U.S. patent application number 11/600254 was filed with the patent office on 2007-06-07 for supercritical refrigeration cycle.
This patent application is currently assigned to DENSO Corporation. Invention is credited to Hiroshi Ishikawa, Toshio Tsuboko.
Application Number | 20070125106 11/600254 |
Document ID | / |
Family ID | 38117366 |
Filed Date | 2007-06-07 |
United States Patent
Application |
20070125106 |
Kind Code |
A1 |
Ishikawa; Hiroshi ; et
al. |
June 7, 2007 |
Supercritical refrigeration cycle
Abstract
A supercritical refrigeration cycle comprises a radiator 2 for
cooling the refrigerant discharged from a compressor 1, a cooling
fan 2a for blowing the atmospheric air to the radiator 2, a
decompression unit 4 for decompressing the refrigerant at the
outlet of the radiator 2 and having the opening degree thereof
controlled to achieve a target high pressure, and an evaporator 5
for evaporating the low-pressure refrigerant decompressed by the
decompression unit 4. The high pressure exceeds the critical
pressure of the refrigerant. A value of information representing
the difference between the actual radiation state of the
refrigerant at the outlet of the radiator 2 and the ideal radiation
state determined by the atmospheric temperature is calculated, and
based on this value of information, the air capacity of the cooling
fan 2a is controlled to decrease the difference. Thus, the cooling
fan of the high-pressure radiator can be properly controlled in the
supercritical refrigeration cycle.
Inventors: |
Ishikawa; Hiroshi;
(Kariya-city, JP) ; Tsuboko; Toshio; (Anjo-city,
JP) |
Correspondence
Address: |
HARNESS, DICKEY & PIERCE, P.L.C.
P.O. BOX 828
BLOOMFIELD HILLS
MI
48303
US
|
Assignee: |
DENSO Corporation
Kariya-city
JP
|
Family ID: |
38117366 |
Appl. No.: |
11/600254 |
Filed: |
November 15, 2006 |
Current U.S.
Class: |
62/183 ;
62/186 |
Current CPC
Class: |
F25B 2700/19 20130101;
F25B 2600/11 20130101; B60H 2001/3277 20130101; F25B 2700/2106
20130101; F25B 2600/111 20130101; F25B 9/008 20130101; F25B
2700/2102 20130101; F25B 2600/17 20130101; B60H 2001/3266 20130101;
B60H 2001/3291 20130101; F25B 2700/21173 20130101; B60H 2001/326
20130101; F25B 40/00 20130101; B60H 1/3217 20130101; B60H 2001/325
20130101; F25B 2309/061 20130101; F25B 2500/19 20130101 |
Class at
Publication: |
062/183 ;
062/186 |
International
Class: |
F25B 39/04 20060101
F25B039/04; F25D 17/04 20060101 F25D017/04 |
Foreign Application Data
Date |
Code |
Application Number |
Nov 16, 2005 |
JP |
2005-331596 |
Claims
1. A supercritical refrigeration cycle where the high pressure
exceeds the critical pressure of the refrigerant, comprising: a
compressor for sucking in and compressing a refrigerant; a radiator
for cooling the refrigerant discharged from the compressor by
exchanging heat between the refrigerant discharged from the
compressor and the atmospheric air; a cooling fan for blowing the
atmospheric air to the radiator; a decompressor for decompressing
the refrigerant at the outlet of the radiator and having the
opening degree thereof controlled to achieve a target high
pressure; and an evaporator for evaporating the low-pressure
refrigerant decompressed by the decompressor and leading the
evaporated gas refrigerant to the inlet of the compressor; wherein
an value of information representing the difference between the
actual radiation state of the refrigerant at the outlet of the
radiator and the ideal radiation state determined by the
atmospheric temperature is calculated, and wherein the air capacity
of the cooling fan is controlled in such a manner as to decrease
the difference based on the value of information.
2. A supercritical refrigeration cycle according to claim 1,
wherein the value of information is specifically the difference
between the refrigerant temperature at the outlet of the radiator
and the atmospheric temperature.
3. A supercritical refrigeration cycle according to claim 2,
wherein, as long as the temperature difference is not less than a
predetermined value, the air capacity of the cooling fan is
controlled upward while, in the case where the temperature
difference is less than the predetermined value, the air capacity
of the cooling fan is controlled downward.
4. A supercritical refrigeration cycle according to claim 1,
wherein the value of information is the pressure difference between
the actual high pressure and the high-pressure setting determined
by the atmospheric temperature.
5. A supercritical refrigeration cycle according to claim 4,
wherein in the case where the pressure difference is not less than
a predetermined value, the air capacity of the cooling fan is
controlled upward, while in the case where the pressure difference
is less than the predetermined value, the air capacity of the
cooling fan is controlled downward.
6. A supercritical refrigeration cycle mounted on an automotive
vehicle according to claim 1, wherein a radiator is arranged at a
position exposed to the dynamic pressure of the running vehicle,
and the air capacity of the passing atmospheric air is changed with
the vehicle speed, and wherein a cooling fan is electrically
driven, and the air capacity of the cooling fan is controlled by
the voltage across the drive motor of the cooling fan.
7. A supercritical refrigeration cycle according to claim 1 wherein
it is determined whether the high pressure is not lower than the
critical pressure of the refrigerant or not, wherein in the case
where the high pressure is not lower than the critical pressure of
the refrigerant, the air capacity of the cooling fan is controlled
based on the value of information, and wherein in the case where
the high pressure is lower than the critical pressure of the
refrigerant, the air capacity of the cooling fan is controlled
directly based on the change in the high pressure.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] This invention relates to the operation of controlling the
cooling fan of a high-pressure radiator in a supercritical
refrigeration cycle that uses CO.sub.2 (carbon dioxide), of which
the high pressure increases beyond the critical pressure
(supercritical state), as a refrigerant.
[0003] 2. Description of the Related Art
[0004] In the supercritical refrigeration cycle using CO.sub.2 as
the refrigerant, as indicated by thick solid line in FIG. 2, the
pressure at the outlet of the high-pressure radiator assuming the
maximum value of the coefficient of performance (COP) is known to
change with the refrigerant temperature at the outlet of the
high-pressure radiator.
[0005] In view of this, it is known that the refrigerant
temperature at the outlet of the high-pressure radiator is detected
and, based on this refrigerant temperature at the outlet of the
high-pressure radiator, the pressure at the outlet of the
high-pressure radiator associated with the maximum COP is set as a
target pressure Po, and the opening degree of an expansion valve is
controlled so that the actual pressure at the outlet of the
high-pressure radiator reach the target pressure Po thereby to
improve the operating efficiency of the supercritical refrigeration
cycle (Japanese Unexamined Patent Publication Nos. 11-125471 and
9-264622).
[0006] As described above, in the supercritical refrigeration
cycle, the high pressure is automatically controlled to improve
COP. Therefore, the high pressure is not an value of information
representing the cooling load unlike the normal refrigeration cycle
(hereinafter referred to as the subcritical refrigeration cycle)
using an HFC-134a or similar refrigerant of which the high pressure
does not exceed the critical pressure.
[0007] In the case where the operation of controlling the cooling
fan of the high-pressure radiator in the subcritical refrigeration
cycle, i.e. the operation of controlling the air capacity of the
cooling fan, corresponding to the high pressure, is used as it is
for the supercritical refrigeration cycle, therefore, the air
capacity of the cooling fan would be inconveniently controlled
upward more than necessary in spite of the fact that the radiation
performance of the high-pressure radiator is sufficiently secured,
thereby undesirably wasting the power consumed by the cooling
fan.
SUMMARY OF THE INVENTION
[0008] In view of this situation, the object of this invention is
to properly control the cooling fan of the high-pressure radiator
in the supercritical refrigeration cycle.
[0009] In order to achieve this object, according to a first aspect
of the invention, there is provided a supercritical refrigeration
cycle comprising a radiator (2) for cooling the refrigerant
discharged from a compressor (1), a cooling fan (2a) for blowing
the atmospheric air to the radiator (2), a decompressor (4) for
decompressing the refrigerant at the outlet of the radiator (2) and
having the opening degree thereof controlled to achieve a target
high pressure and an evaporator (5) for evaporating the
low-pressure refrigerant decompressed by the decompressor (4), the
high pressure exceeding the critical pressure of the
refrigerant,
[0010] wherein an value of information representing the difference
between the actual radiation state of the refrigerant at the outlet
of the radiator (2) and the ideal radiation state determined by the
atmospheric temperature is calculated, and
[0011] wherein the air capacity of the cooling fan (2a) is
controlled to reduce the difference based on the value of
information.
[0012] In this aspect of the invention, the air capacity of the
cooling fan (2a) can be controlled to reduce the difference between
the actual radiation state of the refrigerant at the outlet of the
radiator in the supercritical refrigeration cycle and the ideal
radiation state determined by the atmospheric temperature, and
therefore, the air capacity of the cooling fan (2a) can be properly
controlled in accordance with the actual operation of the
supercritical refrigeration cycle.
[0013] As a result, the power consumption of the compressor (1) and
the cooling fan (2a) is reduced.
[0014] In view of the fact that the velocity and the capacity of
the air passing through the radiator (2) are proportional to each
other, the operation to control the air capacity according to the
invention includes the operation to control the air velocity.
[0015] According to a second aspect of the invention, there is
provided a supercritical refrigeration cycle, wherein the value of
information is specifically the difference (.DELTA.T) between the
refrigerant temperature at the outlet of the radiator (2) and the
atmospheric temperature.
[0016] According to a third aspect of the invention, there is
provided a supercritical refrigeration cycle wherein, as long as
the temperature difference (.DELTA.T) is not less than a
predetermined value, the air capacity of the cooling fan (2a) is
controlled upward while, in the case where the temperature
difference (.DELTA.T) is less than the predetermined value, the air
capacity of the cooling fan (2a) is controlled downward.
[0017] In this aspect of the invention, as long as the temperature
difference (.DELTA.T) is not less than the predetermined value, the
air capacity of the cooling fan (2a) is increased so that the
actual radiation state of the refrigerant at the outlet of the
radiator (2) is made to approach the ideal radiation state, thereby
reducing the high pressure of the cycle to reduce the power
consumption of the compressor (1).
[0018] In the case where the temperature difference (.DELTA.T) is
less than the predetermined value, on the other hand, the actual
radiation state of the refrigerant at the outlet of the radiator
(2) is regarded to have substantially reached the ideal state, and
the air capacity of the cooing fan (2a) is reduced, so that the
power consumption of the cooling fan (2a) is reduced.
[0019] Also, in this aspect of the invention, only a temperature
sensor is used as a detection means for controlling the air
capacity of the cooling fan and, therefore, as compared with the
pressure sensor, the air capacity of the cooling fan (2a) can be
properly controlled using an inexpensive sensor having a simple
configuration.
[0020] According to a fourth aspect of the invention, there is
provided a supercritical refrigeration cycle, wherein the value of
information may specifically be a pressure difference (.DELTA.P)
between the actual high pressure and the high-pressure setting
determined by the atmospheric temperature.
[0021] According to a fifth aspect of the invention, there is
provided a supercritical refrigeration cycle, wherein in the case
where the pressure difference (.DELTA.P) is not less than a
predetermined value, the air capacity of the cooling fan (2a) may
be controlled upward, while in the case where the pressure
difference (.DELTA.P) is less than the predetermined value, on the
other hand, the air capacity of the cooling fan (2a) may be
controlled downward.
[0022] According to a sixth aspect of the invention, there is
provided a supercritical refrigeration cycle mounted on the
vehicle, wherein the radiator (2) is arranged at a position exposed
to the dynamic pressure of a running vehicle, and the air capacity
of the passing atmospheric air is changed with the vehicle
velocity, and wherein the cooling fan (2a) is electrically driven
and the air capacity of the cooling fan (2a) is controlled by the
voltage across the drive motor of the cooling fan (2a).
[0023] In this aspect of the invention, the capacity of the air
passing through the radiator (2) is increased due to the dynamic
pressure of the vehicle running at a high speed and the difference
described above is changed downward by the increased air capacity,
thereby making it possible to control the air capacity of the
cooling fan (2a) downward. As a result, the power consumption of
the cooling fan (2a) can be further reduced at a high vehicle
running speed.
[0024] According to a seventh aspect of the invention, there is
specifically provided a supercritical refrigeration cycle, wherein
it is determined whether the high pressure is not lower than the
critical pressure of the refrigerant, and in the case where the
high pressure is not lower than the critical pressure of the
refrigerant, the air capacity of the cooling fan (2a) is controlled
based on the value of information, while in the case where the high
pressure is lower than the critical pressure of the refrigerant, on
the other hand, the air capacity of the cooling fan (2a) is
controlled directly based on the change in high pressure.
[0025] In this aspect of the invention, the air capacity of the
cooling fan (2a) can be controlled in a suitable way in accordance
with the supercritical state or the subcritical state.
[0026] The reference numerals in the parentheses attached to the
name of each means described above and in the appended claims
indicate the correspondence with the specific means described in
the embodiments explained later.
[0027] The present invention may be more fully understood from the
description of preferred embodiments of the invention, as set forth
below, together with the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0028] FIG. 1 is a diagram showing a general configuration of the
whole system according to a first embodiment of the invention.
[0029] FIG. 2 is a graph showing the relation between the
coefficient of performance and the refrigerant pressure at the
outlet of the radiator in the supercritical refrigeration
cycle.
[0030] FIG. 3 is a flowchart showing the operation of controlling
the voltage across the cooling fan of the radiator according to the
first embodiment.
[0031] FIG. 4 is a graph showing the relation between the power
consumption of the compressor and the temperature difference
.DELTA.T in the supercritical refrigeration cycle.
[0032] FIG. 5 is a graph showing the relation between the air
velocity on the front surface of the radiator and the voltage
across the cooling fan of the radiator.
[0033] FIG. 6 is a flowchart showing the operation of controlling
the voltage across the cooling fan of the radiator according to a
second embodiment.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
First Embodiment
[0034] FIG. 1 is a diagram showing a configuration of the
refrigeration cycle for an automotive air conditioning system
according to a first embodiment of the invention. This
refrigeration cycle uses CO.sub.2 as a refrigerant with the high
pressure exceeding the critical pressure (supercritical state).
This refrigeration cycle, therefore, constitutes a supercritical
refrigeration cycle.
[0035] A compressor 1 for sucking in and compressing the
refrigerant is either a fixed displacement refrigerant compressor
or a variable displacement refrigerant compressor rotationally
driven through an electromagnetic clutch 1a by the engine of an
automotive vehicle not shown. The compressor 1 may be configured of
an electrically-operated compressor.
[0036] A high-pressure radiator 2 generally called a gas cooler is
arranged at the outlet of the compressor 1. This radiator 2 cools
the refrigerant by exchanging heat between the discharged
high-temperature high-pressure refrigerant in a supercritical state
discharged from the compressor 1 and the atmospheric air (outdoor
air).
[0037] The atmospheric air is blown into the radiator 2 by an
electrically-operated cooling fan 2a. Also, the radiator 2 is
arranged in the part exposed to the dynamic pressure of the running
vehicle or, specifically, in the foremost part of the vehicle
engine compartment and, therefore, the amount of atmospheric air
passing therethrough changes with the vehicle speed.
[0038] A high-pressure flow path 3a of an internal heat exchanger 3
is arranged at the refrigerant outlet of the radiator 2. An
electric expansion valve 4 making up a decompression means is
arranged at the outlet of the high-pressure flow path 3a. The
electric expansion valve 4 functions as a pressure control valve
with the opening degree thereof controlled electrically so that the
high pressure of the cycle constitutes a target pressure.
[0039] An evaporator 5 is arranged at the outlet of the electric
expansion valve 4. The evaporator 5 is arranged in a case 6 forming
an air path of the indoor air-conditioning unit of the automotive
air conditioning system, and makes up a cooling means for cooling
the air in the case 6. An electrically-operated blower 7 is
arranged upstream of the evaporator 5 in the air flow. The internal
or external air introduced through an internal-external air switch
box, not shown, is blown into the case 6 and passes through the
evaporator 5.
[0040] Incidentally, a heater core, not shown and making up a
heating means for heating the air, is arranged downstream of the
evaporator 5 in the case 6. The air-conditioning air, regulated in
temperature according to the degree to which the heater core is
heated, is blown into the compartments from an outlet, not shown,
at the downstream end of the case 6 in the air flow.
[0041] An accumulator 8 is arranged at the refrigerant outlet of
the evaporator 5. The accumulator 8 is a gas-liquid separation
means for separating the refrigerant at the outlet of the
evaporator 5 into a liquid refrigerant and a gas refrigerant, and
storing the extraneous refrigerant in the cycle. The gas
refrigerant thus separated is introduced toward the inlet of the
compressor 1.
[0042] At the outlet of the accumulator 8, a low-pressure flow path
3b of the internal heat exchanger 3 is arranged. Therefore, the
outlet pipe of the accumulator 8 is connected to the inlet of the
compressor 1 through the low-pressure flow path 3b.
[0043] The internal heat exchanger 3 exchanges heat between the
low-pressure gas refrigerant (refrigerant sucked into the
compressor) flowing out from the accumulator 8 and the
high-pressure refrigerant at the outlet of the radiator 2, and by
reducing the enthalpy of the refrigerant flowing into the
evaporator 5, increases the enthalpy difference (refrigeration
ability) of the refrigerant between the refrigerant inlet and the
outlet of the evaporator 9, while at the same time preventing the
liquid refrigerant from being sucked into the compressor 1.
[0044] Next, an outline of the electric control unit according to
this embodiment is explained. The air-conditioning control unit 10,
configured of a microcomputer and peripheral circuits, executes a
predetermined arithmetic process in accordance with a predetermined
program and controls the operation of the air-conditioning
devices.
[0045] Specifically, the output of the air-conditioning control
unit 10 is connected with the air-conditioning devices including
the electromagnetic clutch 1a of the compressor 1, the cooling fan
2a of the radiator 2, the electric expansion valve 4 and the
electrically-operated blower 7. The air-conditioning control unit
10 controls the operation of these air-conditioning devices.
[0046] The input of the air-conditioning control unit 10, on the
other hand, is connected with a sensor 11 for detecting the
refrigerant discharged from the compressor 1, a high-pressure
sensor 12, a sensor 13 for detecting the temperature of the
refrigerant at the outlet of the radiator 2, a sensor 14 for
detecting the air blown out from the evaporator 5 and an
atmospheric air temperature sensor 15.
[0047] The high-pressure sensor 12, as shown in FIG. 1, is arranged
at the outlet of the radiator 2 to detect, for example, the
refrigerant pressure at the outlet of the radiator 2. In view of
the fact that the pressure loss of the radiator 2 can be estimated
in the air-conditioning control unit 10, however, the high-pressure
sensor 12 may alternatively be arranged at the inlet of the
radiator 2 (outlet of the compressor 1) to detect the refrigerant
pressure at the outlet of the compressor 1.
[0048] The air-conditioning control unit 10, as is well known, is
supplied also with detection signals from the various sensors 16
including an internal temperature sensor, a sunlight sensor and an
engine water temperature sensor. Further, the air-conditioning
control unit 10 is supplied with various air-conditioning operation
signals from the air-conditioning operation panel 17 arranged in
the neighborhood of the instrument panel in the compartments.
[0049] Specifically, the air-conditioning operation signals,
including the temperature setting signal for setting the internal
temperature of the compartments, the operation command signal for
the compressor 1, the air capacity switch signal for the
electrically-operated blower 7, the blowout mode switch signal for
the indoor air-conditioning unit and the internal-external air
introduction mode switch signal for the internal-external air
switch box are input into the air-conditioning control unit 10 from
the operation members of the air-conditioning operation panel
17.
[0050] Next, the operation of an embodiment having the
above-mentioned configuration is explained. First, the basic
operation of the refrigeration cycle will be explained. Upon
generation of the operation command signal to the compressor 1 by
the operation member of the air-conditioning operation panel 17,
the electromagnetic clutch 1a is energized into a connection state
by the air-conditioning control unit 10. As a result, the drive
force of the vehicle engine is transmitted to the compressor 1
through the electromagnetic clutch 1a and drives the compressor
1.
[0051] The refrigerant, compressed by the compressor 1, is
increased in both temperature and pressure, with the pressure
thereof increasing beyond the critical pressure into a
supercritical state. The refrigerant in the supercritical state
flows into the radiator 2, and after exchanging heat with the
atmospheric air blown by the cooling fan 2a, releases heat into the
atmosphere.
[0052] The refrigerant at the outlet of the radiator 2 passes
through the high-pressure flow path 3a of the internal heat
exchanger 3 and flows toward the expansion valve 4. The refrigerant
at the outlet of the radiator 2, while passing through the
high-pressure flow path 3a of the internal heat exchanger 3,
exchanges heat with the low-temperature low-pressure refrigerant in
the low-pressure flow path 3b and releases heat into the
low-pressure refrigerant.
[0053] The refrigerant, after passing through the high-pressure
flow path 3a of the internal heat exchanger 3, is decompressed in
the reduction path of the expansion valve 4 into a liquid-gas
double-phase low in temperature and pressure. This low-temperature
low-pressure liquid-gas double-phase refrigerant flows into the
evaporator 5, and is evaporated by absorbing heat from the air
blown by the electrically-operated blower 7. As a result, the air
blown by the electrically-operated blower 7 can be cooled by the
evaporator 5 and the cool air can be blown into the
compartment.
[0054] The low-pressure refrigerant, having passed through the
evaporator 5 and flowed into the accumulator 8, is separated into a
saturated liquid refrigerant and a saturated gas refrigerant in the
accumulator 8. The saturated gas refrigerant flows out from the
outlet of the accumulator 8 and is introduced toward the inlet of
the compressor 1.
[0055] The low-pressure gas refrigerant (refrigerant sucked into
the compressor) at the outlet of the accumulator 8 absorbs heat
from the refrigerant at the outlet of the radiator 2 in the
low-pressure flow path 3b of the internal heat exchanger 3. The
refrigerant sucked into the compressor, therefore, is increased in
enthalpy and is overheated. The overheated gas refrigerant having
absorbed heat in the internal heat exchanger 3 is sucked into, and
compressed again, by the compressor 1.
[0056] The pressure of the refrigerant at the outlet of the
radiator can be controlled to maximize the COP by controlling the
opening degree of the electric expansion valve 4. Specifically, the
outlet pressure of the high-pressure radiator maximizing the COP,
i.e. the target high pressure Po, is calculated by the
air-conditioning control unit 10 based on the refrigerant
temperature at the outlet of the high-pressure radiator, as shown
in FIG. 2.
[0057] In the case where the actual high pressure Ph detected by
the pressure sensor 12 is higher than the target high pressure Po,
the opening degree of the electric expansion valve 4 is controlled
upward, while in the case where the actual high pressure Ph is
lower than the target high pressure Po, on the other hand, the
opening degree of the electric expansion valve 4 is controlled
downward.
[0058] By controlling the opening degree of the expansion valve 4
in this way, the actual high pressure Ph can be maintained at the
target high pressure Po, so that the COP is maximized for an
improved operating efficiency of the supercritical refrigeration
cycle.
[0059] Next, the operation of controlling the cooling fan of the
radiator according to this embodiment is explained specifically
with reference to FIG. 3. FIG. 3 is a flowchart showing the control
routine for the cooling fan of the radiator executed by the
air-conditioning control unit 10. This control routine is started
by activating the refrigeration cycle (activating the compressor
1).
[0060] First, in step S1, the terminal voltage of the drive motor
of the cooling fan 2a of the radiator (hereinafter referred to as
the fan terminal voltage) is set at a predetermined intermediate
value of, say, 6 V. The predetermined intermediate value is defined
as a predetermined value lower than the charge voltage (say, 12 V)
of an on-vehicle battery (not shown), and in the case under
consideration, is set at 6 V, i.e. half of the charge voltage (12
V) of the on-vehicle battery (not shown).
[0061] Next, in step S2, the temperature difference .DELTA.T
(=Tg-Ta) between the refrigerant temperature Tg at the outlet of
the radiator detected by the refrigerant temperature sensor 13 and
the atmospheric temperature Ta detected by the atmospheric
temperature sensor 15 is calculated.
[0062] Step S3 determines whether the temperature difference AT is
not lower than a predetermined value, or 2.degree. C. in the case
under consideration. In the case where the temperature difference
.DELTA.T is not lower than 2.degree. C., the process proceeds to
step S4, in which the fan terminal voltage is updated to +1 V in
the present state. As a result, the rotational speed of the cooling
fan 2a of the radiator increases by an amount equal to the increase
(1 V) in fan terminal voltage to increase the air capacity
correspondingly.
[0063] Upon determination in step S3 that the temperature
difference AT is less than 2.degree. C., on the other hand, the
process proceeds to step S5, in which the fan terminal voltage is
updated to the current level of -1 V. As a result, the rotational
speed of the cooling fan 2a of the radiator decreases by an amount
equal to the decrease (1 V) of the fan terminal voltage for a lower
air capacity.
[0064] According to this embodiment, as described above, the fan
terminal voltage is changed in accordance with the temperature
difference .DELTA.T so that the temperature difference .DELTA.T is
maintained at about a predetermined value (=2.degree. C.).
[0065] The technical significance of controlling the cooling fan of
the radiator as described above is explained with reference to FIG.
5. In FIG. 4, the abscissa represents the temperature difference
.DELTA.T (=Tg-Ta) and the ordinate the power consumption L of the
compressor. As understood from FIG. 4, as long as the temperature
difference .DELTA.T is not less than a predetermined value, or
specifically, not lower than 2.degree. C., the temperature
difference .DELTA.T and the compressor power consumption L are
substantially proportional to each other, and with the decrease in
temperature difference .DELTA.T, the compressor power consumption L
decreases.
[0066] Specifically, the decrease in temperature difference
.DELTA.T means the approach of the refrigerant temperature Tg at
the outlet of the radiator to the atmospheric temperature Ta. This
indicates that as long as the heat of the high-pressure refrigerant
can be ideally radiated (cooled) by the radiator 2, the refrigerant
temperature Tg at the outlet of the radiator can be reduced to
about the atmospheric temperature Ta.
[0067] The temperature difference .DELTA.T, therefore, is
considered the value of information indicating the difference
between the actual radiation state of the refrigerant at the outlet
of the radiator in the supercritical refrigeration cycle and the
ideal radiation state determined by the atmospheric temperature.
Thus, the decrease in the temperature difference .DELTA.T, i.e. the
approach of the refrigerant temperature Tg at the outlet of the
radiator to the atmospheric temperature Ta is indicative of the
downward change of the refrigerant pressure (high pressure) at the
outlet of the radiator in FIG. 2.
[0068] According to this embodiment, upon determination that the
radiator 2 is short of air capacity as compared with the ideal
radiation state, at the temperature difference .DELTA.T of not less
than 2.degree. C., the process proceeds to step S4, in which the
fan terminal voltage is increased to increase the air capacity of
the cooling fan 2a of the radiator. As a result, the temperature
difference .DELTA.T can be reduced and so can the power consumption
L of the compressor.
[0069] In the case where the temperature difference .DELTA.T is
less than 2.degree. C., on the other hand, it is understood from
FIG. 4 that the compressor power consumption L is maintained at a
substantially constant value in the neighborhood of the minimum
value. This indicates that according to this embodiment, at a
temperature difference .DELTA.T of less than 2.degree. C., the
radiator 2 is regarded to have reached substantially the ideal
radiation state, and the process proceeds to step S5, in which the
fan terminal voltage is reduced thereby to reduce the air capacity
of the radiator cooling fan 2a. As a result, the compressor power
consumption can be reduced while, at the same time, reducing the
power consumption of the cooling fan 2a of the radiator.
[0070] In FIG. 4, the abscissa represents also the air velocity at
the front of the radiator. With the increase in air velocity on the
front of the radiator, the cooling performance of the radiator is
improved to reduce the temperature difference .DELTA.T.
[0071] In FIG. 5, the abscissa represents the fan terminal voltage,
and the ordinate the air velocity on the front of the radiator. As
shown in FIG. 5, the air velocity on the front of the radiator is
higher, the higher the fan terminal voltage or the vehicle speed.
Even in the case where the fan terminal voltage is low at high
vehicle speed, therefore, the air velocity on the front of the
radiator can be increased to a sufficiently high level thereby to
improve the cooling performance of the radiator.
[0072] With the increase in the air velocity on the front of the
radiator, the cooling performance of the radiator is improved and
the refrigerant temperature Tg at the outlet of the radiator
decreases. As a result, the temperature difference .DELTA.T
(=Tg-Ta) decreases. According to this embodiment, therefore, the
fan terminal voltage is controlled downward (the process of step
S5). In this way, the power consumption of the cooling fan 2a of
the radiator at high vehicle speed can be positively reduced.
Second Embodiment
[0073] The first embodiment represents a case in which the cooling
fan 2a of the radiator shown in FIG. 3 is always controlled without
determining whether the cycle operation is in a supercritical state
or a subcritical state. According to the second embodiment, on the
other hand, as shown in FIG. 6, it is determined whether the cycle
operation is in a supercritical state or a subcritical state as
shown in FIG. 6 and, based on this determination, the control
operation of the cooling fan 2a of the radiator is switched.
[0074] FIG. 6 is a flowchart showing the operation of controlling
the cooling fan 2a of the radiator according to the second
embodiment. Steps S1 to S5 are identical to those of FIG. 3.
According to the second embodiment, step S6 of FIG. 6 determines in
step S6 whether the actual high pressure Ph detected by the
pressure sensor 12 is higher than the critical pressure of the
CO.sub.2 refrigerant or not.
[0075] In the case where the actual high pressure Ph is higher than
the critical pressure of the CO.sub.2 refrigerant (in the
supercritical state), the process proceeds to step S7 to determine
whether the supercritical control flag F is 1 or not. In view of
the fact that supercritical control flag F is initialized to 0 at
the time of starting the control routine, the determination is NO
in step S7 immediately after starting the control routine. In step
S1, therefore, the fan terminal voltage is set to 6 V and, in step
S8, the supercritical control flag F is set to 1. Subsequently,
therefore, in the supercritical state, the process always proceeds
from step S7 to step S2, so that the control process of steps S2 to
S5 is executed as in the first embodiment.
[0076] In the case where step S6 determines that the actual high
pressure Ph is lower than the critical pressure of the CO.sub.2
refrigerant (subcritical state), on the other hand, the process
proceeds to step S9, in which the supercritical control flag F is
set to 0 and, in step S10, the fan terminal voltage is directly
controlled based on the change in the actual high pressure Ph.
[0077] Specifically, the fan terminal voltage is controlled
continuously (or stepwise) upward with the increase in the high
pressure Ph.
[0078] In the subcritical state, the radiator 2 functions as a
condenser for cooling and condensing the refrigerant discharged
from the compressor and, therefore, the refrigerant at the outlet
of the radiator 2 assumes the liquid phase, and the supercooling
degree thereof is changed with the conditions for cycle operation.
In this subcritical state, it is known that the COP can be improved
by controlling the supercooling degree of the refrigerant at the
outlet of the radiator 2 in a predetermined range.
[0079] In view of this, according to the second embodiment, upon
determination of subcritical state, the supercooling degree of the
refrigerant at the outlet of the radiator is calculated based on
the actual high pressure P detected by the pressure sensor 12 and
the actual refrigerant temperature at the outlet of the radiator
detected by the temperature sensor 12, and the opening degree of
the electric expansion valve 4 is controlled to maintain the
supercooling degree within a predetermined range.
[0080] Specifically, the opening degree of the electric expansion
valve 4 is controlled in such a manner that in the case where the
supercooling degree of the refrigerant at the outlet of the
radiator is reduced, the opening degree of the electric expansion
valve 4 is reduced, while in the case where the supercooling degree
of the refrigerant at the outlet of the radiator is increased
beyond a predetermined range, on the other hand, the opening degree
of the electric expansion vale 4 is increased. This operation of
controlling the expansion valve opening degree maintains the
supercooling degree of the refrigerant at the outlet of the
radiator within a predetermined range.
[0081] As described above, in subcritical state, the high pressure
is not controlled but the supercooling degree of the refrigerant at
the outlet of the radiator by the electric expansion valve 4 and,
therefore, the high pressure increases with the increase in the
thermal load of the refrigeration cycle. In subcritical state,
therefore, the air capacity (cooling performance) of the radiator
can be properly controlled in accordance with the thermal load of
the cycle by controlling the fan terminal voltage in accordance
with the high pressure Ph
Other Embodiments
[0082] (1) In the embodiments described above, the temperature
difference .DELTA.T (=Tg-Ta) between the temperature Tg of the
refrigerant at the outlet of the radiator 2 and the atmospheric
temperature Ta is calculated and, in accordance with the value of
the temperature difference .DELTA.T, the terminal voltage of the
cooling fan 2a of the radiator, i.e. the air capacity is
controlled. The refrigerant temperature Tg at the outlet of the
radiator 2, however, is not limited to the temperature of the
refrigerant flowing out from the radiator 2, but the temperature of
the refrigerant in the refrigerant flow path on the outlet side of
the internal flow path of the radiator 2 may alternatively be
detected.
[0083] (2) In the embodiments described above, the air capacity of
the cooling fan 2a of the radiator is controlled in accordance with
the value of the temperature difference .DELTA.T. As an
alternative, the air capacity of the cooling fan 2a of the radiator
may be controlled based on a cycle operation value of information
other than the temperature difference .DELTA.T, with equal
effect.
[0084] Specifically, the refrigerant temperature Tg at the outlet
of the radiator 2 and the atmospheric temperature are so correlated
that by increasing the air capacity of the cooling fan 2a of the
radiator sufficiently, the refrigerant temperature Tg at the outlet
of the radiator 2 can be ideally reduced almost to the atmospheric
temperature Ta.
[0085] In view of this, in place of the refrigerant temperature Tg
at the outlet of the radiator 2, the pressure Pset is set as
determined by the atmospheric temperature Ta, and this set pressure
Pset is determined in such a manner as to increase with the
increase in the atmospheric temperature Ta. Then, the difference
.DELTA.P between the actual high pressure Ph and the set pressure
Pset is calculated. In other words, the pressure difference
.DELTA.P is calculated as the actual high pressure Ph less the set
pressure Pset.
[0086] In the case where this pressure difference .DELTA.P is not
lower than a predetermined value, the terminal voltage of the
cooling fan 2a of the radiator (air capacity) is controlled upward
(the control operation in step S4 of FIGS. 3, 6), while in the case
where the value of the pressure difference .DELTA.P is less than
the predetermined value, the terminal voltage of the cooling fan 2a
of the radiator (air capacity) is controlled downward (the control
operation in step S5 of FIGS. 3, 6). Also in the case where the air
capacity of the cooling fan 2a of the radiator is controlled in
this way, operational effects similar to those of the
aforementioned embodiments are exhibited.
[0087] (3) In the embodiments described above, CO.sub.2 is used as
a refrigerant to construct the supercritical refrigeration cycle in
which the high pressure increases beyond the critical pressure of
the refrigerant (supercritical state). As an alternative to
CO.sub.2, however, ethylene, ethane, etc. may be used as a
refrigerant to construct the supercritical refrigeration cycle.
[0088] (4) In the embodiments described above, the supercritical
refrigeration cycle is used as the refrigeration cycle for the
automotive air conditioning system. This invention, however, is
also applicable to refrigeration cycles in various fields, such as
housing, with equal effect.
[0089] While the invention has been described by reference to
specific embodiments chosen for purposes of illustration, it should
be apparent that numerous modifications could be made thereto, by
those skilled in the art, without departing from the basic concept
and scope of the invention.
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