CN217481650U - Middle cylinder part of hydraulic breaking hammer - Google Patents

Abstract

The utility model discloses a cylinder part in hydraulic breaking hammer, well cylinder part includes well cylinder body, piston ring, switching-over valve and sealing member, well cylinder body inner pore structure from left to right is in proper order from the piston head direction: the piston ring sealing structure comprises a sealing piece groove, an oil return groove, a front cavity, a clearance sealing section E matched with a piston rod, a buffer cavity, a middle cavity, a clearance sealing section F matched with the piston rod, a rear cavity and a piston ring hole; the front cavity and the middle cavity are high-pressure oil cavities, high-pressure oil is always introduced during work, the rear cavity is a variable-pressure cavity, a piston ring inner hole and a piston rod rear section are matched to form a gap sealing section G and a sealing part sealing section, the gap sealing section E, F, G is always introduced with the high-pressure oil, the whole piston is supported by the sealing part and a high-pressure oil film of the gap sealing section during work, the pull damage to the outer circle surface of the piston and the inner hole surface of the middle cylinder body is avoided, the oil leakage phenomenon caused by the pull damage is obviously reduced, and meanwhile the damage rate of the sealing part is reduced.

Description

Middle cylinder part of hydraulic breaking hammer

Technical Field

The utility model relates to a hydraulic breaking hammer technical field especially relates to cylinder parts among hydraulic breaking hammer.

Background

The hydraulic breaking hammer is a breaking machine which converts hydraulic energy into mechanical impact energy, automatically completes high-frequency reciprocating motion of a piston in a cylinder body through mutual feedback control of a valve control system and a cylinder body piston system under the drive of high-pressure oil, and achieves the construction purposes of breaking rocks or concrete and the like through striking a drill rod to output energy.

The prior art cylinder body part (see figure 1) mainly comprises a middle cylinder body 1, a piston 2, a piston ring 3 and a reversing valve 4. The front section of the inner hole structure of the middle cylinder body is a sealing groove from left to right and the front three ways from the piston head direction, the fourth way is an oil return groove, the oil return groove and the outer circle surface of the piston form an oil return cavity, oil is always returned during working and is in normal low pressure, an inner hole of a cylindrical section close to the oil return groove on the right is matched with the outer circle surface of the piston to form a gap sealing section A, a front cavity of an oil cylinder is formed by the inner hole of the middle cylinder body close to the gap sealing section A on the right and the outer circle surface of the piston, and the front cavity is a normal high pressure cavity during working; meanwhile, clearance sealing sections B and C are sequentially formed on the surface of the outer circle of the middle section of the piston and the surface of the inner hole of the middle cylinder body, the rear section of the inner hole of the middle cylinder body and the piston form a rear cavity of the oil cylinder, the rear cavity is a variable pressure cavity (high pressure during piston stroke and low pressure during piston return stroke), the large hole at the rightmost end of the rear section of the inner hole of the middle cylinder body is used for installing a piston ring, an oil return ring groove is arranged in the large hole, and the ring groove is communicated with oil return all the time. When the hydraulic hammer works, when the piston does return stroke motion from left to right in the middle cylinder body, the front cavity is a high-pressure cavity, the back cavity is a low-pressure cavity, oil films in the gap sealing sections A and B generate high-pressure oil films under the action of high-pressure oil of the front cavity, and the front section of the piston and the front section of the middle section of the piston are well supported, but because the back cavity is a low-pressure cavity, the oil films in the gap sealing section C belong to low-pressure oil films, the supporting force for the piston is limited, because the gap sealing sections A and B are positioned in the middle front section of the whole piston, when the piston generates lateral force in work and the piston generates lateral force due to self-weight when the piston is in an inclined or horizontal working state, the piston generates eccentric motion in the cylinder body, so that the excircle surface of the middle and back sections of the piston in the gap sealing section C is in contact with the inner hole wall of the middle cylinder body, the excircle surface of the middle and the inner hole of the middle and back sections of the middle cylinder body are pulled, sometimes, due to the unbalanced support of the piston, the piston is inclined in the cylinder body, and the gap sealing section a is also damaged by pulling.

In addition, when the piston strokes, because the front section of the piston is longer, the front section of the piston continues to run to the sealing section of the sealing part at the front end of the piston after passing through the gap sealing section A in the strokes, the surface of the piston which is pulled to be damaged further damages the sealing part at the front section at the moment, so that the lip (inner hole) of the sealing part is pulled to be damaged by the outer surface of the piston which is pulled to be damaged, the phenomena of oil leakage and weak hitting of the breaking hammer are caused, the working performance of the breaking hammer is influenced and reduced, even the working capacity is lost, and the breaking hammer is finally scrapped.

SUMMERY OF THE UTILITY MODEL

Technical problem to be solved

The utility model provides a not enough to prior art, the utility model provides a hydraulic breaking hammer well jar part, the piston of having solved hydraulic breaking hammer is because its self is heavier, and the unbalanced supporting force of the original decrement of sealing member and clearance seal section is difficult to undertake the supporting role, causes the piston eccentric motion to lead to piston surface and cylinder body hole surface contact in the cylinder body, and then strains piston and cylinder body inner surface, appears the breaking hammer oil leak, strikes powerless problem.

(II) technical scheme

In order to achieve the above purpose, the utility model discloses a following technical scheme realizes: a cylinder assembly for a hydraulic breaker.

Referring to fig. 2, the middle cylinder part of the hydraulic breaking hammer comprises a middle cylinder body 1, a piston 2, a piston ring 3, a reversing valve 4 and a seal, wherein the inner hole structure of the middle cylinder body 1 sequentially comprises from left to right in the piston head direction: the piston ring sealing structure comprises a sealing piece groove, an oil return groove, a front cavity 12, a clearance sealing section E matched with a piston rod, a buffer cavity 15, a middle cavity 16, a clearance sealing section F matched with the piston rod, a rear cavity 17 and a piston ring hole; the front cavity and the middle cavity are high-pressure oil cavities, high-pressure oil is always introduced in the front cavity and the middle cavity during working, the rear cavity is a variable-pressure cavity, and the inner hole gap sealing section E, F is always under the action of the high-pressure oil.

Preferably, one: the piston is integrally in the shape of a shaft cylinder, the diameters of the outer circles of the front section, the middle section and the rear section of the piston are different, the diameter of the front section of the piston is d1, the middle section of the piston is divided into two or more sections of cylinder tables with different or identical diameters, if the middle section of the piston is divided into two sections, as shown in fig. 4, the length of the middle section 22 of the piston is L1, the length of the middle section 221 of the piston is L2, the diameter of the middle section of the piston is d2, the length of the middle section 222 of the piston is L3, the diameter of the middle section of the piston is d4, a groove 223 is arranged on the middle section 221 of the piston, the length of the middle section of the piston is L4, and the diameter of the rear section 23 of the piston is d 5; the diameter d5 of the rear piston section 23 is smaller than the diameter d1 of the front piston section 21, the diameter d1 of the front piston section 21 is smaller than the diameter d2 of the middle front piston section 221, the diameter d2 of the middle front piston section 221 is smaller than the diameter d4 of the rear piston section 222, namely d5< d1< d2< d 4; a. b, c, e and f are respectively the step end faces of each cylindrical section, wherein a is the left end face of the front section 221 in the piston, b and c are respectively the end faces of the left end and the right end of the groove 223 of the middle section 22 in the piston, and e and f are respectively the left end face and the right end face of the rear section 222 in the piston;

in addition, the groove 223 divides the front section 221 of the piston into left and right sections, both of which have a diameter d2, but the tolerances may be different. In addition, under the prerequisite that does not influence the utility model discloses implement the effect, can set up more than one recess on anterior segment 221 in the piston.

A further technical scheme is preferable: referring to fig. 4, a relief groove 224 is provided between the front section 221 and the rear section 222 of the middle section 22 of the piston, so that the relief groove can be extended to a groove with a width of L7 without affecting the function of the middle section of the piston.

A further solution is preferred: referring to fig. 9, the middle-rear section 222 of the piston may be divided into two parts with different diameters, the left-section part 225 has a diameter d3 and a length L8, the right-section part 226 has a diameter d4 and a length L9, L9 is larger than L8, e is a left end face of 225, g and f are respectively a left end face and a right end face of 226, and d5< d1< d2< d3< d4 in the present embodiment.

Preferably, referring to fig. 5, for matching with a preferred piston structure, a first sealing groove 51, a second sealing groove 52, an oil return groove 11 at the front section of the inner hole of the cylinder body, a third sealing groove 53 and a front cavity 12 are sequentially arranged at the front section of the inner hole structure of the middle cylinder body 1 from left to right in the direction of the piston head, the front cavity 12 is a high-pressure oil cavity formed by the right side of a sealing element in the rightmost sealing element groove 53, the inner hole at the front section of the middle cylinder body is communicated with a high-pressure oil way, and high-pressure oil is always introduced in the front cavity during working. In addition, on the premise of realizing the effect of the technical scheme, the number and the arrangement positions of the sealing pieces and the oil return grooves can be changed according to different types of the specific breaking hammers.

Preferably, the middle piston section 22 of the piston 2 structure is matched with the inner hole surface of the middle cylinder body 1, a gap sealing section E, a buffer cavity 15, a middle cavity 16 and a gap sealing section F are sequentially formed from left to right in the piston head direction, a reversing control port groove 13 and a normal and low pressure groove 14 are sequentially arranged on the inner hole of the middle cylinder body of the gap sealing section E on the left side of the buffer cavity 15, the reversing control port groove 13 is communicated with a reversing port 41 of a reversing valve through an internal oil passage, the normal and low pressure groove 14 is arranged on the right side of the reversing control port groove 13 and is normally communicated with oil, and the distance L5 between the right end face 141 of the normal and low pressure groove 14 and the left end face 151 of the buffer cavity 15 is larger than the width L4 of a groove 223 on the middle piston section 22, so that high-pressure oil in the middle working cavity is prevented from being communicated with the normal and low pressure groove 14, and system pressure release is caused.

Referring to fig. 3, when the piston is idle or the breaking hammer needs to move when not in operation, the piston moves downward, the e-end surface of the middle and rear sections 222 of the piston and the cylinder form a closed cavity, namely a buffer cavity 15, and the buffer cavity 15 is communicated with the middle cavity 16 when the piston normally works.

The preferable three further technical schemes are as follows: referring to fig. 7, a high pressure oil groove, but not limited to, is added between the front chamber 12 and the directional control port groove 13, and high pressure oil is normally supplied. For a large piston, the length of the gap sealing section E is correspondingly increased, and a high-pressure oil groove 10 is additionally arranged for preventing the high-pressure oil in the front cavity from being incapable of fully filling the gap sealing section E.

Preferably, the fourth step: referring to fig. 5 or 6, a stepped hole for mounting the piston ring 3 is formed in the right end of the inner hole of the middle cylinder body 1, the right end of the stepped hole is a large hole, the left end of the stepped hole is a small hole, a fourth sealing groove 54, a fifth sealing groove 55 and a sixth sealing groove 56 are sequentially formed in the large hole of the stepped hole from left to right in the piston head direction, a normal high-pressure groove 18 is formed in the sealing grooves and between the fourth sealing groove 54 and the fifth sealing groove 55, the normal high-pressure groove is normally filled with high-pressure oil, and an inner hole rear-section oil return groove 19 is formed between the fifth sealing groove 55 and the sixth sealing groove 56.

Preferably, the four further technical schemes are as follows: the surface of the inner hole of the piston ring 3 is matched with the surface of the outer circle of the piston rear section 23, a gap sealing section G and a sealing piece sealing section are sequentially formed from left to right, the sealing piece sealing section is sequentially provided with a first piston ring sealing groove 31, a piston ring oil return groove 32, a second piston ring sealing groove 33 and a third piston ring 34 sealing groove, and the piston ring oil return groove 32 is communicated with the inner hole rear section oil return groove 19 on the middle cylinder body through an oil return radial through hole 36.

Preferably, the fourth further technical scheme is as follows: the matching of the length L6 of the small hole of the stepped hole, the length of the assembled piston ring can be correspondingly increased by L6, the gap sealing section G between the surface of the inner hole of the piston ring 3 and the outer circle surface of the piston rear section 23 is prolonged to a rear cavity, a plurality of balance grooves are arranged in the inner hole of the piston ring of the gap sealing section G, the radial through hole 35 of high-pressure oil is arranged on the right side of the last balance groove and the left side of the first piston ring sealing groove 31, and the radial through hole 35 of the high-pressure oil is communicated with the normal-high pressure groove 18 of the stepped hole of the piston ring on the middle cylinder body.

The utility model discloses the theory of operation, refer to fig. 5, fig. 6 shows, under the hydraulic pressure quartering hammer operating condition, when the piston return stroke, fluid in antechamber 12 and the lumen 16 is high-pressure oil, back chamber 17 leads to the oil return and is the low pressure, high-pressure oil is used in the a terminal surface of piston 2 and the motion of e terminal surface promotion piston 2 right side, when the a terminal surface on piston 2 crosses the switching-over control mouth slot 13 on the well cylinder body 1, high-pressure oil in antechamber 12 passes through switching-over control mouth slot 13 and the switching-over valve switching-over mouth 41 departments of inside oil duct flow direction switching-over valve and promotes the switching-over valve switching-over, accomplish the return stroke motion, for the stroke motion on next step has prepared. In the process, because the oil in the front cavity 12 and the middle cavity 16 is high-pressure oil, and the gap sealing sections E and F are always under the action of the high-pressure oil, a high-pressure oil film is formed, so that the high-pressure oil film support is provided for the middle section 22 of the piston, and meanwhile, the sealing element in the sealing groove 53 of the front end piston is also always under the action of the high-pressure oil to generate axial compression and radial compression, so that the sealing element is more tightly matched with a sealed surface, and a great support effect is achieved on the front section part of the piston; under the action of high-pressure oil, the support provided by the front end sealing piece of the piston and the middle section gap sealing section E, F greatly reduces the eccentric motion of the piston in the cylinder body, and avoids the contact between the surface of the piston and the surface of the inner hole of the cylinder body. In the rear section 23 of the piston, because the radial through hole 35 of the high-pressure oil is arranged in the rightmost balance groove of the gap sealing section G, the gap sealing section G is always acted by the high-pressure oil, so that a high-pressure oil film is formed, and the rear section 23 of the piston is supported by the high-pressure oil film; meanwhile, the sealing element in the piston sealing groove 31 in the piston ring 3 is always subjected to the action of high-pressure oil to generate axial compression and radial compression, so that the sealing element is matched with the sealed surface more tightly, the supporting effect on the rear piston section 23 is enhanced, the eccentric motion of the piston in the cylinder body is greatly reduced, and the opportunity that the surface of the rear piston section 23 is in contact with the surface of the inner hole of the cylinder body is avoided.

As shown in fig. 3, when the piston strokes, the oil in the front chamber 12 and the middle chamber 15 is high pressure oil, the rear chamber 17 is communicated with the middle chamber through a reversing valve and also communicated with the high pressure oil, since the action area of the high-pressure oil on the right end face f of the middle and rear section 222 of the piston is larger than the sum of the action areas of the left end face a of the middle and front section of the piston and the left end face e of the middle and rear section of the piston, according to the differential principle in the hydraulic transmission, the piston will stroke leftwards, when the b end surface on the piston 2 passes over the reversing control port groove 13 on the middle cylinder body 1, the pressure oil in the groove 13 of the reversing control port is communicated with the normal-low pressure groove 14 through the groove 223 at the middle section of the piston, so that the pressure oil in the groove 13 of the reversing control port is communicated with the oil, therefore, the pressure oil which pushes the reversing valve 4 to reverse at the reversing port 41 of the reversing valve is released, the reversing valve reverses (see figure 2), the stroke movement is completed, and preparation is made for the return movement of the next step. In the stroke, because the oil in the front cavity and the middle cavity is high-pressure oil, the gap sealing sections E and F are always under the action of the high-pressure oil, so that a high-pressure oil film is formed, the high-pressure oil film is provided for supporting the middle section of the piston, and meanwhile, the sealing element in the sealing groove 53 of the front section of the piston is always under the action of the high-pressure oil to generate axial compression and radial compression, so that the sealing element is more closely matched with the sealed surface, the front section 21 of the piston is greatly supported, the eccentric motion of the piston in the cylinder body is greatly reduced, and the opportunity of contact between the surface of the piston and the surface of the inner hole of the cylinder body is avoided. In the rear section 23 of the piston, because the radial through hole 35 of the high-pressure oil is arranged in the rightmost balance groove of the gap sealing section G, the gap sealing section G is always acted by the high-pressure oil, so that a high-pressure oil film is formed, and the rear section 23 of the piston is supported by the high-pressure oil film; meanwhile, the sealing element in the piston sealing groove 31 in the piston ring 3 is always subjected to the action of high-pressure oil to generate axial compression and radial compression, so that the sealing element is matched with the sealed surface more tightly, the supporting effect on the rear piston section 23 is enhanced, the eccentric motion of the piston in the cylinder body is greatly reduced, and the opportunity that the surface of the rear piston section 23 is in contact with the surface of the inner hole of the cylinder body is avoided.

Therefore, in the working process of the hydraulic breaking hammer, no matter in the stroke or return stroke process, the whole piston rod and the surface clearance matching surface of the inner hole of the middle cylinder body are supported by a high-pressure oil film, the eccentric motion of the piston in the cylinder body is greatly reduced, the contact chance between the outer surface of the piston and the surface of the inner hole of the cylinder body is avoided, and the outer surface of the piston and the inner surface of the cylinder body are prevented from being pulled.

In addition, the clearance of the clearance sealing section E between the middle front section 221 of the piston and the inner hole of the middle cylinder body is much smaller than the clearance between the sealing section of the sealing part of the middle front section 21 of the piston and the inner hole of the middle cylinder body, so that even if the middle front section 221 of the piston is pulled, the middle front section 221 of the piston is not contacted with the sealing part all the time in work, the sealing part cannot be damaged, and oil leakage caused by pulling is avoided.

Preferably, five: according to a preferred technical scheme, the utility model discloses further technical scheme is in clearance seal section E and the piston middle section 22 excircle of F sets up the compensating groove on the surface, can be alone set up the compensating groove on the anterior segment part 221 of the piston middle section 22 of clearance seal section E, or be alone set up the compensating groove on the back end part 222 of the piston middle section 22 of clearance seal section F, or be in simultaneously the outer circle of the anterior segment part 221 of the piston middle section 22 of clearance seal section E and F and back end part 222 sets up the compensating groove on the surface, or be in the piston middle section 22 excircle of clearance seal section E and F does not set up the compensating groove on the surface.

Preferably, six: the five preferred further technical schemes are that the setting of the balance groove on the surface of the inner hole of the middle cylinder body 1 of the clearance seal sections E and F is mutually matched with the setting of the balance groove on the surface of the outer circle of the middle piston section 22, the cylinder section of the outer circle of the middle piston section 22, which is provided with the balance groove, is not provided with the balance groove on the inner hole of the middle cylinder body 1 matched with the cylinder section, and the balance groove is arranged on the surface of the inner hole of the middle cylinder body matched with the cylinder section under the condition that the balance groove is not arranged on the surface of the outer circle of the middle piston section 22.

The function of the balancing groove in the part is as follows: 1) due to the geometry and coaxiality errors of the piston, the asymmetrical distribution of the pressure oil in the seal gap during operation will create a radial unbalance force, known as a hydraulic clamping force. After the balance groove is opened, the oil pressure in each direction in the groove tends to be balanced, and the difference of the clearance is reduced, so that the piston can be automatically centered. 2) The resistance of oil leakage is increased, and the sealing performance is improved. 3) The oil liquid is stored, so that the matching pair can automatically lubricate.

The utility model discloses technical scheme is applicable to the hydraulic crushing hammer of various models, also is applicable to external valve formula hydraulic crushing hammer equally.

The utility model provides a clearance seal section G section structure when small-size hydraulic hammer or clearance seal section E, F section clearance seal holding power meet the demands, can not need, see that fig. 11 shows.

To sum up, the utility model discloses a well cylinder body in the centering cylinder part, the brand-new design of piston and piston ring, this hydraulic breaking hammer is no matter at hydraulic hammer's return stroke process or stroke process, especially when the piston strikes the drill rod, when the piston receives the yawing force (including the yawing force that produces in the work, the yawing force that piston dead weight produced during piston slope or horizontal operating condition), piston anterior segment and middle section yawing force receive the support of the high pressure oil film in anterior segment sealing member and the clearance seal section E, F, piston back end yawing force receives the support of the high pressure oil film in back end piston ring sealing member and the clearance seal section G, whole piston receives balanced support in well cylinder body.

(III) advantageous effects

The utility model provides a hydraulic breaking hammer well jar part possesses following beneficial effect:

(1) and because the clearance seal section F formed by the outer circle surface of the middle and rear sections 222 of the piston and the inner hole of the middle cylinder body is always supported by high-pressure oil, the phenomenon that the piston is unbalanced dynamically due to insufficient supporting force of the outer circle surface of the middle and rear sections of the piston in the cylinder body in the prior art, and the phenomenon that the outer circle surface of the clearance fit section E, F or G of the piston contacts the surface of the inner hole of the middle cylinder body to cause internal leakage due to strain and weak strike is avoided.

(2) Because the diameter d2 of the front section 221 of the piston is larger than the diameter d1 of the front section 21 of the piston, the clearance of the clearance sealing section E between the front section 221 part of the piston and the inner hole of the middle cylinder body is much smaller than the clearance between the sealing section of the sealing part of the front section 21 of the piston and the inner hole of the middle cylinder body, even if the front section 221 part of the piston is pulled, because the front section 221 of the piston is not contacted with the sealing element of the front section of the piston all the time in operation, the sealing element can not be damaged, thereby avoiding oil leakage caused by strain, solving the oil leakage phenomenon caused by the fact that the front section of the piston of the existing hydraulic hammer is not only a sealing part sealing section but also a gap sealing section in the market (when the gap sealing section is strained, the strained piston surface can damage the sealing part to cause the oil leakage phenomenon), meanwhile, the service life of the sealing element is prolonged, the production cost is reduced, and the oil leakage failure rate of the hydraulic hammer can be obviously reduced by implementing the technical scheme.

Drawings

FIG. 1 is a schematic view of a cylinder part of a prior art demolition hammer;

FIG. 2 is a schematic view showing a structure of a bore in a cylinder body of the hydraulic breaking hammer of the present invention;

FIG. 3 is a schematic diagram of a structure of a bore in a cylinder body of the hydraulic breaking hammer of the present invention;

FIG. 4 is a schematic view showing a piston structure of a cylinder part in a hydraulic breaking hammer of the present invention;

FIG. 5 is a schematic view showing the first working principle of a cylinder part in a hydraulic breaking hammer of the present invention;

FIG. 6 is a schematic view of a second working principle of a cylinder part in the hydraulic breaking hammer of the present invention;

FIG. 7 is a schematic view of the embodiment of the present invention with a high pressure oil groove added;

fig. 8 is a schematic view of an embodiment of the present invention with an external valve;

fig. 9 is a schematic diagram of a piston structure of a cylinder part in a hydraulic breaking hammer of the present invention;

fig. 10 is a schematic view of a second embodiment of a structure diagram of a mating piston according to the present invention.

Fig. 11 is a schematic view of an embodiment of the present invention cooperating with a piston ring structure in the prior art

Description of the drawings: 1. a middle cylinder body; 2. a piston; 3. a piston ring; 4. a diverter valve; 11. an oil return groove at the front section of the inner hole of the cylinder body; 12. a front cavity; 13. a commutation control port groove; 14. a normal-low pressure groove; 141. the right end face of the normal-low pressure groove 14; 15. a buffer chamber; 151. the left end face of the buffer chamber 15; 16. a middle cavity; 17. A rear cavity; 18. a normal-high pressure groove; 19. an oil return groove is arranged at the rear section of the inner hole of the cylinder body; 21. a piston front section; 221. a middle front section of the piston; 222. a piston middle rear section; 223. a groove is arranged in the middle section of the piston; 224. a tool withdrawal groove; 225. a left section of the middle and rear sections of the piston; 226. the right section of the middle rear section of the piston; 22. a piston middle section; 23. a piston rear section; 31. A first piston ring sealing groove 32 and a piston ring oil returning groove; 33. a second piston ring sealing groove; 34. a third air sealing groove; 35. high-pressure oil radial through holes; 36. an oil return radial through hole; 41. A reversing port of the reversing valve; 51. a first sealing groove; 52. a second sealing groove; 53. a third sealing groove; 54. a fourth sealing groove; 55. a fifth sealing groove; 56. sixth sealing groove

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by those skilled in the art without creative efforts all belong to the protection scope of the present invention.

The first embodiment is as follows: the technical solution of the present invention will be specifically described below with reference to fig. 4, 5 and 6.

The utility model discloses hydraulic breaking hammer well cylinder part of embodiment includes: the inner hole structure of the middle cylinder body 1 sequentially comprises a dustproof sealing ring groove 51, a U-shaped sealing groove 52 and an oil return groove 11 from left to right, the groove is normally communicated with an oil return groove, a Stent sealing groove or a U-shaped sealing groove 53 and a front cavity normal high-pressure groove 12, the groove is normally communicated with high-pressure oil and an inner hole clearance sealing section E matched with the outer circle surface of a middle front section 221 of the piston, 15 balancing grooves are arranged in the inner hole of the middle cylinder body 1 in the section, a reversing control port groove 13 is arranged in the inner hole section, the groove is communicated with a reversing port 41 of the reversing valve through an internal oil duct, a normal low-pressure groove 14 is arranged on the right side of a reversing control port groove 13, the groove is normally communicated with the oil, a buffer cavity 15 and a middle cavity 16 are arranged on the right side of the normal low-pressure groove 14, an inner hole clearance sealing section F matched with the outer circle surface of a middle rear section 222 of the piston is arranged on the right side close to the buffer cavity and the front cavity, the distance L5 between the left end face 151 of the cushion chamber 15 and the right end face 141 of the normal-low pressure groove 14 is required to be greater than the distance L4 between the end faces of the grooves 223 (see fig. 4) b and c in the middle section of the piston, so as to prevent the high-pressure oil in the working chamber from communicating with the normal-low pressure groove 14 and causing system pressure relief. The right end of the middle cylinder body 1 is provided with a stepped hole for mounting the piston ring 3, three O-shaped ring sealing grooves 54, 55 and 56 (the sealing grooves can be arranged on the outer circle of the piston ring) are arranged in the stepped hole, an oil return groove 19 is arranged between the O-shaped ring sealing grooves 55 and 56 and is normally communicated with oil, and a normal high-pressure groove 18 is arranged between the O-shaped ring sealing grooves 54 and 55 and is normally communicated with high-pressure oil. The inner hole structure of the piston ring 3 is sequentially as follows from left to right: an inner hole gap sealing section G, a Stent seal groove 31, an oil return groove 32, a Stent seal groove 33 and an air seal groove 34 which are matched with the outer circle surface of the piston rear section 23, wherein 6 balancing grooves are arranged in the inner hole gap sealing section G, and a radial through hole 35 communicated with the normal-high pressure groove 18 on the middle cylinder body is arranged in the rightmost balancing groove, so that the gap sealing section G is always under the action of high-pressure oil, a high-pressure oil film is formed, and a high-pressure oil film support is provided for the piston; the piston oil returning groove 32 is communicated with the cylinder rear section oil returning groove 19 through a radial through hole 36. In the embodiment shown in fig. 4, the diameter d1 of the front section 21 of the piston 2 is 200mm, the diameter d2 of the middle front section 221 is 205mm, the diameter d4 of the middle rear section 222 is 225mm, and the diameter d5 of the rear section 23 is 195 mm; the distance L4 between the groove b and the end face of the piston middle section is 60mm, and 10 balancing grooves are arranged on the surface of the middle and rear section with the outer diameter d 4; the distance L5 between the left end face 151 of the middle cylinder cushion chamber 15 and the right end face 141 of the normal-low pressure groove 14 is 75 mm; the fit clearance at the clearance sealing section E, F, G is 0.09mm-0.10mm, and the clearance between the sealing section of the partial sealing element of the front piston section 21 and the inner hole of the middle cylinder body is 0.25mm-0.30 mm.

In the working state of the hydraulic hammer, when the piston returns, as shown in fig. 5, oil in the front cavity 12 and the middle cavity 16 is high-pressure oil, the oil in the rear cavity is low-pressure when the oil is introduced into the rear cavity, the high-pressure oil acts on the end surface a and the end surface e of the piston 2 to push the piston 2 to move rightwards, when the end surface a of the piston 2 crosses the reversing control port groove 13 on the middle cylinder body 1, the high-pressure oil in the front cavity flows to the reversing valve reversing port 41 through the reversing control port groove 13 and the internal oil duct to push the reversing valve 4 to reverse, the return movement is completed, and preparation is made for the next stroke movement. In the process, because the oil in the front cavity 12 and the middle cavity 16 is high-pressure oil, and the gap sealing sections E and F are always subjected to the action of the high-pressure oil, a high-pressure oil film is formed, so that high-pressure oil film support is provided for the front section 221 of the piston and the middle and rear sections 222 of the piston, and meanwhile, the sealing element in the third sealing groove 53 at the front end of the piston is also always subjected to the action of the high-pressure oil to generate axial compression and radial compression, so that the front section sealing element of the piston 2 and the front section 21 of the piston are more tightly matched by a sealing surface, a great supporting effect is exerted on the front section 21 of the piston, the eccentric motion of the piston 2 in the cylinder is greatly reduced, the contact chance between the outer circular surface of the piston 2 and the surface of the inner hole of the middle cylinder 1 is avoided, and the pull damage to the inner surfaces of the piston 2 and the middle cylinder 1 is further avoided. In the rear section 23 of the piston, because the high-pressure oil radial through hole 35 is arranged in the rightmost balance groove of the gap sealing section G, the gap sealing section G is always acted by high-pressure oil, so that a high-pressure oil film is formed, and the high-pressure oil film support is provided for the rear section 23 of the piston; meanwhile, the sealing element in the steckel seal groove 31 in the piston ring 3 is always subjected to the action of high-pressure oil to generate axial compression and radial compression, so that the sealing element and the sealed surface of the piston rear section 23 are matched more tightly, the supporting effect on the piston rear section 23 is enhanced, the eccentric motion of the piston 2 in the middle cylinder body 1 is greatly reduced, the contact chance of the surface of the rear section 23 of the piston 2 and the surface of the inner hole of the middle cylinder body 1 is avoided, and the internal surface strain of the rear section of the piston 2 and the middle cylinder body 1 is further avoided.

In the working state of the hydraulic hammer, when the piston strokes, as shown in fig. 6, the oil in the front cavity 12 and the middle cavity 16 is high-pressure oil, and the rear cavity 17 is also high-pressure when being communicated with the front cavity 12 through the reversing valve 4; as shown in FIG. 4, since the diameter d5 of the rear section 23 of the piston 2 is smaller than the diameter d1 of the front section 21, and the action area f of the right end face of the rear section 222 of the piston is larger than the sum of the action areas of the a end face of the front section 221 of the piston and the left end face e of the rear section 222 of the piston, according to the differential principle in hydraulic transmission, the piston will stroke to the left, when the b end face of the piston 2 crosses the groove 13 of the reversing control port on the middle cylinder 1, the pressure oil in the groove 13 of the reversing control port is communicated with the groove 14 of normal low pressure through the groove with the length L4 on the piston 2, the pressure oil in the groove 13 of the reversing control port is communicated with the oil, so that the pressure oil pushing the reversing valve 4 at the reversing port 41 of the reversing valve is released, the reversing valve 4 is reversed (see FIG. 5), and the stroke motion is completed, and the preparation for the return motion of the next step is made. In the process, because the oil in the front cavity 12 and the middle cavity 16 is high-pressure oil, and the gap sealing sections E and F are always subjected to the action of the high-pressure oil, a high-pressure oil film is formed, so that high-pressure oil film support is provided for the front section 221 of the middle section of the piston and the rear section 222 of the middle section of the piston, and meanwhile, the sealing element in the front-end steckel seal groove or the U-shaped seal groove 53 is also always subjected to the action of the high-pressure oil to generate axial compression and radial compression, so that the sealing element and the front section 21 of the piston are more tightly matched by a sealed surface, a great support effect is achieved on the front part of the piston, the eccentric motion of the piston in the cylinder is greatly reduced, the opportunity of contact between the surface of the piston 1 and the surface of the inner hole of the cylinder is avoided, and the pulling damage to the inner surfaces of the piston 2 and the middle cylinder 1 is avoided. Because the inner hole of the piston ring 3 is provided with a radial through hole 35 communicated with the normal and high pressure groove 18 on the middle cylinder body in the rightmost balancing groove, simultaneously, the rear cavity 17 is communicated with the front cavity 12 through the reversing valve 4 and is also high-pressure, the gap sealing section G is always under the action of high-pressure oil, so that a high-pressure oil film is formed, and high-pressure oil film support is provided for the piston rear section 23, meanwhile, the sealing element in the Stepper sealing groove 31 in the piston ring 3 is also always under the action of high-pressure oil to generate axial compression and radial compression, so that the sealing element and the sealed surface of the piston rear section 23 are matched more tightly, a great supporting effect is exerted on the piston rear section 23, the eccentric motion of the piston 2 in the cylinder body is greatly reduced, the contact chance of the surface of the piston 2 and the inner hole surface of the middle cylinder body 1 is avoided, and the pull damage of the piston 2 and the inner surface of the middle cylinder body 1 is avoided.

In addition, because the clearance of the clearance sealing section E between the front section 221 of the piston and the inner hole of the middle cylinder body 1 is 0.09-0.12mm, and the clearance of the sealing section of the sealing member of the front section 21 of the piston and the inner hole of the middle cylinder body 1 is 0.25-0.35mm, even if the outer circle surface of the front section 221 of the piston is damaged by strain, the front section 221 of the piston is not contacted with the sealing member of the front section all the time in work, the sealing member can not be damaged, thereby avoiding oil leakage caused by strain and obviously reducing the oil leakage failure rate of the hydraulic hammer. Through practice, the problems of cylinder pulling and oil leakage of the breaking hammer in work can be effectively solved.

Example two:

the present embodiment is similar to the embodiment in structure and working principle, and the difference is shown in fig. 7, wherein the inner hole structure of the cylinder body 1 is provided with 1 channel of normal high pressure groove 10 between the front cavity 12 and the reversing control port groove 13, and the groove is normally communicated with high pressure oil. When the gap sealing section E is sealed, the pressure of the pressure oil is gradually reduced in the gap, and when the gap sealing section E is longer, 1 path of high-pressure oil is added in the middle, so that the effect of increasing the oil film supporting force can be achieved. The number of the hydraulic hammer can be increased according to the type of the hydraulic hammer, and is not limited to 1 high-pressure oil groove.

Example three:

the embodiment is basically the same as the first embodiment, except that as shown in fig. 11, the piston ring 3 may use a conventional piston ring structure in the prior art, i.e. the inner bore of the rear end of the middle cylinder 1 is provided with two O-ring sealing grooves 55, 56 (the sealing grooves may be arranged on the outer circle of the piston ring), and the oil return groove 19 is arranged between the O- ring sealing grooves 55, 56, and the grooves are normally open to oil return. The inner hole structure of the piston ring 3 is sequentially as follows from left to right: a steiner groove 31, an oil return groove 32, a steiner groove 33 and an air sealing groove 34 which are matched with the outer circular surface of the piston rear section 23.

Example four:

this embodiment is basically the same with first content of embodiment, the utility model discloses technical scheme is applicable to external valve formula structure equally, and the difference is shown as figure 8, and well cylinder 1 adopts external valve formula structure, and external switching-over valve is adopted to switching-over valve 4.

Example five:

the structure and the working principle of the embodiment are similar to those of the embodiment, the difference is as shown in fig. 9 and fig. 10, under the condition of not affecting the working performance of the breaking hammer, the piston structure shown in fig. 4 is reasonably deformed, namely, a cylindrical section with the original diameter d4 and the length L3 of the middle-rear section 222 of the piston is decomposed into two sections with different diameters, wherein the diameter of the left section 225 is d3, the length L8 is d4, the length L9 is d4, and d3 is less than d 4; the diameter of the buffer cavity 15 in the inner hole structure of the middle body 1 is correspondingly reduced so as to form a clearance seal with the outer circumferential surface of the left section 225, the width of the buffer cavity 15 is L10, and L9> L8> L10, so that a buffering effect is generated when the outer circumferential surface of the left section 225 of the middle and rear piston sections 222 enters the buffer cavity 15. The utility model discloses do not influence under the prerequisite of technical scheme effect, the arbitrary realizable deformation to back end 222 and corresponding cylinder body structure in the piston is all in the utility model discloses in the protection range.

The embodiments described herein are merely illustrative of the technical solutions of the present invention. Various modifications or additions may be made to the described embodiments or alternatives may be employed by those skilled in the art without departing from the spirit or scope of the invention as defined in the appended claims.

It should be noted that, in the description of the present invention, the terms "upper", "lower", "left", "right", "front", "back", etc. indicate the orientation or position relationship of the present invention based on the drawings, and are only for convenience of describing the present invention, but do not indicate or imply that the device or component parts indicated must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.

In the technical scheme, the terms "first" and "second" are only used for referring to the same or similar structures or corresponding structures with similar functions, and are not used for ranking the importance of the structures, or comparing the sizes or other meanings.

Claims (12)

1. The utility model provides a cylinder part in hydraulic breaking hammer, includes well cylinder body, piston ring and switching-over valve, its characterized in that: the inner hole structure of the middle cylinder body sequentially comprises the following components from left to right in the piston head direction: the piston ring sealing structure comprises a sealing piece groove, an oil return groove, a front cavity, a clearance sealing section E matched with a piston rod, a buffer cavity, a middle cavity, a clearance sealing section F matched with the piston rod, a rear cavity and a piston ring hole; the front cavity and the middle cavity are high-pressure oil cavities, high-pressure oil is always introduced during working, and the rear cavity is a variable-pressure cavity.

2. A hydraulic breaker hammer cylinder assembly as claimed in claim 1 wherein: the piston is integrally in a shaft-shaped cylinder, the diameters of the outer circles of the front section, the middle section and the rear section of the piston are different, the diameter of the front section of the piston is d1, the middle section of the piston is divided into two or more sections of cylinder platforms with different or same diameters, if the middle section of the piston is divided into two sections, the diameter of the front section part of the middle section of the piston is d2, the diameter of the rear section part of the middle section of the piston is d4, a groove is formed in the outer circle of the front section part of the middle section of the piston, the width of the groove is L4, and the diameter of the rear section of the piston is d 5; the diameter d5 of the rear section of the piston is smaller than the diameter d1 of the front section of the piston, the diameter d1 of the front section of the piston is smaller than the diameter d2 of the front section of the middle section of the piston, and the diameter d2 of the front section of the middle section of the piston is smaller than the diameter d4 of the rear section of the middle section of the piston, namely d5< d1< d2< d 4; a. b, c, e and f are respectively the end faces of the steps of each cylindrical section, wherein a is the left end face of the middle front section of the piston, b and c are respectively the end faces of the left end and the right end of the groove of the middle section of the piston, and e and f are respectively the left end face and the right end face of the middle rear section of the piston.

3. A cylinder block in a hydraulic demolition hammer as defined in claim 2 wherein: a tool withdrawal groove is arranged between the front section and the rear section of the middle section of the piston, the tool withdrawal groove can also be extended to a section of groove, and the width of the tool withdrawal groove is L7.

4. A cylinder block in a hydraulic demolition hammer as defined in claim 2 wherein: the middle-rear section 222 of the piston can be divided into two parts with different diameters, the diameter of the left section 225 is d3, the length is L8, the diameter of the right section 226 is d4, the length is L9, L9 is larger than L8, e is a left end face of 225, g and f are respectively a left end face and a right end face of 226, and the diameter of each step section of the piston in the scheme is d5< d1< d2< d3< d 4.

5. A cylinder block in a hydraulic demolition hammer as defined in claim 2 wherein: the front section of the inner hole structure of the middle cylinder body is sequentially provided with a first sealing groove, a second sealing groove, a cylinder body inner hole front section oil return groove, a third sealing groove and a front cavity from left to right from the direction of a piston head, the front cavity is a high-pressure oil cavity formed by the right side of a sealing element in the rightmost sealing element groove, the inner hole of the front section of the middle cylinder body, the outer circle surface of the piston and the end surface a of the front section of the piston, the front cavity is communicated with a high-pressure oil way, and high-pressure oil is always introduced during working.

6. The hydraulic demolition hammer center cylinder assembly of claim 5 wherein: the well cylinder body hole of clearance seal section E on the left of cushion chamber has set gradually switching-over control mouth slot, normal low pressure slot on, switching-over control mouth slot communicates with each other through inside oil duct and switching-over valve switching-over mouth, normal low pressure slot is on the right side of switching-over control mouth slot, and the oil return is always open, interval L5 between the right-hand member face of normal low pressure slot and the left end face of cushion chamber is greater than the width L4 of recess on the piston middle section.

7. The hydraulic demolition hammer center cylinder assembly of claim 6 wherein: and a high-pressure oil groove is arranged between the front cavity and the groove of the reversing control port, and high-pressure oil is normally supplied.

8. A hydraulic breaker hammer cylinder assembly as claimed in claim 1 wherein: the right-hand member of well cylinder body hole has set up the stepped hole of installation piston ring, and the stepped hole right-hand member is the macropore, and the left end is the aperture, and aperture length is L6 set gradually fourth way sealed slot, fifth way sealed slot from the left hand right side in the macropore of stepped hole from the piston head direction, sixth way sealed slot, and set up normal high pressure slot between fourth way sealed slot and the fifth way sealed slot, normal high pressure slot normal open high pressure oil has set up well cylinder body hole back end oil gallery between fifth way sealed slot and sixth way sealed slot.

9. The hydraulic demolition hammer center cylinder assembly of claim 8 wherein: piston ring hole surface and piston back end excircle surface match, form clearance seal section G and sealing member seal section from the left hand right side in proper order, the sealing member seal section has set gradually first piston ring seal slot from the left hand right side, piston ring oil return slot, and the piston ring seal slot is said to the second, and the airtight slot is said to the third, piston ring oil return slot is linked together through the radial through-hole of oil return and well cylinder body hole back end oil groove.

10. The hydraulic breaker medium cylinder assembly of claim 8 wherein: the cooperation the length L6 of step hole aperture, the piston ring length of assembling can correspondingly increase L6, and the sealed section G of clearance between extension piston ring hole surface and the piston back end excircle surface is to the back chamber set up a plurality of balancing grooves in the piston ring hole of sealed section G of clearance, set up a normal high pressure slot on last balancing groove right side, the sealed slot left side of first piston ring, piston ring step hole normal high pressure slot is linked together on normal high pressure slot and the well cylinder body, the high pressure oil of normal open.

11. A hydraulic breaker hammer cylinder assembly as claimed in claim 2 wherein: set up the compensating groove on the piston middle section excircle surface of clearance seal section E and F, can be in alone set up the compensating groove on the anterior segment part in the piston middle section of clearance seal section E, or be in alone set up the compensating groove on the back end part in the piston middle section of clearance seal section F, or be in simultaneously the anterior segment part in the piston middle section of clearance seal section E and F sets up the compensating groove on the excircle surface of back end part, or be in the piston middle section excircle surface of clearance seal section E and F does not set up the compensating groove.

12. A hydraulic demolition hammer center cylinder assembly as claimed in claim 11 wherein: the setting of the surface balance groove of the inner hole of the middle cylinder body of the clearance seal sections E and F is mutually matched with the setting of the balance groove on the surface of the outer circle of the middle section of the piston, the cylinder section provided with the balance groove on the surface of the outer circle of the middle section of the piston is not provided with the balance groove with the inner hole of the middle cylinder body matched with the cylinder section, and the balance groove is arranged on the surface of the inner hole of the middle cylinder body matched with the cylinder section under the condition that the outer circle of the middle section of the piston is not provided with the balance groove on the surface.

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