U.S. patent application number 12/530622 was filed with the patent office on 2010-07-01 for high-pressure generation device.
Invention is credited to Mituharu Magami, Naoyuki Magami, Takuya Magami.
Application Number | 20100166573 12/530622 |
Document ID | / |
Family ID | 39787855 |
Filed Date | 2010-07-01 |
United States Patent
Application |
20100166573 |
Kind Code |
A1 |
Magami; Mituharu ; et
al. |
July 1, 2010 |
HIGH-PRESSURE GENERATION DEVICE
Abstract
The high-pressure generation device (110) comprises three
pressure chambers which pressurize liquid drawn from the outside
through the pumping operation of a plurality of pistons (1) having
different outer diameters, pressurizes the liquid drawn from the
outside, and discharges the liquid pressurized to a constant
pressure to the outside in each reciprocating operation of the
plurality of pistons (1). The three pressure chambers comprising a
first pressure chamber (31) which draws liquid from the outside, a
second pressure chamber (32) of which the pressurizing area for
pressurizing the liquid is smaller than that of the first pressure
chamber (31), and a third pressure chamber (33) of which the
pressurizing area is smaller than that of the second pressure
chamber (32) and which discharges liquid to the outside. The
pressurizing areas of the second pressure chamber (32) and the
third pressure chamber (33) are set so that the ratio of the
difference between the pressurizing areas of the second pressure
chamber (32) and the third pressure chamber (33) to the thrust when
the plurality of pistons move in the one direction is equal to the
ratio of the pressurizing area of the third pressure chamber (33)
to the thrust when the plurality of pistons move in the other
direction.
Inventors: |
Magami; Mituharu;
(Chiba-shi, JP) ; Magami; Naoyuki; (Chiba-shi,
JP) ; Magami; Takuya; (Chiba-shi, JP) |
Correspondence
Address: |
KNOBBE MARTENS OLSON & BEAR LLP
2040 MAIN STREET, FOURTEENTH FLOOR
IRVINE
CA
92614
US
|
Family ID: |
39787855 |
Appl. No.: |
12/530622 |
Filed: |
March 11, 2008 |
PCT Filed: |
March 11, 2008 |
PCT NO: |
PCT/JP2008/054418 |
371 Date: |
January 14, 2010 |
Current U.S.
Class: |
417/267 ;
417/254 |
Current CPC
Class: |
F04B 9/113 20130101;
F04B 3/00 20130101; F04B 5/02 20130101 |
Class at
Publication: |
417/267 ;
417/254 |
International
Class: |
F04B 5/02 20060101
F04B005/02; F04B 3/00 20060101 F04B003/00 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 12, 2007 |
JP |
2007-102198 |
Claims
1. A high-pressure generation device comprising: a plurality of
reciprocating pistons which are coaxially connected to a
reciprocating drive shaft of a drive unit and have different outer
diameters and three pressure chambers which pressurize liquid drawn
from the outside through the pumping operation of the plurality of
pistons, pressurizes liquid drawn from the outside, and discharges
liquid pressurized to a constant pressure to the outside in each
reciprocating operation of the plurality of pistons, wherein the
three pressure chambers comprising a first pressure chamber for
drawing liquid from the outside, a second pressure chamber of which
the pressurizing area for pressurizing liquid is smaller than that
of the first pressure chamber, and a third pressure chamber of
which the pressurizing area is smaller than that of the second
pressure chamber and which discharges liquid to the outside, and
the pressurizing areas of the second pressure chamber and the third
pressure chamber are set so that the ratio of the difference
between the pressurizing areas of the second pressure chamber and
the third pressure chamber to the thrust when the plurality of
pistons move in the one direction is equal to the ratio of the
pressurizing area of the third pressure chamber to the thrust when
the plurality of pistons move in the other direction, or the
direction opposite to the one direction.
2. The high-pressure generation device as claimed in claim 1,
wherein the drive shaft is reciprocated by a drive unit having a
rotating shaft, and the pressurizing area of the second pressure
chamber is set to be twice as large as the pressurizing area of the
third pressure chamber.
3. The high-pressure generation device as claimed in claim 1 or 2,
comprising an auxiliary chamber which communicates with the first
pressure chamber or the second pressure chamber, wherein the volume
of the auxiliary chamber is adjustable.
4. The high-pressure generation device as claimed in claim 1 or 2,
comprising: an intake port for drawing liquid from the outside; a
first flow passage allowing the liquid drawn from the intake port
to flow into the first pressure chamber; a second flow passage
allowing the liquid pressurized by the first pressure chamber to
flow into the second pressure chamber; a third flow passage
allowing the liquid pressurized to a predetermined pressure to flow
into the third pressure chamber; and an outlet port for discharging
the liquid pressurized to a constant pressure from the third
pressure chamber to the outside, wherein each of the first flow
passage, the second flow passage, and the third flow passage is
provided with a backflow prevention device allowing liquid to flow
only in a predetermined direction.
5. The high-pressure generation device as claimed in claim 4,
wherein when the plurality of pistons move in the one direction,
both the first pressure chamber and the third pressure chamber
increase in volume, opening the backflow prevention devices of both
the first flow passage and the third flow passage, and the second
pressure chamber decreases in volume, closing the backflow
prevention device of the second flow passage, thereby allowing the
liquid pressurized to a constant pressure to be discharged from the
outlet port.
6. The high-pressure generation device as claimed in claim 4,
wherein when the plurality of pistons move in the other direction,
both the first pressure chamber and the third pressure chamber
decrease in volume, closing the backflow prevention devices of both
the first flow passage and the third flow passage, and the second
pressure chamber increases in volume, opening the backflow
prevention device of the second flow passage, thereby allowing the
liquid pressurized to a constant pressure to be discharged from the
outlet port.
7. The high-pressure generation device as claimed in claim 4,
wherein any of the first flow passage, the second flow passage, and
the third flow passage is formed outside the plurality of
pistons.
8. The high-pressure generation device as claimed in claim 4,
wherein the third pressure chamber is formed at the tip of a piston
of which the outer diameter is smallest out of the plurality of
pistons, the third flow passage is formed within the plurality of
pistons, and both the first flow passage and the second flow
passage are formed outside the plurality of pistons.
Description
FIELD OF THE INVENTION
[0001] The present invention relates to a high-pressure generation
device which draws in fluid and discharges it at high pressure.
BACKGROUND OF THE INVENTION
[0002] A piston pump (also referred to as a "plunger pump") has
been used to discharge pressurized liquid at high pressure. The
piston pump reciprocates a liquid drawing/compressing piston using
an external power source, compresses the liquid drawn in from the
outside, and discharges the pressurized liquid at high pressure.
Various types of drive units for reciprocating the
drawing/compressing piston are available, such as one which
converts the rotary motion of a motor or engine as the power source
into a reciprocal motion and one which reciprocates a control
piston by feeding pressurized fluid as the power source into a
fluid pressure cylinder (See Japanese Patent No. 3297143).
[0003] In order to discharge liquid at high pressure, a piston pump
is required to discharge fluid which has been subject to
draw/compression strokes in order to be pressurized to a
predetermined pressure. Piston pumps which bring about less
pulsatory motion in liquid to be discharged employ, in most cases,
a method that uses a plurality of pistons and a method that uses an
accumulator, both of which lead to complicated structures, issues
with upsizing, and high costs in most cases.
[0004] A pressure conversion device which uses a single compressor
is, however, disclosed which is provided with two pressure chambers
for performing compression/discharge processes outside of a piston
which reciprocates by using a fluid pressure cylinder, draws
hydraulic oil from the outside into the first chamber when the
piston moves in one direction, pressurizes the hydraulic oil up to
a predetermined pressure when the piston moves in the other
direction, sends the pressurized hydraulic oil from the first
chamber having a larger compressed volume into the second chamber
having a smaller expanded volume, and at the same time, also
discharges the hydraulic oil to the outside (See Japanese Examined
Patent Application Publication No. 62-21994).
[0005] In this pressure conversion device, however, when the
hydraulic oil is pressurized by the first pressure chamber, mixed
air is also required to be compressed and the need to reduce
compression time to the greatest extent possible remains
unsatisfied. In addition, a flow passage for the hydraulic fluid
for reciprocating the control piston of a drive unit is switched by
two directional control valves in a two-stage manner, resulting in
a problem in that it takes time to actually perform switching.
[0006] A compressor has been proposed which performs threefold
compression in order to obtain high pressure gas efficiently using
a single compressor (See Japanese Unexamined Patent Application
Publication No 3-9088).
[0007] This technique obtains high pressure gas by compressing the
gas in a three-stage manner, but there are difficulties in applying
it directly to liquid because of its structure. In addition, since
it discharges only gas once for each reciprocating operation of a
piston, even if it is applied to liquid, the pressure fluctuation
of the liquid being discharged is large, and the demand to
eliminate pulsation cannot be satisfied.
[0008] The inventors of the present application have proposed a
high-pressure generation device including three pressurizing
chambers within a piston, in which, when the piston actuated by a
drive unit moves in one direction, liquid is drawn from the outside
into first chamber through an inlet port, high-pressure fluid is
fed from the reducing second chamber into the expanding third
chamber, and residual high-pressure fluid is discharged to the
outside, and when the piston moves in the other direction, the
fluid is pressurized by the reducing first chamber and the
expanding second chamber, and the high-pressure fluid is discharged
to the outside from the reducing third chamber (See Japanese
Unexamined Patent Application Publication No. 2003-3966). They have
obtained a US patent for the above-detailed invention (See U.S.
Pat. No. 7,165,951 B2).
[0009] In this high-pressure generation device, however, as shown
in FIG. 9, the three chambers are inside the H-shaped piston,
making its structure complicated and the number of components
large. In addition, since high-precision concentricity and
perpendicularity are required for the components, component
processing is extremely difficult, and it is difficult to avoid
processing errors caused by chucking. Furthermore, since the flow
passage communicating the first chamber and the second chamber is
provided within the piston, and a backflow prevention valve is
required to be provided at this position, it is difficult to
downsize the piston, thereby providing an obstacle to the
downsizing of the high-pressure generation device.
SUMMARY OF THE INVENTION
Problems to be Solved by the Invention
[0010] The present invention has been achieved in view of the
above-described problems. It is an object of the present invention
to provide a high-pressure generation device which is relatively
simple in structure, is easy to process components for, can
discharge high-pressure liquid continuously from the beginning of
operation, can discharge high-pressure liquid with small pressure
fluctuations continuously, and can be downsized.
Means for Solving the Problems
[0011] The high-pressure generation device of the present invention
is a high pressure generation device which includes a plurality of
reciprocating pistons which are coaxially connected to a
reciprocating drive shaft of a drive unit and have different outer
diameters and three pressure chambers which pressurize liquid drawn
from the outside through the pumping operation of the plurality of
pistons, pressurizes liquid drawn from the outside, and discharges
liquid pressurized to a predetermined pressure to the outside in
each reciprocating operation of the plurality of pistons, wherein
the three pressure chambers comprising a first pressure chamber for
drawing liquid from the outside, a second pressure chamber wherein
the pressurizing area for pressurizing liquid is smaller than that
of the first pressure chamber, and a third pressure chamber wherein
the pressurizing area is smaller than that of the second pressure
chamber and which discharges liquid to the outside, and the
pressurizing areas of the second pressure chamber and the third
pressure chamber are set so that the ratio of the difference
between the pressurizing areas of the second pressure chamber and
the third pressure chamber to the thrust when the plurality of
pistons move in one direction is equal to the ratio of the
pressurizing area of the third pressure chamber to the thrust when
the plurality of pistons move in the other direction, or the
direction opposite to the one direction.
[0012] The three pressure chambers are thus formed through the
pumping operation of a plurality of reciprocating pistons which are
coaxially connected to the drive shaft, and all three pressure
chambers are outside the pistons, providing a simple structure with
fewer components in comparison to the inventions disclosed in
Japanese Unexamined Patent Application Publication No. 2003-3966
and U.S. Pat. No. 7,165,951 B2. By having fewer parts into which
the pistons are fitted to slide, the high-pressure generation
device can be installed in a processing machine in a one-chuck
state and can be processed relatively easily. Since the
pressurizing areas of the second pressure chamber and the third
pressure chamber are set so that the ratio of the difference
between the pressurizing areas of the second pressure chamber and
the third pressure chamber to the thrust when the plurality of
pistons move in one direction is equal to the ratio of the
pressurizing area of the third pressure chamber to the thrust when
the plurality of pistons move in the other direction, or the
direction opposite to the one direction, liquid drawn from the
outside is pressurized to a predetermined pressure by any of the
reciprocating operations of the pistons while it is sent from the
first pressure chamber to the second pressure chamber, and from the
second pressure chamber to the third pressure chamber. When the
third pressure chamber expands, the liquid pressurized to a
predetermined pressure by the second pressure chamber fills the
third pressure chamber, and at the same time, the residual liquid
with the predetermined pressure is directly discharged from the
third pressure chamber to the outside. When the third pressure
chamber reduces, the liquid in the third pressure chamber is
pressurized in order to be discharged to the outside. Liquid with a
predetermined pressure can thereby be discharged to the outside at
all times.
[0013] In particular, the above-described high-pressure generation
device, wherein the drive shaft is reciprocated by a drive unit
having a rotating shaft, and the pressurizing area of the second
pressure chamber is set to be twice as large as the pressurizing
area of the third pressure chamber, can also discharge liquid with
a predetermined pressure to the outside at all times.
[0014] In addition, when the above-described high-pressure
generation device includes an auxiliary chamber which communicates
with the first pressure chamber or the second pressure chamber,
wherein the volume of the auxiliary chamber is capable of being
adjusted, the liquid pressurizing area can be finely adjusted, even
when gas is mixed into the liquid to be pressurized by a plurality
of pistons.
[0015] The above-described high-pressure generation device
preferably includes: an intake port for drawing liquid from the
outside; a first flow passage allowing the liquid drawn from the
intake port to flow into the first pressure chamber; a second flow
passage allowing the liquid pressurized by the first pressure
chamber to flow into the second pressure chamber; a third flow
passage allowing the liquid pressurized to a predetermined pressure
by the second pressure chamber to flow into the third pressure
chamber; and an outlet port for discharging the liquid pressurized
to a constant pressure from the third pressure chamber to the
outside, wherein each of the first flow passage, the second flow
passage, and the third flow passage is provided with a backflow
prevention device thereby allowing liquid to flow only in a
predetermined direction.
[0016] By providing such backflow prevention devices, liquid can be
successively sent from the first pressure chamber to the second
pressure chamber, from the second pressure chamber to the third
pressure chamber, and from the third pressure chamber to the outlet
port, allowing the liquid pressurized to a constant pressure to be
discharged from the outlet port.
[0017] Any of the first flow passage, the second flow passage, and
the third flow passage is preferably formed outside the plurality
of pistons. In another preferred embodiment, the third pressure
chamber is formed at the tip of a piston of which the outer
diameter is the smallest out of the plurality of pistons, the third
flow passage may be formed either within or outside of the
plurality of pistons, and both the first flow passage and second
flow passage are formed outside of the plurality of pistons.
[0018] Providing the flow passages outside the pistons in this way
allows the pistons to be downsized and allows the high-pressure
generation device to be easily downsized.
[0019] Furthermore, in another preferred embodiment, the drive unit
is provided with a switching device which reciprocates the drive
shaft by reversing the direction of the liquid which flows into/out
of each of both side chambers of the reciprocating control piston,
wherein the switching device is provided with a rod which moves by
using the control piston approaching each side end of both side
chambers and reverses the direction of the liquid by the movement
of the rod.
[0020] Providing the switching device means that high-speed
switching can be performed stably, thereby allowing liquid to be
discharged from the outlet port with a specific pressure at all
times.
[0021] In yet another preferred embodiment, the plurality of
pistons are connected to both sides of the drive shaft, while the
first pressure chamber and the second pressure chamber are formed
at the tip of the pistons.
[0022] Arranging the first pressure chamber and the second pressure
chamber in this way simplifies the manufacturing of the
high-pressure generation device.
Effect of the Invention
[0023] According to the high-pressure generation device of the
present invention, since all three pressure chambers are outside
the pistons, a simple structure with few components is provided,
and it can be mounted on a processing machine with one chuck and
processed relatively easily. In addition, since the flow passage
connecting the two pressure chambers is provided within the housing
located outside the pistons, it is possible to downsize the device.
Successive pressurization by the three pressure chambers can
discharge liquid with a predetermined pressure from the beginning
of operation. Furthermore, the thrust and speed of the
reciprocating motion by the drive unit are made constant, thereby
allowing liquid with a constant pressure to be discharged
continuously at all times and this also allows liquid with a
constant quantity to be discharged continuously at all times.
BRIEF DESCRIPTION OF THE DRAWINGS
[0024] FIG. 1 is a cross-sectional view showing one example of the
high pressure generation device in accordance with one embodiment
of the present invention.
[0025] FIG. 2 is a cross-sectional view showing one example of the
high pressure generation device in accordance with one embodiment
of the present invention.
[0026] FIG. 3 is a schematic cross-sectional view for illustrating
the operation of the high pressure generation device in accordance
with one embodiment of the present invention.
[0027] FIG. 4 is a schematic cross-sectional view for illustrating
the operation of the high pressure generation device in accordance
with one embodiment of the present invention.
[0028] FIG. 5 is a schematic cross-sectional view for illustrating
the operation of the high pressure generation device in accordance
with one embodiment of the present invention.
[0029] FIG. 6 is a schematic cross-sectional view for illustrating
the operation of the high pressure generation device in accordance
with one embodiment of the present invention.
[0030] FIG. 7 is a schematic cross-sectional view for illustrating
the operation of the high pressure generation device in accordance
with one embodiment of the present invention.
[0031] FIG. 8 is a schematic cross-sectional view for illustrating
the operation of the high pressure generation device in accordance
with one embodiment of the present invention.
[0032] FIG. 9 is a cross-sectional view showing an embodiment of a
high pressure generation device in accordance with a
previously-filed patent application.
[0033] FIG. 10 is a cross-sectional view partially enlarging the
high pressure generation device in accordance with one embodiment
of the present invention.
[0034] FIG. 11 is a diagram showing an example of an actuator in
which an eccentric heart-shaped cam is integral with a rotating
drive shaft.
[0035] FIG. 12 is a diagram showing an example of a crank mechanism
as an actuator in which an eccentric shaft 55 is rotated by a
rotating drive shaft.
[0036] FIG. 13 is an example of a configuration using a double-rod
fluid pressure cylinder as an actuator.
[0037] FIG. 14 is an example using an automatic switching device
for switching a directional control valve of a fluid pressure
cylinder at high speed as an actuator.
[0038] FIG. 15 is an example of the high-pressure generation device
of the present invention in which a piston and a plunger are
arranged to the left and right with an actuator sandwiched
therebetween.
[0039] FIG. 16 is another example of the high-pressure generation
device of the present invention in which a piston and a plunger are
arranged to the left and right with an actuator sandwiched
therebetween.
[0040] FIG. 17 is an example of one configuration of the
high-pressure generation device of the present invention which
reciprocates a piston and a plunger with a drive unit in which an
eccentric cam or bearing is integral with a rotating drive shaft
arranged midway therebetween.
[0041] FIG. 18 is another example of the high-pressure generation
device of the present invention in which a piston and a plunger are
arranged to the left and right with an actuator sandwiched
therebetween.
[0042] FIG. 19 is another example of the high-pressure generation
device of the present invention in which a piston and a plunger are
arranged to the left and right with an actuator sandwiched
therebetween.
[0043] FIG. 20 is an example of a configuration in which the drive
unit shown in FIG. 17 is arranged midway therebetween unlike that
of the actuator shown in the configuration examples of the
high-pressure generation device of the present invention shown in
FIG. 18 and FIG. 19.
[0044] FIG. 21 is an example of the high-pressure generation device
of the present invention in which the second pressure chamber and
the third pressure chamber are provided in both side chambers of
the piston part 8.
[0045] FIG. 22 is a graph showing a waveform (theoretical values)
of the discharge pressure Pd of the high-pressure generation device
in accordance with a preferred embodiment of the present
invention.
[0046] FIG. 23 is a graph showing a waveform (theoretical values)
of the discharge pressure P of the pressure conversion device
including two pressurizing chambers disclosed in Japanese Examined
Patent Application Publication No. 62-21994 as a comparative
example.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0047] Hereinafter, the high-pressure generation device of the
embodiments provided in accordance with the present invention will
be described with reference to the drawings.
[0048] FIG. 1 and FIG. 2 are cross-sectional views showing examples
of the high pressure generation device in accordance with one
embodiment of the present invention.
[0049] As shown in FIG. 1 and FIG. 2, the high pressure generation
device 110 in accordance with one embodiment of the present
invention is provided with three pressure chambers, that is, a
first pressure chamber 31, a second pressure chamber 32, and a
third pressure chamber 33 for performing a pumping operation to
pressurize and discharge liquid in a space in which a piston 1
fitted into a housing 2 reciprocates, an intake port 257 for
drawing the liquid from the outside into the first pressure chamber
31, a first flow passage 254 for communicating the intake port 257
and the first pressure chamber 31, a second flow passage 311 for
communicating the first pressure chamber 31 and the second pressure
chamber 32, a third flow passage 271 for connecting the second
pressure chamber 32 and the third pressure chamber 33, and an
outlet port 267 for discharging the liquid pressurized to a
predetermined pressure from the third pressure chamber 33 to the
outside. The first flow passage 254 is provided with a check valve
81 (which is equivalent to the backflow prevention device in
accordance with the present invention) for allowing the liquid to
flow from the intake port 257 into the first pressure chamber 31
and to prevent it from flowing backwards. The second flow passage
311 is provided with a check valve 82 for allowing the pressurized
liquid to flow from the first pressure chamber 31 into the second
pressure chamber 32 and prevent it from flowing backwards. The
third flow passage 271 is provided with a check valve 83 for
allowing the pressurized liquid to flow from the second pressure
chamber 32 into the third pressure chamber 33 and prevent it from
flowing backwards. Each of the check valves 81, 82, and 83 in
accordance with the present embodiment comprising a ball 812 and a
spring 813. When a predetermined pressure difference between both
sides of the flow passage occurs, the spring 813 is pressed by the
ball 812 and contracts, thereby opening the valve, and when a
pressure difference between both sides of the flow passage occurs,
the valve closes to prevent the liquid from flowing backwards.
However, it should be appreciated that the check valves are not
necessarily limited to this particular structure.
[0050] The first flow passage 254 and the second flow passage 311
in accordance with the present embodiment are provided within the
housing 2, while the third flow passage 271 is provided within the
piston 1, but the third flow passage 271 is not necessarily
provided within the piston 1 and may be provided within the housing
2 in the same manner as the first flow passage 254 and the second
flow passage 311. The first flow passage 254 and the second flow
passage 311 are thus provided outside the piston 1, thereby
allowing the piston 1 to be downsized. In addition, the piston 1
can be downsized further by providing the third flow passage 271
outside the piston 1, thereby allowing the high-pressure generation
device 110 to be downsized.
[0051] The high-pressure generation device 110 in accordance with
the present invention is provided with a large-diameter piston part
8, a piston rod 7 of which the outer diameter is smaller than that
of the piston 8, and a piston part 9 of which the outer diameter is
smaller than that of the piston rod 7, which are coaxially
connected to both sides of the large-diameter piston part 8. Within
the housing, a large-diameter cylinder 8a into which the
large-diameter piston part 8 is fitted is provided. A
small-diameter cylinder 9b into which the small-diameter piston
part 9 is fitted is provided at the center of one end face of the
large-diameter cylinder 8a, while a through hole 7a into which the
piston rod 7 is fitted is provided at the center of the other end
face of the large-diameter cylinder 8a.
[0052] Outside of the piston 1, the large-diameter piston part 8 is
fitted into the large-diameter cylinder 8a, while the
small-diameter piston part 9 is fitted into the small-diameter
cylinder 9b. In the space in which the large-diameter piston part 8
and the small-diameter piston part 9 reciprocate, the first
pressure chamber 31 having the largest liquid pressurizing area,
the second pressure chamber 32 of which the liquid pressurizing
area is smaller than that of the first pressure chamber, and the
third pressure chamber 33 of which the liquid pressurizing area is
smaller than that of the second pressure chamber are formed.
[0053] As shown in FIG. 1, when the piston 1 moves in the one
direction (the left direction shown by the arrow in the figure),
the first pressure chamber 31 increases in volume, the pressure
within the first pressure chamber 31 then becomes lower than the
pressure of the outside liquid F, opening the check valve 81. The
liquid F is then drawn from the intake port 257 into the first
pressure chamber 31. The second pressure chamber 32, meanwhile,
decreases in volume, and the pressure within the second pressure
chamber 32 then becomes higher, closing the check valve 82 and
opening the check valve 83. The high-pressure liquid pressurized by
the second pressure chamber 32 is then fed into the third pressure
chamber 33, and out of the fed high-pressure liquid, the remaining
liquid, after filling the third pressure chamber 33, is discharged
from the outlet port 267.
[0054] As shown in FIG. 2, when the piston 1 moves in the other
direction (the right direction shown by the arrow in the figure),
the first pressure chamber 31 decreases in volume, and the pressure
within the first pressure chamber 31 then becomes higher, closing
the check valve 81. The second pressure chamber 32, meanwhile,
increases in volume, and the pressure within the second pressure
chamber 32 then becomes lower, opening the check valve 82. The
third pressure chamber 33 decreases in volume and the pressure
within the third pressure chamber 33 then becomes higher, closing
the check valve 83. The high-pressure liquid pressurized by the
third pressure chamber 33 is then discharged from the outlet port
267.
[0055] Thus, the liquid drawn from the intake port 257 is
pressurized by the first pressure chamber 31, the second pressure
chamber 32, and the third pressure chamber 33 through the movement
of the piston 1 in one direction and then the other direction,
allowing the liquid to be discharged at all times at a constant
pressure.
[0056] The high-pressure generation device 110 in accordance with
the present embodiment is provided with an auxiliary chamber 52
which communicates with the second pressure chamber 32.
[0057] FIG. 10 is a cross-sectional view partially enlarging the
high pressure generation device in accordance with the present
embodiment. As shown in FIG. 10, a cylindrical hole 53 is formed at
the position of the housing 2 which communicates with the second
pressure chamber. An adjust screw 54 provided with an outer screw
is screwed into the cylindrical hole 53. The space in the
cylindrical hole 53 on the tip side of the adjust screw 54 is the
auxiliary chamber 52. A jam nut 93 is threadably engaged with the
part of the adjust screw 54 which protrudes from the housing 2.
Packing 51 is installed in a packing installation groove on the
periphery of the adjust screw 54, preventing the liquid from
leaking out of the auxiliary chamber. The cylindrical hole 53 can
be moved forward or backward by rotating the adjust screw 54,
allowing the volume of the auxiliary chamber 52 to increase or
decrease.
[0058] Pressure to be generated in the first pressure chamber 31
and the second pressure chamber 32 is determined by the ratio of
the total volume obtained by adding the volumes of the first
pressure chamber 31, the second pressure chamber 32, the auxiliary
chamber 52, part of the first flow passage 254, part of the second
flow passage 311, and part of the third flow passage 271 to the
volume difference between the reduced volume and the expanded
volume in the first pressure chamber 31 and the second pressure
chamber 32. By increasing the volume of the auxiliary chamber 52 by
rotating the adjust screw 54, the pressure to be generated
decreases, while, by decreasing the volume thereof, the pressure to
be generated increases. For liquid, since pressure also depends on
the amount of air incorporated therein and any temperature
difference, by increasing/decreasing the volume of the auxiliary
chamber 52, pressure to be generated can be set at a predetermined
value.
[0059] The operation of the high-pressure generation device 110 in
accordance with the present embodiment will now be described in
more detail.
[0060] FIGS. 3 to 8 are schematic cross-sectional views for
illustrating the operation of the high pressure generation device
in accordance with one embodiment of the present invention.
[0061] FIG. 3 shows a state in which the piston 1 of the
high-pressure generation device in accordance with one embodiment
of the present invention has started moving in the other direction
(the right direction shown by the arrow in the figure), FIG. 4
shows the moment the piston 1 has stopped, and FIG. 5 shows the
state in which the piston 1 has started moving in the one direction
(the left direction shown by the arrow in the figure).
[0062] As shown in FIG. 3, when the piston 1 moves in the right
direction shown by the arrow, the first pressure chamber 31 is
pressurized, and the check valve 81 closes, but the second pressure
chamber 32 expands, and its pressure becomes lower than that of the
first pressure chamber 31, thereby opening the check valve 82.
Letting the reduced volume (the compressed volume) of the
pressurized first pressure chamber 31 be .DELTA.V.sub.1, and
letting the expanded volume of the second pressure chamber 32 be
.DELTA.V.sub.2, when the piston moves in the right direction, the
total volume (.DELTA.V.sub.1+.DELTA.V.sub.2) changes and is
pressurized. In accordance with a change in the total volume
(.DELTA.V.sub.1+.DELTA.V.sub.2), the pressure in the first pressure
chamber 31 and the second pressure chamber 32 is increased.
[0063] The third pressure chamber 33, meanwhile, is reduced through
the movement of the piston 1 in the right direction, and
high-pressure liquid pressurized to a predetermined pressure Pd is
discharged from the outlet port 267.
[0064] Since a reduction in the volume of the first pressure
chamber 31 .DELTA.V.sub.1 is set to be larger than an expansion in
the volume of the second pressure chamber 32 .DELTA.V.sub.2, when
the piston moves in the other direction (the right direction shown
by the arrow in the figure), the pressure in the second pressure
chamber 32 approaches the predetermined pressure Pd, and
immediately before the piston 1 reverses to the backward direction,
the pressure in the second pressure chamber 32 becomes equal to Pd,
or is pressurized to substantially the same value through the fine
movement of the small-diameter piston part 9.
[0065] The difference between an outer diameter D3 of the
small-diameter piston part 9 forming the first pressure chamber 31
and an outer diameter D2 of the piston rod 7 forming the second
pressure chamber 32 is determined in accordance with the discharge
pressure Pd of the high-pressure liquid discharged from the third
pressure chamber 33, and in order to increase the discharge
pressure Pd, D2 is required to be increased.
[0066] Now, when the liquid to be pressurized (compressed) is water
at 20.degree. C., the compressibility ratio .beta. is
0.428.times.10.sup.-9 m.sup.2/N in the pressure range from
1.01325.times.10.sup.5 Pa to 500.times.1.01325.times.10.sup.5 Pa.
Since liquid has, in general, a low compressibility ratio .beta.,
by compressing it only slightly, its pressure increases. In fact,
since air mixes thereinto in many cases, care should be taken in
that the compressibility ratio decreases in accordance with the air
mixing ratio.
[0067] In the position shown in FIG. 3 through to nearly that shown
in FIG. 4, a constant pressure acts on a first control chamber 36
by a working fluid L, and when thrust is added to the piston 1, the
third pressure chamber 33 thereby discharges liquid at the constant
discharge pressure Pd. In this case, when the thrust of an actuator
6 is consumed through a gradual increase in the pressure in both
the first pressure chamber 31 and the second pressure chamber 32 by
the volume difference between a reduction in the volume of the
first pressure chamber 31 and an expansion in the volume of the
second pressure chamber 32, the pressure Pd of the liquid
discharged from the third pressure chamber 33 will decrease, albeit
slightly. However, when the. actuator 6 holds the remaining thrust
power, the pressure Pd of the liquid discharged from the third
pressure chamber 33 will not decrease and as such, balance is
achieved by an increase in the thrust of the actuator 6.
[0068] FIG. 4 shows the moment when a directional control valve 60
(not shown) of the actuator 6 is switched to move the piston 1 in
the backward direction (the left direction) when the piston 1
reaches the end of the working space. The piston 1 stops
instantaneously and the pressure of the liquid in the second
pressure chamber 32 is increased up to a pressure corresponding to
the predetermined discharge pressure Pd.
[0069] FIG. 5 shows a state in which the piston 1 which has
reversed and is moving in one direction (the left direction). The
second pressure chamber 32 is pressurized, closing the check valve
82 and opening the check valve 83. The liquid which has been
pressurized to the pressure Pd by the second pressure chamber 32
and has been discharged fills the third pressure chamber 33, and
the residual liquid is discharged from the outlet port 267. The
first pressure chamber 31 is expanded and its pressure decreases,
allowing the check valve 81 to open and liquid F to flow into the
intake port 257 from the outside. This state continues while the
piston 1 is moving in the one direction (the left direction).
[0070] FIG. 6 shows a state in which the piston 1 has started
moving in the one direction (the left direction shown by the arrow
in the figure), FIG. 7 shows the moment the piston 1 has stopped,
and FIG. 8 shows the state in which the piston 1 has started moving
in the other direction (the right direction shown by the arrow in
the figure).
[0071] FIG. 6 shows a state in which the piston 1 has moved in the
left direction slightly, and the check valves 81, 82, and 83
maintain the same states as those shown in FIG. 5.
[0072] FIG. 7 shows the moment when the directional control valve
60 (not shown) of the actuator 6 is switched to move the piston 1
in the backward direction (the right direction), when the piston 1
reaches the end of the working space, and the piston 1 stops
instantaneously. The third pressure chamber 33 is filled with
liquid pressurized to the discharge pressure Pd or some pressure
close thereto.
[0073] FIG. 8 shows the same state as FIG. 3. While the piston 1
moves, the liquid in the third pressure chamber 33 is pressurized,
allowing the high-pressure liquid to be discharged from the outlet
port 267.
[0074] As described above, the piston 1 moves from FIG. 3 to FIG. 8
to form one cycle, during which the liquid pressurized to Pd
continues to be discharged from the outlet port 267.
[0075] In the high-pressure generation device 110 in accordance
with the present embodiment, a single-rod fluid pressure cylinder
is used as the actuator 6, and a control piston rod 46 of the
actuator 6 is connected to the piston rod 7 on one side of the
piston 1, allowing the piston 1 to reciprocate at a constant
speed.
[0076] The actuator 6 for use in the high pressure generation
device 110 in accordance with the present embodiment has a
structure for preventing working fluid L from leaking to the
outside by allowing a head cover 44 and a rod cover 45 to be fitted
into a cylinder tube 47 in order to close the cylinder tube 47 and
provides packing 48 at the fitting part of the rod cover 45 and the
head cover 44. Packing 49 is provided on a control piston 43 which
is fitted into the cylinder tube 47 where it will reciprocate,
while sealing packing 50 is provided at a part which is fitted into
the rod cover 45 on the outer periphery of the piston rod 46, which
is integrally coupled to the control piston 43. The rod cover 45 is
fixed to the housing 2 by screwing a bolt 4 into the housing 2 from
outside the head cover 44. The working space in which the control
piston 43 moves is formed with a first control chamber 35 and a
second control chamber 36. The head cover 44 and the rod cover 45
are provided with a first control port 221 and a second control
port 222 for feeding the working fluid L to the first control
chamber 35 or the second control chamber 36 and discharging the
working fluid L from the first control chamber 35 or the second
control chamber 36, and are provided with a directional control
valve 60 for switching between feeding the working fluid L to
either one of the first control port 221 or the second control port
222 and discharging the working fluid L from either one of them,
flow passages 62 and 61 between the directional control valve 60
and the control ports 221 and 222, a flow passage 63 for sending
the working fluid L from a pressure source P to the directional
control valve 60, and a flow passage 64 for sending the working
fluid L from the directional control valve 60 to a drain tank
D.
[0077] By switching the flow passages 61 and 62 for the working
fluid L fed from the pressure source P using the directional
control valve 60, working surfaces 112 and 122 of the control
piston 43 are switched to move in either direction, allowing the
piston rod 46 to reciprocate.
[0078] In FIG. 1, since the directional control valve 60 is
switched to a flow passage state 601, the working fluid L enters
the first control port 221 from the flow passage 61 and acts on the
working surface 112 of the first control chamber 35, allowing a
drive mode for moving the piston 1 in the one direction (the left
direction shown by the arrow in the figure) to be established. The
flow passage 62, meanwhile, communicates with the drain tank D
through the flow passage 64, collecting the working fluid L in the
second control chamber 36.
[0079] In FIG. 2, since the directional control valve 60 is
switched to a flow passage state 602, the working fluid L enters
the second control port 222 from the flow passage 62 and acts on
the working surface 122 of the second control chamber 36, allowing
a drive mode for moving the piston 1 in the other direction (the
right direction shown by the arrow in the figure) to be
established. The working fluid L in the first control chamber 35,
conversely, is collected into the drain tank D.
[0080] In the single-rod cylinder having one control piston 43,
since the pressure-receiving surface areas of the working surfaces
112 and 122 of the control piston 43 which receive the working
fluid L are different from each other, the outer diameter of the
control piston 43 and the outer diameter of the piston rod 46 are,
as will be described later, defined by the relationship with the
pressure-receiving surface areas when the liquid F acts on the
second pressure chamber and the third pressure chamber formed on
both sides of the large-diameter piston part 8 of the piston 1.
[0081] An example of the high-pressure generation device using the
single-rod fluid pressure cylinder as the actuator 6 will be
described here, but the actuator 6 is not necessarily a single-rod
fluid pressure cylinder, and may instead be a double-rod fluid
pressure cylinder and a motor or an engine having a rotating shaft
as the power source. An embodiment with an actuator having a
rotating shaft will be described later.
[0082] In the high-pressure generation device 110 in accordance
with the present embodiment, pressure corresponding to the areas of
the pressurizing surfaces on which the large-diameter piston part 8
and the small-diameter piston part 9 is generated in the first
pressure chamber 31, the second pressure chamber 32, and the third
pressure chamber 33, in accordance with the thrust of the actuator
6. The force being in balance with the thrust of the actuator 6 is
represented by the product of the area of a pressurizing surface
acting on a pressure chamber and the generated pressure.
[0083] In order for the discharge pressure of the liquid when
moving in the one direction (the left direction) and the discharge
pressure when moving in the other direction (the right direction)
to be equal, the area B of the pressurizing surface acting on the
second pressure chamber 32 and the area C of the pressurizing
surface acting on the third pressure chamber 33 in accordance with
the thrust of the drive unit are selected.
[0084] FIG. 10 is a cross-sectional view partially enlarging the
high-pressure generation device in accordance with the present
embodiment.
[0085] As shown in FIG. 10, the area A of the pressurizing surface
of the first pressure chamber 31, the area B of the pressurizing
surface of the second pressure chamber 32, and the area C of the
pressurizing surface of the third pressure chamber 33 are
expressed, using the inner diameter of the cylinder 8a, that is,
the outer diameter D1 of the large-diameter piston part, the outer
diameter D2 of the piston rod 7, and the outer diameter D3 of the
small-diameter piston part 9, as
A=.pi.(D.sub.1.sub.2-D.sub.3.sub.2)/4
B=.pi.(D.sub.1.sub.2-D.sub.2.sub.2)/4 C=.pi.D.sub.3.sub.2/4
[0086] In FIG. 2, the thrust f.sub.1 when the piston 1 is moved in
the other direction (the right direction) by the actuator 6 is
expressed by the product of the pressure-receiving surface area
A.sub.l of the working surface 122 of the control piston 43 of the
actuator 6 within the control chamber 36 and the pressure P.sub.36
of the working fluid L acting on the pressure-receiving surface
area A.sub.1. At the beginning, the force caused by the pressure
P.sub.3 generated in the liquid F within the third pressure chamber
33 balances with the thrust f.sub.1. The force is the product of
the area C of the pressurizing surface of the third pressure
chamber 33 and the generated pressure P.sub.3, and the generated
pressure P.sub.3 is the discharge pressure P.sub.d.
(f.sub.1=)A.sub.1.times.P.sub.36=C.times.P.sub.3
therefore A.sub.1/C=P.sub.3/P.sub.36 Equation (1)
[0087] In fact, however, when the piston 1 moves in the other
direction (the right direction), the first pressure chamber 31
reduces to open the check valve 82, and the liquid F flows into the
expanded second pressure chamber 32. Since a reduction in the
volume of the first pressure chamber 31 is set to be larger than an
expansion in the volume of the second pressure chamber 32, the
pressure within the first pressure chamber 31 and the second
pressure chamber 32 gradually increases with the movement of the
piston 1. The thrust f.sub.1 of the actuator 6 is thereby consumed,
albeit slightly.
[0088] The discharge pressure P.sub.d of the liquid discharged from
the outlet port 267 should therefore gradually decrease, albeit
slightly, but in fact, by increasing the pressure P.sub.36 of the
control chamber 36 of the actuator 6, the discharge pressure
P.sub.d of the liquid does not change.
[0089] The product of the difference between the area A of the
pressurizing surface of the first pressure chamber 31 and the area
B of the pressurizing surface of the second pressure chamber 32,
that is, (A-B), and the generated pressure P.sub.2 is a consumed
force when the thrust f.sub.1 of the actuator 6 reaches its
maximum.
therefore
A.sub.1.times.P.sub.36=(C.times.P.sub.3)-((A-B).times.P.sub.2)
Equation (2)
where (A-B).times.P.sub.2 on the right side of Equation (2)
gradually increases from zero as the piston 1 moves in the other
direction (the right direction), while the discharge pressure
P.sub.d decreases, albeit slightly.
[0090] In this regard, fluctuations of the above-described
discharge pressure P.sub.d are caused by the load at the place of
discharge also. In the case of, for example, discharging with the
maximum discharge pressure, the discharge pressure P.sub.d
fluctuates.
[0091] In FIG. 1, the thrust f.sub.2 when the piston 1 is moved in
the one direction (the left direction) by the actuator 6 is
expressed by the product of the pressure-receiving surface area
A.sub.2 of the working surface 112 of the control piston 43 of the
actuator 6 within the control chamber 35 and the pressure P.sub.35
of the working fluid L acting on the pressure-receiving surface.
With respect to the thrust f.sub.2, pressure P.sub.2 is generated
in the liquid F within the second pressure chamber 32, the check
valve 83 opens due to the pressure P.sub.2, and the pressure
P.sub.2 acts on the third pressure chamber 33 in which the force
acts in the opposite direction to the second pressure chamber 32,
balancing with the thrust f.sub.2. The pressure P.sub.2 is
therefore equal to the discharge pressure P.sub.d.
(f.sub.2=)A.sub.2.times.P.sub.35=(B.times.P.sub.2)-(C.times.P.sub.2)
therefore A.sub.2/(B-C)=P.sub.2/P.sub.35 Equation (3)
[0092] Since the pressure P.sub.35 of the working fluid L flowing
into the control chamber 35 of the actuator and the pressure
P.sub.36 of the working fluid L flowing into the control chamber 36
are equal, in order for the liquid F discharged from the outlet
port 267 to have the predetermined pressure P.sub.d at all times,
the discharge pressure P.sub.3 when the piston 1 moves in the other
direction (the right direction) and the discharge pressure P.sub.2
when the piston 1 moves in the one direction (the left direction)
must be equal. From Equation (1) and Equation (3), therefore,
A.sub.1/C=A.sub.2/(B-C) Equation (4)
[0093] Equation (4) forms the foundation to discharge high-pressure
liquid with constant pressure using the high-pressure generation
device in accordance with the present invention.
[0094] Now, letting the thrust in the other direction and the
thrust in the one direction of the actuator 6 be f.sub.1 and
f.sub.2, respectively, the relationship between the area B of the
pressurizing surface of the second pressure chamber 32 and the area
C of the pressurizing surface of the third pressure chamber 33 is
expressed as:
f.sub.1/C=f.sub.2/(B-C)
[0095] Therefore, in order for the discharge pressure P.sub.d for
both directions (the left direction and the right direction) to be
kept constant, it is important that, with respect to a
predetermined pressure-receiving surface area ratio (or a thrust
ratio) .alpha., the working fluid L of the control piston 43 of the
actuator 6 acts on the working surfaces 122 and 112 of the control
chambers 36 and 35, the area B of the pressurizing surface of the
second pressure chamber 32, and the area C of the pressurizing
surface of the third pressure chamber 33 of the piston 1 are
selected so that the above-described Equation (4) holds.
[0096] The value described in Equation (4) is the ratio of the
pressure P.sub.35 and P.sub.36 of the working fluid L fed to the
actuator 6 to the pressure P.sub.d of the liquid F discharged from
the outlet port 267 of the high-pressure generation device, and the
inverse of that ratio is a pressure-increase ratio.
[0097] The compressibility n % of the liquid when the first
pressure chamber 31 and the second pressure chamber 32 communicate
with each other is defined by a total volume V.sub.0 before the
piston moves in the other direction (the right direction) and a
total volume V.sub.1 after it has moved in the other direction (the
right direction).
n=(V.sub.0-V.sub.1)/V.sub.0).times.100%
[0098] In other words, the compressibility is influenced by the
area A of the pressurizing surface of the first pressure chamber 31
and the difference (A-B) between the area A of the pressurizing
surface of the first pressure chamber 31 and the area B of the
pressurizing surface of the second pressure chamber 32. However, in
addition to the volumes of the first pressure chamber and the
second pressure chamber, when the volume of a flow passage is large
and when air is mixed into the liquid, the compressibility
decreases accordingly. It is therefore preferable that any extra
volume, such as that provided by a flow passage, be reduced to the
utmost.
[0099] When a fluid pressure cylinder is used as the actuator 6
like the high-pressure generation device 110 in accordance with the
present embodiment, it depends on Equation (4), but since when the
working fluid L is fed to move a liquid-pressure cylinder, the
thrust on the drive side is generally used with a margin, the
discharge pressure of the liquid F discharged from the outlet port
267 does not fluctuate, and the pressure of the working fluid L
fluctuates. The flows of the liquid F discharged from the outlet
port 267 and the working fluid L basically do not change.
[0100] In FIG. 2, the working fluid L flows into the second control
chamber 36 forming a side chamber of the control piston 43 of the
actuator 6 with a flowrate Q to be acted on the pressure-receiving
surface area A.sub.1 of the control piston 43 of the second control
chamber 36, thereby allowing the control piston 43 to move in the
other direction (the right direction) at a moving speed of v.sub.1.
Through this movement, the third pressure chamber 33 is reduced,
and by means of the area C of the pressurizing surface of the third
pressure chamber 33, the high-pressure liquid F is discharged from
the outlet port 267 with a flowrate of q.sub.1. This relationship
is expressed by the following Equation:
Q=A.sub.1.times.v.sub.1 v.sub.1=q.sub.1/C
therefore Q=A.sub.1.times.q.sub.1/C Equation (5)
[0101] In FIG. 1, the working fluid L flows into the first control
chamber 35 acting as a side chamber of the control piston 43 of the
actuator 6 with a flowrate Q to be acted on the pressure-receiving
surface area A.sub.2 of the control piston 43 of the first control
chamber 35, thereby allowing the control piston 43 to move in the
one direction (the left direction) at a moving speed of v.sub.2.
Through this movement, the second pressure chamber 32 is reduced,
and by means of the area B of the pressurizing surface of the
second pressure chamber 32, the high-pressure liquid F flows into
the expanding third pressure chamber 33, and the residual
high-pressure liquid F, after filling the third pressure chamber
33, is discharged from the outlet port 267 with a flowrate of
q.sub.2. This relationship is expressed by the following
Equation:
Q=A.sub.2.times.v.sub.2 v.sub.2=q.sub.2/(B-C)
therefore Q=A.sub.2=q.sub.2/(B-C) Equation (6)
[0102] From the above-described Equations (5) and (6),
(A.sub.1/C).times.q.sub.1=(A.sub.2/(B-C)).times.q.sub.2 Equation
(7)
[0103] In order for the flowrate q.sub.1 discharged from the outlet
port 267 when the piston is moved in the other direction (the right
direction) and the flowrate q.sub.2 discharged when it is moved in
the one direction (the left direction) to be equal, from Equation
(7),
A.sub.1/C=A.sub.2/(B-C) Equation (4)
[0104] This equation is the same as the above-described Equation
(4).
[0105] This means therefore that when the discharge pressure
P.sub.d of the liquid discharged from the outlet port 267 when the
piston moves in the other direction (the right direction) and when
it moves in the one direction (the left direction) are equal, an
equal discharge flow is provided at the same time.
[0106] When the thrust in the other direction (the right direction)
and the thrust in the one direction (the left direction) imparted
by the actuator 6 are equal, or for example, when the
pressure-receiving surface area A.sub.1 of the first control
chamber 35 and the pressure-receiving surface area A.sub.2 of the
second control chamber 36 of the control piston 43 of the actuator
6 are equal, from Equation (4),
C=B-C (since A.sub.1=P.sub.36=A.sub.2.times.P.sub.35)
therefore B=2C Equation (8)
[0107] In other words, when the area B of the pressurizing surface
of the second pressure chamber 32 is set to be twice as large as
the area C of the pressurizing surface of the third pressure
chamber 33, the liquid F with a constant discharge pressure Pd can
be discharged from the outlet port 267 continuously with a constant
flow.
[0108] When the piston performing the pumping operation is
reciprocated by a motor or engine having a rotating shaft, the
liquid F with a constant discharge pressure Pd can be discharged
from the outlet port 267 continuously, provided that Equation (8)
is fulfilled.
[0109] FIG. 11 is a diagram showing an example of an actuator in
which an eccentric heart-shaped cam is integral with a rotating
drive shaft.
[0110] FIG. 11 shows an example of the high-pressure generation
device 610, in which, as an actuator, a heart-shaped cam 76b is
integral with a rotating drive shaft 76a, where the heart-shaped
cam 76b is sandwiched between recessed extension parts 17a and 17b
through ball bearings 17c and 17d, and the extension parts 17a and
17b are connected with the piston rod 7. Using this actuator, the
moving speed v.sub.1 and the moving speed v.sub.2 can be equal and
constant, thereby allowing the liquid F with a constant pressure Pd
to be discharged from the outlet port 267 continuously with a
constant flow.
[0111] FIG. 12 is a diagram showing an example of a crank mechanism
as an actuator in which an eccentric shaft 55 is rotated by a
rotating drive shaft.
[0112] The example shows the high-pressure generation device 640,
in which, as an actuator, the eccentric shaft 55 is rotated by the
rotating drive shaft 76a and is connected to the piston rod 7
through the crank mechanism 30, 56, and 58. Using this actuator,
the liquid F with a constant pressure Pd can be discharged from the
outlet port 267 continuously.
[0113] FIG. 13 is an example of a configuration using a double-rod
fluid pressure cylinder as an actuator.
[0114] As shown in FIG. 13, a double-rod fluid pressure cylinder is
used as the actuator 6 for reciprocating the piston 1.
[0115] The piston rod 46 integral with the control piston 43 is
connected with the piston rod 7, while a rod 90 integral with the
control piston 43 on the other side is fitted into a circular hole
at the center of the head cover 44, protrudes, and reciprocates. A
ring 91 which is larger than the outer diameter of the rod 90 is
fixed to the protruded part of the rod 90.
[0116] When the working fluid L is fed from the power source P to
the first control chamber 35 of the control piston 43 through a
solenoid-operated valve 60a acting as a directional control valve,
and the other second control chamber 36 communicates with the tank
through the solenoid-operated valve 60a, the control piston 43
moves. When the control piston 43 reaches near the end of its
stroke, the ring 91 of the rod 90 acts on an electric switch 92b,
thereby switching the solenoid-operated valve 60a, allowing the
control piston 43 to move in reverse by flow passage switching.
Then, when it reaches near the end of its stroke, the ring 91 of
the rod 90 acts on an electric switch 92a, thereby switching the
solenoid-operated valve 60a, switching between the flow passages 61
and 62. The piston 1 also reciprocates, thereby drawing the liquid
F from the intake port 257 and discharging the liquid pressurized
at a constant pressure continuously.
[0117] FIG. 14 is an example using an automatic switching device
for switching a directional control valve of a fluid pressure
cylinder at high speed as an actuator.
[0118] The part surrounded by a two-dot chain line shown in FIG. 14
is the "Pressurized fluid automatic switching device" of Japanese
Patent No. 3,650,031 invented by the inventors of the present
application, in which valve-pushing rods of pilot valves protrude
from both side chambers of the reciprocating control piston 43, and
when the control piston reaches the end of its movement, the
valve-pushing rods of the pilot valves are pushed in, thereby
switching a directional control valve controlling the control
piston 43, allowing the piston 1 performing the pumping operation
to reciprocate. The high-pressure generation device 410 is required
to only feed the working fluid L into a feed port 70 and can
provide a highly reliable system without using the above-described
actuator and electric switching means.
[0119] Hereinafter, an example of the high-pressure generation
device in which a drive unit is arranged midway therebetween with
three pressure chambers distributed to the left and right will be
provided.
[0120] FIG. 15 and FIG. 16 are examples of the high-pressure
generation device in which a piston and a plunger are arranged on
the left and right with an actuator sandwiched therebetween.
[0121] As shown in FIG. 15 and FIG. 16, the high-pressure
generation device 210a arranges the piston 1 and a plunger 18 with
the actuator 6 arranged midway therebetween, provides the first
pressure chamber 31 and the second pressure chamber 32 outside the
piston 1 within the housing 2, provides the third pressure chamber
33 in the space at the tip of the plunger 18 on the other side, and
allows the three pressure chambers 31, 32, and 33 to communicate
with each other. The piston 1 and the plunger 18 are driven by the
actuator 6 to reciprocate. The actuator 6 including the double-rod
fluid pressure cylinder is used as a pulsation-free pump, in which
the working fluid L is fed to reciprocate the piston 1 and the
plunger 18, thereby drawing the liquid F and discharging the
pressurized liquid at a constant pressure continuously.
[0122] The high-pressure generation device 210a is different from
the above-described high-pressure generation devices 110, 610, 410,
640 and 810 only in the position for providing the second pressure
chamber 32, and is the same as the above-described high-pressure
generation device 110 in the operation of the first pressure
chamber 31, the second pressure chamber 32, and third pressure
chamber 33 for performing the pumping operation using the
reciprocal movement of the piston 1 and the plunger 18.
[0123] FIG. 17 is an example of one configuration of the
high-pressure generation device which reciprocates a piston and a
plunger with a drive unit in which an eccentric cam or bearing is
integral with a rotating drive shaft arranged midway
therebetween.
[0124] The high-pressure generation device 630 integrates an
eccentric cam or bearing with the rotating drive shaft 76a of the
drive unit, sandwiches the cam or bearing using a recessed
extension part 17, and connects the piston 1 and the plunger 18,
thereby allowing the piston 1 and the plunger 18 used to perform
the pumping operation to reciprocate.
[0125] The force being in balance with the thrust of the drive unit
is expressed by the product of the area of the pressure-receiving
surface when the liquid acts on the second pressure chamber and the
generated pressure.
[0126] When moving in the one direction (the left direction),
through the thrust of the drive unit, the second pressure chamber
32 reduces and the liquid flows into the expanding third pressure
chamber 33. At the same time, the residual liquid is discharged
from the outlet port 267. In order to balance with the thrust of
the drive unit, pressure in accordance with the area of the
pressure-receiving surface acting on the liquid in the second
pressure chamber 32 and the area of the pressure-receiving surface
acting on the liquid in the third pressure chamber 33 is generated,
and the liquid being pressurized is discharged outside from the
outlet port 267.
[0127] When moving in the other direction (the right direction),
the third pressure chamber 33 reduces, and the pressurized liquid
is discharged. In order to balance with the thrust of the drive
unit, pressure in accordance with the area of the
pressure-receiving surface acting on the liquid in the third
pressure chamber 33 is generated. The liquid being pressurized is
discharged outside from the outlet port 267. In addition, pressure
is generated due to the difference in the area of the pressurizing
surface between the first pressure chamber 31 and the second
pressure chamber 32.
[0128] Therefore, in order for the discharge pressure when moving
in the one direction (the left direction) and the discharge
pressure when moving in the other direction (the right direction)
to be equal, in accordance with the thrust of the drive unit, the
area of the pressure-receiving surface on which the liquid in the
second pressure chamber 32 acts and the area of the
pressure-receiving surface on which the liquid in the third
pressure chamber 33 acts are selected.
[0129] When moving in the other direction (the right direction),
through the difference in the pressure-receiving surface between
the first pressure chamber 31 and the second pressure chamber 32 on
which the liquid acts, the pressure within the first pressure
chamber 31 increases as the movement of the piston 1 and the
plunger 18 advances. The discharge pressure from the third pressure
chamber 33 thereby decreases as the movement advances, or when
there is a margin of thrust on the drive side, the discharge
pressure does not change, and the thrust on the drive side
increases. The pressure discharged from the outlet 257 depends on
the load at the place of discharge. When being discharged with the
maximum pressure, or for example, when in the high-pressure
generation device 630 in accordance with the present invention the
discharge pressure at the outlet port 257 when being emitted from a
miniature diameter nozzle is low, the fluctuation is low. The
higher the discharge pressure, the larger the fluctuation.
[0130] FIG. 18 and FIG. 19 are more examples of the high-pressure
generation device in which a piston and a plunger are arranged on
the left and right with an actuator sandwiched therebetween. Unlike
FIG. 15 and FIG. 16, the high-pressure generation device 210B is
provided with the second pressure chamber 32 at the tip of the
small-diameter piston part 9b, but as it shares other
configurations and manner of operation, any description thereof
will be omitted.
[0131] FIG. 20 is a configuration example in which the drive unit
shown in FIG. 17 is arranged midway therebetween instead of the
actuator shown in the configuration examples of the high-pressure
generation device shown in FIG. 18 and FIG. 19.
[0132] This high-pressure generation device 620 has the same
configuration as that shown in those figures, and as such, any
description thereof will be omitted.
[0133] FIG. 21 is an example of the high-pressure generation device
in which the second pressure chamber and the third pressure chamber
are provided in both side chambers of the piston part 8.
[0134] As shown in FIG. 21, this high-pressure generation device
310 arranges the piston 1 and the plunger 18 on the left and right
with the actuator 6 arranged midway therebetween, is provided with
the second pressure chamber 32 and the third pressure chamber 33
outside the piston 1 within the housing 2, is provided with the
first pressure chamber 31 in the space at the tip of the plunger 18
on the other side, and allows the second pressure chamber 32 and
the first pressure chamber 31 to communicate with each other
through the second flow passage 311 provided within the housing 2.
The piston 1 and the plunger 18 reciprocate using the actuator 6.
The actuator 6, which is a double-rod fluid pressure cylinder
having two control pistons, is used as a pulsation-free pump which
feeds the working fluid L to reciprocate the control pistons,
thereby drawing the liquid F from the outside and discharging the
liquid with a constant pressure from the outlet port 267
continuously.
[0135] The housing 2 which has the outlet port 267 and into which
the piston 1 is fitted therewithin and a housing 2a which has the
intake port 257 and into which the plunger 18 is fitted therewithin
are clamped by a bolt 4 with the actuator 6 sandwiched
therebetween. The piston 1 and the large-diameter plunger 18 which
are reciprocated by the actuator 6 are arranged on the left and
right with the actuator 6 arranged midway therebetween. The first
pressure chamber 31 is provided at the tip of the large-diameter
plunger 18. The second pressure chamber 32 is provided in the side
chamber at the inner part of the piston part 8, which reciprocates
in conjunction with the plunger 18 and of which the outer diameter
is smaller than that of the plunger 18. The third pressure chamber
33 is provided in the side chamber of the piston part 8 on the
piston rod 7 side. The check valve 81 is provided in the first flow
passage 254 which communicates via the intake port 257 to the first
pressure chamber 31. The check valve 82 is provided in the second
flow passage 311 which communicates via the first pressure chamber
31 to the second pressure chamber 32. The check valve 83 is
provided in the third flow passage 271 which communicates via the
second pressure chamber 32 to the third pressure chamber 33. The
outlet port 267 is provided which discharges the liquid from the
third pressure chamber 33 to the outside.
[0136] FIG. 22 is a graph showing a waveform (theoretical values)
of the discharge pressure Pd of the high-pressure generation device
in accordance with the present embodiment. The horizontal axis
represents time elapsed, while the vertical axis represents the
pressure of the liquid discharged.
[0137] As shown in FIG. 24, in the high-pressure generation device
110 in accordance with the present embodiment, one stroke at the
onset of operation is pressurized from a zero-pressure state, but
thereafter, except for stop states S, or the moments at which the
movement direction of the piston switches, the discharge pressure
Pd of the liquid is kept constant at all times. The high-pressure
generation device 110 therefore does not require an accumulator and
can discharge high-pressure liquid with very small pressure
fluctuations.
[0138] FIG. 23 is a graph showing a waveform (theoretical values)
of the discharge pressure P of the pressure conversion device
including two pressurizing chambers disclosed in Japanese Examined
Patent Application Publication No. 62-21994 as a comparative
example. The horizontal axis represents time elapsed, while the
vertical axis represents the pressure of the liquid discharged.
[0139] As shown in FIG. 23, since the pressure conversion device
including two pressurizing chambers switches using a directional
control valve, it takes time for switching, and two pressurizing
chambers require pressurizing from a zero-pressure state for each
cycle, thereby providing the liquid discharged with large pressure
fluctuations.
INDUSTRIAL APPLICABILITY
[0140] The high-pressure generation device in accordance with the
present invention can be applied to a various kinds of hydraulic
machines and devices for water jets, can be provided a pressure
intensifier and a volume intensifier, and can be provided as a pump
which discharges liquid such as chemicals and slurries, which are
different from the working fluid L.
* * * * *