CN211009322U

CN211009322U - Differential drop hammer device

Info

Publication number: CN211009322U
Application number: CN201921941533.4U
Authority: CN
Inventors: 曹斌; 刘源; 刘岩; 刘涛
Original assignee: Taian Hengda Machinery Co ltd; Taian Hangshen Machinery Co ltd
Current assignee: Taian Hengda Machinery Co ltd; Taian Hangshen Machinery Co ltd
Priority date: 2019-11-12
Filing date: 2019-11-12
Publication date: 2020-07-14
Anticipated expiration: 2029-11-12

Abstract

The utility model discloses a differential hammer device that falls, including the hammer system that falls, the hammer system that falls includes hydraulic pressure station, lifting cylinder, poppet valve, low pressure energy storage ware, high pressure energy storage ware and back pressure valve, the lifting cylinder is vertical setting, the decurrent two effect single piston rod pneumatic cylinder of piston rod, and its tailpiece of the piston rod portion hookup has the weight, the back pressure valve oil-out connects the oil return pipe at hydraulic pressure station, the oil inlet of two-position four-way electromagnetic directional valve connects the pressure pipe at hydraulic pressure station, its oil return opening connects the oil return pipe at hydraulic pressure station or the no rod chamber hydraulic fluid port that promotes the jar, and its oil-out seals or communicates its oil return opening, and its another oil-out connects the control mouth of two. Utility model has the dual effect of the differential power and the oily resistance of oil extraction benefit when improving hydraulic hammer drop hammer, correspondingly have the effect and characteristics and energy-conservation of improving drop hammer speed, hitting the energy, hitting the power of beating.

Description

Differential drop hammer device

Technical Field

The utility model relates to an engineering machine tool technical field, more specifically say, in particular to differential drop hammer device.

Background

At present, a heavy hammer lifting cylinder of a hydraulic hammer is generally in a double-acting double-piston rod type or a double-acting single-piston rod type. Because the lifting cylinder is vertically arranged above the heavy hammer, a cavity above a piston of the double-acting double-piston rod type lifting cylinder expressed by no terms is called an upper cavity, and a cavity below the piston is called a lower cavity.

The areas of two sides of the double-acting double-piston rod type piston and the volumes of two cavities are equal, and the double-acting double-piston rod type lifting cylinder has the advantages that the volume of an upper cavity is smaller than that of a rodless cavity of a double-acting single-piston rod type lifting cylinder, oil needed by single circulation is less, and the hitting frequency is higher when the oil supply of a hydraulic station is in a certain time. The disadvantage is that the force can not be applied by the difference of two side surfaces of the piston when the hammer is dropped, the oil discharge resistance of the lower cavity and the oil supplement resistance of the upper cavity directly influence the speed of the hammer, and the hitting energy and the hitting force are obviously smaller than those of a free falling body. The other disadvantage is that the lifting piston rod extends upwards during lifting, the height of the whole machine is greatly improved, a higher pile frame is required during piling, the use cost is improved, and the safety and the application range are reduced.

The piston area and the volume of the rodless cavity side of the double-acting single-piston rod type lifting cylinder are larger than those of the rod cavity side, the piston area of the rodless cavity (upper cavity) and the piston area of the rod cavity (lower cavity) are smaller (such as the standard ratio of 1.25:1 or 1.33: 1), differential force application can be realized when the arrangement is reasonable, the differential force counteracts or partially counteracts oil discharge of the rod cavity and oil supplement resistance of the rodless cavity, and at the moment, the rod type lifting cylinder is high in rod drop hammer speed relative to a common double-acting double-piston rod type lifting cylinder, and the corresponding. The main defect is that in order to ensure the oil supplement amount of the rodless cavity, a piston rod with a relatively thin cylinder diameter is adopted to reduce the volume difference of the two cavities, when the hammer is dropped, the rod cavity supplements oil to the rodless cavity, and meanwhile, the residual liquid (most of the residual liquid is discharged through an oil return pipe) of the low-pressure accumulator and pressure oil from a hydraulic station supplement the volume difference of the two cavities, so that the technical requirement is high. When the volume difference of the two cavities is large, oil needs to be absorbed from the oil return pipe even to supplement the rodless cavity, the drop hammer speed is lower, the impact energy and the impact force are small, and the hydraulic hammer belongs to a single-action hydraulic hammer. The drop hammer speed is continuously improved while the liquid flow resistance is increased in a square level, and the drop hammer end speed is far lower than that of a free falling body.

The low-pressure accumulator is small in liquid filling amount and can be discharged to the oil return pipe at any time, the low-pressure accumulator mainly has the function of reducing lifting pressure by reducing oil return resistance, and has the function of small liquid storage and liquid supplement.

Because the area difference between the two cavity surfaces is small, and the rodless cavity is communicated with the oil return pipe, the differential action when the system is well matched and the hammer falls is mainly to partially offset the resistance of oil discharge and oil supplement, and the force application effect is small; when the system is not well matched, the rodless cavity needs to be supplemented with oil absorption from an oil return pipe of the hydraulic station, and the oil absorption resistance is increased.

The utility model discloses a serial number integrated hydraulic means of hydraulic hammer discloses a structure and method that row oil mended oily resistance when reducing techniques such as pipe fitting and reducing the hammer. Because the liquid flow resistance is in direct proportion to the square of the flow velocity in theory, the utility model has the obvious effect of reducing the oil discharge and oil supplement resistance.

The utility model provides a serial number differential hydraulic means of hydraulic hammer provides one kind and realizes the possibility of falling the hammer with higher speed through differential technique, and the last speed that can be effective or be closer to the free fall then depends on oil supplementing technique and system matching.

As a typical case of the hydraulic hammer, a central television station publicly reports a large national weight: "TZ-1900 double-acting type full hydraulic pile hammer" of Taiyuan heavy machinery group Limited company, the weight is 200t, the maximum drop height is 1.5m, the impact energy at the maximum drop height is 1900kJ, the impact energy is only 63% of the potential energy of the weight, and is equivalent to a free falling body less than 1 m. The force application effect of double-acting full hydraulic pressure does not offset the oil discharge and oil supplement resistance in the hammer drop process, the efficiency loss is huge, and the general level of a single-acting hydraulic hammer without force application is not reached. It can be seen from this example that the "double-acting full hydraulic pile hammer" and the related drop hammer force application technology, which directly apply pressure oil to the upper chamber of the lifting cylinder, may not be able to effectively increase the drop hammer speed.

The ramming and crushing hydraulic hammer is generally below 7t and is about 10t individually. The hydraulic hammer with 5t to more than 100t is mainly used for piling. The total height of the hydraulic hammer adopting the double-acting single-piston rod type lifting cylinder is at least lower than that of the double-acting double-piston rod type lifting cylinder by the sum of the maximum working stroke, the reserve stroke for preventing emptying and the safety distance with other parts. Therefore, the area difference of two sides of the piston of the double-acting single-piston rod type lifting cylinder is utilized to improve the drop hammer differential force, and the striking efficiency is favorably improved on the premise of keeping the advantages of good safety, low use cost and wide application range.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a differential drop hammer device.

In order to achieve the above purpose, the utility model adopts the following technical scheme: a differential drop hammer device comprises a drop hammer system, wherein the drop hammer system comprises a hydraulic station, a lifting cylinder, a lifting valve, a low-pressure energy accumulator, a high-pressure energy accumulator and a back pressure valve, the lifting cylinder is a vertically-arranged double-acting single-piston-rod hydraulic cylinder with a downward piston rod, the end part of a piston rod of the lifting cylinder is connected with the heavy hammer, the lifting valve is a two-way cartridge valve consisting of a two-way basic plug-in and a two-position four-way electromagnetic directional valve, the pressure pipe of the hydraulic station is connected with an oil inlet of the high-pressure energy accumulator, the lifting cylinder is provided with a rod cavity oil port and an oil inlet of the two-way basic plug-in, the oil outlet of the two-way basic plug-in is connected with the low-pressure energy accumulator, the lifting cylinder is provided with a rod cavity oil port and the back pressure valve oil inlet, the oil outlet of the back, its normally open oil outlet is closed or communicated with its oil return port, and its another oil outlet is connected with control port of two-way basic plug-in component.

Preferably, the low-pressure accumulator and the high-pressure accumulator are both airbag type accumulators.

Preferably, the back pressure valve is any one of a two-way cartridge valve and a one-way valve which are composed of an overflow valve, an overflow valve and a two-way plug-in with a damping hole and have a pressure regulating function.

Preferably, the rodless cavity oil port and the poppet valve of the lift cylinder are respectively provided with a plurality of oil ports, and the two-way basic plug-in components share one two-position four-way electromagnetic valve for control.

Preferably, the poppet valve is replaced by any valve body of a two-position four-way reversing valve or a three-position four-way reversing valve, wherein the two-position four-way reversing valve is provided with P, T, B oil ports and an A oil port, the P, T, B or B, T or both the four oil ports are normally open, a pressure pipe of the hydraulic station is connected with a high-pressure energy accumulator and a P oil port of the two-position four-way reversing valve, the A oil port of the two-position four-way reversing valve is closed or communicated with a T oil port, the B oil port of the two-position four-way reversing valve is connected with a low-pressure energy accumulator, an oil port of a rodless cavity of a lifting cylinder and an oil inlet.

Preferably, the drop hammer system further comprises a liquid filling valve, the liquid filling valve is a two-way cartridge valve, the liquid filling valve and the lift valve share one two-position four-way electromagnetic directional valve for control, an oil inlet of the two-position four-way electromagnetic directional valve is connected with a pressure pipe of the hydraulic station, an oil return port of the two-position four-way electromagnetic directional valve is connected with an oil return pipe of the hydraulic station or an oil port of a rodless cavity of the lift cylinder, two oil outlets of the two-position four-way electromagnetic directional valve are respectively connected with a control port of the two-way basic cartridge of the liquid filling valve and the lift valve, a pressure pipe of the hydraulic station is connected with a high-pressure energy accumulator and an oil inlet of the liquid filling valve, an oil outlet of the liquid filling valve is connected with an oil inlet of the rod cavity of the lift cylinder and the oil inlet of the two-.

Preferably, the two-position four-way electromagnetic reversing valve is independently arranged or combined with any two-way basic plug-in unit to form a two-way cartridge valve, one oil outlet of the two-position four-way electromagnetic reversing valve is connected with the oil outlet of the liquid filling valve, and the other oil outlet of the two-position four-way electromagnetic reversing valve is connected with a control port of the two-way basic plug-in unit.

Compared with the prior art, the utility model has the advantages of:

the utility model is suitable for a hydraulic hammer of two piston rod lifting cylinder of two effects does not have differential afterburning effect, only reduces the oil extraction when falling the hammer and mends oily resistance.

Therefore, the utility model has the dual effect of the differential force and the oily resistance of oil extraction when improving hydraulic hammer drop hammer, the corresponding effect and characteristics and energy-conserving effect that have improvement drop hammer speed, hit the effect of hitting energy, hitting power of beating.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.

Fig. 1 is a block diagram of a first embodiment of the present invention.

Fig. 2 is a block diagram of a second embodiment of the present invention.

Fig. 3 is a block diagram of a third embodiment of the present invention.

Fig. 4 is a block diagram of a fourth embodiment of the present invention.

Detailed Description

The preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings, so that the advantages and features of the present invention can be more easily understood by those skilled in the art, and the scope of the present invention can be more clearly and clearly defined.

Example 1

Fig. 1 is a drawing of this embodiment, which is a basic solution of the present invention.

A differential drop hammer device comprises a drop hammer system, wherein the drop hammer system comprises a hydraulic station, a lifting cylinder 1, a lifting valve 2, a low-pressure energy accumulator 3, a high-pressure energy accumulator 4 and a back pressure valve 5, the lifting cylinder 1 is a double-acting single-piston-rod hydraulic cylinder with a vertically arranged piston rod facing downwards, and a heavy hammer 6 is connected to the end part of the piston rod of the lifting cylinder, in the embodiment, the lifting valve 2 is a two-way cartridge valve consisting of a two-way basic plug-in unit 11 and a two-position four-way electromagnetic valve 12, the low-pressure energy accumulator 3 and the high-pressure energy accumulator 4 are air bag type energy accumulators, the back pressure valve 5 is a two-way cartridge valve consisting of an overflow valve, an overflow valve and a two-way plug-in unit with a damping hole and having a pressure regulating function and any one-way valve with a set opening pressure, the pressure pipe of the high-pressure energy accumulator 4 and the, The hydraulic lifting device comprises a lifting cylinder 1 rodless cavity oil port and a back pressure valve 5 oil inlet, wherein the oil outlet of the back pressure valve 5 is connected with an oil return pipe of a hydraulic station, the oil inlet P of a two-position four-way solenoid valve 12 is connected with a pressure pipe of the hydraulic station, an oil return port T of the two-position four-way solenoid valve is connected with the oil return pipe of the hydraulic station or the rodless cavity oil port of the lifting cylinder 1, a normally-open oil outlet A of the two-position four-way solenoid valve is closed or communicated with the oil.

To facilitate understanding of the working principle, the ports of the valve bodies in the figures are marked by letters.

The hammer dropping method comprises the following steps: in a normal shutdown state, because the B, T port of the pilot valve two-position four-way electromagnetic valve 12 of the two-way cartridge valve is normally open, the two-way basic plug-in 11 is equivalent to a one-way valve, the rod cavity of the lifting cylinder 1 is communicated with the rodless cavity through the two-way basic plug-in 11, and the heavy hammer 6 is stabilized at an initial position.

The electromagnet of the two-position four-way electromagnetic valve 12 is switched after being electrified, the P, B ports of the two-position four-way electromagnetic valve 12 are communicated, the pressurizing A port of the C port of the two-way basic plug-in 11 is sealed, the pressure oil is filled into the high-pressure energy accumulator 4, the buffering heavy hammer 6 is impacted by the liquid flow at the moment of falling, rotating and rising, until the pressure oil reaches the pressure of the lifting hammer, the pressure oil pushes the rod cavity piston of the lifting cylinder 1, and the heavy hammer 6 is. Meanwhile, hydraulic oil discharged from a rodless cavity of the lifting cylinder 1 is filled into the low-pressure accumulator 3 until the back pressure valve 5 is opened, and redundant oil returns to the hydraulic station through an oil return pipe.

The electromagnet of the two-position four-way electromagnetic valve 12 is reset after power failure, the P, A port and the B, T port of the two-position four-way electromagnetic valve 12 are communicated, the two-way basic plug-in 11 is in a one-way valve state, under the action of the gravity of the heavy hammer 6, oil liquid discharged from a rod cavity of the lifting cylinder 1 is supplied to a rodless cavity through the A port and the B port of the two-way basic plug-in 11, meanwhile, the high-pressure energy accumulator 4, the low-pressure energy accumulator 3 with the pressure set as backpressure and a hydraulic station pressure pipe simultaneously supply oil to the rodless cavity of the lifting cylinder 1, the overshoot action of the back pressure valve 5 and the abundant oil supply enable the pressure of the rodless cavity to be always larger than or equal to the set backpressure, the piston is pushed to move downwards in an accelerating. When the oil supplementing pressure of the rodless cavity is larger than the set back pressure, the redundant oil returns to the hydraulic station through the back pressure valve 5 and the oil return pipe.

By arranging the backpressure valve 5, on the premise that the sum of the hammer lifting pressure, the backpressure and the liquid flow loss of the oil inlet and return pipe is not more than the rated pressure of the hydraulic station, the opening pressure of the backpressure valve 5 can be increased as much as possible, so that the low-pressure accumulator 3 stores abundant oil and has higher pressure which is the same as the backpressure. Because the problem of insufficient oil supply of a rodless cavity of the lifting cylinder 1 in the hammer dropping process does not exist, the area difference of two sides of the piston is increased as much as possible, and the differential force application effect is improved. When the hammer drops, the rodless cavity of the lifting cylinder 1 has sufficient oil supplement amount and improved pressure, the area difference of two sides of the piston is increased, and the product of the pressure and the area difference, namely the downward thrust, is also obviously increased.

The mass of the heavy hammer 6 of the large hydraulic hammer is far larger than that of the frame and the related parts for mounting the heavy hammer 6, and the maximum value of the so-called 'stress' is about the gravity of the frame and the related parts. Otherwise, at the moment when the weight 6 begins to fall, the force acts to jack the frame and the associated parts upwards, resulting in the frame movement and the associated parts colliding with each other.

Therefore, the utility model discloses an this embodiment has the effect that improves the differential afterburning of hydraulic hammer, and corresponding improvement drop hammer speed, hit the effect and the characteristics of beating energy, hitting power.

Example 2

Fig. 2 is a drawing of the present embodiment. The drift diameter of a pressure pipe for connecting an oil port of a rod cavity of the lifting cylinder 1 with an oil inlet A port of the two-way basic plug-in unit is not too large due to the limitation of structure and material supply, if the maximum nominal drift diameter of a high-pressure oil pipe for standard supply with the working pressure of 31.5MPa is DN50, 4 or more oil ports can be adopted for reducing the flow resistance, at least 2 oil ports can be adopted, the drawing 2 of the embodiment limited by a plane graph by a standard principle diagram can only be expressed as 2, the oil pipe is respectively connected with each oil port of the rod cavity of the lifting cylinder 1 in parallel and the oil inlet A port of the two-way standard plug-in unit 11 in parallel, and the oil discharge resistance of.

When the structure and the supply of goods limit and do not conveniently set up the two-way cartridge valve of bigger latus rectum or do not conveniently increase the rodless chamber hydraulic fluid port of lift cylinder 1 or the structure needs, rodless chamber hydraulic fluid port and two-way cartridge valve also can be established a plurality ofly, and the embodiment figure 2 that is limited for the plane figure by the standard schematic diagram can only be expressed as 2, further reduces the liquid flow resistance. The two-way basic plug-in components 11 of each two-way cartridge valve can share one two-position four-way electromagnetic valve 12 for control, namely, ports B of the two-position four-way electromagnetic valves 12 are respectively connected with ports C of the control ports of the two-way basic plug-in components 14, so that the system is simplified, the cost is reduced, and the reliability is improved. The standard two-way plug-in unit diameter specification and the flow of supplying goods are large, and the number of the two-way plug-in units does not need to correspond to the number of oil ports of the rodless cavity of the lifting cylinder 1.

The maximum lifting hammer height of the large hydraulic hammer is more than 1.5m, the final speed of a free falling body is 5.42m/s and the time is 0.55s, for example, a 50t hydraulic hammer, the cylinder diameter of a lifting cylinder 1 is 20cm, the rod diameter is 10cm, the falling distance of a weight with the stroke of 1.5m is 1.5m, the actual drift diameter of a standard supply maximum drift diameter DN50 oil pipe is 50.8mm, the area of a rodless cavity of the lifting cylinder 1 is 236cm2, the volume of the lifting cylinder 1 is 35.3 cm2, the sectional area of the oil pipe is 20.3cm2, the average flow rate of the oil pipe is 31.6m/s according to the free falling body time of 0.55s, the maximum oil discharge of a rod cavity of the lifting cylinder 1 is 128L/s 7680/min and the maximum flow rate of the oil pipe is 63 m/s according to the free falling body final speed, the far overpressure pipe flow rate recommendation value is not more than 10m/s and the oil return pipe flow rate recommendation is not more than 5m/s, when an oil port 4 and an oil pipe are adopted, the flow rate is about the initial set, the resistance is about 25 theoretically, and other technical measures.

The effect and the potential of reducing the oil discharging and supplementing resistance in the drop hammer are far greater than those of any direct force application technology, and the effects are synergistic and energy-saving. After this embodiment is combined with embodiment 1, the utility model discloses have both improved the main power that falls to the hammer, show the dual effect that reduces the resistance that falls to the hammer again.

Example 3

Fig. 3 is a drawing of the present embodiment. The poppet valve 2 of the embodiment adopts a two-position four-way reversing valve 13, and the oil port P, T, B is normally open, and also B, T is normally open or four oil ports are normally open. The pressure pipe from the hydraulic station is connected with a high-pressure energy accumulator 4 and a pressure port P of a two-position four-way reversing valve 13, a port A of the two-position four-way reversing valve 13 is sealed or communicated with a port T, a port B of the two-position four-way reversing valve 13 is connected with a low-pressure energy accumulator 3, an oil port of a rodless cavity of a lifting cylinder 1 and a port A of an oil inlet of a back pressure valve 5, and a port B of an oil outlet of the back pressure valve 5 is connected with an oil return. The two-position, four-way reversing valve 13 may also be replaced by a three-position, four-way reversing valve, in which one position is idle or used.

When the two-position four-way reversing valve 13 is reversed, the port P and the port B are communicated, the heavy hammer 6 is lifted, the heavy hammer falls after the two-position four-way reversing valve 13 is reset, the working principle is the same as that of a two-way cartridge valve, and the two-position four-way reversing valve belongs to equivalent substitution.

Example 4

Fig. 4 is a drawing of the present embodiment. In order to improve the striking frequency and fully utilize the hydraulic energy provided by the hydraulic station, in this embodiment, a charging valve 15 is added on the basis of the technical solution described in embodiment 1, and the charging valve 15 is a two-way cartridge valve similar to the poppet valve 2. To reduce cost and simplify operation, the charge valve 15 and the poppet valve 2 may share one piece of two-position four-way solenoid valve 12 for control. The port P of the two-position four-way electromagnetic valve 12 is connected with a pressure pipe from a hydraulic station, the port T is connected with an oil return pipe of the hydraulic station or an oil port of a rodless cavity of the lifting cylinder 1, and the port A and the port B are respectively connected with a port C of a control port of a two-way basic plug-in unit of the liquid charging valve 15 and the lifting valve 2. For comparison with the embodiment 1, the two-position four-way solenoid valve 12T of the embodiment is connected with the rodless cavity oil port of the lifting cylinder 1. A pressure pipe from a hydraulic station is connected with a high-pressure energy accumulator 4 and an oil inlet A port of a two-way basic plug-in unit of a liquid charging valve 15, an oil outlet B port of the two-way basic plug-in unit of the liquid charging valve 15 is connected with a rod cavity of a lifting cylinder 1 and an oil inlet A port of a basic plug-in unit 11 of a lifting valve 2, an oil outlet B port of the basic plug-in unit 11 of the lifting valve 2 is connected with a low-pressure energy accumulator 3, an oil port of a rodless cavity of the lifting cylinder 1 and an oil inlet A port of a back pressure valve 5. After the two-position four-way electromagnetic valve 12 is electrified and switched, the port P and the port B are communicated with the two-way basic plug-in unit of the control lift valve 2 to be closed, the port A and the port T are communicated with the rear liquid charging valve 15 and the two-way basic plug-in unit is released to be in a one-way valve state, the pressure pipe of the hydraulic station and the high-pressure energy accumulator 4 supply oil to the rod cavity of the lifting cylinder 1 through the port A and the port B of the liquid charging valve 15 together, and the lifting speed of. After the two-position four-way electromagnetic valve 12 is powered off and reset, the port B and the port T are communicated, the two-way basic plug-in unit of the lifting valve 2 is released to be in a one-way valve state, the heavy hammer 6 falls, and the rod cavity of the lifting cylinder 1 and the low-pressure energy accumulator 3 supplement oil to the rodless cavity together; meanwhile, after the port P and the port A are communicated, the two-way basic plug-in of the liquid charging valve 15 is closed, and the hydraulic station charges the high-pressure accumulator 4. Because only the low-pressure energy accumulator 3 fills the volume difference between the rodless cavity and the rod cavity when the hammer is dropped, the pressure is reduced when the low-pressure energy accumulator 3 releases oil, so that the differential force is smaller than that of the embodiment 1 and larger than that of the embodiment without the back pressure valve 5, and the impact frequency of the heavy hammer 6 is improved along with the increase of the lifting speed.

The two-position four-way solenoid valve 12 can be independently arranged or combined with any two-way basic plug-in to form a two-way cartridge valve. The normal-open oil outlet is connected with an oil outlet port C of the two-way basic plug-in unit of the liquid charging valve 15, and the other oil outlet is connected with a control port C of the two-way basic plug-in unit of the poppet valve 2.

The two-position four-way electromagnetic valve 12 can be replaced by a three-position four-way electromagnetic reversing valve, hydraulic principles of hydraulic stations are different, and the two-position four-way electromagnetic valve 12 can be replaced by the three-position four-way electromagnetic reversing valve in order to match with different hydraulic principles or configured hydraulic stations. For example, when the three-position four-way electromagnetic reversing valve is used in a normal-flow hydraulic station, the four oil ports are normally open for unloading, when the three-position four-way electromagnetic reversing valve is used in a normal-pressure hydraulic station, the pressure port is closed, and the other three oil ports are normally open for unloading. After the ports P and B of the three-position four-way electromagnetic directional valve are communicated, the hydraulic station and the high-pressure energy accumulator 4 supply oil to the rodless cavity of the lifting cylinder 1 together, and the heavy hammer is lifted; the port P and the port B are disconnected, and after the port P and the port A are connected, the heavy hammer falls down, and simultaneously the hydraulic station fills liquid into the high-pressure accumulator 4; and a middle position when not in work.

Although the embodiments of the present invention have been described with reference to the accompanying drawings, various changes and modifications can be made by the owner within the scope of the appended claims, and the protection scope of the present invention should not be exceeded by the claims.

Claims

1. The utility model provides a differential hammer device that falls, includes the hammer system that falls, and the hammer system that falls includes hydraulic pressure station, lift cylinder (1), poppet valve (2), low pressure energy storage ware (3), high pressure energy storage ware (4) and back pressure valve (5), its characterized in that: the lifting cylinder (1) is a vertical double-acting single-piston-rod hydraulic cylinder with a downward piston rod, the end part of a piston rod of the lifting cylinder is connected with a heavy hammer (6), the lifting valve (2) is a two-way cartridge valve consisting of a two-way basic plug-in component (11) and a two-way four-way solenoid valve (12), the pressure pipe of the hydraulic station is connected with a rod cavity oil port of the high-pressure energy accumulator (4), a lifting cylinder (1) and an oil inlet of the two-way basic plug-in component (11), the oil outlet of the two-way basic plug-in component (11) is connected with a low-pressure energy accumulator (3), a rodless cavity oil port of the lifting cylinder (1) and an oil inlet of a back pressure valve (5), the oil outlet of the back pressure valve (5) is connected with an oil return pipe of the hydraulic station, the oil return port of the two-way four-way solenoid valve (12) is connected with an oil return pipe, the other oil outlet is connected with the control port of the two-way basic plug-in (11).

2. A differential drop hammer apparatus according to claim 1, wherein: the low-pressure energy accumulator (3) and the high-pressure energy accumulator (4) are both airbag type energy accumulators.

3. A differential drop hammer apparatus according to claim 1, wherein: the back pressure valve (5) is any valve body of a two-way cartridge valve and a one-way valve which are composed of an overflow valve, an overflow valve and a two-way plug-in with a damping hole and have a pressure regulating function.

4. A differential drop hammer apparatus according to claim 1, wherein: the lifting cylinder (1) is provided with a plurality of rodless cavity oil ports and a plurality of lifting valves (2), and the two-way basic plug-in components (11) share one two-position four-way electromagnetic valve (12) for control.

5. A differential drop hammer device according to any one of claims 1 to 4, wherein: the lifting valve (2) is replaced by any valve body of a two-position four-way reversing valve (13) or a three-position four-way reversing valve, wherein the two-position four-way reversing valve (13) is provided with P, T, B oil ports and an A oil port, an oil port P, T, B of the two-position four-way reversing valve (13) is normally open, B, T is normally open or four oil ports are normally open, a pressure pipe of the hydraulic station is connected with a high-pressure energy accumulator (4) and a P oil port of the two-position four-way reversing valve (13), the A oil port of the two-position four-way reversing valve (13) is closed or communicated with a T oil port, an oil port B of the two-position four-way reversing valve (13) is connected with a low-pressure energy accumulator (3), a rodless cavity oil port of a.

6. A differential drop hammer apparatus according to claim 5, wherein: the drop hammer system further comprises a liquid filling valve (15), the liquid filling valve (15) is a two-way cartridge valve, the liquid filling valve (15) and the lift valve (2) share one two-position four-way solenoid valve (12) for control, an oil inlet of the two-position four-way solenoid valve (12) is connected with a pressure pipe of a hydraulic station, an oil return port of the two-position four-way solenoid valve (12) is connected with an oil return pipe of the hydraulic station or an oil port of a rodless cavity of the lift cylinder (1), two oil outlets of the two-position four-way solenoid valve (12) are respectively connected with control ports of the two-way basic cartridge of the liquid filling valve (15) and the lift valve (2), a pressure pipe of the hydraulic station is connected with an oil inlet of a high-pressure energy accumulator (4) and the liquid filling valve (15), an oil outlet of the liquid filling valve (15) is connected with a rod cavity of the lift cylinder (1) and an oil inlet of the two-way basic cartridge (11), the oil outlet of the back pressure valve (5) is connected with an oil return pipe of the hydraulic station.

7. A differential drop hammer apparatus as claimed in claim 6, wherein: the two-position four-way electromagnetic valve (12) is independently arranged or is combined with any two-way basic plug-in component (11) to form a two-way plug-in valve, one oil outlet of the two-position four-way electromagnetic valve (12) is connected with an oil outlet of the liquid filling valve (15), and the other oil outlet of the two-position four-way electromagnetic valve is connected with a control port of the two-way basic plug-in component (11).