JPS5847270Y2 - kiyuyu pump - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a double plunger single-type oil supply pump that can prevent damage to the pump mechanism when the plunger drive motor is reversed.

Due to its characteristics, the lubricating oil delivery pressure of the lubricating pump used in the central lubrication system is generally high (30 to 210 Ky/
(crrl), and its pump structure mainly uses a single plunger type.

Generally speaking, there are two types of plunger type: single plunger type and double type. It is easily affected by dirt and foreign substances contained in the oil, and its reliability is not sufficient.

The latter is equipped with two plungers, and these plungers act in a correlated manner so that they have the same effect as a check valve, but this type of pump has two plungers that operate in a correlated manner. If the direction of rotation of the motor were to be reversed, the timing of the plunger's operation would be disrupted, and abnormal force would be applied to the pump's structural parts, such as the plunger and conduction section, potentially damaging them. be.

An example of conventional safety measures when the rotational direction of the plunger drive motor of the pump is reversed is shown in FIGS. 2 and 3.

FIG. 2 shows a structure in which a rupture disc 102 that ruptures when a hydraulic pressure higher than a predetermined pressure is applied to the main cylinder 105 also serves as a sealing backing.

Although it is structurally simple, it needs to be replaced after one use, and has the disadvantage that the bursting pressure becomes unstable due to fatigue when used for a long period of time.

In addition, in FIG. 2, 101 is the main plunger 103.
104 is a relief outlet, and 106 is an oil inlet.

Figure 3 shows a structure in which a coupling 109 for preventing reverse rotation is provided between the motor shaft 107 and the plunger drive shaft 108.This coupling 109 is designed to slip during reverse rotation, but the slip mechanism is complicated. However, there are also problems in terms of cost.

In FIG. 3, 110 is a motor, 111 is a pump cylinder, 112 is a crank and connecting rod, and 113 is a pulp plunger.

The present invention solves the above-mentioned drawbacks of the conventional device and provides a double plunger single-type oil supply pump that makes it possible to prevent damage to the pump mechanism when the plunger drive motor is reversed.According to the present invention, , a main cylinder 5 and a valve cylinder 12 provided in the pump cylinder 13, a main plunger 1 and a valve plunger 2 fitted in both the cylinders 5 and 12 and reciprocating within the cylinders; In a double plunger one-type oil supply pump consisting of an oil inlet 6 that supplies oil to the main cylinder 5 and a communication port 10 that communicates the main cylinder 5 and the valve cylinder 12, the inside of the part connected to the main cylinder is A spring 4 and a piston 3 are provided in the spring 4 and a piston 3, and a branch passage 8 is provided between the spring storage portion 11 and a valve cylinder 12 located on the oil discharge side 9 from the top dead center of the pulp plunger, and a branch passage 8 is provided to communicate the two. There is obtained an oil supply device characterized in that a branch passage 1 is provided which communicates the branch passage 8 with the main cylinder 5 when the cylinder 3 is moved by constant pressure oil.

Next, the present invention will be explained with reference to the drawings.

Figure 1 is a vertical sectional view of one embodiment of the present invention, Figure 4 (1) -
(6) is an explanatory diagram of the operation of the double plunger type oil supply pump, and FIG. 5 is a schematic diagram showing the connection relationship between the plunger and the drive shaft.

1. The operation of the double plunger one-type fuel pump shown in FIG. 4 is as follows.

(1) Oil is sucked into the main cylinder 5 from a tank (not shown) through the oil inlet 6 which is in an open state.

At this time, the connecting port 10 is closed by the pulp plunger 2.

(2) At the same time as the main plunger 1 advances to the left and closes the oil inlet 6, the pulp plunger 2 retreats to the right and opens the communication port 10.

(3) As the main plunger 1 moves forward in the left direction, the oil in the main cylinder 5 flows through the communication port 10 to the valve cylinder 1.
Pushed out into 2.

(4) At the same time as the main plunger 1 finishes pushing out the oil, the pulp plunger holder 2 moves forward to the left and closes the communication port 10.

(5) While the pulp plunger 2 is sending oil to the oil supply line through the discharge port 9, the pulp plunger 2 closes the communication port 10 in the main cylinder 5, and the main plunger 1 is directed to the right. It retreats, creating a vacuum.

(6) When the main plunger 1 is further retreated to the right and the oil inlet 6 is opened, new oil is sucked into the main cylinder 5 by the aforementioned vacuum.

At this time, the valve plunger 2 begins to retreat.

The plunger 1a (including the main plunger and pulp plunger) is connected to the crank 4a as shown in FIG.
It is connected to a drive shaft 3c connected to a motor via a connecting member 2a and a connecting member 2a.

When the drive shirt 3c rotates, the plunger 1a reciprocates by the eccentric crank 4a.

When the drive shaft 3c is rotating normally, the main plunger
1 and the pulp plunger 2 reciprocate with a certain correlation as described above, but if the drive shaft 3c connected to the motor is reversed, the opening timing of the communication port 10 will be incorrect, and the main cylinder While the oil outlet of -5 is closed, the main pusher 1 performs a pushing operation, so the oil pressure in the main cylinder -5 becomes abnormally high.

The operation of the plunger during reverse rotation of the motor is as shown in FIGS. 4 (6) to (5), (4), (3), etc.
・It will operate in the opposite direction.

As shown in FIG. 1, the fuel pump of the present invention has a piston 3 and a spring 4 housed in a main cylinder 5 adjacent to each other, and a part of the main cylinder 5 housing the spring 4 and a valve cylinder 12. The branch passages 8 and I are provided between the main cylinder 5 and the valve cylinder 12 after the piston 3 has moved by pressing the spring 4 with a constant oil pressure, respectively, to communicate with each other. The piston 3, the spring 4 and the branch passage 7.8 form a safety mechanism when the motor of the oil supply pump of the present invention is reversed.

That is, under normal conditions, the hydraulic pressure generated by the pulp plunger 2 flows into the spring storage part 11 through the branch path 8, and acts on the piston surface 3b where the spring 4 contacts the piston 3, so that the piston 3 is in the position shown in FIG. The spring storage portion 11 is fixed and the right main cylinder 5 is isolated from each other.

In this state, the oil entering from the oil inlet 6 is discharged at high pressure to the discharge port 9 via the pulp cylinder 12 due to the action of the double plunger.

On the other hand, if the motor and the drive shirt (3c) connected to the motor are reversed, the spring storage portion 11
Since the oil pressure in the right main cylinder 5 is lower than that in the right main cylinder 5, the oil pressure generated by the extrusion stroke of the main plunger 1 acts on the piston surface 3a, and the piston 3 presses the spring 4 and moves to the left.

In that case, the oil escapes from the main cylinder 5 after the movement of the piston 3 and directly through the branch path I to the discharge port 9, so the oil pressure in the main cylinder 5 does not increase, and the plunger 3 moves as in the conventional case. Since the pump mechanism and the conductive section can be protected without any abnormal force being applied to them, it is possible to prevent damage to the pump mechanism when the motor is reversed.

Since the spring 4 only serves to return the piston 3 to its original position when it moves to the left, there is no need to use a force that takes into account hydraulic pressure.

In summary, the effects of the present invention are as follows.

(1) Since a safety mechanism consisting of the piston 3, spring 4, and branch passage 7.8 is provided, the pump mechanism will not be damaged even if the drive shaft 3c is reversed, and the performance of these components will also change. Since it is not a permanent item, it can be used over and over again.

(2) Spring storage part 1j and pulp cylinder 12
Moreover, since a branch passage 8 is provided between the piston 3 and the oil discharge port 9 side from the top dead center of the piston 3, which communicates the two, (a) During normal rotation, the discharged hydraulic pressure is transferred to the piston 3b&c.
Therefore, even if the hydraulic pressure generated by the extrusion stroke of the main plunger 1 acts on the piston surface 3a, the pressures cancel each other out and the piston 3 remains stable without moving. .

(b) When the motor is reversed, the pressure in the main cylinder 5 becomes higher than the pressure in the pulp cylinder 12, so the piston 3 moves to the left and the oil in the spring storage part 11 and the main cylinder 5 escapes. A path is formed, and the main cylinder -5
This can prevent damage to the pump mechanism by preventing pressure build-up within the pump.

(3) Operation reliability is higher than that of conventional methods.

As described above, the present invention provides a double plunger single-type oil supply pump that makes it possible to prevent damage to the pump mechanism when the motor reverses rotation, and has great industrial value.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of one embodiment of the present invention, Fig. 2 is an example of a safety mechanism for reversing the plunger drive motor of a conventional refueling pump, and Fig. 3 is the same (different from the conventional example). An example of a safety mechanism, Figures 4 (1) to (6) are operational diagrams of a double pusher one-type refueling pump, and Figure 5 is a schematic diagram showing the connection relationship between the plunger and the drive shaft. . As shown in the figure, 1... Main plunger, 1a...
... Plunger (including main plunger and pulp plunger), 2 ... Pulp plunger,
2a...Connecting rod, 3...
・Piston, 3a. 3b... Piston surface, 3c... Drive shaft, 4... Spring, 4a...
Crank, 5...Main cylinder, 6...
・Oil inlet, 7, 8... Branch road, 9...
Oil discharge port, 10... Connection port, 11...
Spring storage part, 12...Pulp cylinder, 13...Pump cylinder, 14...
...Crankshaft, 1010. -0-0 Main plunger, 102... Bursting disc, 103...
Rupture disc presser, 104... Relief date, 105
...Oil outlet, 106...Oil inlet, 1
07...Motor shaft, 108...Plunger drive shaft, 109...Coupling for preventing reverse rotation, 110...Motor, 111...・
Pump cylinder, 112... Crank and connecting rod.

Claims (1)

[Scope of utility model registration request] The main cylinder 5 and the pulp cylinder 12 provided in the pump cylinder 13, both cylinders 5,
A main plunger 1 and a pulp plunger 2 that are fitted in a cylinder 12 and reciprocate within the cylinder, an oil inlet 6 that supplies oil to the main cylinder 5, and a main cylinder 5 and a pulp cylinder 12. In this double plunger one-type oil supply pump, a spring 4 and a piston 3 are provided in the part connected to the main cylinder, and oil is supplied from the top dead center of the spring storage part 11 and the pulp plunger. A branch passage 8 is provided between the pulp cylinder 12 located on the discharge side 9 and the main cylinder 5, and a branch passage 8 is provided to communicate the two, and a branch passage 8 is provided to communicate the branch passage 8 with the main cylinder 5 when the piston 3 is moved by constant pressure oil. A fuel pump characterized in that a passage 7 is provided.