Patent Application
20160153150
This application claims priority of Italian Patent Application Number MI2014A002043 filed on 27 Nov. 2014, the entirety of which is incorporated by reference.
The present invention refers to a tamping machine for railway ballasts, a railway car and an use of the same tamping machine for making and/or regenerating railway ballasts. The present invention finds its application in the railway field and, particularly, in the technical field of machines destined to construct, service and dismantle railway lines.
Towed or self-propelled cars are used for making and/or regenerating railway ballasts, they are provided with groups of tamping machines arranged inside and outside each rail according to arrangements known as simple and double head (tamping machines using more than two heads, for example 4 or also 16 heads are known). Each tamping machine is generally provided with two pairs of vibrating hammers which are sunk into the ballast from one side and the other of each sleeper in order to mix and fluidify the rocks and tamp by it the sleeper itself.
Known tamping machines are provided of purely mechanical vibrating systems using eccentric masses or mechanisms for causing the hammers to vibrate and sink into the ballast. However, these systems exhibit different drawbacks and limitations due to the (mechanical) nature of the same. A drawback of these tamping machines is due to the vibrating system (eccentric masses/mechanisms) causing high stresses to the mechanical members forming the system itself; therefore, in order to sustain this vibration, the system must be suitably sized and provided with a strong structure, such characteristic generally makes the system complex and expensive to be manufactured. Therefore, these characteristics dictate the limits in terms of vibration frequency which—for preventing excessive stresses damaging the members of the system itself—must fall between determined low limits: the low vibration frequency of the hammers negatively affects also the capability/rapidity of tamping ballasts.
Moreover, it is noted that the above described known machines, whose vibration is simultaneously transmitted to all the hammers pairs of each “head” (the term head means a group of elements operating on each sleeper). This instance is a substantial inconvenience because it causes to build railway cars provided with two different types of vibrating systems respectively adapted to operate on a straight-track and on points; the first (straight-track systems) are of a double head type and are capable of simultaneously operate on two sleepers, while the second (railway points systems) have necessarily only one head and when they are used on straight tracks they do not exhibit an adequate performance: it is just this latter aspect which requires to prepare different cars for straight tracks and for points.
Therefore, new tamping machines, for example described in the patent application No. TO1988A067194, have being developed, which comprise at least one operative head provided with at least two pairs of tamping vibrating hammers each constrained to a support oscillatingly pivoted to a frame of the machine and subjected to the action of hydraulic actuators (hydraulic cylinders).
The actuator exhibits a first and second sections serially connected to each other; the first section is extendable and is adapted to displace the tamping hammer from a substantially vertical working position to a substantially horizontal reversed exclusion position. The second section, in line with the first section, is supplied by distributing means having an alternate cyclical operation and it is adapted to subject the first actuator section and the associated tamping hammer to a corresponding alternated cyclical vibration.
The machine described in the above mentioned patent application, further comprises hydraulic control means configured for controlling the supply of the first section of the actuators in order to enable to selectively displace, by a command of each hammer, from the working position to the exclusion one, and vice versa. Moreover, there are further hydraulic control means configured for managing the supply of the second section of the actuators also based on the position (working or exclusion position) of the tamping hammer.
The solution described in the patent application No. TO1988A067194 is an improvement with respect to the known art described beforehand because it exhibits a substantially simplified structure and is more stable enabling the tamping machine to work at high frequencies (also variable in a wide range of values selectable with respect to the state of the ballast to be regenerated) sharply greater than the one imposed by the known mechanical systems; in addition it is to be noted that the substitution of mechanisms and eccentric masses with hydraulic actuators has substantially reduced the generation of undesired vibrations and therefore of structural stresses. The simplified structure is also positively characterized from the point of view of the size and weights, certainly smaller than the ones of the previous mechanical systems, enabling to implement more compact railway cars having constrained weight and size.
In addition, it is noted that the use of hydraulic actuators makes the tamping machine more flexible from the point of view of its use: the movement of the actuators excluding/operating only some hammers enables to provide only one type of car adapted to execute both the straight-track work and the points work with clear advantages in terms of running and maintenance costs; this latter characteristic enables to further reduce the work times and avoid to substitute the straight-track cars with the points cars, and vice versa.
However, even though the machine described in the above mentioned patent application is an improvement with respect to the mechanical systems, however these hydraulic machines are not devoid of drawbacks. De facto, a first drawback is related to the size of the actuators responsible for actuating the hammers: the structures of the in-series sections (first and second sections) determine a considerable axial size of the actuators. De facto, the length of each single actuator is obtained by summing the axial size of the two sections composing it; the fact of providing a so bulky actuator for moving each hammer surely makes the machine structure complex and difficult to be designed. Due to this drawback (substantial length) the actuators are usually horizontally placed on the machine, which in turn substantially affects the size of each head; this prevents to manufacture heads having more than two pairs of hammers.
It is also known from the patent application No. TO99A000425 hydraulic tamping machines substantially of the above described type and particularly comprising at least one working head provided with at least two pairs of vibrating tamping hammers each constrained to a support oscillatingly pivoted to the machine frame and subjected to the action of a hydraulic actuator (hydraulic cylinder).
Also these machines substantially exhibit a first and second sections respectively dedicated to extend the hammer and vibrate this latter. In comparison with the first cited patent application, these second machines exhibit a first and second sections radially located one from the others.
More specifically, the first section comprises a cylinder, exhibiting a predetermined longitudinal extension and a predetermined diameter, configured for enabling to extend the hammer; the second section comprises a second cylinder defined around the first cylinder; the outer wall of the first cylinder defines also an inner lateral part of the second cylinder.
Hydraulic distributing means and associated control means are provided for this latter tamping machine. De facto, also this second machine comprises hydraulic control means configured for controlling the supply of the first section (first inner cylinder) of the actuators for enabling a selective displacement, commanded by each hammer, from the working position to the exclusion one, and viceversa. In addition, further hydraulic control means configured for managing the supply of the second section (second outer radial cylinder) of the actuators also based on the position (working or exclusion position) of the tamping hammer are provided.
Also the machines described in the second patent application No. TO99A000425, exhibit, with respect to the above discussed mechanical systems, the advantages of the hydraulic tamping machines described in the first patent application No. TO1988A067194. However, in support of the machines described in the second cited patent application, these are equipped with actuators having a reduced axial size: the arrangement of the second cylinder around the first cylinder makes the axial sizes to be substantially defined by the length of this latter. The reduced size of the actuators enables to simplify the design of the heads and possibly to provide more than two pairs of hammers on each head.
However, also the tamping machines described in the above mentioned patent application, are not devoid of limitations and drawbacks. De facto, the arrangement of the second cylinder around the first cylinder entails a great power loss for the vibrating system: in fact it is necessary a high hydraulic power for operating the outer cylinder.
The Applicant has noted that, although the above cited machines enable to tamp railway ballasts, the same however are not devoid of some drawbacks and are improvable under different aspects. De facto, to date hydraulic actuator tamping machines having a compact structure and at the same time having high performances, in other words machines of a simple structure and capable of exploiting small powers for tamping railway ballasts are not known yet.
A novel structurally simple tamping machine has been invented and is disclosed herein having a limited size, particularly adapted to enable to provide railway cars having a reduced weight and size with respect to the known solutions. The size reduction of the tamping machines, object of the present invention, is further adapted to enable to assemble many tamping hammers on each head of the machine so that, if required, this latter can simultaneously work on consecutive sleepers of a track.
The tamping machine having a flexible use and particularly configured for operating with high and variable frequencies in a wide range of values selectable in relation to the state of the ballast to be regenerated. Particularly, it is an object of the invention to provide a tamping machine whose structure avoids the generation of unacceptable structural stresses in favour of a substantial increase of the performance.
The tamping machine may include high efficiency whose actuators—and consequently the hammers—are capable of suitably regenerating the ballasts also by reduced powers.
The tamping machine may be configured for enabling to implement a unique type of car adapted to execute both the straight-track work and the points work with clear advantages in terms of operating and maintenance costs while substantially reducing the operative execution times (during the working step, it is avoided the substitution of the straight-track cars with the points cars, and vice versa). Further, it is an object of the present invention to provide a tamping machine enabling to easily and efficiently monitor the elements directly responsible of the ballast tamping and therefore to define a machine which can be effectively monitored and managed. Then, the tamping machine may be used to verify the soundness of a railway ballast and possibly signal a fail when the condition of this latter does not fall into desired parameters.
In a first aspect, the novel tamping machine (1), particularly for regenerating railway ballasts, comprises:
(i) at least one supporting frame (2) associable above at least one railway track, said railway track being of a type comprising at least two rails and a plurality of sleepers, (ii) at least one tamping hammer (3) extending along a prevalent development direction (D) between an operative portion (3a) and a thrusting portion (3b) and (iii) at least one hydraulic actuator (4).
The tamping hammer (3) may include an engaging portion (3c), interposed between the operative portion (3a) and thrusting portion (3b), pivoted to the frame (2) and adapted to enable a relative rotation of the hammer (3) with respect to the frame (2), the tamping hammer (3) being configured for being arranged at least in a working and an immediately following one along the track, the hammer (3), in the working condition, being configured for being arranged transversally to the tracks and sleepers, particularly vertically to the ballast, the operative portion (3a) facing said ballast (M), the tamping hammer (3) being further configured for being placed at least in one exclusion or receiving condition wherein the hammer (3) is substantially positioned horizontally or in a sloped position with respect to the working position suitable for defining a starting position for tamping the sleeper (T).
The at least one hydraulic actuator (4) may be engaged, on a side, with the thrusting portion (3b) of the tamping hammer (3) and, on the other side, with an abutment portion, the actuator (4) comprising at least one first and one second sections (5, 6), axially aligned and engaged with each other, one of said first and second sections (5, 6) being engaged with the abutment portion while the other being engaged with the thrusting portion (3b) of the tamping hammer (3), the first section (5) being extendable and configured for moving the hammer (3) at least between the working condition and the receiving or exclusion condition, and vice versa, the second section (6) being configured for being powered by distributing means having a cyclic alternating operation for enabling the tamping hammer (3) to vibrate,
the second section (6) comprising at least one jacket (7) extending between a first and second longitudinal ends (7a, 7b) and at least one piston (8) slidingly movable inside the jacket (7),
the jacket (7) is closed at the first and second longitudinal ends (7a, 7b), the piston (8) having an overall axial size defined by respective opposite thrusting faces of the piston (8) itself, which is entirely contained inside the jacket (7).
In a 2nd aspect according to the aspect 1, the jacket (7) of the second section (6) is engaged, particularly directly, with the frame (2) or the thrusting portion (3b) of the tamping hammer (3).
In a 3rd aspect according to anyone of the preceding aspects, the piston (8) is constrained to the tamping hammer (3) or frame (2) by interposition of the jacket (6), particularly the piston (8) is not directly engaged with the tamping hammer (3) and/or frame (2).
In a 4th aspect according to anyone of the preceding aspects, the jacket (7), at said first and second longitudinal ends (7a, 7b), comprises respective fluid-tight blind plugs, particularly devoid of passage openings, the piston (8) being entirely contained in the jacket (7) and entirely interposed between said blind plugs.
In a 5th aspect according to anyone of the preceding aspects, the piston (8) comprises only a head entirely contained in the jacket (7), particularly the piston (8) is devoid of a stem and does not exhibit parts projecting from the longitudinal ends of the jacket (7).
In a 6th aspect according to anyone of the preceding aspects, the first section (5) comprises at least one jacket (9) extending between a first and second longitudinal ends (9a, 9b) and at least one piston (10) slidingly movable inside said jacket (9), the jacket (9) of the first section (5) being engaged with the piston (8) of the second section (6) and being movable in relation to the jacket (7) of said second section (6).
In a 7th aspect according to the preceding aspect, the jackets (9, 7) of the respective first and second sections (5, 6) are axially aligned one with the other.
In an 8th aspect according to the aspect 6 or 7, the second longitudinal end (7b) of the jacket (7) of the second section (6) faces the second longitudinal end (9b) of the jacket (9) of the first section (5), the second ends (7b, 9b) of the jackets (7, 9) of the respective sections (5, 6) are relatively movable by approaching each other and moving away from each other.
In a 9th aspect according to anyone of the preceding aspects, the second section (6) comprises at least one connecting element (11) stably constrained to and transversally emerging from the piston (8) of the second section (6) itself, the jacket (7) of the second section (6) comprising at least one longitudinal through groove (12) arranged on a lateral wall of said jacket (7) between the first and second longitudinal ends (7a, 7b) of the same, the connecting element (11) of the piston (8) passing through and being slidingly axially engaged inside the longitudinal groove (12), and wherein the jacket (9) of the first section (5) comprises at least one anchoring portion (13) engaged with the connecting element (11) of the second section (6), the jacket (9) of the first section (5) being, with the piston (8) and connecting element (11) of the first section (6), relatively movable with respect to the jacket (7) of said second section (6).
In a 10th aspect according to the preceding aspect, the anchoring portion (13) extends as an axial continuation of the jacket (9) of the first section (5) outside the jacket (7) of the second section (6), particularly the anchoring portion (13) extending parallelly to a longitudinal development direction of the jacket (7) of the second section (6).
In an 11th aspect according to the aspect 9 or 10, the jacket (7) of the second section (6) comprises two longitudinal through grooves (12) made opposite one to the other on the lateral wall of said jacket (7), the connecting element (11) passing through and being axially slidingly engaged inside both the longitudinal grooves (12).
In a 12th aspect according to anyone of the aspects from 9 to 11, the anchoring portion (13) of the first section (5) is at least partially countershaped to the jacket (7) of the second section (6) in order to cover at least partially this latter.
In a 13th aspect according to the aspect 11 or 12, the anchoring portion (13) is stably engaged with the connecting element (11) which is slidingly engaged inside both the longitudinal grooves (12).
In a 14th aspect according to anyone of the aspects from 9 to 13, the anchoring portion (13) substantially comprises a tubular jacket at least partially covering the outside of the jacket (7) of the second section (6).
In a 15th aspect according to anyone of the aspects from 6 to 14, the piston (10) of the first section (5) comprises a head (14) slidingly movable inside the jacket (9) of the first section (5) itself and a stem (15) connected to the head (14) and emerging from the first longitudinal end (9a) of the jacket (9) of the first section (5), a portion of the stem (15) emerging from the jacket (9) of the first section (5) being stably constrained to the frame (2) or to a thrusting portion (3b) of a hammer (3).
In a 16th aspect according to anyone of the preceding aspects, the first section (5) comprises a double-acting cylinder.
In a 17th aspect according to anyone of the preceding aspects, the machine (1) comprises:
In an 18th aspect according to the preceding aspect, the first hydraulic control means (16) are configured for managing the supply of the respective supply chambers of the double-acting cylinder of the first section (5).
In a 19th aspect according to the aspect 17 or 18, the first hydraulic control means (16) comprise a group of switching solenoid valves, particularly having a blocking intermediate position.
In a 20th aspect according to anyone of the aspects from 17 to 19, the first hydraulic control means (16) comprise a switching box, particularly the switching box being of a type comprising at least one selected in the group of the following commands: manual, hydraulic, mechanical, electronic, air-actuated.
In a 21st aspect according to anyone of the preceding aspects, the second section (6) comprises a double-acting cylinder.
In a 22nd aspect according to anyone of the preceding aspects, the machine comprises:
In a 23rd aspect according to the preceding aspect, the second hydraulic control means (17) are configured for managing the supply of the respective supply chambers of the double-acting cylinder of the second section (6).
In a 24th aspect according to the aspect 22 or 23, the second hydraulic control means (17) comprise a group of switching solenoid valves, particularly of the two-way and two-position type.
In a 25th aspect according to anyone of the aspects from 22 to 24, the second hydraulic control means (17) comprise a commutator configured for selectively supplying the second section (6) of the type comprising at least one selected in the group of the following commands: manual, hydraulic, mechanical, electronic, air-actuated.
In a 26th aspect according to anyone of the aspects from 22 to 25, the first hydraulic control means (16) are configured for excluding the second hydraulic control means (17) and, therefore, the supply of the second section (6), in the receiving or exclusion condition of the tamping hammer (3).
In a 27th aspect according to the preceding aspect, the first and second sections (5, 6) of the actuator (4) are mechanically serially connected to each other.
In a 28th aspect according to anyone of the preceding aspects, the piston (8) of the second section (6) comprises a cylindrical body longitudinally delimited by the respective faces of the of the first and seconds ends (8a, 8b) of the same piston (8) which define the respective thrusting faces of this latter, the opposite thrusting faces of the piston (8) of the second section (6) exhibiting substantially the same thrusting surface.
In a 29th aspect according to anyone of the preceding aspects, the thrusting surface of both the longitudinal opposite faces of the piston (8) exhibits an area comprised between 5 and 200 centimeters squared (cm2), still more particularly between 20 and 100 cm2, still more particularly between 50 and 100 cm2.
In a 30th aspect according to anyone of the preceding aspects, the faces of the first and second ends (8a, 8b) of the piston (8) define, cooperatively with the inner lateral wall and respective ends (7a, 7b) of the jackets (7) of the second section (6), respective chambers (18, 19), each said respective chamber exhibits a varying volume according to the relative position taken by the piston (8) of the second section (6) in relation to the jacket (7) of this latter section.
In a 31st aspect according to the preceding aspect, the maximum volume definable by each of said chambers is substantially equal, particularly wherein the minimum volume definable by said chambers is substantially equal.
In a 32nd aspect according to the aspect 30 or 31, the maximum volume definable by each chamber is comprised between 20 and 100 cm3, particularly between 20 and 70, still more particularly comprised between 25 and 35 cm3.
In a 33rd aspect according to anyone of the aspects from 30 to 32, the minimum volume definable by each chamber is comprised between 0 and 20 cm3, particularly is comprised between 0 and 10 cm3.
In a 34th aspect according to anyone of the aspects from 6 to 33, the jacket (9) of the first section defines a predetermined transversal passage area greater than a transversal passage area of the jacket (7) of the second section (6).
In a 35th aspect according to anyone of the aspects from 6 to 34, the transversal passage area of the jacket (9) of the first section (5) is comprised between 30 and 250 cm2, particularly between 40 and 150 cm2, still more particularly between 40 and 80 cm2.
In a 36th aspect according to anyone of the preceding aspects, wherein the transversal passage area of the jacket (7) of the second section (6) is comprised between 5 and 200 cm2, still more particularly between 20 and 100 cm2, still more particularly between 50 and 100 cm2.
In a 37th aspect according to anyone of the preceding aspects, the maximum axial stroke of the piston (8) of the second section (6) is comprised between 5 and 30 mm, particularly between 10 and 25 mm.
In a 38th aspect according to anyone of the aspects from 6 to 37, the piston (10) of the first section (5) exhibits a maximum axial stroke greater than a maximum axial stroke of the piston (8) of the second section (6), particularly the ratio of the maximum axial stroke of the piston (10) of the first section (5) to the maximum axial stroke of the piston (8) of the second section (6) is greater than 2, particularly is comprised between 4 and 10.
In a 39th aspect according to anyone of the aspects from 6 to 38, the maximum axial stroke of the piston (10) of the first section (5) is comprised between 50 and 600 mm, particularly between 60 and 250 mm, still more particularly between 80 and 150 mm.
In a 40th aspect according to anyone of the preceding aspects, the machine (1) comprises at least two tamping hammers (3) facing each other and configured for being located at a predetermined distance measured along the development of the tracks, each tamping hammer (3) being configured for moving between the working position and the receiving or exclusion position, particularly around the respective engagement portion (3c).
In a 41st aspect according to the preceding aspect, the pair of tamping hammers (3) are connected and moved by a single actuator (4) exhibiting the first section (5) engaged with a thrusting portion (3b) of a hammer (3) and the second section (6) connected to the other tamping hammer (3).
In a 42nd aspect according to the preceding aspect, the only actuator (4) constrained to the pair of hammers (3) exhibits the jacket (7) of the second section (6) connected to a thrusting portion (3b) of a hammer (3) and the piston (10) of the first section (5) connected to the thrusting portion (3b) of the other hammer (3).
In a 43rd aspect according to anyone of the aspects from 1 to 40, the machine (1) comprises at least two hydraulic actuators (4) each dedicated to move a tamping hammer (3) of said pair of hammers (3), each of said actuators (4) being engaged, on one side, with the frame (2) and, on the other side, with the thrusting portion (3b) of a tamping hammer (3), one of said first and second sections (5, 6) of each actuator being engaged with the frame (2), while the other being engaged with the thrusting portion (3b) of the tamping hammer (3).
In a 44th aspect according to anyone of the aspects from 40 to 43, the tamping hammers (3) of a pair of hammers, in the working condition, are configured for being vertically located with respect to the ballast or are configured for being slightly sloped with respect to each other, the operative portions (3b) being located at a distance less than the distance between the respective thrusting portions (3a), particularly, the respective prevalent development directions (D) of the pair or tamping hammers (3) define between them an oblique angle substantially comprised between 5° and 50°, particularly 10° and 40°.
In a 45th aspect according to anyone of the aspects from 40 to 44, the tamping hammers (3) of the pair of hammers, in the receiving condition, are configured for being slightly sloped with respect to each other, the operative portions (3b) located at a distance greater than the distance between the respective thrusting portions (3a), particularly, the respective prevalent development directions (D) of the pair of tamping hammers (3) define between them an oblique angle substantially comprised between 5° and 50°, particularly between 10° and 40°.
In a 46th aspect according to anyone of the preceding aspects, the piston (8) of the second section (6) is devoid of seals, particularly there are no seals between the jacket (7) and the piston (8) of the second section (6).
In a 47th aspect according to anyone of the preceding aspects the machine (1) comprises at least one transducer (25) engaged on the actuator (4) and configured for generating a signal in relation at least to the movement and the force expressed by the same actuator (4).
In a 48th aspect according to anyone of the preceding aspects, the machine (1) comprises at least one control unit connected to the transducer (25) and configured for receiving the signal from this latter and monitoring at least one of the following conditions of the actuator:
In a 49th aspect according to the preceding aspect, the control unit is connected to the power supply of the actuator (4) and to the hydraulic control means, the control unit being configured for managing the operation of the power supply and of the hydraulic control means for managing and controlling the movement and operation of the first and second sections (5, 6) of the actuator (4).
In a 50th aspect, it is provided a railway car (100) comprising at least one tamping machine (1) according to anyone of the preceding aspects, said railway car (100) comprising at least one supporting structure (101) supporting at least four wheels configured for enabling the abutment and the engagement of the structure (101) on rails of a railway track, the frame (2) of the tamping machine (1) being movably constrained to the supporting structure (101), said frame (2) being configured for translating from a raised position wherein the frame (2) itself is located in proximity with the structure (101) to a lowered position wherein the frame (2) itself is more spaced from the structure (101) than at the retracted position, and vice versa, and wherein the hammers (3) of the tamping machine (1), placed in the working condition, are configured for being spaced from the railway ballast when the frame (2) is in the raised position, and wherein the hammers (3) of the tamping machine (1), placed in the working condition, are configured for sinking at least partially in the railway ballast when the frame (2) is in the lowered position.
In a 51st aspect according to the preceding aspect, the car (100) comprises at least one hydraulic cylinder (102) engaged, on one side, with the supporting structure (101) and, on the other side, with the frame (2), said hydraulic cylinder being configured for moving said frame at least between the raised position and the lowered position, and vice versa.
In a 52nd aspect, it is provided the use of a tamping machine (1) according to anyone of the aspects from 1 to 49 for regenerating railway ballasts and particularly for tamping the track, consisting in taking to a determined level the tracks with respect to the ballast.
Some embodiments and some aspects of the invention will be described in the following with reference to the attached drawings, given only in an indicative and therefore non limiting way, wherein:
A tamping machine 1 is disclosed for making and/or regenerating railway ballasts M; particularly, finds an application in the railway field and, particularly, in the technical field of machines destined to construct, service and dismantle railway lines.
To better comprehend the structure and operation of the tamping machine 1, it is useful to specify that it is configured for being generally mounted on railway cars 100 (
In detail and as it is visible from
The supporting frame 2, generally made of metal (the frame 2 must ensure a determined strength), can comprise a compact structure adapted to be placed above only one rail or can comprise an extended structure having a certain transversal development enabling the same frame 2 to substantially cover the transversal size of two rails (it exhibits a transversal size substantially equal to the width of the track).
The frame 2 substantially represents the support of the tamping machine 1, which is constrained to the structure 101 of the car 100, in a per se known way, by a suspension strut: the strut is configured for enabling the frame 2 to translate with respect to the supporting structure 101. Particularly, the suspension strut comprises one or more hydraulic cylinders 102 (
As it is for example visible in
Specifically, the hammer 3 comprises an engagement portion 3c constrained to a respective engagement portion of the frame 2 placed on a transversal edge of this latter: each hammer 3 is configured for being placed just above a rail. The engagement portion 3c of each hammer 3 is configured for defining with the frame 2 a hinge-type constrain: each hammer 3 can rotate in relation to the frame 2 around the engagement portion 3c. Particularly, each pair of hammers 3 is hinged on one side of the frame 2. As it is for example visible in
As it is specifically visible in
Each of said tamping hammers 3 is configured for being placed at least in a working condition wherein the hammer 3 is located beside a track between a sleeper T and another immediately following one along the track: the hammer 3, in the working condition, is configured for being placed transversally to the rails and sleepers, particularly normal to the ballast, an operative portion 3 facing said ballast (this working condition is for example illustrated in
It is useful to specify that tamping the railway ballasts M is performed by sinking in the ballasts the operative portion 3b of a pair of hammers 3 around a sleeper T. Therefore, in order to enable to sink a pair of hammers 3 into the ballast M, these, in the condition wherein both are placed in the lowered condition, must be located at an predetermined minimum distance greater than the width of a track sleeper T: this enables each pair of hammers 3 to straddle the sleepers T (
As it is for example visible in
Each actuator 4 comprises at least one first and one second sections 5, 6 axially aligned and engaged with each other. In the first arrangement of the machine 1 (one actuator for each hammer 3) one of said first and second sections 5, 6 is engaged with the frame 2, while the other is engaged with the thrusting portion 3b of the tamping hammer 3. In the second arrangement illustrated in
De facto, the first section 5 is an extendable portion of the actuator 4, configured for moving the hammer 3 at least between the working condition and the receiving or exclusion condition, and vice versa. The second section 6 is the vibrating portion of the actuator 4 adapted to enable the hammer 3 to vibrate. In other words, the first section 5 is configured for arranging each hammer in a working condition or in an exclusion one, while the second section 6 is configured for inducing a vibration to the thrusting portion 3b: the thrusting portion 3b vibration propagates from this latter to the operative portion 3a for enabling the hammer 3 to sink into the ballast M and tamping the sleepers T.
In detail, the first section 5 comprises an hydraulic double-acting cylinder exhibiting at least one jacket 9 extending between a first and second longitudinal ends 9a, 9b axially delimiting the cylinder. As it is visible in
The jacket 9 exhibits inside a lateral wall in which the piston 10 slides, having a circular cross-section. Advantageously but in a non limiting way, the jacket 9 exhibits as a whole a cylindrical shape.
From the dimensional point of view, the jacket 7 exhibits a general axial extension, defined substantially from the distance between the first and second longitudinal ends 9a, 9b comprised between 100 and 600 mm, particularly comprised between 200 and 250 mm. However, the inner sliding lateral wall of the jacket 9 exhibits an axial extension comprised between 100 and 300 mm, particularly comprised between 150 and 180 mm. Having still in mind the dimensional aspect of the first section 5, the jacket 9 exhibits, in a non limiting way, a passage cross-section area comprised between 30 and 250 cm2, particularly between 40 and 150 cm2, still more particularly between 40 and 80 cm2. The cross-section passage area means the passage cross-section of the piston 10 defined by the inner lateral sliding wall of the jacket 9.
As hereinbefore specified, the first section 5 comprises a piston 10 slidingly engaged inside the jacket 9. Specifically, the piston 10 substantially comprises a head 14—substantially countershaped to the inner lateral wall of the jacket 9 (cylindrical head)—slidingly moveable inside the jacket 9 and a stem 15 connected to the head 14 (Figures from 5 to 7): the stem 15 emerges from the jacket 9 opening present at the first longitudinal end 9a for enabling to constrain the piston 10 to different outside components. Particularly, a portion of the stem 15, emerging from the jacket 9 of the first section 5, comprises at least one constraining element 20 configured for being associated to the frame 2 or the thrusting portion 3b of the hammer 3.
The attached figures illustrate a preferred but non limiting arrangement of the invention, wherein the constraining element 20 is directly associated to the thrusting portion 3b of the hammer 3. Advantageously, the constraining element 20 can comprise a sleeve or pin adapted to cooperate with a respective pin or sleeve of the thrusting portion 3b for defining a hinge-type constrain. Alternatively, the constraining element 20 and thrusting portion 3b can comprise a mechanical joint also adapted to define a hinge-type constrain.
The piston 10 of the first section 5 is adapted to divide the inner volume of the jacket 9 in two distinct chambers (not illustrated in the accompanying figures), the volume thereof is variable as a function of the piston 10 position; from the dimensional point of view, the piston 10 stroke is sized in order to enable the passage of the hammer from the working condition to the receiving or exclusion one, and vice versa. Particularly, the piston 10 stroke is comprised between 50 and 600 mm, particularly between 60 and 250 mm, still more particularly between 80 and 150 mm.
Further, the first section 5 comprises at least two through supply conduits (not illustrated) made in correspondence of the jacket 9 lateral wall and configured for supplying, according to a known rule, the opposite chambers of the double-acting cylinder. As it will be better described in the following, the tamping machine 1 comprises at least one power supply (not illustrated), particularly a generator defined by a pump-motor group, which is configured for pressurizing a fluid (oil) and delivering it—via a distributing circuit—to first hydraulic control means 16: these are configured for selectively supplying the double-acting cylinder of the first section 5—via the through conduits of the jacket 9—and for moving the tamping hammer 3 from the working condition to the receiving or exclusion one, and vice versa.
As it is visible from Figures from 5 to 7, for example, further the first section 5 comprises an anchoring portion 13 extending as an axial extension of the jacket 9 from a part opposite to the first end 9a. Particularly, the anchoring portion 13 represents a projection emerging from the second end 9b of the jacket 9 away from the first end 9a. In a preferred but non limiting embodiment of the invention, the anchoring portion 13 is joined in one piece to the jacket 9 of the first portion 5 to define a solid body. The anchoring portion 13, as it will be better described in the following, extends towards and is engaged with the second section 6 of the actuator 4.
De facto, the anchoring portion 13 comprises, in a non limiting way, a circular cross-section tubular body opened at an end opposite to the second end 9b of the jacket 9. Specifically, in a non limiting embodiment of the invention, the anchoring portion 13 comprises a cylindrical tubular body joined in one piece to the jacket 9 and having substantially the same shape as this latter (which has also a cylindrical shape). It should be understood the anchoring portion 13 can comprise a projection having any shape and size adapted to enable to engage the jacket 9 of the first section 5 with the second section 6.
As hereinbefore discussed, each actuator 4 further comprises a second section 6 dedicated to enable the hammer 3 to vibrate. As it is visible in the accompanying figures, the second section 6 is engaged and axially aligned with the first section 5: particularly, the sections 5, 6 are longitudinally aligned and axially movable one in relation to the other. In other words, the first and second sections 5, 6 of each actuators are mechanically serially connected to each other.
Also the second section 6 comprises a hydraulic double-acting cylinder exhibiting at least one jacket 7, particularly having a cylindrical shape, extending between the first and second longitudinal ends 7a, 7b axially delimiting the cylinder: the jackets 9, 7 of the respective first and second sections 5, 6 are axially aligned to each other. As it is visible in
As it is visible in
As it is visible in
Moreover, as it is visible from the cross-section views of
In the accompanying figures, the constraining portion 21 is joined in one piece to the first end 7a of the jacket 7; particularly it forms an solid piece with the closing plug of the cylinder, fixed at the first end 7a of the jacket 7. De facto, in the machine 1 object of the present invention, it is just the jacket 7 of the second section 6 to be engaged, particularly directly, with the frame 2 or thrusting portion 3b of the tamping hammer 3. The attached figures illustrate a preferred but non limiting embodiment of the invention wherein the jacket 7 is constrained and fixed to the frame 2.
As it is visible in
From the dimensional point of view, the jacket 7 exhibits an overall axial extension, substantially defined by the distance between the first and second longitudinal ends 7a, 7b, comprised between 150 and 200 mm. However, the inner sliding lateral wall of the jacket 7 exhibits an axial extension comprised between 160 and 190 mm. Still referring to the jacket 7 of the second section 6 from the dimensional point of view, this latter exhibits, in a non limiting way, a passage cross-section smaller than the passage cross-section of the jacket 9; specifically, the passage cross-section area of the jacket 7 of the second section 6 is comprised between 5 and 200 cm2, still more particularly between 20 and 100 cm2, still more particularly between 50 and 100 cm2. The cross-section passage area means the passage cross-section of the piston 8 defined by the inner lateral sliding wall of the jacket 7.
As hereinbefore described, the second section 6 comprises at least one piston 8 slidingly moveable inside the jacket 7 along a prevalent development axis of the same: the piston 8 is axially movable with respect to the jacket 7. As hereinbefore described, the jacket 7 is closed at the first and second longitudinal ends 7a, 7b: the piston 8 exhibits an overall axial size defined by respective opposite thrusting faces of the piston 8 itself which is entirely received inside the jacket 7.
De facto, the piston 8 of the second section 6 comprises only a head completely received in the jacket 7: the piston 8 is devoid of a stem and does not exhibit parts projecting from the longitudinal ends of the jacket 7. In other words, the piston 8 exhibits an overall axial extension defined by the distance between a first and second longitudinal ends 8a, 8b at which the thrusting faces of the piston 8 itself are defined: the first end of the piston 8 is inside the jacket 7 and faces the first closed end 7a of this latter, while the second end 8b of the piston 8 is inside the jacket 7 and faces the second closed end 7b of the jacket 7. As it is for example visible in
Each chamber exhibits a volume variable as a function of the relative position taken by the piston 8 of the second section 6 with respect to the jacket 7 of this latter section. It is to be noted, due to the absence of the stem of the piston, the maximum value, particularly both the maximum value and the minimum value, definable by each of said chambers, is substantially identical. As illustrated in
Moreover, it is noted that the structure and size of the piston 8 of the second section 6, enable at the same piston 8 to operate inside the jacket 7 without using seals: there are no seals between the jacket 7 and the piston 8 of the second section 6.
More particularly, as it is visible in the accompanying figures, the piston 8 of the second section 6 comprises a cylindrical body longitudinally delimited by the thrusting faces of the first and second ends 8a, 8b; at a lateral wall, the piston comprises an engagement portion 24 configured for stably receiving a connecting element 11 fixed with respect to the piston 8 and emerging transversally with respect to this latter.
The connecting element 11 of the piston 8 is axially slidingly engaged inside at least one longitudinal groove 12 of the jacket 7. Particularly, the connecting element 11 comprises a plate fixed to the piston 8 and emerging normal to the lateral wall of this latter: the plate defines a kind of mechanical stop configured for axially slidingly being engaged inside the groove 12. The connecting element 11, during the movement of the piston in relation to the jacket 7, slides inside the groove 12 and defines a kind of stop for the piston 8. The attached figures illustrate a preferred but non limiting arrangement of the invention, wherein the jacket 7 comprises two grooves 12 and a connecting element 11 emerging from opposite sides of the piston 8 and configured for being slidingly engaged inside the two grooves 12.
Preferably, the connecting element 11 is fixed via mechanical members, for example screws, at the center line of the piston 8: in this way, the mechanical stop defined by the connecting element 11 is engaged in a balanced way with the piston 8 and prevents an undesired development of stresses when sliding on the same.
The connecting element 11, besides defining a kind of stop, is configured for being stably engaged with the anchoring portion 13 of the first section 5; as it is visible in the attached figures, the anchoring portion 13 extends around the jacket 7 of the second section 6 to above the groove 12 (to the two grooves 12) and engages the connecting element 11. De facto, the jacket 9 of the first section 5 is joined to the piston 8 of the second section 6 by the connecting element 11: the piston 8 is therefore moveable along a same axis, with the connecting element 11 and jacket 9.
In a preferred but non limiting embodiment of the invention, the anchoring portion 13 of the first section 5 extends at least partially around the jacket 7 of the second section 6 and engages the connecting portion 11 at opposite sides of said jacket 7: the anchoring portion 13 comprises substantially a tubular jacket at least partially outwardly covering the jacket 7 of the second section 6 to the grooves 12 and engaging the connecting element 11.
From the dimensional point of view, the opposite longitudinal thrusting faces of the piston (ends 8a, 8b) substantially exhibit the same thrusting surface, particularly the thrusting surface of both the faces is comprised between 5 and 200 cm2, more particularly between 20 and 100 cm2, still more particularly between 50 and 100 cm2. As hereinbefore described, the second section 6 is dedicated to the vibration of the hammer 3; for this purpose, the piston 8 of the second section 6 exhibits a maximum axial stroke smaller than the piston 10 axial stroke. Specifically, the ratio of the maximum axial stroke of the piston 10 of the first section 5 to the maximum axial stroke of the piston 8 of the second section 6 is greater than 2, particularly is comprised between 4 and 10. Quantitatively, the maximum axial stroke of the piston 8 of the second section is comprised between 5 and 30 mm, particularly between 10 and 25 mm.
The cross-section of the jacket 7 and the stroke of the piston 8 define the maximum and minimum volumes of each chamber 18 and 19. The maximum volume definable by each chamber 18, 19 is comprised between 20 and 100 cm3, particularly between 20 and 70, still more particularly is comprised between 25 and 35 cm3, while the minimum value definable by the same is comprised between 0 and 20 cm3, particularly is comprised between 0 and 10 cm3.
As it is visible in
Then, the control unit can be connected to the power supply of the actuator 4 and hydraulic control means 16 and 17; the control unit is configured for managing the operation of the power supply and hydraulic control means 16, 17 for managing and controlling the movement and operation of the first and second sections 5, 6 of each actuator 4.
Advantageously but without limitation, each actuator 4 could comprise seals 26, 27 (
As hereinbefore described, the machine 1 comprises power supplies and hydraulic control means 16, 17 for the first and second sections 5 and 6. The first section 5, as hereinbefore described, is extendable and is configured for moving the respective tamping hammer 3 from a substantially vertical working position (the condition illustrated in
The sections 5 and 6 of each actuator 4 are distinctly supplied by hydraulic circuits connected to the cited power supply (for example a single motor-pump group); the first section 5 is extendable by a respective supply-discharge commutator drivable by the operator in order to enable to exclude one or more actuators 4 of each machine 1 when required by the track trajectory; the second section 6 by the supply-discharge commutators driven according to a cyclical sequence by one or more distributing means 17.
The diagram of
In the blocking intermediate position, shown in the figure, the solenoid valves intercept all the conduits (they are definable as supply or discharge conduits based on the position of the solenoid valve) of the corresponding section of the actuator 4 making in this way the piston and jacket of the same cross-section reciprocally integral to each other.
The second section 6 of each actuator 4 is supplied, via respective switching two-way type solenoid valves without a blocking position and the solenoids of said solenoid valves are cyclically supplied by a variable frequency oscillator, preferably of the electronic type. As clearly shown in
The circuit illustrated in
In the variant in
The variant in
Moreover, the invention refers to a railway car 100 provided with a supporting structure 101 exhibiting at least four wheels configured for enabling the abutment and the engagement of the car on a track: the supporting structure substantially defines cars abutting on rails. The car 100 comprises at least one tamping machine 1 (advantageously there are a plurality of tamping machines 1, for example from 2 to 4, for each car 100) engaged with the supporting structure 101 so that the same machine 1 is interposed between the track and structure 101.
Each tamping machine 1 is engaged with the supporting structure 101 so that a pair of hammers 3 are placed above a track at at least one sleeper T of the ballast (see
In detail, the frame 2 of the tamping machine 1 is movably constrained to the supporting structure 101: the frame 2 is configured for translating from a raised position wherein the frame 2 itself is placed in proximity of the structure 101 to a lowered position wherein the frame 2 itself is more spaced from the structure 101 than from the retracted position, and vice versa.
Advantageously, the railway car 100 comprises at least one hydraulic cylinder 102 (
The hammers 3 of the tamping machine 1, arranged in the working condition, are configured for being spaced from the railway ballast M when the frame 2 is in the raised position (
The hammers 3 of the tamping machine 1, arranged in the working condition, are configured for sinking at least partially into the railway ballast when the frame 2 is in the lowered position (
Under the condition wherein the car is provided with a plurality of tamping machines 1, it is possible to connect the same machines to a control unit (not illustrated in the accompanying figures) configured for commanding independently the raised or lowered condition of each machine 1 or for coordinating the movement of all the machines. Advantageously, the control unit is connected to the hydraulic cylinders 102 of each machine 1 and, at the same time, to all the actuators of these latter.
Therefore, the control unit is configured for managing both the translation of each single machine 1 and the working and tilting conditions of each single hammer 3.
Further, the car 100 control unit can be connected to the transducers 25 of the actuators 4 for detecting at least one of the following parameters: the position of the tamping hammer 3 in relation to the frame 2 or in relation to another hammer 3, the vibration frequency of the actuator, the force exerted by the actuator and therefore the force for tamping the ballast M.
Based on the signal received by the transducer 25, the control unit can measure the force exerted by the hammer 3 and the counteracting force of the ballast during the tamping operations; this parameter is useful for evaluating the state of the ballast M. De facto, the control unit, by the transducers 25, is capable of effectively monitoring the actuators directly operating for tamping the ballast; by the signals received by the transducers 25 (the force exerted by the actuators and the counteracting force of the ballast), the control unit is configured for verifying the soundness of the railway ballast M and possibly signaling a fail in case the condition of this latter does not fall inside desired parameters.
Advantageously, the car 100 can comprise a power supply group (not shown) consisting of a diesel engine and one or more hydraulic pumps with associated fuel and hydraulic fluid tanks; the power supply group can be housed in a hood adjacent to the control cab and can be configured for supplying one or more machines 1 (the power supply can supply both the cylinders 102 and actuators 4).
Moreover, the control unit can be connected to the power supply both of the cylinder 102 and actuators 4 so that the same can coordinate the raised and lowered condition of the tamping machine 1 with the lowered (operative) and receiving or exclusion conditions of the hammers 3.
Advantageously, the control unit can be connected to the hydraulic control means 16 and 17 of each tamping machine for driving the solenoid valves and then managing the sections 5 and 6 of each actuator.
The present invention enables to solve the described limitations and drawbacks of the prior art and enables to obtain remarkable advantages. Particularly, the tamping machine 1 object of the present invention exhibits a certainly simplified and compact structure enabling to easily mount it on the car 100 and a straightforward maintenance. De facto, the particular structure of each actuator 4 enables to provide extremely compact cylinders both longitudinally and transversally. This makes the machine 1 extremely compact, this characteristic enabling to certainly improve the stability and strength of the same. The high stability of the machine enables the same to operate under high frequencies (the hammers 3 can operate at high frequencies) and variable inside a wide range of values selectable in relation to the state of the ballast to be regenerated: the structure of the machine 1 avoids the generation of unacceptable structural stresses on behalf of a substantial increase of the performance thereof.
Moreover, reducing the size of the tamping machine 1, object of the present invention, enables to fit several tamping hammers 3 on each machine 1 so that, if required, this latter can simultaneously operate on consecutive sleepers of a track. De facto, the possibility of fitting on the same side of the car 100 a plurality of machines and therefore of tamping hammers 3, enables to simultaneously regenerate plural sleepers T. Further, it is noted that the possibility of rapidly excluding one or more hammers 3 from the tamping machine 1, makes its use extremely flexible: the possibility of using the first section 5 for excluding a hammer 3 enables to use the machine both on straight-tracks and points of a track. An important advantage of the invention is given by the particular structure of the actuators 4; particularly, the structure of the piston 8 of the second section 6 ensures a substantial efficiency: the absence of a stem enables the piston to exploit, on both the piston 8 faces, a common large thrusting surface. The fact that the piston 9 can completely remain received in the jacket 7 and that it can generate on the opposite faces the same force, enables to define an extremely compact and balanced double-acting cylinder. The absence of the stem enables to reduce the transversal size of the piston 8 and consequently of all the second section 6. The force exerted by the second section 6 (the vibrating section) is capable of vibrating each hammer at high frequencies and simultaneously exerting a high movement force: each hammer 3 is capable of suitably regenerating the ballast also by means of small powers.
While at least one exemplary embodiment of the present invention(s) is disclosed herein, it should be understood that modifications, substitutions and alternatives may be apparent to one of ordinary skill in the art and can be made without departing from the scope of this disclosure. This disclosure is intended to cover any adaptations or variations of the exemplary embodiment(s). In addition, in this disclosure, the terms “comprise” or “comprising” do not exclude other elements or steps, the terms “a” or “one” do not exclude a plural number, and the term “or” means either or both. Furthermore, characteristics or steps which have been described may also be used in combination with other characteristics or steps and in any order unless the disclosure or context suggests otherwise. This disclosure hereby incorporates by reference the complete disclosure of any patent or application from which it claims benefit or priority.
| Number | Date | Country | Kind |
|---|---|---|---|
| MI2014A002043 | Nov 2014 | IT | national |
