FI88381B - Power transmission and steering arrangement for vehicles - Google Patents

Description

88381

This invention relates to a transmission and steering arrangement: for vehicles, in particular for vehicles equipped with rollers or reversible wheels.

In the past, in track or wheel vehicles, the turning of which is effected by a difference in speed between the right and left wheels / rollers, various arrangements are known for obtaining said speed difference. Butter-. . be used to the full hydrostatic transmission, wherein the right / left wheels / telo, and each driven by '·' · one's own hydraulic motor, which again both rotated in their own variable pump. Such an initially expensive arrangement becomes even more disadvantageous if a moderately good traction peak speed combination is achieved.

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A conventional clutch / brake arrangement in connection with a conventional differential is still known. This arrangement causes large power losses and is not suitable for relatively light and fast vehicles due to its inaccuracy. Efforts have been made to remedy the poor characteristics of the clutch / brake arrangement by equipping a special control gearbox with which several fixed radii of curvature can be selected. The features of such an arrangement in no way meet the requirements of accurate, fast driving, despite their complexity and high cost.

In addition, a mechanical variator connecting the drive shafts can be used in connection with the differential, whereby the rotational speeds of the drive shafts with respect to one another can be continuously adjusted. However, such an arrangement does not operate at zero speed, and moreover, the high torque necessarily acting on the drive shafts requires a very heavy variator structure.

Accordingly, it is an object of the present invention to provide a skid-steer vehicle with a transmission and steering arrangement in which the above-mentioned shortcomings are eliminated.

The invention therefore provides a very compact, light and inexpensive steering / transmission arrangement, which allows completely precise and automatic steering and also allows the vehicle to turn in place. Furthermore, the arrangement according to the invention makes it possible to make full use of the power of the main power source (e.g. an internal combustion engine) at all speeds, a. Read on for the best transmission technology.

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Other advantages and features of the invention will become apparent from the following detailed description and claims.

The invention is described in more detail below with reference to the accompanying figures, in which:

Figure 1 shows in general an exemplary vehicle equipped with a transmission and steering arrangement according to the invention.

Figure 2 shows a section in the direction of the drive axes from the application of the arrangement according to the invention in the direction of arrows 2-2 in Figure 3.

Figure 3 outlines the mutual position of the input shafts of an embodiment of the arrangement according to the invention.

Figure 4 shows a detail of an embodiment of the arrangement according to the invention, viewed in the direction of arrows 4-4 in Figure 2.

Figure 5 shows an end view of the transverse axis included in the arrangement.

In Fig. 1, the number 1 denotes an internal combustion engine, the rotational movement of which is transmitted via a conventional clutch 2 and a gearbox 3 to a cardan shaft 4 connected to a transmission / control system according to the invention (hereinafter The steering gear) to the input flange 5, which also rotates the input bevel gear 7 on the bearing shaft 6. This rotates the main sprocket 9 attached to the main shaft 8, whereby the main shaft 8 rotates naturally as the shaft 6 rotates as determined by the center ratio of the wheels 7, 9. The outer bevel gears 12 of the epicyclic parts of the steering gear 12 are fixed to the outer ends 11 by means of a shaft 8. -thio gear wheel, hereinafter with a ring gear 14 In this embodiment, two ring gears 14 are mounted on a transverse shaft 15, through the central part of which the main shaft 8 passes and which (15) is fixed at its ends (in this application by screws 16) to the housing part 13. The ring gears 14 are in tooth contact with the inner (center line 10) bevel gear 18 of the epicyclic part. with. In the described embodiment, the structure of the bevel gear 18 extends outwards with respect to the center line 17 and inwards with respect to the center line 10 towards said center line 10 so that a conical guide plate wheel 19 is formed on the outer circumference. in both directions of rotation. In the illustrated embodiment, the gear wheel 21 is mounted directly on the shaft 22 of the hydraulic motor 20 for simplicity. In fact, only the main flywheel 9 is a part which has no counterpart on the other side of the center line 10 (and this affects, of course, a small number of the structure of the main axle 8).

In order to provide a compact structure, i.e. low weight and low cost, as well as good off-road capability for the vehicle itself, the bevel gear 18 and the steering wheel 19 are formed in one embodiment from one and the same blank. This is by no means necessary for the idea of the invention; after all, the toothing of the bevel gear 18 in the axial direction 8 can be brought somewhat even closer to the toothing of the rack 19, so that it is not even possible to make teeth sensibly in one and the same blank material; , brazing, grooving, etc. in a suitable manner.

It can also be seen from Figure 2 (cf. the requirement of compactness) that the main shaft 8 is mounted by bearings 24 on the rotating parts per se, i.e. the gear assembly 18, 19. The bearings 24 can be of such a type that they are able to absorb the axial 8 loads themselves. in addition to the radial loads, or in the area 25 a special thrust bearing must be provided between the wheels 18, 19 and 9. The radial loads on the shaft 8 are finally transferred to the outermost radial bearings 26, which rest on a fixed outer shell 27. The radial bearings 26 also mount the gear assemblies 18, 19 in the outer shell 27. by means of bearings 28 to the shell parts 13, the outer ends 29 (with respect to the center line 10) of which are so mounted (in the illustrated embodiment by the angular contact ball bearings 30) that they can transmit said axial loads on the conical portions 31 of the outer shell. The shell portions 13 are mounted at their inner ends (relative to the centerline 10) by radial bearings 32 on the outer shell 27.

The axial loads on the ring gears 14 are received: Y: by the pressure bearings 33, and likewise the axial loads on the gears 12 V are received by the pressure bearings 34.

Let us now consider the method of operation of the control gear according to the invention. The gear ratio 7 · 9 of the gears 7, 9 is denoted by the value i ^ so that when the input shaft 6 rotates at a speed n, the gears 12 rotate at a speed n, in.

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The epicyclic parts in the steering gear cause the shell parts 13 and the drive shafts 35 attached to these ends to rotate at a speed of ns.i ^ / 2.

The gear ratio of the gears 21, 19 is further denoted by ig so that when the gear on the shaft 22 rotates at a speed nQ, the gears 19 (and thus the gears 18) rotate at a speed nQ.ig, but in different directions. Assuming that the shaft 6 (and thus the shaft 8) is not rotated, the drive shafts 35 rotate under the influence of the epicyclic parts at a speed of n 1/2, and in different directions. When the shaft 6 rotates simultaneously with the rotation of the shaft 22, the drive shafts rotate at a speed 35:

One (n + and the other (n ^ i- ^ - no.i2) / 2

Since the speed and direction of rotation of the hydraulic motor 20 can be infinitely adjusted by means of a continuously adjustable hydraulic pump 36 (the steering wheel of the vehicle acts on the lever 37 on the control shaft of the pump 36), a fully automatic control is thus obtained. If the pump 36 is mounted in such a way that it also rotates when the gearbox 3 is in the neutral position, the vehicle can be turned completely in place while the drive shafts 35 rotate in different directions.

Claims (2)

1. Power transmission and steering arrangements for vehicles in which the arrangement of the main power source is transmitted via the clutch and the transmission to an input shaft (6) whose tapered input gears (7) rotate the main shaft (8) main shaft (8) of the main shaft (8) , while said relative reduction ratio Sr (i) of said wheel such that when the input shaft (6) rotates at a speed (ns) is the rotational speed (ng.ii) of the main shaft, characterized by the fact that tapered gears (12) on the outermost shaft (8) ends (11) star in gear with two or more peripheral wheels (14) arranged on the main shaft (8) transverse-axis (15) through whose center portions the main shaft (8) passes, which peripheral wheels (14) star in gear relative to the input shaft (6) inner tapered gears (18), the latter (18) forming a unitary unit with, relative to the input shaft (6) even further located and relative to the shaft (8) with regard to the main disc wheel (9) outer steering disc wheels (19), which latter (19) are in gear with a shaft (22) arranged on the shaft (8) of the hydraulic motor (20), arranged conical gear (21) with a reduction gear. the ratio (i2) such that as the shaft rotates with the speed (ng), the rotational speed (nQ.i2) is the rotational speed (nQ ng.i2) / 2 and (¾. ^ - nQ.i2) / 2, when the hydraulic motor (20) can be driven by a continuously adjustable hydraulic pump (36) in both directions. 1. yes Voimansiirto- ohjausjärjestely ajoneuvoja varten, jossa järjestelyssä päävoimanlähteen liike välitetään kytkimen yes vaihdelaatikon kautta sisääntuloakselille (6), jonka Si sääntulokartiohammaspyörä (7) pyörittää sisääntuloakselin suhteen poikittaisen pääakselin (8) päälautaspyörää (9), mainittujen pyörien keskinäisen välityssuhteen ollessa (in ^) the site, one sisääntuloakselin (6) pyöriessä nopeudella (na) »on pääakselin (8) pyörimisnopeus (ng.i- ^), thin ttu siitä, one pääaksselin (8) ulommaisissa päissä (11) olevat kartiohammaspyöret (12) pääakselin (8) suhteen poikittaisille akseleille (15), joiden keskiosien läpi pääakseli (8) kulkee, järjestetyn kahden tai useamman kehäpyörän (14) odds, mainittujen kehäpyörien (14) ollessa hammaskosketuksessa säisu viimeksi mainitut (18) muodostavat yhtenäisen kokonaisuuden sisääntul oakselin (6) suhteen vieläkin sisempien ja akselin (8) suhteen päälautaspyörään (9) proximity ulompien ohjauslautaspyörien (19) odds, viimeksi mainittujen (19) ollessa hammaskosketuks-: sa hydraulimoottorin (20) suunnassa pääksselin (8) suhteen, olevan kartiohammas-pyörän (21) chance velocitysshteella (12) site, one axle. ···. (22) pyöriessä nopeudella (n ^), on hammaspyörien (18) pyöri- misnopeus (nQ.12), jolloin akseleihin (15) kiinnitettyihin; ; (16) choriocyanine (13) chiinnityt vetoaxselite (35) pyörivät * · * · * nopeuksilla (ng.i ^ + n0. I2) / 2 ja (ns · i2) / 2, only hydraulicotoria (20) voidaan pyörittää molempiin suuntiin por -:. ** in taattomasti séädettävällä hydraulipumpulla (36). . ···. 2. Patent tivaatimuksen 1 mukainen voimansiirto- ja ohjaus- • · ·, ···. järjestely, tunnettu siitä, etä hyd ra ui i pumppu (36) on the site asennettu, että se voi pyöriä myös vaihde-: laatikon (3) ollessa vapaa-asennossa. 8 88381 Power transmission and steering arrangement according to claim 1, characterized in that the hydraulic pump (36) is mounted so that it can also rotate when the gearbox (3) is in the off position.