U.S. patent application number 11/577629 was filed with the patent office on 2007-10-25 for device for generating highly compressed gas.
Invention is credited to Klaus Baumer, Dirk Grullch, Norbert Schoiz, Herbert Wlegand.
Application Number | 20070248472 11/577629 |
Document ID | / |
Family ID | 35613763 |
Filed Date | 2007-10-25 |
United States Patent
Application |
20070248472 |
Kind Code |
A1 |
Baumer; Klaus ; et
al. |
October 25, 2007 |
Device for Generating Highly Compressed Gas
Abstract
In order to generate a highly compressed gas, a multistage
high-pressure compressor is used, which has a number of 3
compressor stages (10a, 10b, 10c, 10d). A vortex tube (20a, 20b,
20c, 20d) is connected downstream from these compressor stages
(10a, 10b, 10c, 10d). The pressure difference between the pressure
line (4) of the high-pressure compressor and the compressed gas
reservoir (7) to be filled is used for driving, together with an
expansion turbine (5), a pre-compressor (2) for pre-compressing the
gas before entering the first compressor stage (10a).
Alternatively, a vortex tube for cooling gas can be mounted between
the last compressor stage (10d) and the compressed gas reservoir
(7). The inventive device permits a direct filling of a compressed
gas reservoir in order to reach a limit value of the pressure in
the compressed gas reservoir at a predetermined limit temperature,
said limit value being stipulated according to the technical
rules.
Inventors: |
Baumer; Klaus; (Bonn,
DE) ; Grullch; Dirk; (Siegburg, DE) ; Schoiz;
Norbert; (Troisdorf, DE) ; Wlegand; Herbert;
(Koln, DE) |
Correspondence
Address: |
RENNER OTTO BOISSELLE & SKLAR, LLP
1621 EUCLID AVENUE
NINETEENTH FLOOR
CLEVELAND
OH
44115
US
|
Family ID: |
35613763 |
Appl. No.: |
11/577629 |
Filed: |
October 14, 2005 |
PCT Filed: |
October 14, 2005 |
PCT NO: |
PCT/EP05/55278 |
371 Date: |
April 20, 2007 |
Current U.S.
Class: |
417/251 |
Current CPC
Class: |
F25B 9/04 20130101 |
Class at
Publication: |
417/251 |
International
Class: |
F04B 25/00 20060101
F04B025/00 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 21, 2004 |
DE |
10 2004 051 189.6 |
Oct 21, 2004 |
DE |
10 2004 051 191.8 |
Feb 15, 2005 |
DE |
10 2005 006 751.4 |
Apr 6, 2005 |
DE |
10 2005 016 114.6 |
Claims
1. A device for generating highly compressed gas comprising a
single-stage or a multistage compressor (10a, 10b, 10c, 10d) and a
cooling device downstream of at least one compressor stage, the
cooling device being configured as a vortex tube (20a, 20b, 20c,
20d; 40a, 40b, 40c, 40d).
2. The device of claim 1, characterized by a multistage
high-pressure compressor (10a-10d), wherein downstream of at least
one compressor stage a vortex tube (20a, 20b, 20c, 20d; 40a, 40b,
40c, 40d) is arranged, and an expansion unit (5) is arranged
between the high-pressure compressor and a pressure gas container
(7), the expansion unit driving a pre-compressor (2) for
compressing the gas before it enters into the first compressor
stage (10a).
3. The device of claim 1, wherein, in a multistage high-pressure
compressor, the vortex tube is arranged between the last compressor
stage (10d) and a pressure gas container (7).
4. The device of claim 1, wherein the vortex tubes (20a, 20b, 20c,
20d) have a cold gas outlet (22a, 22b, 22c, 22d) and a hot gas
outlet (24a, 24b, 24c, 24d), the gas being supplied from the cold
gas outlet to the subsequent compressor stage and the temperature
of the gas from the hot gas outlet is reduced by throttling the hot
gas flow and is returned into the respective compressor stage.
5. The device of claim 1, wherein, between the individual
compressor stages (10a, 10b, 10c, 10d), the vortex tubes are
supercritical and are operated at the same pressure ratio.
6. The device of claim 4, wherein the throttling is effected
through throttle points (25a, 25b, 25c, 25d) dimensioned such that
a predetermined mass ratio between the cold gas and the hot gas is
observed.
7. The device of claim 4, wherein the cold gas (22d) is redirected
into the first compressor stage (10a) by means of a switching
device (101), whereby the cold gas flow is subjected to further
throttling and thus to an additional reduction in temperature, if
the temperature of the cold gas exceeds a predefined temperature
for filling the pressure gas container (7).
8. The device of claim 1, wherein the outlet of the last compressor
stage (10d) of the multistage compressor is connected to a vortex
tube (20d) whose cold gas outlet is adapted to be connected to the
inlet of the first compressor stage (10a) via a return pipe
(104).
9. The device of claim 8, wherein the return pipe (104) includes a
throttle (103).
10. The device of claim 8, wherein the connection of the outlet of
the last compressor stage (10d) with the inlet of the first
compressor stage (10a) is established in dependence on the measured
gas temperature in the cold gas flow (22d) of the vortex tube (20d)
of the last compressor stage (10d).
11. The device of claim 1, wherein a pre-compression to between 0.5
bar and 2.0 bar is effected in a pre-compressor (2), the output
pressure of the high-pressure compressor being freely selectable
within a wide range.
12. The device of claim 11, wherein, by predefining the output
pressure of the multistage high-pressure compressor, the
temperature decrease is adjusted to the ambient temperature through
the throttling effect an the Joule-Thomson effect during the
filling of the pressure gas container (7), so that a pressure of
200 bar is reached in the pressure gas container (7) at a reference
temperature of 15.degree. C., independent of the ambient
temperature.
13. The device of claim 1, wherein, for cooling, the com-pressed
gas is passed over a cooler (33) using water as the cooling
medium.
14. The device of claim 1, wherein at least some of the vortex
tubes (40a, 40b, 40c, 40d) are cooled from outside by a cooling
device (44a, 44b, 44c, 44d).
15. The device of claim 13, wherein the heated water dissipates its
heat through a heat exchanger (33) for use in heating domestic
water and/or heating water for room heating.
16. The device of claim 15, wherein the expansion unit (5) drives a
pump (8) for an additional circulation of the water in the primary
circuit of the heat exchanger (33).
17. A device for decreasing the temperature of a pressurized gas
comprising a feed pipe (101) leading to a swirl generator (102) and
a vortex tube (105) branching from the swirl generator (102) for
conveying a rotating vortex flow (121), wherein the outside of the
vortex tube (105) is exposed to a cooling device (130), that a
swirl brake (109) for slowing the vortex flow (121) down is
arranged in the vortex tube (105), and that a flow path (122) leads
from the swirl brake (109) into a filling pipe (107).
18. The device of claim 17, wherein the flow path (122) extends
centrically through the vortex tube (105) within the vortex flow
(121).
19. The device of claim 17 or 18, wherein the filling pipe (107)
also branches from the swirl generator (102) and wherein the
diameter of the filling pipe (107) is smaller than the diameter of
the vortex tube (105).
20. The device of claim 17, wherein the swirl brake (109) is a
closure (110) arranged in the vortex tube (105).
21. The device of claim 20, wherein the closure (110) is a piston
adapted to be adjusted axially in the vortex tube.
22. The device of claim 17, wherein the cooling device (130)
comprises a cooling jacket (131) surrounding the vortex tube (105),
a cooling medium flowing through the jacket.
23. The device of claim 17, characterized by its use for filling a
pressure gas container.
Description
[0001] The invention refers to a device for generating highly
compressed gas with a single-stage or a multistage compressor.
Besides various other applications, the present device is useful in
a gas fueling system for fueling vehicles running on natural gas,
methane or similar gases or on hydrogen.
[0002] A problem with gases as an energy storage in vehicles is the
greater storage volume required as compared to liquid energy
sources, which, for natural gas, is greater by three orders of
magnitude under ambient conditions. For this reason, it has been
regulated that natural gas is available at gas stations at a
pressure of 250 bar so that, as defined by technical rules, a
pressure of 200 bar is reached and not exceeded in the pressure gas
container of a vehicle at a reference temperature of 15.degree. C.
Thus, compared to a fuel-operated vehicle, at least only three
times the storage volume has to be made available in a car.
[0003] In gas fueling installations, the pressurizing work to be
performed causes a heating of the gas in the pressure gas
container. The Joule-Thomson effect (a change in the gas
temperature by throttling) of the real gas generally counter-acts
this heating. However, it is only under very favorable conditions,
i.e. at sufficiently low temperatures, that the Joule-Thomson
effect and the heat dissipation to the environment suffice to
compensate for the heating caused by the pressurizing work of the
gas. In gas fueling installations without a cooling device, if
these favorable conditions do not exist, the pressure gas container
will be filled short upon decanting. This is due to the fact that
the pressurizing work creates a high temperature and thus a
corresponding high pressure in the pressure gas container, whereby
the available pressure difference for filling is reduced to such an
extent that the fueling operation takes a long time and is
therefore terminated before the pressure gas container holds the
volume of gas possible according to technical specifications.
[0004] DE 197 05 601 A1 describes a natural gas fueling method
without cooling of the gas, wherein the fueling of the pressure gas
container is continued until the pressure in the conduit to the
pressure gas container exceeds a maximum pressure. Another
possibility provides that the fueling operation is terminated as
soon as the mass flow falls below a limit value.
[0005] WO 97/06385 A1 describes a gas charging system for
high-pressure gas bottles. Here, the gas is cooled by flushing the
high-pressure gas bottle to be filled, whereby two connections for
the feed and the return flow are needed. In the flushing circuit,
the gas is cooled via a heat exchanger or by mixing it with gas in
a reservoir.
[0006] EP 0 653 585 A1 describes a system for fueling a pressure
gas container. Here, a test pulse is performed, which is evaluated
with reference to the thermal equation of state for the real gas.
Further, a switching to reservoirs at higher pressures (multiple
unit method) during the fueling is described. The fueling operation
is performed intermittently. No cooling device is provided for the
gas.
[0007] DE 102 18 678 A1 describes a method and a device, wherein
the gas for filling the pressure gas container is fed from a
high-pressure reservoir through a vortex tube acting as a cooling
device. The vortex tube takes advantage of the differential
pressure prevailing in the fueling system to separate the gas flow
into a hot gas flow and a cold gas flow. The latter is then
supplied to the pressure gas container. The functionality of this
method is based on the fact that the gas is fed to a swirl
generator at a supercritical pressure ratio, the generator being
arranged axially between two pipes having different inlet
diameters. A decrease in temperature through the use of a vortex
tube can be achieved if, and only if, supercritical pressure ratios
exist. At a critical pressure ratio for natural gas of .pi.*=0.5427
and a pressure in the reservoir of p.sub.v=250 bar, which is
generally not reached, when a plurality of vehicles are refueled in
shirt succession, a subcritical condition is obtained when the
pressure in the pressure gas container has risen to p.sub.o=135
bar. This means that, when filling a pressure gas container with
natural gas in a pressure range from p.sub.o=135 bar to p.sub.o=200
bar, the use of a vortex tube will result in no further decrease in
the gas temperature under the preconditions defined by the
technical specifications.
[0008] A direct fueling is feasible where setting up publicly
accessible natural gas fueling stations is not economic.
Vehicles--and not only those of individual transport--could be
refueled where they are during their standstill times. This may be
in industrial parks, garages or car boards. Many households or
buildings have natural gas available for heating. A compressor
(natural gas compressor) could compress this natural gas at night
from the regular natural gas network level of 50 mbar to 200 bar at
a reference temperature of 15.degree. C. A vehicle could be fueled
therewith.
[0009] Another possible field of application for such a fueling
system is seen in agriculture, where large volumes of biological
gas are produced. Instead of feeding this biological gas into a
public gas network, it could be compressed in situ and be used to
operate agricultural vehicles and machines. In the future, this
would allow to replace biodiesel in agriculture.
[0010] One requirement to be fulfilled by this compressor is that
the compressor has to be configured such that a complete filling
with fuel has to be possible within one night (about 8 hours) at
200 bar and a reference temperature of 15.degree. C. The major
problems of a multistage high-pressure compressor are the
intermediate cooling and the cooling of the gas at the compressor
outlet, which, when entering the pressure gas container, must not
exceed 60.degree. C. at any time during fueling.
[0011] It is an object of the invention to provide a device for
generating highly compressed gas, wherein the compressed gas, which
heats up during compression, is cooled in a cooling device which is
of simple structure, provides a high cooling performance and is
adapted to be realized with small dimensions.
[0012] The device of the present invention is defined in claim 1.
According to the invention, the cooling device arranged downstream
of the compressor stage is designed as a vortex tube.
[0013] Vortex tubes are particularly well suited for ultra-short
time decreases in temperature. In contrast to conventional gas
coolers, these decreases in temperature can be achieved over very
short path lengths. Moreover, the invention is based on the insight
that the pressure ratio in the compressor stages of the
high-pressure compressor is larger than 3. Thereby, it is
guaranteed that the vortex tubes in all compressor stages will be
in the supercritical range, which is essential for a trouble-free
operation of the vortex tubes.
[0014] A particular embodiment of the invention provides to
maintain, in direct fueling, the reference temperature of
15.degree. C. at a pressure of 200 bar in the pressure gas
container to be filled even if the decrease of the gas temperature
in the vortex tubes is longer sufficient for this purpose under
unfavorable peripheral and environmental conditions. Suitably,
after the last compressor stage with an adjoining throttle point,
the gas is not introduced into the pressure gas container to be
filled, but is returned to the compressor inlet after an adiabatic
throttling (Joule-Thomson effect). In the closed gas circuit, the
gas temperature decreases continuously under isotropic compression
and adiabatic throttling (production of cold by adiabatic
throttling, caused by the Joule-Thomson effect in real gases).
According to the invention, the gas circuit will remain closed
until the decrease in temperature required by the technical
specifications for the filling of the pressure gas container is
reached.
[0015] A particularly suitable embodiment of the invention provides
for using the heat produced in the vortex tubes to heat water for
domestic use or to use it for heating a building.
[0016] Suitably, the output pressure of a multistage compressor is
set so high that this pressure is above the critical pressure of
the pressure gas container to be filled. In contrast to the filling
of a pressure gas container by an overflow from a reservoir in
which the gas pressure is limited to 250 bar according to the
technical specifications for natural gas, these regulations do not
apply to direct fueling using a high-pressure compressor, provided
that the legal provisions for the pressure gas container are
observed.
[0017] In a preferred embodiment of the invention, throttling via
an expansion unit takes the gas flow leaving the final stage of the
high-pressure compressor to the pressure allowed in the pressure
container. The mechanical work arising at the expansion unit is
used to drive a compressor for pre-compressing the gas taken from
the gas network.
[0018] Using the pre-compression, the output pressure at the
compressor can be varied via the input pressure at the
high-pressure compressor. By throttling a defined output pressure,
the ambient conditions during the fueling can be taken into account
and the gas temperature in the pressure gas container can be
influenced indirectly.
[0019] The invention further refers to a device for decreasing the
temperature of a gas from a reservoir containing pressurized gas,
comprising a feed pipe leading to a swirl generator, a filling pipe
leading to the pressure gas container, and a vortex tube branching
from the swirl generator for conducting a rotating vortex flow.
[0020] At higher temperatures, the volume of a gas is larger. Thus,
for reasons of space, it is often necessary to cool the gas since
then a larger gas mass can be stored in a determined volume. A
typical application for gas cooling are gas fueling operations.
[0021] For a fast fueling of a gas-fueled vehicle, a fueling
installation is required that is adapted to perform a fast
decantation of high-pressure gas from a reservoir to a pressure gas
container. Such gases to be decanted may comprise natural gas or
methane or similar gases, as well as gases such as nitrogen,
oxygen, argon, air or hydrogen.
[0022] In gas fueling operations it is intended to fill such a mass
of gas into the pressure gas container, independent of the ambient
temperature, that a limit value of pressure defined by the
technical specifications is possibly reached in the pressure gas
container at a predetermined reference temperature. For example,
technical specifications provide that a pressure of 200 bar at a
reference temperature of 15.degree. C. must not be exceeded in a
pressure gas container. For a fast fueling operation by overflow,
the reservoir must be under high pressure for the required mass of
gas to be transferred into the pressure gas container.
[0023] In gas fueling installations, the pressurizing work to be
performed causes a heating o the gas in the pressure gas container.
The Joule-Thomson effect (change in temperature of the gas by
throttling) of the real gas generally counteracts this heating.
However, it is only under very favorable conditions, i.e. at
sufficiently low temperatures, that the Joule-Thomson effect and
the heat dissipation to the environment will suffice to compensate
the heat caused by the pressurizing work of the gas. If these
favorable conditions do not exist, a fast decanting in gas fueling
installations without cooling device will result in a short-filling
of the pressure gas container. This is due to the fact that a high
temperature and a corresponding high pressure are caused in the
pressure gas container by the pressurizing work, whereby the
pressure difference available for fueling is lowered to such a
degree that the fueling operation takes a long time and is
therefore terminated before the pressure gas container holds the
mass of gas possible according to the technical specifications.
[0024] It is another object of the invention to provide a device
for lowering the temperature of a gas, which can be manufactured
with small dimensions, is of a simple structure and has a short
response time with a great cooling effect.
[0025] The present device for lowering temperature has the features
of claim 17. The device is characterized in that the outside of the
vortex tube is exposed to a cooling device, that a swirl brake for
slowing the vortex flow is arranged in the vortex tube, and that a
flow path leads from the swirl brake to the discharge pipe.
[0026] In the present device for lowering temperature, the entire
gas flow is made substantially free of swirls after the temperature
of the vortex flow has been lowered, and the gas flow is fed to the
pressure gas container. No throttling means for controlling a hot
gas flow is required. Compared to the known methods for filling
pressure gas containers by overflow, it is an essential advantage
that the pressure of the gas flow is lowered only to the
instantaneous pressure in the pressure gas container, which is
energetically advantageous.
[0027] In the present device, the gas is supplied tangentially to a
swirl generator at a supercritical pressure ratio, i.e. at a speed
just below the speed of sound. The swirl generator introduces a
rotating vortex flow into the vortex tube. The vortex flow expands
in the vortex tube at a high axial speed, whereby the tube wall is
heated up strongly. The heavily turbulent mixing causes an
adiabatic layering, and, due to the high centrifugal pressure, the
outer portion of the vortex flow has a higher static temperature
than the inner portion. The vortex flow is cooled by the cooling
device acting on the vortex tube from outside, and is then slowed
down by a swirl brake. The flow is then fed over a flow path to the
filling tube leading to the pressure gas container. In this manner,
the entire gas taken from the reservoir reaches the pressure gas
container.
[0028] According to a preferred embodiment of the invention, it is
provided that the flow path extends centrally through the vortex
within the vortex flow. While the vortex flow rotates, a centric
return flow forms along its axis. While the outer vortex flow
continues to heat up, the linear inner return flow is much
colder.
[0029] In an advantageous embodiment of the invention provides that
the filling pipe also branches from the swirl generator and that
the diameter of the filling pipe is smaller than the diameter of
the vortex tube. In the process, the swirl-free linear return flow
again reaches the swirl generator from where it gets into the
filling pipe.
[0030] Preferably, the swirl brake is a closure arranged in the
vortex tube. The same slows down the vortex flow near the wall
because of the absence of centrifugal forces so that a radial
inward flow is obtained. For reasons of continuity, a centric
return flow in the form of a core flow is thus produced in the
axial direction, flowing in a direction opposite to the rotating
vortex flow. The lower speed of the return flow, as compared to the
vortex flow, has effect in a further reduction of the static
temperature of the inner flow with respect to the surrounding
vortex flow, whereby the temperature difference between these two
flows is still increased.
[0031] The invention starts from the insight that it is
advantageous to dissipate the heat transferred from the rotating
flow to the tube wall, which, as experience has shown, is at a high
temperature level there.
[0032] According to a preferred embodiment of the invention, a
water cooler designed as a coaxial pipe is used to cool the tube
wall of the vortex tube in a counter current process. Thus, it is
achieved, overall, that by cooling the tube wall, which is the more
effective, the greater the temperature difference between the
object to be cooled and the cooling medium is, an additional
reduction in temperature of the inner flow in the tube is effected
through a reduction in temperature of the outer flow of the
tube.
[0033] A particularly advantageous embodiment of the invention
provides that the closure forming the swirl brake is a piston
adapted to adjusted axially in the vortex tube. Thereby, the
effective length of the vortex flow is variable so as to optimize
the filling operation in dependence on the pressure and the
temperature of the gas in the reservoir. The effective length of
the vortex tube, i.e. the length of the effective vortex tube
section, can be changed by adjusting the piston, e.g. by means of a
threaded bar.
[0034] The following is a detailed exemplary description of the
invention with reference to a four-stage high-pressure compressor
and to the accompanying drawings.
[0035] In the figures:
[0036] FIG. 1 is a schematic general view of the gas fueling system
comprising a high-pressure compressor using a vortex tube according
to Ranque-Hilsch for lowering the temperature of the gas after
compression, wherein a separation into cold gas and hot gas is
effected in the vortex tube,
[0037] FIG. 2 shows the same gas fueling system as FIG. 1, however,
using the pressure energy with its work capacity in an adiabatic
throttling process after the last compressor stage in an expansion
unit,
[0038] FIG. 3 illustrates the same gas fueling systems as FIG. 2,
however, using the heat in the hot gas for heating domestic and/or
heating water via a heat exchanger,
[0039] FIG. 4 shows the same gas fueling system as FIG. 3, however,
using a vortex tube without gas separation, wherein the vortex tube
is cooled from outside and the heat in the cooling water is
available for heating domestic and/or heating water,
[0040] FIG. 5 is a longitudinal section through a device for
lowering the temperature of gases, and
[0041] FIG. 6 is a perspective view of the device of FIG. 5 to
illustrate the feeding and the distribution of the gas flow and the
water cooling.
[0042] The gas fueling system illustrated in FIG. 1 has a take-off
pipe 1 leading to the series-connected compressor stages 10a, 10b,
10c and 10d. A check valve 11a, 11b, 11c, 11d is arranged in the
pipeline 1 upstream of each compressor stage. An inlet pipe 12a,
12b, 12c, 12d leads from the check valve to the following
compressor stage. The outlet of the compressor stage is connected
to the inlet of a vortex tube 20a, 20b, 20c, 20d via a take-off
pipe 13a, 13b, 13c, 13d. The vortex tubes are generally structured
as described in DE 102 18 678 A1 so that a detailed explanation of
the structure of the vortex tubes can be omitted. The vortex tubes
20a, 20b, 20c, 20d serve to decrease the gas temperature after a
previous compression.
[0043] The vortex tubes 20a, 20b, 20c, 20d operating according to
the counter-current method are connected to the compressor stages
10a, 10b. 10c, 10d via the take-off pipes 13a, 13b, 13c, 13d.
Through the take-off pipes 13a, 13b, 13c, 13d, the gas flow reaches
the inflow nozzles forming the narrowest flown-through cross
section 21a, 21b, 21c, 21d between two compressor stages. As a
vortex flow at the speed of sound, the gas flows from the inflow
nozzles into the central tube of the vortex tube where a separation
into a cold gas flow and a hot gas flow is effected. At one end of
the central tube, the cold core of the forming swirl is collected
and fed to the subsequent compressor stage via the inlet pipes 12b,
12c, 12d. At the opposite end of the central tube, the hot gas flow
23a, 23b, 23c, 23d is collected and discharged via the pipelines
24a, 24b, 24c, 24d. The throttle points 25a, 25b, 25c, 25d provided
in the pipelines 24a, 24b, 24c, 24d serve to preset the mass ratio
between the cold gas and the hot gas portions. Downstream of the
throttle points 25a, 25b, 25c, 25d, the hot gas flow flows through
the return flow pipes 26a, 26b, 26c, 26d into the same compressor
stage from which the gas was taken. The check valves 27a, 27b, 27c,
27d in the return flow pipes 26a, 26b, 26c, 26d and the check
valves 11a, 11b, 11c, 11d in the inlet pipes 12a, 12b, 12c, 12d
allow the gas to flow from the return flow pipes 26a, 26b, 26c, 26d
into the inlet pipes 12a, 12b, 12c, 12d.
[0044] From the gas supplied, each vortex tube produces a hot gas
flow 23a, 23b, 23c, 23d and a cold gas flow 22a, 22b, 22c, 22d. The
hot gas flow 23a, 23b, 23c, 23d is returned to the respective
compressor stage 10a, 10b, 10c, 10d.
[0045] On the other hand, the cold gas flow 22a, 22b, 22c, 22d is
fed to the subsequent compressor stage. The check valves 11a, 11b,
11c, 11d prevent returned gas from entering the cold gas outlet of
the previous vortex tube. The check valves 27a, 27b, 27c, 27d help
to avoid that the cold gas of the previous vortex tube gets into
the return pipe of the hot gas of the subsequent vortex tube.
[0046] From the vortex tube 20d of the last compressor stage 10d,
the cold gas flow 22d reaches the pressure pipe 4. If the gas
temperature there, measured by a temperature measuring means 100,
is above a predetermined reference value, the three-way stopcocks
101, 102 are operated as triggered by a measurement signal.
Normally, these are set such that the gas flow leads from the
take-off pipe 1 to the series-connected compressor stages 10a, 10b,
10c, 10d and the cold gas flow 22d is fed into the pressure gas
container 7 through the pressure line 6. If the cold gas
temperature exceeds a predefined limit value at the measuring point
100, the cold gas flow 22d is redirected via the return manifold
104 using the three-way stopcock 101. Before the cold gas flow is
again fed to the first compressor stage 10a through the return
manifold 104 via the three-way stopcock 102 and the inlet pipe 12a,
the cold gas flow is subjected to a further reduction in
temperature at the throttle point 103. The three-way valve 102 is
operated simultaneously with the three-way valve 101 so that no gas
is supplied through the take-off line 1 and a closed circuit is
established after the three-way stopcocks 101, 102 have been
operated. In this closed system, an adiabatic throttling
(Joule-Thomson effect) reduces the temperature in the hot gas flow
23a, 23b, 23c, 23d at the throttle points 25a, 25b, 25c, 25d and in
the cold gas flow 22d at the throttle point 103. Due to the
Joule-Thomson effect, the decrease in temperature obtained by
throttling is larger with a real gas like natural gas than the
increase in temperature in the gas caused by the compression in the
previous compressor stages 10a, 10b, 10c, 10d. Thus, in a closed
gas circuit, the gas temperature can be lowered by compression and
adiabatic throttling. As soon as the temperature measuring means
detects that the temperature in the cold gas flow 22d corresponds
to a predefined reference temperature, a measurement signal is
triggered operating the three-way stopcocks 101, 102 so that the
take-off pipe 1 is again in communication with the compressor
stages 10a, 10b, 10c, 10d and the cold gas flow 22d is introduced
into the pressure gas container 7 via the pressure pipe 6.
[0047] Other than the system in FIG. 1, the gas fueling system
illustrated in FIG. 2 has a pre-compressor 2 connected to the
take-off pipe 1. A pipeline 3 leads from the pre-compressor 2 to
the series-connected compressor stages 10a, 10b, 10c, 10d. A check
valve 11a, 11b, 11c is provided in the pipeline 3, upstream of each
compressor stage. The last compressor stage 10d is not provided
with a check valve. An inlet pipe 12a, 12b, 12c leads from the
check valve to the subsequent compressor stage. The outlet of the
compressor stage is connected to the inlet of a vortex tube 20a,
20b, 20c via a take-off pipe 13a, 13b, 13c.
[0048] From the last compressor stage 10d, a pressure pipe 4 leads
to an expansion unit 5. In the expansion unit, the gas flow is
subjected to a reduction in temperature after the last compressor
stage 10d, before the gas is introduced into the pressure gas
container 7. Normally, the three-way stopcock 101 is set such that
the pressure pipe 6a, 6b is connected through. At the same time,
mechanical work is taken from the gas flow in the expansion unit 5
that is used to drive the pre-compressor 2. The expansion unit 5
drives the pre-compressor 2.
[0049] The gas compressed in the pre-compressor 2 is fed to the
first compressor stage 10a through the pipeline 3 via the inlet
pipe 12a provided with the check valve 11a. The vortex tubes 20a,
20b, 20c operating according to the counter-current process are
connected to the compressor stages 10a, 10b, 10c via the take-off
pipes 13a, 13b, 13c. Through the take-off pipes 13a, 13b, 13c, the
gas flow reaches the inflow nozzles that form the narrowest cross
section 21a, 21b, 21c between the compressor stages 20, 20b, 20c.
The cold gas flow 22a, 22b, 22c of the vortex tubes 20a, 20b, 20c
is fed to the following compressor stage via the inlet pipes 12b,
12c, 12d, and the hot gas flow 23a, 23b, 23c is discharged via the
pipelines 24a, 24b, 24c. The throttle points 25a, 25b, 25c provided
in the pipelines 24a, 24b, 24c serve to preset the mass ratio
between the cold gas and the hot gas portions. Downstream of the
throttle points 25a, 25b, 25c, the hot gas flow 23a, 23b, 23c
returns, via the return pipes 26a, 26b, 26c, into the same
compressor stage from which the gas was taken. The check valves
27a, 27b, 27c in the return pipes 26a, 26b, 26c and the return
valves 11a, 11b, 11c in the inlet pipes 12a, 12b, 12c allow the gas
to flow from the return pipes 26a, 26b, 26c to the inlet pipes 12a,
12b, 12c.
[0050] From the gas supplied, each vortex tube produces a hot gas
flow 23a, 23b, 23c and a cold gas flow 22a, 22b, 22c. The hot gas
flow 23a, 23b, 23c is returned to the respective compressor stage
10a, 10b, 10c. On the other hand, the cold gas flow 22a, 22b, 22c
is fed to the subsequent compressor stage. The check valves 11a,
lb, llc prevent returned gas from entering the cold gas outlet of
the previous vortex tube. The check valves 27a, 27b, 27c help to
avoid that the cold gas of the previous vortex tube gets into the
return pipe of the hot gas of the subsequent vortex tube.
[0051] As is further obvious from FIG. 2, the closed gas circuit
can be designed as described with respect to FIG. 1, so as to start
a decrease in the gas temperature when the gas temperature exceeds
a predetermined reference temperature at the temperature
measurement point 100.
[0052] The embodiment of FIG. 3 differs from that of FIG. 2 in that
the hot gas flow 23a, 23b, 23c of the vortex tubes is fed via a
respective return pipe 26b, 26c, 26d that leads back to the inlet
pipe 12a, 12b, 12c of the compressor stage 10a, 10b, 10c. The
return pipes 26a, 26b, 26c each include a gas cooler 30a, 30b, 30c
to draw heat from the gas. Downstream of each gas cooler, a
throttle point 25a, 25b, 25c is mounted in the return pipe.
[0053] The gas coolers 30a, 30b, 30c are water-cooled heat
exchangers. By forced circulation, a circulation pump 8 driven by
the expansion unit 5 feeds the water through a pipe 31 to the gas
coolers 30a, 30b, 30c that are connected in parallel to
corresponding feed pipes 31a, 31b, 31c. From the gas coolers, the
cooling medium flows in return pipes 32a, 32b, 32c that combine to
a return manifold 32. The return manifold 32 leads to a heat
exchanger 33. Here, the cooling medium that acts as a heat carrier
transfers the heat received in the gas coolers to a second heat
transfer medium that is supplied from a feed 34-1 of the secondary
circuit and exits from the heat exchanger through a drain 34-2. The
heat transfer medium conveyed in the secondary circuit may be
domestic water and/or heating water for a building heating. Having
left the heat exchanger 33, the heat transfer medium conveyed in
the primary circuit returns to the intake side of the circulation
pump 8 via a pipe 35.
[0054] In the gas fueling system of FIG. 4, a vortex tube is
employed that operates without gas separation. The gas taken from
the take-off pipe 1 is brought to a higher pressure level in a
pre-compressor 2 driven by the expansion unit 5. Via the pipe 3,
the pre-compressed gas is fed to the inlet pipe 12a of the first
compressor stage 10a of the high-pressure compressor. After
compression in the first compressor stage 10a, the gas reaches the
vortex tube 40a via the take-off line 13a for a reduction in the
temperature of the gas. The same is valid for the following
compressor stages 10b, 10c with the take-off pipes 13b, 13c and the
vortex tubes 40b, 40c.
[0055] The vortex tubes 40a, 40b, 40c are connected to the
compressor stages 10a, 10b, 10c through the take-off pipes 13a,
13b, 13c. Through the take-off pipes 13a, 13b, 13c, the gas flow
reaches the inflow nozzles that form the narrowest flown-through
cross section 41a, 41b, 41c between two compressor stages. As a
vortex flow at the speed of sound, the gas flows from the inflow
nozzles into the central tube of the vortex tubes 40a, 40b, 40c
which are closed at one end 43a, 43b, 43c. At the solid bottom of
the closed-end tube, the flow is slowed down near the wall because
of the absence of centrifugal forces so that at the end, near the
bottom, a radial inward flow is obtained. For reasons of
continuity, a rising flow is produced in the axial direction, which
flows as a core flow in the direction opposite to the rotating flow
and flows out at the opposite ends 42a, 42b, 42c of the closed
tubes into the inlet pipes 12a, 12b, 12c.
[0056] The increase in static temperature on the outside and its
decrease on the inside necessarily cause different temperatures
between the inner flow in the tube and the outer flow in the tube.
All in all, a decrease in temperature of the outer flow in the tube
by cooling the tube wall allows for an additional decrease in the
temperature of the inner flow in the tube. Thus, the vortex tubes
40a, 40b, 40c are equipped with water coolers 44a, 44b, 44c that
surround the central tube of the vortex tubes 40a, 40b, 40c and are
used for cooling the outer wall of the tube according to the
counter-current technique. As is further obvious from FIG. 4, the
primary and the secondary circuit can be designed according to the
cooling circuit described in connection with FIG. 3.
[0057] The gas is supplied to the last compressor stage 10d via the
inlet pipe 12d. In the expansion unit 5, the gas flow is subjected
to further temperature reduction downstream of the compressor stage
10d, before the gas is introduced into the pressure gas container
7. At the same time, mechanical work is taken from the gas flow in
the expansion unit 5, which is used to drive the pre-compressor 2
and the circulation pump 8.
[0058] The device for reducing the temperature illustrated in FIGS.
5 and 6 comprises a feed pipe 101 coming from a reservoir and
leading to a swirl generator 102. The functionally essential parts
thereof are an annular plenum chamber 103, from which tangential
inflow nozzles 104 are directed inward and lead into the end of a
vortex tube 105. Adjoining the end of the vortex tube 105 is an
oppositely directed pipe section 106 that is connected with a
filling pipe 107 leading to the pressure gas container (not
illustrated). The inner diameter of the pipe section 106 is clearly
smaller than that of the vortex tube 105. As a consequence, the
rotating vortex flow 121 produced in the swirl generator 102 flows
into the vortex tube where it moves away from the swirl generator
102 (to the left in FIG. 1). The throttle point with the narrowest
flown-through cross section between the reservoir and the pressure
gas container to be filled is formed by the inflow nozzles 104 of
the swirl generator 102. From the inflow nozzles 104, the gas flows
into the vortex tube 105 as a rotating vortex flow 121 at almost
the speed of sound. For dissipating the heat caused by the vortex
flow 121 from the tube wall of the vortex tube 105, a cooling
device 130 is provided around the vortex tube 105. The same
comprises a cooling jacket 131 coaxially surrounding the vortex
tube, which is provided with a feed pipe 132 and a drain pipe 133
and forms a water cooler according to the counter-current
technique.
[0059] At the end averted from the swirl generator 102, the vortex
tube 105 is provided with a swirl brake 109. The same comprises an
axially adjustable piston 110 that is arranged in the vortex tube,
closing it off sealingly. To adjust the piston 110, a spindle 111
is used that can be turned manually. The vortex flow 121 is slowed
down at the closure 110 so that, for reasons of continuity, an
axially directed return core flow flowing back along a flow path
122 is formed, flowing in a direction opposite to the vortex flow
121. The flow path 122 extends coaxially within the vortex flow
121. The pressure difference between the inner and the outer flow
in the vortex tube 105 has the effect that the core flow flowing
along the inner flow path 122 flows through the pipe section 106
into the filling pipe 107 that is connected with the pressure gas
container to be filled.
[0060] The perspective view in FIG. 6 represents the flow course of
a gas in the device, the gas supply being effected through the feed
pipe 101 in the direction of the arrows 120. From here, the gas,
e.g. natural gas, reaches the vortex tube 105 at a supercritical
pressure ratio and at the speed of sound via the plenum chamber 103
and the inflow nozzles 104 of the swirl generator 102. Caused by
the swirl generated in the swirl generator 102, the rotating flow
121 is formed in the vortex tube. Near the wall, due to the absence
of centrifugal forces, this rotating flow is slowed down so far at
the solid bottom of the vortex tube closed by the closure 110 that
an oppositely directed core flow 122 is formed. The latter is then
fed to the pressure gas container via the pipe section 106.
* * * * *