FR2486588A1 - INTERNAL COMBUSTION ENGINE WITH FIVE CYLINDERS IN LINE, EQUIPPED WITH A BALANCING SHAFT - Google Patents

Abstract

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

Description

I

  The present invention relates to a combustion engine

  internal five-cylinder in-line bustion of which the city

  brequin has staggered crank pins in order

  1 - 3 - 5 - 4 - 2 and which, together with the

  crankshaft, a balancing shaft rotating at the same speed and in the opposite direction of the crankshaft whose balancing masses are arranged in the region of the terminal planes of the crankshaft. On a system of this category known from the patent application filed in the Federal Republic of Germany DE-PS 1 142 727, the second-order mass moments occurring during the operation of the engine are considerably reduced by the particular offset crank pin crankshaft. he

  It is possible to compensate for the mass

  first order by a single balance shaft. For this purpose, the balancing masses are preferably arranged in the region of the end planes of the crankshaft. The

  important distance reserved between the masses of balance

  brage provides sufficient balancing torques even

  when the balancing weights are of reduced dimensions

  you, so light. On the other hand, the stepwise assembly of the balancer shaft, which is long and subjected to high bending moments, becomes more difficult and requires

  particular work for the precise alignment of the

liers.

  The purpose of the invention is to indicate how, in the best possible way and without the use of a solution increasing the weight, balancing masses can be used to compensate for first-order mass torques. balancing weights must maintain their exact parallel position under all operating conditions

  to the axis of the crankshaft. The provisions laid down by the

  This problem is solved by the fact that the balancing masses are fixed on coaxial shafts each rotating in two bearings arranged on or in the crankcase, a drive pinion being fixed on one of the two shafts and the two shafts. being united

  in rotation npr a connecting shaft.

  This results in a particularly rigorous mounting of the two balancing masses on short shafts and independent of each other. One compensates by a certain angular mobility of the connecting shaft the small deviations, with respect to the common axis, of the trees

  building on the two opposite ends of the

  possible deviations from manufacturing tolerances.

  or arise during engine operation.

  Moreover, even the axial thermal expansions can be compensated by the connecting shaft. This one

  only for the transmission of the couple, its

truction is relatively simple.

  The invention also provides that the shaft on which the drive gear is fixed is housed, with

  the balancing mass, in the timing case.

  There is no need to provide for these parts a special sump. The oaliers of the tree are preferably to be provided in the partitions facing the narrow

  timing case. Moreover, with this

  tioning, the shaping of the shaft can be effected

  hold by distribution channel.

  According to the invention, the shaft on which is fixed only one balancing mass can be housed in a recess of the motor housing, chambering closed upwards by the cylinder head. This arrangement allows a good mounting on bearings of this short shaft using the rigid walls and very close to each other of the chambering. It is not necessary to provide a

special lid.

  According to another advantageous provision of the

  the two balancing mass shafts can

  each be mounted in a bearing flange of the crankshaft.

  This mounting on transverse partitions o are provided

  the bearings of the crankshaft do not require any adapta-

  the crankcase and also allows the subsequent mounting of balance weights. The invention also provides that the trees to

  balancing masses and the connecting shaft are con-

  formed into hollow trees. This gives a construction

  light weight and the possibility of simple lubrication of the bearings of the trees by the interior of these. It is no longer necessary to resort to passages of

ducts through the housing.

  In the following, the invention is explained in detail with the aid of exemplary embodiments illustrated by figures. These represent: FIG. 1: a longitudinal section of the bearings and the drive of the balancing masses of a

  internal combustion engine in accordance with this

  FIG. 2: a schematic view of the distribution system of this internal combustion engine, FIG. 3: a longitudinal section of the bearings and the drive of the balancing masses of an engine according to a second embodiment of the invention.

present invention.

  The mass balancing system represented

  in Figure 1, mounted on an internal combustion engine

  in-line five-cylinder engine whose crankshaft has crank pins staggered in the order (of their cylinders) 1 - 3 - 5 - 4 - 2 consists of balancing masses 13, 14 fixed on short coaxial shafts 11 and 12 and angularly offset from each other by 1800. The two coaxial shafts 11 and 12 are,

  by their ends, mounted on or in the housing of

  crank 15, respectively in the plain bearings 16

  and 17 on the one hand, 18 and 19 on the other, and rendered

  in rotation by a connecting shaft 20. The drive

  balancing weights 13 and 14 are provided by a timing pinion 21 integral in rotation with the shaft 11 on which it is mounted beside the mass

balancing 13.

  The balancing mass 13 and the pinion of

  distribution 21 are mounted in the distribution housing.

  bution 22 of the internal combustion engine, crankcase

  distribution which, in the area of the balance mass,

  13, is limited by a front wall 23 and by other partitions belonging to the crankcase and to the yoke 24, as well as by a cover 25, The sliding bearing 17 is disposed in the front wall 23 and the sliding bearing 16 in the lid 25. After

  removal of the cover 25, the shaft 11 can be easily

  dismantled, with balancing mass 13 and the

sprocket 21.

  -The balancing mass 14 is housed in a recess 26 disposed on the other end wall 27 of the crankcase 15. The recess 26 is closed at the top by a concave partition 28 of the yoke 24. The plain bearings 18 and 19 are willing

  in the partitions 29, 30 of the recess 26. The envelope

  port 31 of the sliding bearing 19 is closed outwards by

a lid 32.

  The assembly provided for the two balancing masses

  brage 13 and 14 on and in the crankcase

  allows to transmit directly to the crankcase

  brequin 15 the efforts acting on the plain bearings

16 to 19.

  The connecting shaft 20 is mounted with play in a bore 33 of the crankcase 15. This shaft is, at both ends, provided with external grooves 34 355 which come into crisis with internal grooves.

  corresponding to the inner ends

  trees 11 and 12. This system allows a certain

  angular mobility of the connecting shaft 20 allows

  to compensate for certain misalignments

  of the two shafts 11 and 12 with respect to the central axis

common tral.

  The oil intended for the lubrication of

  The smooth bearings 16 to 19 of the shafts 11 and 12 are brought into the front wall 23 via a channel 36. The inner bearing surface of the sliding bearing 17 is directly connected.

  with the channel 36 by a piercing 37. For the food

  of the other plain bearings 16, 18 and 19, the

  11 and 12 and the connecting shaft 20 are formed into hollow shafts with axial channels 38, 39 and

  40. By a circular groove 41 and a transverse piercing

  42 to the shaft 11, the lubricating oil reaches the channel 38 and thence is conveyed by the channel 40 of the connecting shaft 20 in the channel 39 of the shaft 12. Cross holes 43 practiced in the shafts 11 and 12 allow to route the oil

  lubrication bearings 16, 18, 19.

  11 and 12 are closed at their outer ends by a cover 44. The annular seals 46 housed in the circular grooves 45 of the connecting shaft 20 have the role of ensuring, in the region of the grooves 34 and

  , the seal between the connecting shaft 20 and the ar-

11 and 12.

  As shown in Figure 2, the system of dis-

  tribution mounted in the timing case 22 of the internal combustion engine consists, for the most part,

  in a timing gear 48 fixed on the crankshaft

  47, pinion which, by the inner face 49 of a

  double-sided dispensing cat 50, trains the

  distribution pins 51 and 52 mounted on the camshaft 53 and the shaft 54 of an auxiliary member, for example an injection pump. The cat 50 leads, moreover, by

  its outer side 55, the distribution pinion 21

  on the tree 11; this shaft is thus driven in the opposite direction of the timing gear 48 of the crankshaft 47. The direction of rotation of the distribution gears

  48, 51, 52 and 21 is indicated in the figure by arrows

  ches. The equality of the rotational speeds of the shaft 11 and of the crankshaft 47 results from that of the diameters of the

  distribution gears 21 and 48. The balancing masses

  13 and 14 respectively mounted on the shaft 11 and shaft 12 driven through the connecting shaft 20 rotate at the same speed as the crankshaft 47 and in an opposite direction. The marker 56

  designates a tensioner acting on the chain 50.

  this of the arrangement shown on the sketch, where we see the timing gear 21 of the shaft 11 mounted between the timing gears 51 and 52, the invention

  also provides for a provision where this sprocket

  tribution 21 is mounted at another point, on the side

  55 of the chain 50. The trees 11 and 12 can

  may also be driven by toothed belt at

place of a chain transmission.

  Balancing masses 57 and 58 likewise

  heavy weight, shown in Figure 3, and offset from each other by 1800 are also mounted on

  short coaxial axes 59, 60 made integral with rotation

  tion by a connecting shaft 61 provided on each side with flutes. The two trees 59 and 60 are, by their

  ends respectively mounted in plain bearings

  its 62 and 63 on the one hand, 64 and 65 on the other hand which, unlike the previous example, are provided in bearing covers 66 and 67 of the front bearing 68 and

  of the rear bearing 69 of the crankshaft 70 of the combustion engine

  internal bustion. Countersinks 71 and 72 provided in the bearing covers 66 and 67 allow the rotation of the balancing masses 57 and 58 which, when they occupy their lower position, plunge into the

oil sump of the engine.

  On the shaft 59 is fixed, next to the balancing mass, a pinion 73 acting as a drive pinion. The bearing cover 66 rotates in a plain bearing 74 a multi-section shaft 75 mounted by its median sector 76, which has a greater diameter than the outer sector 77 and the inner sector 78. On the inner sector 78 protruding into the recess 71, is fixed a pinion 79 meshing with the pinion 73 of the same size of the shaft 59. On the outer sector 77 of the shaft, is fixed a distribution pinion 80 which, by a

  chain not shown, is connected to a sprocket

  tribution of the same size attached to the crankshaft 70.

  Thanks to this system, balancing masses 57 and 58

  are trained at the same speed and in a different

  of the crankshaft 70 via the timing pinion 80 and the pair of pinions

  79/73 acting as an inverter system.

Claims (5)

  1 - In-line five-cylinder internal combustion engine whose crankshaft has crank pins shifted in the order 1 - 3 - 5 - 4 - 2 and which has, parallel to the crankshaft, a balancing shaft rotating at the same speed and in sense   contrary to this crankshaft, whose balance masses   brage are arranged in the region of the end planes of the crankshaft, characterized in that the balancing masses (13,14) are respectively fixed on two coaxial shafts (11,12) each rotating in two bearings arranged on or in the housing motor (15), a driving pinion (21) being fixed on one (11) of the two shafts and the two shafts (11, 12) being rendered   secured in rotation by a connecting shaft (20).   2 - Internal combustion engine according to the   1, characterized in that the shaft (11) on which the driving pinion (21) is fixed is housed with the balancing mass (13) in the housing of distribution (22).   3 - Internal combustion engine according to one of   claims 1 and 2, characterized in that   the shaft (12) on which only one balancing mass (14) is mounted is housed in a recess (26) of the motor casing (15) closed at the top by the cylinder head (24).   4 - Internal combustion engine according to the   1, characterized by the fact that both   (59,60) with balance weights (57,58) rotate each   cun in a flange-bearing (66,67) of the crankshaft (70).   5 - Internal combustion engine according to one of   claims 1 to 4, characterized in that   shafts (11,12) with balance weights (13,14) and the shaft   linkages (20) are hollow shafts.