JPS6210485A - Improvement in pump - 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 A. Field of Industrial Application The present invention relates to a pump or improvements related to the pump, and more particularly to a liquid pump for use in various industrial fields, particularly in the fields of milling and cement pouring.

BACKGROUND OF THE INVENTION A variety of liquid pumps are currently being produced for use, including centrifugal pumps, reciprocating pumps, vibratory pumps, screw pumps, single pumps, and the like. Each of the above types of pumps has its own advantages and disadvantages in performance. For example, centrifugal pumps pump relatively large volumes of liquid at relatively low pressures, but pump out less liquid as pressure increases.

At Kishimamomi Industries, we prefer pumps that can push out relatively small volumes of liquid at relatively high pressures, such as reciprocating pumps, while pumps that can push out relatively large volumes of liquid (usually centrifugal pumps) are preferable. A pump is needed to clean the massage hole. After these two steps, a special pump is also required to carry out the cement injection operation. Thus, six sets of power plants and piping systems must be provided for six different types of pumps, creating numerous service and maintenance problems while resulting in very low efficiency.

To solve the above problems, multi-stage centrifugal pumps have been proposed which have a constant volume of liquid of 1 tt at relatively high pressures, but require additional power. However, it is still unsuitable for milling operations as it is easily disturbed by sand, mud and stones carried by the circulating water during operation. Other recently proposed pumps, such as multi-piston reciprocating pumps and screw pumps, have made certain improvements, but in some respects do not adequately meet the demands of kneading operations. In particular, it is very large and requires a large amount of power, making it uneconomical. For example, typically 1977E'/h (5000 US gallons)
A screw pump pumping a liquid volume f would require a length of 4 m (12 ft) and a power of 15 KW (20 horsepower).

Ha. PROBLEMS TO BE SOLVED BY THE INVENTION It is an object of the present invention to provide a pump for use in kneading, cement injection, etc., with which the above-mentioned disadvantages can be overcome or at least alleviated.

two. SUMMARY OF THE INVENTION Accordingly, the present invention comprises a double-acting diaphragm pump, which pump has at least one diaphragm, first and second chambers, a device for bending the or each diaphragm, and, during use, During the forward stroke, the volume of the first chamber increases and the volume of the second chamber decreases, and during the return stroke, the volume of the first chamber increases and the volume of the second chamber decreases.
and a device in which the volume of the chamber is reduced and the volume of the second chamber is increased.

Thus, the present invention can provide a pump that is simple in construction and lightweight, has a large capacity of liquid at high pressure, and requires only a small amount of power when operating with mud, water or even cement injection. . Only one such pump is required for processes involving mashing, pouring and cement injection. Thus, the operations of milling out and cement injection can be carried out sequentially by using a drill rond for cement injection and much higher efficiency can be achieved.

In order to further understand the invention and to show how the advantages are achieved, reference is made to the accompanying drawings of exemplary embodiments.

E. Embodiment and operation Now referring to the drawings, the pump of the present invention used in the kishimomi industry has two large flexible diaphragms acting in opposite directions and a low speed motor of 100 to 120 revolutions per minute. It is a double acting, double diaphragm pump. The low speed motor 3 is fixed to the frame 1 by four bolts 2, and the pump casing 5 is fixed to the frame 1 by four bolts 4.
It is fixed again to frame 1. The drive shaft 6 of the motor 3 is engaged by the rotary plate 7, and the shaft 9 with a 7-lunge is fixed in the eccentric hole of the rotary plate 7 by four bolts, so that the rotation of the drive shaft 6 of the motor 3 is controlled by the rotary plate. 7 and the motor 3 to move the flanged shaft 9 about a common axis. A ring 11 having a variable length between the bearings has a ring on a part of the flanged shaft 9 extending beyond the rotating plate 7, and four bearings equal to the total length of the extended portion of the flanged shaft 9. 2
A pair of bearings is installed. Bearing 10 has 6 bolts 13
and axially closed by a cover 12 attached to the outer end of the seven-flange shaft 9 by means of six spring washers. An extension of the flanged shaft 9, with a bearing, slides along an elongated groove in a swinging arm 15, the other end of which is connected to the support [17] by a shaft 16 passing through a hole 18.

Since six bearings are attached to the shaft 16, the swing arm 1
5 can swing around the axis of the hole 1B of the support device 17. A hole 19 is provided in the swinging arm 15 below the hole 18, through which the metal threading shaft 20 is also mounted by a set of bearings 21 and a ring 22, so that the swinging arm 15 is connected to the shaft 26, respectively.
．． 27 is also connected to the connecting block 23 which has holes 24 and 25 on either side of the hole 19 so as to connect the connecting block to the connecting rods 28, 29.

It is understood that the drive mechanism for each diaphragm is the same for both mechanisms, but will now be described with reference to the left hand diaphragm as shown in FIG. The outer end of the articulation 1I 28.29 extends through the piston head 30.31 and is screwed into the piston cover 32. When the piston cover 32 is screwed on, the central parts of the diaphragms 33, 56 are tightly clamped between the piston head and the piston cover by the inner part 34 of the piston cover, while the peripheries of the diaphragms 33, 56 are connected to the casing 5. With the pump cylinder 36 and six bolts 38 (c)
The cylinder 36 is tightly tightened with a pump cover 37 in the housing 35, thereby connecting the pump cylinder 36 to the casing 5. The valve devices 40 and 39 are respectively connected to the pump cover 3
7 is attached to the upper and lower parts. Lower valve device 39
is connected to the pump cover 37 by an adapter 41,
Meanwhile, the upper valve device 40 is also connected to the pump cover by an adapter 61. Valve device 39.40 is steel ball 42.4
3 and ball seats 44 and 45 respectively. The ball seats 44,45 are similar in construction except that the upper part of one ball seat 45 has six or four small posts 46 of triangular cross-section which limit the movement of each ball 43. There are no such posts on the other valve seats 44, but two or six posts are placed on the pump cover to perform a similar function and limit the movement of their respective balls 42.

The pump is approximately symmetrical about the center line as shown in FIG. 39. It has two separate mouths connected to 51 and the whole. The outlet pipe 52 of the pump has its central port connected to the kneading machine or the like in use, and the other two mouthpieces each connected by seven flange 53.54 to the outlet valve 40.55 of the pump, also in T-shape. be.

The diaphragm 33.56 has a six layer sandwich construction. The two outer layers are constructed from 3 to 6 mm thick rubber plates with a total thickness of 10 to 12 inches, while the central layer is comprised of elastic sheet metal that provides stiffness to the diaphragm. The sheet metal surfaces are lubricated with grease to completely dissipate heat from friction.

When operating a double-acting double diaphragm pump, it should first be ensured that the machine is level.

Otherwise, the steel balls 42, 43 are unlikely to be seated correctly and thus seal the valve completely, which results in low efficiency of the pump. The central opening of the inlet tube 48 is then connected with a hose to a water tank, flowing pond, etc., while the central opening of the outlet tube 52 is connected to the outflow inlet of a rotary head for a milling machine or the like. When the motor 3 starts (rotating at 100 to 120 revolutions per minute with right or left rotation), the motor shaft 6 rotates the rotary plate 7, and the shaft 9 with seven flange fixed to the plate 7 rotates around the circumference. 57. 7
The extension of the flange-equipped shaft 9 is the elongated groove 5 of the swing arm 15.
8, the movement of the flanged shaft 9 causes the swing arm 15ffi to swing around the axis of the hole 18 with an amplitude of 36 degrees.

Since the connecting block 23 is connected through the entire hole 19, when the swinging arm 15 swings, it reciprocates.

As shown in FIG. 2, when the swing arm 15 swings to the left, it pushes the connecting block 23 and the connecting rod 28 through-hole diaphragm 33 to the left, while the diaphragm mount [56] is pulled to the left. The pressure created in the left hand pump space pushes all the liquid out of the pump pushing the steel ball 42 tightly against its seat so as to seal the lower valve, while leaving the steel ball 43 from its seat so as to open the upper valve. to cause the liquid to flow out into the outlet tube 52. Meanwhile, the back pressure generated in the pump space on the right side draws liquid from the inlet pipe 48 into the pump, and the steel ball 62 is pushed up by the liquid so as to open the inlet valve 51.
Steel ball 59 closes 5.

be lowered. When the swinging arm 15 swings to the right, the liquid in the right hand pump space is pushed into the outlet tube 52 and the left hand pump space draws liquid from the inlet t48. Thus, once the motor 3 is started, liquid is continuously pumped from the water tank into the kneading machine.

The left-right travel length of the flexible diaphragm is approximately 3
It is 0m. The liquid pressure created by the pump is approximately 14
k<9/ctrt'(1,4×10' Newtons per square meter (200 Bonds per square inch)) can be reached. The liquid capacity of the pump can be calculated as follows:

3.2 x 10-” cubic meters ([], 85 US
gallons) can be moved per stroke. If the piston moves 100 times per minute (the motor has a speed of 100 revolutions per minute), then 0.32 cubic meters (85 US
gallons) can be moved every minute. Therefore, the pump capacity is approximately 19 cubic meters (5,000 US gallons) per hour.

[Brief Description of the Drawings] Fig. 1 is a front view of the pump of the present invention, Fig. 2 is a sectional view of the pump of Fig. 1, Fig. 6 is a side view of the pump of Fig. 1, and Fig. 4 is a front view of the pump of the present invention. FIG. 5 is a cross-sectional side view of the pump shown in FIG. 1, and FIG. 5 is a plan view of the pump of FIG. 1: Frame, 3: Low speed motor, 5: Casing, 6
: Drive shaft, 7: Rotating plate, 9: Shaft with flange, 15: Digging arm, 16: Shaft, 17: Support device, 23: Connecting block, 26.2T: Shaft, 2B, 29: Connecting rod, 30.31
: Piston head, 32: Piston cover, 34: Inner part, 33.56: Diaphragm, 36: Pump cylinder, 37: Pump cover, 39.40: Valve device, 42.
43.59.62: Steel ball, 44.45: Ball seat, 46
: Small pillar, 48: T-shaped inlet pipe, 51: Inlet valve, 52
: Outlet pipe, 55: Outlet valve, 58: Long and narrow groove.

Claims (15)

[Claims] (1) A double-acting diaphragm pump, the pump comprising at least one diaphragm, first and second chambers, and a device for bending the or each diaphragm;
During use, the volume of the first chamber increases and the volume of the second chamber decreases during the forward stroke, and the volume of the first chamber decreases and the volume of the second chamber increases during the return stroke. A double-acting diaphragm pump characterized in that it has a device for doing so. (2) A claim characterized in that the invention comprises a first diaphragm that limits the first chamber, a second diaphragm that limits the second chamber, and a bending device arranged so as to simultaneously bend both diaphragms. Pump according to paragraph 1. (3) The bending device comprises a motor and a pivotable device that changes the rotation of the motor into longitudinal movement of the or a portion of each diaphragm. Pumps listed in section. (4) The pump according to claim 3, wherein the drive shaft of the motor engages with a rotating plate that supports an eccentric shaft. (5) the pivotable device has a swinging arm, the swinging arm being pivotable about the casing of the pump, and the eccentric shaft being slidable in an elongated groove in the swinging arm; A pump according to claim 4, characterized in that: (6) The pump according to claim 5, wherein the motor and the casing of the pump are mounted on a frame. (7) a piston rod bending the or each diaphragm is spaced from the pivot axis of the swing arm with respect to the casing and pivotable with respect to the swing arm about the pivot axis parallel to the pivot axis; The pump according to claim 5 or 6, characterized in that: (8) the or each piston rod extends through the piston head and is screwed into the piston cover, the central portion of the or each diaphragm being clamped between the piston head and the piston cover, while the or each diaphragm 8. A pump according to claim 7, characterized in that the periphery of the diaphragm is clamped between an annular member and a cover of the pump. (9) A pump according to claim 8, characterized in that the or each annular member is connected to the casing, and valves are attached to the upper and lower parts of the pump cover or each pump cover. . (10) Each valve is a ball valve having a steel ball and a valve seat, and the valve seat of the or each upper valve has a device for guiding the movement of the respective ball, and the lower valve or 10. A pump as claimed in claim 9, characterized in that each lower valve has a device on the pump cover for guiding the movement of the respective ball. (11) The diaphragm or each diaphragm has an overall thickness of 10 mm to 12 mm and two outer layers of 3 m.
Claims 1 to 10 characterized in that it has a three-layer sandwich structure made of rubber plates with a thickness of from m to 6 mm, and a central layer of elastic sheet metal.
Pumps described in Section 1. (12) The pump has a central port connected to the supply pipe, one of the other two ports connected to the inlet valve of the first chamber, and the other two ports connected to the inlet valve of the second chamber. a T-shaped inlet pipe having another one of the ports, a central port connectable to a kneading machine and one of the other two ports connected to the outlet valve of the first chamber and an outlet valve of the second chamber; 12. A pump according to any one of claims 1 to 11, characterized in that it has a T-shaped outlet pipe with another one of the other two ports connected to the pump. . (13) A pump according to any one of claims 1 to 12, characterized in that the stroke length of the or each diaphragm is approximately 30 mm. (14) The fluid pressure exerted by said pump is about 14
kg/cm^2 {1.4 x 10^6 Newtons per square meter (200 pounds per square inch)} pump. (15) The capacity of the pump is approximately 19 m^3/h (5,0
15. A pump according to any one of claims 1 to 14, characterized in that the pump is 00 US gallons).