GB2480510A

GB2480510A - Oil Pump Module with an Oil Pump and an Associated Balance Shaft

Info

Publication number: GB2480510A
Application number: GB1017271A
Authority: GB
Inventors: Georg Zwickler; Wolf-Dietrich Bicker; Manfred Holzh User
Original assignee: GM Global Technology Operations LLC
Current assignee: GM Global Technology Operations LLC
Priority date: 2010-05-20
Filing date: 2010-09-24
Publication date: 2011-11-23
Anticipated expiration: 2030-09-24
Also published as: CN102251824A; US20110283966A1; RU2548534C2; GB2480510B; DE102010022134A1; GB201017271D0; RU2011120149A

Abstract

An oil pump module 1 has an oil pump module housing 3, and is situated in an oil pan of an internal combustion engine 5 below a crankshaft 6. All moving parts of an oil pump 7 and an angular momentum balance shaft 8 are situated in the oil pump module housing, and a rotor 9 of the oil pump is situated on a rotor shaft 10 which is separate from the angular momentum balance shaft. The rotor shaft and angular momentum balance shaft are mechanically connected with the module housing via a spur gear transmission 11. The rotor shaft may be driven from the crankshaft by a chain drive 13, and the arrangement allows the speed of the oil pump rotor to be de-coupled from the speed of the angular momentum balance shaft. This may permit the speed of the angular momentum balance shaft to be equal to or double crankshaft speed while permitting step-up or step-down in the speed of the oil pump rotor.

Description

Oil pump module having an oil pump module housing The application relates to an oil pump module having an oil pump module housing. The oil pump module is situated in an oil pan of an internal combustion engine below a crankshaft.

All moving parts of an oil pump and an angular momentum bal-ance shaft are situated in the oil pump module housing.

A combined oil pump and angular momentum balance module for installation in an oil sump of a reciprocating piston engine is known from the publication US 6,601,557 Bi, a rotating an- gular momentum balance shaft carrying balance weights on di-ametrically opposing ends, in order to balance the unbalanced angular momentum forces of the reciprocating piston engine.

In addition, it is known from US 6,205,970 B1 that the oil pump housing can be formed together with the housing of angu- lar momentum balance shafts, in order to thus reduce the num- ber of the components and the production time of the assem- bly. A schematic outline of such an oil pump module in an in-ternal combustion engine is shown in Figure 3. Furthermore, Figure 4 shows a cross-section through the oil pump according to the prior art, whose rotor is fixed rotationally fixed on one of two angular momentum balance shafts.

Figure 3 shows a schematic outline of the known oil pump mod- ule 2, in which, for a four-cylinder engine having the cy-linders 31, 32, 33, and 34, only the connecting rods are shown in the schematic outline, which cooperate via plain bearings 16 with a crankshaft 6 and cooperate in the engine compartment 17, which is symbolized here as a block having a dash-three-dot line.

Outside the engine compartment 17, the crankshaft 6 has a gear ring 28 of a chain drive 13, which drives a first angu-lar momentum balance shaft 29 below the crankshaft 6 having two balance weights 23 and 24 via a drive chain gearwheel 12.

On this first angular momentum balance shaft 29, a spur gear transmission 11 having a transmission ratio 1:1 is situated, which drives a second angular momentum balance shaft 35, on which a rotor 9 of an oil pump 7 is situated in an oil pan 4, an intake opening 14 of the oil pump 7 being immersed in an oil sump.

Since the angular momentum balance shafts 29 and 35 rotate at the same speed as the crankshaft 6 and are fixed in a rota-tionally-fixed manner on the angular momentum balance shaft of the rotor 9, the oil pump 7 operates at the same speed as the crankshaft 6.

In addition, Figure 4 shows a cross-section through the part of the oil pump module 2 according to the prior art, in which the oil pump 7 having its rotor 9 is situated. The rotor 9 is fixed on the second angular momentum balance shaft 35, on which the balance weights 23 and 24 are also situated. The angular momentum balance shaft 35 is mounted on plain bear-ings 36 and 37, the plain bearing 36 being situated between the rotor 9 of the oil pump 7 and a spur gear 38 of the spur gear transmission 11 and a second plain bearing 37 being si-tuated between a first front balance weight 23 and a second rear balance weight 24.

This known oil pump module 2 is situated with its oil pump housing 3 at an angle c below the crankshaft in such a manner that the intake opening 14 of the oil pump 7 lies in an oil sump 15 and the balance weights 23 and 24 rotate above a lev-el 39. Although in Figure 4 the oil pump housing 40 is flanged on a housing 41 of the second angular momentum bal-ance shaft 35, the prior art of this document discloses at the beginning that the housing 40 and 41 may be formed as the oil pump module housing 3. Nonetheless, the disadvantage re- mains that the speed of the rotor 9 of the oil pump 7 is dis-advantageously connected to the speed of the angular momentum balance shaft 35.

The object of the application is to overcome the disadvantage in the prior art and to provide an oil pump module in which the speed of the oil pump rotor is not coupled to the speed of the angular momentum balance shafts.

This object is achieved by the subject matter of independent Claim 1. Advantageous refinements of the application result from the dependent claims.

According to one embodiment of the application, an oil pump module having an oil pump module housing is provided. The oil pump module is situated in an oil pan of an internal combus-tion engine below a crankshaft. All moving parts of an oil pump and an angular momentum balance shaft are situated in the oil pump module housing. A rotor of the oil pump is si-tuated on a rotor shaft, which is separate from the angular momentum balance shaft, in the oil pump module housing. The rotor shaft is mechanically connected via a spur gear trans- mission in the oil pump module housing to the angular momen-tum balance shaft.

Through the rotor shaft, which is independent and/or separate from the angular momentum balance shaft, it is possible to supply the rotor of the oil pump with an optimized speed. The speed can be above or also below the speed of the crankshaft.

A volume-flow-regulated vane pump can be used as the oil pump, in which an eccentricity between the vane housing and the rotor shaft can be regulated as a function of the oil pressure in a main oil gallery of the engine via a corres-ponding hydraulic return line. A further regulating chamber can be switched on in the oil pump module housing via an electromechanical oil control valve, whereby the volume flow can be reduced and the oil pressure can be decreased. All moving parts required for this purpose are integrated in the oil pump module housing of the oil pump module.

In a further embodiment of the application, it is provided that a drive chain gearwheel is situated on the rotor shaft outside the oil pump module housing, which is mechanically connected via a chain drive to the crankshaft. The rotor shaft is thus advantageously supplied directly by the trans-mission of the chain drive with an optimum rotor speed, which is independent of the speed required for the angular momentum balance shafts. Furthermore, it is provided that an intake opening of the oil pump of the oil module is immersed in an oil sump of the oil pan.

As already mentioned above, a two-stage oil pump having a main regulating chamber and an expansion regulating chamber is situated in the oil pump module housing. In addition to the plain bearings of the engine and further components, the plain and/or roller bearings in the oil pump module housing are also supplied by this two-stage oil pump. The oil pump module has a drive shaft, on which the drive chain gearwheel is situated in a rotationally-fixed manner outside the oil pump module housing. The drive shaft has a drive gearwheel of the spur gear transmission to the angular momentum balance shaft between two shaft bearings inside the oil pump module housing. This drive gearwheel of the spur gear transmission is designed in such a manner that, together with an output gearwheel situated on the angular momentum balance shaft, it ensures a step-up or step-down transmission which causes the angular momentum balance shaft to rotate at the same speed as the crankshaft with a three-cylinder motor or at twice the speed with a four-cylinder motor.

The two balance weights, which are situated on the angular momentum balance shaft between two shaft bearings, compensate for the unbalance of the torque impulses of an internal corn- bustion engine having reciprocating pistons. For this pur-pose, the angular momentum balance shaft is situated as an output shaft having an output gearwheel in relation to the rotor shaft having drive gearwheel in the oil pump module housing. As a result, the output gearwheel of the angular mo-mentum balance shaft meshes with the drive gearwheel of the rotor shaft of the oil pump in this oil pump module housing

and not vice versa as in the prior art.

Furthermore, the transmission ratio of the spur gear trans-mission situated in the oil pump module housing is designed in such a manner that, in consideration of the transmission ratio of the chain drive situated outside the oil pump module housing, the speed of the angular momentum balance shaft is equal to or twice as high as the speed of the crankshaft.

A possibility is thus provided using this oil pump module of providing the speed of the rotor of the oil pump varyingly in relation to the speed of the crankshaft to the angular momen- tum balance shaft, so that a step-up or step-down transmis-sion ratio of the chain drive defines the rotor speed of the rotor of the oil pump.

In a further embodiment of the invention, for a three-cylinder engine, the speed of the rotor of the oil pump is provided as lower than the speed of the crankshaft of the three-cylinder engine. This oil pump module is therefore pre- ferably used in a vehicle having an internal combustion en-gine which has three cylinders.

The application will now be explained in greater detail on the basis of the appended figures.

Figure 1 shows a schematic outline of an oil pump module ac-cording to an embodiment of the application; Figure 2 shows a schematic outline of an oil pump module ac- cording to Figure 1 in cooperation with the crank-shaft of an internal combustion engine; Figure 3 shows a schematic outline of an internal combustion engine having an oil pump module according to the

prior art;

Figure 4 shows a schematic cross-section through a subarea of an oil pump module 2 according to Figure 3.

Figure 1 shows a schematic outline of an oil pump module 1 according to an embodiment of the application. The oil pump module 1 has an oil pump module housing 3, in which all mov-ing parts of an oil pump 7 and an angular momentum balance shaft 8 are situated. A rotor 9 of the oil pump 7 is situated on a rotor shaft 10, which is separate from the angular mo-mentum balance shaft 8, and is implemented as the drive shaft 18, in the oil pump module housing 3. The rotor shaft 10 is mechanically connected via a spur gear transmission 11 in the oil pump module housing 3 to the angular momentum balance shaft 8.

I.e., the rotor shaft 10, as the drive shaft 18, drives the angular momentum balance shaft 8 having its balance weights 23 and 24. For this purpose, the angular momentum balance shaft 8, as the output shaft 27, has an output gearwheel 22 of the spur gear transmission 11. While the rotor shaft 10, as the drive shaft 18, is driven by the crankshaft via a drive chain gearwheel 12, which is situated outside the oil pump housing 3, and a chain drive 13, the angular momentum balance shaft mounted in the shaft bearings 25 and 26 rotates at a speed which is specified by the spur gear transmission 11.

The spur gear transmission 11 can therefore have a transmis-sion ratio which is not equal to 1:1 and thus compensates for a transmission ratio of the chain drive 13, so that the re-quired smooth running between angular momentum balance shaft 8 and crankshaft of the internal combustion engine is en-sured. In addition, the spur gear transmission 11 ensures a rotational direction reversal of the angular momentum balance shaft in relation to the rotational direction of the crank-shaft.

The advantage of this oil pump module is, on the one hand, that the speed of the rotor 9 of the oil pump 7 can be de- signed individually and optimally. On the other hand, a com- pact oil pump module housing 3 is possible, which is assem-bled from two oil pump module housing halves, for example, whereby the costs for separate oil pump housing and housing for the angular momentum balance shaft housing may be re-duced, since fewer parts are possible, on the one hand, and a lower weight is also possible, on the other hand. Through the spur gear transmission, which is situated in the oil pump module housing, not only is the difference between the speed for the rotor shaft and the crankshaft compensated for again, but rather also the required rotational direction reversal for the angular momentum balance shaft is also achieved si-multaneously.

While the shaft mounting of the drive shaft by a bearing 19 is situated between the drive chain gearwheel 12, which is situated outside the oil pump module housing 3, and the drive gearwheel 21 of the spur gear transmission 11, the second shaft bearing 20 of the drive shaft 18 is located between the drive gearwheel 21 of the spur gear transmission 11 and the oil pump 7. Two shaft bearings 25 and 26 are provided for the mounting of the angular momentum balance shaft 8, between which the output gearwheel 22 of the spur gear transmission 11 and the two balance weights 23 and 24 are situated.

Figure 2 shows a schematic outline of an oil pump module 1 according to Figure 1 in cooperation with a crankshaft 6 of the three-cylinder engine 30, which has three cylinders 31, 32, and 33, of which only the connecting rods are shown, which cooperate with plain bearings 16 of the crankshaft 6.

Outside the crankshaft housing, a chain gearwheel 28 is si-tuated on the crankshaft 6, which is connected via a chain drive 13 to the drive chain gearwheel 12 for the rotor shaft 10. While the area of the engine compartment 17 of the inter-nal combustion engine 5 is enclosed by a dash-three-dot line, the chain drive 13 outside the engine compartment 17 is marked by a dash-four-dot line. The oil pump module 1 in the pump housing 3 marked by a dot-dash line corresponds to Fig-ure 1, components having the same functions as in Figure 1 being identified by the same reference numerals and not being explained further separately.

It is once again clear from Figure 2 that an arbitrary step-up or step-down transmission for the drive of the rotor 9 in the pump 7 is possible using the chain drive 13, particularly because an equalization of the speed to the speed of the crankshaft 6 is possible for the angular momentum balance shaft 8 through the spur gear transmission 11 with rotational direction reversal to the crankshaft 6.

Figures 3 and 4 were already explained in the introduction, so that a repetition will be dispensed with here.