High-energy impact hydraulic system

Abstract

The utility model discloses a high-energy impact hydraulic system, belongs to the technical field of hydraulic pressure, and solves the problem of how to improve impact force and impact frequency of an existing breaking hammer. The hydraulic system comprises a striking piston and further comprises an energy accumulator and a reversing control valve, an oil port P of the reversing control valve is communicated with a system hydraulic oil supply path through an oil inlet main path, an oil port T of the reversing control valve is communicated with a system hydraulic oil return path through an oil return main path, an oil port A of the reversing control valve is communicated with a large cavity through a first oil path, and an oil port B of the reversing control valve is communicated with a second oil path. An oil port B of the reversing control valve is communicated with the end b of the two-position three-way pilot valve through a second oil way, the small cavity is communicated with the oil inlet main way through a third oil way, and the third oil way is further communicated with the end b of the two-position three-way pilot valve through a fourth oil way. According to the hydraulic system disclosed by the utility model, the striking piston has strong impact force and high-frequency resetting capability, and the cost is effectively reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of hydraulics, and more specifically, to a high-energy impact hydraulic system. Background Art

[0002] Demolition, that is, breaking and removing, is a typical and professional construction method. Under general working conditions, a hydraulic excavator equipped with a traditional breaker can perform demolition operations. However, under harsh working conditions, especially when demolishing hard objects in a narrow space, it is a pain point problem in the construction industry. Small excavators can enter, but small breakers cannot do the job; medium and large breakers can do the job, but medium and large excavators cannot enter. If a small breaker wants to obtain powerful demolition ability, the key is to increase the impact force and reset frequency of the striking piston, which is one of the core technologies of the breaker.

[0003] The striking force of a traditional breaker is the impact resultant force generated by hydraulics and nitrogen together, and the frequency is generated by the system flow rate and the energy instantaneously released by the accumulator. Through the action of the reversing control valve, the up and down movement of the striking piston is realized, driving the reciprocating movement of the drill rod, so as to realize the conversion of impact energy into kinetic energy.

[0004] As Figure 1-2 shown, a nitrogen chamber 120 is arranged at the top of the striking piston 102 of the traditional breaker, which is filled with nitrogen at a certain pressure. On the one hand, it plays a role in damping during the recoil of the striking piston 102. On the other hand, the striking piston 102 compresses nitrogen upward under the action of the system pressure to provide instantaneous burst energy for the downward movement of the striking piston 1. Due to the limited external dimensions of the small breaker, it is difficult to make the nitrogen chamber 120 larger. Therefore, it is difficult to increase the impact force of nitrogen. If the system pressure is increased, on the premise of a certain breaking power, the flow rate will decrease instead, and the decrease in flow rate will lead to a decrease in frequency, so this method is obviously not advisable. Then, without increasing the system pressure, if the hydraulic impact force is to be increased, it is necessary to increase the acting area of the large chamber 3 above the striking piston 1, but this will inevitably reduce the acting area of nitrogen, and this method is also difficult to significantly increase the impact force.

[0005] The accumulator 110 of the traditional breaker is connected to the small chamber 103 end below the striking piston 102. On the one hand, it plays a certain role in stabilizing pressure and damping vibration. On the other hand, it stores the remaining energy and the recoil energy of the striking piston 102 during the previous strike of the breaker, and releases the energy during the next strike, so as to increase the striking ability to a certain extent. Generally, small breakers do not have an accumulator, and only medium and large breakers are equipped with it. Due to the limited external dimensions of the breaker, the accumulator installed inside is small, and the one installed outside is far away, so its effect on the frequency is small. During recoil, the oil in the large chamber 106 end of the striking piston 102 needs to return oil through the reversing control valve 111 entirely. Due to the limitation of the valve core diameter, it is impossible to return oil quickly. Therefore, it is difficult to increase the frequency.

[0006] With the development of the market, the demand for high-energy breaker hammers is increasing. However, the operating efficiency of traditional breaker hammers is relatively low, and their size and weight are relatively larger, making it difficult to be suitable for small excavators. Therefore, it can only rely on imported breaker hammers. However, the price of imported high-energy breaker hammers is extremely expensive, which is a significant economic burden for demolition construction parties.

[0007] Therefore, it is urgent to research and develop a high-energy impact hydraulic system. Summary of the Utility Model

[0008] The technical problem to be solved by the present utility model is in view of the above deficiencies of the prior art. The purpose of the present utility model is to provide a high-energy impact hydraulic system, so that the striking piston has a powerful impact force and the ability of high-frequency reset, effectively reducing costs.

[0009] To achieve the above object, the present utility model provides a high-energy impact hydraulic system, including a striking piston, on which a two-position three-way pilot valve is provided. A large chamber and a small chamber are respectively provided above and below the striking piston. The system also includes an accumulator and a directional control valve. The P port of the directional control valve is connected to the system hydraulic oil supply circuit through an oil supply main circuit. The T port of the directional control valve is connected to the system hydraulic oil return circuit through an oil return main circuit. The A port of the directional control valve is connected to the large chamber through a first oil circuit. The B port of the directional control valve is connected to the b end of the two-position three-way pilot valve through a second oil circuit. The small chamber is connected to the oil supply main circuit through a third oil circuit. The third oil circuit is also connected to the b end of the two-position three-way pilot valve through a fourth oil circuit. The third oil circuit is also connected to the c end of the directional control valve through a fifth oil circuit. The b end of the two-position three-way pilot valve is also connected to the d end of the directional control valve through a sixth oil circuit. The first oil circuit is connected to the oil inlet of the accumulator through a seventh oil circuit, and a boosting device for boosting the rapid entry of hydraulic oil into the accumulator is provided on the seventh oil circuit.

[0010] As a further improvement, the boosting device includes a Y-shaped cover and a conical spring. The conical spring is sleeved on the pipeline corresponding to the seventh oil circuit, and one end of the conical spring is connected to the pipeline corresponding to the seventh oil circuit, and the other end is connected to the Y-shaped cover. The accumulator is a diaphragm accumulator, and the Y-shaped cover presses on the diaphragm inside the accumulator.

[0011] Further, the fourth oil circuit is also connected to the oil return main circuit through an eighth oil circuit, and a frequency modulation valve is provided on the eighth oil circuit.

[0012] Further, the frequency modulation valve is a screw plug or an orifice damper or a two-position three-way valve.

[0013] Further, the commutation control valve is a two-position four-way valve, which has an A oil port, a B oil port, a P oil port, a T oil port, a pilot small chamber c end, and a pilot large chamber d end.

[0014] Further, a large-diameter drill rod is provided below the impact piston, and the accumulator is installed above the large-diameter drill rod.

[0015] Beneficial effects

[0016] Compared with the prior art, the present utility model has the following advantages:

[0017] 1. In the high-energy impact hydraulic system of the present utility model, the nitrogen chamber above the impact piston is cancelled, and the small accumulator below is cancelled. The impact energy is provided by full hydraulic pressure. Compared with the explosion energy jointly acting by hydraulic pressure and nitrogen, the impact piston can obtain greater downward impact kinetic energy, which not only enables the impact piston to have a strong impact force and the ability of high-frequency reset, effectively reducing costs, but also has a more compact shape, lighter weight, more convenient operation, no need for nitrogen filling maintenance, and more efficient crushing operation.

[0018] 2. In the high-energy impact hydraulic system of the present utility model, the accumulator is a high-pressure large-capacity accumulator and is connected to the large chamber of the impact piston instead of the small chamber. On the one hand, it plays a better role in stabilizing pressure and damping vibration for the impact piston; on the other hand, it increases the downward impact kinetic energy of the impact piston; while quickly replenishing oil, it improves the reset frequency of the impact piston. For a small breaker, this accumulator is not dispensable but plays a key role.

[0019] 3. In the high-energy impact hydraulic system of the present utility model, by setting a boosting device on one side of the oil inlet of the accumulator, the oil replenishing speed of the high-pressure large-capacity accumulator can be further accelerated, and the reset frequency of the impact piston can be increased. Description of the drawings

[0020] Figure 1 is the hydraulic schematic diagram of the traditional breaker hydraulic system at the initial stage of impact;

[0021] Figure 2 is the hydraulic schematic diagram of the traditional breaker hydraulic system during reset after impact;

[0022] Figure 3 is the hydraulic schematic diagram of the high-energy impact hydraulic system of the present utility model at the initial stage of impact;

[0023] Figure 4 is the hydraulic schematic diagram of the high-energy impact hydraulic system of the present utility model during rapid reset after impact.

[0024] Wherein: 101 - large-diameter drill rod, 102 - impact piston, 103 - small chamber, 104 - sixth oil circuit, 105 - second oil circuit, 106 - large chamber, 107 - first oil circuit, 108 - seventh oil circuit, 109 - boosting device, 110 - accumulator, 111 - reversing control valve, 112 - main oil inlet path, 113 - main oil return path, 114 - eighth oil circuit, 115 - third oil circuit, 116 - fifth oil circuit, 117 - frequency modulation valve, 118 - fourth oil circuit, 119 - two-position three-way pilot valve, 120 - nitrogen chamber, 1091 - Y-shaped cover, 1092 - conical spring. Detailed implementation manner

[0025] The following further describes the present utility model with reference to specific embodiments in the accompanying drawings.

[0026] From the impact energy It can be known from the impact force F = E / t that the greater the impact energy, the greater the impact force; the shorter the impact time or the higher the impact frequency, the greater the impact force; the greater the mass, the greater the impact energy. Therefore, in this embodiment, three means of increasing the impact energy, impact frequency, and increasing the diameters of the impact piston and the drill rod are simultaneously adopted to achieve higher demolition ability.

[0027] Specifically refer to Figure 3-4As shown in the figure, a high-energy impact hydraulic system of the present utility model includes a striking piston 102, on which a two-position three-way pilot valve 119 is provided. Above and below the striking piston 102, there are a large chamber 106 and a small chamber 103 respectively. The striking piston 2 is slidably arranged in a closed cylinder body, just like the structure of a piston cylinder, which is prior art and will not be elaborated here. The hydraulic system also includes an accumulator 110 and a reversing control valve 111. The accumulator 110 is a high-pressure large-capacity accumulator, and the reversing control valve 111 is a two-position four-way valve. This two-position four-way valve has an A oil port, a B oil port, a P oil port, a T oil port, a pilot small chamber c end, and a pilot large chamber d end. Among them, the P oil port of the reversing control valve 111 is connected to the system hydraulic oil supply line through an oil inlet main line 112. The system hydraulic oil supply line can be a fuel tank with a fuel pump. The oil inlet main line 112 is connected to the fuel pump to provide system hydraulic oil for the entire hydraulic system. The T oil port of the reversing control valve 111 is connected to the system hydraulic oil return line through an oil return main line 113. The system hydraulic oil return line can be a fuel tank to form a circulating hydraulic oil. The A oil port of the reversing control valve 111 is connected to the large chamber 106 through a first oil line 107. The B oil port of the reversing control valve 111 is connected to the b end of the two-position three-way pilot valve 119 through a second oil line 105. The small chamber 103 is connected to the oil inlet main line 112 through a third oil line 115. The third oil line 115 is also connected to the b end of the two-position three-way pilot valve 119 through a fourth oil line 118. The third oil line 115 is also connected to the c end of the reversing control valve 111 through a fifth oil line 116. The oil inlet of the fifth oil line 116 is located on the pipeline between the oil inlet main line 112 and the fourth oil line 118. The b end of the two-position three-way pilot valve 119 is also connected to the d end of the reversing control valve 111 through a sixth oil line 104. The first oil line 107 is connected to the oil inlet of the accumulator 110 through a seventh oil line 108. A boosting device 109 for boosting the rapid entry of hydraulic oil into the accumulator 110 is provided on the seventh oil line 108. By providing a boosting device on one side of the accumulator oil inlet, the oil replenishment speed of the high-pressure large-capacity accumulator can be further accelerated, and the reset frequency of the striking piston can be increased.

[0028] Under the same pressure and volume, from the bursting energy of compressed gas and the bursting energy of liquid it can be known that the bursting energy E of the liquid 1 is much greater than the bursting energy E of the gas. Therefore, in the high-energy impact hydraulic system of the present utility model, the nitrogen chamber 120 above the striking piston 102 is cancelled, and the small accumulator below is cancelled. The full hydraulic pressure is used to provide the impact energy. Compared with the bursting energy jointly exerted by the hydraulic pressure and nitrogen, the striking piston can obtain a greater downward striking kinetic energy. This not only enables the striking piston to have a powerful impact force and the ability of high-frequency reset, effectively reducing costs, but also has a more compact shape, lighter weight, more convenient operation, no need for nitrogen filling maintenance, and more efficient crushing operation.

[0029] Meanwhile, according to the principle that the higher the impact frequency, the faster the liquid drainage. Since the volume of the large chamber above the impact piston is larger and requires liquid drainage in a shorter time, it is difficult to achieve complete drainage of all the return oil only by the direction control valve. Therefore, its accumulator is a high-pressure large-capacity accumulator, which is connected to the large chamber of the impact piston rather than the small chamber. On the one hand, it plays a better role in stabilizing pressure and damping vibration for the impact piston; on the other hand, when the impact piston moves upward to reset, the return oil in the large chamber of the impact piston can quickly replenish the oil to the large-capacity high-pressure accumulator, instantaneously release energy for the next impact, increase the downward impact kinetic energy of the impact piston; while quickly replenishing the oil, it improves the oil drainage speed of the large chamber of the impact piston, shortens the reset time of the impact piston, and increases the reset frequency of the impact piston. For a small breaker, this accumulator is not dispensable but plays a key role.

[0030] Preferably, the boosting device 109 includes a Y-shaped cover 1091 and a conical spring 1092. Among them, the conical spring 1092 is sleeved on the pipeline corresponding to the seventh oil passage 108, and one end of the conical spring 1092 is connected to the pipeline corresponding to the seventh oil passage 108, and the other end is connected to the Y-shaped cover 1091. The accumulator 110 is a diaphragm accumulator, and the Y-shaped cover 1091 presses on the diaphragm inside the accumulator 110.

[0031] In this embodiment, under the action of the elastic force of the conical spring 1092 and the pressure of the nitrogen gas inside the accumulator 110, the Y-shaped cover 1091 always presses against the diaphragm of the accumulator 110, playing a role in accelerating the oil replenishment of the large-capacity high-pressure accumulator 110.

[0032] Preferably, the fourth oil passage 118 is also communicated with the main oil return passage 113 through the eighth oil passage 114. A frequency modulation valve 117 is provided on the eighth oil passage 114. The eighth oil passage 114 is a speed regulation oil passage from the fourth oil passage 118 to the main oil return passage 113, used to adjust the impact frequency of the impact piston 102. Further, the frequency modulation valve 117 is a screw plug or an orifice damper or a two-position three-way valve. Generally, an orifice damper can be used to achieve high-frequency output.

[0033] Preferably, a large-diameter drill rod 101 is provided below the impact piston 102, which is applied to a crushing device. The accumulator 110 is installed above the large-diameter drill rod 101, which is convenient for disassembly, installation and maintenance.

[0034] A control method for a high-energy impact hydraulic system includes the above-mentioned high-energy impact hydraulic system. This method is to respectively fill hydraulic oil into the large chamber and the small chamber of the impact piston to drive the impact piston to reciprocally impact. This method uses full hydraulics to provide impact energy, so that a greater impact force than that of a traditional breaker filled with nitrogen can be obtained, and the nitrogen filling maintenance work can be eliminated.

[0035] This method includes:

[0036] As Figure 3 shown, when the system pressure oil enters, the system pressure oil passes through the main oil inlet path 112, the third oil path 115, the fourth oil path 118, the two-position three-way pilot valve 119 b end of the impact piston 102, and the sixth oil path 104 to reach the pilot large cavity d end of the reversing control valve 111; at the same time, the system pressure oil also passes through the main oil inlet path 112, the third oil path 115, and the fifth oil path 116 to reach the pilot small cavity c end of the reversing control valve 111. At this time, the force at the pilot large cavity d end of the reversing control valve 111 is greater than the force at the pilot small cavity c end. The hydraulic oil pushes the reversing control valve 111 to move towards the c end, connecting the main oil inlet path 112. One path of the system pressure oil enters the large cavity 106 of the impact piston 102 through the first oil path 107, and the other path of the system pressure oil enters the accumulator 110 through the first oil path 107 and the seventh oil path 108; when the system pressure oil fills the large cavity 106 of the impact piston 102 and the accumulator 110 and the pressure continuously rises to the explosion point, the explosion energy is released, providing downward impact kinetic energy for the impact piston 102. The impact piston 102 impacts downward to complete one impact action;

[0037] As Figure 4 shown, when the impact is completed, the two-position three-way pilot valve 119 of the impact piston 102 is at the a end, connecting the sixth oil path 104 and the second oil path 105. The pilot oil at the d end of the reversing control valve 111 returns oil. Under the action of the system pressure oil at the c end of the reversing control valve 111, the reversing control valve 111 is pushed to move towards the d end, and the system pressure oil stops supplying oil to the large cavity 106 of the impact piston 102 and the large accumulator 110. The system pressure oil supplies oil to the small cavity 103 of the impact piston 102 through the main oil inlet path 112 and the third oil path 115, pushing the impact piston 102 to move upward. A small part of the oil in the large cavity 106 of the impact piston 102 returns oil through the first oil path 107 and the reversing control valve 111. Under the action of the boosting device 109, most of the oil in the large cavity 106 of the impact piston 102 quickly replenishes oil to the accumulator 110 and stores energy through the first oil path 107 and the seventh oil path 108. When the pressures in the large cavity 106 and the small cavity 103 of the impact piston 102 reach pressure balance, the reset is completed. At this time, the b end of the two-position three-way pilot valve 119 of the impact piston 102 is connected to the system pressure oil, opening the next impact mode;

[0038] When the system pressure oil continuously enters, the impact piston 102 moves reciprocally at high speed and continuously operates at high frequency;

[0039] When there is no system pressure oil entering, the impact piston 102 does not operate.

[0040] Preferably, the boosting device 109 includes a Y-shaped cover 1091 and a conical spring 1092. When quickly refilling the accumulator 110 with oil and storing energy, the conical spring 1092 pushes the Y-shaped cover 1091 to move, and the Y-shaped cover 1091 quickly pushes back the diaphragm of the accumulator 110, thereby realizing the quick oil filling of the accumulator 110.

[0041] Preferably, a large-diameter drill rod 101 is provided below the impact piston 102. When the impact piston 102 impacts downward, after the lower end of the impact piston 102 impacts the top of 101, the impact force acts on the large-diameter drill rod 101, and the large-diameter drill rod 101 then impacts the object to be demolished, thereby completing a crushing action.

[0042] The above are only the preferred embodiments of the present invention. It should be noted that for those skilled in the art, without departing from the structure of the present invention, several deformations and improvements can be made, and these will not affect the implementation effect of the present invention and the practicality of the patent.

Claims

1. A high-energy impact hydraulic system, comprising a striking piston (102), wherein the striking piston (102) is provided with a two-position three-way pilot valve (119), and a large chamber (106) and a small chamber (103) are respectively provided above and below the striking piston (102), characterized in that: The invention also comprises an accumulator (110) and a reversing control valve (111), wherein the P oil port of the reversing control valve (111) is connected to the system hydraulic oil supply circuit through the main oil inlet circuit (112), the T oil port of the reversing control valve (111) is connected to the system hydraulic oil return circuit through the main oil return circuit (113), the A oil port of the reversing control valve (111) is connected to the large chamber (106) through the first oil circuit (107), the B oil port of the reversing control valve (111) is connected to the b end of the two-position three-way pilot valve (119) through the second oil circuit (105), and the small chamber (103) is connected to the main oil inlet circuit (112) through the third oil circuit (115). The third oil circuit (115) is also connected to the b end of the two-position three-way pilot valve (119) through the fourth oil circuit (118), the third oil circuit (115) is also connected to the c end of the reversing control valve (111) through the fifth oil circuit (116), and the b end of the two-position three-way pilot valve (119) is also connected to the d end of the reversing control valve (111) through the sixth oil circuit (104); the first oil circuit (107) is connected to the oil inlet of the accumulator (110) through the seventh oil circuit (108), and the seventh oil circuit (108) is provided with a boosting device (109) that can boost the hydraulic oil to quickly enter the accumulator (110).

2. A high energy impact hydraulic system according to claim 1, characterized in that: The boosting device (109) comprises a Y-shaped cover (1091) and a conical spring (1092); the conical spring (1092) is sleeved on a pipeline corresponding to the seventh oil circuit (108); one end of the conical spring (1092) is connected to the pipeline corresponding to the seventh oil circuit (108); and the other end is connected to the Y-shaped cover (1091); the accumulator (110) is a diaphragm accumulator; and the Y-shaped cover (1091) is pressed against a diaphragm inside the accumulator (110).

3. A high energy impact hydraulic system according to claim 1, characterized in that: The fourth oil circuit (118) is also connected to the main oil return circuit (113) through the eighth oil circuit (114), and a frequency regulating valve (117) is provided on the eighth oil circuit (114).

4. A high energy impact hydraulic system according to claim 3, characterized in that: The frequency modulation valve (117) is a screw plug or an aperture damping or a two-position three-way valve.

5. A high energy impact hydraulic system according to claim 1, characterized in that: The reversing control valve (111) is a two-position four-way valve having an A oil port, a B oil port, a P oil port, a T oil port, a pilot small chamber c end and a pilot large chamber d end.

6. A high energy impact hydraulic system according to any one of claims 1 to 5, characterized in that: A large-diameter drill rod (101) is provided below the striking piston (102), and the energy accumulator (110) is installed above the large-diameter drill rod (101).

Images