JPH049446Y2 - - Google Patents

Description

[Detailed description of the invention] <Industrial application field> This invention relates to a multiple pressure intensifier in which multiple plunger pumps are simultaneously driven by one fluid pressure actuated cylinder. This technology prevents the piston and plunger from tilting even if there is a difference in the load between them.

<Prior Art> A conventional multiple pressure intensifier has a structure shown in FIG. 3.

That is, the cylinder body 5 of the hydraulically operated cylinder 2
Pump body 13 of multiple plunger pump 3
are fixed in a butt shape, one piston 9 is slidably inserted into the cylinder body 5, and the pump body 1
The plunger 17 is inserted into each of the plurality of plunger chambers 16 in the piston 3, and each plunger 17 is fixed to one piston 9.

<Problems to be solved by the invention> The multiple pressure intensifier 1 is used, for example, to raise the upper mold in parallel, as shown in FIG.

That is, when pressurized fluid such as compressed air or pressure oil is injected into the drive chamber 50 in the cylinder body 5, the piston 9 is driven to move forward in the right direction in the drawing, and the four plungers 17 are simultaneously driven to move forward. Each plunger chamber 1
The hydraulic oil in each of the four hydraulic cylinders 51
By pressing up the four corners of the die plate 53 of the upper mold 52 with each hydraulic cylinder 51,
The upper mold 52 is raised parallel to the lower mold 54 while being guided by the guide post 55.

In the above conventional structure, when the upper mold 52 is lifted in parallel, when the center of gravity of the upper mold 52 deviates from the center point in plan view, a difference is created in the loads applied to each of the four hydraulic cylinders 51, and this Since a moment is generated due to the difference in the loads L of the four plungers 17, the piston 9 and the plunger 17
is tilted and twisted, and the frictional resistance of the sliding surface increases abnormally.

For this reason, transmission efficiency decreases, energy loss increases, and output decreases. Moreover,
The sliding surface is abnormally worn, resulting in poor durability.

The object of the present invention is to prevent the piston and plunger from tilting and twisting even when there are differences in the loads applied to a plurality of cylinders.

<Means for Solving the Problems> The present invention, as shown in FIGS. 1 and 2, for example, adds the following improvements to the structure of the conventional example.

That is, straight guide holes 35a and 35b are formed in the end wall 7 of the cylinder body 5 and the pump body 13, respectively, parallel to the axes of the cylinder body 5 and the plunger chamber 16, and straight guide shafts 37a and 37b are formed from both end surfaces of the piston 9. Each straight guide hole 35a, 35b
fixedly extending concentrically with each linear guide shaft 37a,
37b is fitted into each of the straight guide holes 35a and 35b so as to be able to freely guide and slide.

<Function> According to the present invention, both linear guide shafts 37a, 37
b is linearly guided by both linear guide holes 35a and 35b over a long distance along its axial direction, thereby preventing its inclination. Along with this,
The piston 9 fixed to both linearly moving guide shafts 37a, 37b and each plunger 17 fixed to the piston 9 are similarly guided linearly and prevented from tilting.

Therefore, when each plunger 17 is propelled by the piston 9, when a load difference occurs between each plunger 17 and a moment is generated to prevent the piston 9 from tilting, that moment is transferred to both linear guide shafts 37a. , 37b, and is received by both straight guide holes 35a, 35b. Thereby, the piston 9 and the plunger 17 are guided straight and smoothly along both the linear guide holes 35a, 35b via the linear guide shafts 37a, 37b, and are not tilted or twisted.

<Example> Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal sectional front view of the multiple pressure intensifier 1, and the second
The figure shows a sectional view taken along the - line in FIG. 1.
The multiple pressure intensifier 1 is comprised of a pneumatic double-acting hydraulic cylinder 2 and a hydraulic multiple plunger pump 3 interlockingly connected thereto.

The cylinder body 5 of the hydraulic cylinder 2 has a cylinder tube 6 and an end wall 7 fitted to the left end of the cylinder tube 6 in an airtight manner.
8 is an O-ring. A piston 9 is inserted into the cylinder tube 6 via a pair of U gaskets 10, 10 in an airtight and slidable manner.

On the other hand, the pump body 13 of the multiple plunger pump 3 is hermetically fitted to the right end of the cylinder tube 6. 14 is an O-ring. The pump body 13 is fixed to the cylinder body 5 through a plurality of tie rods 15 in an abutting manner. The pump body 5 has four plunger chambers 16 arranged at equal intervals in the circumferential direction and oriented laterally to the axis.
7 is inserted. The plunger 17 is slidable in an oil-tight manner on the fitting surface of the plunger chamber 16 via an O-ring 19 and a U-packet 20.

Further, a pump cover 21 that closes the plunger chamber 16 is screwed to the right end surface of the pump body 13 via a plurality of bolts 22.
1 and each plunger chamber 16 are oil-tight via an O-ring 23. The discharge hole 24 formed in the pump cover 21 is connected to a hydraulic cylinder (not shown) via a discharge nozzle 25.

Further, the plunger chamber 16 communicates with a hydraulic oil storage tank (not shown) via an oil supply hole 26.

The left end of each plunger 17 is hermetically fixed to the piston 9 via a bolt 28. 29
is an O-ring.

Of the left and right chambers 5a, 5b in the cylinder body 5 partitioned by the piston 9, a port 31 formed in the end wall 7 is opened in one of the chambers 5a, which is used as a drive chamber, and A port 32 formed in the pump body 13 is opened in the chamber 5b.

The multiple pressure intensifier 1 operates as follows.

FIG. 1 shows the state before the start of operation, with one chamber 5a communicating with an air pressure source and the other chamber 5b open to the atmosphere by a directional control valve (not shown). When air pressure is applied to one of the chambers 5a, the piston 9 advances each plunger 17, and an increased hydraulic pressure is generated in each plunger chamber 16 in accordance with the area ratio of the piston 9 and plunger 17. This oil pressure is transmitted from the discharge nozzle 25 to a hydraulic cylinder (not shown). In this case, a load L is applied to each plunger 17 from each of the hydraulic cylinders.

Contrary to the above, when one chamber 5a is opened to the atmosphere and the other chamber 5b is communicated with the air pressure generation source, the piston 9 moves the plunger 17 backward, and the oil pressure in the plunger chamber 16 decreases.

In the multiple pressure intensifier configured as described above, the piston 9
And guide means for guiding the plunger 17 straight is provided. This guide means is composed of a guide hole 35 formed in both the cylinder body 5 and the pump body 13, and a shaft member 37 fixed to the piston 9 and fitted into the guide hole 35.

First, the guide hole 35 will be explained. A linear guide hole 35a is penetrated through the end wall 7 of the cylinder body 5 coaxially with the axis thereof. In addition, a linear guide hole 35b is provided in the pump body 13 on the same axis as the axis thereof.
is penetrated.

The shaft member 37 also includes a linear guide shaft 37a that extends from the left end surface of the piston 9 and fits into the linear guide hole 35a, and a linear guide shaft 37a that extends from the right end surface of the piston 9 and fits into the linear guide hole 35b. It is integrally molded with the guide shaft 37b. A midway portion in the longitudinal direction of the shaft member 37 is inserted into a through hole 9a formed on the axis of the piston 9, and is clamped and fixed to the piston 9 in an airtight manner via an enlarged diameter portion 38 and a lock nut 39. 42 to 44 are O-rings that seal the shaft member 37, and an air vent hole 45 is formed in the pump cover 21.

In addition, in this embodiment, both straight guide holes 35a,
35b to the cylinder body 5 and pump body 1, respectively.
3, but instead of this, a plurality of both straight guide holes 35a, 35b may be formed. In this case, it is preferable that both the linear guide holes 35a, 35b are arranged parallel to the axes of the cylinder body 5 and the plunger chamber 16 and at equal intervals in the circumferential direction.

Furthermore, although the fluid pressure operated cylinder 2 is of a pneumatic type, it may be of a hydraulic type.

<Effects of the Invention> The present invention has the following effects because it is configured and operates as described above.

That is, even if there is a difference in the load applied to the plunger, the piston and the plunger are guided straight and smoothly along both the linear guide holes via both the linear guide shafts, and are not tilted or twisted. Therefore, an abnormal increase in frictional resistance between the sliding surfaces of the piston and the plunger is prevented. As a result, there is no reduction in transmission efficiency, increased energy loss, or reduction in output, and
Abnormal wear of the sliding surface can be suppressed and durability can be improved.

In addition, both linear guide holes and both linear guide shafts are
When positioned coaxially with the axis of the cylinder body and the center axis of the pump body, the eccentric distance of the linear guide hole and the linear guide shaft is short no matter which plunger it is from, so the difference in load is Therefore, regardless of which plunger the moment is applied, it can always be kept to a small moment without much difference, so the linear guide shaft can be used with a small one.
All you need to do is set up a book.

[Brief explanation of the drawing]

Figures 1 and 2 show an embodiment of this invention; Figure 1 is a longitudinal sectional front view of a multiple pressure intensifier;
FIG. 3 is a sectional view taken along the line - in the figure, and is a schematic diagram showing a conventional example. DESCRIPTION OF SYMBOLS 1... Multiple pressure intensifier, 2... Fluid pressure operation cylinder, 5... Cylinder body, 7... End wall, 9... Piston, 13... Pump body, 16... Plunger chamber, 17... Plunger , 35a, 35b...
Straight guide hole, 37a, 37b...straight guide shaft.

Claims (1)

[Claims for Utility Model Registration] 1. The pump body 13 of the multiple plunger pump 3 is fixed to the cylinder body 5 of the fluid pressure operating cylinder 2 in abutting manner, and one piston 9 is slidably inside the cylinder body 5. Insert the pump body 13
In a multiple pressure intensifier configured by inserting a plunger 17 into a plurality of plunger chambers 16 and fixing each plunger 17 to one piston 9, a straight line is inserted into the end wall 7 of the cylinder body 5 and the pump body 13, respectively. Guide holes 35a, 35b
are formed parallel to the axes of the cylinder body 5 and the plunger chamber 16, and the linear guide shafts 37a, 37b are inserted into each linear guide hole 35 from both end surfaces of the piston 9.
a, 35b, and extend each linear guide shaft 37a, 37b concentrically with each linear guide hole 35a, 35b.
A multiple pressure intensifier 2 characterized in that the linear guide holes 35a, 35b and the linear guide shafts 37a, 37b are fitted in the cylinder body 5 in a slidable manner.
The multiple pressure intensifier according to claim 1, which is located coaxially with the axis of the pump body 13 and the central axis of the pump body 13.