JPS58117368A - Oil pump of engine - Google Patents

Abstract

PURPOSE:To obtain an oil pump suitable for a two cycle engine, by providing two kinds of control mechanisms, which supply oil with delivery characteristics being different in response to the load of the engine, in one oil pump. CONSTITUTION:When a worm wheel 22 is rotated by a worm 21 which is associatively moved by the rotation of a two cycle engine, a projection 23 rides on a concentric cam 15 against the energizing force of a coil spring 30 at the time of a discharge stroke. At the time of intake stroke, when the projection 23 is inserted in the concentric cam 15 by the energizing force of the coil spring 30, the worm wheel 22 performs two reciprocating movements per rotation of the rotary movement. At the discharge sroke, a plunger 27 is moved rightward together with the worm wheel 22, a discharge path 38 of a first actuating chamber 31 is aligned with a discharge port 43a, a discharge path 40 of a second actuating chamber 32 is aligned with a discharge port 44b, and the discharge of the oil is completed. The actuating chamber 31 is operated along the entire operating region of the engine. The actuating chamber 32 performs the oil intake and discharge only when the load is equal to the preset load of the engine or more.

Description

[Detailed description of the invention] The question is regarding the best oil pump VC for the engine.

Conventionally, one pump could simultaneously handle two types of I and C+.
Introducing the Ministry 41 required method, 1 entry 11 out 11 points system Ministry 11
In the pumps and 1-, the plunger pumps 11 and 1 disclosed in Japanese Patent Publication No. 53-25124 are
A pump unit 1 having a cylinder chamber 1a, a suction T-111) and at least one leaf 111C, and an end face cam 2a, 3a at each outer end, integrally rotates 1 to 1 in the direction of rotation. 9 ((to the force 11rl, there is a cylinder chamber connected to -1- in a movable manner)
A pair of plungers 2 and 3 are fitted in the sliding function, and a rotating function is fitted in the above-mentioned main cylinder on each side (,14+) by interlocking with the element. - Note!
? ! + The guide cylinder part 1 with a straight slope that comes into contact with the end cams 2a and 3a, respectively:) A pump chamber P that can communicate with the suction port] 1) and the discharge port IC is formed, and the pair of plungers 2.
3) There is a device in which suction and discharge are performed by rotationally driving one side, and the amount of suction and discharge is changed by the control element.

By the way, when the above-mentioned plunger pump' is used as an oil pump for an automobile engine, it is necessary to supply oil to the intake passage and the engine working chamber with different discharge characteristics depending on the engine load. There is a demand for downsizing due to the need to incorporate it into a narrow engine room, but in the plunger pump described above, the discharge characteristics of the two discharge ports are the same, and the cam 2a that regulates the stroke of the plunger 2.3, 3a is required, which increases the size of the pump and increases the cost.

The non-invention was made in view of the conventional problems mentioned in 2. The plunger is fitted into a housing so as to be rotatable and movable in the axial direction, and a cam portion provided at one end of the plunger is supported within the housing. The control cam is formed so as to come into contact with a control cam that rotates by a required angle depending on the load of the general-purpose engine, and to increase the reciprocating distance of one lange as the engine changes from a light load force to a high load, In an oil pump for an engine, in which the cam part slides into contact with the control cam when the plunger rotates, and the plunger reciprocates to discharge oil from the working chamber, the plunger and the casing are fitted to the other end of the plunger. A first working chamber is provided, which is composed of a fixed part and a fixed part, whose volume changes over the entire moving area of the engine, and which inhales and discharges the liquid, and reciprocates a required distance in the axial direction at the other end of the plunger.
A movable member is fitted therein, and a second working chamber is formed by the movable member and the plunger and whose volume changes to suck in and discharge oil only when the set load of the engine is exceeded.
In addition to downsizing, the second working chamber allows oil to be discharged with different discharge characteristics from the first working chamber when the load exceeds the set load, making it suitable for use as an engine oil pump. It is something.

Embodiments of the invention will now be described in detail with reference to the accompanying drawings.

Figures 2 and 3 of the first embodiment show the discharge "second dead center" under light load, Figure 4 shows the suction bottom dead center under light load, and Figure 5 shows the discharge top dead center under high load. The figures are cross-sectional views of the suction bottom dead center under high load.

Each figure Vc:E? and the oil pump has lids 10 on both ends.
．． A housing 1lii consisting of a cylindrical body closed at 10 is formed inside the housing 11, and a cam chamber 12 is formed in the left part in the figure, a worm foil chamber 13 is in the center part, and a pump chamber 14 is formed in the right part. .

The cam chamber 12 has a pair of large diameter concentric cams 15.
A camshaft 17 having a small-diameter eccentric cam 16 is rotatably supported in the direction perpendicular to the axis, and an accelerator pedal interlocking member 19 is attached to the end of the camshaft 17 that protrudes to the outside via a seal IH 18'e. It’s 20! 11th chapter Unrestrictedly fastened and fixed.

The relationship between the accelerator pedal interlocking member 19 and the eccentric cam 16 is such that when the load is light, the eccentric cam 16 moves to the right position (the 21st
(Fig. 4), and eccentric to the left position at high loads (Fig. 5, Fig. 4).
(Fig. 6).

A worm wheel 22 that meshes with a worm 21 that is linked to the rotation of the two-stroke engine is fitted into the worm wheel chamber 13 so as to be rotatable and movable in the axial direction.
The left MNC of the worm wheel 22 is a pair of chevron-shaped cams 2 that come into contact with one concentric cam 15.
8.28'? r, and the angle-shaped cam 23.28 fits between the concentric cams 15.15 and the eccentric cam 16 at the suction bottom dead center under light load (Fig. 4). The center stopper 24 that stops and the centripetal cams 15' and 1 at the suction bottom dead center (Fig. 6) under high load.
A peripheral stopper 25 is provided to abut against and stop at 5.

Further, on the right side of the worm wheel 22, a coupling convex portion 26'fr is provided which fits into a plunger 27, which will be described later.

A plunger 27 is fitted into the pump chamber 14 so as to be rotatable and movable in the axial direction.On the left side of the plunger 27 is a cup into which the coupling convex portion 26 of the worm wheel 22 is fitted. A link ff11 is provided on the right side of the plunger 27 and is integrated with a first binuton 33, which will be described later, through which the plunger 27 is inserted.
A coil spring 30 is compressed between the housing 1 and the housing 1.
The lid 10 of No. 1 abuts and stops the link part 1 29, and the coil spring 30 urges the plunger 27 in the leftward movement direction, and the worm wheel 22 also moves in the leftward movement direction via the coupling uneven part 28.26'i. The chevron cams 23.28 are biased against the concentric cams 15.15 during the discharge stroke against the full biasing force (FIGS. 2 and 5), and the concentric cams 15.15 are biased by the biasing force during the suction stroke. 15 (Fig. 4, Fig. 6 2゜ above plunger 271/II:
The first part has a small diameter and passes through the right part to about 2/3 of the depth.
A working chamber 31 and a large-diameter second working chamber 32 inserted from the right side to approximately 1/3 depth are formed congruently, and the first working chamber 3
1 includes a first binuton 3 integrated with the ring portion) 729;
In addition, the 21f working chamber 82 is provided with a second binuton 34 whose inner hole is slidably fitted into the first piston 33 and whose outer periphery is slidably fitted into the second working chamber 32. , second
The inner hole of the binuton 34 is provided with a shoulder portion 36 that can be applied to the stepped portion 35 of the first piston 33.

The plunger 27 is provided with a suction passage 37 and a discharge passage 38 which communicate with the first working chamber a lvc, and also with a suction passage 39 and a discharge passage 40 which communicate with the second working chamber 32. are penetrated at a 180 degree symmetrical position at the middle part of the plunger 27, and each prefecture entrance passage B7,
Plunger 2 is installed in each discharge passage 88.40 in the same phase as 89.
Penetrate at 18 () degree symmetrical positions between the left and right parts of No.7.

The housing 11 has suction ports 42a and 42bk that allow the suction passages 87 and 89 to coincide with each other and communicate with the joint suction passage 41 of the housing 11 during the suction stroke of the plunger 27.
On the other hand, during the discharge stroke of the plunger 27, the IC discharge passage 38 coincides with the discharge ports 43a, 43b which communicate with the intake passage of the engine, and the discharge passage 40 coincides with each other to prevent engine operation. Discharge port 44a communicating with the chamber
, 441) (Fig. 2, Fig. 5).

Each suction port 42a, 42b and each discharge port 48a, 43b, 4
4a and 44b are set to have a phase difference of 90 degrees.

If the engine malfunctions as described above, when the engine is under light load, the camshaft 17 is rotated by the near 19 of the accelerator pedal interlocking part 1 and the eccentric cam 16 is moved to the right as shown in Figs. 2 to 4. in position.

The worm wheel z2 is rotated by the worm 21 which is linked to the rotation of the two-stroke engine, and during the discharge stroke, the angular force A2B, 2B is multiplied by the concentric cam 15.15 against the biasing force of the coil spring 30. (Fig. 2), then during the suction stroke, the biasing force of the coil spring 30 causes the chevron cam 28.28
When the worm wheel 22 is fitted into the concentric cam 15° ri&] (FIG. 4), the worm wheel 22 performs two reciprocating movements per rotation in combination with the rotational movement.

In the discharge stroke, the plunger 27 together with the worm wheel 22 is moved to the right from vC2 in FIG. 4 to the state shown in FIG.
The discharge passage 38 of the first working chamber 31 coincides with the discharge port 4sa, the discharge passage 40 of the second working chamber 32 coincides with the discharge port 44b, and oil discharge is completed (Figs. 2 and 13). (a
), (bl).

However, when the engine is under light load, the second
Since the pressure inside the working chamber 32 does not rise, the discharge passage 4
Even if 0 coincides with the discharge port 44b, oil is not discharged.

When the plunger z7 rotates by 90 degrees together with the worm wheel 22 (FIG. 14), the plunger 7!7 is moved to the left together with the worm wheel 22, and the suction passage 37 of the first working chamber 31 coincides with the suction port 42a, and the 14th Figure 14 shows that the suction passage 39 of the second working chamber 32 coincides with the suction port 42tlj (Fig. Since the pressure becomes negative, oil is sucked only by the left side of the plunger 27Q, while no oil is sucked into the second working chamber 32 because the second piston 34 moves to the left due to the negative pressure and there is no change in volume.

Then, when the plunger 27 and the worm foil 22 are rotated 90 times (180 degrees from the beginning) (Fig. 15)
, the plunger 27 is moved to the right together with the worm wheel 22, and the discharge passage 38 of the first working chamber 31 is discharged.
15(a)), the discharge 1m path 40 of the second working chamber 32 is 1! ] Out r'+ Matches 441 with 1- (
In FIG. 15 (bl), only the oil in the first working chamber 31 is supplied to the engine intake passage (12th
(See figure (a)). This means that during the double suction stroke, the first
This is because oil is sucked into the working chamber 31 and no oil is sucked into the oxidation stage chamber 32.

Furthermore, the plunger 27 together with the worm foil 22 is
xT bolt (Fig. 16), the plunger 27 together with the worm wheel 22 is moved to the left from the state shown in Fig. 2, and the suction stroke reaches the state shown in Fig. IM4 (Fig. 161)
.

(Mountain).

Next, Businji A127 with worm wheel 22
9 U fD: (360 history from the beginning) When rotated (Fig. 13), the worm wheel 22 and Pubunshi A
l27 is in the state shown in Figure 4 when the sword is moved to the right and the first working chamber 31
11-1 out i Kawaji 38 out in January [+ 43 a and -w
As shown in FIG. 13 (al), the first outlet passage 40 of the second cylinder j chamber 32 coincides with the discharge rl 44 b (181st
1(1)l), only the oil in the first working chamber 31 is supplied to the intake passage of the engine (see (a) in FIG. 12).

After that, this operation is repeated.

On the other hand, when the engine is loaded, Fig. 51, Fig. 6171
Accelerator pedal] Sato'M'FA Usu No. 19 V
When the cam shirt 7 is rotated, the eccentric cam 16 becomes 11, and the movement of the plunger 27 together with the foil 2z becomes 132 times as large.

-Then, the plunger 27 rotates 90 degrees with the worm wheel Z2 from the dead center to the discharge point 11 in Fig. 5 (a
14), 1 run A with worm foil 2z
727 is moved to the left at 710-k, which is approximately twice that of light and negative at the same time, and the suction passage 37 of the first working chamber 31 is opened to the suction r'l 42 a.
Fc-matching (FIG. 14(C)), the suction passage 39 of the second working chamber 32 coincides with the suction N42b (141st channel (C)).
Mountain〕. Therefore, in the suction stroke at the discharge "second dead center" shown in FIG. 5 and the suction F dead center "1" shown in FIG.
1 is related to Kimi 1 piston 33, so it will take 1 hour, so if the oil is sucked in by the amount of left movement of plunger 27, it will be 1 hour.
At time J, the second working chamber 32 moves to the left as the second pin 1-84 is sucked by the bolt, but the shoulder 36 of the second pier 34 is moved by the first screw 83. 1. ．． 1
1, and then it becomes negative 1 due to the connection with the second binuton 34, so that the amount of movement of the plunger 27 to the left after that causes the suction to be suppressed.

Next, worm foil 2: B: 1 run to Tomo 27
When it rotates from 90 degrees (from the first position to 180 degrees) (Fig. 15, 9), the plunger 27 moves to the right with the worm wheel z2 with a stroke approximately twice that of a light load of 11 lbs, and the oil discharged from the first working chamber 31. 15 (al), 2nd work 1171 room 32, 11 exit I
IIJ path 4 () coincides with discharge II 4.41 (first
5 (bl), the oil in the first working chamber 31 is supplied to the intake passage of the engine (See 1.j in FIG. 12 (b)) At the same time, the oil in the second working chamber 32 is supplied to the engine (See (c) in Figure 12).

Furthermore, if the plunger 27 rotates by 9 () degrees (271 If from the beginning) together with the foil 22 (?
, 161 Sentence 1), the plunger 27 is moved to the left together with the worm wheel z2, and the inhalation described in ``-? It will be done once or so.

Next, when the plunger 27 is rotated 901 degrees (360 degrees from the beginning) together with the worm wheel 22 (W' 18
(Fig.) If the plunger 27 is moved to the right together with the pump foil 22, the discharge passage 38 of the first working chamber 31 will be discharged by 14J.
, '+ 481 (73% Fig. 13 ta+), the discharge passage 4 () of the second working chamber 32 coincides with the discharge n 441) (Fig. 13 (1) 'l, the discharge passage 4 of the first working chamber 3I Oil is supplied to the engine's intake oil passage ((b) in Figure 1z)
At the same time, the A-il in the second working chamber 32 is supplied to the FF working chamber of the engine (see (c) and (b) in FIG. 12).

Figures 7 and 8 of the second embodiment show the 111 excavation dead center under light load, Figure 9 shows the suction bottom dead center under light load, and Figure 10 shows the discharge bottom dead center under high load. Figure 11 shows high load II! Each of the inhalation bottom dead centers of i is 1jJ+ in+ lso1.

2 in each figure, housing sink 11, cam history 2, foil chamber 13, pump chamber 14, camshaft 17, worm 21, worm foil 22, etc. (14 or the same as in the first embodiment) Sword/Ra Explanation will be omitted.

A plunger 50 is fitted into the pump chamber 14 so as to be rotatable and movable in the axial direction.
On the right side of
2, 30 coil springs are compressed between the disc 1555 of the link part 1452 and the plunger 50, and the zH1 (1-c link 1452 of the housing 11 is fitted), and the coil is compressed. Plunge A・50 by spring 30
is biased in the left direction.

-J: fTatsu emergency room J3 (housing) 1
), a first working chamber 53 is formed by a curve with the right side of the worm wheel 22, and a second working chamber 54r is formed through which the plunger 50 is inserted from the right side to a certain depth. In the first working chamber 53, the worm foil 27! 1-7 serves as the first pinion 33 in the first embodiment, and the second working chamber 54 is provided with a second piston 51 that is slidably fitted therein, and a second screw 1-7 is provided. The sink section 51 has one sink section I'A' 52.
A flange portion 56 is provided on the disc piece 155 of the disc 155. 2nd Pinuton 51i, 1 Disc Files
It is also slidably fitted to the 55 VC.

In addition, the suction passage 87 and the discharge passage 38 that communicate with the first working chamber 53 of the plunger 50, the suction passage 39 and the 11 outlet passage 4 ('', which communicate with the second working chamber 54, and the suction r1 of the housing 11)
4Za, 4213, nl-if affected-14,3a.

481), 44a, 441) are the implementation f da j and the studs.

Therefore, even in the direction 1 of -1-, it is possible to achieve the same effect as in the first embodiment.

As is clear from the above iNj', Akira, Akira Kio is
The casing circle is connected to the moving plunger, and the first working chamber 53 is moved over the entire operating range of the engine to take in all the oil and the first working chamber 53 is connected to the other end of the plunger for a distance of 1yr. A movable bottle that strokes slowly is fitted inside, and a second working chamber is provided in which the volume changes only when the movable bottle and the plunger are lowered (Q) than the set load of the plunger. When the oil pump has a load of 1 or more, the second working chamber causes the first operation I]W
It becomes possible to completely supply oil with different discharge characteristics.

Since the size of the pump is 1ζ and the cam part is 1111mm, the pump can be made smaller and the cost can be reduced to within 100%.

[Brief explanation of the drawing]

Fig. 1 shows a 1υ side view of a conventional plunger pump, and Figs. 2 to 6 show a first embodiment of an oil pump according to the invention.
Figure 2 is a cross-sectional view of the discharge top dead center under light load. Figure 3 is a 1vT diagram at the 90 degree turn in position in Figure 2, Figure 4 is a cross-sectional view of the suction bottom dead center under a light load, and Figure 5 is a high load,
Figure 6 is a cross-sectional view of the "discharge" second dead center.
11, Figure 7 is a cross-sectional view of the second dead center under light load and discharge.
The diagram is in Figure 7! 1 turn plane 1 n 1 at In degree rotation position, Figure 9 is light load, sectional view at suction bottom dead center, Figure 10 is? rH load, cross-sectional view of discharge top dead center, Fig. 11 is a cross-sectional view of high load, suction 1ζ dead center, figure 12 is a graph of 111 outputs of 1,11, 1, 1, 1, 1, 1, 1, 1, 2, and 13 of each performance example. Figures ~ Figure 16 are plunge A
・In the operation explanatory diagram, Fig. 13 J is the A-A r plane view of No. 21 x I, Fig. 13
81-1 (c) is the same C-C cross section, No. 131 ¥1 (the mountain is 1
．． ) -1) The cross section is 1 x 1. 11...house sink, 12...cam chamber, 1
3. Warm foil chamber, 14. Pump pain,
15... Concentric cam, 16... Eccentric cam,
2 things should happen, 22...warm foil, 23.
・Type 111 cutlet・、27゜、50・・・Plunger、
29, 52 river link parts, 30... coil spring,
81.58...First working chamber, 32.54...Second
ff moving chamber, 38...l piston, 34.51...
・Second Beerton, 37.39 ・Inhalation Isanji,
3 8, 4 +1 -nt near 1'1jli
l tract, 4 z a, 42 ■)...inhalation [
", 43 a, 4 B +), 44 a,
44 +)...I'l: 11111-1.

Claims (1)

[Claims] (11 Housing 1)] Niniraranja rotatable knife - Fitted so as to be movable in the axial direction, a cam part provided at one end is supported within the housing, and the number of rotations is adjusted according to the engine load. The MI control cam is formed so that it comes into contact with the first cam which widens in the angular direction, and increases the reciprocating cut 141f of the plunger as the engine changes from light load to surface load. The part is in sliding contact with the adjacent cam of the two-note system and reciprocates in a reciprocating manner to discharge one yen of oil. /ζ fixed part (by the bottom), the shape changes over the entire operating range of the engine, and the oil purple intake P
A first working chamber for reciprocating the discharge is provided, and the curved end of the plunger is provided with a required distance AI [to reciprocate -i'iJ].
14 moving parts are fitted together (-1 applicable! IIJ1 part and plunger are formed into a second working chamber that changes volume only when the engine's set load is 1° and takes in and releases oil. An engine oil pump characterized by the following: