CN215950025U - Middle cylinder part of hydraulic breaking hammer - Google Patents
Middle cylinder part of hydraulic breaking hammer Download PDFInfo
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- CN215950025U CN215950025U CN202122610403.6U CN202122610403U CN215950025U CN 215950025 U CN215950025 U CN 215950025U CN 202122610403 U CN202122610403 U CN 202122610403U CN 215950025 U CN215950025 U CN 215950025U
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Abstract
The utility model relates to a middle cylinder part of a hydraulic breaking hammer, which comprises a middle cylinder body, wherein an annular buffer seal groove, a front oil return groove and a damping cavity are arranged on the inner circumferential side wall of the middle cylinder body, and a buffer sealing piece is arranged in the buffer seal groove. The middle cylinder cavity accommodates a piston. The middle cylinder body is provided with a high-pressure energy accumulator, a high-pressure oil duct, a front oil return channel and a main oil return channel. The front oil return groove, the front oil return channel and the main oil return channel are communicated in sequence. The high-pressure oil groove is arranged on the circumferential side wall in the middle cylinder body and located between the front oil return groove and the damping cavity, and the high-pressure oil groove, the high-pressure oil duct and the high-pressure energy accumulator are communicated in sequence. The oil return pipe has the beneficial effects that pulse impact of ultrahigh pressure pulse oil on an oil return pipeline is avoided, and impact of ultrahigh pressure oil entering the buffer seal groove on the buffer sealing element is avoided. The piston, the middle cylinder body and the guide sleeve are not easy to pull and damage, and the service life of the middle cylinder body is prolonged.
Description
Technical Field
The utility model relates to the technical field of hydraulic breaking hammers, in particular to a middle cylinder component of a hydraulic breaking hammer.
Background
The hydraulic breaking hammer is a tool for breaking solid such as ore or concrete, and is generally installed on an excavator.
Referring to fig. 1, the hydraulic breaking hammer mainly includes a front cylinder, a middle cylinder part, a rear cylinder, a piston, and a drill rod. The middle cylinder body part comprises a middle cylinder body and a guide sleeve, and the front cylinder body, the middle cylinder body and the rear cylinder body are sequentially arranged from front to back. The middle cylinder body is provided with a cavity which is communicated with the front and the back, and a piston is accommodated in the cavity of the middle cylinder body. The cavity of the front cylinder body is communicated with the cavity of the middle cylinder body, the drill rod is accommodated in the cavity of the front cylinder body, and a drill rod sleeve is sleeved between the drill rod and the front cylinder body. The piston horizontally reciprocates back and forth along the cavity of the middle cylinder body, the piston is in a stroke when moving forwards, and the piston is in a return stroke when moving backwards. The piston strikes the drill rod at high speed during the stroke, and the solid is broken by the drill rod. Through the multiple strokes and return strokes of the piston, the piston repeatedly strikes the drill rod to realize the crushing operation.
The middle part of the piston protrudes outwards along the radial direction to form a first annular bulge and a second annular bulge, and the first annular bulge and the second annular bulge are arranged from front to back at intervals.
On the anterior inner circumference lateral wall of well cylinder body, set gradually annular buffering seal groove, preceding oil gallery and damping chamber from front to back. And a buffer sealing element is arranged in the buffer sealing groove. The front oil return groove is communicated with a main oil return channel on the middle cylinder body.
In the process of piston stroke and return stroke, when the first annular bulge in the middle of the piston enters the damping cavity, hydraulic oil in the damping cavity is extruded to form ultrahigh pressure oil, and the ultrahigh pressure oil respectively enters the front oil return groove and the buffer sealing groove through a gap between the middle cylinder body and the piston. The ultra-high pressure oil entering the buffer seal groove can impact the buffer sealing element, so that the buffer sealing element is easy to damage and lose efficacy. The ultrahigh pressure oil in the front oil return groove can be converted into ultrahigh pressure pulse oil pressure during high-low pressure conversion, and the ultrahigh pressure pulse oil pressure can impact the front oil return passage when entering the front oil return passage through the front oil return groove, so that the oil return passage with a larger diameter needs to be arranged to meet the oil return requirement, but the supply flow of the hydraulic oil can be increased, and the use cost is further increased. Meanwhile, ultrahigh pulse oil pressure enters an oil return pipeline of the excavator through the front oil return groove, the front oil return channel and the main oil return channel and causes pulse impact in the oil return pipeline, the pulse impact easily causes the damage and failure of a hydraulic oil radiator on the excavator, the front oil return channel in the oil return pipeline of the hydraulic breaking hammer generates impact, and the pulse impact easily causes the damage and failure of the hydraulic oil radiator on the excavator. Wherein the pressure of the hydraulic oil supplied to the hydraulic breaking hammer is 20-30 MPa, and the pressure of the ultrahigh pressure oil is several times to dozens of times of the pressure of the hydraulic oil.
In summary, there is a need for a middle cylinder component of a hydraulic breaker capable of simultaneously solving the problems that a buffer seal is easy to break and fail and a front oil return passage is easy to be impacted by pulse oil pressure in the processes of piston stroke and return stroke.
SUMMERY OF THE UTILITY MODEL
Technical problem to be solved
In view of the above disadvantages and shortcomings of the prior art, the present invention provides a middle cylinder component of a hydraulic breaker, which solves the technical problems that a buffer seal is prone to damage and failure and a front oil return channel is prone to be impacted by a pulse oil pressure during the piston stroke and the return stroke of the middle cylinder component of the conventional hydraulic breaker.
(II) technical scheme
In order to achieve the purpose, the utility model adopts the main technical scheme that:
in a first aspect, an embodiment of the present invention provides a middle cylinder component of a hydraulic breaking hammer, including a middle cylinder body, where the middle cylinder body is provided with a front-rear through cavity, an inner circumferential side wall of a front portion of the middle cylinder body is sequentially provided with an annular buffer seal groove, a front oil return groove and a damping cavity from front to rear, and a buffer seal is arranged in the buffer seal groove;
the cavity of the middle cylinder body accommodates a piston, the piston is in clearance fit with the middle cylinder body, and the middle part of the piston protrudes outwards along the radial direction to form a second annular bulge:
the middle cylinder body is provided with a high-pressure energy accumulator, a high-pressure oil duct, a front oil return channel and a main oil return channel;
the front oil return groove, the front oil return channel and the main oil return channel are communicated in sequence;
the inner circumferential side wall of the front portion of the middle cylinder body is further provided with an annular high-pressure oil groove, the high-pressure oil groove is located between the front oil return groove and the damping cavity, and the high-pressure oil groove, the high-pressure oil duct and the high-pressure energy accumulator are sequentially communicated.
According to the utility model, the middle cylinder part of the hydraulic breaking hammer further comprises a guide sleeve, the guide sleeve is an annular body, and the guide sleeve is positioned between the piston and the middle cylinder body and is positioned at the rear part of the middle cylinder body;
the guide sleeve is in clearance fit with the piston, and the clearance between the guide sleeve and the piston is 0.06-0.1 mm.
According to the utility model, the diameter of the front oil return channel is 6-7 mm.
According to the utility model, the middle part of the middle cylinder body is provided with the reversing valve, and the rear part of the middle cylinder body is provided with the middle cylinder body oil inlet and return channel;
the front part of the guide sleeve is provided with a guide sleeve oil inlet and return channel, the guide sleeve oil inlet and return channel is communicated with the inner circumferential side wall and the outer circumferential side wall of the guide sleeve, and the guide sleeve oil inlet and return channel, the middle cylinder body oil inlet and return channel and the reversing valve are communicated in sequence.
According to the utility model, at least one annular guide sleeve groove is arranged on the inner circumferential side wall of the front part of the guide sleeve, and at least one guide sleeve groove is arranged at intervals and is positioned on the front side of the guide sleeve oil inlet channel and the guide sleeve oil return channel.
According to the utility model, the rear part of the guide sleeve is provided with a guide sleeve oil return passage, the guide sleeve oil return passage is positioned at the rear side of the guide sleeve oil inlet return passage, the guide sleeve oil return passage is communicated with the inner circumferential side wall and the outer circumferential side wall of the guide sleeve, and the guide sleeve oil return passage is communicated with the main oil return passage on the middle cylinder body.
According to the utility model, at least one annular first Stent seal groove is arranged on the inner circumferential side wall of the rear part of the guide sleeve at intervals;
the first stet seal groove is positioned between the guide sleeve oil inlet return passage and the guide sleeve oil return passage;
a Stent seal is arranged in the first Stent seal groove.
According to the utility model, a second Stent seal groove and an air seal groove are sequentially arranged on the inner circumferential side wall of the rear part of the guide sleeve from front to back, and the second Stent seal groove is positioned at the rear side of the return oil passage of the guide sleeve;
and a Stent seal is arranged in the second Stent seal groove, and a gas seal is arranged in the gas seal groove.
According to the utility model, a first sealing groove and a second sealing groove are arranged on the outer circumferential side wall of the rear part of the guide sleeve at intervals from front to back, the first sealing groove is positioned between the guide sleeve oil inlet and return channel and the guide sleeve oil return channel, and the second sealing groove is positioned on the rear side of the guide sleeve oil return channel;
and O-shaped sealing rings are arranged in the first sealing groove and the second sealing groove.
According to the utility model, the rear cylinder body is arranged at the rear side of the middle cylinder body, an annular boss is formed on the inner circumferential side wall of the rear part of the middle cylinder body in a protruding mode inwards along the radial direction of the inner circumferential side wall, and two ends of the guide sleeve respectively abut against the annular boss and the front end face of the rear cylinder body.
(III) advantageous effects
The utility model has the beneficial effects that: according to the middle cylinder part of the hydraulic breaking hammer, the front high-pressure oil duct and the high-pressure energy accumulator are arranged on the middle cylinder body, the high-pressure oil groove is formed in the side wall of the inner circumference of the middle cylinder body, the high-pressure oil groove, the high-pressure oil duct and the high-pressure energy accumulator are sequentially communicated, after ultrahigh pressure oil is balanced by the high-pressure energy accumulator into high-pressure oil, the high-pressure oil continuously flows along a gap between the middle cylinder body and a piston, a part of the high-pressure oil sequentially flows through the front oil return groove and the front oil return duct to enter the main oil return oil duct of the middle cylinder body, and the other part of the high-pressure oil flows to the buffer sealing piece in the buffer sealing groove.
The ultrahigh pressure oil is balanced into high pressure oil, so that when the ultrahigh pressure oil directly acts on the front oil return groove, the ultrahigh pressure oil in the front oil return groove is converted into ultrahigh pressure pulse hydraulic oil, the ultrahigh pressure pulse hydraulic oil sequentially enters an oil return pipeline of the excavator through the front oil return groove, the front oil return channel and the main oil return channel, and pulse impact is caused in the oil return pipeline, and the pulse impact easily causes damage and failure of a hydraulic oil radiator on the excavator. The ultrahigh pressure oil is balanced into high pressure oil, and the impact of the ultrahigh pressure oil entering the buffer seal groove on the buffer sealing element can be avoided, so that the buffer sealing element is damaged and fails. Therefore, through the arrangement, the service lives of the hydraulic oil radiator and the buffering sealing member can be prolonged.
Meanwhile, after the ultrahigh pressure oil is balanced into high pressure oil, when the high pressure oil flows through the front oil return groove and the front oil return passage in sequence and enters the oil return passage of the middle cylinder body, the diameter requirement on the front oil return passage is reduced, and the oil return requirement can be met by arranging the oil return passage with a smaller diameter, so that the flow of the hydraulic oil is saved, and the cost is reduced.
Secondly, a guide sleeve is arranged between the piston and the middle cylinder body, and the guide sleeve is positioned at the rear part of the middle cylinder body. The guide sleeve is in clearance fit with the piston, and hydraulic oil is continuously supplied into a clearance between the guide sleeve and the piston so as to form a lubricating oil film between the guide sleeve and the piston. The clearance between the guide sleeve and the piston is 0.06-0.1 mm.
The clearance between the guide sleeve and the piston is reduced to 0.06-0.1mm, the clearance is matched with the clearance (0.06-0.1mm) between the front part of the middle cylinder body and the piston and the clearance (0.06-0.1mm) between the middle part of the middle cylinder body and the piston, so that when the piston moves in a state that the axis of the piston is inclined to the axis of the middle cylinder body, the circumferential side wall of the front part of the piston abuts against the front part of the middle cylinder body, the circumferential side wall of the rear part of the piston abuts against the guide sleeve, the rear part of the piston is supported by the guide sleeve, and the phenomenon that the annular bulge on the piston abuts against the inner circumferential side wall of the middle part of the middle cylinder body to be pulled and damaged is avoided. Even if the uide bushing damage became invalid, the change expense of uide bushing is lower, only needs several hundred yuan, very big reduction the maintenance cost of well cylinder body part. Meanwhile, the rear part of the piston is supported by the guide sleeve, the guide distance to the piston can be further prolonged, the included angle between the axis of the piston and the axis of the middle cylinder body can be reduced by increasing the guide distance, the contact area between the front part of the piston and the front part of the middle cylinder body and the contact area between the rear part of the piston and the guide sleeve are further increased, so that the pressure values of the piston acting on the middle cylinder body and the guide sleeve are reduced, lubricating oil films between the piston and the middle cylinder body and between the piston and the guide sleeve are not easy to break, the piston, the middle cylinder body and the guide sleeve are not easy to pull and damage, and the service life of the middle cylinder body is further prolonged.
Drawings
FIG. 1 is a cross-sectional view of a mid-cylinder component of a prior art hydraulic demolition hammer;
FIG. 2 is a cross-sectional view of the middle cylinder component of the hydraulic demolition hammer of the present invention;
FIG. 3 is an enlarged schematic view of the middle cylinder block component and piston of FIG. 2;
FIG. 4 is an enlarged schematic view taken at A in FIG. 3;
fig. 5 is a cross-sectional view of the guide sleeve of fig. 2.
[ description of reference ]
1: a front cylinder body;
2: the middle cylinder body: 211: sealing the groove in a dustproof way; 212: a buffer sealing groove; 213: a main oil seal tank; 214: a front oil return groove; 215: a first middle cylinder groove; 216: a high pressure oil sump; 217: a second middle cylinder groove; 218: a reversing oil tank; 219: a middle oil return groove; 221: a damping chamber; 222: a front chamber; 223: a rear chamber; 231: a main oil return passage; 232: a front oil return passage; 233: a high pressure oil passage; 234: the middle cylinder body is provided with an oil inlet and return channel; 24: an annular boss; 25: a high pressure accumulator; 26: a diverter valve;
3: a rear cylinder body;
4: a drill rod;
5: a piston; 51: a first annular projection; 52: a second annular projection 52;
6: a guide sleeve; 61: a guide sleeve groove; 62: the guide sleeve enters an oil return channel; 621: the guide sleeve enters the oil return channel; 622: the guide sleeve enters an oil return groove; 63: a first steiner slot; 64: the guide sleeve returns to the oil duct; 65: a second steiner; 66: a gas seal groove; 67: a first seal groove; 68: a second seal groove;
l1: the distance between the front end surface of the first middle cylinder groove 215 on the middle cylinder 2 and the abutting surface of the annular boss 24 of the middle cylinder 2;
l2: the distance between the front end surface of the first middle cylinder groove 215 on the middle cylinder 2 and the rear end surface of the air seal groove 66 on the guide sleeve 6.
Detailed Description
For the purpose of better explaining the present invention and to facilitate understanding, the present invention will be described in detail by way of specific embodiments with reference to the accompanying drawings. Where reference herein to "front" is with reference to the orientation on the left side of fig. 1, and "rear" is with reference to the orientation on the right side of fig. 1.
Referring to fig. 1 and 2, the present invention provides a hydraulic breaker including a front cylinder block 1, a middle cylinder block, a rear cylinder block 3, a drill rod 4, and a piston 5. The middle cylinder body part comprises a middle cylinder body 2, and the front cylinder body 1, the middle cylinder body 2 and the rear cylinder body 3 are sequentially arranged from front to back. The middle cylinder body 2 is provided with a cavity which is through from front to back, and the cavity of the middle cylinder body 2 contains a piston 5. The cavity of the middle cylinder body 2 is communicated with the cavity of the front cylinder body 1, and the cavity of the front cylinder body 1 contains a drill rod 4. The piston 5 horizontally reciprocates back and forth along the cavity of the middle cylinder 2, and the forward movement of the piston 5 is a stroke, and the backward movement of the piston 5 is a return stroke. The piston 5 strikes the drill rod 4 at high speed during its stroke, breaking up the solids by the drill rod 4. Through the multiple strokes and return strokes of the piston 5, the piston 5 repeatedly strikes the drill rod 4 to realize the crushing operation.
The piston 5 is in clearance fit with the middle cylinder body 2. The gap between the piston 5 and the middle cylinder 2 is continuously supplied with hydraulic oil to form a lubricating oil film between the piston 5 and the middle cylinder 2, and the lubricating oil film provides lubrication, support, sealing, cleaning and cooling for the back and forth movement of the piston 5.
Further, the middle portion of the piston 5 protrudes outward in the radial direction thereof to form a first annular projection 51 and a second annular projection 52, and the first annular projection 51 and the second annular projection 52 are provided at intervals from front to rear.
Referring to fig. 2 and 3, a main oil return channel 231 is further provided on the middle cylinder 2, and the main oil return channel 231 extends horizontally along the axial direction of the middle cylinder 2. The front part of the middle cylinder body 2 is provided with a front oil return passage 232 and a high-pressure oil passage 233 in sequence from front to back. The middle part of the middle cylinder body 2 is provided with a high-pressure accumulator 25. The front part of the inner circumferential side wall of the middle cylinder body 2 is provided with an annular buffer seal groove 212, a front oil return groove 214, a high-pressure oil groove 216 and a damping cavity 221 from front to back in sequence. The front oil return groove 214, the front oil return passage 232 and the main oil return passage 231 are communicated in sequence. The high-pressure oil groove 216, the high-pressure oil passage 233, and the high-pressure accumulator 25 are communicated in sequence. A cushioning seal is disposed within the cushioning seal pocket 212.
Referring to fig. 2 and 3, during the stroke and the return stroke of the piston 5, when the first annular protrusion 51 on the piston 5 enters the damping cavity 221, the hydraulic oil in the damping cavity 221 is squeezed to form ultra-high pressure oil, the ultra-high pressure oil enters the high-pressure accumulator 25 through the high-pressure oil groove 216 and the high-pressure oil groove 233 in sequence from the gap between the middle cylinder body 2 and the piston 5, the high-pressure accumulator 25 balances the ultra-high pressure oil into high pressure oil, the high pressure oil flows back to the gap between the middle cylinder body 2 and the piston 5 through the high-pressure oil groove 233 and the high-pressure oil groove 216 and continues to flow in the gap, a part of the high pressure oil flows into the main oil return channel 231 of the middle cylinder body 2 through the front oil return channel 214 and the front oil return channel 232 in sequence, and the other part of the high pressure oil flows into the buffer seal in the buffer seal groove 212.
The ultrahigh pressure oil is balanced into high pressure oil, so that when the ultrahigh pressure oil directly acts on the front oil return groove 214, the ultrahigh pressure oil in the front oil return groove 214 is converted into ultrahigh pressure pulse hydraulic oil, the ultrahigh pressure pulse hydraulic oil sequentially enters an oil return pipeline of the excavator through the front oil return groove 214, the front oil return channel 232 and the main oil return channel 231, pulse impact is caused in the oil return pipeline, and the pulse impact easily causes damage and failure of a hydraulic oil radiator on the excavator. The ultrahigh pressure oil is balanced into high pressure oil, and the impact of the ultrahigh pressure oil entering the buffer seal groove 212 on the buffer sealing element can be avoided, so that the buffer sealing element is damaged and fails. Therefore, through the arrangement, the service lives of the hydraulic oil radiator and the buffering sealing member can be prolonged.
Meanwhile, after the ultrahigh pressure oil is balanced into high pressure oil, when the high pressure oil sequentially flows through the front oil return groove 214 and the front oil return passage 232 and enters the main oil return passage 231 of the middle cylinder body 2, the requirement on the diameter of the front oil return passage 232 is reduced, and the requirement on oil return can be met by arranging the front oil return passage 232 with a smaller diameter. Therefore, the diameter of the front oil return passage 232 is changed from 10-12mm in the prior art to 6-7mm, so that the hydraulic oil flow is saved, and the cost is reduced.
Referring to fig. 2 and 3, specifically, the front portion of the inner circumferential side wall of the middle cylinder 2 is further provided with an annular dustproof seal groove 211, at least one main oil seal groove 213, at least one first middle cylinder groove 215 and at least one second middle cylinder groove 217 from front to back in sequence, the main oil seal groove 213 is located on the front side of the front oil return groove 214, the at least one middle cylinder groove is located between the front oil return groove 214 and the high pressure oil groove 216, and the at least one second middle cylinder groove 217 is located between the high pressure oil groove 216 and the damping cavity 221.
The dustproof sealing groove 211 is internally provided with a dustproof sealing ring for preventing external dust from entering the cavity of the middle cylinder body 2. A U-shaped seal ring is disposed in at least one of the main oil seal grooves 213 for sealing hydraulic oil and preventing the hydraulic oil from leaking out from a gap between the middle cylinder 2 and the piston 5. The first and second middle cylinder grooves 215 and 217 store hydraulic oil, and form and maintain a lubricating oil film between the middle cylinder 2 and the piston 5. The middle cylinder 2 is provided with a first middle cylinder groove 215 and an inner circumferential side wall of a second middle cylinder rear groove forming a support area of the front of the middle cylinder 2 to the front of the piston 5.
Further, a front chamber 222, a direction-changing oil groove 218, a middle oil return groove 219 and a rear chamber 223 are sequentially provided from front to rear in the middle of the inner circumferential side wall of the middle cylinder body 2. The middle part of the middle cylinder body 2 is also provided with a reversing valve 26, and the reversing valve 26 is communicated with the rear chamber 223. The rear part of the middle cylinder 2 is provided with a middle cylinder oil inlet and return channel 234.
The specific principle of the middle cylinder 2 for driving the piston 5 to stroke and return is as follows: when the return stroke of the piston 5 starts, the last impact of the piston 5 is finished, the piston 5 is in an instant pause state, the rear cavity 223 is communicated with the main oil return channel 231 under the control of the reversing valve 26, at the moment, the piston 5 performs the return stroke movement under the action of high-pressure oil in the front cavity 222, and nitrogen in a nitrogen chamber on the rear cylinder 3 is compressed. After the piston 5 moves backwards, the reversing valve 26 reverses to enable the rear chamber 223 to be communicated with the high-pressure oil channel 233, at the moment, the piston 5 stops instantaneously, the nitrogen pressure in the nitrogen chamber increases, the pressure value exerted on the piston 5 by the hydraulic oil in the rear chamber 223 is larger than the pressure value exerted on the piston 5 by the hydraulic oil in the front chamber 222 (the action area of the high-pressure oil in the rear chamber 223 on the piston 5 is larger than the action area of the high-pressure oil in the front chamber 222 on the piston 5, the same oil is pressed down, the pressure with the large action area is large), the piston 5 starts stroke motion, the drill rod 4 is struck to be broken, and the piston 5 returns after striking is completed.
Specifically, the rear portion of the inner circumferential side wall of the middle cylinder block 2 also protrudes inward to form an annular boss 24.
Referring to fig. 2-5, further, the middle cylinder part also includes a guide sleeve 6, the guide sleeve 6 is an annular body, and the guide sleeve 6 is located between the piston 5 and the middle cylinder 2 and at the rear of the middle cylinder 2. The both ends of uide bushing 6 support the preceding terminal surface of annular boss 24 and rear cylinder body 3 respectively to with the rigidity of uide bushing 6, avoid uide bushing 6 drunkenness from the front and back. The guide sleeve 6 is in clearance fit with the piston 5, and hydraulic oil is continuously supplied into the clearance between the guide sleeve 6 and the piston 5 so as to form a lubricating oil film between the guide sleeve 6 and the piston 5, wherein the lubricating oil film is used for supporting the piston. The clearance between the guide sleeve 6 and the piston 5 is 0.06-0.1 mm.
Referring to fig. 1, the gap between the guide sleeve 6 and the piston 5 in the prior art is 0.28 to 0.35mm, which is large, and the piston 5 cannot abut against the guide sleeve 6 when the piston 5 moves in a state where its axis is inclined to the axis of the middle cylinder 2. In the application, the gap between the guide sleeve 6 and the piston 5 is reduced to 0.06-0.1mm, and the gap is matched with the gap (0.06-0.1mm) between the front part of the middle cylinder body 2 and the piston 5 and the gap (0.06-0.1mm) between the middle part of the middle cylinder body 2 and the piston 5, so that when the piston 5 moves under the state that the axis of the piston 5 is inclined to the axis of the middle cylinder body 2, the circumferential side wall of the front part of the piston 5 abuts against the front part of the middle cylinder body 2, the circumferential side wall of the rear part of the piston 5 abuts against the guide sleeve 6, and the rear part of the piston 5 is supported by the guide sleeve 6, so that the second annular bulge 52 on the piston 5 abuts against the middle part of the middle cylinder body 2, and the inner circumferential side wall of the middle part of the middle cylinder body 2 is prevented from being pulled and damaged. Even if the uide bushing 6 is damaged inefficacy, the change expense of uide bushing 6 is lower, only needs several hundred yuan, very big reduction the maintenance cost of well cylinder body 2. Meanwhile, the rear part of the piston 5 is supported by the guide sleeve 6, and the guide distance for supporting the piston 5 can be further prolonged, and the distance L1 between the front end surface of the first middle cylinder groove 215 on the original middle cylinder 2 and the abutting surface of the annular boss 24 of the middle cylinder 2 is changed into the distance L2 between the front end surface of the first middle cylinder groove 215 on the middle cylinder 2 and the rear part of the guide sleeve 6 in the application. The included angle between the axis of the piston 5 and the axis of the middle cylinder body 2 can be reduced by increasing the guide distance, so that the contact area between the front part of the piston 5 and the front part of the middle cylinder body 2 and the contact area between the rear part of the piston 5 and the guide sleeve 6 are increased, the pressure value of the piston 5 acting on the middle cylinder body 2 and the guide sleeve 6 is reduced, lubricating oil films between the piston 5 and the middle cylinder body 2 and between the piston 5 and the guide sleeve 6 are not easy to break, the piston 5, the middle cylinder body 2 and the guide sleeve 6 are not easy to pull and damage, and the service life of the middle cylinder body 2 is prolonged.
The guide sleeve 6 in the prior art is provided with at least one first stet seal groove 63, a second stet seal groove 65 and an air seal groove 66 in a ring shape from front to back in sequence. The guide sleeve 6 is further provided with a guide sleeve oil return passage 64, the guide sleeve oil return passage 64 is located between the first stet seal groove 63 and the second stet seal groove 65, the guide sleeve oil return passage 64 is communicated with the inner circumferential side wall and the outer circumferential side wall of the guide sleeve 6, and the guide sleeve oil return passage 64 is communicated with a main oil return passage 231 on the middle cylinder body 2. A first sealing groove 67 and a second sealing groove 68 are sequentially formed in the outer circumferential side wall of the guide sleeve 6 from front to back, and the first sealing groove 67 and the second sealing groove 68 are located on the front side and the rear side of the guide sleeve oil return passage 64 respectively.
Referring to fig. 4 and 5, the present application extends the length of the guide bush 6 based on the guide bush 6 of the prior art, and adds at least one annular guide bush groove 61 and a guide bush oil inlet/return passage 62 to the front of the guide bush 6. The guide bush groove 61 is located on the inner circumferential side wall of the guide bush 6. The guide sleeve oil inlet and return channel 62 is communicated with the inner circumferential side wall and the outer circumferential side wall of the guide sleeve 6, and the guide sleeve groove 61, the guide sleeve oil inlet and return channel 62 and the first Steer seal groove 63 are sequentially arranged from front to back.
The guide sleeve oil inlet and return channel 62, the middle cylinder oil inlet and return channel 234 and the reversing valve 26 are sequentially communicated, the reversing valve 26 is sequentially communicated with a gap between the guide sleeve 6 and the piston 5 through the middle cylinder oil inlet and return channel 234 and the guide sleeve oil inlet and return channel 62, or hydraulic oil reversely flows back to the reversing valve 26, so that the hydraulic oil continuously flows in the gap between the guide sleeve 6 and the piston 5, a lubricating oil film is formed between the guide sleeve 6 and the piston 5, the piston 5 is supported through the lubricating oil film, the guide sleeve 6 and the piston 5 are prevented from being damaged due to contact, and the service lives of the guide sleeve 6 and the piston 5 are further prolonged. The guide sleeve groove 61 stores hydraulic oil, so as to better maintain the hydraulic oil environment between the guide sleeve 6 and the piston 5 and provide good lubrication for the movement of the piston 5.
Specifically, the guide sleeve oil inlet and return passage 62 includes a guide sleeve oil inlet and return groove 622 and a guide sleeve oil inlet and return passage 621, the guide sleeve oil inlet and return groove 622 is located on the inner circumferential side wall of the guide sleeve 6, and the guide sleeve oil inlet and return passage 621 communicates the guide sleeve oil inlet and return groove 622 with the outer circumferential side wall of the guide sleeve 6.
The stet seal is arranged in the first stet seal groove 63 to prevent the pulse hydraulic oil formed by the guide sleeve entering the oil return groove 622 during high-low pressure conversion from sequentially entering the main oil return channel 231 and an oil return pipeline of the excavator through the guide sleeve oil return channel 64 and causing pulse impact in the oil return pipeline, wherein the pulse impact easily damages a hydraulic oil radiator on the excavator. A steve seal is provided in the second steve seal groove 65 for preventing the hydraulic oil from leaking out through the gap between the guide sleeve 6 and the piston 5. An air seal is provided in the air seal groove 66 for sealing the nitrogen gas of the nitrogen gas chamber in the rear cylinder block 3. O-ring seals are disposed in the first seal groove 67 and the second seal groove 68, and the O-ring seals in the first seal groove 67 are used for isolating the guide sleeve oil inlet/return passage 62 and the guide sleeve oil return passage 64. The O-ring seal in the second seal groove 68 is used to prevent hydraulic oil from leaking out of the gap between the guide sleeve 6 and the middle cylinder block 2.
Specifically, the distance between the front end surface of the first middle cylinder groove 215 on the middle cylinder 2 and the rear end surface of the air seal groove 66 on the guide sleeve 6 forms the guide distance L2 for the piston 5 in this application.
Preferably, the material of the guide sleeve 6 is 20CrMo, and the material has good wear resistance so as to prolong the service life of the guide sleeve 6.
Simultaneously, the uide bushing 6 of this application's simple structure, the processing of being convenient for.
Although embodiments of the present invention have been shown and described above, it should be understood that the above embodiments are illustrative and not restrictive, and that those skilled in the art may make changes, modifications, substitutions and alterations to the above embodiments without departing from the scope of the present invention.
Claims (10)
1. A middle cylinder part of a hydraulic breaking hammer comprises a middle cylinder body (2), wherein the middle cylinder body (2) is provided with a cavity which is through from front to back, an annular buffer sealing groove (212), a front oil return groove (214) and a damping cavity (221) are sequentially arranged on the inner circumferential side wall of the front part of the middle cylinder body (2) from front to back, and a buffer sealing piece is arranged in the buffer sealing groove (212);
the cavity of the middle cylinder body (2) accommodates a piston (5), the piston (5) is in clearance fit with the middle cylinder body (2), the middle part of the piston (5) protrudes outwards along the radial direction to form a second annular bulge (52), and the piston is characterized in that:
the middle cylinder body (2) is provided with a high-pressure energy accumulator (25), a high-pressure oil duct (233), a front oil return passage (232) and a main oil return passage (231);
the front oil return groove (214), the front oil return channel (232) and the main oil return channel (231) are communicated in sequence;
the inner circumferential side wall of the middle cylinder body (2) is further provided with an annular high-pressure oil groove (216), the high-pressure oil groove (216) is located between the front oil return groove (214) and the damping cavity (221), and the high-pressure oil groove (216), the high-pressure oil passage (233) and the high-pressure accumulator (25) are communicated in sequence.
2. A middle cylinder part of a hydraulic breaking hammer as set forth in claim 1, wherein:
the middle cylinder part of the hydraulic breaking hammer further comprises a guide sleeve (6), the guide sleeve (6) is an annular body, and the guide sleeve (6) is located between the piston (5) and the middle cylinder body (2) and is located at the rear part of the middle cylinder body (2);
the guide sleeve (6) is in clearance fit with the piston (5), and the clearance between the guide sleeve (6) and the piston (5) is 0.06-0.1 mm.
3. A middle cylinder part of a hydraulic breaking hammer according to claim 1, characterized in that the diameter of the front oil return channel (232) is 6-7 mm.
4. A middle cylinder part of a hydraulic breaking hammer according to claim 2, characterized in that a reversing valve (26) is arranged at the middle part of the middle cylinder (2), and a middle cylinder inlet and return channel (234) is arranged at the rear part of the middle cylinder (2);
the oil return passage (62) is arranged on the guide sleeve (6), the guide sleeve oil return passage (62) is communicated with the inner circumferential side wall and the outer circumferential side wall of the guide sleeve (6), and the guide sleeve oil return passage (62), the middle cylinder body oil return passage (234) and the reversing valve (26) are communicated in sequence.
5. A middle cylinder part of a hydraulic breaking hammer as set forth in claim 4, characterized in that at least one annular guide bush groove (61) is provided on an inner circumferential side wall of the guide bush (6), and at least one of the guide bush grooves (61) is provided at intervals and is located on a front side of the guide bush oil inlet/return passage (62).
6. A middle cylinder part of a hydraulic breaking hammer according to claim 4, wherein the guide sleeve (6) is provided with a guide sleeve return oil passage (64), the guide sleeve return oil passage (64) is located at the rear side of the guide sleeve inlet oil passage (62), the guide sleeve return oil passage (64) communicates with the inner circumferential side wall and the outer circumferential side wall of the guide sleeve (6), and the guide sleeve return oil passage (64) communicates with the main oil passage (231) on the middle cylinder body (2).
7. A medium cylinder part of a hydraulic breaking hammer as set forth in claim 6, characterized in that at least one annular first Stent seal groove (63) is provided at intervals on the inner circumferential side wall of the guide sleeve (6);
the first Stent seal groove (63) is positioned between the guide sleeve oil inlet and return channel (62) and the guide sleeve oil return channel (64);
a Stent seal is arranged in the first Stent seal groove (63).
8. A middle cylinder part of a hydraulic breaking hammer as claimed in claim 6, characterized in that the inner circumferential side wall of the guide sleeve (6) is further provided with a second Stent seal groove (65) and an air seal groove (66) from front to back, and the second Stent seal groove (65) is positioned at the rear side of the guide sleeve return oil passage (64);
a Stent seal is arranged in the second Stent seal groove (65), and a gas seal is arranged in the gas seal groove (66).
9. The medium cylinder part of a hydraulic breaker according to claim 6, wherein a first seal groove (67) and a second seal groove (68) are provided at intervals from front to rear on the outer circumferential side wall of the pilot sleeve (6), the first seal groove (67) is located between the pilot sleeve oil inlet/return passage (62) and the pilot sleeve oil return passage (64), and the second seal groove (68) is located on the rear side of the pilot sleeve oil return passage (64);
o-shaped sealing rings are arranged in the first sealing groove (67) and the second sealing groove (68).
10. A middle cylinder part of a hydraulic breaker according to claim 2 wherein a rear cylinder body (3) is provided at the rear side of the middle cylinder body (2), an annular boss (24) is formed on the inner circumferential side wall at the rear part of the middle cylinder body (2) to protrude inward in the radial direction thereof, and both ends of the guide sleeve (6) abut against the annular boss (24) and the front end surface of the rear cylinder body (3), respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122610403.6U CN215950025U (en) | 2021-10-26 | 2021-10-26 | Middle cylinder part of hydraulic breaking hammer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122610403.6U CN215950025U (en) | 2021-10-26 | 2021-10-26 | Middle cylinder part of hydraulic breaking hammer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN215950025U true CN215950025U (en) | 2022-03-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122610403.6U Active CN215950025U (en) | 2021-10-26 | 2021-10-26 | Middle cylinder part of hydraulic breaking hammer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN215950025U (en) |
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2021
- 2021-10-26 CN CN202122610403.6U patent/CN215950025U/en active Active
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