JPS6073169A - Face cam drive - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a front cam drive device having a circular front cam plate with a diameter of 1 mm. The rollers are adapted to cooperate in a transmission manner, with the rollers being supported on pins oriented radially relative to the front cam plate axis, and the pins being supported with their ends in the support member. The support member has a cutout for receiving the roller and is fitted into the casing with its outer circumferential section, and a guide plate arranged on the pin is located adjacent to the cutout in the support member. It is of the type having an end face shape adapted to the wall and in contact with the radially outwardly facing end face of the roller.

Prior Art A front cam drive device of the type described above is disclosed in U.S. Pat. No. 3,374,68.
No. 5, the roller support ring has an inner ring and an outer ring and is rotatably fitted into a cylindrical casing, the inner ring and the outer ring receiving the rollers. The inner ring and the outer ring are supported by the ends that limit the notch for the ring. The pin is provided radially outward with a guide ring and a floating bushing, on which the actual roller is supported. The rollers and floating bushes contact a guide ring radially outwardly, the guide ring having its radially outwardly directed end adapted to the circular peripheral wall surface of the outer ring of the roller support ring. In order to guarantee an always uniformly large contact surface between the roller and the cam surface of the front cam plate running on this roller, the floating bushing is configured with a spherical outer circumference.
As a result, the rollers are pivotable. Configured in this way, the cam 1 drive with a cylindrical floating pusher allows the pins to be moved radially outwards during high loads on the front cam plate, and the cylindrical pusher receiving the roller retaining ring. It has the disadvantage that it can penetrate the wall of the casing. In extreme cases, the walls of the casing can break, and the rotatability of the roller support ring is impaired if the fuel injection pump is driven for a long time in one rotational position of the roller support ring. This impediment to the possibility of rotation occurs in particular when the front cam plate is driven to run on rollers and the roller support ring is substantially stationary. In such an arrangement, a corrective adjustment movement of the roller support ring is necessary only to adjust the injection start timing. If a break in the cylindrical wall occurs which is unfavorable, the rotation of the roller retaining ring is impeded if the pin gets stuck in the broken wall section during the adjustment movement.

Problems to be Solved by the Invention It is an object of the present invention to prevent the pins supporting the rollers from moving radially outward, and to prevent the corrective adjustment movement of the roller support ring supporting the pins. - That is.

Measures for solving the problem In order to achieve the object described above, the invention provides that the pin is connected at least indirectly and in a radially force-transmissible manner to the support element.

ADVANTAGES OF THE INVENTION With the arrangement of the invention, the radially outward force component acting on the pin is absorbed by the support member and not transmitted to the casing wall, eliminating damage to the casing wall and allowing correction of the support member. Coordination movement is guaranteed.

With the embodiment according to claim 2, the radial force components are transmitted to the support element via large surfaces and wear is kept low.

The embodiment according to claim 6 provides a simple construction of the joint, in which case the geometry of the girder and guide plate does not have to be changed.

The embodiment according to claim 4 provides a large transmission contact surface for the pin, and the intermediate sleeve is preferably shrink-fitted.

The embodiment according to claim 5 simplifies the Ω assembly and ensures a more secure connection between the roller and the pin with only slight damage to the supporting surface compared to known groove bottoms.

In this case, the roller is mounted on a floating intermediate ring, which is tangentially connected to the stop ring as a force transmitting element.

Furthermore, according to an advantageous embodiment of claim 8, the pin and guide brake!・Reliable force transmission between the two is guaranteed.

Embodiment As shown in FIG. 1, a pump piston 1 of a distribution type fuel injection pump is mounted on a front cam plate 3 with a foot 2, and is non-rotatably connected to the front cam plate through a pin 4. There is. Further, the pump piston is pressed against the front cam plate by a compression spring 5Vc supported by a support (not shown) fixed to the casing and the foot 2.

The front cam plate has a circular cross section and has a cam surface on its edge facing away from the pump piston 1, with which it contacts the roller 7. The roller 7 is supported on a pin 9 via a floating bush 8 which projects on both sides and is supported at its free end in a U-shaped recess 10. .The notches 10 are the inner ring 12 and outer ring 14 of the roller support ring 15.
The end face is redundant. The roller support ring is the same (having a circular cross section, cylinder 1 of the casing of the fuel injection pump
6, and is fitted into a pivotable position using a pivoting device (not shown). The rotation of the roller support ring is carried out for the generally known purpose of adjusting the injection start timing.

The pins 9 are oriented in the radial plane parallel to and radially to the front cam plate and are distributed in such a way as to transmit the supporting force produced by the roller 7 symmetrically to the front cam plate.

Several guide plates 18 are provided on the pin 9 between the end faces of the rollers 7 and the floating bushes 8 and the inner side of the outer ring 14 of the roller support ring, the guide plates being for example shrink-fitted or press-fitted. It is connected to the pin by frictional force.

guide plate 18, roller 7 and floating bush 8;
Inner ring 12 and outer ring 1 of roller support ring 15
It protrudes into a ring-shaped notch 19 formed between 4 and 4.

The roller support ring 15 is rotated at 6 for adjustment as described above and is substantially immovable, and is supported by the support ring 20 at the bottom of the casing in the axial direction of the pump piston, while the front The cam play 1 is rotated by a drive shaft 22 via a series connection 23. A cam ridge on the front cam plate defines the pump stroke per revolution of the pump piston.

When the front cam plate is moved upwards against the force of the return spring, an impulsive force acts on the rollers γ, which tend to displace the pins 19 outwardly in conjunction with the rotational movement. In the configuration of the present invention, the pin 9 is connected to the guide plate 18 by frictional force.
along the outer ring 14 of the roller support ring, thus avoiding loading of the cylinder 16 of the casing. [Guide]0 rate is shaped so that the outer end surface conforms to the inner diameter of the outer ring and contacts the inner circumferential surface of the outer ring.
Figure 2C (also in the second embodiment shown, the pin 9 is inserted into the U-shaped notch 10 of the roller support ring 15)
supported within. However, in this exemplary embodiment, the floating shoe 8a is constructed as an intermediate sleeve that is shrink-fitted onto the pin, on which the roller 7 is supported.

A guide plate 18 is provided between the end surface of the intermediate sleeve and the inner circumferential surface of the outer ring 14, as in the embodiment shown in FIG. contact together. In this embodiment, therefore, the pin 9 is supported on the roller support ring via the guide plate 18 by means of an intermediate sleeve.

The shrink fit of the intermediate sleeve provides a large surface contact with the pin 9, resulting in a secure connection. Alternatively, the pin 9 can have a collar in the same place instead of the shrink-fitted intermediate sleeve (this offers manufacturing and assembly engineering advantages. Advantageously, in this embodiment The pins 9 are constructed symmetrically, so that a mistake-free assembly is possible.

In the embodiment shown in FIG. 6, the pin 9a has a ring-shaped notch 24, and a retaining ring 25 is fitted into the notch. The retaining ring 25 extends beyond the outer diameter of the pin 9a and is attached to the floating bush 8a described in FIG.
It protrudes into a notch 26 formed at the outer end of the inner periphery of b. In this case, the recess 26 can advantageously be designed as a chamfer of the inner bore. floating bush 8ab
A roller 7 is supported as shown in FIG. The rollers 7 and the bushes 8ab rotate radially along a guide plate (18), which is also provided here, and which is rotatably mounted on the pin 9a on the opposite side of the retaining ring. In this embodiment, either the pin 9a rotates along the guide plate 18 together with the retaining ring 25, or the floating bush 8ab rotates with the securing ring 25KG.

In both cases, the pins 9a are stopped axially outwards. It is a disadvantage if the floating bushings are constructed asymmetrically on one side, which can lead to mix-ups during installation. In order to avoid these disadvantages, a symmetrically designed bushing has the disadvantage, however, that the supporting surface for a given construction space is very small. These drawbacks are obviated by the construction of the embodiment shown in FIG. 4, in which the floating bushing 8'ac is constructed symmetrically without a recess and is shortened by the width of the retaining ring 250.

The support surface is therefore somewhat smaller than in the case of a roller support ring groove molding which does not retain the pin; however, in this case a larger support surface is obtained than in the embodiment of FIG. The space requirement on the supporting side of the pin is reduced by the fact that the guide plate 8 has a chamfer where it comes into contact with the retaining ring 25. The width of the bushing is therefore reduced by approximately half the width of the retaining ring. I can't let it happen.

In the embodiment shown in FIG. 5, a guide plate, a floating bush 8 and a roller 7 are arranged freely rotatable on the pin 9, in which case the pin 9 is arranged in order to stop the pin 9 against axial displacement. The bearing part is the roller support ring 154'l.
: Welded. Such welding is advantageously carried out accurately using an electron beam without significant heat generation.

In the embodiment shown in FIG. 6, instead of welding the pin 9, a ring of wear-resistant material is fitted into the cylindrical wall in contact with the pin, so that the area in which the cylindrical wall contacts the pin 9 It will no longer be damaged or deformed.

[Brief explanation of the drawing]

The drawings show embodiments of the present invention; FIG. 1 is a sectional view of the first embodiment, FIG. 2 is a sectional view of the second embodiment, and FIG. 3 is a sectional view of the second embodiment.
4 is a sectional view of the fourth embodiment, FIG. 5 is a sectional view of the fifth embodiment, and FIG. 6 is a sectional view of the sixth embodiment. DESCRIPTION OF SYMBOLS 1... Pump piston, 2... Foot part, 3... Front cam plate, 4... Pin, 5... Compression spring, 6...
...Cam surface, 7...Roller, 8...Button, 9.
... Pin, 10... Notch, 12... Inner/side ring, 14... Outer ring, 15... Roller support ring, 16... Cylinder, 18... Guide plate, 19...・
・Notch, 2o...Support ring, 22...Drive shaft,
23... Connecting portion, 24... Notch, 25... Retaining ring, 26... Notch Continued from page 1 0 Inventor Helmut, Simon Gegg, Federal Republic of Germany 48 0 Inventor Valdemar 59 Pingen, Tribauer, Weiplingen, Genseckers

Claims (1)

[Scope of Claims] 1. A front cam drive device equipped with a circular front cam plate (3), wherein the circular cam surface (6) of the front cam plate
) is designed to dynamically cooperate with one roller (7), and the roller is connected to the front cam plate axis (IM).
A pin (9) oriented radially with respect to Missing (
19) and is fitted into the casing with its outer circumferential section, a guide plate (18) with a pin (9) VC arranged in the wall adjacent to the recess (19) of the support member (15). The support member has an adapted end shape and is in contact with the radially outwardly facing end face of the roller (7), so that the pin (9) can at least indirectly and radially transmit force. (15). 2. The pin (9) is coupled to the support member via the guide plate (18) so as to be capable of transmitting force. Claim 1
The front cam drive device described in Section 1. 6. Front cam drive according to claim 2, wherein the guide plate (18) is fixedly connected to the pin. 4. The front cam drive device according to claim 2, wherein an intermediate sleeve (8a) is immovably connected to the pin (9), and a roller (7) is supported on the intermediate sleeve. 5. The front cam drive device according to claim 2, wherein a retaining ring (25) is arranged on the pin (9a) between the guide plate (1B) and the roller (7). 6. Front cam drive according to claim 5, wherein the intermediate sleeve (8ab) is supported as a bearing for the roller (7) on the pin (9a). Front cam drive according to claim 1, wherein the Z pin (9) is welded to the support member (15) at at least one support point. 8. The pin (9) has a portion with a larger diameter than at least one portion supported in the support member (15) of the pin, which portion serves as a bearing for the roller (7); A front cam drive device according to claim 2.