Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 1 of 13 PageID #: 25489
`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 1 of 13 PagelD #: 25489
`
`EXHIBIT 6
`EXHIBIT 6
`
`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 2 of 13 PageID #: 25490
`
`muuuuimmiiii
`
`111111111111111
`
`WA-0014268
`
`(19) United States
`(12) Reissued Patent
`Busley et al.
`
`US RE48,268 E
`(10) Patent Number:
`(45) Date of Reissued Patent: Oct. 20, 2020
`
`(54) CONSTRUCTION MACHINE, IN
`PARTICULAR ROAD MILLING MACHINE,
`RECYCLER OR STABILIZER, AS WELL AS
`DRIVE TRAIN FOR CONSTRUCTION
`MACHINES OF THIS TYPE
`
`(71) Applicant: Wirtgen GmbH, Windhagen (DE)
`
`(72)
`
`Inventors: Peter Busley, Linz/Rhein (DE); Dieter
`Simons, Buchholz (DE)
`
`(56)
`
`References Cited
`
`U.S. PATENT DOCUMENTS
`
`2/1923 Jehu
`1,445,617 A
`3,414,327 A * 12/1968 Austin
`
`(Continued)
`
` EOIC 23/088
`299;1.5
`
`FOREIGN PATENT DOCUMENTS
`
`(73) Assignee: Wirtgen GmbH (DE)
`
`(21) Appl. No.: 15/934,603
`
`(22) Filed:
`
`Mar. 23, 2018
`
`Related U.S. Patent Documents
`
`8,408,659
`Apr. 2, 2013
`12/985,400
`Jan. 6, 2011
`
`Reissue of:
`(64) Patent No.:
`Issued:
`Appl. No.:
`Filed:
`U.S. Applications:
`(63) Continuation of application No. 11/918,247, filed as
`application No. PCT/EP2006/060907 on Mar. 21,
`2006, now Pat. No. 7,891,742.
`
`(30)
`
`Foreign Application Priority Data
`
`Apr. 15, 2005
`
`(DE)
`
` 10 2005 017 754
`
`(51) Int. Cl.
`E01C 23/088
`E01C 23/12
`
`(2006.01)
`(2006.01)
`(Continued)
`
`(52) U.S. Cl.
` E01C 23/088 (2013.01); 1360K 17/02
`CPC
`(2013.01); 13601f 17/04 (2013.01); B601( I 7/28
`(2013.01);
`
`(Continued)
`(58) Field of Classification Search
`CPC .... E01C 23/088; EO1C 23/085; EO1C 23/127;
`EOIC 23/122; E21C 27/24; E21C 31/02;
`(Continued)
`
`AT
`CH
`
`7/1994
`397826 B
`11/1978
`606626 A5
`(Continued)
`
`OTHER PUBLICATIONS
`
`English translation of CH-606626-A5 accessed at <http://
`translationportal.epo.org/emtp/translate/?ACTION=description-
`retrieval&COUNTRY=CH&ENGINE=google&FORMAT=docdb
`&KIND-A5&LOCALE=en_EP&NUMBER-606626&OPS=ops.
`epo.org/3.2&SRCLANG-de&TRGLANG-en>.*
`(Continued)
`
`Primary Examiner — Peter C English
`(74) Attorney Agent, or Firm — Lucian Wayne Beavers;
`Patterson Intellectual Property Law, PC
`
`ABSTRACT
`(57)
`A construction machine, in particular road milling machine,
`recycler or stabilizer, with a machine frame (4) that is carried
`by a chassis (2) with a working drum (6) and a drive train
`(8) comprising at the least a drive engine (10), a traction
`mechanism (12) for the mechanical drive of the working
`drum (6) with a drive element, an output element and a
`traction element (30), a device (14) for switching the torque
`between the drive engine (10) and working drum (6), and
`device (16) for driving at least one hydraulic pump; it is
`provided that elements of the drive train (8) are divided into
`at least two groups, the first group (3) shows at least the
`drive engine (10), the second group (5) shows at least the
`drive element (11) of the traction mechanism. and where the
`first and the second groups (3, 5) are connected to one
`another via an articulated coupling device (20).
`
`39 Claims, 3 Drawing Sheets
`
`11
`
`17
`
`1
`
`(8
`
`
`
`26
`
`16
`
`20
`
`28
`
`10
`
`22
`
`r:41 : 111\
`18
`22
`
`24
`
`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 3 of 13 PageID #: 25491
`
`US RE48,268 E
`Page 2
`
`(51) Int. Cl.
`B6OK 17/02
`B6OK 17/04
`B6OK 17/28
`B60K 25/02
`(52) U.S. CL
`CPC
`
`(2006.01)
`(2006.01)
`(2006.01)
`(2006.01)
`
` E01C 23/127 (2013.01); B6OK 2025/022
`(2013.01)
`
`(58) Field of Classification Search
`CPC .. E21C 31/06; E02F 3/20; E02F 3/283; E02F
`3/84; E02F 9/20; E02F 9/22; E02F
`9/2292; B6OK 2025/022; B6OK 25/02;
`B6OK 17/02; B6OK 17/04; B6OK 17/28
`See application file for complete search history.
`
`(56)
`
`References Cited
`
`U.S. PATENT DOCUMENTS
`
`3,779,608
`3,796,462
`4,193,636
`4,343,513
`
`12/1973 Hatcher et al.
`A
`3/1974 Staab
`A
`3/1980 Jakob
`A
`A * 8/1982 Godbersen
`
`4,929,121 A
`4,934,978 A
`5,203,388 A
`5,378,080 A
`5,383,743 A
`5,657,803 A
`5,809,985 A
`6,877,818 BI
`7,891,742 B2 *
`2004/0021364 AI
`2004/0231910 Al
`2004/0237490 Al
`2005/0016304 Al *
`
`5/1990 Lent et al.
`6/1990 Arzberger et al.
`4/1993 Bowling
`1/1995 Dickson
`1/1995 Swisher, Jr.
`8/1997 Kappel et al.
`9/1998 Kingsley et al.
`4/2005 Gaertner et al.
`2/2011 Busley et al.
`2/2004 Busley et al.
`11/2004 Mercier et al.
`12/2004 Yasuda et al.
`1/2005 Ishii et al.
`
` EO IC 23/088
`172/3
`
` 299/39.1
`
` B6OK 17/28
`74/15.4
`
`FOREIGN PATENT DOCUMENTS
`
`CN
`DE
`DE
`DE
`DE
`EP
`EP
`EP
`WO
`
`1143919 A
`2331588 Al
`3149768 Al
`10031195 Cl
`10300745 Al
`0080831 Al
`305658 Al
`1875004 Bl
`WO-0201005 Al *
`
`2/1997
`1/1975
`6/1983
`1/2002
`7/2004
`6/1983
`3/1989
`7/2010
`1/2002
`
`.......
`
`EOIC 23/088
`
`OTHER PUBLICATIONS
`
`English translation of DE-3149768-Al accessed at <http://
`translationportal .epo .org/emtp/translate/?ACTION=descri ption-
`retrieval&COUNTRY=DE&ENGINE=google&FORMAT -docdb
`&KIND- A 1 &LOC ALE- en_EP&NUMBER- 3149768&OPS- ops.
`epo.org/3.2&SRCLANG=de&TRGLANG=en>.*
`English translation of Second Brief of Catepillar (in Italian litiga-
`tion) (41 pages) (not prior art).
`Parts Manual for PM-565 dated Nov. 1999 (733 pages, uploaded in
`4 parts) (Exhibit 79).
`Parts Manual for PM-565 dated Sep. 2001 (1029 pages, uploaded in
`6 parts) (Exhibit 80).
`Operation and Maintenance Manual for PM-565 dated Jan. 1995
`(152 pages) (Exhibit 81).
`Technical Presentation (STMG) for PM-565 dated Aug. 1993 (182
`pages, uploaded in 4 parts) (Exhibit 82).
`Excerpt from the Disassembly and Assembly: 3408 Engine Supple-
`ment manual for PM-565 dated Jun. 1993 (5 pages) (Exhibit 83).
`Excerpt from the Disassembly and Assembly: Cold Planer Machine
`Systems manual for PM-565 dated Jun. 1993 (3 pages) (Exhibit 84).
`
`Statement by Mr. Michael W. Nedra, dated Oct. 19, 2017, concern-
`ing. among other things: (i) the sale of several PM-565 cold planers
`in the period 1994-1996; and (ii) Catepillar's Corporate Procedure
`in force during the same period in relation to the supply of technical
`manuals together with each machine sold (18 pages) (Exhibit 85).
`Excerpt from Catcpillar's Corporate Procedure, Aug. 28, 1991,
`concerning the Technical Literature and Technical Information (4
`pages) (Exhibit 86).
`Catepillar's Factory Notification List. Version No. 274 of Feb. 1995
`(7 pages) (Exhibit 87).
`Catepillar's Factory Notification List, Version No. 293 of Sep. 1996
`(8 pages.) (Exhibit 88).
`Sales invoice for a PM-565 machine, Serial No. 3TK00096, dated
`Sep. 15, 1995 (1 page) (Exhibit 89).
`Shipping order for a PM-565 machine, Serial No. 3TK00105, dated
`Mar. 5, 1996 (1 page) (Exhibit 90).
`PM-565B brochure dated Aug. 1997 (8 pages) (Exhibit 91).
`PM-565B brochure dated Jul. 1998 (8 pages) (Exhibit 92).
`Parts Manual for PM-565B dated Feb. 2001 (951 pages, uploaded
`in 6 parts) (Exhibit 93).
`Operating and Maintenance Manual for PM-565B dated Apr. 2001
`(172 pages, uploaded in 4 parts) (Exhibit 94).
`Technical Presentation (STMG) for PM-565B dated Jul. 1998 (216
`pages) (Exhibit 95).
`Dissembly and Assembly Manual for PM-565B dated Oct. 2004
`(128 pages. uploaded in 4 parts) (Exhibit 96).
`Systems Operating Testing & Adjusting manual for PM-565B dated
`May 2001 (52 pages) (Exhibit 97).
`Salesgram for PM-565B dated Jun. 2001 (6 pages) (Exhibit 98).
`Product Bulletin for PM-565B dated Sep. 1997 (44 pages) (Exhibit
`99).
`Bid Specifications for PM-565B dated Oct. 1999 (2 pages) (Exhibit
`100).
`Bid Specifications for PM-565B dated Jun. 2001 (4 pages) (Exhibit
`101).
`Sale invoices of PM-565B machines dating between Jul. 25, 2001
`(Serial No. 8GS0211) and Dec. 14.2004 (Serial No. 8G50267) with
`clients name redacted for confidentiality reasons (28 pages) (Exhibit
`102).
`Excerpts from www.machinerytradeoff.com, www.machinerytrader.
`corn, www.usedmachineryfinder.com and www.mascus.co.us; online
`listings for used Caterpillar PM-565 and PM-565B machines manu-
`factured before the priority date of EP'004 (28 pages) (Exhibit 103).
`Excerpts from Catepillar's website relating to technical manuals for
`PM-565, PM-565B and PB-465 offered for sale to the public (3
`pages) (Exhibit 104).
`Statement by Mr. Dario Sansone, Product Specialist at Catepillar
`Servizi Italia S.r.l., dated Mar. 30, 2018, concerning the features of
`the PM-565 and PM-565B machines (6 pages) (Exhibit 105).
`Wirtgcn First Legal Brief (Mar. 1, 2018) (20 pages) (sec p. 9-11)
`(not prior art).
`Wirtgen First Technical Brief (Mar. 6, 2019) (122 p.) (see p. 46-51)
`(not prior art).
`CAT First Technical Brief EP 1875004 (Mar. 13, 2019) (66 pages)
`(not prior art).
`Wirtgen Second Technical Brief (Apr. 16, 2019) (127 p.) (see p.
`58-83) (not prior art).
`CAT Second Technical Brief (Apr. 18, 2019) (104 pp.) (see p.
`23-35) (not prior art).
`CAT Third Legal Brief (Apr. 23, 2018) (32 pages) (see p. 2-4) (not
`prior art).
`Wirtgen Third Legal Brief (Apr. 23, 2018) (30 pages) (seep. 15-20)
`(not prior art).
`Doc. 13—Brochures of Catepillar PM 565 Cold Planer, dated Dec.
`1992.
`Statement of Defense (in Italian litigation) (60 pages) (not prior art).
`English translation of Statement of Defense (57 pages) (not prior
`art).
`Catepillar—Doc. 32: Parts Manual PM-565 Cold Planer (25 pages)
`(Sep. 2001).
`Catepillar Parts Manual PM-465 Cold Planer, vol. 1 (Oct. 2000)
`(uploaded to EFS Web in 2 parts).
`
`WA-0014269
`
`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 4 of 13 PageID #: 25492
`
`US RE48,268 E
`Page 3
`
`(56)
`
`References Cited
`
`OTHER PUBLICATIONS
`
`Caterpillar Parts Manual PM-465 Cold Planer vol. II (Oct. 2000)
`(uploaded to EFS Web in 2 parts).
`Written Opinion of the International Searching Authority in corre-
`sponding PCT/EP2006/060907 (6 pages) (not prior art).
`CAT Third Technical Brief (Oct. 16, 2019X39 p.Xsee p. 16-22XEng-
`lish translationXnot prior art).
`Prelimary Technical Report of CTE (Dec. 23, 2019X114 p.Xsee p.
`76-90XEnglish translation) (not prior art).
`Wutgen Third Technical Brief (Oct. 15, 2019X58 p.XSee p. 27-36XEng-
`lish translationXnot prior art).
`CAT Observations To The Preliminary Report (Jan. 15, 2020X69
`p.xsee p. 48-50XEnglish translationXnot prior art).
`Final Technical Report of CTE (Mar. 27, 2020X148 p.Xsee p.
`82-90) (English translation) (not prior art).
`Wirtgen Observations To The Preliminary Report (Jan. 16, 2020X76
`p.Xsee p. 49-75XEnglish translationXnot prior art).
`Exhibit 1: Machine Design, "A second look at gearbox efficiencies",
`Jun. 20, 2002 (2 p.).
`Exhibit 3: Catalog of GMT GmbH, Nov. 2004 (138 p.) (uploaded in
`3 parts).
`Exhibit 4: Catalog of Phoenix AG, Mar. 2004 (89 p.) (uploaded in
`2 parts).
`Exhibit 5: Centaflex-A Catalog (2004X.16 p.).
`
`* cited by examiner
`
`WA-0014270
`
`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 5 of 13 PageID #: 25493
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`U.S. Patent
`
`Oct. 20, 2020
`
`Sheet 1 of 3
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`US RE48,268 E
`
`r4
`
`H
`
`V)
`H
`
`O
`4-1
`
`LL.
`
`WA-0014271
`
`

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`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 6 of 13 PageID #: 25494
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`U.S. Patent
`
`Oct. 20, 2020
`
`Sheet 2 of 3
`
`US RE48,268 E
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`22
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`22
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`Fig.2
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`Fig.3
`
`Fig.4
`
`14
`
`11
`
`18
`
`14
`
`22
`18
`2
`
`11
`
`18
`
`11
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`18
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`WA-0014272
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`

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`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 7 of 13 PageID #: 25495
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`U.S. Patent
`
`Oct. 20, 2020
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`Sheet 3 of 3
`
`US RE48,268 E
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`26
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`16
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`18
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`12
`14
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`18,
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`Fig.5
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`WA-0014273
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`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 8 of 13 PageID #: 25496
`
`US RE48,268 E
`
`1
`CONSTRUCTION MACHINE, IN
`PARTICULAR ROAD MILLING MACHINE,
`RECYCLER OR STABILIZER, AS WELL AS
`DRIVE TRAIN FOR CONSTRUCTION
`MACHINES OF THIS TYPE
`
`Matter enclosed in heavy brackets [ ] appears in the
`original patent but forms no part of this reissue specifica-
`tion; matter printed in italics indicates the additions
`made by reissue; a claim printed with strikethrough
`indicates that the claim was canceled, disclaimed, or held
`invalid by a prior post-patent action or proceeding.
`
`5
`
`10
`
`15
`
`This application is a reissue of U.S. patent application Ser.
`No. 12/985,400 filed Jan. 6, 2011, now U.S. Pat. No.
`8,408,659, which is a continuation of U.S. patent application
`Ser. No. 11/918,247 entitled "Construction Machine, In 20
`Particular Road Milling Machine, Recycler Or Stabilizer, As
`Well As Drive Train For Construction Machines Of This
`Type", of Busley et al., filed Oct. 11, 2007, now U.S. Pat.
`No. 7,891,742, which is a U.S. National Stage filing of
`PCT/EP2006/060907 having an international filing date of 25
`Mar. 21, 2006, which claims priority to DE 102005017754.9
`filed Apr. 15, 2005.
`
`BACKGROUND OF THE INVENTION
`
`30
`
`The invention concerns a construction machine, in par-
`ticular a road milling machine, a recycler or a stabilizer, as
`well as a drive train for construction machines of this type.
`Construction machines of this type are known, for
`instance, from DE 10031195 Cl. The construction machine 35
`for working ground surfaces shows a chassis that carries a
`machine frame. A working drum is driven mechanically by
`a drive train that comprises a drive engine, a pump transfer
`case, a clutch and a belt drive. The direct mechanical drive
`of the working drum, which consists of a milling drum, can 40
`be engaged or disengaged again by means of the clutch.
`The support of the drive engine must be designed in a very
`stiff manner, as this is also the support for the belt pulley of
`the belt drive on the drive side relative to the machine frame.
`It is understood that a coaxial, rigidly supported arrange- 45
`ment of the shafts connecting the elements of the drive train
`is required and that, with regard to the belt drive, a rigid,
`track-aligned arrangement of the belt pulley on the drive
`side and on the output side is a basic requirement for the
`functional pertormance and long life of such a belt drive. A so
`soft, elastic support is not feasible in particular for the reason
`that the belt pulley on the drive side is supported in a
`cantilevered manner. This means that the two supporting
`points of the support are located on one side of the belt
`pulley, with the belt pulley itself projecting freely on that 55
`side that lies opposite the support.
`Supporting the belt pulley on both sides is not desired
`because of the transport width of the machine that has to be
`adhered to. The stiff support of the drive train is disadvan-
`tageous in that vibrations from the drive engine are trans- 60
`mined to the machine frame to a greater extent. The vibra-
`tions are not only unpleasant for the machine operator, in the
`form of the vibrations transmitted to him, but impair the
`working conditions because larger flat machine components
`like, for instance, hoods or tanks, are stimulated to sound 65
`vibrations that are disturbing during the operation of the
`machine.
`
`2
`The effort to increase the performance results in an
`increased space requirement for the drive engine that needs
`to be accommodated within the pre-determined fixed trans-
`port width.
`
`SUMMARY OF THE INVENTION
`
`The purpose of the invention is, therefore, to further
`develop a construction machine of the type first mentioned
`above, as well as a drive train for construction machines of
`that type, in such a manner that less vibrations from the drive
`engine are transmitted to the machine frame, with the drive
`train being sufficiently rigid at the same time to be capable
`of transmitting high mechanical power.
`The invention provides in an advantageous manner that
`the elements of the drive train are divided into at least two
`groups, that the first group shows, i.e. includes, at least the
`drive engine, the second group shows at least the drive
`element of the traction mechanism. and that the first and the
`second group are connected to one another via an articulated
`coupling device. Dividing the drive train into two groups
`makes it possible to support the groups of the drive train
`with different degrees of rigidity on the machine frame for
`the purpose of reducing the transmission of vibrations from
`the drive engine to the machine frame. The articulated
`coupling device between the first and the second group is
`capable of balancing the different vibrational behavior of the
`first group and the second group due to its articulation,
`without impeding a high transmission of power.
`In conclusion, this means that the support of the combus-
`tion engine, possibly with further elements of the drive train,
`in the first group may be considerably softer than the support
`of the elements of the drive train accommodated in the
`second group, which are to be attached to the machine frame
`in an as stiff manner as possible or in a rigid manner.
`The first group with the drive engine is attached to the
`machine frame elastically with low spring stiffness that
`damps the vibrations from the drive engine for the purpose
`of reducing the transmission of vibrations to the machine
`frame, and the second group is attached to the machine
`frame with high spring stiffness or in a rigid manner.
`Dividing the drive train into two groups makes it possible
`to achieve in an advantageous manner that, on the one hand,
`the one group that comprises the drive engine, preferably a
`combustion engine, is supported in a relatively soft manner
`at the machine frame, by way of which the vibrations from
`the drive engine that are transmitted to the machine frame
`are damped considerably, and that, on the other hand, the
`other group can be supported at the machine frame with high
`spring stiffness in a nearly rigid or rigid manner, by way of
`which higher forces are supported and higher outputs are
`transmittable as a result. In doing so, the first and the second
`group, which are attached to the machine frame with dif-
`ferent degrees of rigidity, are connected to one another via
`an articulated coupling device so that a slight dynamic axle
`offset and/or angular error of the output shaft of the first
`group with the drive engine is permissible vis-à-vis the drive
`shaft of the second group.
`In a preferred embodiment, it is provided that the first
`group comprises at least the drive engine and the device for
`driving at least one hydraulic pump, and the second group
`comprises the device for switching the torque and/or the
`support of a drive element of the traction mechanism on the
`drive side, preferably a belt drive. In this embodiment, the
`drive engine is coupled in a rigid manner with the device for
`
`WA-0014274
`
`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 9 of 13 PageID #: 25497
`
`US RE48,268 E
`
`25
`
`3
`driving the at least one hydraulic pump, and is supported
`together with that device elastically vis-a-vis the machine
`frame.
`The second group shows the device for switching the
`torque, by means of which the power flow can be inter- 5
`rupted, and/or the support of the drive element of the traction
`mechanism on the drive side. This second group may be
`attached to the machine frame in a rigid or at least nearly
`rigid manner.
`This embodiment offers the advantage that the device for to
`driving the at least one hydraulic pump, which also gener-
`ates vibrations, can be supported together with the drive
`engine, preferably a combustion engine, in a soft manner in
`the first group of the drive train. This embodiment offers the
`additional advantage that, in spite of the drive train for the 15
`milling drum being disengaged, the hydraulic supply of the
`machine is ensured when the drive engine is running. Those
`elements of the drive train, however, that generate only
`slight vibrations are combined in the second group.
`In accordance with an alternative embodiment, it may be zo
`provided that the first group comprises at least the drive
`engine and the device for switching the torque, and the
`second group comprises the device for driving at least one
`hydraulic pump and/or the support of a drive element of the
`traction mechanism on the drive side.
`In accordance with yet another alternative embodiment, it
`is provided that the first group comprises at least the drive
`engine, and the second group comprises the device for
`driving the at least one hydraulic pump, as well as the device
`for switching the torque and/or the support of the drive 30
`element of the traction mechanism on the drive side.
`The articulated coupling device may be torsionally rigid.
`The articulated coupling device may, for instance, be a
`cardan shaft. Alternatively, the articulated coupling device
`may also be torsionally flexible and may, for instance, be an 35
`elastomeric coupling.
`The device for driving the at least one hydraulic pump and
`the device for switching the torque, as well as the support of
`the drive element of the traction mechanism on the drive side
`may form an entity that is jointly attached to the machine 40
`frame with high spring stiffness or in a rigid manner.
`The device for driving the at least one hydraulic pump
`may consist of a pump transfer case for several hydraulic
`pumps.
`The device for switching the torque is preferably arranged 45
`between the device for driving the at least one hydraulic
`pump and the drive element of the traction mechanism on
`the drive side.
`The transfer casing may show a gearbox casing with
`several hydraulic pumps arranged at an outer circumference so
`of the gearbox casing, the said hydraulic pumps being
`capable of being jointly driven by means of the transfer case.
`The hydraulic pumps project from the gearbox casing,
`pointing towards the drive engine or pointing away from the
`drive engine. The coupling device extends in the interior 55
`space of the gearbox casing that is free from hydraulic
`pumps. The arrangement of the coupling device in the free
`interior space of the gearbox casing enables a compact
`design.
`In a preferred embodiment, it is provided that the coupling 60
`device permanently couples an output shaft of the drive
`engine with an input shaft of the device for driving the at
`least one hydraulic pump and/or an input shaft of the device
`for switching the torque. The arrangement of the coupling
`device in the radially inner intermediate space of the gear- 65
`box casing, which is free from hydraulic pumps, enables a
`compact design of the drive train, both in that case in which
`
`4
`the transfer case is a part of the first group, in which the
`hydraulic pumps point away from the drive engine, as well
`as in that case in which the transfer case forms the input
`element of the second group, in which the hydraulic pumps
`project in the direction of the drive engine.
`The coupling device permanently couples an output shaft
`of the drive engine, or of the first group, with an input shaft
`of the device for driving the at least one hydraulic pump, or
`an input shaft of the device for switching the torque, or of
`the second group.
`
`BRIEF DESCRIPTION OF THE DRAWINGS
`
`In the following, embodiments of the invention are
`explained in more detail with reference to the drawings. The
`following is shown:
`FIG. 1 a first embodiment of the invention in the example
`of a road milling machine,
`FIG. 2 a second embodiment,
`FIG. 3 a third embodiment,
`FIG. 4 a fourth embodiment, and
`FIG. 5 a side view of the embodiment in FIG. 4.
`FIG. 1 shows a schematic cross-section of a construction
`machine, and namely in particular a road milling machine,
`a recycler or a stabilizer with a working drum 6 that is
`supported in a machine frame 4. Alternatively, the working
`drum 6 may be supported in a drum housing that is in turn
`firmly attached to the machine frame or may also be sup-
`ported to pivot at a machine frame 4. The machine frame 4
`is carried by a chassis that is not depicted in the drawings.
`The working drum 6 may consist of, for instance, a milling
`drum. The working drum 6 of the construction machine is
`driven by a drive train 8 that shows at least the following
`elements:
`The drive train 8 includes a drive engine 10 that prefer-
`ably consists of a combustion engine.
`A traction mechanism 12 for the mechanical drive of the
`working drum 6 shows a drive element 11 that is coupled in
`a non-rotatable manner with an output shaft 17, and an
`output clement 13 that is coupled in a non-rotatable manner
`with the drive shaft 15 of the working drum 6. A planetary
`gear may additionally be arranged between the drive shaft
`15 and the working drum 6.
`The traction mechanism 12 preferably is a belt drive
`where the drive and output elements 11, 13 consist of belt
`pulleys, with several drive belts 30 revolving around the said
`belt pulleys. Alternatively, the traction mechanism 12 may
`also consist of a chain drive, where the drive and output
`elements 11, 13 then consist of the corresponding sprockets.
`The drive train 8 further shows a device for switching the
`torque 14, which is arranged in the drive train 8 between the
`drive engine 10 and the working drum 6 and preferably
`consists of a clutch.
`The drive train 8 further includes a device 16 for driving
`hydraulic units, for instance, hydraulic pumps 18. where the
`said device 16 for driving hydraulic units is coupled with the
`drive engine 10.
`The entire drive train 8 is divided into at least two groups,
`with the first group showing at least the drive engine 10 and
`the second group showing at least the drive element 11 of the
`traction mechanism 12. The first and the second groups 3, 5
`are connected to one another mechanically via an articulated
`coupling device 20. The articulated coupling device 20
`transmits the power supplied by a not depicted output shaft
`of the drive engine 10 to the second group 5 of the drive train
`8.
`
`WA-0014275
`
`

`

`Case 1:17-cv-00770-JDW Document 250-6 Filed 10/25/23 Page 10 of 13 PageID #: 25498
`
`US RE48,268 E
`
`5
`In FIG. 1, the first group comprises the combustion engine
`10 only, which is coupled with the second group 5 via the
`coupling device 20. In the embodiment of FIG. 1. the second
`group 5 comprises the device 16 for driving at least one
`hydraulic pump 18, namely a pump transfer case, the clutch
`14 and the belt pulley 11 of the belt drive 12.
`The combustion engine 10 is attached to the machine
`frame 4 by means of elastic spring/damping elements 22
`showing low spring stiffness, in such a manner that the
`vibrations occurring in particular in a combustion engine 10,
`as well as structure-borne sound, are transmitted to the
`machine frame 4 to the smallest possible extent.
`The second group 5, on the other hand, is attached to the
`machine frame 4 by means of spring/damping elements 24
`showing high spring stillness, so that the second group 5 is
`attached to the machine frame 4 in a nearly rigid manner.
`The different manner of support or attachment of the first
`and the second groups 3, 5 of the drive train 8 has the effect
`that, when in operation, the not depicted output shaft of the
`combustion engine 10 is not permanently in precise align-
`ment with the also not depicted input shaft of the pump
`transfer case 16, with the articulated coupling device 20
`balancing the dynamic misalignment occurring during
`operation without the flow of power in the drive train 8 being
`disturbed.
`As shown in FIGS. 1 and 5 the working drum 6 has a drum
`rotational axis which is the rotational axis of shaft 15. As
`also shown in FIGS. 1 and 5 the driven pulley 13 is also
`mounted on the shaft 15 and thus has a driven pulley
`rotational axis which is parallel and co-axial with the
`rotational axes of the working drum 6 and the shaft 15. As
`shown in FIGS. 1 and 5 the drive pulley 11 has a drive pulley
`rotational axis which is the rotational axis of the shaft 17 on
`which the drive pulley is mounted. As furthershown in FIGS.
`1 and 5 the drive pulley 11 and the driven pulley 13 are
`aligned with each other in the direction that the drive belts
`30 extend, and the rotational axes of the drive pulley 11 and
`the driven pulley 13 are parallel to each other. And as is
`shown in FIG. 1 an output axis of the drive engine 10 is
`aligned with an input axis of the hydraulic pump drive
`device 16 and with an input axis of the drive pulley 11 prior
`to operation of the construction machine. The articulated
`coupling device 20 accommodates a lack of precise align-
`ment between the output axis of the drive engine 10 and the
`input axes of the hydraulic pump drive device 16 and the
`drive pulley 11 due to dynamic movement ofthe drive engine
`10 relative to the second group 5 during operation of the
`construction machine.
`Dividing the drive train and supporting the components of
`the drive train 8 in a different manner achieves that consid-
`erably less vibrations are transmitted from the combustion
`engine 10 to the machine frame 4. lu this way, it is further
`prevented that larger flat machine components are stimu-
`lated to sound vibrations that are disturbing during the
`operation of the machine.
`The articulated coupling device 20 may be torsionally
`rigid, and may consist of a cardan shall.
`Alternatively, the articulated coupling device 20 may also
`be torsionally flexible, where the coupling device then
`consists of an elastomeric coupling.
`FIG. 2 shows a second embodiment, in which the first
`group 3 comprises the combustion engine 10 and the pump
`transfer case 16. As in the embodiment of FIG. 1, the pump
`transfer case 16 shows several hydraulic pumps 18 that
`axially project from the gearbox casing 26 of the pump
`transfer case 16, preferably in a circumferentially uniformly
`distributed manner.
`
`6
`A spur gear is arranged inside the pump transfer case,
`which jointly drives the individual hydraulic pumps. The
`arrangement of the hydraulic pumps 18 results in a central
`free interior space 28 between the hydraulic pumps 18, in
`5 which the coupling device 20 may extend which serves to
`connect the first and the second groups 3, 5 of the drive train
`8. This design of the pump transfer case 16 with a free
`interior space 28 enables the available space for arranging
`the drive train 8 across the width of the machine to be used
`10 in a better way, so that a more powerful combustion engine
`10 can be used due to the space-saving arrangement of the
`components of the drive train 8.
`In the embodiment of FIG. 2, the pump transfer case 16
`15 is also included in the first group, so that vibrations that
`might be coming from the pump transfer case can also be
`absorbed by the spring/damping [element] elements 22.
`The second group 5 is formed by the clutch 14 and the belt
`pulley 11 of the belt drive 12. By means of the coupling
`20 device 20, the power of the combustion engine is first
`transmitted to the clutch 14 and then to the belt pulley 11.
`As shown in FIG. 2 an output axis of the drive engine 10
`is aligned with an input axis of the clutch 14 and with an
`input axis of the drive pulley 11 prior to operation of the
`25 construction machine. The articulated coupling device 20
`accommodates a lack of precise alignment between the
`output axis of the drive engine 10 and the input axes of the
`clutch 14 and the drive pulley 11 due to dynamic movement
`of the drive engine 10 relative to the second group 5 during
`30 operation of the construction machine.
`Insofar as the drive belts 30 and the second belt pulley 13,
`which serves as output element, are also part of the drive
`train 8, it is to be stated that these are also supported rigidly
`vis-à-vis the machine frame 4, namely in that the second belt
`35 pulley 13 is arranged on the drive shaft 15 of the working
`drum 6.
`In a further, not depicted variant of the embodiment of
`FIG. 2, the pump transfer case 16 may be arranged on that
`side of the combustion engine 10 that lies opposite the
`40 coupling device 20, so that in this case the combustion
`engine 10 and the pump transfer case 16 also form the first
`group 3 of the drive train. This embodiment is advantageous
`when a good accessibility of the components of the drive
`train 8 is desired.
`In the embodiment of FIG. 3, the first group 3 of the drive
`train comprises the combustion engine 10 and the clutch 14.
`This embodiment also offers the advantage of a good usabil-
`ity of the available width of the machine frame 4.
`FIGS. 4 and 5 show an embodiment in which the first
`so group 3 of the drive train 8 is fonned by the combustion
`engine 10 that is coupled with the pump transfer case 16 via
`the coupling device 20. With the belt pulley 11 of the belt
`drive 12, the pump transfer case 16 forms the second group
`5 of the drive train 8. which is supported on the machine
`55 frame 4 in a rigid or nearly rigid manner.
`As can be seen from FIG. 5, the pump transfer case 16
`shows, for instance, six