; Each of the inlets is connected to the oil inlet passage (101) in a one-to-one correspondence.

4. A high-frequency hydraulic breaker for preventing gear oil from sucking into air, as described in claim 2 or 3, characterized in that: The connection between the oil outlet passage (103) and the oil inlet passage (101) is located at the non-end of the oil inlet passage (101) so that when the oil outlet passage (103) and the oil inlet passage (101) are connected, the valve core (102) will not block the connection between the oil outlet passage (103) and the oil inlet passage (101).

5. A high-frequency hydraulic breaker for preventing gear oil from cavitating, as described in claim 4, characterized in that: The distance between the connection point of the oil outlet passage (103) and the oil inlet passage (101) and the end of the oil inlet passage (101) is greater than or equal to the width of the valve core (102).

6. A high-frequency hydraulic breaker for preventing gear oil from cavitating, as described in claim 2 or 3, characterized in that: The width of the oil outlet passage (103) is less than the width of the valve core (102); or, the width of the connection between the oil outlet passage (103) and the oil inlet passage (101) is less than the width of the valve core (102).

7. A high-frequency hydraulic breaker for preventing gear oil from cavitating, as described in claim 2 or 3, characterized in that: The cross-section of the oil inlet passage (101) is circular; the valve core (102) is a sphere.

8. A high-frequency hydraulic breaker for preventing gear oil from sucking into air, as described in claim 2 or 3, characterized in that: It also includes a shock absorber box (2); the excitation box (1) is located inside the shock absorber box (2); the anti-air suction valve (10) is installed on the shock absorber box (2).

9. A high-frequency hydraulic breaker for preventing gear oil from cavitating, as described in claim 8, characterized in that: The oil inlet passage (101) in the anti-air suction valve (10) is a straight passage, and the length direction of the oil inlet passage (101) is parallel to the excitation direction of the excitation box (1).

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