VISCOSE DAMPER ARRANGEMENT WITH LOCKING FUNCTION

Abstract

Hydraulic damper assembly (100), comprising: a housing (104) with an interior (108), a first end (112) and a second opposite end (116), wherein the first end is configured for attachment to a fixed support and the second end is configured for attachment to a structure under load; a hollow cylindrical shock tube (148) arranged axially inside the housing interior (108); a piston assembly (128) which is axially movable within the interior of the hollow cylinder (148), wherein the piston assembly (128) comprises a piston (136) and a piston rod (132) extending from the second end of the housing (104), wherein the piston (136) defines variably dimensioned adjacent chambers (210, 218) within the hollow shock tube (148), each chamber (210, 218) being filled with a hydraulic fluid; a first end arrangement (156) sealed at the first end (112) of the housing (104) and a second end arrangement sealed at the second end (116) of the housing (104), wherein the second end arrangement comprises a sealed opening through which the piston arrangement (128) is slidably moved; a fluid circuit comprising fluid passages defined in the first end arrangement (156) and the second end arrangement, and a tubular element arranged axially between an outer surface of the hollow cylindrical shock tube (148) and an inner surface of the housing (104), wherein the passage (184) in the end arrangement (156) is further connected to a lateral passage (176) connected to a passage (170) extending into the chamber (218), wherein the fluid circuit connects each of the adjacent chambers (210, 218) to each other and is configured to move the fluid between the chambers (210, 218) in accordance with the movement of the piston arrangement (128) under load; an accumulator (150) arranged in an accumulator surrounding at least a section of the outer surface of the cylindrical tube within a defined space, wherein the end arrangement (156) further comprises an axial passage (190) formed therein, which is fluidically connected to a lateral passage (194) which is connected to the space holding the accumulator (150); and a locking arrangement arranged within the end arrangement (156), wherein the locking arrangement comprises a locking pin (180) and a locking pin (197), the locking pin (180) being arranged in the lateral passage (176) and having a tapered section (182) dimensioned such that the axial passage (170) can be completely closed by the locking pin (180) when the locking pin (180) is adjusted accordingly by a user, and the locking pin (197) being arranged in the lateral passage (194) and having a tapered section (201) dimensioned such that the axial passage (190) can be closed by the locking pin when the locking pin (197) is adjusted accordingly by a user.

Description

CROSS-REFERENCE TO RELATED REGISTRATIONS

[0001] This application claims priority over USSN 62 / 252,834 (published under US 10 544 850 B2) filed on November 9, 2015, under relevant sections of 35 USC §119, the entirety of which is hereby incorporated by reference. TECHNICAL AREA

[0002] The subject matter of this patent application relates to the field of load damping arrangements and in particular to a hydraulic damper arrangement which includes an adjustable locking function which can be successfully used for both linear and non-linear loads. STATE OF THE ART

[0003] US 2015 / 0158364A1 discloses shock absorbers, in particular hydraulic shock absorbers, whose damping curve can be adjusted either in the compression stage, in the rebound stage or in both stages.

[0004] EP 0202941 A2 generally relates to devices for damping or cushioning the movement between two objects moving relative to each other and relates in particular to a new and improved dashpot-type damper. BACKGROUND

[0005] Load damping arrangements, such as those manufactured by the applicant, are generally known in the field. In such damping arrangements, there are situations or requirements where the damper arrangement should be deliberately deactivated or "locked" for the sake of maintaining a structural system, for example, a balanced mass damping system.

[0006] For background purposes, a known version of a hydraulic damper arrangement 10 with a locking function is shown in Fig. 1 and Fig. Figure 2 shows that this damper assembly 10 is defined by a cylindrical housing 14 that encloses a hollow cylindrical tube 16 arranged axially inside the housing 14. The damper assembly 10 includes a movable end 18, which is attached to a load (not shown), and an opposite end 22, which is fixedly attached to a support (not shown). A clevis 24, 25 is provided at both the movable and the fixed ends 18, 22 of the assembly 10 to provide a mounting option for both the load and the support by means of articulated bearings 26 provided in each clevis 24, 25.A piston assembly 28 is movably mounted within the boundaries of the cylindrical housing 14 at the movable end 18 of the arrangement 10, the piston assembly 28 comprising a piston rod 30 and a piston 34, which is moved through a defined hydraulic chamber 38 provided within the housing 14 and, in particular, the interior of the hollow cylindrical tube 16. The ends of the hollow cylindrical tube 16 are attached to a cylinder end assembly 44, which is mounted at the fixed end 22 of the damper assembly 10, and a bearing bracket 52 is rigidly attached to the opposite end of the housing 14 at the movable end 18 of the arrangement 10.

[0007] When movement is caused by a transmitted load, a damping force is generated when the piston assembly 28 within the housing 14 is either extended (under tension) or retracted (under pressure), the piston rod being dimensioned to move through a closed central opening formed in the bearing holder 52. When pressurized, hydraulic fluid is moved through a series of axial openings 48 formed in the cylinder end assembly 44. This fluid is directed to an intermediate space 50 formed between the outer surface of the hollow cylindrical tube 16 and the inner surface of the housing 14. An accumulator 53 made of foam or another suitable material is provided in the defined intermediate space or chamber 50, the accumulator 53 comprising an axial section of the assembly 10.The accumulator 53 is wound around the shock tube section of the arrangement, with a distance (not shown) arranged between the wound ends.

[0008] Under tension and with the piston rod 30 extended, the check valves in the piston base 34 are closed, and hydraulic fluid can only be directed to the accumulator chamber 50 through an axial opening 24 formed in the body of the bearing holder 52. As a result, high dynamic pressure is generated in the fluid chamber between the piston 34 and the bearing holder 52.

[0009] On the other hand, due to the movement of the piston 34, hydraulic fluid is drawn from the accumulator chamber 50 through check valves into the cylinder end assembly 44 between the piston 34 and the cylinder end assembly 44. As a result, a slight dynamic pressure is generated in the fluid chamber between the piston 34 and the cylinder end assembly 44. While under tension, the opening 24 is located on the downstream side of the valve. During normal operation, the adjusting valve is fully open, and therefore the opening ensures the desired damping characteristic. When the adjusting valve is closed, the hydraulic fluid is blocked at the valve, and since it cannot flow elsewhere, the damper essentially becomes a rigid strut, creating a blockage under tension.

[0010] Under pressure and with the piston rod 30 compressed, the check valves in the piston base 34 are open, and the check valves in the cylinder end assembly 44 are closed. As a result, hydraulic fluid between the piston 34 and the cylinder end assembly 44 can only flow through the check valves in the piston base to the fluid chamber between the piston 34 and the bearing bracket 52, and then through an axial opening 24 formed in the body of the bearing bracket 52. Consequently, high dynamic pressure is generated in both fluid chambers between the bearing bracket 52 and the piston 34. Due to the differential area of ​​the piston, a compressive damping force is achieved. When the adjusting valve is fully closed, the retained hydraulic fluid is blocked by the closed valve, and since it cannot flow elsewhere, the damper becomes a rigid valve, creating a pressure lock.

[0011] According to this version, a locking sub-arrangement 90 is provided at the movable end 18 of the arrangement 10. This locking sub-arrangement 90 is defined in particular by a spring-loaded plunger 94 attached to the bearing bracket 52, which can be moved into and out of engagement with the defined axial opening (not shown). Because the locking sub-arrangement 90 is provided at the movable end 18 of the damper arrangement 10, it is difficult and risky to make modifications. Furthermore, the operation of the arrangement 10 is limited by the fact that damping is only implemented for dynamic (V-squared) loads and not for linearly transmitted loads.

[0012] Accordingly, there is a general need in this field to provide a damper assembly with a more versatile locking function to allow improved access when this function is desired. Furthermore, there is a desire to provide a damper with a locking function that can be successfully used under tension and compression under various load conditions. SHORT DESCRIPTION

[0013] Therefore, and according to one aspect, a hydraulic arrangement is provided comprising a housing with a piston assembly movably mounted at a first end of the arrangement, the arrangement having a second, opposite end configured for mounting on a fixed support. The piston assembly moves within a hollow cylindrical tube axially located within the housing, the piston assembly defining adjacent chambers, each filled with hydraulic fluid. Upon axial movement of the piston, the hydraulic fluid is moved between the hydraulic chambers via a fluid circuit defined around the hollow cylindrical tube. A locking arrangement defined in the fixed end includes at least one pin element that is controllably movable into a fluid passage of the fluid circuit to regulate the flow of the hydraulic fluid.

[0014] According to another aspect, a hydraulic damper assembly is provided, comprising a housing with an interior, a first end, and a second, opposite end. The first end is configured for mounting to a fixed support, and the second end is configured for mounting to a structure under load. A hollow cylindrical tube is arranged axially within the housing interior, and a piston assembly is axially movable within the interior of the hollow cylinder. The piston assembly includes a piston crown and a piston rod extending from the second end of the housing. According to this claim, the piston defines variably dimensioned, adjacent chambers within the hollow cylindrical tube, each chamber being filled with a hydraulic fluid.A first end assembly is sealed to the first end of the housing, and a second end assembly is sealed to the second end of the housing. The second end assembly includes a sealed opening through which the piston assembly is slidably moved under load. A hydraulic or fluid circuit includes fluid passages formed in both the first and second end assemblies, as well as a tubular element arranged axially between the outer surface of the hollow cylindrical tube and an inner surface of the housing. The fluid circuit connects all adjacent chambers and allows hydraulic fluid to move between them based on the movement of the piston assembly under load.The damper further includes a locking arrangement located within the first end arrangement, which comprises at least one pin that is controllably movable in order to selectively close a fluid passage of the fluid circuit.

[0015] One advantage provided by the damper arrangement described herein is that the design allows its use in a range of load conditions and that locking settings can be easily activated by a user.

[0016] Another advantage achieved is that the locking function can be easily adjusted and further used to set the damping constant of the arrangement or to fine-tune it in other ways.

[0017] A further advantage provided by the damper arrangement described herein is that the design allows its use in a range of damping configurations (i.e., linear and non-linear damping) and that locking settings can be easily activated by the user.

[0018] These and other features and advantages are clearly evident from the detailed description below, which should be read in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a perspective view of a hydraulic damper assembly manufactured according to the state of the art; Fig. Figure 2 is a side elevation view of the damper arrangement according to the prior art of Fig. 1, shown in section; Fig. Figure 3 is a perspective view of a hydraulic damper arrangement according to an exemplary embodiment; Fig. 4(a) is a side elevation view of the hydraulic damper assembly of Fig. 3, shown in section; Fig. 4(b) is an enlarged sectional view of an end section of the hydraulic damper assembly of Fig. 3; Fig. 4(c) is an enlarged sectional view of an opposite end section of the hydraulic damper assembly of Fig. 3 - 4(b); Fig. 5(a) is a side elevation view of the hydraulic damper assembly of Fig. 4(a), wherein this view is rotated by 90 degrees about the primary axis of the damper assembly; Fig. 5(b) is an enlarged sectional view of a section of the hydraulic damper assembly of Fig. 5(a); Fig. 6(a) is another side elevation view of the hydraulic damper arrangement of Fig. 3, wherein the piston assembly is moved into a compression operating mode; Fig. Figure 6(b) is an enlarged view of an end section of the hydraulic damper assembly of Fig. 6(a); Fig. Figure 7 is a side elevation view of the hydraulic damper assembly, shown in section and at approximately 45 degrees relative to that of Fig. 5(A) turned, and Fig. Figure 8 is a partial end view of the hydraulic damper assembly of Fig. 3 - 7. DETAILED DESCRIPTION

[0019] The following relates to an exemplary hydraulic damper (also referred to throughout this document as the "damper assembly") that can be configured for use under both linear and non-linear load conditions. As discussed herein, the damper assembly includes at least one locking feature that allows for easier adaptation than previous versions and is configured to provide suitable damping under tension as well as compression operating modes for a tunable mass or other structure. It is understood that the specific application for the assembly and related method described herein may be appropriately varied. Furthermore, certain terms are used throughout to provide a suitable frame of reference with respect to the accompanying drawings.These terms, which include “inner”, “outer”, “distal”, “proximal”, “interior”, “outer surface” and the like, are not intended to limit the overall scope of the invention, including the claims, and should not be interpreted as such unless expressly stated.

[0020] As used herein, the terms "about" or "approximately" for numerical values ​​or ranges indicate a suitable dimensional tolerance that will allow the part or assembly of components to function for its intended purpose as described herein. In particular, "about" or "approximately" may refer to a range of values ​​of at least ±20% of the stated value. Likewise, the terms "above" and "below" are not restrictive in the course of this discussion with respect to absolute alignment.

[0021] It should also be noted that the accompanying drawings are not necessarily to scale and that therefore no restrictive interpretation should be made regarding the dimensions shown herein.

[0022] As used herein, the singular forms “ein”, “eine”, “einer” and “der”, “die”, “das” are also intended to include the corresponding plural forms, unless the context clearly indicates otherwise.

[0023] The terms “include”, “includes”, “comprehensive”, as used herein, are intended to mean that additional elements may be included and that a set of elements having any of these terms used in connection with it denotes a minimum number which can be readily extended.

[0024] The terms “include”, “includes” and “enclose”, as used herein, are intended to cover the same scope as the terms “comprise”, “comprises” and “comprehensive” listed above.

[0025] Referring to the characters and especially to Fig. Figure 3 shows a damper 100 (also referred to as a "damper assembly" throughout the document) manufactured according to one embodiment. The damper 100 is defined by a cylindrical or other suitably shaped housing 104 with an interior 108. Fig. 4(a), which, as described herein, is dimensioned and configured to accommodate a plurality of components. The arrangement 100 is defined by a first end 112 configured for attachment to a fixed support (not shown) and an opposing second end 116 supporting a piston assembly 128 configured for movable attachment to a mass (not shown). Both the first and second ends 112, 116 further include a clevis 120, 122 configured to allow the damper 100 to be attached to the fixed support and the mass or other structure under load (all not shown). Each clevis 120, 122 according to this embodiment may include a pivot bearing 124 accommodated within a transverse central opening 125 of the clevis 120, 122.

[0026] Referring to Fig. 3 and Fig. 4(a) The piston assembly 128 includes a piston rod 132 and a piston 136 configured for axial movement within the interior 108 of the housing 104 of the damper 100. The piston rod 132 extends from the second end 116 of the damper 100 and includes a proximal end 138, which is fixedly attached to the clevis 122, and a distal end 140, which receives the piston 136. The piston rod 132 passes through a sealed central opening 145 formed by a bearing support 144, the latter being fixedly attached to the second end 116 of the housing 104. The piston assembly 128 is dimensioned to move within a defined chamber filled with hydraulic fluid inside the housing 104, the chamber being defined by a coaxially mounted hollow shock tube 148 extending through the entire axial extent of the housing 104.

[0027] An accumulator 150 made of foam or another suitable material is further arranged around the majority of the outer surface of the shock tube 148, with the exception of a circumferential section thereof. The accumulator 150 is attached to the outer surface of the shock tube 148 by means of suitable adhesives or other fastening means such as cable ties and is arranged between the inner surface of the cylindrical housing 104 and the outer surface of the shock tube 148. The thickness of the accumulator 150 allows for a small radial distance between them. The circumferential section of the shock tube 148 that is not covered by the accumulator 150 defines a channel 151 that extends over the axial extent of the damper 100, which allows for the placement of a section of a hydraulic fluid ring line and, in particular, a tubular element 153. Both the channel 151 and the tubular element 153 are described with reference to Fig. 8 better to see. The channel 151 is dimensioned to accommodate the tubular element 153, which also extends axially over the housing 104, and is configured to move the hydraulic fluid.

[0028] With reference to Fig. 4(a) and Fig. 4(c) The cylinder end assembly 156 within the first end 112 of the damper housing 104 is a one-piece body made of a structural material, enclosing a shoulder 160 formed on an opposite inner end 164, which engages an end of the shock tube 148 and an edge of the accumulator 150. The clevis head 120 is either formed integrally with this assembly 156 or can be a separate component firmly attached to an outwardly facing side of it by means of fasteners or other suitable means.

[0029] With reference to Fig. 4(a) and Fig. 4(b) The bearing bracket 144, attached to the second end 116 of the damper housing 104, also includes a shoulder 146 formed on an opposite inner end 149 to engage an opposite end of the shock tube 148 and the edge of the accumulator 150 in a similar manner. At least one sealing element 152, such as an elastomer ring, is arranged within an annular groove or notch formed on the outer surface of the body of the bearing bracket 144. When inserted, the extension section of the sealing element 152 is brought into compressive contact with the inner surface of the housing 104. The shock tube 148 can be attached to either the bearing bracket 144 or the cylinder end assembly 156. Fig. 4(c), are fastened in place by means of set screws (not shown) or other suitable means to secure the components in place.

[0030] As in Fig. As shown in Figure 4(A), a section of the interior of the housing 104 within the shock tube 148, through which the piston assembly 128 moves axially (between the piston 136 and the bearing support 144), is referred to herein as the "tension chamber" 210, while the remaining interior 108 of the housing 104 formed within the shock tube 148 is referred to throughout this document as the "compression chamber" 218. The axial length and circumference of the tension chamber 210 and the compression chamber 218 are variable based on the movement of the piston assembly 128, as described herein, the introduced nomenclature being helpful for the purpose of describing the operation of the damper 100.

[0031] Referring to the sectional views of Fig. 4(a), Fig. 4(b) and Fig. 4(c) According to this embodiment, both the bearing support 144 and the cylinder end assembly 156 include a plurality of formed passages that allow the hydraulic fluid to flow into and out of the tension chamber 210 and the compression chamber 218. This series of formed passages, as described herein, is connected together with the tubular element 153 to define a continuous hydraulic loop or circuit.

[0032] Referring first to Fig. 4(b) The inwardly facing side 149 of the bearing holder 144 includes an axial passage 147, which extends partially into the body of the bearing holder 144. This axial passage 147, as described herein, engages an end 155 of the tubular fluid element 153, the end 155 being configured with a laterally extending section that is connected to the end of the axial passage 147. As shown, the axial passage 147 is fluidically connected to the stress chamber 210.

[0033] Referring to Fig. 4(c) An axial passage 170 extends inward from the inwardly facing end 164 of the cylindrical end assembly 156 to the distal end of a lateral passage 176, which is configured and dimensioned to receive an adjustable locking pin 180, at the opposite fixed end 112 of the arrangement 100. Another similarly configured axial passage 184 extends from a central section of the lateral passage 176. This latter axial passage 184 extends toward the inwardly facing end 164 and is connected to the opposite end 185 of the tubular element 153, which is located between the outer surface of the shock tube 148 and the inner surface of the housing 104 within the channel 151. This end 185 of the tubular element 153 extends laterally into the cylindrical end assembly 156 and directly into the axial passage 184 at a central section thereof.Although the axial passage 184, as shown, extends completely to the inwardly facing end 164 of the cylinder end assembly 156, this configuration is based on the possibility of adequately shaping the passage 184. To prevent fluid from flowing uncontrolled into or out of the compression chamber 218 directly into the end of the axial passage, the end of the axial passage 184 is fitted with a closure 187 or is otherwise sealed. Consequently, and during operation, only the axial passage 170 is fluidically connected to the compression chamber 218. Flow of hydraulic fluid into and out of the compression chamber 218 via the axial passage 184 is prevented.

[0034] Referring further to Fig. 4(C) In this embodiment, the upper section of the adjustable locking pin 180, above the axial fluid passage 184, includes a group of threads (not shown) that engage with a corresponding group of threads (not shown) provided in the interior of an upper axial section of the lateral passage 176. A hexagonal head 181 is provided at the upper (proximal) end of the locking pin 180 to allow adjustment. The opposite distal end of the pin 180 includes a tapered section 182 dimensioned to set and close the axial passage 170 when adjusted appropriately by the user, as described in more detail below.Meanwhile, the outer diameter of the adjustable locking pin 180 along the lateral passage 176 is slightly smaller than the outer diameter of the locking pin 180, thus directing hydraulic fluid around the locking pin 180 when the damper assembly 100 is in operation, as described in more detail below. Sealing elements, such as O-rings or other elastomeric sealing elements, are provided between the threaded section at the proximal end of the locking pin 180 and the central axial passage 184 to prevent fluid leakage.

[0035] As mentioned, the above structure defines a continuous hydraulic loop or circuit which is formed and fluidically connected to the tension chamber 210 and the compression chamber 218 and is moved in the fluid according to the movement of the piston arrangement 128, Fig. 4(a).

[0036] Before discussing the operation of the damper 100 and referring to Fig. 5(a) and Fig. 5(b) Sectional views are additionally provided, rotated by 90 degrees about the primary axis 101 of the damper 100, in order to better illustrate, in particular, additional features of the cylinder end assembly 156. As shown in particular in Fig. As shown in Figure 5(B), another axial passage 190 extends from the inwardly facing end 164 of the cylinder end assembly 156 toward the clevis head 120 and terminates at the distal end of the laterally extending passage 194, which contains an adjustable locking pin 197. A section of the laterally extending passage 194 is configured to allow movement of the hydraulic fluid, including around the outer surface of an axial section of the locking pin 197 and extending to a formed central axial passage 198, which extends toward the inwardly facing side 164.

[0037] A lateral fluid passage 202 extends from the central axial passage 198 to the outer space enclosing the accumulator 150, which in turn surrounds and axially encloses the damper 100. According to this exemplary version, although the axial passage 198, as shown, extends to the inwardly facing end 164 of the cylinder end assembly 156, the end incorporates a closure 205. Consequently, hydraulic fluid is permitted to enter and exit the compression chamber 218 via the axial passage 190, but not via the axial passage 198.

[0038] Similar to the adjustable locking pin 180 described above, the adjustable locking pin 197 in this embodiment includes a group of threads adjacent to its proximal end, which engage in a corresponding group of threads similarly configured within the lateral passage 194. Furthermore, the locking pin 197 includes a hexagonal head 199 to allow adjustment of the thread, and the distal end of the locking pin 197 includes a tapered section 201 dimensioned such that the axial passage 170 is set and closed when appropriately adjusted by a user. To prevent leakage of hydraulic fluid, sealing elements, such as O-rings or other suitable elements, are provided between the central axial passage 198 and the threaded section at the proximal end of the locking pin 197.

[0039] In the assembled state, both the tension chamber 210 and the compression chamber 218, as well as the tubular channel 153 formed between the shock tube 148 and the housing 104, are filled with hydraulic fluid via a filling nozzle (not shown). The cylinder end assembly 156, the piston assembly 128, and the bearing holder 144 each contain corresponding seals that prevent fluid from leaking out of the damper 104, either statically or during operation.

[0040] Load conditions can occur that put the damper 100 either into a tension mode, in which the piston assembly 128 is moved towards the end 116, or into a compression mode, in which the piston assembly 128 is moved axially towards the fixed end 112 of the assembly 100. Referring first to Fig. Sections 4(a) - 4(c) describe the operation of the damper assembly 100 in a tension mode. As mentioned, the piston assembly 128, and in particular the piston rod 132, is caused to extend outwards and axially from the damper housing 104, while the piston rod 132 is moved through the sealed central opening 145 of the bearing holder 144. When this axial movement occurs, hydraulic fluid contained in the tension chamber 210 is displaced under force into the axial passage 147 defined within the bearing holder 144. This displaced hydraulic fluid is further guided, by the force generated by the piston assembly 128, through the tubular element 153, which is arranged between the shock tube 148 and the housing 104, and subsequently through the various passages 185, 184, 176, and 170 formed within the cylinder end assembly 156.The displaced hydraulic fluid is moved as an annular motion around the outer surface of the adjustable locking pin 180 in the passage 176, with the hydraulic fluid exiting the axial passage 170 into the compression chamber 218, the volume of which is increased as a result of the axial movement of the piston assembly 128 and the reduced volume of the adjacent tension chamber 210. The movement of the fluid generates a suitable damping force when the piston assembly 128 is retracted through the tension chamber 210.

[0041] The discussion now concerns the compression operating mode of the damper 100 described herein, wherein the piston assembly 128, including the piston rod 132, is moved through the sealed central opening 145 of the bearing bracket 144 towards the first or fixed end 112. In this embodiment, and due to the volume occupied by the piston rod 132, the hydraulic fluid in the compression chamber 218 has a larger effective area than the hydraulic fluid in the adjacent tension chamber 210. Consequently, the piston 136 is provided with a number of axial openings 220, Fig. 6(b), which extend through therein, each of the openings 220 (referred to herein as "equalizing openings") having check valves 224 configured to allow the flow of hydraulic fluid through them only when in compression operating mode. According to this embodiment, two (2) equally spaced openings 220 are provided, although this parameter can be suitably modified. This means that, in tension operating mode, differential pressure between the adjacent hydraulic chambers 210, 218 prevents hydraulic fluid from the compression chamber 218 from passing through the equalizing openings 220 into the tension chamber 210.

[0042] This refers to Fig. 6(a) and Fig. Refer to 6(b). Hydraulic fluid contained in the compression chamber 218 is displaced into the compression chamber 218 by means of the piston force acting on the hydraulic fluid. As a result, a portion of this hydraulic fluid is driven into the axial passage 170 formed in the cylinder end assembly 156 around the locking pin 180 contained therein and through each of the passages 184, 185, including the connected tubular element 153 of the defined hydraulic loop or circuit. The displaced hydraulic fluid exits the axial passage 147 to fill the compression chamber 210 when the piston assembly 128 is moved towards the cylinder end assembly 156.

[0043] With reference to Fig. 5(a) and Fig. 5(b) causes a further portion of the hydraulic fluid to pass through the axial passage 190 and the various fluid passages of the sealed cylinder end assembly 156; that is, through the lateral passage 194 and around the outer surface of the adjustable locking pin 197, the central axial passage 198, and the lateral passage 202 into the circumferential and axial space occupied by the accumulator 150. This portion of the hydraulic fluid must also be moved to accommodate the larger compression chamber 218 and the volume of the extended piston rod 132, which remains in the tension chamber 210.

[0044] Referring to Fig. 7 and Fig. 8 and according to this specific embodiment, at least one group of check valves 240 is additionally provided within another corresponding group of axial passages 238 formed in the body of the cylinder end assembly 156 to allow hydraulic fluid to be returned from the accumulator 150 to the compression chamber 218 when the voltage operating mode of the damper assembly 100 described herein is continued. As more clearly shown in Fig. As shown in Figure 8, a total of four (4) axial passages 238 with corresponding check valves 240 at 90-degree intervals are provided according to this embodiment. This parameter can be suitably changed, for example, depending on the diameter of the openings of the axial passages 238. The check valves 240 prevent hydraulic fluid from passing through any of the axial passages 238 during the compression operating mode.

[0045] With reference to Fig. 4(c), Fig. 5(b) and Fig.6(b) and to adjust the damper 100 described herein for locking, the adjustable locking pin 180 can be axially adjusted by engaging the hexagonal head 181, causing threaded movement of the pin 180 and allowing the extended distal end of the locking pin 180, and in particular the tapered section 182, to be fully advanced to completely block the axial passage 170. Similarly, the hexagonal head 199 of the adjustable locking pin 197 can also be engaged by means of a suitably sized tool (e.g., a wrench) to axially advance the pin 197 and the tapered distal section 201 to close the axial passage 190. This adjustment prevents hydraulic fluid from moving within the defined hydraulic fluid circuit in either of the operating modes (compression or tension).Preferably, both locking pins 180, 197 are set to provide this latter function.

[0046] Similar adjustments can be made to partially close the axial passages 170, 190 using the adjustable locking pins 180, 197, thereby setting or fine-tuning the damping constant of the damper arrangement 100 described herein in order to optimize the overall performance of the arrangement.

[0047] It will be clearly evident that numerous modifications and variations can be made within the scope of the inventive concepts described herein, including the following attached claims of this application.

Claims

[1] Hydraulic damper assembly (100) comprising: a housing (104) with an interior (108), a first end (112) and a second opposite end (116), wherein the first end is configured for attachment to a fixed support and the second end is configured for attachment to a structure under load; a hollow cylindrical shock tube (148) arranged axially inside the housing interior (108); a piston assembly (128) which is axially movable within the interior of the hollow cylinder (148), wherein the piston assembly (128) comprises a piston (136) and a piston rod (132) extending from the second end of the housing (104), wherein the piston (136) defines variably dimensioned adjacent chambers (210, 218) within the hollow shock tube (148), each chamber (210, 218) being filled with a hydraulic fluid; a first end arrangement (156) sealed at the first end (112) of the housing (104) and a second end arrangement sealed at the second end (116) of the housing (104), wherein the second end arrangement comprises a sealed opening through which the piston arrangement (128) is slidably moved; a fluid circuit comprising fluid passages defined in the first end arrangement (156) and the second end arrangement, and a tubular element arranged axially between an outer surface of the hollow cylindrical shock tube (148) and an inner surface of the housing (104), wherein the passage (184) in the end arrangement (156) is further connected to a lateral passage (176) connected to a passage (170) extending into the chamber (218), wherein the fluid circuit connects each of the adjacent chambers (210, 218) to each other and is configured to move the fluid between the chambers (210, 218) in accordance with the movement of the piston arrangement (128) under load; an accumulator (150) arranged in an accumulator surrounding at least a section of the outer surface of the cylindrical tube within a defined space, wherein the end arrangement (156) further comprises an axial passage (190) formed therein, which is fluidically connected to a lateral passage (194) which is connected to the space holding the accumulator (150); and a locking arrangement arranged within the end arrangement (156), wherein the locking arrangement comprises a locking pin (180) and a locking pin (197), the locking pin (180) being arranged in the lateral passage (176) and having a tapered section (182) dimensioned such that the axial passage (170) can be completely closed by the locking pin (180) when the locking pin (180) is adjusted accordingly by a user, and the locking pin (197) being arranged in the lateral passage (194) and having a tapered section (201) dimensioned such that the axial passage (190) can be closed by the locking pin when the locking pin (197) is adjusted accordingly by a user. [2] Hydraulic damper arrangement according to claim 1, wherein each of the locking pins (180, 197) has a threaded section configured to engage corresponding threads in a passage supporting each locking pin (180, 197). [3] Hydraulic damper arrangement according to claim 2, wherein each of the locking pins (180, 197) is controllably movable in a passage (176, 194) defined in the end arrangement (156), wherein a section of each lateral passage (176, 194) is part of the fluid circuit. [4] Hydraulic damper arrangement according to claim 3, wherein the fluid is configured to flow over the outer surface of each locking pin (180, 197) when the tapered section (182, 201) is not inserted. [5] Hydraulic damper arrangement according to claim 1, wherein the piston (136) includes a plurality of axial openings passing through it, each axial opening having a check valve configured to limit the flow between the adjacent chambers. [6] Hydraulic damper arrangement according to claim 1, wherein the end arrangement (156) has a group of axial passages (238) that allow fluid to flow from the spaced opening into the hydraulic chamber (218) when the load is reduced, wherein each of the group of axial passages (238) has a check valve (240) to allow movement of the fluid in only one direction. [7] Method for manufacturing a hydraulic damper assembly, the method comprising: Provision of a housing (104) with an interior (108), a first end (112) and a second opposite end (116), wherein the first end is configured for attachment to a fixed support and the second end is configured for attachment to a structure under load; Arrangement of a hollow cylindrical shock tube (148) inside the interior (108); Arrangement of an axially movable piston assembly (128) within the interior of the hollow cylinder (148), wherein the piston assembly (128) comprises a piston (136) and a piston rod (132) extending from the second end of the housing, wherein the piston (136) defines variably dimensioned adjacent chambers (210, 218) within the hollow shock tube (148), each chamber (210, 218) being filled with a hydraulic fluid; Provision of an end assembly (156) sealed at the first end (112) of the housing (104) and a second end assembly sealed at the second end (116) of the housing (104), wherein the second end assembly has a sealed opening through which the piston assembly (128) is slidably moved; Provision of a fluid circuit comprising fluid passages defined in the first end arrangement (156) and the second end arrangement, and a tubular element arranged axially between an outer surface of the hollow cylindrical shock tube (148) and an inner surface of the housing (104), wherein the passage (184) in the end arrangement (156) is further connected to a lateral passage (176) connected to a passage (170) extending into the chamber (218), wherein the fluid circuit connects each of the adjacent chambers (210, 218) to each other and is configured to move the fluid between the chambers (210, 218) in accordance with the movement of the piston arrangement (128) under load; Provision of an accumulator (150) arranged in an accumulator (150) within a defined space around at least one section of the outer surface of the cylindrical tube, wherein the end arrangement (156) further comprises an axial passage (190) extending to the adjacent chamber (218), which is fluidically connected to the accumulator (150) by a lateral passage (194), wherein the axial and lateral passages are separated from each other by the tubular element (153) and the accumulator (150); and Provision of a locking arrangement arranged within the end arrangement (156), wherein the locking arrangement comprises a locking pin (180) and a locking pin (197), the locking pin (180) being arranged in the lateral passage (176) and having a tapered section (182) dimensioned such that the axial passage (170) can be completely closed by the locking pin (180) when the locking pin (180) is adjusted accordingly by a user, and the locking pin (197) being arranged in the lateral passage (194) and having a tapered section (201) dimensioned such that the axial passage (190) can be closed when the locking pin (197) is adjusted accordingly by a user. [8] The method according to claim 7 further comprising: Providing the end arrangement (156) with a group of axial passages (238) which allow fluid to flow from the spaced opening into the hydraulic chamber (218) when the load is removed, each of the axial passages having a check valve (240) to allow movement of the fluid in only one direction. [9] Method according to claim 7, further comprising providing each of the locking pins (180, 197) with a threaded section configured to engage in corresponding threads in the lateral passage (176, 194) which each locking pin (180, 197) carries. [10] Method according to claim 9, wherein hydraulic fluid flows around the outside of each locking pin (180, 197) when the tapered section (182, 201) does not completely close the axial passage (170, 190). [11] Method according to claim 7, further comprising: Configuring the piston (136) with a plurality of axial openings extending through the piston (136), and further configuring the openings with a check valve (240) that allows the flow of hydraulic fluid in only one direction.

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