JPH07332230A - Series type double cylinder type mortar pump - Google Patents

Abstract

PURPOSE: To provide a mortar pump capable of discharging even viscous mortar at a constant rate with no pressure loss. CONSTITUTION: In this mortar pump, a suction/compression cylinder 29, a hydraulic cylinder 10 and a push-feeding/storing chamber cylinder 30 are arranged in line from an outlet 4 of a hopper 1, while a mortar passage 11a is formed in the hydraulic cylinder 10. Accordingly, because mortar is sucked and discharged in line, even the mortar having large viscosity is discharged at a constant rate with a small pressure loss.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The disclosed technology relates to a mortar pump used for coating a steel frame of a building with mortar.

[0002]

2. Description of the Related Art As is well known, in constructing a high-rise building, it is a common mode to employ a steel frame structure for efficient construction, shortening the construction period, and improving earthquake resistance. In construction and the like, in order to improve dustproofness, soundproofing and fire resistance, it is adopted as an important construction technique to inject and coat mortar on the surface of the steel frame with a mortar pump.

A conventional mortar pump of the type described above is constructed as shown in FIG. 6, and when the main piston 50 moves backward, the suction valve 51 is opened hydraulically and the discharge valve 52 is closed. When mortar (not shown) flows into the pump cylinder 53, and mortar inside the pump cylinder 53 (on the rear side of the main piston 56) is discharged from the discharge port 55 through the connecting conduit 54, and conversely when the main piston moves forward. The suction valve 51 is closed,
The discharge valve 52 is opened, and a part of the mortar existing inside the pump cylinder 53 in front of the main piston 50 is charged through the inside of the connecting conduit 54 to the rear side of the main piston 56 and is discharged from the discharge pipe 55 repeatedly. For example, it is a single-cylinder type differential drive system as disclosed in Japanese Patent Publication No. 58-20021.

As described above, in the conventional type, the mortar is configured to be filled between the main piston 56 and the cylinder drum at the rear surface of the main piston 56 through the connecting conduit 54 at the time of discharge, so that the ground pressure is reduced. It is known that the pulsating development of the material approaches "0" as the area ratio between the front surface and the rear surface of the receiving piston 56 becomes about 1/2.

Therefore, in order to have the pumping force of the material when the main piston 56 moves forward and backward, the diameter ratio of the area between the front surface and the rear surface of the main piston 56 of the hydraulic cylinder is about 1/2. The prevailing method is the constant pressure difference method.

[0006]

However, in the single-cylinder type differential drive type mortar pump as described above, in order to fill the material on the rear side of the main piston 56, the connecting conduit 5 is required.
However, at this time, the material is filled in the direction of 90 degrees, 180 degrees, and twice in a circulatory manner through the hydraulic discharge valve 52, so that the mortar material is viscous. There is a drawback that the pressure loss increases as the strength increases, and the mortar material leaks slightly, due to the wear of the packing in the cylinder lock 57 due to the repeated reciprocating motion of the main piston 56. Further, there is a problem that the volume of the pump becomes large, such as a limit switch for switching the forward and backward movements of the piston rod 50 being provided outside the cylinder, and the structure becomes so complicated, resulting in an initial cost and running. There was a drawback that the cost was high.

[0007]

The object of the present invention is to solve various problems of the single-cylinder type differential drive type mortar ratio pump based on the above-mentioned prior art.
Alternatively, the primary goal is to provide a mortar pump that does not have any pressure loss due to the bending flow phenomenon at the time of discharge, and to provide a mortar pump that has the characteristic that mortar is always pushed with the same force even when the piston is moving forward or backward. The second is to do this, and the third is to provide the structure of the pump in a simple and compact manner without providing a limit switch or the like outside the conventional discharge valve of this type and the pump.

[0008]

In order to solve the above-mentioned problems, the cylinder of the mortar pump is for suction, and in order to solve the above-mentioned problems, the structure of the invention of the present application is based on the above-mentioned object. Cylinder for extrusion and for pushing,
The storage cylinder is separated into cylinders, which are connected to the front and rear of the transport cylinder as cylinder blocks and connected in a straight line.The piston rod of the hydraulic cylinder has a mortar passage inside. Manufactured in a hollow shape, equipped with piston heads on both ends, suction and push cylinders are connected to the suction valve side for push, and a check valve is provided at the end of the storage chamber cylinder. By being configured as an in-line type mortar pump with an attached discharge port,
By eliminating the curved flow phenomenon at the time of mortar discharge and eliminating the pressure loss, the mortar is always pushed by the same force when the piston moves forward and backward, and by providing a check valve inside the discharge port No hydraulic discharge valve is required, and a cushion room is formed in the cylinder block that connects the hydraulic cylinders to each cylinder, and two hydraulic passages are provided inside the cushion room to provide one of the two hydraulic passages. By changing the flow of hydraulic pressure due to the difference in hydraulic pressure generated from the hydraulic passages, the forward and backward movement of the pump rod is repeated so that there is no need to provide a limit switch or the like outside the pump as in the past. It was taken.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The following will describe one embodiment of the invention of this application with reference to the drawings.

It should be noted that parts that are the same as those in FIG. 6 will be described using the same symbols.

The overall structure of the in-line recuperative cylinder pump for coating the steel frame, which constitutes the subject matter of the invention of this application, is as shown in FIG.

That is, a hydraulic drive device 7 is operated vertically below the outlet 4 of the mortar S formed below the front end of a known hopper 1 having a motor 3 installed therein and a transfer screw 2 provided therein. A suction valve 5 is installed, which is connected to the front end side of the suction / compression cylinder 29, and is connected to the front end side of the hydraulic cylinder 10 at the other end side via a cylinder block 14a.

A cylinder 30 for pushing and storing chamber is connected to the other end of the hydraulic cylinder 10 through a cylinder block 15a, and a discharge port 32 is provided at the end of the cylinder 30 for pushing and storing chamber. A check valve 33 is connected to the discharge port member 31 provided with a spring 32.

The piston rod 11 of the hydraulic cylinder 10 has a hollow shape in which a mortar passage 11a is bored, and a piston ring 12 is fixedly provided at the center of the piston rod 11. Both ends of the piston rod 11 are fixed. Suction through the cylinder blocks 14a and 15a, respectively, in the seal direction,
Also, the extrusion cylinder 29 and the pushing / storing chamber cylinder 30 are extended and installed inside, and piston heads 21 and 27 having mortar passages 24 and 28 respectively drilled are connected to the ends of these cylinders. Piston head 2
1 has a check valve 22 by a spring 24.
Is installed.

As shown in FIG. 5, the hydraulic cylinder 10
Has an inner diameter of D ₀ , a diameter of a general portion of the piston ring 12 is d ₂ , and an outer diameter of the pump rod 11 of the hydraulic cylinder 10 is d ₁ .

The piston ring 12 has a protrusion 1
3, 13 are formed on the front and rear, and the cylinder block 14
As shown in FIG. 2, cushion chambers 14b and 15b, into which the projecting portions 13 and 13 of the piston ring 12 are inserted, are provided inside the a and 15a, respectively.

Further, the cylinder blocks 14a, 15b
2 and 3, the cushion rooms 14b and 15b are provided with two hydraulic passages 17, 18, 19, and 20 inside thereof, respectively. As shown in FIGS. , 19 and 20 are connected to one-way control valves 60 and 61, which are provided in the hydraulic circuits a and c, respectively.

As described above, the suction / compression cylinder 29 and the hydraulic cylinder 10, or the pushing / storing chamber storage cylinder 30 and the discharge port member 31 are formed in a straight line. The ratio of the inner diameter to the inner diameter of the pressure / storage chamber cylinder 30 is 2: 1.

Reference numeral 62 is a hydraulic tank, and 63a and 63a.
b is a main hydraulic pump and an auxiliary hydraulic pump,
Reference characters a and 64b are check valves.

In the above structure, the operation is performed as follows.

In the state shown in FIGS. 1 and 3, the hydraulic fluid having the main pressure Pr 'passes through the hydraulic circuit g, the one-way control valve 60, and the hydraulic circuit a by the main hydraulic pump 63a to the hydraulic passage of the cylinder block 14a. When flows into 20 the hydraulic piston rings _{^{12 (D 0 2 -d 1 2}} /4)
Extrude to the right while pressing with a force of × 3.14 × Pr '.

Further, the main hydraulic pressure Pr 'pushes the spool of the one-way control valve 61 to the right through the hydraulic circuit a, the check valve 64a and the hydraulic circuit b.

Accordingly, the hydraulic fluid Pr ″ supplied from the auxiliary hydraulic pump 63b flows into the suction valve hydraulic cylinder 7 through the hydraulic circuit i, the one-way control valve 61 and the hydraulic circuit e, whereby the suction valve 5 is opened. In this state, the mortar S is sucked into the suction / compression cylinder 29 through the inlet 4.

As described above, in the process in which the piston ring 12 approaches the cylinder block 15a, the oil stored on the right side of the piston ring 12 inside the hydraulic cylinder 10 is in the hydraulic passage 18 of the cylinder block 15a.
Then, the oil is drained to the hydraulic tank 62 via the hydraulic circuit c, the one-way control valve 60, and the hydraulic circuit h.

When such operation is continued and the projecting portions 13, 13 of the pump ring 12 inside the hydraulic cylinder 10 pass through the hydraulic passage 18 of the cylinder block 15a, as shown in FIG. Is the oil pressure Pc of the oil filled in the cushion room 15b = the force applied to the right side of the piston ring 12 ÷
Cross-sectional area of cushion room 15b = (D ₀ ² −d ₁ ² /
4) × 3.14 × Pr '÷ (d 2 2 -d 1 2/4) ×
3.14 = (D ₀ ² −d ₁ ² / d ₂ ² −d ₁ ² ) Pr ′
It suddenly rises with kg / cm ² (ignoring resistance during oil drain).

Therefore, the pressure Pc increased as described above pushes the spool of the directional control valve 61 to the left side through the hydraulic circuit until the force that urges the spool to the right side is Pr 'kg / cm. ² and
Since Pc> Pr ', the flow direction of hydraulic pressure is as shown in FIG.
It will be switched.

Therefore, the flow of the hydraulic pressure PR ″ supplied from the auxiliary hydraulic pump 63b is switched so that the hydraulic circuit i
And the one-way control valve 61, the hydraulic circuit f, and
The suction valve 5 is moved up through the hydraulic circuit j via the hydraulic cylinder 7 to shut off the inflow port 4 and push the spool of the directional control valve 60 to the right side in the figure to switch the flow of the lubrication passage as shown in FIG.

With the hydraulic circuit switched as described above, oil is supplied to the right side of the piston ring 12 through the hydraulic circuit c, the hydraulic circuit 18, and the one-way switching valve 60 to push the entire piston rod 11 to the right side. Become.

However, since the piston head 21 compresses the mortar S filled in the suction / compression cylinder 29 while the suction valve 5 is closed as described above, the mortar S is pressurized with a large pressure. Therefore, the mortar passage 1 inside the piston rod 11 is resisted against the check valve 22 through the hole 24 of the piston head 21.
It flows into the inside of the cylinder 30 for a pushing and storing chamber through 1a.

At this time, the ratio of the inner diameter of the suction / compression cylinder 29 to the inner diameter of the cylinder 30 for the pushing / storage chamber is 2: 1.
Since half of the mortar S that is transferred is stored inside the cylinder 30 for the delivery / storage chamber, only the remaining half is pushed out of the check valve 33 of the discharge port member 31 and pushed out from the discharge port 32. become.

In the process, the oil in the hydraulic cylinder 10 of the piston ring 12 is transferred to the hydraulic passage 20,
Oil is drained to the hydraulic tank 62 through the hydraulic circuit a, the one-way adjusting valve 60, and the hydraulic circuit h.

Then, as the piston head 21 moves to the left and the projecting portion 13 of the piston ring 12 passes through the hydraulic passage 20 of the cylinder block 14a, the hydraulic pressure inside the cushion room 14b increases and the above-described operation is performed. The same high hydraulic pressure pushes the spool of the one-way control valve 61 to the right through the hydraulic passage 19, and the flow path of the one-way control valve 61 is switched, while the auxiliary hydraulic pressure Pr is set.
'' Lowers and opens the suction valve 5 by the hydraulic cylinder 7 and at the same time pushes the spool of the one-way control valve 60 to the right to instantaneously switch the direction of hydraulic pressure as shown in FIG. ′ Gradually flows into the inside of the hydraulic cylinder 10 on the left side of the piston ring 12 through the hydraulic circuit g, the one-way control valve 60, and the hydraulic circuit a to further push the piston heads 21 and 27 to the right side.

Next, new mortar S is again introduced into the suction / compression cylinder 29, and the piston head 27 pushes the mortar S inside the pushing / storing chamber cylinder 30 to the discharge port 32.

Therefore, as described above, the piston rod 1
While the reciprocating motion of the mortar 1 and the operation of changing the hydraulic circuit are continuously repeated automatically, the mortar S discharges the mortar S.
Extruded from 1.

[0035]

As described above, the mortar pump according to the invention of this application has a structure in which the pump cylinder is separated by the suction / extrusion cylinder and the extrusion / storage chamber cylinder. Since the cylinder is configured in a straight line, the piston rod in the hydraulic cylinder moves forward and backward, so that the mortar S is sucked into the suction / compression cylinder, and is moved through the piston rod 11 by the pushing / storage chamber cylinder. Since it is discharged in a straight line, the suction and discharge of the mortar are performed in a straight line shape, and the problem that the pressure loss due to the circulation is increased does not occur as long as the mortar material has a high viscous force as in the past. The excellent effect that is to be achieved is achieved.

By setting the ratio of the inner diameter of the suction / compression cylinder to the inner diameter of the extrusion / storage chamber cylinder to 2: 1, a certain amount of mortar is constantly extruded even when the piston moves forward and backward. The effect is played.

Further, by applying the reciprocating motion of the piston to the reciprocating motion by applying the pressure difference applied to the pressing space formed between the cylinder heads of the oil cylinders, it is possible to automatically operate without a limit switch auxiliary holding mechanism outside the cylinder. It has the effect of configuring a reciprocating circuit.

[Brief description of drawings]

FIG. 1 is an overall configuration diagram of a mortar pump according to one embodiment of the invention of this application.

FIG. 2 is a sectional view showing a state where the piston rod of the mortar pump is retracted.

FIG. 3 is a sectional view showing a state where a piston rod of the mortar pump is advanced.

FIG. 4 is a sectional view of a cylinder and a piston rod portion in the mortar pump of the same.

5 is an enlarged view of the illustrated portion of FIG. 2. FIG.

FIG. 6 is a diagram showing the configuration of a conventional mortar pump.

[Explanation of symbols]

 10 Hydraulic Cylinder 11 Piston Rod 11a Mortar Passage 12 Piston Rod 13 Projection 14a, 15a Cylinder Block 14b, 15b Cushion 17,17,19,20 Hydraulic Passage 21,27 Piston Head 29 Suction / Compression Cylinder 30 Compression / Storage Chamber Cylinder 32 Discharge port 31 Discharge port member 33 Check valve

Claims (4)

[Claims] 1. A suction valve is provided below a mortar inlet formed below a tip of a hopper provided with a motor and a transfer screw, wherein a suction / compression cylinder and a hydraulic cylinder are provided. Then, a compression / storage chamber cylinder provided with a discharge port member provided with a check valve inside the discharge port is connected and installed in a straight line shape,
The piston rod inside the hydraulic cylinder has a pintle fixed at the center and a mortar passage formed inside, and a piston head and a hole in which a check valve is provided inside the hole at both ends. Piston heads are provided, and these are installed so as to extend inside the cylinders for suction / extrusion and the cylinders for compression / storage chambers, respectively. The series-type double-cylinder mortar pump characterized by the above. 2. The series type double cylinder according to claim 1, wherein the ratio of the inner diameter of the suction / compression cylinder to the inner diameter of the cylinder for the pressure feed / storage chamber is 2: 1. Type mortar pump. 3. A piston ring of said piston rod is provided with protrusions at both ends thereof, and the protrusions can be inserted into and removed from a cushion room of cylinder blocks at both ends of a hydraulic cylinder. Claim 1st
In-line type double cylinder type mortar pump as described in the item. 4. The length of the protrusions at both ends of the piston ring is set such that the ends can be located between the hydraulic circuits from the outside in a state where the protrusions are inserted in the cushion room. Claim 1 characterized in that
In-line type double cylinder type mortar pump as described in the item.