Fuel injection pump for internal combustion engines
BACKGROUND OF THE INVENTION 
     The demands made on such a cam disk vary greatly. On the one hand, the clutch member of the cam disk or ring must exhibit sufficient elasticity to withstand even jolt-like torques without causing fatique fracture, while conversely the front cam rolling surface must be as hard and wear-resistant as possible to withstand the extraordinarily high pressure occurring between the cam surface and the rollers. The magnitude of the piston force may be selected proportionately to the wear resistance of the cam surface material, i.e., the greater the wear resistance, the greater may be the piston force, while the torque to be transmitted should be proportionate to the elasticity of the coupling assembly which is subjected to extreme bending stress, i.e. the greater the elasticity of the coupling assembly, the greater may be the torque selected for transmission. 
     OBJECT AND SUMMARY OF THE INVENTION 
     The principal object of the invention is the development of a cam disk which attains these divergent requirements to the effect that as compared to known cam-type drives, performance is substantially improved, thereby resulting especially in advantageous overall dimensions of the injection pump. 
     This object is attained according to the invention, by an improved design of the cam disk which comprises two parts, i.e. a support member carrying the coupling part, and a ring connected rigidly with the latter which is constructed of a harder material and on which the cams are arranged. 
     According to an advantageous embodiment of the invention, this concept employs the manufacture of a cam disk in which the latter consists of two specially machine-finished parts of material having a variable hardness and connected rigidly with each other, one of the parts thereof being made as a support member with the coupling parts and the second as a ring provided with cam surfaces. 
     In the preferred embodiment of the invention, the support member is provided with an outwardly extending flange portion, the radial extent of which overlaps at least in part the radial extension of the cam ring with the support member and cam ring being secured together by electron beam welding. 
    
    
     BRIEF DESCRIPTION OF THE DRAWING 
     FIG. 1 is a longitudinal section through the lower portion of a fuel injection pump; and 
     FIG. 2 is a longitudinal section in view of the cam disk in an enlarged scale. 
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Turning now to the drawings, FIG. 1 shows in dotted outline the housing of a fuel injection pump used for multi-cylinder internal combustion engines. Rotatably mounted within the housing is a drive shaft 10 connected with an axial cam plate 7 which has as many cam lobes 8 as correspond to the number of cylinders in the engine. The axial cam plate 7 is axially reciprocated by rotation through interaction with locally fixed rollers 4, the latter being supported in the carrier element 5. 
     It will be observed that the roller carrier 5 is pinned to the shaft 6. The cam disk 3 comprises two members i.e., a support member 7 and a cam ring 8. As is customary in structures of this general type, the support member 7 is associated on the one hand with a coupling 9 with the drive shaft 10 and on the other hand with the pump plunger 12 by way of a pin 11. 
     The cam disk is urged into contact with the roller 4 by a spring 13 to thereby cause the pump plunger 12 to execute, in addition to the rotary motion induced by the coupling means 9 and 11, a reciprocal motion when the shaft 10 rotates and the cam ring 8 passes over the rollers 4. 
     The technical demands made on the cam ring 8 and on the support member 7 differ greatly, that is to say, that due to the torque transmission, and especially because of the coupling assembly, the support member 7 must be manufactured of an elastic material, e.g. an extrudable casehardenable material (16Mn Cr 5, i.e., an alloy comprising 16% manganese and 5% chromium) which exhibits a high degree of core toughness. In contrast thereto, the cam ring 8 should be made of a highly wear-resistant material, e.g. DMO 5 casehardened, i.e., steel used in high speed applications and also known as S652 steel, which comprises 6% tungsten, 5% Molybdenum and 2% vanadium so as to attain the greatest possible pressure between the cam surface and the roller. The support member 7 and the cam ring 8 are fused as illustrated at 14 by means of an electron beam welding method. The support member 7 overlaps the cam ring 8 by means of a flange 15 (see FIG. 2) in order to achieve first of all a favorable transmission of power, and secondly, to be able to execute the welding seam 14 in a radial direction.