CN210194736U - Automatic frequency modulation breaking hammer hydraulic system and excavator - Google Patents
Automatic frequency modulation breaking hammer hydraulic system and excavator Download PDFInfo
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- CN210194736U CN210194736U CN201920642851.4U CN201920642851U CN210194736U CN 210194736 U CN210194736 U CN 210194736U CN 201920642851 U CN201920642851 U CN 201920642851U CN 210194736 U CN210194736 U CN 210194736U
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Abstract
The utility model discloses a breaking hammer hydraulic system and an excavator capable of automatically adjusting frequency, wherein the breaking hammer hydraulic system comprises a main pump, a main valve, a cartridge valve, a hydraulic control reversing valve, an unloading reversing valve, a throttle valve, a breaking hammer body, a stroke switching valve, an electromagnetic reversing valve and a hydraulic oil tank; the cartridge valve, the hydraulic control reversing valve, the unloading reversing valve, the throttle valve and the stroke switching valve are integrated on the breaking hammer body to form a hydraulic control unit of the breaking hammer, and the hydraulic control unit is communicated with the main pump, the main valve, the electromagnetic reversing valve and the hydraulic oil tank through hydraulic pipelines; the electromagnetic directional valve is controlled to be switched by manually switching the key on the control panel by an operator, so that the short-stroke operation and the automatic frequency modulation operation of the piston are realized. The utility model realizes the double-gear frequency modulation of the breaking hammer, aiming at the working conditions of hard rock and soft rock; and the waste of impact energy is reduced.
Description
Technical Field
The utility model relates to a but automatic frequency modulation's quartering hammer hydraulic system, concretely relates to excavator has two grades of adjustable frequency's quartering hammer hydraulic system under broken operating mode, belongs to excavator quartering hammer technical field.
Background
Along with the continuous improvement of national requirements on safety and environmental protection in the fields of capital construction, mining and the like, the number of traditional blasting construction projects is continuously reduced, the number of excavator crushing projects is continuously increased, and the demand of the excavator with the crushing hammer is increased rapidly. In addition, the hydraulic breaking hammer is a device which takes hydraulic energy as a power source and converts the hydraulic energy into mechanical striking kinetic energy in the movement process so as to enable a piston to push a drill rod to carry out breaking operation. As a novel crushing tool, the novel crusher has the characteristics of low noise, excellent crushing performance, energy conservation, environmental protection and the like.
At present, the research on the breaking hammer and the control technology thereof in China is not sufficient, and the working conditions of hard rock and soft rock are not distinguished. The working condition of hard rock is characterized by high energy, low frequency and long stroke motion of a piston; the soft rock working condition is characterized by low energy, high frequency and short stroke motion of the piston. The breaking hammer with the fixed piston stroke is suitable for the problem of impact energy waste caused by the working condition of soft rock breaking or hard rock secondary breaking.
SUMMERY OF THE UTILITY MODEL
In order to overcome the deficiencies in the prior art, the utility model provides a but automatic frequency modulation's quartering hammer hydraulic system.
The utility model discloses realize according to following technical scheme:
a breaking hammer hydraulic system capable of automatically adjusting frequency comprises a main pump, a main valve, a cartridge valve, a hydraulic control reversing valve, an unloading reversing valve, a throttle valve, a breaking hammer body, a stroke switching valve, an electromagnetic reversing valve and a hydraulic oil tank; the cartridge valve, the hydraulic control reversing valve, the unloading reversing valve, the throttle valve and the stroke switching valve are integrated on the breaking hammer body to form a hydraulic control unit of the breaking hammer, and the hydraulic control unit is communicated with the main pump, the main valve, the electromagnetic reversing valve and the hydraulic oil tank through hydraulic pipelines; the electromagnetic directional valve is controlled to be switched by manually switching the key on the control panel by an operator, so that the short-stroke operation and the automatic frequency modulation operation of the piston are realized.
Further, the quartering hammer body includes the steel body and is located piston and the drill rod in the steel body, is equipped with the E hydraulic fluid port on the steel body of piston epicoele department, is equipped with the A hydraulic fluid port below the E hydraulic fluid port, is equipped with the D hydraulic fluid port on the steel body of piston lower chamber department, is equipped with C hydraulic fluid port and B hydraulic fluid port above the D hydraulic fluid port.
Further, the oil port A is communicated with a hydraulic control reversing valve, the oil port E is communicated with a cavity D of the cartridge valve, the cavity E of the cartridge valve is connected with the unloading reversing valve, the oil port C and the oil port B are respectively communicated with the stroke switching valve, a port f of the stroke switching valve is communicated with the cartridge valve, a port C of the hydraulic control reversing valve is communicated with the stroke switching valve, a port a of the hydraulic control reversing valve is communicated with a main valve after being connected with a port B of the hydraulic control reversing valve, and the oil port D is communicated with the main valve.
Further, the throttle valve is connected between the oil port E and the oil port A.
Furthermore, one end of the electromagnetic reversing valve is connected with the main pump, and the other end of the electromagnetic reversing valve is connected with the unloading reversing valve; when the electromagnetic reversing valve is not electrified, the unloading reversing valve is in a right position state under the action of the spring, the cartridge valve is in a closed state, the f port of the stroke switching valve has no high-pressure oil action, and the stroke switching valve does not reverse; when the electromagnetic directional valve is electrified, the unloading directional valve is reversed and is in a left state, and at the moment, the e cavity of the cartridge valve is communicated with the hydraulic oil tank.
An excavator comprises the automatic frequency-adjustable breaking hammer hydraulic system.
The utility model discloses beneficial effect:
the utility model realizes the double-gear frequency modulation of the breaking hammer, aiming at the working conditions of hard rock and soft rock; and the waste of impact energy is reduced.
Drawings
FIG. 1 is a schematic diagram of conventional crushing;
FIG. 2 is a schematic diagram of the short stroke rise of the piston (lowest point) according to the present invention;
FIG. 3 is a schematic diagram (highest point) of the short stroke descending of the piston of the present invention;
fig. 4 is an automatic frequency-modulation long-short stroke ascending schematic diagram (lowest point) of the utility model;
FIG. 5 is a schematic diagram of the automatic frequency modulation short-stroke descent (highest point) of the present invention;
fig. 6 is the principle diagram (highest point) of the automatic frequency modulation long-stroke descending of the present invention.
Detailed Description
In order to make the purpose, technical solution and advantages of the present invention clearer, the following will combine the drawings in the embodiments of the present invention to perform more detailed description on the technical solution in the embodiments of the present invention. In the drawings, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The described embodiments are only some, but not all embodiments of the invention. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention. Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
Fig. 1 shows a crushing principle diagram of the conventional technology, and the conventional technical scheme does not distinguish hard rock working conditions from soft rock working conditions. The working condition of hard rock is characterized by high energy, low frequency and long stroke motion of a piston; the soft rock working condition is characterized by low energy, high frequency and short stroke motion of the piston. The breaking hammer with the fixed piston stroke is suitable for the problem of impact energy waste caused by the working condition of soft rock breaking or hard rock secondary breaking.
As shown in fig. 2 to 6, the breaking hammer hydraulic system capable of automatically adjusting the frequency comprises a main pump 1, a main valve 2, a cartridge valve 3, a hydraulic control reversing valve 4, an unloading reversing valve 5, a throttle valve 6, a breaking hammer body 7, a stroke switching valve 8, an electromagnetic reversing valve 9 and a hydraulic oil tank 10; the cartridge valve 3, the hydraulic control reversing valve 4, the unloading reversing valve 5, the throttle valve 6 and the stroke switching valve 8 are integrated on the breaking hammer body 7 to form a hydraulic control unit of the breaking hammer, and are communicated with the main pump 1, the main valve 2, the electromagnetic reversing valve 9 and the hydraulic oil tank 10 through hydraulic pipelines; the electromagnetic directional valve 9 is controlled to be switched by manually switching the key on the control panel by an operator, so that the modes of piston short-stroke operation and automatic frequency modulation operation are realized.
Continuing to refer to fig. 2, the breaking hammer body 7 includes a steel body 12, and a piston 11 and a drill rod 13 which are located in the steel body 12, an oil port E is arranged on the steel body 12 at an upper cavity of the piston, an oil port a is arranged below the oil port E, an oil port D is arranged on the steel body 12 at a lower cavity of the piston, and an oil port C and an oil port B are arranged above the oil port D.
It should be noted that, piston 11 increases the E chamber hydraulic fluid port in the quartering hammer body, and the area of action in E chamber is less, and its counter action force can be ignored. The cavity E is communicated with a port d of the cartridge valve, and high-pressure oil acts on a port f of the stroke switching valve 8 to change the direction of the spring when the pressure is high enough to push the spring of the cartridge valve 3, and the high-pressure oil mainly comes from the piston to compress the cavity E; the throttle valve 6 is connected with the oil port E and the oil port A, the oil port A is connected with the hydraulic oil tank 10 in the rising process of the breaking hammer piston, but the oil port E is compressed due to the throttle valve 6, the pressure of the oil port E is rapidly increased, the compression strokes of the oil port E are different under different working conditions, and the generated pressures are also different;
with continued reference to fig. 2, the port a is communicated with the pilot-operated directional control valve 4, the port E is communicated with the chamber D of the cartridge valve 3, the chamber E of the cartridge valve 3 is connected with the unloading directional control valve 5, the port C and the port B are respectively communicated with the stroke switching valve 8, the port f of the stroke switching valve 8 is communicated with the cartridge valve 3, the port C of the pilot-operated directional control valve 4 is communicated with the stroke switching valve 8, the port a of the pilot-operated directional control valve 4 is communicated with the main valve 2 after being connected with the port B of the pilot-operated directional control valve 4, and the port D is communicated with. And the throttle valve 6 is connected between the oil port E and the oil port A.
One end of the electromagnetic directional valve 9 is connected with the main pump 1, and the other end of the electromagnetic directional valve 9 is connected with the unloading directional valve 5; when the electromagnetic directional valve 9 is not powered, the unloading directional valve 5 is in a right position state under the action of the spring, the cartridge valve 3 is in a closed state, the f port of the stroke switching valve 8 has no high-pressure oil function, and the stroke switching valve 8 does not change direction; when the electromagnetic directional valve 9 is electrified, the unloading directional valve 5 is reversed and is in a left state, and at the moment, the cavity e of the cartridge valve 3 is communicated with the hydraulic oil tank 10.
As shown in fig. 2 and 3, when the electromagnetic directional valve 9 is not energized, the unloading is performedThe reversing valve 5 is in a right position state under the action of the spring, at the moment, the e cavity and the d cavity of the cartridge valve 3 are communicated, the area of the e cavity is larger than that of the d cavity, the cartridge valve 3 is in a closed state under the action of the spring, the f end of the stroke switching valve 8 has no high-pressure oil action, and the stroke switching valve 8 does not reverse. The piston moves upwards after impacting the drill rod, and the area of the port a of the hydraulic control reversing valve 4 is SaGreater than b port area SbThe hydraulic control directional valve 4 is in the position shown in the figure 2, the upper piston cavity connected with the oil port A is connected with the hydraulic oil tank 10, the lower piston cavity connected with the oil port D is high-pressure oil, and at the moment, the piston moves upwards. When the piston moves to the end face connected with the oil port C, the oil port C is high-pressure oil, the stroke switching valve 8 is not reversed, the high-pressure oil is transmitted to the port C of the hydraulic control reversing valve 4, the hydraulic control reversing valve 4 reverses, and the upper cavity of the piston connected with the oil ports A, E is communicated with the high-pressure oil. Due to the upper cavity area S of the pistonAIs larger than the area S of the lower cavity of the pistonDAnd, in addition to the nitrogen gas reaction force in the accumulator, the piston stops and moves downward as shown in fig. 3. The piston moves with a short stroke, and the breaking hammer performs striking work with low energy. It should be noted that the breaking hammer works with a short piston stroke no matter under the soft rock working condition or the hard rock working condition as long as the electromagnetic directional valve 9 is not powered (the cross-sectional area of the oil cavity corresponding to the oil port E is small, and the acting force can be ignored).
As shown in fig. 4, 5 and 6, when the electromagnetic directional valve 9 is energized, the unloading directional valve 5 is switched to a left position, and at this time, the e-chamber of the cartridge valve 3 is communicated with the hydraulic oil tank 10.
When the breaking hammer works under the working condition of soft rock, the piston moves upwards under the action of high-pressure oil because the piston does not rebound after impacting the drill rod, as shown in figure 4. When the piston moves to the end face connected with the oil port C, the oil port C is high-pressure oil. And the piston compresses the oil cavity corresponding to the oil port E, the pressure is increased, but the pressure at the moment can not overcome the spring force of the cavity of the cartridge valve 3E, the f end of the stroke switching valve 8 has no high-pressure oil action, the stroke switching valve 8 does not change the direction, the high-pressure oil is transmitted to the port c of the hydraulic control reversing valve 4, and the hydraulic control reversing valve 4 reverses. A. The upper piston cavity connected with the oil port E is communicated with high-pressure oil, and the area S of the upper piston cavity isAIs larger than the area S of the lower cavity of the pistonDAnd, in addition to the nitrogen gas reaction force in the accumulator, the piston stops and moves downward as shown in fig. 5. The piston moves with a short stroke, and the breaking hammer performs striking work with low energy.
When the breaking hammer works under the working condition of hard rock, because the piston rebounds after impacting the drill rod, the piston accelerates to move upwards under the action of high-pressure oil and the rebounding force, as shown in figure 4. When the piston moves to the end face connected with the oil port C, the oil port C is high-pressure oil. But the piston continues to move upwards due to the effect of the rebound force. At this time, the piston compresses the oil chamber corresponding to the oil port E, the pressure rises and is enough to overcome the spring force of the chamber E of the cartridge valve 3, and high-pressure oil acts on the end f of the stroke switching valve 8, so that the stroke switching valve 8 is reversed. When the piston moves to the end face connected with the oil port B, the oil port B is high-pressure oil, and the high-pressure oil is transmitted to the port c of the hydraulic control reversing valve 4 due to the area S of the port ccAnd b port area SbThe sum is greater than the a port area SaThe hydraulic control reversing valve 4 reverses, and the upper cavity of the piston connected with the A, E oil port is communicated with high-pressure oil. Due to the upper cavity area S of the pistonAIs larger than the area S of the lower cavity of the pistonDAnd, in addition to the nitrogen gas reaction force in the accumulator, the piston stops and moves downward as shown in fig. 6. The breaking hammer performs striking operation with high energy aiming at the working condition of hard rock.
It should be noted that: the mode of realizing the short stroke operation and the automatic frequency modulation operation of the piston can control the reversing of the electromagnetic reversing valve by manually switching the key on the control panel through manual operation, thereby realizing the switching.
The utility model also provides an excavator, but including aforementioned automatically regulated's quartering hammer hydraulic system.
Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention and not for limiting the same; although the present invention has been described in detail with reference to preferred embodiments, it should be understood by those skilled in the art that: the invention can be modified or equivalent substituted for some technical features; without departing from the spirit of the present invention, it should be understood that the scope of the claims is intended to cover all such modifications and variations.
Claims (6)
1. The utility model provides a but automatic frequency modulation's quartering hammer hydraulic system which characterized in that: the hydraulic control hydraulic breaker comprises a main pump (1), a main valve (2), a cartridge valve (3), a hydraulic control reversing valve (4), an unloading reversing valve (5), a throttle valve (6), a breaking hammer body (7), a stroke switching valve (8), an electromagnetic reversing valve (9) and a hydraulic oil tank (10);
the cartridge valve (3), the hydraulic control reversing valve (4), the unloading reversing valve (5), the throttle valve (6) and the stroke switching valve (8) are integrated on the breaking hammer body (7) to form a hydraulic control unit of the breaking hammer, and are communicated with the main pump (1), the main valve (2), the electromagnetic reversing valve (9) and the hydraulic oil tank (10) through hydraulic pipelines;
the electromagnetic directional valve (9) is controlled to be switched by manually switching the keys on the control panel by an operator, so that the short-stroke operation and the automatic frequency modulation operation of the piston are realized.
2. An automatically frequency-tunable hydraulic demolition hammer system according to claim 1, characterized in that: the breaking hammer body (7) comprises a steel body (12), a piston (11) and a drill rod (13) which are positioned in the steel body (12), an oil port E is arranged on the steel body (12) at the upper cavity of the piston, an oil port A is arranged below the oil port E,
and a D oil port is arranged on the steel body (12) at the lower cavity of the piston, and a C oil port and a B oil port are arranged above the D oil port.
3. An automatically frequency-tunable hydraulic demolition hammer system according to claim 2, characterized in that: the hydraulic control reversing valve is characterized in that an oil port A is communicated with a hydraulic control reversing valve (4), an oil port E is communicated with a cavity D of a cartridge valve (3), a cavity E of the cartridge valve (3) is connected with an unloading reversing valve (5), an oil port C and an oil port B are respectively communicated with a stroke switching valve (8), an opening f of the stroke switching valve (8) is communicated with the cartridge valve (3), an opening C of the hydraulic control reversing valve (4) is communicated with the stroke switching valve (8), an opening a of the hydraulic control reversing valve (4) is communicated with a main valve (2) after being connected with an opening B of the hydraulic control reversing valve (4), and an oil port D is communicated with the main valve.
4. An automatically frequency-tunable hydraulic demolition hammer system according to claim 2, characterized in that: and the throttle valve (6) is connected between the oil port E and the oil port A.
5. An automatically frequency-tunable hydraulic demolition hammer system according to claim 1, characterized in that: one end of the electromagnetic directional valve (9) is connected with the main pump (1), and the other end of the electromagnetic directional valve (9) is connected with the unloading directional valve (5);
when the electromagnetic directional valve (9) is not powered, the unloading directional valve (5) is in a right position state under the action of the spring, the cartridge valve (3) is in a closed state, the f port of the stroke switching valve (8) has no high-pressure oil action, and the stroke switching valve (8) does not change direction;
when the electromagnetic directional valve (9) is electrified, the unloading directional valve (5) is reversed and is in a left position state, and at the moment, the e cavity of the cartridge valve (3) is communicated with the hydraulic oil tank (10).
6. An excavator, characterized in that: a hydraulic system comprising an automatically tunable demolition hammer as claimed in any one of claims 1 to 5.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920642851.4U CN210194736U (en) | 2019-05-07 | 2019-05-07 | Automatic frequency modulation breaking hammer hydraulic system and excavator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920642851.4U CN210194736U (en) | 2019-05-07 | 2019-05-07 | Automatic frequency modulation breaking hammer hydraulic system and excavator |
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| Publication Number | Publication Date |
|---|---|
| CN210194736U true CN210194736U (en) | 2020-03-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920642851.4U Withdrawn - After Issue CN210194736U (en) | 2019-05-07 | 2019-05-07 | Automatic frequency modulation breaking hammer hydraulic system and excavator |
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| CN (1) | CN210194736U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110005014A (en) * | 2019-05-07 | 2019-07-12 | 徐州徐工挖掘机械有限公司 | It is a kind of can automatic frequency adjustment quartering hammer hydraulic system, control method and excavator |
| WO2022217666A1 (en) * | 2021-04-12 | 2022-10-20 | 何泽康 | Single-axis rotation and time-based frequency control breaking hammer |
-
2019
- 2019-05-07 CN CN201920642851.4U patent/CN210194736U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110005014A (en) * | 2019-05-07 | 2019-07-12 | 徐州徐工挖掘机械有限公司 | It is a kind of can automatic frequency adjustment quartering hammer hydraulic system, control method and excavator |
| CN110005014B (en) * | 2019-05-07 | 2023-06-27 | 徐州徐工挖掘机械有限公司 | Breaking hammer hydraulic system capable of automatically adjusting frequency, control method and excavator |
| WO2022217666A1 (en) * | 2021-04-12 | 2022-10-20 | 何泽康 | Single-axis rotation and time-based frequency control breaking hammer |
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Granted publication date: 20200327 Effective date of abandoning: 20230627 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20200327 Effective date of abandoning: 20230627 |