U.S. patent application number 16/655957 was filed with the patent office on 2020-05-07 for self-propelled road milling machine for milling road surfaces, in particular large-scale milling machine, and method for milling.
The applicant listed for this patent is Wirtgen GmbH. Invention is credited to Cyrus Barimani, Hardy Emme, Andreas Salz.
Application Number | 20200141072 16/655957 |
Document ID | / |
Family ID | 47683780 |
Filed Date | 2020-05-07 |
![](/patent/app/20200141072/US20200141072A1-20200507-D00000.png)
![](/patent/app/20200141072/US20200141072A1-20200507-D00001.png)
![](/patent/app/20200141072/US20200141072A1-20200507-D00002.png)
![](/patent/app/20200141072/US20200141072A1-20200507-D00003.png)
![](/patent/app/20200141072/US20200141072A1-20200507-D00004.png)
![](/patent/app/20200141072/US20200141072A1-20200507-D00005.png)
United States Patent
Application |
20200141072 |
Kind Code |
A1 |
Emme; Hardy ; et
al. |
May 7, 2020 |
Self-Propelled Road Milling Machine For Milling Road Surfaces, In
Particular Large-Scale Milling Machine, And Method For Milling Road
Surfaces
Abstract
In a self-propelled road milling machine for milling road
surfaces comprising a milling roller housing arranged at the
machine frame between the front and rear chassis axles, it is
provided that the rear end, as seen in the direction of travel, of
the milling roller housing is flush with a height adjustable
stripper shield which laterally rests in the milling track of the
milling roller and resiliently against a milling edge of the
milling track extending orthogonally to the road surface.
Inventors: |
Emme; Hardy; (Dattenberg,
DE) ; Barimani; Cyrus; (Konigswinter, DE) ;
Salz; Andreas; (Neustadt/Wied, DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Wirtgen GmbH |
Windhagen |
|
DE |
|
|
Family ID: |
47683780 |
Appl. No.: |
16/655957 |
Filed: |
October 17, 2019 |
Related U.S. Patent Documents
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
|
|
15232905 |
Aug 10, 2016 |
10450709 |
|
|
16655957 |
|
|
|
|
13786940 |
Mar 6, 2013 |
9416502 |
|
|
15232905 |
|
|
|
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
E01C 23/127 20130101;
E01C 23/088 20130101 |
International
Class: |
E01C 23/088 20060101
E01C023/088; E01C 23/12 20060101 E01C023/12 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 8, 2012 |
DE |
102012203649.0 |
Claims
1-14. (canceled)
15: A self-propelled construction machine, comprising: front and
rear ground engaging supports, as seen in a direction of travel; a
machine frame supported from the front and rear ground engaging
supports; a working roller housing arranged at said machine frame
between said front and rear ground engaging supports; a single
working roller in said working roller housing; a hydraulic or
electric working roller drive unit operably associated with said
working roller; two linear guides supported from said machine frame
between said front and rear ground engaging supports, said working
roller housing and said working roller being supported on said two
linear guides between said front and rear ground engaging supports,
wherein a first one of said linear guides is a tubular guide; and
wherein said working roller, together with said working roller
housing and said working roller drive unit, is supported so as to
be displaceable along the two linear guides transversely to the
direction of travel between multiple operating positions of said
working roller while maintaining movement of the construction
machine in the direction of travel during working engagement of the
working roller with a ground surface.
16: The self-propelled construction machine according to claim 15,
wherein the two linear guides are spaced from each other in the
direction of travel.
17: The self-propelled construction machine according to claim 15,
wherein the first one of the linear guides defines a locating
bearing.
18: The self-propelled construction machine according to claim 15,
wherein a maximum lateral traveling distance of the working roller
is in a range from 500 to 1000 mm.
19: The self-propelled construction machine according to claim 15,
wherein said working roller, together with said working roller
housing and said working roller drive unit, are continuously
displaceable along the two linear guides.
20: The self-propelled construction machine according to claim 15,
further comprising an actuator configured to displace said working
roller, together with said working roller housing and said working
roller drive unit, along the two linear guides transversely to the
direction of travel.
21: The self-propelled construction machine according to claim 20,
wherein the actuator includes a piston and cylinder unit connected
between the machine frame and the working roller housing.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
[0001] The invention relates to a self-propelled road milling
machine for milling road surfaces, in particular large-scale
milling machines, and a method for milling road surfaces.
2. Description of the Prior Art
[0002] Road milling machines having a milling width of
approximately 1500 mm and more are referred to as large-scale
milling machines, for example. Such road milling machines have a
large weight and are thus normally supported by a chassis
comprising crawler-type traveling gears. The milling roller is
supported at the machine frame between the traveling gears of the
front axle and the rear axle in spaced relationship to the axles.
Large-scale milling machines comprise a height adjustable chassis
including front and rear traveling gears which define the front
axle and the rear axle, respectively. The machine frame is
supported by the chassis, wherein between the axles of the front
and rear traveling gears a milling roller housing is arranged at
the machine frame, which comprises a single roller mill rotatably
supported in the milling roller housing. The milling roller housing
has coupled thereto, via a belt shoe, a conveyor belt means for
removing the milling product milled-off and ejected by the milling
roller in forward direction, as seen in the direction of
travel.
[0003] Such a large-scale milling machine is known from EP 2 011
921 A, for example.
[0004] A front end of the milling roller housing is nearly flush
with an outer side of the machine frame, the so-called zero side,
to allow milling to be performed as near as possible to edges or
obstacles. The milling roller housing is not adjustable in height
relative to the machine frame such that the overall machine weight
can be transmitted to the milling roller to produce high cutting
forces and thus a large milling depth.
[0005] So far large-scale milling machines have been used mainly
for milling large surfaces only, inter alia, because of their
limited maneuverability, wherein, depending on the course of the
road, it has been possible to perform milling work in curves of the
road having a large curve radius.
[0006] In particular during milling work performed towards the
inside relative to the zero side large-scale milling machines are
problematic in that it has not been possible for the machine
operator to follow a curve with a narrow curve radius. A solution
to this problem is described in EP 2 011 921, which allows for a
visual check when steering a large-scale milling machine, whereby
the maneuverability of a large-scale milling machine could be
improved.
[0007] In the case of roads with right-hand traffic, the zero side
of a road milling machine is preferably provided on the right-hand
side of the machine, as seen in the direction of travel. In the
case of roads with left-hand traffic, the zero side is preferably
provided on the left-hand side (as seen in the direction of
travel). It is understood that a large-scale milling machine can be
turned around when there is enough room for a turning maneuver and
thus a large-scale milling machine having the zero side on the
right-hand side, as seen in the direction of travel, can also be
used on roads with left-hand traffic. This is disadvantageous in
that the road milling machine having its zero side on the
right-hand side, as seen in the direction of travel, has to travel
opposite to the moving traffic when a road cannot be completely
closed when roadwork is performed. Such a situation is encountered,
for example, when on a highway the left-hand traffic lane is to be
milled flush with the left-hand side of the road. This is
disadvantageous in that the trucks receiving the milled-off product
in front of the road milling machine must also travel opposite to
the traffic flow to the front side of the road milling machine and
then travel away from there. Further, when narrow roads are
concerned it is often desirable to be able to optionally mill the
road on the left-hand or the right-hand side without the need to
turn the large-scale milling machine.
[0008] For example, in DE 83 15 139 U it is provided that in a road
milling machine supported by a wheel-type traveling gear a single
hydraulically operated milling roller is displaced transversely to
the direction of travel by a small stroke along sliding guides. The
machine concerned is not a large-scale milling machine which can
produce large cutting forces since the milling roller is supported
such that it is pivotable about a horizontal axis and rests on the
ground merely due to its dead weight. The milling roller can thus
be raised and lowered relative to the machine frame and further can
be pivoted about an axis extending in the direction of travel to
adapt to the inclination of the road. The capability of being
transversely displaced is to allow for an accurate control of the
milling track. It is understood that due to this rocker support of
the milling roller no large cutting forces can be exerted and such
a milling machine is suitable only for milling surfaces where no
large milling depths are required.
SUMMARY OF THE INVENTION
[0009] It is an object of the present invention to provide a
self-propelled road milling machine of the type described above,
and a method for milling road surfaces, which machine is more
universally usable and whose maneuverability is improved.
[0010] According to the present invention, the milling roller drive
unit preferably is a hydraulic or electric drive unit integrated in
the milling roller, and the milling roller, together with the
milling roller housing and the milling roller drive unit, is
supported at the machine frame in a displaceable manner
transversely to the direction of travel, whereby the zero side is
adapted to be defined on the one outer side or on the opposite
outer side of the machine frame.
[0011] The solution according to the present invention offers the
advantage that essentially the overall machine weight acts upon the
milling roller due to the arrangement of the milling roller between
the axles of the chassis, whereby large milling depths at high
advance rates can be achieved. Since the milling roller is capable
of being displaced the zero side can optionally be defined on the
one outer side or on the opposite outer side such that work can be
performed optionally flush right or flush left along obstacles
while maintaining the direction of travel. The milling roller can
be displaced during milling operation, for which purpose the
milling roller preferably comprises additional chiseling tools at
its front edges. The milling roller, together with the milling
roller housing and the milling roller drive unit integrated in the
milling roller, is displaced linearly and transversely to the
direction of travel at the machine frame. Linear guiding below the
machine frame offers the advantage that neither the milling depth
nor the transverse inclination of the milling roller is affected by
the linear displacement. This is of importance with regard to
leveling of the road milling machine with the aid of a height
adjustable chassis. An essential advantage is that only the
position of the machine frame must be monitored to make
corrections, if necessary. Another advantage is that the milling
roller can be displaced during operation without any interruption
of operation.
[0012] The milling depth can be adjusted via the height adjustable
chassis. The high pressure load exerted by the milling roller in
connection with the milling roller housing via the machine frame
allows for milling depth of at least 30 cm such that during a
single passage the complete road surface can be removed.
[0013] Turning away from the usual mechanical drive concept
comprising a belt drive and integration of preferably two motors
into the milling roller allow the position of the milling roller
transverse to the direction of travel to be varied.
[0014] The milling roller drive is preferable realized on both
sides, i. e. using two drive means integrated in the front ends of
the milling roller.
[0015] Preferably, the milling roller housing is linearly displaced
along two linear guides spaced from each other in the direction of
travel of the machine frame.
[0016] The two linear guides allow for rigidly supporting the
milling roller housing at the machine frame and thus rigidly
supporting the milling roller in vertical direction such that a
precise milling depth adjustment is maintained. Further, the
milling roller housing is rigidly supported in the direction of
travel such that the milling roller is movable only in transverse
direction with respect to the direction of travel.
[0017] A first one of the linear guides is a tubular guide and
defines a locating bearing, and a second one of the linear guides
is a guide arranged between two plane surfaces and defines a
non-locating bearing.
[0018] The support of the milling roller housing thus comprises a
locating bearing and a non-locating bearing, wherein the clearance
between the plane surfaces of the non-locating bearing may be
adjustable.
[0019] Preferably, the linear guides are fixed to the machine frame
at a location below the machine frame.
[0020] Arrangement of the linear guides below the machine frame
offers the advantage that the weight force of the machine can be
directly transmitted to the milling roller via the milling roller
housing, and that the guides can be arranged in a space saving
manner.
[0021] The milling roller housing is rigidly fixed to the machine
frame in vertical direction and the direction of travel.
[0022] The milling roller housing comprises at its front ends
respective height adjustable side shields. The cutting circle at
the front ends of the milling roller when milling along an
obstacle, e. g. a lamppost or a bridge pier, is preferably spaced
from the obstacle by less than 120 mm, preferably 105 mm, or less
than 105 mm.
[0023] The maximum lateral traveling distance of the milling roller
ranges between 500 and 1000 mm. This traveling distance allows the
zero side to be optionally defined on the left-hand or the
right-hand side of the road milling machine.
[0024] The milling roller is preferably adapted to be hydraulically
driven on both sides. The both-sided drive offers the advantage
that the torsional load of the milling roller can be reduced, and
that finally a higher power can be transmitted to the milling
roller. Alternatively, an electric drive unit can be provided.
[0025] At the milling roller housing a belt shoe for receiving the
lower end of the conveyor belt means can be fixed in a height
adjustable manner. The belt shoe can follow the movement of the
milling roller housing transversely to the direction of travel such
that the lower end of the conveyor belt means is always arranged at
the milling product ejection opening at the milling roller
housing.
[0026] For this purpose it is provided that the conveyor belt means
is articulated to the belt shoe.
[0027] For articulating the lower end of the conveyor belt means to
the belt shoe, the belt shoe comprises an essentially concave,
preferably spherical reception socket which cooperates with a lower
side of the lower end of the conveyor belt means, whose shape is
adapted to the shape of the reception socket.
[0028] The front side of the conveyor belt means at the machine
frame is adapted to be displaced in longitudinal direction along
the longitudinal axis of the conveyor belt means and is supported
by a cardan joint.
[0029] The conveyor belt means is adapted to be pivoted at its
front side about a vertical axis, which is vertical when the
machine frame is horizontally aligned, and a transverse axis
extending in parallel to the milling roller axis.
[0030] At least on the front side the conveyor belt means comprises
on the lower side a conveyor belt-side support element preferably
having a convex bearing surface and extending essentially in the
longitudinal direction of the conveyor belt means for ensuring
flexible support, said support element being laterally guided and
resting on a frame-side support element preferably having a convex
supporting surface and fixed transversely to the direction of
travel at the machine frame. The bearing surface and the support
surfaces define a cardan joint, which additionally offers the
advantage that even a slight rolling motion about the longitudinal
axis of the conveyor belt means is possible.
[0031] The conveyor belt-side support element and/or the frame-side
support element can be defined by a profile with a rounded cross
section or a hollow profile. They may preferably rest on top of
each other and thus allow a point support which permits
displacement of the conveyor belt means along its longitudinal
axis.
[0032] The belt shoe is preferably height adjustable via a
synchronized guide. Guiding of the belt shoe for raising and
lowering purposes is performed in the form of linear guiding where
the height adjustment is effected synchronously by the same amount
on the right-hand and the left-hand side of the belt shoe.
[0033] At the milling roller housing a hydraulic angular manifold
for supplying the hydraulic drive units, at least the milling
roller drive units provided at the milling roller housing may be
fixed in place.
[0034] The hydraulic angular manifold fixed in place at the milling
roller housing allows the hydraulic lines at the milling roller
housing to extend in a rigid manner to the drive units and prevent
excessively narrow bend radii of the supply lines from the
hydraulic pumps.
[0035] For improving the maneuverability and permitting universal
usability of a large-scale milling machine, the rear end, as seen
in the direction of travel, of the milling roller housing may be
flush with a height adjustable stripper shield which, in the
milling track of the milling roller, laterally and resiliently
bears upon milling edges of the milling track extending
orthogonally to the road surface.
[0036] Since the stripper shield is adapted to laterally
spring-deflect, the large-scale milling machine can travel narrow
curve radii without the stripper shield getting jammed. Another
advantage is that, since the stripper shield elastically bears upon
the milling edge of the milling track, the stripper shield can
strip the milling track without leaving milling product
residues.
[0037] The rear end, as seen in the direction of travel, of the
milling roller housing can be flush with a height adjustable
stripper shield which comprises at both lateral ends a respective
movable shield element whose lower edge is essentially flush with
the stripper shield and which, together with the latter, is
adjustable in height, wherein the shield elements, together with
the stripper shield and the milling roller axle, are adjustable
against a spring bias to dynamically adapt the stripper shield
width during the milling operation.
[0038] In a method for milling road surfaces using a self-propelled
road milling machine comprising a machine frame including lateral
outer sides, a single rotatably supported milling roller and a
milling roller drive unit for the milling roller, wherein a front
end of the milling roller is nearly flush with a lateral outer side
of the machine frame, the so-called zero side, to allow milling to
be performed as near as possible to edges or obstacles, it is
provided that the zero side is optionally defined on the one outer
side or on the opposite outer side of the machine frame by
integrating the milling roller drive unit as a hydraulic or
electric drive unit in the milling roller and supporting the
milling roller, together with the milling roller drive unit, in a
displaceable manner transversely to the direction of travel.
BRIEF DESCRIPTION OF THE DRAWINGS
[0039] Hereunder an exemplary embodiment of the present invention
is described in detail with reference to the drawings in which:
[0040] FIG. 1 shows a schematic partial view of the self-propelled
road milling machine,
[0041] FIG. 2 shows a milling roller housing as a displaceable
module,
[0042] FIG. 3 shows the milling roller housing with an articulated
conveyor belt means,
[0043] FIG. 4 shows a rear view of the milling roller housing
comprising a stripper shield, and
[0044] FIG. 5 shows a perspective bottom view of a combination of
the milling roller housing with the conveyor belt means coupled
thereto.
DETAILED DESCRIPTION
[0045] FIG. 1 shows a road milling machine 1, in particular a
large-scale milling machine, comprising a machine frame 8 and a
chassis 4 including front and rear traveling gears 5,6, as seen in
the direction of travel 31. The traveling gears 5,6 define a
steerable front axle and a steerable rear axle. The chassis 4 is
connected with the machine frame 8 via lifting columns 7 with the
aid of which the distance of the machine frame 8 to a road surface
2 is adjustable. Each chassis axle comprises at least one
crawler-type traveling gear 5,6 or a wheel-type traveling gear.
[0046] At a front side, as seen in the direction of travel, of the
road milling machine 1 a vertically and laterally pivotable
conveyor belt means 18 for removing the milled-off milling product
is arranged.
[0047] The front and rear traveling gears 5,6 of the chassis 4 may
be crawler-type traveling gears or wheel-type traveling gears.
[0048] The machine frame 8 comprises lateral outer sides 26,28
essentially extending vertically and in parallel to the
longitudinal center axis of the road milling machine 1. It is
understood that the outer sides 26,28 need not extend perfectly
vertically and absolutely in parallel to the longitudinal center
axis of the road milling machine 1 and that minor deviations are
acceptable. The outer side 26,28 is preferably integral, wherein
the outer sides 26 and 28 preferably lie in the same plane.
[0049] Between the traveling gears 5,6 a milling roller 12 is
arranged which, together with its milling roller axle, is supported
in a milling roller housing 10.
[0050] The one front end 22 of the milling roller 12 comes up to
the outer side 26,28 of the machine frame 8 shown as the zero side
in FIG. 1. At the zero side the corresponding front end 22 of the
milling roller 12 is located very near to the outer side of the
road milling machine 1 such that milling can be performed very near
to road edges or obstacles.
[0051] In the front end 22 of the milling roller 12 hydraulic or
electric milling roller drive units 14 are preferably integrated on
both sides, which are supplied by hydraulic pumps or generators
arranged at the machine frame 8, which in turn are driven by a
combustion engine 3 supplying the driving power for the traction
drive unit, the milling drive unit and auxiliary equipment.
[0052] At the front ends 22 of the milling roller 12 and next to
the milling roller housing 10 a respective height adjustable side
shield 15 is arranged which serves as an edge guard.
[0053] The milling roller 12 is preferably arranged centrally
between the front traveling gear 5 and the rear traveling gear 6,
as seen in the direction of travel 31.
[0054] The milling roller 12 is provided with tools 13. The milling
roller 12 rotates in clockwise direction as seen from the
right-hand side of FIG. 2.
[0055] The single milling roller 12 may be composed of a plurality
of parts or of at least one tubular roller slid upon a base body,
for example. Likewise, the milling roller may be composed of a
plurality of segments.
[0056] Above the milling roller 12 there is a driver's platform 16
which may comprise two seats 20 and two steering means 24 which are
respectively provided for flush left and flush right milling along
a road. It is understood that a driver's platform adapted to be
displaced transversely to the direction of travel and comprising
one seat 20 with an associated steering means 24, which is
displaceable to the left-hand side or the right-hand side of the
road milling machine 1, as required, may also be used.
[0057] The seat 20 is preferably aligned with respect to the
lateral outer wall 26,28 such that the seat 20 at least partly
laterally projects beyond the outer wall 26,28.
[0058] If the zero side of the road milling machine 1 is moved
along an obstacle, e. g. a lamppost, the driver's platform 16
including the seat 20, an arm rest and an operator's panel 25 can
be displaced inwardly to allow for flush milling along the
obstacle.
[0059] The outer side 26,28 comprises a recess 32 in front of the
driver's platform 16. This recess 32 allows the front traveling
gear 5 and thus the current steering angle to be monitored.
[0060] In FIG. 1 the milling roller housing 10 is shown with a
raised stripper shield 64, wherein the side shield 15 is also
raised to show the position of the milling roller 12. The milling
roller housing 10 is supported at the machine frame 8 such that it
is adapted to be displaced linearly and transversely to the
direction of travel 31, whereby the zero side can be optionally
defined on the one outer side 26,28 or on the opposite outer side
26,28 of the machine frame 8.
[0061] Displacement of the milling roller housing 10 is performed
with the aid of two guides 34,36 spaced from each other in the
direction of travel of the machine frame 8 and configured as linear
guides.
[0062] The first one of the linear guides 34 is a tubular guide
which, in FIGS. 2 to 4, is arranged on the upper side of the
milling roller housing 10.
[0063] The second linear guide 36 is also arranged in spaced
relationship on the upper side of the milling roller housing 10.
Linear guiding is performed between the plane surfaces 37,38 as can
best be seen in FIGS. 2 and 3. The plane surface 37 is provided on
both the upper side and the lower side of a beam 39 which is fixed
in place on the lower side of the machine frame 8 using flange
parts 41. The plane surfaces 37 are encompassed by guide parts 43
fixed in place at the milling roller housing 10 and comprising the
plane surfaces 38 which are in contact with the plane surfaces 37
of the beam 39. The distance of the plane surfaces 38, which are in
contact with the plane surfaces 37, is adjustable such that the
clearance between the plane surfaces 37 and 38 can be adjusted with
the aid of the guide parts 43.
[0064] The second linear guide 36 defines a non-locating bearing,
while the tubular guide of the first linear guide 34 defines the
locating bearing.
[0065] The tubular guide is composed of an inner tube 33 fixed in
place at the lower side of the machine frame 8 via flange parts 42,
on which a hollow cylinder 35 fixed in place at the milling roller
housing 10 can slide.
[0066] A piston cylinder unit 45 whose one end is fixed to the
machine frame 8 and whose other end is fixed to the milling roller
housing 10 is adapted to displace the overall unit of the milling
roller housing 10 including the milling roller 12 and the other
elements of the milling roller housing 10 shown in FIGS. 2 and 3,
inclusive of the lower end 44 of the conveyor belt unit 18, between
a position of the milling roller 12 flush left or flush right with
respect to the outer side of the road milling machine 1.
[0067] The stroke of the piston cylinder unit 45 preferably ranges
between approximately 500 and approximately 1000 mm. This means
that the milling roller housing 10 including all the components
shown in FIGS. 2 and 3 can be displaced by this traveling distance
transversely to the direction of travel 31. For example, if the
front end of the milling roller 12 is at a location on the
left-hand side of the machine, as seen in the direction of travel
31, and on the other side of or near the outer side 26,28, then the
zero side of the machine is provided on the left-hand side.
[0068] The stroke of the piston cylinder unit 45 is regarded in
relation to the width of the milling roller 12 which is
approximately 1500 mm and more, typically 2000 mm, in large-scale
milling machines. The piston cylinder unit 45 can exert
sufficiently large forces to displace the milling roller housing 10
including the milling roller 12 even during milling operation. For
this purpose, additional tools 13 may be provided at the respective
front ends of the milling roller.
[0069] The two linear guides 34,36 arranged in spaced relationship
to each other, as seen in the direction of travel of the machine
frame 8, are preferably spaced from each other as far as possible.
They can transmit the machine weight to the milling roller housing
10 and to the milling roller 12 supported therein to produce large
cutting forces at large milling depths.
[0070] The combination of the linear guides 34,36 allows for an
optimum absorption of the produced forces and torques.
[0071] The side shield 15 is fixed on both sides of the milling
roller housing 10 via double arrangement of piston cylinder units
17, wherein the double arrangement allows for a particularly large
stroke of the piston cylinder units 17.
[0072] As can only be seen in FIG. 2, the illustrated exemplary
embodiment of a milling roller drive unit 14 may comprise at least
one hydraulic drive unit 80 which is integrated in the front end 22
of the milling roller 12. The illustrated exemplary embodiment
shows a hydraulic drive unit 80 at both front ends 22 of the
milling roller 12, wherein hydraulic supply lines 82 extending to
the drive units 80 are connected via a manifold 84 and further
hydraulic lines 86 with a hydraulic pump driven by the combustion
engine 3.
[0073] The further hydraulic lines 86 are schematically shown as a
single line. It is understood that the at least one hydraulic drive
unit 80 requires at least one supply and return line. The manifold
84 is fixed in place at the milling roller housing 10 such that the
hydraulic lines 82 need not be flexible and merely the further
hydraulic lines 86 must be deformable in such a manner that the
traveling distance of the displaceable unit can be configured as
shown in FIG. 2.
[0074] In FIGS. 2 and 3 a belt shoe 40 is arranged at the front end
of the milling roller housing 10, which serves for receiving the
lower end 44 of the conveyor belt means 18.
[0075] The belt shoe 40 receives the lower end 44 of the conveyor
belt means 18. The belt shoe 40 is arranged centrally with respect
to an ejection opening 11 of the milling roller housing 10 and can
be adjusted in height with the aid of a synchronous guide 60. The
synchronous guide 60 is composed of two link mechanisms 62 each
including a piston cylinder unit 63 and arranged next to the
conveyor belt means 18, wherein the synchronism of the two link
mechanisms 62 is ensured via a coupling shaft 66 such that the
synchronous guide cannot get jammed.
[0076] FIG. 3 shows a representation corresponding to that of FIG.
2 with an integrated conveyor belt means 18.
[0077] The front support of the conveyor belt means 18 can best be
seen in FIG. 5. At the machine frame 8 a frame-side support element
56 is fixed in place. The frame-side support element 56 preferably
comprises a convexly rounded support surface, a tube in the present
exemplary embodiment, upon which the front upper end 46 of the
conveyor belt means 18 can rest via a conveyor belt-side support
element 52. Since both support elements 52,56 comprise convexly
rounded support surfaces, the front side 46 of the conveyor belt
means 18 is supported in a point support, wherein the support
defines a cardan joint. Further, the conveyor belt-side support
element 52 can be displaced in longitudinal direction when the
milling roller housing 10 is displaced from one side to the other
side of the road milling machine 1. The articulated support further
allows for slight rolling motion of the conveyor belt means 18.
[0078] Lateral guides 54 secure the conveyor belt-side support
element 52 in position.
[0079] Due to the displacement motion of the milling roller housing
10 transversely to the direction of travel 31 it is required that
the lower end 44 of the conveyor belt means 18 is received on the
belt shoe 40 in an articulated manner.
[0080] The belt shoe 40 may comprise an essentially concave,
preferably spherical receiving socket 48 for receiving the lower
end 44 in an articulated manner, said receiving socket 48
cooperating with a lower side of the lower end 44 of the conveyor
belt means 18 whose shape is adapted to the shape of the receiving
socket 48. This articulated reception of the lower end 44 of the
conveyor belt means 18 allows for raising the belt shoe 40 together
with the lower end 44 of the conveyor belt means 18 and for
displacing the milling roller housing 10 by a traveling distance of
500 to 1000 mm, wherein the lower end 44 of the conveyor belt means
18 is always arranged in front of the ejection opening 11 of the
milling roller housing 10.
[0081] The receiving socket 48 is defined by inclined surfaces 50
which receive the lower end 44 of the conveyor belt means 18.
Additionally, lateral guides elements 51 are provided which allow,
on the one hand, the lower end 44 to be pivoted about a vertical
axis and, on the other hand, the lower end 44 to be laterally
secured in position. The lower end 44 of the conveyor belt means 18
comprises centrally on its lower side a preferably spherical
support means 49 which is shown dashed in FIG. 2 and which rests on
the belt shoe 40 in an area in front of the central inclination 50.
The support element 49 and its resting position are also shown
dashed in FIG. 5.
[0082] The ejection opening 11 of the milling roller housing 10
need not be arranged centrally with respect to the milling roller
housing 10 but can also be eccentrically arranged. The tools 13 of
the milling roller 12 are spirally arranged in circumferential
direction, wherein the milling roller 12 comprises opposed spirals
of tools 13 which transport the milled-off material to the ejection
opening 11 and convey it from the ejection opening 11 to the
conveyor belt means 18.
[0083] FIG. 4 shows a perspective rear view of the milling roller
housing 10 at which a height adjustable stripper shield 64 is
arranged with the aid of piston cylinder units 65. The stripper
shield 64 is further adapted to be pivoted upwards when the tools
13 at the milling roller 12 must be accessible.
[0084] At its side facing the milling roller 12 the stripper shield
64 comprises at its lateral outer edges a respective shield element
74 which is adapted to be pressed, with the aid of a resilient
biasing means 76 (FIG. 4), against the milling edge 70 (FIG. 1)
extending orthogonally to the road surface 2.
[0085] The lower edge 78 of the laterally movable shield element 74
is flush with the lower edge of the stripper shield 64. The shield
elements 74 are adjustable in height together with the stripper
shield 64. The resilient biasing means 76 can produce the bias in
various ways. In the exemplary embodiment shown in FIG. 4 the
biasing means 76 are shown as piston cylinder elements which are
adapted to be hydraulically biased.
* * * * *