SU1254186A1 - Coupling for automatic changing of advance angle of fuel feed - Google Patents

Description

The invention relates to engine building, namely, to devices for automatically changing the angle of advance of the start of fuel injection to the cylinders of an internal combustion engine.

The purpose of the invention is to increase the efficiency of the clutch by improving engine performance by bringing the actual clutch characteristic to the desired one.

FIG. 1 shows the characteristics of the prototype clutch; in fig. 2 - characteristics of the proposed coupling; in fig. 3 - coupling, longitudinal section.

FIG. 1 positions indicate the required characteristic of the clutch, the characteristic is 2 clutches, the characteristic of 3 forces per spool from the centrifugal forces of the goods, the characteristic 4 of the pre-loaded spring of the spool, Lal - the magnitude of the working stroke; F ".. c. and P is the centrifugal force of the weights and the force of the springs, the L-dode is the size of the preliminary-south under / cate.

FIG. 2 g) zi1l1-mi indicated the required characteristic of the 5 clutch, the characteristic of the 6 clutch, the characteristic of 7 forces per spool from centrifugal weights, characteristic 8 pre-loaded and doio, :) i1 ch chu; 1st spring of the spool, hjioroi.r-- the value prednaritelio - go preload. the magnitude of the working stroke Hp (u ;;: pfiTC: ibi; o preloaded right) is alive, A is well, and the warp gap has a gap of 1 1;; springs.

An automatic measurement clutch of an angle 011 ere / -kepi1: the fuel supply contains a reserve. 9. size is “servo1nne 10. In the spool 9, the channels 11 and the ring n are made). 12. In the servo 10 gears ; KO. ihucBbie gi) c / tok 13 and 14 and compo- nent go cie nx Kgiyyol 15, as well as direct 1-outer splines n slanting internal}) spar splines. The servo-hood 10 is fixed, c) c 16 centrifugal weights 17 and the ur ring is installed, about 18 and sleeve 19. Between the sleeve 19 ii plate 2) rozm1. cs1: 4 with predprivile1) 11m nodzhatiy; 5os1 ragnam spring 21 servg) 10. High flooded 22) close 20 closed between body 23 and qi, lindr 24, is the result of something 20 in the axial direction -. 13 of the original iolopeep return spring 21 11:; There is a se}) in question in K) to the housing 23. In the cylinder. 24, the channels 25 are made, the channel groove is 26, and the channel is 1s internal. In ko}) nusa 23 vnevnepo. The bore hole 27. Inside the spool 9 is placed 28, the threaded 1 is fastened in the housing 23. The ha 28 relative to the housing 23 is firmly locked by a nirik 29 and a spring sleeve 30. The other end of the ha 28 is centered in the iM cover. shoulder clamp 28 and gold end

9 is placed with preliminary pressing spring 32 of the valve 9, acting through the valve 9 on the legs of the centrifugal weights 17, resulting in the initial

the position of the goods is pressed to the hub of the servo-piston 10. When screwing in or out of the pull-rod 28, the magnitude of the preload of the spring 32 of the spool 9 changes. Between the sleeve 33 placed on the rod 28 and the retaining ring 34 fixed in

 spool 9, fitted with pre-clearance A, additional spring 35 of spool 9. Clearance A is varied by a set of adjusting rings 36. Case 23 is centered in cover 37 and secured to cylinder 24 with screws. On the outer cylindrical surfaces of the casing 23 and the cylinder 24 are placed the gear 38 of the high pressure fuel pump. Gear 38 is fixed to the cylinder 24 by bolts and connected to the gear.

0 39 transmission diesel. The cylinder 24 is placed in the casing 40, zakrepletochny PA diesel crankcase. In the casing 40, an oil supply (not shown) is made to the annular groove 26 of the cylinder 24 from the central lubrication system.

5 diesel. The servo piston 10 at our outer splines is connected by the faces of the housing 23 and oblique internal splines with the splines of the bushings 41. The splined bush 41 is fixed to the camshaft shaft of the high-pressure fuel pump (not shown). Building 23,

0 cylinder 24 and servo piston K) form a closed cavity 42.

The clutch for automatic change of carbon ahead of the start of nodachi tonlpva works as follows.

When starting the diesel, torque g, e. 5 is transmitted from iuec IH 39 transmission gear 38,:; to the cylinder 24, servo horn 10, and through the splined 4i cam of the high pressure pump1 fuel shaft. With start-up frequencies

 The spring 32 of the spool 9 is clamped to the hub of the servo-hole 10, since the force from the centrifugal loads is not enough to overcome the preload force of the G1p / gin 32. 23

5, and the advance angle of the start of the fuel flow rate remains unchanged.

P) and an increase in the frequency of Bpameinifi VCH-; iHe from centrifugal weights 17 also increases and overcomes the effort of idle reduction of spring 32 of the spool 9.

 The sleeves 17 rotate on wasps x 16 and slide the spool 9 to the left until the force from the centrifugal weights 17 does not become equal to the compressible force / NINA 32. As a result, 1 s-kohtseva — flow through j kg. 12 spool 9 mixes with annular groove 13 servo 0. At the same time, the oil from the central lubrication system is under the pressure at the collar point.

14, the channels 15 and the annular groove 13 of the servo-piston 10 enters the annular groove 12 of the spool 9. Then, the oil enters the cavity 42 through the annular gap between the rotary hammer 9 and the flange 28 of the cavity. As a result, under the pressure of the oil, overcoming the force of pre-pressing the springs 21, the servo piston 10 moves to the left following the spool until the annular groove 12 of the spool 9 is aligned with the annular groove 13 of the servo piston 10. The preload value of the spring 32 of the spool 9, men The time of the coupling start, i.e., the beginning of a change in the angle of advance of the beginning of the fuel supply, is also at When moving the servo motor 10 to the left, the split sleeve 41, which is connected to it with oblique slots, rotates. Consequently, the cam shaft of the fuel pump is rotated, thereby increasing the advance angle of the fuel start. The weights 17, moving with the servo piston 10 to the left, abut their legs on the end face of the spool 9 and turn on the axles 16, returning to the initial position, since the force from the centrifugal forces of the loads 17 is equal to the force from the spring 32.

With a further increase in the frequency of rotation, the force from the centrifugal forces of the loads 17 again begins to exceed the force of the spring 32 of the spool 9. As a result, the loads 17 are again rotated on the axles 16 and the tabs slide the spool to the left until the force from the centrifugal weights 17 force of the spring 32. In this case, the annular groove 12 of the spool 9 is again aligned with the annular groove 13 of the servo piston 10 and the oil under pressure enters the cavity 42. The servo piston moves behind the spool 9, thereby increasing the advance angle opliva.

When moving the servo motor 10 to the left, the gap between the additional spring 35 of the valve 9 and the sleeve is reduced.

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33. The spring 17 of the spool 9 works alone as long as it provides the maximum approximation of the actual spring characteristic (see section EC in Fig. 2), and consequently, the actual coupling characteristic to the required one.

Then, an additional spring 35 of spool 9 comes into operation, as with further increase in the frequency of rotation, the forces of one spring 32 are not enough to ensure that the actual coupling characteristic reaches the required one as much as possible.

With a further increase in the frequency of rotation, both springs work together (see section CD in Fig. 2), thereby ensuring the maximum approximation of the actual characteristics of the spring and coupling to the required ones.

By changing the value of the preliminary clearance of the additional spring 35 of the spool 9, the changeover and the moment when the second spring comes to work (see point C in Fig. 2). It is obvious that the maximum approximation of the actual characteristics of the spring and the coupling to the required ones is provided with a clearance A of 0.5hpaEi, where hjjajji is the magnitude of the working stroke of the pre-loaded spool spring. Taking into account the technological tolerances for the manufacture of parts included in the assembly of the coupling, the gap A is (0.5 ± 0.2) h. A i. When the rotational speed decreases, the force from the centrifugal weights 17 decreases and the valve 9 under the influence of springs 35 and 32 shifts to the right, thereby stopping the access of oil to the cavity 42. The oil pressure in the cavity 42 as a result of oil drainage through the opening 27 of the housing 23 to the diesel crankcase decreases sharply and the servo piston 10 is shifted to the right by the force of the return spring 21, turning the splined sleeve 41. and hence the camshaft of the high-pressure fuel pump. At the same time, the advance angle of the fuel start is reduced.

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Make up., M. Prahaltsev

Tehred I. VeresKorrektor S. Cherni

Circulation 523Signature

VNIIPI USSR State Committee

for inventions and discoveries

113035, Moscow, Zh-35, Raushsk nab. 4/5

Branch PPP "Patent, Uzhgorod, st. Project, 4

Claims (2)

1. CLUTCH FOR AUTOMATIC CHANGE OF ANGLE OF ADVANCE OF FUEL FEEDING, comprising a housing, servo-piston, spool, pre-pressed spool spring with a given stroke, centrifugal weights and axles, centrifugal weights placed on axes fixed in a servo piston, which is located in the spool, in the servo piston and interacts with centrifugal loads, characterized in that, in order to increase efficiency, it additionally contains a rod, a thrust sleeve, a retaining ring and an additional spring, and the rods is formed with a shoulder, it is arranged inside the slide and fixed in the housing, the retaining ring connected to the spool, and the stop sleeve - with traction preload spring mounted on the slide rod between the collar and plug. and an additional spring is placed on the rod between the thrust sleeve and the retaining ring and has a preliminary clearance with it. 2. Coupling in π. 1. characterized in that the value of the preliminary clearance of the additional spring is 0.3 - 0.7 of the specified working stroke of the pre-pressed spring of the spool. I