Information
-
Patent Grant
-
6823671
-
Patent Number
6,823,671
-
Date Filed
Thursday, June 27, 200222 years ago
-
Date Issued
Tuesday, November 30, 200420 years ago
-
Inventors
-
Original Assignees
-
Examiners
Agents
- St. Onge Steward Johnston & Reens, LLC
-
CPC
-
US Classifications
Field of Search
US
- 060 413
- 060 414
- 060 416
- 060 419
-
International Classifications
-
Abstract
The invention relates to a free-piston unit for pumping fluid from a low pressure to a high pressure. The free piston is displaced by a hydraulic part under the influence of the fluid pressure on a plunger which is connected to a combustion piston. The force exerted on the plunger by the fluid pressure in a pressure chamber during the compression stroke can be set using conversion means by setting a third pressure for fluid which is to be displaced via a pressure chamber from the first fluid source to the second fluid source.
Description
The invention relates to a free-piston unit. A unit of this type is known from NL 6814405. The drawback of the known device is that the first, low pressure and the second, high pressure are dependent on the use of the device or the use which is being made at a specific moment of the hydraulic energy which is generated. Consequently, the unit is difficult to control, since the forces acting on the plunger cannot be set independently of the low or high pressure; with the result that the energy supplied to or extracted from the combustion piston is difficult to regulate. To avoid this drawback, the unit is designed in yet another way. It is thus possible to set the energy supplied to or extracted from the combustion piston independently of the first pressure and/or the second pressure, so that accurate control of the combustion process and also part-load operation are possible.
According to a refinement, the unit is designed in yet another way. It is thus possible to set the amount of energy supplied to the combustion pistons so that the combustion process can be controlled more successfully.
According to a refinement, the unit is designed in yet another way. This makes it easy to set the third pressure.
According to a refinement, the unit is designed in yet another way. This ensures uninterrupted use of the unit.
According to a refinement, the unit is designed in yet another way. In this way, it is easy to drive rotationally driven auxiliary equipment; such as a dynamo, a fan and the like.
According to a further refinement, the device is designed in yet another way. This improves the operation of the hydraulic transformer, since fluctuations in pressures and fluid flows are evened out.
According to one embodiment, the device is designed in yet another way. As a result, the fluid flow through the hydraulic transformer is always equal to the volume pumped to the second fluid source by the unit, so that this volume can also be known in the control unit.
According to one embodiment, the device is designed in yet another way. In this way, it is easy to set the force exerted on the plunger.
According to one embodiment, the device is designed in yet another way. As a result, the supply of fluid from the unit to the second fluid source always takes place via the hydraulic transformer, so that the supply of fluid is more or less free of pulsations which limits the energy losses and prevents pressure pulsations if there is no accumulator in the system connected to the second fluid source. It is also possible for the fluid flow to be directly adapted to the fluid flow extracted by the consumers.
The invention also comprises a device in yet another way. This makes the flow of fluid to the second fluid source more uniform.
The invention is explained below with reference to a number of exemplary embodiments and with the aid of a drawing, in which:
FIG. 1
shows a diagrammatic cross section through a first embodiment of a free-piston unit with a hydraulic transformer;
FIG. 2
shows a diagrammatic cross section through a second embodiment of a free-piston unit with a hydraulic transformer;
FIG. 3
shows a diagrammatic cross section through a third embodiment of a free-piston unit with a hydraulic transformer;
FIG. 4
shows a diagrammatic cross section through a fourth embodiment of a free-piston unit with a hydraulic transformer;
FIG. 5
shows a diagrammatic cross section through a fifth embodiment of a free-piston unit with a hydraulic transformer;
FIG. 6
shows a diagrammatic cross section through a sixth embodiment of a free-piston unit with a hydraulic transformer;
FIG. 7
shows a diagrammatic cross section through a seventh embodiment of a free-piston unit with a hydraulic transformer;
FIG. 8
shows a diagrammatic cross section through an eighth embodiment of a free-piston unit with a hydraulic transformer;
FIG. 9
shows a number of interacting free-piston units as shown in
FIG. 4
;
FIG. 10
shows a number of free-piston units which interact in an adapted way and as shown in
FIG. 6
;
FIG. 11
diagrammatically depicts a ninth embodiment of the hydraulic part of a free-piston unit;
FIG. 12
diagrammatically depicts a tenth embodiment of the hydraulic part of a free-piston unit;
FIG. 13
diagrammatically depicts an eleventh embodiment of the hydraulic part of a free-piston unit;
FIG. 14
diagrammatically depicts a twelfth embodiment of the hydraulic part of a free-piston unit;
FIG. 15
diagrammatically depicts a thirteenth embodiment of the hydraulic part of a free-piston unit; and
FIG. 16
diagrammatically depicts an exemplary embodiment of a free-piston unit with a hydraulic transformer, the two combustion pistons being movably coupled between two combustion spaces.
As far as possible, the same reference symbols are used for corresponding components throughout the various figures.
FIG. 1
shows a diagrammatic cross section through a free-piston unit
3
which, by means of a transformer line
14
, is coupled to a hydraulic transformer
11
. The free-piston unit
3
is known from earlier publications and is only outlined here. A combustion piston
17
can move in a reciprocating manner in a first cylinder
19
. The first cylinder
19
is closed at one end, where it forms a combustion space
2
in conjunction with the combustion piston
17
. In a known way, combustion air is introduced into the combustion space
2
by means of an air-supply device
4
. During a compression stroke A, the combustion piston
17
moves toward a top dead center, the position of the combustion piston
17
in which the volume of the combustion space
2
is minimal, and, in the process, compresses the combustion air. When the combustion piston
17
is close to the top dead center, fuel is introduced into the combustion space
2
by a fuel-supply system
1
. The fuel ignites on account of the high temperature of the compressed combustion air. As a result, the gas pressure in the combustion space
2
will rise and the combustion piston will move from the top dead center toward a bottom dead center. During this expansion stroke B, the combustion gases expand and the energy released during the combustion will be predominantly discharged by the combustion piston
17
. The bottom dead center is the position of the combustion piston
17
in which the volume of the combustion chamber
2
is at its maximum. During the movement of the combustion piston
17
toward the bottom dead center, first of all an outlet duct
18
is opened, so that the combustion gases are able to leave the combustion space
2
. Then, an air-supply duct is opened, with the result that further combustion air can flow into the combustion space
2
.
The fuel-supply system
1
may be suitable for supplying fluid fuel which, for example, is atomized when injected into the combustion space. The fuel-supply system may also be suitable for supplying gaseous fuel. If appropriate, the fuel may also be ignited by spark ignition instead of by self-ignition.
A piston rod
5
is attached to the combustion piston
17
, which piston rod
5
connects a plunger
7
to the combustion piston
17
. The plunger
7
can move in a reciprocating manner in a second cylinder
15
. Together with the closed end of the second cylinder
15
, the plunger
7
forms a first pressure chamber
8
. A seal
6
is arranged around the piston rod
5
. The oil which is scraped off by the seal
6
is discharged via a leakage oil line
16
.
The assembly comprising the combustion piston
17
and the plunger
7
moves freely in a reciprocating manner under the influence of the forces exerted thereon. These forces are produced by the pressure of the gases in the combustion space
2
and the pressure of the fluid in the first pressure chamber
8
. For compression of the combustion air, fluid is fed into the first pressure chamber
8
via a compression line
14
. The pressure of the fluid in the first pressure chamber
8
during the movement of the combustion piston
17
from the bottom dead center toward the top dead center determines the amount of energy which is supplied to the combustion air during the compression and therefore the combustion. The pressure of the fluid in the first pressure chamber
8
during the movement of the combustion piston
17
from the top dead center toward the bottom dead center determines the amount of energy which is extracted. By making a control unit set the pressure of the fluid in the first pressure chamber
8
correctly, it is possible for the combustion piston
17
to move in such a manner that the combustion takes place optimally. To ensure that this process takes place correctly, sensors which are able to detect the position of the plunger
7
in the vicinity of the bottom dead center are positioned in a known way.
To control the fluid pressure in the first pressure chamber
8
, the compression line
14
is coupled to one of the ports of the hydraulic transformer
11
A hydraulic transformer of this type is known, for example, from patent applications WO 9731185, WO 9940318 and WO 9951881, in the name of the same applicant, and the contents of which are hereby deemed to be incorporated. The hydraulic transformer
11
is coupled to a low-pressure connection T via a low-pressure line
13
and to the high-pressure connection P via a high-pressure line
10
. If appropriate, the low-pressure line
13
is provided with a low-pressure accumulator
12
, and if appropriate the high-pressure line
10
is provided with a high-pressure accumulator
9
, in order to reduce pressure pulsations in the lines
10
and
12
, respectively.
The hydraulic transformer
11
is provided with an adjustment device which is able very quickly to set the pressure in the compression line
14
at a medium pressure C. During compression stroke A, that is to say the movement of the combustion piston
17
from the bottom dead center toward the top dead center, the pressure in the first pressure chamber
8
is the medium pressure C which is, for example, approximately the mean of the pressure in the high-pressure connection P and the low-pressure connection T. When the combustion piston
17
is at the top dead center, the hydraulic transformer
11
is adjusted so that the pressure in the first pressure chamber
8
becomes equal to or slightly higher than the pressure in the high-pressure connection P. When the combustion piston
17
, after the expansion stroke B, has moved back to the bottom dead center, the hydraulic transformer
11
is adjusted in such a manner that the pressure in the first pressure chamber
8
becomes approximately equal to zero, so that the combustion piston
17
comes to a standstill. If appropriate, the changes in the pressure in the first pressure chamber
8
take place more gradually during the piston movement, in which case the control unit regulates the settings of the hydraulic transformer
11
and therefore of the pressure in the first pressure chamber
8
on the basis of the desired release of energy to or uptake of energy from the combustion piston
17
.
As a result of the hydraulic transformer
11
being used, it is also possible for the pressure in the first pressure chamber
8
, during the movement of the combustion piston
17
toward the bottom dead center, to be kept at a lower level than the pressure in the high-pressure connection P. The amount of energy extracted from the combustion piston
17
is then also lower and the amount of fuel supplied is likewise lower. As a result, it is thus possible to make the free-piston unit function on part-load for each stroke, which may be an advantage during start-up, when the free-piston unit
3
is cold, or, for example, under zero load. In other situations too it may be advantageous that the power of the free-piston unit
3
can be regulated in two ways, both by controlling the stroke frequency and by controlling the amount of fuel supplied and therefore the amount of energy converted for each stroke.
For the free-piston unit
3
to operate correctly, the control system is designed as an electronic system and also encompasses the control unit of the fuel-injection system
1
and of the hydraulic transformer
11
. For the purposes of control, if appropriate temperature sensors are arranged in the free-piston unit
3
and pressure sensors are arranged in the high-pressure connection P and the low-pressure connection T. Other sensors which are required for correct operation are also coupled to the control unit, in the manner which is known to the person skilled in the art.
FIG. 2
shows an improved embodiment of the free-piston unit
3
having a second pressure chamber
21
, which is connected to the high-pressure connection P via a coupling line
20
. The fluid which is present in the second pressure chamber
21
exerts a force on the plunger
7
which is directed away from the combustion space
2
, so that the combustion piston
17
will move toward the bottom dead center. As a result, it is easier, if no ignition of the fuel has taken place after compression and fuel injection, for the combustion piston
17
to be moved back to the bottom dead center for a further stroke.
FIG. 3
shows an embodiment of the free-piston unit
3
in which the first pressure chamber
8
is connected, via a nonreturn valve
22
, to the high-pressure connection P. A nonreturn valve
23
is also positioned in the compression line
14
. During the expansion stroke, as the combustion piston
17
moves toward the bottom dead center, fluid will be pumped out of the first pressure chamber
8
directly to the high-pressure connection P, via the nonreturn valve
22
. The high pressure (peak) which occurs in the first pressure chamber
8
is blocked by the nonreturn valve
23
. This reduces the load on the hydraulic transformer
11
, which can therefore be of smaller design.
While the combustion piston is stationary at the bottom dead center, it is possible for fluid Lo leak out of the second pressure chamber
21
to the first pressure chamber
8
past the plunger
7
. As a result, the plunger
7
will move at creep speed toward the top dead center, which is undesirable. To prevent this creep, the first pressure chamber
8
is connected to the low-pressure connection T via an anti-creep valve
25
. The anti-creep valve
25
is opened if the combustion piston is to remain stationary at the bottom dead center for a prolonged period.
Instead of using the hydraulic transformer
11
, in another embodiment, during the compression stroke the pressure chamber
8
can be provided with fluid under a possibly adjustable pressure in another way. Instead of the hydraulic transformer
11
, it is possible to use a pump for supplying fluid to the first pressure chamber
8
, which pump if appropriate may have an adjustable output. This pump may be a rotary pump or, if appropriate, a linear piston. The pump can be driven by a rotating hydraulic motor or, if appropriate, a hydraulic cylinder. The pump and/or hydraulic motor may be provided with adjustment means, so that the output or the pressure to be supplied can be adjusted.
FIG. 4
shows another embodiment in which the supply of fluid to the first pressure chamber
8
is switched using a starting valve
27
which is positioned in the line leading from the high-pressure connection P to the hydraulic transformer
11
. In this case, the setting of the hydraulic transformer
11
remains more or less constant and is dependent on the combustion process in the combustion space
2
. If the combustion piston
17
is to execute a compression stroke, the starting valve
27
is opened. If the combustion piston
17
is to remain at the bottom dead center, the starting valve
27
is closed.
FIG. 5
shows an embodiment with a starting valve
28
in the compression line
14
between the hydraulic transformer
11
and the first pressure chamber
8
. In the embodiment shown, the compression line
14
is also split into two connections to the first pressure chamber
8
, the compression line
14
″ being closed by the plunger
7
when the combustion piston
17
is in the bottom dead center. The starting valve
28
is positioned in the compression line
14
′ which maintains an open connection with the first pressure chamber
8
. A nonreturn valve
23
′ and
23
″ is positioned in each compression line
14
′ and
14
″ respectively. Splitting the compression line
14
into a connection which can be closed off by the plunger
7
and a connection which remains open allows the starting valve
28
to be of smaller design while the flow losses remain limited.
FIG. 6
shows an embodiment in which a valve
29
is accommodated in the compression line
14
″ which can be closed off by the plunger
7
. As a result, it is possible to close the compression line
14
″ and to depressurize the first pressure chamber
8
by opening the valve
25
. As a result, it is possible, in the event of misfiring, to move the combustion piston
17
toward the bottom dead center without having to change the setting of the hydraulic transformer
11
.
FIG. 7
shows an embodiment in which the compression line
14
is connected to an accumulator
30
. As a result, the supply of fluid to the first pressure chamber
8
can be primed rapidly, with the mass to be accelerated being minimal and without the hydraulic transformer
11
firstly having to be brought up to speed.
FIG. 8
shows an embodiment in which the connection of the first pressure chamber
8
to the high-pressure connection P is designed with two lines and two nonreturn valves
22
′ and
22
″. When the combustion piston
17
is in the vicinity of the bottom dead center, the plunger
7
closes the line to the nonreturn valve
22
″. It is thus possible to design the latter with a lower flow resistance, which limits losses, since it is not necessary for this nonreturn valve
22
″ to close rapidly.
FIGS. 9 and 10
show the use of a number of free-piston units
3
which are connected to the high-pressure connection P and the low-pressure connection T. The embodiment shown in
FIG. 9
shows the free-piston unit
3
in the design shown in FIG.
4
. The control unit preferably switches the starting valves
27
in such a manner that the compression stroke A and therefore the ignition processes in the combustion space take place successively, so that the flow of fluid to the high-pressure connection P takes place as evenly as possible. The embodiment shown in
FIG. 10
shows free-piston units
3
in the design shown in FIG.
6
. The free-piston units
3
have a common hydraulic transformer
11
, the level of the medium pressure C in the compression line
14
being adapted to the optimum action of the free-piston units
3
.
FIGS. 11-15
show exemplary embodiments of the hydraulic part of the free-piston unit, predominantly illustrating the components which play a role in the generation of hydraulic pressure, so that inter alia the valves which are required to, for example, prevent creep of the free piston and to return the free piston to the starting position are not shown in further detail.
FIG. 11
shows an exemplary embodiment in which the fluid supplied by the unit is supplied directly to the high-pressure line
10
via a nonreturn valve
22
. The medium pressure C supplied by the hydraulic transformer
11
is, via a medium-pressure line
32
and the accumulator
30
, permanently present in the second pressure chamber
21
and, during the compression stroke, in the first pressure chamber
8
. The force exerted on the plunger by the fluids present in the hydraulic part is therefore dependent on the medium pressure C in the medium-pressure line
32
. In this exemplary embodiment, the flow of oil through the hydraulic transformer
11
is limited to the supply to the first pressure chamber
8
, which supply takes place at relatively low pressure, so that the energy losses in the hydraulic transformer
11
are limited. Consequently, the efficiency of this embodiment is relatively high.
FIG. 12
shows an embodiment in which the starting and stopping of the free piston is carried out by means of a piston drive
31
, a third pressure chamber
33
being used in a known way. The force exerted on the plunger
7
is dependent on the one hand on the pressure prevailing in the piston drive
31
and on the other hand on the medium pressure C prevailing in the medium-pressure line
32
. The means for setting the pressure in the piston drive
31
are not shown in further detail. The fluid flowing to the first pressure chamber
8
is immediately sucked out of the low-pressure line
13
via the nonreturn valve
23
and is pumped to the high-pressure line
10
via the nonreturn valve
22
and the hydraulic transformer
11
. The advantage of this embodiment is that the fluid supplied to the high-pressure line
10
is free of pulsations and that it is not necessary to position a high-pressure accumulator in the high-pressure line
10
.
FIG. 13
shows an embodiment which is similar to the embodiment shown in
FIG. 11
, except that the piston drive
31
and the third pressure chamber
33
have been added. This embodiment combines relatively high efficiency with good controllability of the energy supplied to the plunger
7
.
FIG. 14
shows an exemplary embodiment which is similar to the embodiment shown in FIG.
13
and in which the second pressure chamber
21
is also connected to the high-pressure line
10
via a nonreturn valve
22
b
. As a result, fluid is supplied to the high-pressure line
10
during the compression stroke and during the expansion stroke, so that the pulsations occurring in this supply of fluid are smaller while the efficiency benefit is retained.
FIG. 15
shows an exemplary embodiment which is similar to the embodiment shown in
FIG. 14
, with fluid being pumped to the high-pressure line
10
both during the compression stroke and during the expansion stroke.
FIG. 16
shows an exemplary embodiment of a free-piston unit in which two combustion pistons
34
are coupled via the piston rod
5
, which in this case is continuous and to which the plunger
7
is attached. Together with a cylinder, the plunger
7
forms a right-hand pressure chamber
35
and a left-hand pressure chamber
36
. The pressure chambers
35
and
3
c
are connected to the high-pressure line
10
via nonreturn valves
22
. The power to be supplied to the combustion pistons
34
during a compression stroke can be adjusted by the right-hand pressure chamber
35
and the left-hand pressure chamber
36
being connected to the medium-pressure line
32
, the medium pressure C of which can be set by the hydraulic transformer
12
, via the nonreturn valves
23
.
The auxiliary equipment required is not shown in the various exemplary embodiments. This auxiliary equipment may comprise, inter alia, a cooling fan, a generator and possibly a pump. Equipment of this nature is preferably driven in rotation, and to this end the rotor which forms part of the hydraulic transformer
11
is provided with an output shaft. The power required for the auxiliary equipment is proportional to the power which is to be supplied by the unit. The power to be supplied by the unit is proportional to the rotation of the hydraulic transformer
11
, so that using the rotation or the hydraulic transformer to drive the auxiliary equipment avoids losses caused by zero load and leads to higher efficiency.
To increase the stability of the hydraulic transformer
11
, it is also possible to provide the rotor with an output shaft and to couple the latter to a rotatable mass. This provides some degree of damping of changes in the rotational speed of the rotor, so that the hydraulic transformer can be controlled more accurately.
The design details which are shown in the various embodiments can also be used in other embodiments, in which case similar effects are achieved in this use as well.
Claims
- 1. A free-piston unit for converting fuel into hydraulic energy by displacing fluid from a first fluid source which is at a first, low pressure to a second fluid source which is at a second, high pressure, comprising a combustion part, a hydraulic part and a control unit, the combustion part comprising a first cylinder with a combustion piston and a combustion space the volume of which becomes smaller during a compression stroke and becomes larger during an expansion stroke, a fuel-supply system for supplying fuel, the hydraulic part comprising a plunger which is coupled to the combustion piston and can move in at least one cylinder thus forming one or more pressure chambers on which fluid which is present in the pressure chamber(s) during the compression stroke and during the expansion stroke, exerts a force directed toward the combustion space, characterized in that adjustable pressure conversion means for setting a third pressure for fluid which is to be displaced via the pressure chamber from the first fluid source to the second fluid source.
- 2. The free-piston unit as claimed in claim 1, wherein means are present for setting the energy which is supplied to the plunger during the compression stroke.
- 3. The free-piston unit as claimed in claim 1, wherein the adjustable conversion means comprise a hydraulic transformer which is connected to the first fluid source and the second fluid source.
- 4. The free-piston unit as claimed in, wherein the hydraulic transformer is provided with a rotor for enabling unlimited fluid flows to be achieved.
- 5. The free-piston unit as claimed in claim 4, wherein the rotor functions as a motor for driving auxiliary equipment.
- 6. The free-piston unit as claimed in claim 4, wherein the rotor is coupled to a rotatable mass for stabilizing its rotational speed.
- 7. The free-piston unit as claimed in claim 3, wherein the supply of fluid from the first fluid source to the second fluid source takes place via at least one pressure chamber and the hydraulic transformer.
- 8. The free-piston unit as claimed in claim 3, wherein the supply of fluid from the first fluid source to a pressure chamber takes place via the hydraulic transformer.
- 9. The free-piston unit as claimed in claim 3, wherein discharge of fluid from a pressure chamber to the second fluid source takes place via the hydraulic transformer.
- 10. A free-piston unit for converting fuel into hydraulic energy as claimed in claim 1, comprising at least two free-piston units, wherein the control unit enables the free piston units to successively execute a compression stroke.
Priority Claims (1)
Number |
Date |
Country |
Kind |
1013996 |
Dec 1999 |
NL |
|
PCT Information
Filing Document |
Filing Date |
Country |
Kind |
PCT/NL00/00955 |
|
WO |
00 |
Publishing Document |
Publishing Date |
Country |
Kind |
WO01/49998 |
7/12/2001 |
WO |
A |
US Referenced Citations (2)
Number |
Name |
Date |
Kind |
3606591 |
Potma |
Sep 1971 |
A |
6116138 |
Achten |
Sep 2000 |
A |
Foreign Referenced Citations (4)
Number |
Date |
Country |
6814405 |
Apr 1970 |
NL |
WO 9854450 |
Dec 1998 |
WO |
WO 9854468 |
Dec 1998 |
WO |
WO 9854468 |
Dec 1998 |
WO |