CA1157057A - Recoil damper for a reciprocating member - Google Patents
Recoil damper for a reciprocating memberInfo
- Publication number
- CA1157057A CA1157057A CA000367990A CA367990A CA1157057A CA 1157057 A CA1157057 A CA 1157057A CA 000367990 A CA000367990 A CA 000367990A CA 367990 A CA367990 A CA 367990A CA 1157057 A CA1157057 A CA 1157057A
- Authority
- CA
- Canada
- Prior art keywords
- piston
- flange
- cavity
- damper
- fluid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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- Percussive Tools And Related Accessories (AREA)
Abstract
A Recoil Damper for a Reciprocating Member Abstract A recoil damper for a reciprocating member mounted in a housing includes a annular ring mounted-adjacent a flange formed on the reciprocating member, the annular ring mounted in a viscous fluid interior of the housing. The annular ring cooperates with the flange of the reciprocating member to allow a relatively free flow of the viscous fluid around the flange upon motion of the reciprocating member in one direction and to restrict flow of the viscous fluid around the flange upon motion of the reciprocating member in the other opposite direction.
Description
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Description A Recoil Damper for a Reciprocating Member Technical Field This invention relates to rock-breaking machinery. In particular it relates to a recoil damper for the reciprocating member of such machinery.
Background Art In reciprocating machinery, and particularly rock breakers, there is a requirement to dampen the motion of the reciprocating mechanism on the recoil stroke. In some rock breakers an eccentric mechanism provides intermittent power strokes to the rock breaker tip or shank through an intermediate impact link located between the eccentric and the shank. In the earlier impact devices the shank was usually impacted directly by the eccentric ring. A seal was generally provided between the shank and the housing.
The seal generally experienced a short life due to the large number of cycles and large displacement (8-1/2 to 9 cm) during each cycle. Recoil of the shank was absorbed by conventional dampening devices located exterior of the drive mechanism. An example of such an exterior recoil damper is found in U.S. Patent 3,868,145.
With the advent of a limited displacement (1-1/2 cm) type intermediate impact link positioned between the eccentric and the shank, the intermediate impact link itself must be dampened as it is relatively free floating in comparison to the more conventional shank and eccentric. That is, the intermediate impact link~ being located between the enclosed eccentric and the exterior shank, transmits -- ~:
: . ' ~ '.~, khe force of the eccentric to the shank. In order to provide relatively free movement toward the shank, the intermediate impact link is mounted in appropriate bearings positioned in the housing. However, upon recoil, the recoil force would ordinarily be transmitted to the eccentric thus causing excessive wear on the eccentric unless some form of recoil damper is used.
In such intermediate impact link type rock breakers, the force to be applied to the shank ordinarily does not occur until the shank is displaced rearwardly to engage the intermediate impact link which is also displaced rearwardly into position to be contacted by the eccentric. As the eccentric rotates so that its periphery contacts the intermediate impact link, the force of the eccentric is transmitted through the intermediate impact link to the shank which in turn acts on the working sur~ace. As the eccentric continues to rotate, the force is relieved from the intermediate impact link, thus permitting the shank to recoil with such recoil transmitted to the intermediate impact link. Although the motion of the shank could be dampened in the manner shown in the U.S.
Patent No. 3,868,145, that is an exterior damper may be mounted adjacent the shank, the recoil motion of the intermediate impact link which is contained substantially within the housing must also be dampened.
The present invention is directed to overcoming one or more o~ the problems as set forth above.
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Disclosure of the Invention In one aspect of the present invention, there is provided a recoil damper comprising: a housing, a member reciprocally mounted in said housing for movement in first and second opposite directions, a radial flange on said member, first and second cavities defined in said housing on opposite sides of said flange and containing a damping fluid therein, and damping means-for restricting flow of said damping flu;d from said second cavity to said first cavity in response to compression of damping fluid in said second cavity by said flange when said member is moved in said first direction and for permitting relatively free flow of damping fluid from said first cavity to said second cavity in response to compression of damping fluid in said first cavity by said flange when said member is moved in said second direction.
According to another aspect of the invention there is provided a hydraulic piston damper, comprising: a housing having a piston bore providing opposite end portions; a fluid cavity in the housing communicating with said piston bore intermediate said end portions thereof; a reciprocal piston axially slidably disposed in said piston bore and having a radially outwardly extended flange projecting into said cavity in fluid pumping relation to a fixed volume of trapped fluid within the cavity; a damper control member disposed for axial sliding movement within said cavity relative to said flange and providing a restricted orifice; and spring means for biasing said control member toward a position blocking the flow of fluid past said flange to force fluid through said orifice in dampening relation to movement of said piston in one axial direction of travel, and said control member being responsive to fluid pressure within said cavity for movement to a position providing substantially unrestricted flow of fluid past said flange B
~57V~i7 -3a-during travel of said piston in an opposite axial direction.
Brief Description of-the Drawings Figure 1 is a schemati`c view, partly in section, of an em~odiment of a recoil damper as us~ed with an intermedïate link of a rock breaker.
Figure 2 is a detailed sectional view of the embodiment of the recoil damper shown in Figure 1.
Figure 3 is a schematic view of an alternate embodiment of the recoil damper.
Best Mode of Carrying-Out the Invention Referring to Figure l, a recoil damper 10 is shown with an intermediate impact link 12 of an impact type rock breaker.
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The impact type rock breaker consists of a shank 14 having as a portion thereof a rock breaker tip 16 used to impact and thus break rock. An eccentric mechanism 18 provides intermittent power strokes to intermediate impact link 12 which in turn are transmitted to shank 14. It should be noted that Figure 1 illustrates the rock breaker in the "at rest" condition. As the rock breaker ~ip 16 is brought into contact with the material to be broken, the shank 14, which is pivoted from a mounting (not shown), is in turn brought into contact with a portion 20 of intermediate impact link 12. Further imposition of force by rock breaker tip 16 against a surface to be broken results in intermediate impact link 12 moving downwardly as shown in Figure 1 or in a first direction thus bringing the intermediate impact link 12 into the range of eccentric 18. This range is denoted by the dashed circle 22 in Figure 1. As eccentric 18 rotates, it will contact intermediate impact link 12 to urge it in a second opposite direction.
Housing 24 defines a bore 25 in which intermediate impact link 12 is slidably positioned. Also defined in housing 24 is a cavity 26 generally adjacent the midpoint of bore 25 of housing 24. Intermediate impact link 12 is preferably cylindrical and has a flange 28 extending generally about the midpoint thereof. The flange 28 is adapted to be received in the cavity 26.
In order to form cavity 26 to concurrently receive flange 28, housing 24 must be made in at least two portions, front portion 30 and rear portion 32. In the embodiment shown in Figure 1, ..
'7 a mid portion 34 is also utilized to facilitate installation of other centering devices 36 utilized to center intermediate impact link 12 in housing 24.
Appropriate fastening means 37, in this instance elongated bolts, are utilized to interconnect the various portions of housing 24.
Damping means 35 for retarding movement of the reciprocating intermediate impact link 12 are located in cavity 26. These means include an annular ring 38 which, in this embodiment, is formed to slidably move on flange 28 of intermediate impact link 12 in said first and second directions. Formed in annular ring 38 are a plurality of orifices 40. Each orifice 40 is oriented in the axial direction thus permitting communication of a viscous fluid which also forms a portion of the means for retarding recoil and which is located in cavity 26.
Annular ring 38 is biased toward front portion 30 of housing 24 by a plurality of resilient members such as helical springs 42. Located at the rearward end of cavity 26 is a stop 44. Referring to Figure 2, it can be seen that stop 44 may also be an annular ring which is located adjacent the outer portion of cavity 26. The inner diameter of stop 44 is less than the outer diameter of annular ring 38, so that upon movement of annular ring 38 downwardly as shown in Figure 2, ring 38 will contact stop 44 before coming into contact with housing 24. A
plurality of grooves 45 are formed in the upper surface of stop 44 so that fluid trapped in cavity 26a and cavity 26b with annular ring 38 seated or in close proximity to stop 44 may pass thereby into cavity 26c.
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~L~S7~5~7 It can be seen in Figure 1 that intermediate impact link 12 is journaled by appropriate bearings 46 in housing 24. Bearings 46 are preferably relatively fluid tight and thus also substantially impervious to deleterious material which could affect the operation of eccentric 18. It should be understood that eccentric 18, which is driven by a prime mover (not shown), is preferably sealed in a chamber 48 which may also be filled with lubricant or the like. At the other opposite end of intermediate impact link 12 is portion 20 which, as shown in Figure 1, need not be integral with intermediate impact link 12, but rather be received in a central bore 50 of intermediate impact link 12. This particular construction is appropriate to provide a replaceable portion of the intermediate impact link 12.
Industrial A~plicability Referring to Figure 1, a recoil damper 10 is shown in the environment of a rock breaker which consists of a shank 14, an intermediate impact link 12, and an eccentric 18. The intermediate impact link 12 is mounted in the housing 24 for movement in first and second opposite directions.
As shown in Figure l, the rock breaker embodiment is in the "at rest" condition with intermediate impact link 12 ~ust resting on the range circle 22 of eccentric 18. Bringing the rock breaker tip 16 into contact with a working surface (not shown) results in shank 14 moving downwardly as shown in Figure 1 into contact with portion 20. ~urther movement of rock breaker tip 16 downwardly results in intermediate impact link 12 moving downwardly against the centering forces of devices 36. As point 51 of .
- , `
i7~'7 eccentric 18 moves around circle 22, contact is made with surface 52 of intermediate impact link 12 by eccentric 18 at a point on the surface thereof between point 53 (on the base circle of eccentric 18) and point 51. As a result of this contact, intermediate impact link 12 is thrust upwardly in Figure 1 causing shank 14 to impart the force of eccentric 18 against the working surface or rock.
Referring to Figure 2, the link 12 is shown in its movement in a second direction during the force stroke toward the working surface. The viscous fluid contained in cavity 26 has been partially compressed in front of the leading edge of flange 28 thus forcing annular ring 38 downwardly against the biasing force of helical spring 42. This movement allows relatively free flow of fluid from the forward portion of cavity 26 denoted as 26a in Figure 2 around the flange 28 and annular ring 38 through the annular cavity 26b formed between the outer surface of annular ring 38 and cavity 26 and into the area 26c behind flange 28 and annular ring 38. As intermediate impact link 12 reaches its full forward or up position, the helical spring 42 urges annular ring 38 back toward the position shown in Figure 1. When recoil motion starts, fluid in portion 26c of cavity 26 is influenced by flange 28 moving downwardly. With annular ring 38 in the up position as shown in Figure 1, fluid is then forced to escape through orifice 40 into cavity 26a thus restricting or retarding movement of the intermediate impact link 12 in the downward direction.
The device 36 serves to center intermediate impact link 12 generally at a mid position as shown in :
, . .
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.
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7(1S'7 Figure 1 so that without rock breaker tip 16 being in contact with a working surface, the intermediate impact link 12 will remain out of contact with eccentric 18.
Finally, stop 44 limits movement of annular ring 38 downwardly during the force stroke. Should annular ring 38 contact stop 44 or come in close proximity thereto during the upward stroke of link 12, grooves 45 will allow the flow of fluid from cavity 26a to cavity 26c. By appropriate sizing of the cavities, annular ring 38 need never come in contact with stop 44 except in extreme conditions.
A Second Mode for Carrying_ ut the Invention Referring now to Figure 3, a second mode for carrying out this invention in the same environment is shown. The like parts are denoted by the same numerals, while new parts are denoted by new numerals.
In this embodiment the damping means 135 includes an annular ring 138 that has an inside diameter slightly smaller than the outside diameter of flange 28 so that during the "at rest" position, annular ring 138 may rest against the rear surface 54 of flange 28. Resilient means such as a helical spring 144 serve to urge annular ring 138 into this position. Annular ring 138 has formed therein a plurality of axial orifices 140 in the manner of an annular ring 38 in the just described embodiment.
Industrial Applicability of the Second Mode Operation of the second embodiment is quite 3~ similar to the first embodiment and will be described in the same context of the rock breaker.
Movement of intermediate link 12 in the upward direction as shown in Figure 3 results in a , . .
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'7 fluid contained in portion 26a of cavity 26 passing freely around flange 28 and the opening formed between forward surface 150 of annular ring 138 and lower surface 54 of flange 28. As recoil starts, annular ring 138 is urged upwardly by helical spring 144 to come into contact with surface 54 of flange 28 thus blocking communication of fluid through the opening between surfaces 54 and 150.
Fluid is then forced through orifice 140 as intermediate impact link 12 moves. Such flow of fluid through orifice 140 retards the movement of intermediate impact link 12 in the downward directionO
Other aspects, objects, and advantages of this invention can be obtained from a study of the drawings, the disclosure, and the appended claims.
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Description A Recoil Damper for a Reciprocating Member Technical Field This invention relates to rock-breaking machinery. In particular it relates to a recoil damper for the reciprocating member of such machinery.
Background Art In reciprocating machinery, and particularly rock breakers, there is a requirement to dampen the motion of the reciprocating mechanism on the recoil stroke. In some rock breakers an eccentric mechanism provides intermittent power strokes to the rock breaker tip or shank through an intermediate impact link located between the eccentric and the shank. In the earlier impact devices the shank was usually impacted directly by the eccentric ring. A seal was generally provided between the shank and the housing.
The seal generally experienced a short life due to the large number of cycles and large displacement (8-1/2 to 9 cm) during each cycle. Recoil of the shank was absorbed by conventional dampening devices located exterior of the drive mechanism. An example of such an exterior recoil damper is found in U.S. Patent 3,868,145.
With the advent of a limited displacement (1-1/2 cm) type intermediate impact link positioned between the eccentric and the shank, the intermediate impact link itself must be dampened as it is relatively free floating in comparison to the more conventional shank and eccentric. That is, the intermediate impact link~ being located between the enclosed eccentric and the exterior shank, transmits -- ~:
: . ' ~ '.~, khe force of the eccentric to the shank. In order to provide relatively free movement toward the shank, the intermediate impact link is mounted in appropriate bearings positioned in the housing. However, upon recoil, the recoil force would ordinarily be transmitted to the eccentric thus causing excessive wear on the eccentric unless some form of recoil damper is used.
In such intermediate impact link type rock breakers, the force to be applied to the shank ordinarily does not occur until the shank is displaced rearwardly to engage the intermediate impact link which is also displaced rearwardly into position to be contacted by the eccentric. As the eccentric rotates so that its periphery contacts the intermediate impact link, the force of the eccentric is transmitted through the intermediate impact link to the shank which in turn acts on the working sur~ace. As the eccentric continues to rotate, the force is relieved from the intermediate impact link, thus permitting the shank to recoil with such recoil transmitted to the intermediate impact link. Although the motion of the shank could be dampened in the manner shown in the U.S.
Patent No. 3,868,145, that is an exterior damper may be mounted adjacent the shank, the recoil motion of the intermediate impact link which is contained substantially within the housing must also be dampened.
The present invention is directed to overcoming one or more o~ the problems as set forth above.
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Disclosure of the Invention In one aspect of the present invention, there is provided a recoil damper comprising: a housing, a member reciprocally mounted in said housing for movement in first and second opposite directions, a radial flange on said member, first and second cavities defined in said housing on opposite sides of said flange and containing a damping fluid therein, and damping means-for restricting flow of said damping flu;d from said second cavity to said first cavity in response to compression of damping fluid in said second cavity by said flange when said member is moved in said first direction and for permitting relatively free flow of damping fluid from said first cavity to said second cavity in response to compression of damping fluid in said first cavity by said flange when said member is moved in said second direction.
According to another aspect of the invention there is provided a hydraulic piston damper, comprising: a housing having a piston bore providing opposite end portions; a fluid cavity in the housing communicating with said piston bore intermediate said end portions thereof; a reciprocal piston axially slidably disposed in said piston bore and having a radially outwardly extended flange projecting into said cavity in fluid pumping relation to a fixed volume of trapped fluid within the cavity; a damper control member disposed for axial sliding movement within said cavity relative to said flange and providing a restricted orifice; and spring means for biasing said control member toward a position blocking the flow of fluid past said flange to force fluid through said orifice in dampening relation to movement of said piston in one axial direction of travel, and said control member being responsive to fluid pressure within said cavity for movement to a position providing substantially unrestricted flow of fluid past said flange B
~57V~i7 -3a-during travel of said piston in an opposite axial direction.
Brief Description of-the Drawings Figure 1 is a schemati`c view, partly in section, of an em~odiment of a recoil damper as us~ed with an intermedïate link of a rock breaker.
Figure 2 is a detailed sectional view of the embodiment of the recoil damper shown in Figure 1.
Figure 3 is a schematic view of an alternate embodiment of the recoil damper.
Best Mode of Carrying-Out the Invention Referring to Figure l, a recoil damper 10 is shown with an intermediate impact link 12 of an impact type rock breaker.
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The impact type rock breaker consists of a shank 14 having as a portion thereof a rock breaker tip 16 used to impact and thus break rock. An eccentric mechanism 18 provides intermittent power strokes to intermediate impact link 12 which in turn are transmitted to shank 14. It should be noted that Figure 1 illustrates the rock breaker in the "at rest" condition. As the rock breaker ~ip 16 is brought into contact with the material to be broken, the shank 14, which is pivoted from a mounting (not shown), is in turn brought into contact with a portion 20 of intermediate impact link 12. Further imposition of force by rock breaker tip 16 against a surface to be broken results in intermediate impact link 12 moving downwardly as shown in Figure 1 or in a first direction thus bringing the intermediate impact link 12 into the range of eccentric 18. This range is denoted by the dashed circle 22 in Figure 1. As eccentric 18 rotates, it will contact intermediate impact link 12 to urge it in a second opposite direction.
Housing 24 defines a bore 25 in which intermediate impact link 12 is slidably positioned. Also defined in housing 24 is a cavity 26 generally adjacent the midpoint of bore 25 of housing 24. Intermediate impact link 12 is preferably cylindrical and has a flange 28 extending generally about the midpoint thereof. The flange 28 is adapted to be received in the cavity 26.
In order to form cavity 26 to concurrently receive flange 28, housing 24 must be made in at least two portions, front portion 30 and rear portion 32. In the embodiment shown in Figure 1, ..
'7 a mid portion 34 is also utilized to facilitate installation of other centering devices 36 utilized to center intermediate impact link 12 in housing 24.
Appropriate fastening means 37, in this instance elongated bolts, are utilized to interconnect the various portions of housing 24.
Damping means 35 for retarding movement of the reciprocating intermediate impact link 12 are located in cavity 26. These means include an annular ring 38 which, in this embodiment, is formed to slidably move on flange 28 of intermediate impact link 12 in said first and second directions. Formed in annular ring 38 are a plurality of orifices 40. Each orifice 40 is oriented in the axial direction thus permitting communication of a viscous fluid which also forms a portion of the means for retarding recoil and which is located in cavity 26.
Annular ring 38 is biased toward front portion 30 of housing 24 by a plurality of resilient members such as helical springs 42. Located at the rearward end of cavity 26 is a stop 44. Referring to Figure 2, it can be seen that stop 44 may also be an annular ring which is located adjacent the outer portion of cavity 26. The inner diameter of stop 44 is less than the outer diameter of annular ring 38, so that upon movement of annular ring 38 downwardly as shown in Figure 2, ring 38 will contact stop 44 before coming into contact with housing 24. A
plurality of grooves 45 are formed in the upper surface of stop 44 so that fluid trapped in cavity 26a and cavity 26b with annular ring 38 seated or in close proximity to stop 44 may pass thereby into cavity 26c.
, :
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: :
~L~S7~5~7 It can be seen in Figure 1 that intermediate impact link 12 is journaled by appropriate bearings 46 in housing 24. Bearings 46 are preferably relatively fluid tight and thus also substantially impervious to deleterious material which could affect the operation of eccentric 18. It should be understood that eccentric 18, which is driven by a prime mover (not shown), is preferably sealed in a chamber 48 which may also be filled with lubricant or the like. At the other opposite end of intermediate impact link 12 is portion 20 which, as shown in Figure 1, need not be integral with intermediate impact link 12, but rather be received in a central bore 50 of intermediate impact link 12. This particular construction is appropriate to provide a replaceable portion of the intermediate impact link 12.
Industrial A~plicability Referring to Figure 1, a recoil damper 10 is shown in the environment of a rock breaker which consists of a shank 14, an intermediate impact link 12, and an eccentric 18. The intermediate impact link 12 is mounted in the housing 24 for movement in first and second opposite directions.
As shown in Figure l, the rock breaker embodiment is in the "at rest" condition with intermediate impact link 12 ~ust resting on the range circle 22 of eccentric 18. Bringing the rock breaker tip 16 into contact with a working surface (not shown) results in shank 14 moving downwardly as shown in Figure 1 into contact with portion 20. ~urther movement of rock breaker tip 16 downwardly results in intermediate impact link 12 moving downwardly against the centering forces of devices 36. As point 51 of .
- , `
i7~'7 eccentric 18 moves around circle 22, contact is made with surface 52 of intermediate impact link 12 by eccentric 18 at a point on the surface thereof between point 53 (on the base circle of eccentric 18) and point 51. As a result of this contact, intermediate impact link 12 is thrust upwardly in Figure 1 causing shank 14 to impart the force of eccentric 18 against the working surface or rock.
Referring to Figure 2, the link 12 is shown in its movement in a second direction during the force stroke toward the working surface. The viscous fluid contained in cavity 26 has been partially compressed in front of the leading edge of flange 28 thus forcing annular ring 38 downwardly against the biasing force of helical spring 42. This movement allows relatively free flow of fluid from the forward portion of cavity 26 denoted as 26a in Figure 2 around the flange 28 and annular ring 38 through the annular cavity 26b formed between the outer surface of annular ring 38 and cavity 26 and into the area 26c behind flange 28 and annular ring 38. As intermediate impact link 12 reaches its full forward or up position, the helical spring 42 urges annular ring 38 back toward the position shown in Figure 1. When recoil motion starts, fluid in portion 26c of cavity 26 is influenced by flange 28 moving downwardly. With annular ring 38 in the up position as shown in Figure 1, fluid is then forced to escape through orifice 40 into cavity 26a thus restricting or retarding movement of the intermediate impact link 12 in the downward direction.
The device 36 serves to center intermediate impact link 12 generally at a mid position as shown in :
, . .
- :
.
, ~ :
7(1S'7 Figure 1 so that without rock breaker tip 16 being in contact with a working surface, the intermediate impact link 12 will remain out of contact with eccentric 18.
Finally, stop 44 limits movement of annular ring 38 downwardly during the force stroke. Should annular ring 38 contact stop 44 or come in close proximity thereto during the upward stroke of link 12, grooves 45 will allow the flow of fluid from cavity 26a to cavity 26c. By appropriate sizing of the cavities, annular ring 38 need never come in contact with stop 44 except in extreme conditions.
A Second Mode for Carrying_ ut the Invention Referring now to Figure 3, a second mode for carrying out this invention in the same environment is shown. The like parts are denoted by the same numerals, while new parts are denoted by new numerals.
In this embodiment the damping means 135 includes an annular ring 138 that has an inside diameter slightly smaller than the outside diameter of flange 28 so that during the "at rest" position, annular ring 138 may rest against the rear surface 54 of flange 28. Resilient means such as a helical spring 144 serve to urge annular ring 138 into this position. Annular ring 138 has formed therein a plurality of axial orifices 140 in the manner of an annular ring 38 in the just described embodiment.
Industrial Applicability of the Second Mode Operation of the second embodiment is quite 3~ similar to the first embodiment and will be described in the same context of the rock breaker.
Movement of intermediate link 12 in the upward direction as shown in Figure 3 results in a , . .
` '~-, . , , ~
'7 fluid contained in portion 26a of cavity 26 passing freely around flange 28 and the opening formed between forward surface 150 of annular ring 138 and lower surface 54 of flange 28. As recoil starts, annular ring 138 is urged upwardly by helical spring 144 to come into contact with surface 54 of flange 28 thus blocking communication of fluid through the opening between surfaces 54 and 150.
Fluid is then forced through orifice 140 as intermediate impact link 12 moves. Such flow of fluid through orifice 140 retards the movement of intermediate impact link 12 in the downward directionO
Other aspects, objects, and advantages of this invention can be obtained from a study of the drawings, the disclosure, and the appended claims.
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Claims (12)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A recoil damper comprising:
a housing, a member reciprocally mounted in said housing for movement in first and second opposite directions, a radial flange on said member, first and second cavities defined in said housing on opposite sides of said flange and containing a damping fluid therein, and damping means for restricting flow of said damping fluid from said second cavity to said first cavity in response to compression of damping fluid in said second cavity by said flange when said member is moved in said first direction and for permitting relatively free flow of damping fluid from said first cavity to said second cavity in response to compression of damping fluid in said first cavity by said flange when said member is moved in said second direction.
a housing, a member reciprocally mounted in said housing for movement in first and second opposite directions, a radial flange on said member, first and second cavities defined in said housing on opposite sides of said flange and containing a damping fluid therein, and damping means for restricting flow of said damping fluid from said second cavity to said first cavity in response to compression of damping fluid in said second cavity by said flange when said member is moved in said first direction and for permitting relatively free flow of damping fluid from said first cavity to said second cavity in response to compression of damping fluid in said first cavity by said flange when said member is moved in said second direction.
2. The recoil damper of claim 1 wherein said damping means comprises an annular ring positioned between said first and second cavities.
3. The recoil damper of claim 2 wherein said damping means further comprises means for biasing said annular ring in said second direction.
4. The recoil damper of claim 2 further comprising a plurality of orifices formed axially through said ring.
5. The recoil damper of claim 2 wherein said annular ring is slidably mounted on the periphery of said flange.
6. The recoil damper of claim 2 wherein said annular ring has an inside diameter less than an outside diameter of said flange and is positioned on an axial side of said flange.
7. The recoil damper of claim 1 wherein said member comprises an impact link and further including a shank having a tip thereon, and eccentric means for intermittently reciprocating said impact link and said shank.
8. A hydraulic piston damper, comprising:
a housing having a piston bore providing opposite end portions;
a fluid cavity in the housing communicating with said piston bore intermediate said end portions thereof;
a reciprocal piston axially slidably disposed in said piston bore and having a radially outwardly extended flange projecting into said cavity in fluid pumping relation to a fixed volume of trapped fluid within the cavity;
a damper control member disposed for axial sliding movement within said cavity relative to said flange and providing a restricted orifice; and spring means for biasing said control member toward a position blocking the flow of fluid past said flange to force fluid through said orifice in dampening relation to movement of said piston in one axial direction of travel, and said control member being responsive to fluid pressure within said cavity for movement to a position providing substantially unrestricted flow of fluid past said flange during travel of said piston in an opposite axial direction.
a housing having a piston bore providing opposite end portions;
a fluid cavity in the housing communicating with said piston bore intermediate said end portions thereof;
a reciprocal piston axially slidably disposed in said piston bore and having a radially outwardly extended flange projecting into said cavity in fluid pumping relation to a fixed volume of trapped fluid within the cavity;
a damper control member disposed for axial sliding movement within said cavity relative to said flange and providing a restricted orifice; and spring means for biasing said control member toward a position blocking the flow of fluid past said flange to force fluid through said orifice in dampening relation to movement of said piston in one axial direction of travel, and said control member being responsive to fluid pressure within said cavity for movement to a position providing substantially unrestricted flow of fluid past said flange during travel of said piston in an opposite axial direction.
9. The piston damper of claim 8 in which said control member effectively divides said cavity into opposed discrete compartments located substantially entirely radially outwardly of said flange of the piston which are alternately opened and closed with respect to each other during reciprocation of said piston.
10. The piston damper of claim 9 in which said piston is cylindrical and provides opposite power and recoil strokes; said control member is an annular ring disposed in circumscribing relation to said piston; and said spring means includes a plurality of compression springs disposed within one compartment of said cavity and providing only a minimum of resistance to said fluid pressure in the opposite compartment during said power stroke of the piston and effective to position said ring in its blocking position prior to initiation of said piston to its recoil dampening stroke.
11. The piston damper of claim 10 in which said flange on the piston and said control ring are radially overlapping for sealing engagement with each other when the ring is in said blocking position.
12. The piston damper of claim 10 in which said control ring is disposed in circumscribing relation to said flange on the piston; and said cavity being defined by a wall having a portion adapted to be engaged in sealing relation by said ring in its blocking position.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US24524680A | 1980-05-27 | 1980-05-27 | |
| PCT/US1980/000641 WO1981003532A1 (en) | 1980-05-27 | 1980-05-27 | A recoil damper for a reciprocating member |
| US245,246 | 1980-05-27 | ||
| US80/00641 | 1980-05-27 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1157057A true CA1157057A (en) | 1983-11-15 |
Family
ID=26762707
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000367990A Expired CA1157057A (en) | 1980-05-27 | 1981-01-07 | Recoil damper for a reciprocating member |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1157057A (en) |
-
1981
- 1981-01-07 CA CA000367990A patent/CA1157057A/en not_active Expired
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