US3921836A

US3921836A - Articulated hydraulic travelling loader

Info

Publication number: US3921836A
Application number: US411811A
Authority: US
Inventors: Zenon Wyslouch; Eugeniusz Brachmanski
Original assignee: MASZYN BUDOWLANYCH FADROMA PO1
Current assignee: FABRYKA MASZYN BUDOWLANYCH 'FADROMA'PO19721104158617; MASZYN BUDOWLANYCH FADROMA PO1
Priority date: 1972-11-04
Filing date: 1973-11-01
Publication date: 1975-11-25
Anticipated expiration: 1992-11-25
Also published as: DE2354850A1; JPS504719A; DE7339250U; GB1434821A; PL74598B2; FR2205910A7

Abstract

In heavy-duty hydraulic loaders, the employing of a common internal combustion engine for driving the traversing gear of the machine, and the hydraulic pumps of the working system of the machine is disadvantageous for constructional and operational reasons. In the design according to the invention, two separate internal combustion engines are employed, the one of which drives exclusively the traversing gears of the loader chassis, the other one drives the hydraulic pumps of the working system, and the auxiliaries. The engine driving the hydraulic pumps is situated on the front part of the articulated frame of the loader. The traversing gears and the engine driving them are situated on the rear part of the loader chassis. It is preferable to arrange the engine driving the pumps, behind the driver''s cab, transversely to the longitudinal axis of the machine, above the articulated joint of the frame.

Description

United States Patent 1 1 Wyslouch et al.

[ 1 Nov. 25, 1975 1 1 ARTICULATED HYDRAULIC TRAVELLING LOADER [75] Inventors: Zenon Wyslouch; Eugeniusz Brachmanski, both of Wroclaw, Poland [73] Assignee: Fabryka Maszyn Budowlanych Fadroma, Wroclaw, Poland [22] Filed: Nov. 1, 1973 211 App1.No.:4ll,81l

[30] Foreign Application Priority Data Nov. 4, 1972 Poland 158617 [52] US. Cl 214/142; 180/51 [51] Int. Cl. B601 1/16 [58] Field of Search 180/51, 14 R, 14 A, 12, 180/11, 53 R 66 R; 214/142 [56] References Cited UNlTED STATES PATENTS 1,862,999 6/1932 Ball 180/53 R 2,689,621 9/1954 Donley..... 180/53 R 3,305,039 2/1967 Molby 180/51 3,334,702 8/1967 Granryd... 180/11 X 3,349,932 10/1967 Wagner 180/51 X l/1968 Salna et al. 180/51 7/1970 Korotkin 1140/66 R X Primary Examiner-Kenneth H. Betts Attorney, Agent, or Firm-Haseltine, Lake & Waters [57] ABSTRACT In heavy-duty hydraulic loaders, the employing of a common internal combustion engine for driving the traversing gear of the machine, and the hydraulic pumps of the working system of the machine is disadvantageous for constructional and operational reasons. In the design according to the invention, two separate internal combustion engines are employed, the one of which drives exclusively the traversing gears of the loader chassis, the other one drives the hydraulic pumps of the working systems, and the auxiliaries.

The engine driving the hydraulic pumps is situated on ,the front part of the articulated frame of the loader.

The traversing gears and the engine driving them are situated on the rear part of the loader chassis.

It is preferable to arrange the engine driving the pumps, behind the drivers cab, transversely to the longitudinal axis-of the machine, above the articulated joint of the frame.

3 Claims, 2 Drawing Figures U.S. Patent Nov. 25, 1975 ARTICULA'IIEILHYDRAULIC TRAVELLING r LOADER The invention relates to a hydraulic'bucket'loader mounted on a:.wheeled chassis;:t-he frame of which consists of two parts connected with-an articulated joint.

There are knowntwheeled hydraulic loaders in which the traversing gear-and the hydraulic system actuating the working unit are driven by a common internalcombustion engine.

The trend to increase the performance of loaders entails the necessity of to mount hydraulic systems showing larger and largerfpowerrequirements: In modern loaders the power consumed by the pumps of the hydraulic system exceeds in some phases oftheworking cycle 50% of the entire power rating of the driving engine of the machine. The'peak power requirement of the hydraulic system occurs during shoveling the excavated material, connecting with cutting it. Simultaneously the highest power consumption by the traversing gear of the machine occurs. That results therefrom that the cutting of the ground and taking the excavated material to the bucket occurs during the travel of theentire machine forward.

The phenomenon described above causes a necessity of to mount for the loader driving engines much more powerful as it would result from the power requirement for the traversing drive of the machine. In consequence thereof the engines of known loaders operate in most cases under disadvantageous conditions. On one hand, at long travels of the machine the traversing gear consumes only a dozen or so percents of the engine rated power, and on the other hand at the time of taking up the excavated material, when the power consumption by the hydraulic system rapidly increases, the power requirement for the traversing drive increases too. That leads in the consequence to an overloading of the engine. In both cases the engines operate with insufficient performance.

Moreover, the application of engines having the power rating higher than the power requirements of the traversing gear entails a necessity of a re-dimensioning of said units. The gearboxes, the torque converters, and the driving axles of known loaders must be calculated with taking such excess power into account, and that causes an increase of their dimensions and weights, thus also of manufacturing and operating costs of the machine.

The object of the invention is to eliminate the disadvantages of known loaders, as described hereinabove, and the task leading thereto consists in providing a mutually independent operation of both systems of the machine: the hydraulic working system and the traversing gear.

According to the invention said object is achieved by employing separate internal combustion engines for driving the working system, and the traversing gear.

Namely, on the rear part of the articulated frame of the loader the engine is mounted, driving the traversing gear of the machine, and its auxiliary systems as the steering and the braking system the working system of the machine, actuated by means of hydraulic servomotors however is driven by an other engine mounted on the front part of the frame behind the drivers cab and above the articulated joint.

This engine, differently as the former'one, is-prefera- -bly mounted transversely to the direction of travel of the machine.

The fundamental advantage of the specified design is the possibility of proper matching the .power of the en- ,gines, to, the specific operating conditions of both systems. The smaller engine of the traversing drive can in such a case work for a longer time with high utilization of the loading rating, but without overloading resulting from. the temporary high .power requirement of the pumps of the hydraulic system. The engine driving the working system canhowever develop a considerable power at the time of the peak power requirement, and during longer travels of the, machinelsaid engine may be stoppedatall. 7 K,

, In theconsequence, both engines operate within the range of better performances, are more economical,

tions into the traversing gear drive. When smaller en gines are amployed, the proper selection of them is more simple, owing to narrower ranges of the power ratings of subsequent uni'ts.

Moreover, the application of two separate engines admits to design the loaders more advantageously,The loadings of the front and the rear axle of the machine can be better distributed, what significantly influes on the tractive properties.

It is of particular significance in heaviest machines, where a very great engine is mounted behind the rear axle of the loader.

Further, the arranging of the working system engine on the front part of the articulated frame of the loader admits to simplify the supplying of the working medium from the pumps to the distributors and servo-motors. In known designs the oil must be fed from the rear part of the frame by means of long flexible conduits or rotary connectors, if the pumps are arranged near to the engine, or it is necessary to transmit the drive from the rear part of the machine to'the front one, where the pumps are mounted. In the design according to the invention the hydraulic system is more simple, and the conduits are more compact, what increases the performance and the reliability of the system.

The subject of the invention is shown by the way of an exemplary embodiment in the accompanying drawing, where 1 FIG. 1 is the longitudinal sectional view, and

FIG. 2 is the top view ofthe' loader according to the invention.

As shown in the drawing, the machine is provided with a frame composed of two parts, the front part 1 being connected with the rear part 2 by means of an articulated joint 3.

On the front part of the chassis the working system 4 is mounted, and the drivers cab 5, behind which the internal combustion engine 6 is situated, driving the hydraulic pumps of the working system 4.

On the rear part 2 of the chassis the internal combustion engine 7 is situated, driving the traversing gears of the loader: the torque converter, the gear box 9, and

the driving axles 10.

3,921,836 3 4 What is claimed is: g. a second prime mover operable independently of 1. A self-propelled articulated loading machine vsaid first prime mover mounted on said second which comprises: frame section behind said rear axle and drivably a. first and second frame sections; connected to at least one of said front and rear b. an articulated joint interposed between and con- 5 axles; and

necting said frame sections to permit relative h. first and second control systems connected respecmovement therebetween; tively to said first and second prime movers. c. front and rear wheel-bearing axles mounted re- 2. An articulated loading machine as defined in claim spectively on said first and second frame sections; 1, wherein said second prime mover has a power rating d. a hydraulically operable jib and loader mechanism sufficient to provide tractive power for said machine carried by said first frame section; during all phases of the work cycle, such power rating e. a drivers cab carried by said first frame section; being less than the power rating of said first prime f. a first prime mover mounted on said first frame secmover.

tion behind said driver's cab located a predeterl5 3. An articulated loading machine as defined in claim mined distance behind said front axle such that it 2, wherein said first prime mover is mounted on said serves as a counterweight for said jib and loader first frame section transverse of the longitudinal axis of mechanism, said first prime mover being drivably the machine and vertically above said articulated joint. connected to said jib and loader mechanism;

Claims

1. A self-propelled articulated loading machine which comprises: a. first and second frame sections; b. an articulated joint interposed between and connecting said frame sections to permit relative movement therebetween; c. front and rear wheel-bearing axles mounted respectively on said first and second frame sections; d. a hydraulically operable jib and loader mechanism carried by said first frame section; e. a driver''s cab carried by said first frame section; f. a first prime mover mounted on said first frame section behind said driver''s cab located a predetermined distance behind said front axle such that it serves as a counterweight for said jib and loader mechanism, said first prime mover being drivably connected to said jib and loader mechanism; g. a second prime mover operable independently of said first prime mover mounted on said second frame section behind said rear axle and drivably connected to at least one of said front and rear axles; and h. first and second control systems connected respectively to said first and second prime movers.

2. An articulated loading machine as defined in claim 1, wherein said second prime mover has a power rating sufficient to provide tractive power for said machine during all phases of the work cycle, such power rating being less than the power rating of said first prime mover.

3. An articulated loading machine as defined in claim 2, wherein said first prime mover is mounted on said first frame section transverse of the longitudinal axis of the machine and vertically above said articulated joint.