JPH08144938A - High-pressure pump - Google Patents

Abstract

PURPOSE: To deliver a fluid at high pressure by providing a piston with a shock application mechanism for the application of a shock thereto during downward stroke according to the preset period, and arranging a working chamber between a fluid intake passage and a fluid delivery passage. CONSTITUTION: A rotary member 8 and a hammering body 15 are formed into a shock application mechanism. Also, a piston 18 is coupled to and held on a cylinder 16, so as to be capable of reciprocating motion. A working chamber 21 is formed in the cylinder 16 for water intake and delivery according to the reciprocating motion of a piston 18a, and kept communicated to an intake passage 22 and a delivery passage 25. Thus, water intake takes place periodically at every rotation of the member 8. Furthermore, the piston 18 is subjected to high pressure associated with a large impact from the body 15 at every rotation, and high pressure water is delivered from the passage 25 via a nozzle hole 24 on the end of a nozzle 23. According to this construction, a high-pressure pump 1 can be made compact. Also, the pump 1 allows an easy transport, washing or serration work, and ensures cost reduction or the like.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-pressure pump for discharging a fluid at a high pressure, and more particularly to a high-pressure pump configured to discharge a high-pressure fluid by utilizing a periodically generated impact force.

[0002]

2. Description of the Related Art Conventionally, based on mechanical energy from an electric motor, an engine or the like, water or other fluid is sucked to give a required pressure and the high-pressure fluid is discharged to an object to be discharged. As such pumps, reciprocating pumps, gear pumps, vortex pumps, axial flow pumps, etc. are known.

Then, these pumps are allowed to have a high-pressure discharge performance, a nozzle is connected to the discharge port of the pump through a hose, and a high-pressure fluid, for example, high-pressure water is discharged from the tip of the nozzle, so that the inside of the sewer pipe can be discharged. It has come to be used for cleaning equipment, construction machinery, etc., peeling off concrete and road surface paint, peeling floor pillars, and removing rough skin from persimmon trees.

[0004]

By the way, each of the pumps exemplified above cannot obtain sufficient high-pressure discharge performance when driven by a low horsepower using a relatively small electric motor or engine. Is the reality. Therefore, when a small engine or the like is used in order to meet the demand for a lightweight and compact pump, the discharge pressure of the fluid discharged from the discharge port of the pump through the nozzle tip to the discharge surface is This leads to a shortage.

Due to this, the inside of the sewer pipe cannot be cleaned and the cleat peeling work can be performed reliably and efficiently, and in order to avoid such problems, the pump must be enlarged. However, it becomes impossible to meet the demand for compactness and the like, which is extremely disadvantageous in terms of usability, workability, and cost when performing each of the above-mentioned operations.

Considering the cause of such a problem, for example, taking a reciprocating pump among the above-mentioned pumps as an example, its general structure includes a piston that reciprocates by the operation of a crank mechanism. The fluid is sucked into the working chamber when the piston moves backward, and the fluid is discharged from the working chamber by applying pressure to the fluid when the piston moves forward.

However, with such a reciprocating pump structure, the fluid is simply sucked and discharged in accordance with the reciprocating movement of the piston. In other words,
The pressing force of the piston acting on the fluid is obtained only by the linked operation by the direct connection between the crank mechanism and the piston, and due to this, sufficient high-pressure discharge performance cannot be obtained.

A high-pressure washing machine is known as a concrete example of pump devices in which high-pressure water is discharged from the tip of a nozzle through a discharge port of a pump and a hose leading to the discharge port. The high-pressure washer that is used has a power source of 180
It is the extent that a discharge pressure of kg / cm ² can be obtained.

The present invention was devised under the circumstances described above, and a high pressure is applied to a fluid by utilizing a large impact force which cannot be obtained by the conventional pump structure. It is an object of the present invention to obtain an extremely high fluid discharge pressure even with a small and low horsepower drive source.

[0010]

Means for Solving the Problems To solve the above problems, the present invention takes the following technical means.

That is, the invention according to claim 1 of the present application is a high-pressure pump configured to perform suction and discharge of fluid in accordance with the reciprocating motion of the piston, and retains the piston so that the piston can reciprocate. A cylinder, an impact force applying mechanism that applies an impact force to the forward side to the piston in a predetermined cycle, and is provided between the fluid suction side passage and the fluid discharge side passage at the tip of the cylinder. The working chamber is provided, and the fluid is drawn into the working chamber by applying a pressure to the fluid sucked into the working chamber by an impact force acting on the piston on the forward movement side.

In this case, the impact force applying mechanism includes, as an example, a rotating member that is rotationally driven by a power source,
And a striking body having a constant mass movably supported at an eccentric position of the rotating member, and the movement trajectory of the striking body interferes with the base end portion of the piston. 2).

As another example, the impact force applying mechanism includes a striking body that is held so as to be movable in the reciprocating direction and reciprocates by the operation of the driving means, and the tip end portion of the striking body is the above-mentioned. It is configured to abut the base end portion of the piston (claim 3).

In order to ensure the suction and discharge of the fluid to and from the working chamber, a check valve or an orifice having the working chamber side in the forward direction is provided at the communicating portion between the working chamber and the suction side passage. It is preferable to provide (claim 4).

In the high-pressure pump according to claim 2, it is possible to provide a plurality of the cylinders, the pistons, and the working chambers with respect to the single rotating member and the impacting body ( Claim 5).

[0016]

According to the main structure (Claim 1) of the present invention, the working chamber is disposed at the tip of the cylinder that holds the piston so that the piston can reciprocate, and the piston faces the tip side. When moving forward, a periodic impact force is applied to the piston by the operation of the impact force applying mechanism.
Along with this, a high pressure is intermittently applied to the fluid in the working chamber, and as a result, extremely high-pressure fluid is discharged from the discharge side passage communicating with the working chamber.
When the piston is returned, the fluid is sucked into the working chamber through the suction side passage.

As described above, the impact force acts on the fluid in the working chamber through the piston in accordance with the operation of the impact force applying mechanism, whereby the fluid is pressurized and ejected. The pressure is effectively increased as compared with the conventional one. That is, as in the conventional case, the pressure does not act on the fluid in accordance with the reciprocating motion of the piston simply due to the direct connection with the crank mechanism, but the fluid is struck through the piston that is struck with the operation of the impact force applying mechanism. As a result of the impact force being applied to the fluid, pressure is applied to the fluid,
This enables high-pressure discharge of fluid that could not be obtained with conventional reciprocating pumps.

In addition, since the discharge pressure of the fluid is effectively increased as described above, the drive source may be relatively small and have low horsepower, which makes it possible to downsize the entire pump and easily carry it. It is also possible to obtain the advantage of cost reduction and further cost reduction.

When a so-called rotary hammer mechanism (claim 2) is adopted as an example of the impact force imparting mechanism, the striking body held movably by the rotary member is driven by the power source. However, the centrifugal force pushes the rotating member radially outward of the rotating member. In this case, since the base end portion of the piston is arranged so as to interfere with the movement trajectory of the hitting body, the piston is axially moved by the impact of the hitting body acting on the base end portion and the centrifugal force. Receive the impact force of. Then, due to this impact force, a high-pressure fluid is discharged from the working chamber. In this case, since the hitting body is movably held by the rotating member, the impact reaction force when the hitting body collides with the piston is appropriately absorbed, and the vibration transmitted to the pump body. Is also obtained.

When the rotary hammer mechanism is adopted, a single rotating member and a striking body may be provided with a plurality of cylinders, pistons, and working chambers (claim 5). A single striker will collide with the base end of the piston in sequence. As a result, the fluid is frequently discharged from each working chamber in a short cycle, and the high-pressure fluid is discharged more efficiently.

When a so-called breaker type mechanism (claim 3) is adopted as another example of the impact force imparting mechanism, the striking body reciprocates while moving within a predetermined range by the operation of a crank mechanism or the like. Exercise. When the forward end of the striker comes into contact with the base end of the piston during the forward movement, an axial impact force acts on the piston, and this impact force causes the high-pressure fluid to be discharged from the working chamber. Become.

On the other hand, in order to smoothly suck and discharge the fluid to and from the working chamber, it is preferable to dispose a valve mechanism at each of the communicating portions of the suction side passage and the discharge side passage to the working chamber. As the valve mechanism, it is possible to use, for example, an electromagnetic valve whose opening / closing is controlled according to the timing of the suction stroke and the discharge stroke, but preferably, the communication portion between the suction side passage and the working chamber is used. A check valve or an orifice having the working chamber side in the forward direction is provided (claim 4). According to this, the suction and discharge strokes can be reliably performed with a simple structure, the valve mechanism can be prevented from becoming complicated, and at the same time the cost can be reduced.

[0023]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The preferred embodiments of the present invention will be described below.
A specific description will be given with reference to the drawings. In each of the following embodiments, the case where the high-pressure pump according to the present invention is used as a high-pressure washing machine will be described as an example.

1 to 3 show a high pressure pump according to a first embodiment of the present invention.

First, referring to FIG. 1, an overall schematic structure of a high pressure pump 1 according to a first embodiment of the present invention will be described. An engine 3 as a drive source and an accessory 4 are elastically supported above a substantially barrel-shaped housing 2 via vibration-proof rubbers 5 arranged at the four corners thereof. Further, on one side and above one side of the housing 2, there are gripping bodies 6 and 7 which are respectively gripped by the right hand and the left hand of an operator.
It is attached via a and 7a. A throttle operating lever 3x for controlling the rotation of the engine 3 is attached to the upper grip body 6.

On the other hand, as shown in detail in FIGS. 2 and 3, in the cylindrical inner space X in the housing 2, a rotating member 8 which is rotationally driven by the engine 3 is held. The rotating member 8 is formed by integrating a pair of oval flange portions 8c and 8d, which are arranged with a predetermined distance therebetween, by a connecting portion 8e having a function of a balance weight.

Then, the pair of oval flange portions 8
Rotation supporting shafts 8a and 8b are provided on the outer side surfaces of c and 8d so as to project on the same axis, and both rotation supporting shafts 8a and 8b are provided.
Are rotatably supported on the side wall of the housing 2 via bearings 9 and 10. In this first embodiment, the means for transmitting the rotational driving force to the rotating member 8 is
A drive wheel 11 such as a pulley or a sprocket fixed to the output shaft of the engine 3, a driven wheel 12 fixed to the one rotation support shaft 8a, and a belt or a chain wound around the both wheels 11 and 12. And the like endless transmission belt 13.

Further, the pair of oval flange portions 8
c and 8d are respectively provided with elliptical holding holes 14 and 14 on the opposite side of the connecting portion 8e with the rotation axis of the rotating member 8 interposed therebetween. Both ends of the hitting body 15 having a shape are supported. This hitting body 1
5 is rotatable in a state where both ends are restrained in the holding holes 14 and 14, and at the same time, is movable in a direction perpendicular to the axis within a range allowed by a gap between the holding holes 14 and 14 and the inner surfaces thereof. There is. And in this 1st Example, mainly,
The rotating member 8 and the hitting body 15 constitute an impact force applying mechanism.

A holder 17 having a cylinder 16 is fixed below the housing 2, and a lower portion of a piston 18 is fitted and held in the cylinder 16 so as to be vertically reciprocable. . In this embodiment, the piston 18 is composed of a lower first piston 18a and an upper second piston 18b which are separately formed. The first piston 18a is fitted and held in the cylinder 16, and the first piston 18a is biased upward by a main spring 19 as an elastic biasing body.

On the other hand, the second piston 18b
Is fitted and held in an inner hole of a cylindrical sleeve 20 fitted and fixed to the lower wall portion of the housing 2 so as to be vertically reciprocable. Also, the second piston 18b is
The base end surface 18c, which is the upper end surface, is a flat surface and is provided with a buffer hole 18d having a predetermined depth that opens to the base end surface 18c. The movement locus L of the hitting body 15 (see FIG. 3) is configured to interfere with the base end portion of the piston 18, specifically, the base end surface 18c of the second piston 18b. In this case, the first piston 18a and the second piston 18b forming the piston 18 are formed.
And are arranged on the same axis. The first piston 18a and the second piston 18b may be integrated to form a single piston 18.

In the first embodiment, the first piston 18a and the second piston 18b can be independently reciprocated, and the first piston 1
Large-diameter flanges 18e and 18f are integrally formed at the upper end of 8a and the lower end of the second piston 18b, respectively. The main spring 19 is provided between the large-diameter flange 18e of the first piston 18a and the receiving portion 17a of the holder 17, and the large-diameter flange 18f of the second piston 18b is the main spring. By contacting the lower end of the cylindrical sleeve 20 by the urging force of 19, the movement of the second piston 18b inward of the housing 2 is restricted.

Further, as shown in detail in FIGS. 4 and 5, at the lower end portion (tip portion) of the cylinder 16 in the holder 17, water is sucked and discharged as the first piston 18a reciprocates. A working chamber 21 for performing the operation is formed. The working chamber 21 can communicate with a suction-side passage 22 that communicates with a water supply source (not shown) (for example, a water faucet or a water storage tank) and a discharge-side passage 25 that communicates with a nozzle 24 at the tip of the nozzle 23. Has been done.

More specifically, the suction side passage 22 is formed as an inner hole of a suction pipe 22x connected to one side of the holder 17, and the discharge side passage 25 is formed as follows.
Discharge pipe 25x connected to the lower end of the holder 17
Is formed as an inner hole (see FIGS. 1 and 2).

Further, a suction side valve chamber 26 is formed in a communication portion between the working chamber 21 and the suction side passage 22, and the working chamber 21 side is the forward direction of the suction side valve chamber 26. A first check valve 27 is provided. That is, this first
The check valve 27 allows the inflow of water to the working chamber 21 side, while blocking the outflow of water from the working chamber 21 to the suction side passage 22. Specifically, this first check valve 27
Is a spherical first valve body 27a which is seated on and away from the first valve seat 28 according to the water pressure in the working chamber 21, and a first spring which biases the first valve body 27a in the seating direction. 27b and.

On the other hand, a discharge side valve chamber 29 is formed in the communicating portion between the working chamber 21 and the discharge side passage 25, and the working chamber 21 side is the opposite direction to this discharge side valve chamber 29. A second check valve 30 is provided. That is, this second
The check valve 30 allows the outflow of water from the working chamber 21 to the discharge side passage 25, while blocking the inflow of water into the working chamber 21. Specifically, the second check valve 30 is provided with a second valve seat 31 depending on the water pressure in the working chamber 21.
Second valve body 30 having a tip spherical portion that is seated on and taken off from
a and a second spring 30b that biases the second valve body 30a in the seating direction. In this case, the second valve seat 3 is attached to the tubular wall portion 32 where the second valve seat 31 is formed.
A plurality of through holes 33 are formed at the position immediately downstream of 1, and a plurality of concave grooves 34 are formed in the pedestal portion 30c of the second valve body 30a.

Next, the first aspect of the present invention having the above configuration
The operation of the high pressure pump 1 according to the embodiment will be described.

For example, when the surface A to be ejected is present in the vertical plane, as in the case of cleaning the wall surface of a building or the construction machine, or the work of peeling a tree, as shown in FIG. An operator holds the gripping bodies 6 and 7 with both hands and supports the high-pressure pump 1 so that the injection port 24 of 23 is oriented in the horizontal direction. When the surface to be ejected is present in a horizontal plane, such as when peeling off road surface coating, or in an inclined surface having a predetermined angle, the nozzle hole 24 of the nozzle 23 is vertically downward or upward or inclined. The worker supports the high-pressure pump 1 so as to be oriented.

Under such a condition, the operator operates the throttle operating lever 3x to increase the rotational speed of the engine 3, whereby the centrifugal clutch (not shown) is actuated to rotate the engine 3. It is transmitted to the rotary member 8 in the housing 2 through the endless transmission belt 13 and the following operation is performed.

That is, as shown in FIGS. 4 and 5,
When the rotating member 8 is rotating in the direction of the arrow a, the impacting body 15 moves the base end surface 1 of the piston 18 (second piston 18b).
Immediately before the piston 18 is pushed down by interfering with 8c, water is sucked into the working chamber 21, and the first check valve 27 and the second check valve 30 are closed. .

From this state, the rotary member 8 rotates in the direction of arrow a, so that the hammer 15 pushes down the piston 18, and the first piston 18a accordingly.
The front end surface of the device applies pressure to the water in the working chamber 21. And
As shown in FIGS. 6 and 7, when the outer peripheral surface of the hitting body 15 comes into contact at the center line position of the base end surface 18c of the second piston 18b, the first piston 18a moves downward (forward). Moving end) and the volume of the working chamber 21 is minimized.

At this stage, the water in the working chamber 21 has a high pressure, and at the same time, as shown in FIG. 8, the action of the high-pressure water causes the second valve element 30a of the second check valve 30 to move to the second valve. The first valve body 2 of the first check valve 27 which is separated from the seat 31
7a is pressed against the first valve seat 28 and seated. As a result, the high-pressure water in the working chamber 21 passes through the through hole 33 below the second valve seat 31 into the discharge side valve chamber 29 as shown by the dotted arrow v in FIG. As shown by a dotted arrow w in the figure, the concave groove 34 of the pedestal portion 30c of the second valve body 30a is formed.
Is discharged to the discharge side passage 25. Then, the high-pressure water is discharged from the discharge side passage 25 to the nozzle 2 at the tip of the nozzle 23.
It is ejected toward the surface A to be ejected via 4.

Thereafter, as the rotating member 8 further rotates in the direction of arrow a, as shown in FIG. 9, the hitting body 15 separates from the base end surface 18c of the second piston 18b, and the first, The second pistons 18a and 18b move upward (return) by the urging force of the main spring 19. As a result, the first valve body 27a of the first check valve 27 is replaced by the first valve seat 28.
10 and the water in the intake passage 22 flows into the first valve chamber 26 as shown by a dotted arrow x in FIG. 10, and passes through the path shown by an arrow y in FIG. Inhaled into.

In this case, when tap water or the like is supplied to the suction side passage 22 at a predetermined pressure, the supply pressure causes the first check valve 27 to open. It is also possible to move the first and second pistons 18a and 18b upward by the supply pressure. Therefore, when the water supply pressure from the suction side passage 22 is high, the main spring 1
It is possible to omit 9 but it is necessary to increase the spring constant or spring force of the second spring 30b so that the second check valve 30 does not open due to the supply pressure. On the other hand, when the main spring 19 is present, the volume expansion ratio of the working chamber 21 due to the upward movement of the first and second pistons 18a and 18b and the water from the suction side passage 22 are increased. The second check valve 30 can be eliminated if the relationship with the supply pressure is that the positive and negative pressures do not act on the working chamber 21.

On the other hand, when the suction passage 22 is merely connected to the water storage tank, the urging force of the main spring 19 causes the first and second pistons 18a,
The upward movement of 18b brings the inside of the working chamber 21 into a negative pressure state. Based on this negative pressure, the first check valve 27 is opened, and at the same time, the second check valve 3 is opened.
0 is closed. Therefore, in this case, the main spring 19 and the second check valve 30 are essential constituent elements.

Incidentally, the elimination of the main spring 19 or the elimination of the second check valve 30 can be similarly applied to each of the following embodiments.

The suction and discharge of water as described above are periodically performed every one rotation of the rotary member 8 in the direction of arrow a. The striking body 15 movably held by the rotating member 8 is pressed outward in the radial direction of the rotating member 8 within the range of free movement by its centrifugal force, and the piston 18 is rotated by each rotation. Hitting body 1
5 receives a great impact. Therefore, high pressure due to the impact force acts on the water in the working chamber 21, and extremely high-pressure water is discharged from the discharge side passage 25 through the injection port 24 at the tip of the nozzle 23.

In addition, the discharge pressure of water is
Since it can be effectively enhanced by the impact force of 8, the engine 3 can be small and have a low horsepower, and the high pressure pump 1 can be downsized, and the carrying, cleaning or peeling work can be facilitated. Costs can be reduced. According to the results of experiments conducted by the applicant, the high-pressure pump 1 according to the first embodiment is 300 to 1000 kg / cm with a drive source of 1.3 horsepower, for example.
^It has been found that a discharge pressure of ² can be obtained.

Further, since the hitting body 15 is movably held by the rotating member 8, the impact reaction force when the hitting body 15 collides with the piston 18 is appropriately absorbed, and the housing 2 and the gripping body 6 are absorbed. , 7 and the like will be reduced.

FIGS. 12 and 13 show a second embodiment of the high-pressure pump 1 according to the present invention. The second embodiment differs from the first embodiment in that the first check valve described above is used. 27
Is eliminated and the orifice 40 is formed in the communication portion between the suction side passage 22 and the working chamber 21. Since the configuration of each of the other parts is the same as that of the first embodiment, the description of the overall configuration thereof will be omitted, and in the following description based on FIG. 12 and FIG. 13, it will be common to the first embodiment. Constituent requirements are assigned the same reference numerals and explanations thereof are omitted.

According to this second embodiment, when the piston 18 (first piston 18a) shown in FIG. 12 moves up, the water that has passed through the orifice 40 from the suction side passage 22 and is sucked into the working chamber 21 is The piston 18 shown in FIG. 13 is discharged to the discharge side passage 25 while receiving a high pressure when the piston 18 moves downward. Then, at the time of this discharge, a small amount of water leaks to the suction side passage 25 through the orifice 40, but most of the water in the working chamber 21 is discharged through the paths shown by the dotted arrows v1 and w1. Since the water is discharged into the side passage 25, the above leakage does not pose a problem, and the high pressure water can be discharged in substantially the same manner as in the case of the first embodiment.

By forming the orifice 40 instead of the check valve as in the second embodiment, the working chamber 2
The valve body and valve seat of the check valve, which are caused by the extremely high pressure inside 1, are not worn or damaged, and the number of parts is reduced and the structure is simplified. can get.

FIGS. 14 and 15 show a third embodiment of the high pressure pump 1 according to the present invention. The high-pressure pump 1 according to the third embodiment has a holder 17x, a cylinder, and a holder 17x in the upper portion of the housing 2 so as to be vertically symmetrical with the lower portion of the housing 2, which is a characteristic component of the first embodiment. 16x, tubular sleeve 20x, piston 18x
(First piston 18ax, second piston 18bx), main spring 19x, and working chamber 21x are arranged. Incidentally, also in the description of the third embodiment, the constituents common to those of the first embodiment are designated by the same reference numerals and the description thereof will be omitted.

In the high-pressure pump 1 according to the third embodiment, a suction side passage 22 leading to a water supply source is branched, and both suction side branch passages 22x, 22x are a lower working chamber 21 and an upper working chamber. It communicates with 21x. Then, both the intake side branch passages 22x, 22x and the both working chambers 21, 21
First check valves 27, 27x having forward direction on the side of both working chambers 21, 21x are arranged at respective communicating portions with x. Further, the upper working chamber 21x and the lower working chamber 21 are connected by an auxiliary discharge side passage 50 for guiding the high pressure water generated in the upper working chamber 21x to the lower working chamber 21. The communication portion between the auxiliary discharge side passage 50 and the lower working chamber 21 has a third portion in which the working chamber 21 side is the forward direction.
The check valve 51 is provided.

According to the third embodiment, when the state shown in FIG. 14 is reached, that is, as the rotary member 8 rotates in the direction of the arrow a, the striker 15 has the lower piston 18 (second piston 18b). When colliding with the base end surface 18c of the water, the water sucked into the lower working chamber 21 receives high pressure and is discharged to the discharge side passage 25. At this point in time, the first check valve 27 and the third check valve 27 and the third check valve 27, which are respectively disposed in the communicating portions of the working chamber 21 to the intake side branch passages 22x, 22x, respectively.
All check valves 51 are closed, and the second check valve 30 disposed in the communication portion of the working chamber 21 to the discharge side passage 25 is opened. is there.

When the rotary member 8 is rotated about 180 degrees in the direction of arrow a from such a state, as shown in FIG. 15, the hitting body 15 is the base end surface of the upper piston 18x (second piston 18bx). By colliding with 18cx,
Pressure is applied to the water sucked into the upper working chamber 21x, and the water is first discharged to the auxiliary discharge side passage 50. Then, this high-pressure water passes through the auxiliary discharge side passage 50, opens the third check valve 51, flows into the lower working chamber 21, and then opens the second check valve 30. Is discharged to the discharge passage 25. At this time point, the first check valve 27 is in the closed state.

The hitting body 15 is the base end surface 18c, 18c of each of the upper and lower pistons 18, 18x.
Even when it is separated from x, the first check valves 27, 2
7x is opened, and water is sucked into the working chambers 21 and 21x from the suction side branch passages 22x and 22x, respectively.

As a result of the above operation, high-pressure water is discharged from the lower working chamber 21 to the discharge-side passage 25 twice for each rotation of the rotary member 8, whereby high-pressure water per rotation is discharged. The number of times of discharging is doubled, and the discharging efficiency is improved. Along with this, it is possible to further increase the discharge pressure of the high-pressure water, and it is possible to perform various cleaning operations and concrete peeling operations more strongly and quickly.

FIG. 16 shows a fourth embodiment of the high pressure pump 1 according to the present invention. In addition to the configuration of the second embodiment, the high-pressure pump 1 according to the fourth embodiment has holders 17y and 17z, which are symmetrical with respect to the right side portion and the left side portion of the housing 2. Cylinders 16y, 16z,
Cylindrical sleeves 20y, 20z, pistons 18y, 18z
(First piston 18ay, 18az, second piston 18
by, 18bz), main springs 19y and 19z, and working chambers 21y and 21z, respectively. In addition, also in the description of the fourth embodiment,
The same components as those of the embodiment are designated by the same reference numerals and the description thereof will be omitted.

The high pressure pump 1 according to the fourth embodiment has four pumps for distributing and supplying water from the suction side passage 22 leading to the water supply source B to the four working chambers 21, 21x, 21y and 21z. Intake side branch passages 60, 60x, 60
y and 60z are provided. Further, three discharge chambers 21x, 21y, 21z of the above-mentioned respective working chambers are connected with three discharge side branch passages 61x, 61y, 61z for guiding the discharged high pressure water to the lower working chamber 21. Has been done.
Furthermore, the above three working chambers 21x, 21y, 21z,
Corresponding intake side branch passages 60x, 60y, 60
The first check valves 27x and 27x are provided at the communicating portions with z, respectively.
y and 27z are provided.

According to the fourth embodiment, the striker 15 collides with the base end faces 18c, 18cy, 18cx, 18cz of the pistons each time the rotary member 8 rotates 90 degrees in the direction of the arrow a, and the collision is caused. Each time it is done, high pressure water is in the lower working chamber 2
1 is discharged to the discharge side passage 25. As a result, the number of times the high-pressure water is ejected per revolution of the rotating member 8 is quadrupled, the ejection efficiency is further improved, and various cleaning operations and peeling operations can be made even stronger and faster. It will be possible.

The structures of the check valves on the suction side and the discharge side used in the high-pressure pump 1 in the above-described first to fourth embodiments are not limited to those shown in the illustrated examples. Check valves of other structures may be used as long as they can perform the same action.

Further, since the piston used in the high-pressure pump 1 in the above-mentioned first to fourth embodiments is constructed such that the first piston and the second piston can be moved independently, the hitting body At the time of collision with 15, etc., the first and second pistons move following each other while repeating slight separation and contact. However, even if both pistons are integrally formed, substantially the same impact force and high-pressure water resulting therefrom can be discharged.

Further, the high pressure pump 1 exemplified above is the single cylinder type described in the first and second embodiments, the two cylinder type described in the third embodiment, and the four cylinder types described in the fourth embodiment. Although it relates to the cylinder type of the book, besides this,
The present invention can be similarly applied to three cylinder types or four or more cylinder types.

In addition, the high-pressure pump 1 in the first to fourth embodiments employs a so-called rotary hammer type impact force applying mechanism having a rotary impacting body 15, but other types are used. Impact force applying mechanism,
For example, a breaker type impact force applying mechanism may be adopted as shown in the following fifth embodiment.

That is, as shown in FIG. 17, the high pressure pump 1 according to the fifth embodiment has a striking body 71 which is fitted and held in the inner hole 70a of the cylindrical housing 70 so as to be capable of reciprocating.
And a cylindrical slider 72 reciprocally held in the inner hole 71a of the hitting body 71, and a crank mechanism 73 for driving the slider 72. Then, the crank mechanism 73 reciprocates the slider 72, whereby the upper end surface (base end surface) 18c of the piston 18 fitted and held in the cylinder 16 below the housing 70 is held.
On the other hand, the lower end surface of the hitting body 71 is periodically abutted to exert an impact force. Incidentally, also in the description of the fifth embodiment, the same constitutional requirements as those of the first embodiment,
Specifically, the suction side passage 22, the first check valve 27, the working chamber 2
The same reference numerals are given to the first and second check valves 30, the discharge side passage 25, etc., and the description thereof will be omitted.

According to the fifth embodiment, the rotational movement of the disk 73a constituting the crank mechanism 73 is converted into the reciprocating movement of the slider 72 via the connecting rod 73b, and thus the slider 72 reciprocates. By moving, the striking body 71 also reciprocates following this. In this case, the lower end surface of the slider 72 and the inner hole 71 of the striker 71 are
Air is appropriately filled in the gap S formed between the bottom surface of a and a. Therefore, when the hitting body 71 moves upward as the slider 72 moves upward, and when the slider 72 moves downward after reaching the upper end of the slider 72, the air in the gap S is caused due to the downward movement delay of the hitting body 71. Is compressed, and an extremely large impact force acts on the piston 18 from the hitting body 71 with this air compression force.

The impact force applies pressure to the water in the working chamber 21, and the high-pressure water is discharged into the discharge passage 25.
Is discharged. As described above, the high-pressure pump 1 using the breaker type impact force imparting mechanism according to the fifth embodiment also discharges high-pressure water by using the impact force acting on the piston 18, which is small and compact. Even when the low horsepower engine 3 is used as a drive source, an extremely high discharge pressure can be obtained.

There are various types of breaker type impact force imparting mechanisms other than those shown in the drawings, but the high pressure pump according to the present invention is of a known breaker type other than those shown in the drawings. It goes without saying that the same can be applied to the case where the impact force applying mechanism is adopted.

Further, the high pressure pumps according to the above-mentioned first to fifth embodiments are constructed so that the high pressure water is directly discharged from the working chamber through the discharge side passage 25 through the injection port 24 at the tip of the nozzle 23. However, an accumulator is separately provided at a suitable place in the communication section from the working chamber to the discharge side passage 25, or in the middle of the discharge passage 25, and the water accumulated in the accumulator is discharged from the injection port 24. May be.

Further, all of the high-pressure pumps according to the above-mentioned embodiments exemplify the case of discharging water at high pressure, but it is also possible to discharge liquids or gas other than water at high pressure. . In addition, the usage of the high-pressure pump is not limited to the above-exemplified ones, and may be used for other purposes as long as the work is performed using a high-pressure fluid. Needless to say. Further, although the high-pressure pump according to each of the above-described embodiments uses the engine 3 as a drive source, other drive sources such as an electric motor may be used instead.

[Brief description of drawings]

FIG. 1 is a front view showing the outer appearance of a high-pressure pump according to a first embodiment of the present invention.

FIG. 2 is an enlarged vertical side view taken along the line II-II in FIG.

FIG. 3 is an enlarged vertical sectional front view taken along line III-III in FIG.

FIG. 4 is an enlarged vertical cross-sectional front view of essential parts showing a peripheral structure of a striking body, a piston, and a working chamber, which are components of the high-pressure pump according to the first embodiment.

FIG. 5 is an enlarged vertical cross-sectional front view of essential parts showing a peripheral structure of a working chamber and a check valve, which are components of the high-pressure pump according to the first embodiment.

FIG. 6 is an enlarged vertical sectional front view corresponding to FIG. 3 and showing the operation of the high-pressure pump according to the first embodiment.

FIG. 7 is an enlarged vertical sectional front view of an essential part corresponding to FIG. 4, showing the operation of the high-pressure pump according to the first embodiment.

FIG. 8 is an enlarged vertical sectional front view of an essential part corresponding to FIG. 5, showing the operation of the high-pressure pump according to the first embodiment.

FIG. 9 is an enlarged vertical sectional front view of an essential part corresponding to FIGS. 4 and 7, showing the operation of the high-pressure pump according to the first embodiment.

FIG. 10 is an enlarged vertical sectional front view of an essential part corresponding to FIGS. 5 and 8, showing the operation of the high-pressure pump according to the first embodiment.

FIG. 11 is a schematic front view showing an example of a usage state of the high-pressure pump according to the first embodiment.

FIG. 12 is a vertical sectional front view showing a main part of a high-pressure pump according to a second embodiment of the present invention and corresponding to FIGS. 5, 8 and 10 described above.

FIG. 13 is a vertical sectional front view of an essential part corresponding to FIGS. 5, 8 and 10, showing an operation of a main part of the high-pressure pump according to the second embodiment.

FIG. 14 is a vertical sectional front view showing the configuration and operation of a high-pressure pump according to the third embodiment of the present invention.

FIG. 15 is a vertical sectional front view showing the configuration and operation of the high-pressure pump according to the third embodiment.

FIG. 16 is a schematic vertical sectional front view showing the configuration and operation of the high-pressure pump according to the fourth embodiment of the present invention.

FIG. 17 is a schematic vertical sectional front view showing the configuration and operation of the high-pressure pump according to the fifth embodiment of the present invention.

[Explanation of symbols]

 1 High-pressure pump 2 Housing 8 Impact force imparting mechanism (rotating member) 15 Impact force imparting mechanism (impact body) 16 Cylinder 18 Piston 18c Piston base end (base end face of second piston) 18cx Piston base end (second) Piston base end surface 18cy Piston base end portion (second piston base end surface) 18cz Piston base end portion (second piston base end surface) 21 Working chamber 21x Working chamber 21y Working chamber 21z Working chamber 22 Suction side passage 25 Discharge side passage 27 Check valve (first check valve) 27x Check valve (first check valve) 40 Orifice 71 Impact force imparting mechanism (striking body) 72 Impact force imparting mechanism (slider) 73 Impact force imparting Mechanism (crank mechanism)

Claims (5)

[Claims] 1. A high-pressure pump configured to suck and discharge a fluid in accordance with the reciprocating motion of a piston, wherein the cylinder holds the piston so that the piston can reciprocate, and the piston moves forward and backward. The piston includes the impact force applying mechanism that applies an impact force in a predetermined cycle, and a working chamber that is provided at a tip end portion of the cylinder between a fluid suction side passage and a fluid discharge side passage. A high-pressure pump, characterized in that it is configured to apply a pressure to the fluid sucked into the working chamber by an impact force acting on the forward side to discharge the fluid. 2. The impact force applying mechanism includes a rotating member that is rotationally driven by a power source, and a striking body having a constant mass movably held at an eccentric position of the rotating member, and The high-pressure piston according to claim 1, wherein the movement trajectory of the impacting body is configured to interfere with the base end portion of the piston. 3. The impact force applying mechanism includes a striking body which is held so as to be movable in the reciprocating direction and reciprocates by the operation of a driving means, and a tip end portion of the striking body is a base end portion of the piston. The high-pressure pump according to claim 1, which is configured to come into contact with the high pressure pump. 4. A check valve or an orifice having a forward direction on the side of the working chamber is provided at a communication portion between the working chamber and the passage on the suction side. High pressure pump as described. 5. The high-pressure pump according to claim 2, wherein a plurality of cylinders, pistons, and working chambers are provided for a single rotary member and hitting body.