Hydraulic hammer with damping accumulator

Abstract

A hydraulic hammer (102) for impacting and breaking a work object includes a hammer housing (130) having a cylinder (138) disposed between a front head (134) and a rear head. A piston (142) reciprocatingly movable within the cylinder (138) abuts the work tool (132) and may extend and retract the work tool (132) from the hammer housing (130). To damp momentum and impact forces, an accumulator head (154) is attached to the aft head (136) and may contain hydraulic and damping fluids in separate first and second sub-chambers. The damping sub-chamber may be in direct fluid communication with an internal damping fluid reservoir in the aft head (136).

Description

TECHNICAL FIELD

[0001] The present patent disclosure relates to a hydraulic hammer, and more particularly, to a hydraulic hammer having an accumulator chamber that can receive a damping fluid to dampen the impact forces generated by operation of the hydraulic hammer. BACKGROUND

[0002] Hydraulic hammers are work tools that can be attached to various carrier machines or other structures such as excavators, backhoe loaders, stationary or static platforms, and other tool carriers for the purpose of grinding or breaking up stone, concrete, and other construction materials. Hydraulic hammers convert a flow of pressurized hydraulic fluid to a reciprocating motion of a work tool that can impart impact forces against an object such as a work structure or other surface. The repeated and sudden application of impact forces are of sufficient magnitude to break and fragment the work object of interest. However, the impact forces can also be of sufficient magnitude to vibrate and possibly damage the carrier machine or other structure in the vicinity of the hydraulic hammer. In addition, repeated exposure to the reciprocating impact forces can cause the operator to be uncomfortable and disoriented over an extended period of time.

[0003] To dampen the impact forces acting on the carrier machine, the hydraulic hammer can include a damping or impact system that absorbs the impact forces transmitted through the structure of the carrier machine or other structure. For example, one simple solution can be to position rubber or other resilient material at the joints and connections between the hydraulic hammer and the carrier machine. Other solutions can utilize the force absorption and fluid properties of viscous fluids to provide active damping of the impact forces. For example, U.S. Patent No. 10,570,930 describes an accumulator configured for use with an impact hammer that utilizes a working gas to dampen the impact forces generated by operation of the hammer. The present invention similarly relates to improvements in the field of active force damping of hydraulic hammers by utilizing a damping fluid or gas. SUMMARY

[0004] In one aspect, the present invention describes a hydraulic hammer that includes a cylinder body disposed between a rear head and a front head. A cylinder bore extending along a hammer axis is defined in part within the cylinder body. A piston is reciprocally movable disposed within the cylinder bore for reciprocation along the hammer axis. The piston can be an elongated rod-like structure that includes a first piston end and a second piston end. The hydraulic hammer can also include a seal carrier disposed in the rear head that is configured to receive the second piston end as the piston reciprocates along the hammer axis. To facilitate damping of momentum and impact forces, an accumulator head can be attached at an axially rearward end of the rear head. The accumulator head defines an accumulator chamber in which a membrane is disposed that separates the accumulator chamber between a hydraulic sub-chamber for containing hydraulic fluid and a damping sub-chamber for containing a damping fluid. The damping sub-chamber is axially proximate to and in fluid communication with the rear head.

[0005] In another aspect, the present invention describes a hydraulic hammer including a cylinder disposed between a rear head and a front head. A cylinder bore extending along a hammer axis is defined in part in the cylinder. A piston is reciprocally disposed in the cylinder bore for reciprocation along the hammer axis. The piston is an elongated rod-like structure and can include a first piston end and a second piston end. To facilitate damping of momentum and impact forces, an accumulator head is attachable to an axially rearward end of the rear head. The accumulator head defines an accumulator chamber in which a membrane is disposed that separates the accumulator chamber between a hydraulic sub-chamber for containing hydraulic fluid and a damping sub-chamber for containing damping fluid. The hydraulic hammer further includes an internal damping fluid reservoir in the rear head in direct fluid communication with the damping sub-chamber disposed in the accumulator head. BRIEF DESCRIPTION OF DRAWINGS

[0006] Figure 1 is a top perspective view of a carry machine equipped with a hydraulic hammer for breaking and crushing material at a worksite.

[0007] Figure 2 is a perspective view of a hydraulic hammer that converts pressurized flow of hydraulic fluid to reciprocation of a work tool.

[0008] Figure 3 is a perspective cross-sectional view of a hydraulic hammer including a rear head and an accumulator head that includes an accumulator chamber separated into sub-chambers by a membrane that are arranged to advantageously utilize working fluids associated with the hammer.

[0009] Figure 4 is a side cross-sectional view of the rear head and the accumulator head with the accumulator cap arranged for direct fluid communication between a damping sub-chamber disposed in the accumulator cap and an internal damping reservoir disposed in the rear head. DETAILED DESCRIPTION

[0010] Reference will now be made to the drawings wherein like numerals refer to like features throughout the several figures, and Figure 1An embodiment of a carry machine 100 equipped with a hydraulic hammer 102 is shown in FIG. 1. To physically transport the hydraulic hammer 102 around a worksite, the carry machine 100 as a backhoe loader can include a machine frame 104 that is supported on a plurality of propulsion devices such as wheels, or in other embodiments, on continuous tracks. To power the carry machine 100, the machine frame 104 can also include an engine compartment 106 in which an internal combustion engine or another type of power plant and associated power train components are housed. To accommodate an operator, an operator station or operator cab 108 can be provided on the machine frame 104. It should be appreciated that while the present disclosure is described with respect to a backhoe loader, aspects of the present disclosure will be applicable to other types of mobile carry machines such as excavators, skid loaders, and the like. Moreover, the present disclosure is not limited to hydraulic hammers 102 coupled to mobile machines, but can be applied to fixed and stationary applications.

[0011] To support and manipulate the hydraulic hammer 102, the carry machine 100 can include an articulated arm 120 or associated mechanical linkage. The articulated arm 120 has a first link, referred to as a boom 122, that is pivotally attached at one end to the machine frame 104, and a second link, referred to as a stick 124, that is joined at a hinge 126 to an opposite end of the boom 122. To articulate the boom 122 and the stick 124, the articulated arm 120 can be operatively associated with one or more actuators in embodiments of hydraulic cylinders 128. The hydraulic cylinders 128 can telescopically extend and retract to articulate the articulated arm 120 relative to the hinge 126 to raise, lower, and swing the hydraulic hammer 102. To provide pressurized hydraulic fluid to the hydraulic cylinders 128, the carry machine 100 can be operatively associated with a hydraulic system that includes hydraulic pumps, filters, conduits, and associated hydraulic equipment. The hydraulic system can also supply pressurized hydraulic fluid to the hydraulic hammer.

[0012] To break and fragment material at a worksite, the hydraulic hammer 102 can include a hammer body or housing 130 and a working tool 132 that partially protrudes from the hammer housing 130 and is extendable and retractable relative to the hammer housing 130. The hammer housing 130 can include a front head 134 from which the working tool 132 protrudes, a rear head 136 coupled and attached to a distal end of the arm 124, and a cylinder body 138 extending between the front head 134 and the rear head 136. As used herein, directional terms such as "front" or "forward" relative to the front head 134 and "rear" or "rearward" relative to the rear head 136 are for reference purposes only and do not constitute a limitation on the present disclosure. The hammer housing 130 also covers and houses actuating equipment and devices that forcibly reciprocate the working tool 132 relative to the hammer housing 130. To impact and penetrate working objects around a worksite, the working tool 132 in various embodiments can be implemented as a pick or a chisel bit.

[0013] Referring to Figure 2 The cylinder body 138 can form and be shaped as a cylinder that defines a cylinder bore 140 within which a piston 142 is housed. The piston 142 can have an elongated rod-like shape and can extend between a first or front piston end 144 disposed generally within the cylinder body 138 and a second or rear piston end 146 disposed generally within the rear head 136. The front piston end 144 can abut the working tool 132 disposed within the front head 134 of the hammer housing 130. The piston 142 can be complementary in shape and size to the cylinder bore 140 and can be reciprocally movable within the cylinder bore 142 along a hammer axis 148 corresponding to an axis of the hydraulic hammer. The hammer axis 148 can extend axially through the hammer housing 130 such that the front head 134 and the rear head 136 are at opposite axial ends of the hydraulic hammer 102.

[0014] To reciprocate the piston 142, and thus the working tool 132 along the hammer axis 148, the rear head 136 can include a hydraulic coupler 150 having an inlet and an outlet to receive and / or discharge pressurized hydraulic fluid from, for example, a carrier machine. To dampen forces associated with axial reciprocation of the piston 142 and abutting working tool 132 along the hammer axis 148, an accumulator head 154 can be attached at an axially rear end 156 of the rear head 136. The front head 134 can include an inner bushing 158 and a seal disposed about and slidable relative to the piston 142 to seal the cylinder bore 140.

[0015] Referring to Figure 3 and Figure 4, there is an embodiment of the interior arrangement of the rear head 136 of the hydraulic hammer 102 and the upper portion of the cylinder 138. As described above, the piston 142 has a rod-like shape, including a rear piston end 146 disposed within the rear head 136. To receive and house the rear piston end 146 of the reciprocally movable piston 142, a seal carrier 160 can be disposed within the rear head 136. The seal carrier 160 can have a cap-like structure or shape including a cylindrical carrier wall 162 and an axial carrier end face 164. The cap-like structure or shape of the seal carrier 160 defines a piston-receiving volume 166 that is complementary in shape and size to the rear piston end 146 and is capable of slidably receiving the rear piston end 146. Fluid communication with the piston-receiving volume 166 is established through a plurality of carrier fluid ports 168 disposed through the cylindrical carrier wall 162. The seal carrier 160 can also be disposed in fluid communication with the bore 140, and similarly, concentrically with respect to the hammer axis 148.

[0016] In one embodiment, the seal carrier 160 can be reciprocally movable within the rear head 136 with respect to the hammer axis 148. In this embodiment, the outer diameter of the cylindrical carrier wall 162 can be sized relative to the diameter of the concentric bore 140 to allow for limited axial displacement of the seal carrier 160 to accommodate the greater axial displacement of the reciprocating piston 142.

[0017] A plurality of interior hydraulic fluid passages 170 and one or more diverter valves 172 can also be disposed within the rear head 136 that direct pressurized hydraulic fluid with respect to the piston 142 to cause reciprocating motion along the hammer axis 148. Figure 4 An exemplary arrangement of the hydraulic fluid passages 170 and diverter valves 172 is shown, but the present invention is not limited to any particular arrangement, but can be applied to more complex and competing arrangements of passages and valves. As an example, the hydraulic fluid passages 170 can be in direct or indirect fluid communication with the hydraulic coupler 150 located outside of the rear head 136 to receive and / or discharge pressurized hydraulic fluid. In one example, the diverter valves 172 can be three-way valves (symbolically indicated) that are capable of selectively diverting hydraulic fluid to different locations. For example, the diverter valves 172 can selectively divert incoming pressurized hydraulic fluid between the carrier fluid ports 168 of the seal carrier 160 and a retraction passage 174 that is disposed axially through the rear head 136 and the cylinder 138, and parallel to and offset from the bore 140 and the piston 142 therein.

[0018] During hydraulic hammering operations, to axially retract the piston 142 rearward along the hammer axis 148 so that the rear piston end 146 is received into the piston receiving volume 166 of the seal carrier 160, the diverter valve 172 can be configured to direct hydraulic fluid to the retraction passage 174. The retraction passage 174 can be in fluid communication with the bore 140 at an axially forward position relative to the rear head 136 and the seal carrier 160 so that pressurized hydraulic fluid entering the bore 140 displaces the piston 142 upward within the hammer housing 130. To extend the piston 142 axially forward along the hammer axis 148 and to expel the rear piston end 146 from the piston receiving volume 166, the diverter valve 172 can be configured to direct pressurized hydraulic fluid to the carrier fluid port 168 in the seal carrier 160. The accumulation of pressurized hydraulic fluid within the piston receiving volume 166 forces the piston 142, and thus the abutting work tool, forward relative to the hammer housing 130 and thus performs a percussive hammering operation.

[0019] It can be appreciated that the reciprocating extension and retraction of the piston along the hammer axis 148 will generate momentum forces parallel to the hammer axis 148 that tend to moveably rock or vibrate the hydraulic hammer 102. Likewise, when the work tool impacts the work object, impact forces will be transmitted or propagated through the piston 142 and the hammer housing 130 parallel to the hammer axis 148. Accordingly, in one embodiment, the accumulator head 154 located axially rearward of the rear head 136 can be configured to dampen or dissipate momentum and impact forces generated by the operation of the hydraulic hammer.

[0020] For example, the accumulator head 154 can be configured to utilize pressurized hydraulic fluid and a second, damping fluid that can readily flow and displace to absorbively accommodate momentum and impact forces. In one embodiment, the accumulator head 154 can define an accumulator chamber 180 therein that can be a hollow, open volume for receiving fluid. In particular embodiments, to define the accumulator chamber 180, the accumulator head 154 can include an accumulator shell 182 made of a rigid material, such as structural steel, and the accumulator shell 182 can be attached to the axially rear end 156 of the rear head 136 via threaded fasteners 184, such as bolts, or in other embodiments, the accumulator shell 182 can be welded to the rear head 136. The accumulator shell 182 can be shaped to define a first, interior accumulator cavity 186. Corresponding to the accumulator shell 182, the axially rear end 156 of the rear head 136 can also be configured to define a second, interior accumulator cavity 188. In another embodiment, the first and second interior accumulator cavities 186, 188 can have opposing dome or frustoconical shapes, and the accumulator chamber 180 can be generally circular with varying diameters that taper or increase and decrease along the hammer axis 148.

[0021] To separately contain the hydraulic fluid H and the second damping fluid D, a flexible diaphragm or membrane 190 can be located in the accumulator chamber 180. The membrane 190 can be made of a sheet of flexible or bendable material such as rubber or flexible thermoplastic, and can have a thin, disc-like shape. The shape of the membrane 190 can be circular to correspond to the circular cross-section of the accumulator chamber 180. To support the membrane 190 within the accumulator chamber 180, a circular peripheral edge 192 of the membrane 190 can be clamped or sandwiched between the axial rear end 156 of the rear head 136 and the accumulator shell 182 when the membrane 190 is fastened to the accumulator shell 182.

[0022] The membrane 190 can be generally perpendicular to the hammer axis 148, and thus acts as a barrier that separates the accumulator chamber 180 into a first sub-chamber 194 (hereinafter referred to as a damping sub-chamber) and a second sub-chamber 196 (hereinafter referred to as a hydraulic sub-chamber). The damping sub-chamber contains the damping fluid D, and the hydraulic sub-chamber contains pressurized hydraulic fluid H that can be supplied from the hydraulic coupler 150 on the rear head 136. The damping sub-chamber 194 and the hydraulic sub-chamber 196 can exhibit a truncated conical or dome-like shape of the first and second internal cavities 186 with which they are associated. The damping sub-chamber 194 can be disposed axially in front of the hydraulic sub-chamber 196 with respect to the hammer axis 148 and the membrane 190 that is oriented perpendicularly thereto. In a structural sense, the damping sub-chamber 194 can be closely defined by or within the rear head 136, and the hydraulic sub-chamber 196 can be defined by or within the accumulator shell 182 that is located axially rearward of the rear head 136.

[0023] The flexible nature of the membrane 190 can allow the membrane to shift into the damping sub-chamber 194 or the hydraulic sub-chamber 196 depending on the pressure differential between the sub-chambers. In one embodiment, the membrane 190 can be configured as a rolling diaphragm 200. The rolling diaphragm 200 has a diameter that is greater than the diameter of the hole in which it is fixed, and includes a flexible rolling flange 202 that extends between a flat head portion 204 and the peripheral edge 192 of the membrane 190. The rolling flange 202 can be offset in a direction from the flat head portion 204, and is joined to the head by a head radius 206. The rolling flange 202 can be connected to the peripheral edge 192 of the membrane at a second flange radius 208. To accommodate movement of the membrane 190 into the damping sub-chamber 194 and the hydraulic sub-chamber 196, the rolling flange 202 can flexibly translate generally between the head radius 206 and the flange radius 208 by folding over on itself, thereby allowing the distance between the flat head portion 204 and the peripheral edge 192 of the membrane 190 to be adjusted. In other embodiments, the membrane 190 can be a substantially flat flexible sheet or can have any other suitable shape.

[0024] To receive the damping fluid D, the damping sub-chamber 194 can be in fluid communication with a damping fluid port 210 located externally via a damping fluid passage 212 provided through the material of the rear head 136. The damping fluid D can be any suitable compressible damping liquid or gas, and in an embodiment, can be gaseous nitrogen. The damping fluid D can be contained in the damping sub-chamber at an appropriate pre-charge pressure (e.g., 40 to 60 bar).

[0025] To receive the hydraulic fluid H, the hydraulic sub-chamber 196 can be in fluid communication with a hydraulic fluid passage 170 provided in the hammer housing 130. In one embodiment, the hydraulic sub-chamber 196 can be fluidly associated with a hydraulic sub-chamber passage 214 provided through the rear head 136 and the accumulator housing 182 to establish fluid communication with the retraction passage 174 downstream of the diverter valve 172. Thus, the hydraulic sub-chamber 196 can be in pressure equilibrium with the cylinder bore 142 in which the piston 142 is reciprocally and slidably disposed. As such, the hydraulic sub-chamber 196 can also receive pressurized hydraulic fluid H from a hydraulic system associated with a carrier machine via the hydraulic coupler 150 located externally of the rear head 136.

[0026] In one embodiment, the rear head 136 can include an internal damping fluid reservoir 216 located therein. The internal damping fluid reservoir 216 can be generally axially aligned with and rearward of the seal carrier 160, and can be defined between the axial carrier end face 164 and the axial rear end 156 of the rear head 136. The internal damping fluid reservoir 216 can be formed as part of the cylinder bore 140, and can be separated by the seal carrier 160 from the remainder of the cylinder bore 140. In orientation with respect to the hammer axis 148, the internal damping fluid reservoir 216 is axially rearward of the seal carrier 160 and axially forward of the accumulator chamber 180.

[0027] To receive the damping fluid D, the internal damping fluid reservoir 216 can be in direct fluid communication with the damping sub-chamber 194 via a plurality of damping fluid holes 218 provided through the second internal accumulator cavity 188 and the axial rear end 156 of the rear head 136. As used herein, direct fluid communication refers to the damping fluid D flowing directly between the internal damping fluid reservoir 216 and the damping sub-chamber 194 without being directed through an elongated or tortuous passage or pathway. In the present embodiment, the damping sub-chamber 194 and the internal damping fluid reservoir 216 are effectively the same integral volume with the damping fluid D flowing freely therebetween via the plurality of damping fluid holes 218.

[0028] The advantages of placing the damping sub-chamber 194 and the internal damping fluid reservoir 216 in an axially adjacent, tightly coupled arrangement, such that damping fluid D can flow directly between the two structures, is that the overall height of the hydraulic hammer can be reduced, and the need for long and / or tortuous internal fluid passages to direct damping fluid between the two structures is eliminated. Further, the internal damping fluid reservoir 216 is in fluid communication with the damping fluid port 210 through the damping sub-chamber 194, such that only a single damping fluid port is required to charge the hydraulic hammer with pressurized damping fluid.

[0029] INDUSTRIAL APPLICABILITY

[0030] WITH REFERENCE TO Figure 3 AND Figure 4 With continued reference to all of the Figures, in operation, when the piston 142 extends relative to the bore 140 to cause the work tool 132 to impact and strike a work object, an impact force can be transmitted rearward relative to the hammer axis 148. The impact force can tend to displace the seal carrier 160, which is movably disposed in the bore 140, upward. As a result, the axial carrier end face 164 compresses the damping fluid D in the internal damping fluid reservoir 216, which exerts an opposing reaction force to the impact force. As a result, the damping fluid D absorbs and / or dissipates the impact force.

[0031] Further, if these opposing reaction forces are less than the magnitude of the impact force and insufficient to resist movement of the seal carrier 160, the damping fluid D in the internal damping fluid reservoir 216 can be transferred into the damping sub-chamber 194 via the plurality of damping fluid apertures 218. In the event that damping fluid D moves from the internal damping fluid reservoir 216 into the damping sub-chamber 194, the pressurized hydraulic fluid H can be expelled from the hydraulic sub-chamber 196 by the flexible movement of the membrane 190, and can flow to the hydraulic fluid passage 170 via the hydraulic sub-chamber passage 214.

[0032] Conversely, when the piston 142 is axially retracted into the bore 140, the momentum force can be directed parallel to the hammer axis 148 toward the seal carrier 160, causing the seal carrier to press against the internal damping fluid reservoir 216. The damping fluid D in the internal damping fluid reservoir 216 can again resist further transmission of the momentum force, and can be displaced into the damping sub-chamber 194 if necessary. The pressurized hydraulic fluid H in the oppositely disposed hydraulic sub-chamber 196 will resist further movement of the damping fluid D into the damping fluid sub-chamber by exerting pressure against the membrane 190.

[0033] As a result, the opposing pressures of the hydraulic fluid H in the hydraulic sub-chamber 196 and the damping fluid D in the damping sub-chamber 194 can balance, counter, dissipate, and reduce momentum and impact forces in the hydraulic hammer 102.

[0034] It should be understood that the foregoing description is only illustrative of the embodiments of the disclosed system and techniques. However, various modifications can be made to the embodiments described above, in addition to those not specifically described or suggested herein, without departing from the spirit of the present application. All references to the application or its examples are intended to reference the particular example being discussed at that point in time and not necessarily all examples alike, but are intended to cover all bases equally. All language of distinction and disclaimer, whether explicitly found or implied, should be regarded in that light.

[0035] Unless otherwise stated herein, recitation of a range of values herein is merely intended to serve as a shorthand method of referring individually to each separate value falling within the range, and each separate value is incorporated in the specification as if it were individually recited herein. All methods described herein can be performed in any suitable order unless otherwise specified herein or otherwise clearly contradicted by context.

[0036] In the context of describing the application (particularly in the context of the appended claims), the use of the terms “one” and “an” and “the” and “at least one” and similar referents in reference to an item should be interpreted to cover both the singular and plural of that item, unless otherwise indicated by context. The use of the term “at least one” following the presentation of a list of one or more items should be interpreted to indicate that any single item in the list can be present or that any combination of the items in the list can be present, unless otherwise indicated by context. In other words, the use of “at least one” should not be interpreted as requiring the presence of at least one item, but rather indicating that one or more items can be present.

[0037] Accordingly, the present application includes all modifications and equivalents of the subject matter recited in the claims appended hereto as permitted by applicable law. Moreover, any combination of the elements from any of the previously described examples can be covered within the scope of the present application, unless otherwise indicated herein or otherwise clearly contradicted by context.

Claims

1. A hydraulic hammer (102), comprising: A cylinder block (138) is disposed between the rear head (136) and the front head (134) and partially defines a cylinder bore (140) extending along the hammer axis (148); A piston (142) is reciprocally disposed within the cylinder bore (140) for reciprocating motion along the hammer axis (148), the piston (142) comprising a first piston end and a second piston end; A sealing support (160), disposed in the rear head (136) and configured to receive the second piston end during the reciprocating motion of the piston (142) along the hammer axis (148); and An accumulator head (154) is disposed on the axial rear end (156) of the rear head (136), the accumulator head (154) defining an accumulator chamber (180) in which a membrane (190) is disposed, the membrane (190) separating the accumulator chamber (180) between a hydraulic sub-chamber (196) for containing hydraulic fluid and a damping sub-chamber (194) for containing damping fluid, wherein the damping sub-chamber (194) is axially adjacent to the rear head (136).

2. The hydraulic hammer (102) according to claim 1, wherein the diaphragm (190) is disposed substantially perpendicular to the hammer axis (148).

3. The hydraulic hammer (102) according to claim 2, wherein the rear head (136) has an internal damping fluid reservoir (216) disposed therein, the internal damping fluid reservoir (216) being axially located between the sealing support (160) and the axial rear end (156) of the rear head (136).

4. The hydraulic hammer (102) according to claim 3, wherein the internal damping fluid reservoir (216) is in fluid communication with the damping sub-chamber (194).

5. The hydraulic hammer (102) according to claim 4, wherein the internal damping fluid reservoir (216) and the damping sub-chamber (194) are in fluid communication with a damping fluid port (210) located outside the rear head (136).

6. The hydraulic hammer (102) according to claim 5, wherein the sealing support (160) is adapted to move axially within the cylinder bore (140) to displace relative to the internal damping fluid reservoir (216).

7. The hydraulic hammer (102) according to claim 6, wherein the sealing support (160) has a cap-shaped shape including a cylindrical support wall (162) and an axial support end face (164).

8. The hydraulic hammer (102) according to claim 1, wherein the hydraulic sub-chamber (196) is in fluid communication with a plurality of hydraulic fluid channels (170), and the plurality of hydraulic fluid channels (170) are in fluid communication with the cylinder bore (140).

9. The hydraulic hammer (102) according to claim 1, wherein the diaphragm (190) is configured as a rolling diaphragm (200).

10. The hydraulic hammer (102) according to claim 1, wherein the damping sub-chamber (194) and the hydraulic sub-chamber (196) have opposing truncated conical shapes.

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