CN207567849U - A kind of quartering hammer with fluid pressure support piston function - Google Patents
A kind of quartering hammer with fluid pressure support piston function Download PDFInfo
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- CN207567849U CN207567849U CN201721423848.0U CN201721423848U CN207567849U CN 207567849 U CN207567849 U CN 207567849U CN 201721423848 U CN201721423848 U CN 201721423848U CN 207567849 U CN207567849 U CN 207567849U
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Abstract
The utility model discloses a kind of quartering hammers with fluid pressure support piston function, including middle cylinder, the piston of reciprocating motion is installed in middle cylinder, piston is installed by support liquid mechanism supports and middle cylinder clearance fit, the utility model is by setting hydraulic support mechanism, make to be supported by original relying only on oil sealing support and increase fluid pressure between piston and cylinder body, it avoids because of pulling between piston and cylinder body caused by oil sealing aging or oil sealing are of poor quality, 3 times or so are increased to the service life of oil sealing again, replacement oil sealing and additional maintenance expense of the oil sealing in the short time are saved, the repair downtime of operator.
Description
Technical field
The utility model is related to hydraulic breaking hammer technical fields, are concretely related to a kind of with fluid pressure support piston
The quartering hammer of function.
Background technology
From the perspective of accompanying piston, the course of work of beater mechanism divides backhaul acceleration, backhaul deceleration, stroke to accelerate and beat
Pause four-stage is hit, this four-stage forms a work period.Backhaul stores energy for stroke, is the preparation rank of stroke
Section.Stroke realizes the accelerated motion of piston, is the process that fluid or gas do work to piston.Strike pauses be piston by kinetic energy with
The form of stress wave is transmitted to the collision process of the objects such as rock by drill steel.
Piston forms closed loop feedback control circuit with reversal valve.Reversal valve is controlled by piston displacement or each chamber oil pressure,
The fluid course of valve is opened and closed when its commutation action is moved by impact piston to complete, the commutation of valve in turn is had switched again into cylinder
The fluid course of body completes the conversion between piston stroke and backhaul, so in cycles, by position feedback automatic performance period
The ballistic motion of property.It, can by shock machine because of piston and the difference of valve core movement cooperation by taking single side oil return is in a manner of oil as an example
The movement of structure is divided into 5 stages.
Quartering hammer（Backhaul）Operation principle is as shown in Figure 1, a. backward stroke of the piston boost phases, and spool is motionless, such as Fig. 1 (a)
Shown, after piston is once impacted with drill steel in completion, there are one instantaneous stopping states.This state is defined as a work period
Original state.Change-over valve core is in end face A5Locate to be in lower limit position under the action of high pressure oil P.
High pressure oil enters piston ante-chamber through cylinder inner bore road, and piston back cavity is through change-over valve core central duct and oil return phase
Even.The nitrogen P for having certain pressure is acted in nitrogen chamber at this time3,To the active force that piston is downward, but nitrogen active force is less than ante-chamber
Fluid active force.Therefore piston accelerates upwards, while compressed nitrogen storage energy.
B. piston continues backhaul acceleration, and spool commutation is as shown in Fig. 1 (b), as the end face A of piston1When crossing hydraulic control hole a,
The high pressure oil P of ante-chamber1It is introduced in the lower face A of reversing valve core4.Because of A4＞ A5, spool moved to upper pole by upward active force
Extreme position.
Quartering hammer（Stroke）Fundamental diagram is as shown in Figure 2：
C. backward stroke of the piston is slowed down, and spool is motionless as shown in Fig. 2 (c), and high pressure oil P enters piston through valve core inside duct
Back cavity.Piston front/back cavity leads to high pressure oil simultaneously and forms differential connection at this time.But A2＞ A1, fluid active force suffered by piston to
Under.Piston is simultaneously by downward nitrogen active force.Therefore, piston accelerates end speed to do retarded motion as initial velocity using backhaul,
Until speed is 0.
D. piston stroke accelerates, and spool is motionless as shown in Fig. 2 (d), and piston has slowed down is in backhaul maximum displacement for 0
Position.Compared with the backhaul decelerating phase, the force direction of this stage nitrogen and fluid does not change, therefore piston is in zero initial velocity
It is accelerated under degree.
E. piston strike idle periods, spool commutation hit pricker as shown in Fig. 3 (e) when piston motion is to lower limit position
Bar.While strike is collided, piston end surface B1Downward across hydraulic control hole a so that spool lower face A4Be detached from high pressure oil and with
Oil return communicates, and such reversal valve is forced downwards to be returned to lower limit position.Beater mechanism enters next work period, i.e.,
In state a.
The quartering hammer of above structure, when tilting broken, big specification piston dead weight be can not ignore, and piston is difficult to by this spy's envelope
Support, piston face is caused to abrade, pull with middle cylinder inner bore, its tired longevity under impact loading of the surface after pulling
Order extremely low, and gas leak of the oil leakage.
Fig. 4：Traditional quartering hammer middle cylinder is schemed with piston cooperation
1 piston and 6 middle cylinders are clearance fit, and 2 dust seals, 3 main oil sealings and 4 bufferings seal interior point of cylinder body notch in being mounted on 6
Do not play a part of dust-proof, oil-leakage-prevention and support.It is clearance fit between 8 piston rings and 6 middle cylinders, 8 piston rings mainly play solid
The effect of fixed piston, 7O types circle, 9 this spy envelope and 10 sealing glands be separately mounted in 8 piston ring inner circle notches, play respectively support and
Seal the effect of gas.
Traditional 1 piston structure of cylinder body pulls failure mode and reason：The frictional force of 1 piston be with cylinder body mating surface in 6, by
It beats to cause to be in direct contact between 6 middle cylinders and piston partially in the support force deficiency of 1 piston and operator and pull.
The position that piston friction crackle generates：Mainly 1 is learnt from 6 middle cylinder of Fig. 4 tradition quartering hammer and 1 piston cooperation figure
Oil groove and hit two discs at end and cylinder body coordinates among piston, therefore, 1 piston in the friction of cylinder body pull mainly by this two
At a circle.
The condition that crackle generates：Impact+friction, friction are 60- the main reason for causing part failure and material consumption
The failure of 80% machine components is as caused by abrasion, and about 30% abrasion in different forms of the energy of world industry developed country disappears
Consumption.Therefore monitor mechanical equipment fretting wear state, identification equipment premature wear failure for machine energy-saving consumption-reducing, rationally
Operation and safety in production are respectively provided with important meaning.
The calculating of frictional force：
Frequency of impact determines every stroke required time namely time it is known that stroke s is it is known that by Formula V2 t—V2 0=2as；
End speed Vt=V0+at, in formula：T is calculated by frequency of impact, V0=0, a can be obtained by bringing end speed into above formula, it is known that frequency of impact
F, then cycle T=1/f, every half stroke take t=T`=1/2f and then seek motive force of the compressed nitrogen to piston, when this makes every effort to
Afterwards, the ratio that frictional force accounts for motive force has certain range；
Object working surface is called abrasion due to the phenomenon that relative motion is lost without breakdown.Two contact surfaces are rolled or are rolled
Dynamic when sliding compound friction, in the case where alternation contacts action of compressive stress, the phenomenon that making material surface fatigue and generating material damage, is named
Do Surface fatigue wear；
Adhesive wear：Due to real contact area very little between the secondary two antithesis surfaces of friction, contact point stress is very high, contact point
Temperature is sometime up to 1000 DEG C, even higher, and substrate temperature is generally relatively low, therefore once disengages, contact point temperature
Just it is rapid to decline（Contact point high-temperature duration only has several ms under normal circumstances)
The influence factor of abrasion
Area mean pressure, i.e. normal load divided by nominal contact area.When area mean pressure is less than σ s, wear intensity
Stablize constant；
When area mean pressure is more than σ s, wear intensity increased dramatically, and be changed into sharp wear by slowly wearing, when serious
Kill phenomenon.This is because when area mean pressure is less than σ s, the plastically deforming area under the micro- peak to contact with each other is most absolutely
Number is independent from each other, and at this moment real contact area is directly proportional to normal load, and contact stress will not be because of the increasing of normal load
Increase greatly；
When area mean pressure is more than σ s, the plastically deforming area interaction under the micro- peak to contact with each other, entire surface layer
All it is in Plastic Flow state, at this moment real contact area no longer increases with the increase of normal load, adhesion wear easily occurs
Phenomenon.
Frictional force：The frictional force confrontation fatigue wear of contact surface has important influence.In general, the frictional force of pure rolling
Only the 1%~2% of normal load, and introduce after slip, frictional force rises to 10% or even bigger of normal load.
Frictional force promote During Contact Fatigue the reason of be：Frictional force effect makes maximum shear stress position tend to surface, increases
The possibility that crackle has been added to generate.In addition, the tensile stress caused by frictional force can promote crack propagation to accelerate.
Cyclic Stress speed also influences contact fatigue, and since friction surface all generates heat in each contact, stress follows
Ring speed is bigger, and surface area heat build-up amount and temperature are higher, makes metal softening and reduces mechanical performance, therefore accelerates surface fatigue
Abrasion.
The fatigue wear of surface germinating is occurred mainly in the friction pair based on slip, and crackle is happened on friction surface
Stress raiser, such as cutting mark, damage, corrode or the trace of other abrasions etc..At this point, crackle by surface with cunning
Direction is moved into 20 degree ~ 40 degree angular surface layer internal extendeds.
Either annealed steel or quenched and tempered steel, the pure rolling or friction pair for rolling and sliding, pitting cracking originate from table
Face, then extended along rotating direction into surface layer, and form fan-shaped fatigue hole.
Solution：Using hydraulic pressure support, abrasion is reduced, destroys crackle formation condition.
Utility model content
The technical problem to be solved by the present invention is to provide it is a kind of with fluid pressure support piston function quartering hammer,
Mainly increase support to piston to solve due to oil sealing aging, pulling between middle cylinder body and piston caused by the factors such as beating partially is asked
Topic.
To solve the above-mentioned problems, the utility model uses following technical scheme：
A kind of quartering hammer with fluid pressure support piston function, including middle cylinder, reciprocating motion is equipped in middle cylinder
Piston, piston are installed by support liquid mechanism supports and middle cylinder clearance fit.
It is that the utility model advanced optimizes said program below：
First three road of oil sealing is installed close to the position of one end in the middle cylinder to combine, the position in middle cylinder close to the other end is same
Axis is equipped with piston ring, in piston ring close to the position of one end be coaxially equipped with oil sealing after three combinations.
It advanced optimizes：The support liquid mechanism is included in piston ring close to the position of three combination sides after oil sealing
The rear hydrostatic bearing coaxially assembled.
It advanced optimizes：It is offered and the oil return in middle cylinder close to the position of first three road of oil sealing combination side in the middle cylinder
The first oil-recovery tank that road communicates, the position in middle cylinder close to the first oil-recovery tank side are coaxially equipped with preceding hydrostatic bearing.
It advanced optimizes：Corresponding position is combined with after oil sealing three offer the second oil-recovery tank in the middle cylinder.
It advanced optimizes：Circular array shows at least four oil inlets respectively on the preceding hydrostatic bearing and rear hydrostatic bearing.
It advanced optimizes：On the inner wall of the preceding hydrostatic bearing or rear hydrostatic bearing with the corresponding position of each oil inlet
The oil pocket of arcuate structure is offered respectively, and each oil pocket connects respectively with corresponding oil inlet.
It advanced optimizes：Third oil return is offered respectively along the axial direction of the hydrostatic bearing between the wantonly two adjacent oil pocket
Slot.
It advanced optimizes：Each third oil-recovery tank extends respectively to corresponding preceding hydrostatic bearing or rear hydrostatic bearing
Both ends.
The utility model makes to rely only on oil sealing support by original between piston and cylinder body by setting hydraulic support mechanism
Fluid pressure support is increased again, avoids the drawing because caused by oil sealing aging or oil sealing are of poor quality between piston and cylinder body
Wound, and 3 times or so are increased to the service life of oil sealing, save replacement oil sealing and additional repair of the oil sealing in the short time
Upkeep cost, the repair downtime of operator.
The utility model is suitable for full hydraulic, nitrogen explosion type, dynamic hydraulic combined formula hydraulic crushing by power source classification
Hammer；Suitable for pressing triangular form, the square of rack formal classification（Tower）, box（Mute type）Hydraulic breaking hammer；It is not limited to liquid
Press the size specification of quartering hammer；It is not limited to single side oil return, two-sided oil return hydraulic breaking hammer；It has been not limited to valve-type, valveless type hydraulic pressure
Quartering hammer；It is not limited to that control valve is built-in, external hydraulic quartering hammer；It is not limited to control valve travel feedback formula, pressure-feedback-type
Hydraulic breaking hammer.
The utility model is described in further detail with reference to the accompanying drawings and examples.
Description of the drawings
Attached drawing 1 is the utility model quartering hammer in the background technology（Backhaul）Fundamental diagram；
Attached drawing 2 is the utility model quartering hammer in the background technology（Stroke）Fundamental diagram；
Attached drawing 3 is the utility model quartering hammer in the background technology（It pauses）Fundamental diagram；
Attached drawing 4 for the utility model, with piston cooperation scheme in the background technology by traditional quartering hammer middle cylinder；
Structure diagram of the attached drawing 5 for the utility model hydraulic shock quartering hammer in embodiment；
Attached drawing 6 is the utility model fundamental diagram of film feedback and hydrostatic bearing in embodiment；
Attached drawing 7 is the utility model connection relationship diagram of flow controller and preceding hydrostatic bearing in embodiment；
Attached drawing 8 is the utility model connection relationship diagram of flow controller and rear hydrostatic bearing in embodiment.
In figure：1- pistons；2- dust seals；The main oil sealings of 3-；4- buffering envelopes；5- middle cylinders；6-O type circles；7- piston rings；8- Si is special
Envelope；9- sealing glands；10- drill steels；Cylinder under 11-；12- cotter pilotages；Hydrostatic bearing before 13-；14- middle cylinders；Hydrostatic bearing after 15-；On 16-
Cylinder；It combines in first three road of 17- oil sealings；Three combination after 18- oil sealings；19- flow controllers；The first oil-recovery tanks of 20-；21- oil inlets；22-
Second oil-recovery tank；23- oil pockets；24- epicoeles；25- cavity of resorptions；26- third oil-recovery tanks；27- circumferential direction oil sealing surfaces；Ps- input pressures；T-
Piston cycle；Every half stroke of t- pistons takes；S- piston strokes；F- piston impact frequencies；V- piston speeds；A- piston strokes；
V0Piston initial velocity；ViPiston end speed.
Specific embodiment
Embodiment, as shown in Fig. 5 to Fig. 8, a kind of quartering hammer with fluid pressure support piston function, including middle cylinder
14, the piston 1 of reciprocating motion is installed, piston 1 is installed by support liquid mechanism supports and 14 clearance fit of middle cylinder in middle cylinder 14.
First three road of oil sealing combination 17 is coaxially installed with close to the position of one end in the middle cylinder 14, close to another in middle cylinder 14
The position at end is coaxially installed with piston ring 7.
The position of close one end is coaxially equipped with three combinations 18 after oil sealing in the piston ring 7.
The support liquid mechanism is included after coaxially being assembled close to the position of three combinations 18 after oil sealing in piston ring 7
Hydrostatic bearing 15.
Offer what is communicated with the back oil road in middle cylinder 14 close to the position of first three road of oil sealing combination 17 in the middle cylinder 14
First oil-recovery tank 20.
First oil-recovery tank 20 is loop configuration, and its cross section is trapezoidal.
In the middle cylinder 14 preceding hydrostatic bearing 13 is coaxially equipped with close to the position of 20 side of the first oil-recovery tank.
18 corresponding positions being combined with after oil sealing three in the middle cylinder 14 and offering the second oil-recovery tank 22, this is second time
One end of oil groove 22 is communicated with the back oil road in middle cylinder 14, and the gap between the other end and piston ring 7 and piston 1 communicates, in this way
The hydraulic oil of rear hydrostatic bearing 15 can be delivered in the back oil road in middle cylinder 14 by design.
Circular array shows at least four oil inlets 21 respectively on the preceding hydrostatic bearing 13 and rear hydrostatic bearing 15.
The symmetrically arranged oil inlet 21 of each two is connected separately with a flow controller 19, and each flow controller 19 is solid respectively
Dingan County is outer close to the position of corresponding hydrostatic bearing mounted in middle cylinder 14.
Distinguish on the inner wall of the preceding hydrostatic bearing 13 or rear hydrostatic bearing 15 with each 21 corresponding position of oil inlet
The oil pocket 23 of arcuate structure is offered, the depth of oil pocket 23 is Z1, Z1=30-60h0, h0It is piston with after（Before）Hydrostatic bearing is matched
The gap of conjunction.
Each oil pocket 23 connects respectively with corresponding oil inlet 21, and oil inlet 21 is communicated and begun with the oil input channel of cylinder body
It is eventually high pressure oil, high pressure oil enters oil pocket 23, and high pressure oil is surround after entering cylinder body with piston 1, and multi-faceted high pressure oil supports
Piston is suspended in cylinder body, is not easy to directly contact with cylinder body.
Third oil-recovery tank 26, third are offered respectively along the axial direction of the hydrostatic bearing between described wantonly two adjacent oil pockets 23
The depth of oil-recovery tank 26 is Z2, Z2Numerical value chosen between 0.6-1.3mm, in this way design be to ensure holding for hydrostatic bearing
Loading capability and oil circuit it is unimpeded.
Angle between the center line and adjacent oil inlet 21 of each third oil-recovery tank 26 is π/4.
Each third oil-recovery tank 26 extends respectively to the both ends of corresponding preceding hydrostatic bearing 13 or rear hydrostatic bearing 15,
Design is primarily to make the oil in preceding hydrostatic bearing 13 or rear hydrostatic bearing 15 uniformly be pooled to 14 oil duct of middle cylinder in this way
In oil return system.
Circumferential oil sealing surface 27 is respectively formed between the adjacent third oil-recovery tank 26 and oil pocket 23, each circumferential direction oil sealing surface
27 width is b1, b1=0.1 hydrostatic bearing aperture, design is in order to which oil pocket is made to set up required pressure in this way.
There are two types of oil inlet modes for the flow controller 19, and mode as shown in Figure 7, Figure 8 is by 21 fuel feeding of oil inlet, into oil
In chamber 23, flowed out respectively by the first oil-recovery tank 20 and the second oil-recovery tank 22 through third oil-recovery tank 26；It can also lead to respectively in turn
The first oil-recovery tank 20 and the second oil-recovery tank 22 are crossed to 26 fuel feeding of third oil-recovery tank, hydraulic oil enters in oil pocket 23 and by oil inlet 21
Outflow.
The middle part of each flow controller 19 is provided with film, between the inner wall of the upper surface of the film and the flow controller 19
It is cavity of resorption 25 for epicoele 24, between the lower face of the film and the inner wall of the flow controller 19.
One end in the middle cylinder 14 close to piston ring 7 has been bolted to connection upper cylinder half 16.
In the middle cylinder 14 lower cylinder 11, lower cylinder 11 have been bolted to connection close to one end of first three road of oil sealing combination 17
The drill steel 10 of reciprocating motion is inside provided with, drill steel 10 is fixed by cotter pilotage 12 and controls its reciprocating stroke.
As shown in fig. 6, film feedback and the operation principle of hydrostatic bearing：
hg：When pressure differential is 0, the film of flow controller 19 is in the state that maintains an equal level, hg1=hg3。
Hydraulic pressure support operation principle：
Illustrating by taking thin film restrictor as an example, thin film restrictor directly utilizes pressure feedback Throttle Principle, when bearing zero load,
Piston is in concentric with bearing, and upper lower oil cavitie pressure is identical, thus the pressure of film both sides is equal, and film is in flat
State；
When piston is by downward load, piston axes attempt to move down, if eccentricity is e, upper and lower two oil pocket goes out
Oil-gap changes, and flow is caused to change, and makes that upper oil cavitie oil pressure becomes smaller according to the pressure regulation effect of flow controller and lower oil cavitie oil pressure becomes larger,
Pressure differential resists outer carry；
Meanwhile pressure differential also forces the film of flow controller to raise up, and upper and lower throttle clearance is made accordingly to change：Epicoele throttles
Device gap is by hgIt is reduced to hg1, that is, the throttling liquid resistive for adjusting upper oil cavitie is big, and upper cavity pressure is promoted more to reduce；Equally, cavity of resorption
Throttle clearance is by hgIncrease to hg1, i.e. adjusting throttling cavity of resorption liquid resistive is small, promotes PsRaising.In this way, resist the outer pressure differential carried
Just further increase, makes the position of piston be gone up, and by very short time, reaches new under being deviated in less axle center and puts down
Weighing apparatus.
In use, piston 1 is supported by hydraulic support mechanism moves back and forth strike drill steel 10, and pass through drill steel 10 and transmit strike
Power crushes object, while the first oil-recovery tank 20 and the second oil-recovery tank 22 form circuit with hydraulic support mechanism, by hydraulic pressure support machine
The oil that structure sprays is delivered to oil return system.
The utility model makes to rely only on oil sealing support by original between piston and cylinder body by setting hydraulic support mechanism
Fluid pressure support is increased again, avoids the drawing because caused by oil sealing aging or oil sealing are of poor quality between piston and cylinder body
Wound, and 3 times or so are increased to the service life of oil sealing, save replacement oil sealing and additional repair of the oil sealing in the short time
Upkeep cost, the repair downtime of operator, the utility model are suitable for the full hydraulic by power source classification, nitrogen outburst
Formula, dynamic hydraulic combined formula hydraulic breaking hammer；Suitable for pressing triangular form, the square of rack formal classification（Tower）, box（It is mute
Type）Hydraulic breaking hammer；It is not limited to the size specification of hydraulic breaking hammer；It is not limited to single side oil return, two-sided oil return hydraulic breaking hammer；No
It is limited to have valve-type, valveless type hydraulic breaking hammer；It is not limited to that control valve is built-in, external hydraulic quartering hammer；It is not limited to control valve
Travel feedback formula, pressure-feedback-type hydraulic breaking hammer.
Claims (7)
1. a kind of quartering hammer with fluid pressure support piston function, including middle cylinder（14）, middle cylinder（14）It is inside equipped with reciprocal
The piston of movement（1）, it is characterised in that：Piston（1）By support liquid mechanism supports and middle cylinder（14）Clearance fit is installed, middle cylinder
（14）The position of interior close one end is equipped with the combination of first three road of oil sealing（17）, middle cylinder（14）Coaxially pacify the position of the interior close other end
Equipped with piston ring（7）, piston ring（7）The position of interior close one end is coaxially equipped with three combinations after oil sealing（18）, support liquid
Mechanism is included in piston ring（7）Three combination after interior close oil sealing（18）The rear hydrostatic bearing that the position of side is coaxially assembled
（15）.
2. a kind of quartering hammer with fluid pressure support piston function according to claim 1, it is characterised in that：It is described
Middle cylinder（14）It is upper to be combined close to first three road of oil sealing（17）The position of side offers and middle cylinder（14）On back oil road communicate
One oil-recovery tank（20）, middle cylinder（14）Upper close first oil-recovery tank（20）The position of side is coaxially equipped with preceding hydrostatic bearing（13）.
3. a kind of quartering hammer with fluid pressure support piston function according to claim 2, it is characterised in that：It is described
Middle cylinder（14）It is upper to be combined with after oil sealing three（18）Corresponding position offers the second oil-recovery tank（22）.
4. a kind of quartering hammer with fluid pressure support piston function according to claim 3, it is characterised in that：It is described
Preceding hydrostatic bearing（13）With rear hydrostatic bearing（15）Upper circular array respectively shows at least four oil inlets（21）.
5. a kind of quartering hammer with fluid pressure support piston function according to claim 4, it is characterised in that：It is described
Preceding hydrostatic bearing（13）Or rear hydrostatic bearing（15）Inner wall on each oil inlet（21）Corresponding position offers respectively
The oil pocket of arcuate structure（23）, each oil pocket（23）Respectively with corresponding oil inlet（21）Connection.
6. a kind of quartering hammer with fluid pressure support piston function according to claim 5, it is characterised in that：It is described
Wantonly two adjacent oil pockets（23）Between along the axial direction of the hydrostatic bearing offer third oil-recovery tank respectively（26）.
7. a kind of quartering hammer with fluid pressure support piston function according to claim 6, it is characterised in that：It is described
Each third oil-recovery tank（26）Extend respectively to corresponding preceding hydrostatic bearing（13）Or rear hydrostatic bearing（15）Both ends.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721423848.0U CN207567849U (en) | 2017-10-31 | 2017-10-31 | A kind of quartering hammer with fluid pressure support piston function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201721423848.0U CN207567849U (en) | 2017-10-31 | 2017-10-31 | A kind of quartering hammer with fluid pressure support piston function |
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| Publication Number | Publication Date |
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| CN207567849U true CN207567849U (en) | 2018-07-03 |
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ID=62692718
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| CN201721423848.0U Active CN207567849U (en) | 2017-10-31 | 2017-10-31 | A kind of quartering hammer with fluid pressure support piston function |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989107A (en) * | 2017-10-31 | 2018-05-04 | 山东天瑞重工有限公司 | Hydraulic shock quartering hammer with fluid pressure support piston function |
| CN112411660A (en) * | 2020-10-27 | 2021-02-26 | 天津辰龙重工机械有限公司 | Inlay cover type hydraulic breaking hammer |
-
2017
- 2017-10-31 CN CN201721423848.0U patent/CN207567849U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989107A (en) * | 2017-10-31 | 2018-05-04 | 山东天瑞重工有限公司 | Hydraulic shock quartering hammer with fluid pressure support piston function |
| CN107989107B (en) * | 2017-10-31 | 2024-01-26 | 山东天瑞重工有限公司 | Hydraulic impact breaking hammer with hydrostatic pressure supporting piston function |
| CN112411660A (en) * | 2020-10-27 | 2021-02-26 | 天津辰龙重工机械有限公司 | Inlay cover type hydraulic breaking hammer |
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