U.S. patent application number 11/141134 was filed with the patent office on 2005-12-01 for heat cycle.
This patent application is currently assigned to DENSO Corporation. Invention is credited to Hotta, Tadashi, Inaba, Atsushi.
Application Number | 20050262858 11/141134 |
Document ID | / |
Family ID | 35423683 |
Filed Date | 2005-12-01 |
United States Patent
Application |
20050262858 |
Kind Code |
A1 |
Inaba, Atsushi ; et
al. |
December 1, 2005 |
Heat cycle
Abstract
The waste heat recovering operation mode (a Rankine cycle) is
started and operated for a predetermined period of time T1 (s)
(S430 to S450). In the case where the difference (P2-P1) between
the upstream pressure P1 and the downstream pressure P2 of the
liquid pump is higher than the predetermined pressure P, the waste
heat recovering operation mode is continued. In the case where the
difference (P2-P1) is not more than the predetermined pressure P,
after the air conditioning mode is started (S480 to S500), the
waste heat recovering operation mode is started again (S430 to
S450). Due to the foregoing, it is possible to provide a heat
cycle, which is provided with a refrigerating cycle and a Rankine
cycle which are changeable each other, in which an incomplete start
at the time of Rankine cycle can be reduced and a deterioration of
the cycle efficiency can be reduced.
Inventors: |
Inaba, Atsushi;
(Kariya-city, JP) ; Hotta, Tadashi; (Nishio-shi,
JP) |
Correspondence
Address: |
HARNESS, DICKEY & PIERCE, P.L.C.
P.O. BOX 828
BLOOMFIELD HILLS
MI
48303
US
|
Assignee: |
DENSO Corporation
Kariya-city
JP
Nippon Soken, Inc.
Nishio-shi
JP
|
Family ID: |
35423683 |
Appl. No.: |
11/141134 |
Filed: |
May 31, 2005 |
Current U.S.
Class: |
62/190 ;
62/238.6; 62/467 |
Current CPC
Class: |
F25B 1/04 20130101; B60H
2001/3297 20130101; F04C 18/0215 20130101; F04C 2240/45 20130101;
B60H 1/00878 20130101; F25B 2327/001 20130101; B60H 2001/3295
20130101; F25B 49/005 20130101; B60H 1/3204 20130101; F04C 29/005
20130101; B60H 2001/00928 20130101; F01C 1/0215 20130101; F01C
20/08 20130101; F04C 23/003 20130101; F04C 23/008 20130101; B60H
1/32 20130101; Y02A 30/274 20180101; F25B 27/00 20130101 |
Class at
Publication: |
062/190 ;
062/467; 062/238.6 |
International
Class: |
F25B 041/00; F25B
049/00; F25B 027/00; F25B 001/00 |
Foreign Application Data
Date |
Code |
Application Number |
May 31, 2004 |
JP |
2004-161805 |
Claims
What is claimed is:
1. A heat cycle device comprising: a rotary fluid machine for
mutually converting between fluid energy of refrigerant and
mechanical rotary energy; a condenser for condensing the
refrigerant supplied from the rotary fluid machine; a Rankine cycle
system including a fluid pump for moving the refrigerant supplied
from the condenser and also including a vapor generator for heating
the refrigerant, which has been moved by the fluid pump, by the
heat of a heat generating body; a refrigerating cycle system
including an evaporator for evaporating the refrigerant supplied
from the condenser; and a control unit for conducting a refrigerant
condensing operation in which the refrigerant in the refrigerating
cycle system is compressed by the rotary fluid machine at the time
of operating the Rankine cycle system and the compressed
refrigerant is condensed by the condenser.
2. A heat cycle device according to claim 1, the control unit
including: a judging means for judging whether or not the Rankine
cycle system is normally operated after the operation of the
Rankine cycle system was started; and a control means for
continuing the operation of the Rankine cycle system in the case
where it is judged that the Rankine cycle system is normally
operated, and for conducting the refrigerant condensing operation
in the case where it is judged that the Rankine cycle system is not
normally operated.
3. A heat cycle device according to claim 2, further comprising: an
upstream refrigerant pressure sensor for measuring pressure of the
refrigerant, arranged in an upstream side portion of the
refrigerant flow of the fluid pump; and a downstream refrigerant
pressure sensor for measuring pressure of the refrigerant, arranged
in a downstream side portion of the refrigerant flow of the fluid
pump, wherein the judging means judges that the Rankine cycle is
normally operated at the time of operating the Rankine cycle system
in the case where a difference (P2-P1) between the detected
pressure of the downstream refrigerant pressure sensor and the
detected pressure (P) of the upstream refrigerant pressure sensor
is larger than the predetermined pressure (P), and the judging
means judges that the Rankine cycle is not normally operated at the
time of operating the Rankine cycle system in the case where the
difference (P2-P1) between the detected pressure (P2) of the
downstream refrigerant pressure sensor and the detected pressure
(P1) of the upstream refrigerant pressure sensor is not more than
the predetermined pressure (P).
4. A heat cycle device according to claim 2, wherein the judging
means judges that the Rankine cycle system is normally operated in
the case where a work-load of the liquid pump is heavier than a
predetermined work-load at the time of operating the Rankine cycle
system, and the judging means judges that the Rankine cycle system
is not normally operated in the case where the work-load of the
liquid pump is not more than the predetermined work-load at the
time of operating the Rankine cycle system.
5. A heat cycle device according to claim 4, wherein the liquid
pump is an electric liquid pump, and the work-load is represented
by electric power consumed by the electric liquid pump.
6. A heat cycle device according to one of claim 1, further
comprising an air blowing means for blowing air, the temperature of
which is adjusted by the refrigerating cycle system, wherein the
control unit conducts the refrigerant condensing operation under
the condition that the air blowing means is not operated.
7. A heat cycle device according to claim 1, further comprising a
sensor for measuring a physical value having a correlation with the
temperature of the refrigerant inside the liquid pump, wherein the
control unit determines the time, which has passed from the start
of the refrigerant condensing operation to when the physical value
measured by the sensor shows that the refrigerant inside the
refrigerant pump is in the supercooled state, to be the
continuation time for continuing the refrigerant condensing
operation.
8. A heat cycle device according to claim 1, wherein the condenser
is a heat exchanger for condensing the refrigerant by exchanging
heat between the outside air and the refrigerant, the heat cycle
device further comprising: an outside air temperature sensor for
measuring the temperature of the outside air; and a sensor for
measuring a physical value having a correlation with the
temperature of the refrigerant inside the liquid pump, wherein the
control unit determines a target temperature at which the
refrigerant inside the refrigerant pump is in the supercooled state
according to the outside air temperature measured by the outside
air temperature sensor, and further the control unit determines the
time, which has passed from the start of the refrigerant condensing
operation to when the physical value measured by the sensor becomes
the target temperature, to be the continuation time for continuing
the refrigerant condensing operation.
9. A heat cycle device according to claim 7, wherein the sensor is
a temperature sensor for measuring the temperature of the housing
of the refrigerant pump.
10. A heat cycle device according to claim 7, wherein the sensor is
a temperature sensor for measuring the temperature of air
immediately after heat was exchanged with the refrigerant in the
evaporator.
11. A heat cycle device according to claim 1, wherein the condenser
is a heat exchanger for condensing the refrigerant by exchanging
heat between the outside air and the refrigerant, further
comprising an outside air temperature sensor for measuring the
outside air temperature, wherein the control unit includes a
continuation time setting means for determining the continuation
time (T21), in which the refrigerant condensing operation is
continued, according to the temperature measured by the outside air
temperature sensor.
12. A heat cycle device according to claim 1, wherein the rotary
fluid machine is a reversible rotary machine capable of being
reversibly operated as an expansion machine for obtaining power
when the refrigerant is expanded, or operated as a compressor for
compressing the refrigerant when power is supplied to the
compressor.
13. A heat cycle device according to claim 12, wherein the control
unit conducts the refrigerant condensing operation by operating the
rotary fluid machine as a compressor before the rotary fluid
machine is operated as an expansion machine and the operation of
the Rankine cycle system is started.
14. A heat cycle device according to claim 12, wherein the
reversible rotary machine is composed being integrated with the
fluid pump into one body, and the fluid pump is arranged so that it
can be cooled by the gas-phase refrigerant sucked into the
reversible rotary machine at the time of operating the
refrigerating cycle system.
15. A heat cycle device according to claim 1, wherein the rotary
fluid machine includes an expansion machine for expanding the
refrigerant to obtain power and a compressor for compressing the
refrigerant when power is supplied to the compressor.
16. A heat cycle device according to claim 15, wherein the control
unit conducts the refrigerant condensing operation by operating the
compressor before the expansion machine is operated and the
operation of the Rankine cycle system is started.
17. A heat cycle device according to claim 15, wherein the control
unit conducts the refrigerant condensing operation by operating the
compressor simultaneously when the expansion machine is operated
and the operation of the Rankine cycle system is started.
18. A heat cycle device comprising: a Rankine cycle system
including a fluid pump for moving refrigerant and also including a
vapor generator for heating the refrigerant, which has been moved
by the fluid pump, by the heat of a heat generating body; a
refrigerating cycle system including an evaporator for evaporating
the refrigerant; and a control unit for conducting the cooling
operation for cooling the fluid pump by operating the refrigerating
cycle system at the time of operating the Rankine cycle system.
19. A heat cycle device according to claim 18, wherein the
refrigerating cycle system includes a compressor, and the fluid
pump is arranged so that it can be cooled by the gas-phase
refrigerant sucked into the compressor.
20. A heat cycle device according to claim 18, wherein the control
unit conducts the cooling operation before the operation of the
Rankine cycle system is started and/or while the Rankine cycle
system is being operated.
21. A heat cycle comprising: a refrigerating cycle in which
refrigerant of low pressure is evaporated so as to absorb heat from
a low temperature side and the evaporated gas-phase refrigerant is
compressed so as to raise the temperature and the heat absorbed
from the low temperature side is radiated to a high temperature
side so as to condense the gas-phase refrigerant into the
liquid-phase refrigerant; a Rankine cycle including a vapor
generator for generating the gas-phase refrigerant by heating the
liquid-phase refrigerant of the refrigerating cycle by the waste
heat of a heat generating body, also including a liquid-phase pipe
for connecting a liquid-phase takeout section for taking out the
liquid-phase refrigerant from the refrigerating cycle, with the
vapor generator, also including a liquid pump arranged in the
liquid-phase pipe, for moving the liquid phase refrigerant to the
vapor generator, also including an expansion machine for obtaining
power by expanding the gas-phase refrigerant, and also including a
condenser for condensing the gas-phase refrigerant which has been
expanded by the expansion machine; a control means for controlling
a state of operation of the refrigerating cycle and also
controlling a state of operation of Rankine cycle; and a
change-over means for changing over between a case in which the
Rankine cycle is operated and a case in which the refrigerating
cycle is operated by a signal sent from the control means, wherein
the control means operates the Rankine cycle in such a manner that
the refrigerating cycle is operated by the refrigerant condensing
operation so as to condense the gas-phase refrigerant into the
liquid-phase refrigerant and then the Rankine cycle is
operated.
22. A heat cycle comprising: a refrigerating cycle in which
refrigerant of low pressure is evaporated so as to absorb heat from
a low temperature side and the evaporated gas-phase refrigerant is
compressed so as to raise the temperature and the heat absorbed
from the low temperature side is radiated to a high temperature
side so as to condense the gas-phase refrigerant into the
liquid-phase refrigerant; a Rankine cycle including a vapor
generator for generating the gas-phase refrigerant by heating the
liquid-phase refrigerant of the refrigerating cycle by the waste
heat of a heat generating body, also including a liquid-phase pipe
for connecting a liquid-phase takeout section for moving the
liquid-phase refrigerant from the refrigerating cycle, with the
vapor generator, also including a liquid pump arranged in the
liquid-phase pipe, for moving the liquid-phase refrigerant to the
vapor generator, also including an expansion machine for obtaining
power by expanding the gas-phase refrigerant, and also including a
condenser for condensing the gas-phase refrigerant which has been
expanded by the expansion machine; a control means for controlling
a state of operation of the refrigerating cycle and also
controlling a state of operation of Rankine cycle; and a
change-over means for changing over between the case in which the
Rankine cycle is operated and the case in which the refrigerating
cycle is operated by a signal sent from the control means, wherein
after the Rankine cycle has been operated, the control means judges
whether or not the Rankine cycle is normally operated, in the case
where operation of the Rankine cycle has been judged to be normal,
the Rankine cycle is kept operated and in the case where operation
of the Rankine cycle has been judge to be not normal, the control
means operates in such a manner that it stops the operation of the
Rankine cycle and operates the refrigerating cycle so as to conduct
the refrigerant condensing operation for recovering the
liquid-phase refrigerant and the Rankine cycle is operated again
after the refrigerant condensing operation.
23. A heat cycle according to claim 22, further comprising: an
upstream refrigerant pressure sensor arranged in a portion on the
upstream side of the flow of the refrigerant of the liquid pump,
the upstream refrigerant pressure sensor outputting a signal of the
refrigerant pressure to the control means; and a downstream
refrigerant pressure sensor arranged in a portion on the downstream
side of the flow of the refrigerant of the liquid pump, the
downstream refrigerant pressure sensor outputting a signal of the
refrigerant pressure to the control means, wherein in the case
where a value (P2-P1), which is obtained when a detected pressure
value (P1) of the upstream refrigerant pressure sensor is
subtracted from a detected pressure value (P2) of the downstream
refrigerant pressure sensor, is higher than a predetermined
pressure value (P) when the Rankine cycle is operated, the control
means judges that the Rankine cycle is normally operated, and in
the case where the value (P2-P1), which is obtained when the
detected pressure value (P1) of the upstream refrigerant pressure
sensor is subtracted from the detected pressure value of the
downstream refrigerant pressure sensor, is not more than the
predetermined pressure value (P), the control means judges that the
Rankine cycle is not normally operated.
24. A heat cycle according to claim 22, wherein the control means
judges that the Rankine cycle is normally operated in the case
where a work-load of the liquid pump is more than a predetermined
work-load when the Rankine cycle is operated, and the control means
judges that the Rankine cycle is not normally operated in the case
where the work-load of the liquid pump is not more than the
predetermined work-load when the Rankine cycle is operated.
25. A heat cycle according to claim 24, wherein the liquid pump is
an electric liquid pump driven by electricity, and the work-load is
represented by electric power consumed by the electrically-driven
liquid pump.
26. A heat cycle according to claim 21, wherein the expansion
machine is a reversible rotary machine having the function of a
compressor for compressing the gas-phase refrigerant in the
refrigerating cycle, the reversible rotary machine is integrated
with the liquid pump, and the liquid pump is cooled by the
gas-phase refrigerant sucked into the reversible rotary machine at
the time of operating the refrigerating cycle.
27. A heat cycle according to claim 21, further comprising: an air
blowing means for blowing air conditioned by the refrigerating
cycle; and an operation demand means for demanding the operation of
the refrigerating cycle, wherein in the case of conducting the
refrigerant condensing operation, the control means conducts the
refrigerant condensing operation without operating the air blowing
means when the operation of the refrigerating cycle is not demanded
by the operation demand means.
28. A heat cycle according to claim 21, wherein, the condenser is a
heat exchanger for condensing the gas-phase refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle further comprises an outside air temperature sensor for
measuring the temperature of the outside air, the control means
determines the continuation time (T21) for continuing the
refrigerant condensing operation, and the continuation time (T21)
is determined on the basis of the outside air temperature.
29. A heat cycle according to claim 21, further comprising a sensor
for measuring a physical value having a correlation with a
temperature of the refrigerant inside the liquid pump, wherein the
control means determines the continuation time in which the
refrigerant condensing operation is continued, and the continuation
time is the time from the start of the refrigerant condensing
operation to when the physical value measured by the sensor becomes
the temperature at which the refrigerant inside the refrigerant
pump is supercooled.
30. A heat cycle according to claim 21, wherein the condenser is a
heat exchanger for condensing the gas-phase refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle further comprises an outside air temperature sensor for
measuring the temperature of the outside air and also comprises a
sensor for measuring a physical value having a correlation with the
temperature of the refrigerant inside the liquid pump, the control
means determines the temperature at which the refrigerant inside
the refrigerant pump is supercooled by the outside air temperature,
and also determines the continuation time in which the refrigerant
condensing operation is continued, and the continuation time is the
time from the start of the refrigerant condensing operation to when
the physical value measured by the sensor becomes the temperature
at which the refrigerant inside the refrigerant pump is
supercooled.
31. A heat cycle according to claim 30, wherein the sensor for
measuring the physical value is a temperature sensor for measuring
the temperature of the housing of the refrigerant pump
32. A heat cycle according to claim 30, wherein the refrigerating
cycle includes an evaporator for evaporating the refrigerant of low
pressure by exchanging heat between the refrigerant of low pressure
and air, and the sensor for measuring the physical value is a
temperature sensor for measuring the temperature of air immediately
after heat is exchanged with the refrigerant of low pressure.
33. A heat cycle device according to claim 8, wherein the sensor is
a temperature sensor for measuring the temperature of the housing
of the refrigerant pump.
34. A heat cycle device according to claim 8, wherein the sensor is
a temperature sensor for measuring the temperature of air
immediately after heat was exchanged with the refrigerant in the
evaporator.
35. A heat cycle according to claim 22, wherein the expansion
machine is a reversible rotary machine having the function of a
compressor for compressing the gas-phase refrigerant in the
refrigerating cycle, the reversible rotary machine is integrated
with the liquid pump, and the liquid pump is cooled by the
gas-phase refrigerant sucked into the reversible rotary machine at
the time of operating the refrigerating cycle.
36. A heat cycle according to claim 22, further comprising: an air
blowing means for blowing air conditioned by the refrigerating
cycle; and an operation demand means for demanding the operation of
the refrigerating cycle, wherein in the case of conducting the
refrigerant condensing operation, the control means conducts the
refrigerant condensing operation without operating the air blowing
means when the operation of the refrigerating cycle is not demanded
by the operation demand means.
37. A heat cycle according to claim 22, wherein, the condenser is a
heat exchanger for condensing the gas-phase refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle further comprises an outside air temperature sensor for
measuring the temperature of the outside air, the control means
determines the continuation time (T21) for continuing the
refrigerant condensing operation, and the continuation time (T21)
is determined on the basis of the outside air temperature.
38. A heat cycle according to claim 22, further comprising a sensor
for measuring a physical value having a correlation with a
temperature of the refrigerant inside the liquid pump, wherein the
control means determines the continuation time in which the
refrigerant condensing operation is continued, and the continuation
time is the time from the start of the refrigerant condensing
operation to when the physical value measured by the sensor becomes
the temperature at which the refrigerant inside the refrigerant
pump is supercooled.
39. A heat cycle according to claim 22, wherein the condenser is a
heat exchanger for condensing the gas-phase refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle further comprises an outside air temperature sensor for
measuring the temperature of the outside air and also comprises a
sensor for measuring a physical value having a correlation with the
temperature of the refrigerant inside the liquid pump, the control
means determines the temperature at which the refrigerant inside
the refrigerant pump is supercooled by the outside air temperature,
and also determines the continuation time in which the refrigerant
condensing operation is continued, and the continuation time is the
time from the start of the refrigerant condensing operation to when
the physical value measured by the sensor becomes the temperature
at which the refrigerant inside the refrigerant pump is
supercooled.
40. A heat cycle according to claim 29, wherein the sensor for
measuring the physical value is a temperature sensor for measuring
the temperature of the housing of the refrigerant pump
41. A heat cycle according to claim 29, wherein the refrigerating
cycle includes an evaporator for evaporating the refrigerant of low
pressure by exchanging heat between the refrigerant of low pressure
and air, and the sensor for measuring the physical value is a
temperature sensor for measuring the temperature of air immediately
after heat is exchanged with the refrigerant of low pressure.
Description
BACKGROUND OF THE INVENTION
[0001] 1. Field of the Invention
[0002] The present invention relates to Rankine cycle in which
power is obtained from heat energy given to a refrigerant.
[0003] 2. Description of the Related Art
[0004] Conventionally, a heat cycle device referred to as a
refrigerating cycle device has been known, and a heat cycle device
referred to as Rankine cycle device has also been known. According
to the refrigerating cycle device, when refrigerant is compressed
being given power so as to transfer heat, a high or a low
temperature can be provided. According to Rankine cycle device,
power can be obtained from heat energy given to refrigerant. For
example, a Rankine cycle device is disclosed in Japanese Granted
Patent Publication No. 3356449 and of Japanese Unexamined Utility
Model Publication No. 63-92021. These Rankine cycle device can be
used as an electric power generating device in which waste heat is
recovered so as to generate electric power. Alternatively, this
Rankine cycle device can be used as an automotive power generating
device in which waste heat of an internal combustion engine of an
automobile is recovered so as to generate automotive power.
[0005] In Japanese Patent Application No. 2003-390893, the present
inventors proposed an air conditioner (refrigerating cycle) for
vehicle use having Rankine cycle for recovering heat energy from
waste heat exhausted from an engine mounted on a vehicle. This air
conditioner for vehicle use will be referred to as an example of
the prior application.
[0006] This example of the prior application will be explained
below by referring to FIG. 1. The example of the prior application
includes components to compose a refrigerating cycle device to
provide an air-conditioning operation mode (refrigerating cycle
operation) in which the refrigerant is made to flow in the order of
the reversible rotary machine 10.fwdarw.the radiator 11.fwdarw.the
gas-liquid separator 12.fwdarw.the decompressor 13.fwdarw.the
evaporator 14.
[0007] Further, this prior application includes a liquid-phase pipe
31 for connecting the pipe composing the refrigerating cycle with
the vapor generator 30; and a liquid pump 32, which is arranged in
the liquid-phase pipe 31, for moving the liquid-phase refrigerant
to the vapor generator 30. The prior application further includes:
components to compose a Rankine cycle device to provide a waste
heat recovery operation mode (Rankine cycle operation) in which the
refrigerant is made to flow in the order of the liquid pump
32.fwdarw.the vapor generator 30.fwdarw.the reversible rotary
machine 10.fwdarw.the radiator 11.
[0008] Due to the foregoing, at the time of the air conditioning
operation mode, the vehicle room can be air-conditioned, and at the
time of the waste heat recovering operation mode, the waste heat
exhausted from the engine 20 can be recovered by the reversible
rotary machine 10 in the form of power.
[0009] However, in the example of the prior application, the
following cases may occur. In the case where a quantity of the
refrigerant staying the gas-liquid separator 12 is small on the
basis of a state of operation of the air conditioner (the
refrigerating cycle) for vehicle use or in the case where the
liquid-phase refrigerant inside the liquid pump 32 is evaporated by
a rise in the temperature inside the liquid pump 32, bubbles of the
gas-phase refrigerant may enter into the inside of the liquid pump
32, and the liquid-phase refrigerant can not be moved to the vapor
generator 30 even when the liquid pump 32 is operated. Due to the
foregoing, there is a possibility that it becomes impossible to
normally operate the waste heat recovering operation mode (Rankine
cycle).
[0010] Even in the case where the liquid pump 32 can move the
liquid-phase refrigerant to the vapor generator 30, the operation
efficiency of the liquid pump 32 is lowered by the bubbles of the
gas-phase refrigerant mixed into the liquid pump 32. In other
words, a quantity of the refrigerant to be conveyed is decreased
with respect to the power consumption of the pump. That is, a
quantity of the refrigerant to be supplied to the vapor generator
30 is decreased, and there is a possibility that the efficiency of
a Rankine cycle may be lowered.
[0011] One object of the present invention is to reduce the
possibility of the occurrence of an incomplete start of a Rankine
cycle device.
[0012] Another object of the present invention is to reduce the
possibility of the deterioration of the efficiency of a Rankine
cycle device.
[0013] Still another object of the present invention is to make it
possible to stably operate a Rankine cycle device by utilizing the
function of a refrigerating cycle device in the heat cycle device
which can be used for both the Rankine cycle device and the
refrigerating cycle device.
SUMMARY OF THE INVENTION
[0014] In order to accomplish the above objects, the present
invention employs the following technical means.
[0015] The invention described in aspect 1 employs a heat cycle
device comprising: a rotary fluid machine (10, 10b, 10c) for
mutually converting between fluid energy of refrigerant and
mechanical rotary energy; a condenser (11) for condensing the
refrigerant supplied from the rotary fluid machine (10, 10b, 10c);
a Rankine cycle system (10, 11, 30, 32, 300) including a fluid pump
(32, 300) for moving the refrigerant supplied from the condenser
(11) and also including a vapor generator (30) for heating the
refrigerant, which has been moved by the fluid pump, by the heat of
a heat generating body (20); a refrigerating cycle system (10, 11,
13, 14) including an evaporator (14) for evaporating the
refrigerant supplied from the condenser (11); and a control unit
(40) for conducting a refrigerant condensing operation in which the
refrigerant in the refrigerating cycle system (10, 11, 13, 14) is
compressed by the rotary fluid machine (10, 10b, 10c) at the time
of operating the Rankine cycle system (10, 11, 30, 32, 300) and the
compressed refrigerant is condensed by the condenser (11).
[0016] According to this invention, when a Rankine cycle system is
operated, the refrigerant in the refrigerating cycle system is
compressed by the rotary fluid machine and condensed by the
condenser. Therefore, the liquid-phase refrigerant can be supplied
to a Rankine cycle system. As a result, it is possible to suppress
the occurrence of an incomplete start of a Rankine cycle system.
Further, it is possible to suppress the deterioration of the
efficiency during the operation.
[0017] The invention described in aspect 2 employs a heat cycle
device according to aspect 1, the control unit (40) including: a
judging means for judging whether or not the Rankine cycle system
(10, 11, 30, 32, 300) is normally operated after the operation of
the Rankine cycle system (10, 11, 30, 32, 300) was started; and a
control means for continuing the operation of the Rankine cycle
system (10, 11, 30, 32, 300) in the case where it is judged that
the Rankine cycle system (10, 11, 30, 32, 300) is normally
operated, and for conducting the refrigerant condensing operation
in the case where it is judged that the Rankine cycle system (10,
11, 30, 32, 300) is not normally operated.
[0018] According to this invention, when it is judged that the
Rankine cycle system is not normally operated, the refrigerant
condensing operation is executed. Therefore, the liquid-phase
refrigerant can be supplied to the Rankine cycle system.
Accordingly, it is possible to suppress the occurrence of an
abnormal state caused by lack of the liquid-phase refrigerant.
[0019] According to one embodiment of the present invention, the
refrigerant condensing operation can be executed when the operation
of the Rankine cycle system is temporarily stopped. According to
another embodiment of the present invention, the refrigerant
condensing operation can be executed simultaneously while the
operation of the Rankine cycle system is being continued.
[0020] The invention described in aspect 3 employs a heat cycle
device according to aspect 2, further comprising: an upstream
refrigerant pressure sensor (42) for measuring pressure of the
refrigerant, arranged in an upstream side portion of the
refrigerant flow of the fluid pump (32, 300); and a downstream
refrigerant pressure sensor (43) for measuring pressure of the
refrigerant, arranged in a downstream side portion of the
refrigerant flow of the fluid pump (32, 300), wherein the judging
means judges that the Rankine cycle (10, 11, 30, 32, 300) is
normally operated at the time of operating the Rankine cycle system
(10, 11, 30, 32, 300) in the case where a difference (P2-P1)
between the detected pressure (P2) of the downstream refrigerant
pressure sensor (43) and the detected pressure (P1) of the upstream
refrigerant pressure sensor (42) is larger than the predetermined
pressure (P), and the judging means judges that the Rankine cycle
(10, 11, 30, 32, 300) is not normally operated at the time of
operating the Rankine cycle system (10, 11, 30, 32, 300) in the
case where the difference (P2-P1) between the detected pressure
(P2) of the downstream refrigerant pressure sensor (43) and the
detected pressure (P1) of the upstream refrigerant pressure sensor
(42) is not more than the predetermined pressure (P).
[0021] According to this invention, it is possible to appropriately
judge an abnormality of the Rankine cycle system caused by a lack
of the liquid-phase refrigerant.
[0022] The invention described in aspect 4 employs a heat cycle
device according to aspect 2, wherein the judging means judges that
the Rankine cycle system (10, 11, 30, 32, 300) is normally operated
in the case where a work-load of the liquid pump (32, 300) is
heavier than a predetermined work-load at the time of operating the
Rankine cycle system (10, 11, 30, 32, 300), and the judging means
judges that the Rankine cycle system (10, 11, 30, 32, 300) is not
normally operated in the case where the work-load of the liquid
pump (32, 300) is not more than the predetermined work-load at the
time of operating the Rankine cycle system (10, 11, 30, 32,
300).
[0023] According to this invention, it is possible to appropriately
judge an abnormality of the Rankine cycle system caused by a lack
of the liquid-phase refrigerant.
[0024] The invention described in aspect 5 employs a heat cycle
device according to aspect 4, wherein the liquid pump is an
electric liquid pump (32), and the work-load is represented by
electric power consumed by the electric liquid pump (32).
[0025] According to this invention, it is possible to judge an
abnormality of the Rankine cycle system by a simple structure.
[0026] The invention described in aspect 6 employs a heat cycle
device according to one of aspects 1 to 5, further comprising an
air blowing means (14a) for blowing air, the temperature of which
is adjusted by the refrigerating cycle system (10, 11, 13, 14),
wherein the control unit (40) conducts the refrigerant condensing
operation under the condition that the air blowing means (14a) is
not operated.
[0027] According to this invention, the refrigerant condensing
operation can be provided when the cooling device or the
refrigerating device in the refrigerating cycle system is operated,
and a state in which the blast means is not operated is provided by
the means for providing the operation in which the liquid-phase
refrigerant is increased. As a result, the liquid-phase refrigerant
can be positively supplied.
[0028] The invention described in aspect 7 employs a heat cycle
device according to one of aspects 1 to 6, further comprising a
sensor (46, 47) for measuring a physical value having a correlation
with the temperature of the refrigerant inside the liquid pump (32,
300), wherein the control unit (40) determines the time, which has
passed from the start of the refrigerant condensing operation to
when the physical value measured by the sensor (46, 47) shows that
the refrigerant inside the refrigerant pump (32) is in the
supercooled state, to be the continuation time for continuing the
refrigerant condensing operation.
[0029] According to this invention, it is possible to suppress an
excessive refrigerant condensing operation.
[0030] The invention described in aspect 8 employs a heat cycle
device according to one of aspects 1 to 6, wherein the condenser
(11) is a heat exchanger for condensing the refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle device further comprising: an outside air temperature
sensor (45) for measuring the temperature of the outside air; and a
sensor (46, 47) for measuring a physical value having a correlation
with the temperature of the refrigerant inside the liquid pump (32,
300), wherein the control unit (40) determines a target temperature
at which the refrigerant inside the refrigerant pump (32) is in the
supercooled state according to the outside air temperature measured
by the outside air temperature sensor (45), and further the control
unit (40) determines the time, which has passed from the start of
the refrigerant condensing operation to when the physical value
measured by the sensor (46, 47) becomes the target temperature, to
be the continuation time for continuing the refrigerant condensing
operation.
[0031] According to this invention, it is possible to suppress an
excessive refrigerant condensing operation.
[0032] The invention described in aspect 9 employs a heat cycle
device according to aspect 7 or 8, wherein the sensor is a
temperature sensor (46) for measuring the temperature of the
housing of the refrigerant pump.
[0033] According to this invention, it is possible to provide a
simple structure of the heat cycle device.
[0034] The invention described in aspect 10 employs a heat cycle
device according to aspect 7 or 8, wherein the sensor is a
temperature sensor (47) for measuring the temperature of air
immediately after heat was exchanged with the refrigerant in the
evaporator (14).
[0035] According to this invention, it is possible to provide a
simple structure of the heat cycle device.
[0036] The invention described in aspect 11 employs a heat cycle
device according to one of aspects 1 to 6, wherein the condenser
(11) is a heat exchanger for condensing the refrigerant by
exchanging heat between the outside air and the refrigerant,
further comprising an outside air temperature sensor (45) for
measuring the outside air temperature, wherein the control unit
(40) includes a continuation time setting means for determining the
continuation time (T21), in which the refrigerant condensing
operation is continued, according to the temperature measured by
the outside air temperature sensor (45).
[0037] According to this invention, it is possible to suppress an
excessive refrigerant condensing operation.
[0038] The invention described in aspect 12 employs a heat cycle
device according to one of aspects 1 to 11, wherein the rotary
fluid machine is a reversible rotary machine (10) capable of being
reversibly operated as an expansion machine for obtaining power
when the refrigerant is expanded, or operated as a compressor for
compressing the refrigerant when power is supplied to the
compressor.
[0039] According to this invention, when the rotary fluid machine,
which can reversibly function as an expansion machine or a
compressor, is used, the refrigerant condensing operation can be
executed when the rotary fluid machine functions as a compressor at
the time of operating the Rankine cycle system.
[0040] The invention described in aspect 13 employs a heat cycle
device according to aspect 12, wherein the control unit (40)
conducts the refrigerant condensing operation by operating the
rotary fluid machine as a compressor before the rotary fluid
machine is operated as an expansion machine and the operation of
the Rankine cycle system (10, 11, 30, 32, 300) is started.
[0041] According to this invention, when the rotary fluid machine
is made to function reversibly, the refrigerant condensing
operation can be realized before the operation of the Rankine cycle
system is started.
[0042] The invention described in aspect 14 employs a heat cycle
device according to aspect 12 or 13, wherein the reversible rotary
machine (10) is integrated with the fluid pump (32, 300) into one
body, and the fluid pump (32, 300) is arranged so that it can be
cooled by the gas-phase refrigerant sucked into the reversible
rotary machine (10) at the time of operating the refrigerating
cycle system (10, 11, 13, 14).
[0043] According to this invention, the temperature of the liquid
pump can be decreased when the refrigerating cycle system is
operated.
[0044] The invention described in aspect 15 employs a heat cycle
device according to one of aspects 1 to 11, wherein the rotary
fluid machine includes an expansion machine (10c) for expanding the
refrigerant to obtain power and a compressor (10b) for compressing
the refrigerant when power is supplied to the compressor.
[0045] According to this invention, when both the expansion machine
and the compressor are provided, the refrigerant condensing
operation can be executed by using the compressor function at the
time of operating Rankine cycle system.
[0046] The invention described in aspect 16 employs a heat cycle
device according to aspect 15, wherein the control unit (40)
conducts the refrigerant condensing operation by operating the
compressor (10b) before the expansion machine (10c) is operated and
the operation of the Rankine cycle system (10, 11, 30, 32, 300) is
started.
[0047] According to this invention, it is possible to realize the
refrigerant condensing operation before the operation of Rankine
cycle system is conducted.
[0048] The invention described in aspect 17 employs a heat cycle
device according to aspect 15, wherein the control unit (40)
conducts the refrigerant condensing operation by operating the
compressor (10b) simultaneously when the expansion machine (10c) is
operated and the operation of the Rankine cycle system (10, 11, 30,
32, 300) is started.
[0049] According to this invention, at the time of starting the
Rankine cycle system, the refrigerant condensing operation can be
realized. The refrigerant condensing operation can be executed in
parallel with the operation of the Rankine cycle system.
[0050] The invention described in aspect 18 employs a heat cycle
device comprising: a Rankine cycle system (10, 11, 30, 32, 300)
including a fluid pump (32, 300) for moving refrigerant and also
including a vapor generator (30) for heating the refrigerant, which
has been moved by the fluid pump, by the heat of a heat generating
body (20); a refrigerating cycle system (10, 11, 13, 14) including
an evaporator (14) for evaporating the refrigerant; and a control
unit (40) for conducting the cooling operation for cooling the
fluid pump by operating the refrigerating cycle system (10, 11, 13,
14) at the time of operating the Rankine cycle system (10, 11, 30,
32, 300).
[0051] According to this invention, when the Rankine cycle system
is operated, the liquid pump can be cooled. Therefore, it is
possible to prevent the occurrence of a problem caused by the
gas-phase refrigerant.
[0052] The invention described in aspect 19 employs a heat cycle
device according to aspect 18, wherein the refrigerating cycle
system includes a compressor (10, 10b), and the fluid pump (32,
300) is arranged so that it can be cooled by the gas-phase
refrigerant sucked into the compressor (10, 10b).
[0053] According to this invention, the rotary machine can be
integratedly arranged. Further, in this constitution, it is
possible to cool the liquid pump.
[0054] The invention described in aspect 20 employs a heat cycle
device according to aspect 18 or 19, wherein the control unit (40)
conducts the cooling operation before the operation of the Rankine
cycle system (10, 11, 30, 32, 300) is started and/or while the
Rankine cycle system (10, 11, 30, 32, 300) is being operated.
[0055] According to this invention, the liquid pump can be cooled.
Therefore, it is possible to prevent the occurrence of a problem
caused by the gas-phase refrigerant. When the cooling operation is
executed before the operation of the Rankine cycle system is
started, it is possible to reduce the gas-phase refrigerant in the
liquid pump. Therefore, the occurrence of an incomplete start of
the Rankine cycle system can be suppressed. When the cooling
operation is executed in the beginning of the start of the Rankine
cycle system, that is, when the cooling operation is executed
immediately after the Rankine cycle system is started, it is
possible to suppress the occurrence of an incomplete start of the
Rankine cycle system. When the cooling operation is executed during
the operation of the Rankine cycle system, it is possible to
suppress a deterioration of the efficiency of the Rankine cycle
system.
[0056] The present invention has been devised in order to
accomplish the above objects. The invention described in aspect 21
provides a heat cycle comprising: a refrigerating cycle (10, 11,
13, 14) in which refrigerant of low pressure is evaporated so as to
absorb heat from a low temperature side and the evaporated
gas-phase refrigerant is compressed so as to raise the temperature
and the heat absorbed from the low temperature side is radiated to
a high temperature side so as to condense the gas-phase refrigerant
into the liquid-phase refrigerant; a Rankine cycle (10, 11, 30, 32)
including a vapor generator (30) for generating the gas-phase
refrigerant by heating the liquid-phase refrigerant of the
refrigerating cycle (10, 11, 12, 14) by the waste heat of a heat
generating body (20), also including a liquid-phase pipe (31) for
connecting a liquid-phase takeout section (12, 52) for taking out
the liquid-phase refrigerant from the refrigerating cycle (10, 11,
13, 14) with the vapor generator (30), also including a liquid pump
(32, 300) arranged in the liquid-phase pipe (31), for moving the
liquid-phase refrigerant to the vapor generator (30), also
including an expansion machine (10) for obtaining power by
expanding the gas-phase refrigerant, and also including a condenser
(11) for condensing the gas-phase refrigerant which has been
expanded by the expansion machine (10); a control means (40) for
controlling a state of operation of the refrigerating cycle (10,
11, 13, 14) and also controlling a state of operation of a Rankine
cycle (10, 11, 30, 32, 300); and a change-over means (35a, 36) for
changing over between a case in which a Rankine cycle (10, 11, 30,
32, 300) is operated and a case in which the refrigerating cycle
(10, 11, 13, 14) is operated by a signal sent from the control
means (40), wherein the control means (40) operates Rankine cycle
(10, 11, 30, 32, 300) in such a manner that the refrigerating cycle
(10, 11, 13, 14) is operated by the refrigerant condensing
operation so as to condense the gas-phase refrigerant into the
liquid-phase refrigerant and then the Rankine cycle (10, 11, 30,
32, 300) is operated.
[0057] Due to the foregoing, when the refrigerating cycle (10, 11,
13, 14) is operated before the Rankine cycle (10, 11, 30, 32, 300)
is operated, the gas-phase refrigerant can be condensed to the
liquid-phase refrigerant. As a result, the liquid pump (32, 300)
can positively suck the liquid-phase refrigerant from the
liquid-phase refrigerant takeout section (12, 52) and move it to
the vapor generator 30. Accordingly, the Rankine cycle (10, 11, 30,
32, 300) can be normally started.
[0058] In addition, it is possible to suppress a deterioration of
the operation efficiency of the liquid pump (32, 300) caused by
bubbles in the gas-phase refrigerant. Therefore, it is possible to
prevent the efficiency of Rankine cycle from being
deteriorated.
[0059] The invention described in aspect 22 provides a heat cycle
comprising: a refrigerating cycle (10, 11, 13, 14) in which
refrigerant at low pressure is evaporated so as to absorb heat from
a low temperature side and the evaporated gas-phase refrigerant is
compressed so as to raise the temperature and the heat absorbed
from the low temperature side is radiated to a high temperature
side so as to condense the gas-phase refrigerant into the
liquid-phase refrigerant; a Rankine cycle (10, 11, 30, 32, 300)
including a vapor generator (30) for generating the gas-phase
refrigerant by heating the liquid-phase refrigerant of the
refrigerating cycle (10, 11, 12, 14) by the waste heat of a heat
generating body (20), also including a liquid-phase pipe (31) for
connecting a liquid-phase takeout section (12, 52) for taking out
the liquid-phase refrigerant from the refrigerating cycle (10, 11,
13, 14) with the vapor generator (30), also including a liquid pump
(32, 300) arranged in the liquid-phase pipe (31), for moving the
liquid-phase refrigerant to the vapor generator (30), also
including an expansion machine (10) for obtaining power by
expanding the gas-phase refrigerant, and also including a condenser
(11) for condensing the gas-phase refrigerant which has been
expanded by the expansion machine (10); a control means (40) for
controlling a state of operation of the refrigerating cycle (10,
11, 13, 14) and also controlling a state of operation of the
Rankine cycle (10, 11, 30, 32, 300); and a change-over means (35a,
36) for changing over between the case in which the Rankine cycle
(10, 11, 30, 32, 300) is operated and the case in which the
refrigerating cycle (10, 11, 13, 14) is operated by a signal sent
from the control means (40) wherein, after the Rankine cycle (10,
11, 30, 32, 300) has been operated, the control means (40) judges
whether or not the Rankine cycle (10, 11, 30, 32, 300) is normally
operated, the Rankine cycle (10, 11, 30, 32, 300) is kept being
operated in the case where the operation of the Rankine cycle (10,
11, 30, 32, 300) has been judged to be normal, and in the case
where the operation of the Rankine cycle (10, 11, 30, 32, 300) has
been judged to be not normal, the control means (40) operates in
such a manner that it stops operation of the Rankine cycle (10, 11,
30, 32, 300) and operates the refrigerating cycle (10, 11, 13, 14)
so as to conduct the refrigerant condensing operation for
recovering the liquid-phase refrigerant and Rankine cycle (10, 11,
30, 32, 300) is operated again after the refrigerant condensing
operation.
[0060] Due to the foregoing, and only when Rankine cycle (10, 11,
30, 32, 300) is abnormally operated, the refrigerating cycle (10,
11, 13, 14) is operated and the same effect as that of aspect 1 can
be exhibited. Therefore, it is possible to prevent the occurrence
of a case in which the refrigerating cycle is unnecessarily
operated before the Rankine cycle (10, 11, 30, 32, 300) is
operated.
[0061] The invention described in aspect 23 provides a heat cycle
according to aspect 22, further comprising: an upstream refrigerant
pressure sensor (42) arranged in a portion on the upstream side of
the flow of the refrigerant of the liquid pump (32, 300), the
upstream refrigerant pressure sensor (42) outputting a signal of
the refrigerant pressure to the control means (40); and a
downstream refrigerant pressure sensor (43) arranged in a portion
on the downstream side of the flow of the refrigerant of the liquid
pump (32; 300), the downstream refrigerant pressure sensor (43)
outputting a signal of the refrigerant pressure to the control
means (40) wherein, in the case where a value (P2-P1), which is
obtained when a detected pressure value (P1) of the upstream
refrigerant pressure sensor (42) is subtracted from a detected
pressure value (P2) of the downstream refrigerant pressure sensor
(43), is higher than a predetermined pressure value (P) when the
Rankine cycle (10, 11, 30, 32, 300) is operated, the control means
(40) judges that the Rankine cycle (10, 11, 30, 32, 300) is
normally operated, and in the case where the value (P2-P1), which
is obtained when the detected pressure value (P1) of the upstream
refrigerant pressure sensor (42) is subtracted from the detected
pressure value (P2) of the downstream refrigerant pressure sensor
(43), is not more than the predetermined pressure value (P), the
control means (40) judges that the Rankine cycle (10, 11, 30, 32,
300) is not normally operated.
[0062] In this connection, when the liquid pump (32, 300) is
normally operated, the detected pressure (P1) of the upstream
refrigerant pressure sensor (42) is lower than the detected
pressure (P2) of the downstream refrigerant pressure sensor (43).
Therefore, and specifically when the difference (P2-P1) is not more
than the predetermined pressure (P), it is possible to judge that
the Rankine cycle (10, 11, 30, 32, 300) is not normally
operated.
[0063] According to the invention described in aspect 24, there is
provided a heat cycle according to aspect 22, in which the control
means (40) judges that the Rankine cycle (10, 11, 30, 32, 300) is
normally operated in the case where a work-load of the liquid pump
(32, 300) is more than a predetermined work-load when the Rankine
cycle (10, 11, 30, 32, 300) is operated, and the control means (40)
judges that the Rankine cycle (10, 11, 30, 32, 300) is not normally
operated in the case where the work-load of the liquid pump (32,
300) is not more than the predetermined work-load when the Rankine
cycle (10, 11, 30, 32, 300) is operated.
[0064] The invention described in aspect 25 provides a heat cycle
according to aspect 24, in which the liquid pump is an electric
liquid pump (32) driven by electricity, and the work-load is
representated by electric power consumed by the electrically driven
liquid pump (32). Thus, the work-load can be specifically
calculated.
[0065] According to the invention described in aspect 26, there is
provided a heat cycle according to one of aspects 21 to 25, in
which the expansion machine is a reversible rotary machine (10)
having the function of a compressor for compressing the gas-phase
refrigerant in the refrigerating cycle (10, 11, 13, 14), the
reversible rotary machine (10) is composed being integrated with
the liquid pump (32, 300), and the liquid pump (32, 300) is cooled
by the gas-phase refrigerant sucked into the reversible rotary
machine (10) at the time of operating the refrigerating cycle (10,
11, 13, 14).
[0066] Due to the foregoing, the liquid pump (32, 300) is cooled by
the gas-phase refrigerant of low temperature which is sucked when
the reversible rotary machine (10) functions as a compressor.
Therefore, the liquid-phase refrigerant inside the liquid pump (32,
300) is supercooled and the refrigerant inside the liquid pump (32,
300) can be prevented from evaporating. Accordingly, the
liquid-phase refrigerant can be positively moved to the vapor
generator 30.
[0067] As the liquid pump (32, 300) and the expansion machine (10)
are integrated with each other into one body, the parts composing
the liquid pump (32, 300) and the expansion machine (10) can be
used in common, which can make the fluid machine smaller in
size.
[0068] The invention described in aspect 27 provides a heat cycle
according to one of aspects 21 to 26, further comprising: an air
blowing means (14a) for blowing air conditioned by the
refrigerating cycle (10, 11, 13, 14); and an operation demand means
(41) for demanding the operation of the refrigerating cycle
wherein, in the case of conducting the refrigerant condensing
operation, the control means (40) conducts the refrigerant
condensing operation without operating the air blowing means (14a)
when the operation of the refrigerating cycle (10, 11, 13, 14) is
not demanded by the operation demand means (41).
[0069] Due to the foregoing, in the refrigerant condensing
operation, in which the refrigerating cycle (10, 11, 13, 14) is
operated even when an operator of the heat cycle do not demand the
operation of the refrigerating cycle (10, 11, 13, 14), a blast of
air, the temperature and humidity of which are adjusted, is not
sent. Therefore, the refrigerant condensing operation can be
conducted without causing discomfort to the operator. In this
connection, in the present invention, the term air-conditioning
includes temperature adjustment and humidity adjustment.
[0070] The invention described in aspect 28 provides a heat cycle
according to one of aspects 21 to 27, wherein the condenser (11) is
a heat exchanger for condensing the gas-phase refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle further comprises an outside air temperature sensor (45)
for measuring the temperature of the outside air, the control means
(40) determines the continuation time (T21) for continuing the
refrigerant condensing operation, and the continuation time (T21)
is determined on the basis of the outside air temperature.
[0071] In this connection, in the refrigerating cycle, the
condensing temperature and refrigerant pressure, at which the
gas-phase refrigerant is condensed to the liquid-phase refrigerant,
are determined by the outside air temperature. That is, in the case
where the outside air temperature is high, the refrigerant pressure
is increased so as to raise the condensing temperature. On the
other hand, the higher the condensing temperature is, the higher
the temperature the liquid-phase refrigerant is supercooled to.
[0072] Therefore, the control means (40) is made to determine the
continuity time (T21) according to a relation between the outside
air temperature and the period of time in which the liquid-phase
refrigerant is supercooled by the continuous operation of the
refrigerating cycle. As a result, the liquid-phase refrigerant can
be positively cooled. Therefore, the liquid pump (32, 300) can
positively supply the liquid-phase refrigerant to the vapor
generator 30.
[0073] The invention described in aspect 29 provides a heat cycle
according to one of aspects 21 to 27, further comprising a sensor
(46, 47) for measuring a physical value having a correlation with a
temperature of the refrigerant inside the liquid pump (32, 300),
wherein the control means (40) determines the continuation time in
which the refrigerant condensing operation is continued, and the
continuation time is the time from the start of the refrigerant
condensing operation to when the physical value measured by the
sensor (46, 47) becomes the temperature at which the refrigerant
inside the refrigerant pump (32) is supercooled.
[0074] Due to the foregoing, the refrigerant inside the refrigerant
pump (32) is positively put into the liquid-phase. Therefore, the
liquid pump (32, 300) can positively supply the liquid-phase
refrigerant to the vapor generator 30.
[0075] For example, when the refrigerant condensing operation is
continued until the refrigerant temperature inside the refrigerant
pump (32) becomes lower than the minimum refrigerant condensing
temperature which is determined by the minimum outside air
temperature in the heat cycle using environment, the above effect
can be exhibited.
[0076] The invention described in aspect 30 provides a heat-cycle
according to one of aspects 21 to 27, wherein the condenser (11) is
a heat exchanger for condensing the gas-phase refrigerant by
exchanging heat between the outside air and the refrigerant, the
heat cycle further comprises an outside air temperature sensor (45)
for measuring the temperature of the outside air and also comprises
a sensor (46, 47) for measuring a physical value having a
correlation with the temperature of the refrigerant inside the
liquid pump (32, 300), the control means (40) determines the
temperature, at which the refrigerant inside the refrigerant pump
(32) is supercooled by the outside air temperature, and also
determines the continuation time in which the refrigerant
condensing operation is continued, and the continuation time is the
time from the start of the refrigerant condensing operation to when
the physical value measured by the sensor (46, 47) becomes the
temperature at which the refrigerant inside the refrigerant pump
(32) is supercooled.
[0077] Due to the foregoing, the invention provides the same effect
as that of aspect 29 and, further, the temperature to which the
refrigerant inside the liquid pump (32, 300) is supercooled is
determined by the outside air temperature. Therefore, the
continuation time of the refrigerant condensing operation can be
reduced.
[0078] As described in aspect 31, in a heat cycle according to
aspect 29 or 30, the sensor for measuring the physical value may be
a temperature sensor (46) for measuring the temperature of the
housing of the refrigerant pump.
[0079] As described in aspect 32, in a heat cycle according to
aspect 29 or 30, the refrigerating cycle (10, 11, 13, 14) may
include an evaporator (14) for evaporating the refrigerant of low
pressure by exchanging heat between the refrigerant of low pressure
and air, and the sensor for measuring the physical value may be a
temperature sensor (47) for measuring the temperature of air
immediately after heat is exchanged with the refrigerant of low
pressure.
[0080] In this connection, reference numerals in the parentheses
described in each means correspond to the specific means shown in
the embodiment described later.
[0081] These and other objects, features and advantages of the
present invention will be more apparent in light of the detailed
description of exemplary embodiments thereof as illustrated by the
drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0082] FIG. 1 is an overall arrangement view showing the first
embodiment. FIG. 1 is also a schematic illustration for explaining
the prior application.
[0083] FIGS. 2a and 2b are schematic illustrations for explaining a
reversible rotary machine of the first embodiment.
[0084] FIG. 3 is a flow chart showing a control operation of the
electronic control unit of the first embodiment.
[0085] FIG. 4 is a flow chart showing a primary portion of the
control operation of the electronic control unit of the first
embodiment.
[0086] FIG. 5 is an overall arrangement view of the second
embodiment.
[0087] FIG. 6 is a flow chart showing a primary portion of the
control operation of the electronic control unit of the second
embodiment.
[0088] FIG. 7 is a flow chart showing a primary portion of the
control operation of the electronic control unit of the third
embodiment.
[0089] FIG. 8 is an overall arrangement view of the fourth
embodiment.
[0090] FIG. 9 is a flow chart showing a primary portion of the
control operation of the electronic control unit of the fourth
embodiment.
[0091] FIG. 10 is an overall arrangement view of the fifth
embodiment.
[0092] FIG. 11 is a sectional view showing a reversible rotary
machine of the fifth embodiment.
[0093] FIG. 12 is a flow chart showing a primary portion of the
control operation of the electronic control unit of the fifth
embodiment.
[0094] FIG. 13 is an overall arrangement view of the sixth
embodiment.
[0095] FIG. 14 is a flow chart showing a primary portion of the
control operation of the electronic control unit of the sixth
embodiment.
[0096] FIG. 15 is an overall arrangement view of the seventh
embodiment.
[0097] FIG. 16 is an overall arrangement view showing a variation
of the vapor compression type refrigerating machine of the first
embodiment.
[0098] FIG. 17 is an overall arrangement view showing another
variation of the vapor compression type refrigerating machine of
the first embodiment.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0099] In one embodiment of the present invention, at the time of
operating a Rankine cycle system, the refrigerating cycle system is
operated. According to one of the features of the embodiment, in
the refrigerating cycle system, a refrigerant condensing operation
is conducted in which the refrigerant is compressed by a rotary
fluid machine and condensed by a condenser. When this refrigerant
condensing operation is conducted, the liquid-phase refrigerant can
be positively supplied to the Rankine cycle system. The refrigerant
condensing operation can be conducted before the Rankine cycle
system is started, or in the beginning of the starting of the
Rankine cycle system immediately after the start of the Rankine
cycle system or during the operation of the Rankine cycle system.
The refrigerant condensing operation can be started in accordance
with a signal to indicate the start of Rankine cycle system. When
the refrigerant condensing operation is executed before the
operation of Rankine cycle system is started, the liquid-phase
refrigerant can be positively supplied at the time of starting the
Rankine cycle system. When the refrigerant condensing operation is
executed simultaneously when the Rankine cycle system is started or
immediately after the Rankine cycle system is started, the
liquid-phase refrigerant can be positively supplied at the time of
starting the Rankine cycle or in the beginning of starting the
Rankine cycle. When the refrigerant condensing operation is
executed during the operation of the Rankine cycle system, the
liquid-phase refrigerant can be positively supplied during the
operation of the Rankine cycle system. The refrigerant condensing
operation can be started by judging whether or not the liquid-phase
refrigerant needs to be supplied to the Rankine cycle system. For
example, a trial run of the Rankine cycle system is made, and it is
judged from the behavior of the Rankine cycle whether or not the
liquid-phase refrigerant is needed. When it is judged that the
supply of the liquid-phase refrigerant is needed, the refrigerant
condensing operation is started. Alternatively, according to the
accumulation of experiential data, an environmental condition in
which the liquid-phase refrigerant is lacking is set and, when this
condition is satisfied, the refrigerant condensing operation may be
started. The refrigerant condensing operation can be stopped after
it is conducted for a predetermined period of time or after it has
been conducted for a variable period of time. For example, after a
fixed constant period of time has passed, the refrigerant
condensing operation can be stopped. Alternatively, when it is
detected that the state has become a state in which the
liquid-phase refrigerant can be supplied or when it is detected
that the liquid-phase refrigerant is being stably supplied to
Rankine cycle system, the refrigerant condensing operation may be
stopped. The refrigerant condensing operation can be conducted when
the refrigerating cycle system is operated as a cooling device or a
refrigerating device. In this case, a means for increasing the
amount of the liquid-phase refrigerant can be provided. For
example, a means for providing a state in which an air blowing
means for blowing air to the evaporator in the refrigerating cycle
is not operated, can be arranged. Alternatively, a means for
providing a state in which a volume of blast air is suppressed, can
be arranged.
[0100] The rotary fluid machine can be provided by a device having
both the function of an expansion machine and the function of a
compressor. The rotary fluid machine can convert energy between
fluid energy and mechanical energy generated by rotation. When the
rotary fluid machine is rotated, the fluid is compressed from low
pressure to high pressure. When the fluid is moved from the high
pressure side to the low pressure side, rotation is generated. The
rotary fluid machine may be a displacement type machine or
non-displacement type machine. For example, it is possible to use a
reversible fluid machine which can reversibly function as an
expansion machine or a compressor. In this case, the operation of
Rankine cycle system and the operation of the refrigerating cycle
system can be selectively executed. In this constitution, before
the operation of Rankine cycle system, the refrigerant condensing
operation can be executed by the refrigerating cycle system. The
rotary fluid machine can be provided with both the expansion
machine and the compressor. In this case, the expansion machine and
the compressor can be selectively operated. In addition to that,
the expansion machine and the compressor can be simultaneously
operated.
[0101] Another feature will be described below. In the operation of
the refrigerating cycle system, the cooling operation for cooling
the liquid pump is executed. When the liquid pump is cooled, it is
possible to prevent the occurrence of a problem caused by the
existence of the gas-phase refrigerant. The cooling operation can
be executed before the operation of Rankine cycle system is started
and during the operation of Rankine cycle system. When the cooling
operation is executed before the operation of the Rankine cycle
system is started, it is possible to reduce the gas-phase
refrigerant in the liquid pump, and the occurrence of an incomplete
start of Rankine cycle system can be suppressed. When the cooling
operation is executed at the beginning of the start of the Rankine
cycle system immediately after the operation of the Rankine cycle
system is started, it is possible to suppress the occurrence of an
incomplete start of the Rankine cycle system. When the cooling
operation is executed during the operation of the Rankine cycle
system, it is possible to prevent the efficiency of the Rankine
cycle system from deteriorating. The liquid pump composing the
Rankine cycle system can be arranged in the neighborhood of the
suction passage of the compressor composing the refrigerating cycle
system.
First Embodiment
[0102] In this embodiment, the heat cycle of the present invention
is applied to a vapor pressure compression type refrigerating
machine (refrigerating cycle) having a Rankine cycle. FIG. 1 is a
schematic illustration showing a model of this embodiment. The
vapor compression type refrigerating machine having a Rankine cycle
of this embodiment recovers energy from waste heat generated from
the engine 20 which is a heat engine for generating power used for
running a vehicle. At the same time, the vapor compression type
refrigerating machine having a Rankine cycle of this embodiment
utilizes cold heat ("cold", which is similar hereinafter) and hot
heat ("thermal heat", which is similar hereinafter), which is
generated by the vapor compression type refrigerating machine, for
air conditioning of a vehicle room.
[0103] The reversible rotary machine 10 shown in FIG. 1 is a rotary
type fluid machine having both the function of a compressor for
sucking and compressing the refrigerant and the function of an
expansion machine for isentropically expanding superheated vapor to
obtain power. The reversible rotary machine 10 is a rotary type
fluid machine capable of being reversibly operated as an expansion
machine for obtaining power by expanding the refrigerant or
operated as a compressor for compressing the refrigerant when power
is supplied to the machine 10. The reversible rotary machine 10 may
be referred to as a compressor integrated with an expansion
machine.
[0104] The motor generator 10a is operated as a power source for
supplying power (torque) to the reversible rotary machine 10 in the
case where the reversible rotary machine 10 is operated as a
compressor. On the other hand, the motor generator 10a is a
dynamo-electric machine operated as a generator for generating
electric power from the power recovered by the expansion machine,
that is, as a generator for generating electric power by the
reversible rotary machine 10 in the case where the reversible
rotary machine 10 is operated as an expansion machine. In this
connection, the structure of the reversible rotary machine 10 will
be described later.
[0105] The radiator 11 is connected to the discharge side of the
reversible rotary machine 10 when the reversible rotary machine 10
is operated as a compressor, and heat is radiated from the
refrigerant to the outside air. That is, the radiator 11 is a
cooler for cooling the refrigerant by the outside air. The
refrigerant flowing out from the radiator 11 flows into the
gas-liquid separator 12 (receiver) for separating the gas-phase
refrigerant and the liquid-phase refrigerant from each other.
[0106] The decompressor 13 decompresses and expands the
liquid-phase refrigerant which has been separated by the gas-liquid
separator 12. This embodiment adopts a temperature-type expansion
valve which isentropically decomprresses the refrigerant and
controls the degree of opening of the valve so that the degree of
superheat of the refrigerant sucked into the reversible rotary
machine 10 can become a predetermined value when the reversible
rotary machine 10 is operated as a compressor.
[0107] The evaporator 14 is a heat absorber for absorbing heat from
the refrigerant when the refrigerant decompressed by the
decompressor 13 is evaporated. The refrigerant flowing out from the
evaporator 14 flows into the reversible rotary machine 10 again. As
described above, the vapor compression type refrigerating machine
(the refrigerating cycle) to move the heat from the low temperature
side to the high temperature side is composed of the compressor
(the reversible rotary machine 10), the radiator 11, the gas-liquid
separator 12, the decompressor 13 and the evaporator 14. In this
connection, the evaporator 14 is provided with a blower 14a for
sending a blast of air, which has been conditioned when the
refrigerant is evaporated and absorbs heat, into a vehicle room.
This blower 14a is controlled by the electronic control unit
40.
[0108] In this connection, this embodiment includes an engine
cooling circuit for circulating the cooling water to cool the
engine 20 which is a heat generating body. The water pump 22
arranged in the engine cooling circuit circulates the engine
cooling water, and the radiator 23 is a heat exchanger for cooling
the engine cooling water by exchanging heat between the engine
cooling water and the outside air. The bypass circuit 24 is a
detour circuit by which the cooling water can be flown while by
passing the radiator 23, and the thermostat 25 is a flow regulating
valve for adjusting a quantity of cooling water which flows into
the bypass circuit 24, and a quantity of water which flows into the
radiator 23.
[0109] In this connection, the water pump 22 is a mechanical type
pump driven by the power of the engine 20. However, of course, the
water pump 22 may be an electric pump driven by an electric
motor.
[0110] There is provided a vapor generator 30 in a portion on the
downstream side of the refrigerant flow of the engine 20 in the
engine cooling circuit, and in the refrigerant circuit to connect
the reversible rotary machine 10 with the radiator 11 in the
refrigerating cycle. In this vapor generator 30, the refrigerant is
heated when heat is exchanged between the refrigerant flowing in
the refrigerant circuit and the engine cooling water which has
recovered the waste heat from the engine 20.
[0111] The three-way valve 21 arranged in the engine cooling
circuit changes over between a case in which the engine cooling
water flowing out from the engine 20 is circulated in the vapor
generator 30 and a case in which the engine cooling water flowing
out from the engine 20 is not circulated in the vapor generator 30.
In this embodiment, operation of the three-way valve 21 is
controlled by the electronic control unit 40.
[0112] In this connection, the first bypass circuit 31, which is a
liquid-phase pipe, is a refrigerant passage for introducing the
liquid-phase refrigerant, which has been separated by the
gas-liquid separator 12, to the refrigerant inlet and outlet side
of the vapor generator 30 on the radiator 11 side. This first
bypass circuit 31 includes: a liquid pump 32 to circulate the
liquid-phase refrigerant; and a check valve 33a to allow the
refrigerant to flow only onto the vapor generator 30 side from the
gas-liquid separator 12 side. In this connection, in this
embodiment, the liquid pump 32 is an electrically driven pump and
is controlled by the electronic control unit 40.
[0113] The second bypass circuit 34 is a refrigerant passage to
connect the refrigerant outlet side when the reversible rotary
machine 10 is operated as an expansion machine, with the
refrigerant inlet side of the radiator 11. This second bypass
circuit 34 includes a check valve 33b to allow the refrigerant to
flow only onto the refrigerant inlet side of the radiator 11 from
the refrigerant outlet side when the reversible rotary machine 10
is operated as an expansion machine.
[0114] In this connection, the check valve 33c allows the
refrigerant to flow only from the refrigerant outlet side of the
evaporator 14 to the suction side of the compressor 10. The opening
and closing valve 35a arranged between the vapor generator 30 and
the radiator 11 is opened and closed under the control of the
electronic control unit 40. The control valve 36 functions as a
discharge valve when the reversible rotary machine 10 is operated
as a compressor, that is, the control valve 36 functions as a check
valve to allow the refrigerant only to flow onto the vapor
generator 30 side from the reversible rotary machine 10 side. When
the reversible rotary machine 10 is operated as an expansion
machine, the control valve 36 is opened. Operation of this control
valve 36 is controlled by the electronic control unit 40. As
described above, a Rankine cycle is composed in which the
refrigerant flows in the reversible rotary machine 10, the
condenser 11, the gas-liquid separator 12 and the liquid pump
32.
[0115] The electronic control unit 40 includes an input section
into which the detection temperature T.sub.w of the water
temperature sensor 44 for detecting the temperature of the engine
cooling water after the engine cooling water absorbed heat from the
engine 20, the air conditioner operation signal (A/C operation
demanding signal) sent from the electronic control unit 41 for an
air-conditioner, the detection pressure P1 of the upstream
refrigerant pressure sensor 42 for detecting the pressure on the
upstream side of the liquid pump 32 and the detection pressure P2
of the downstream refrigerant pressure sensor 43 for detecting the
pressure on the downstream side of the liquid pump 32 are
inputted.
[0116] The electronic control unit 40 controls the operations of
the control valve 36, the liquid pump 32 and the three-way valve 21
according to the previously stored program on the basis of the
detection temperature of the water temperature sensor 44, that is,
on the basis of the waste heat temperature T.sub.w and also on the
basis of presence or absence of A/C operation demanding signal.
[0117] The structure and operation of the reversible rotary machine
10 will be briefly explained as follows.
[0118] FIG. 2a is a view showing a case in which the reversible
rotary machine 10 is operated as a compressor, and FIG. 2b is a
view showing a case in which the reversible rotary machine 10 is
operated as an expansion machine. In this embodiment, the
reversible rotary machine 10 is composed of a well-known vane-type
fluid machine.
[0119] In the case where the reversible rotary machine 10 is
operated as a compressor, the rotor 10b is rotated by the motor
generator 10a so that the refrigerant can be sucked and compressed.
At the same time, the discharged refrigerant of high pressure is
prevented from flowing backward onto the rotor 10b side by the
control valve 36.
[0120] In the case where the reversible rotary machine 10 is
operated as an expansion machine, the control valve 36 is opened
and superheated vapor generated by the vapor generator 30 is
introduced into the reversible rotary machine 10, so that the rotor
10b can be rotated and thermal energy can be converted into
mechanical energy.
[0121] Next, operation of the vapor compression type refrigerating
machine (the air conditioner) having a Rankine cycle according to
this embodiment will be described below. In the vapor compression
type refrigerating machine provided with Rankine cycle relating to
this embodiment, the operation mode is controlled being changed
over by the control means 40 according to the presence or absence
of the A/C operation demanding signal and the waste heat
temperature T.sub.w. First, the air conditioning operation mode and
the waste heat recovering operation mode will be explained as
follows.
[0122] 1. Air Conditioning Operation Mode
[0123] In this air conditioning operation mode, while the
evaporator 14 is exhibiting a refrigerating capacity, the
refrigerant is cooled by the radiator 11. In this connection, in
this embodiment, the vapor compression type refrigerating machine
is operated only for the cooling operation and the dehumidifying
operation in which the cold heat generated by the vapor compression
type refrigerating machine is utilized, that is, the heat absorbing
action is utilized. The vapor compression type refrigerating
machine is not operated for the heating operation, in which the hot
heat generated by the radiator 11 is utilized. However, even at the
time of heating operation, the operation of the vapor compression
type refrigerating machine is the same as that of the cooling
operation and the dehumidifying operation.
[0124] Specifically, the operation is conducted as follows. Under
the condition that the liquid pump 32 is stopped, the opening and
closing valve 35a is opened and the control valve 36 is made to
function as a discharge valve, the motor generator 10a is energized
so as to rotate the rotor 10b, and the three-way valve 21 is
operated as shown by the broken line in FIG. 1, so that the cooling
water is circulated while bypassing the vapor generator 30.
[0125] Due to the foregoing, the refrigerant circulates in the
order of the reversible rotary machine (compressor) 10.fwdarw.the
vapor generator 30.fwdarw.the radiator 11.fwdarw.the gas-liquid
separator 12.fwdarw.the decompressor 13.fwdarw.the evaporator
14.fwdarw.the reversible rotary machine (compressor) 10. In this
connection, as the engine cooling water is not circulated in the
vapor generator 30, the refrigerant is not heated by the vapor
generator 30, and the vapor generator 30 functions only as a
refrigerant passage.
[0126] Accordingly, the refrigerant of low pressure, which has been
decompressed by the decompressor 13, absorbs heat from the air
blowing out into the vehicle room by the blower 14a, and the thus
evaporated gas-phase refrigerant is compressed by the reversible
rotary machine 10 and the temperature of the refrigerant is raised.
The refrigerant of high temperature is cooled and condensed by the
outside air in the radiator 11.
[0127] In this connection, in the present embodiment, the
refrigerant is alternate fleon (HFC-134a). However, as long as the
refrigerant can be liquidized on the high pressure side, the
refrigerant is not limited to HFC-134a.
[0128] 2. Waste Heat Recovering Operation Mode
[0129] In this operation mode, the air conditioner, that is, the
reversible rotary machine 10 is stopped and the waste heat of the
engine 20 is recovered so that it can be utilized as usable
energy.
[0130] Specifically, the liquid pump 32 is operated under the
condition that the opening and closing valve 35a is closed and that
the control valve 36 is open, and the three-way valve 21 is
operated as shown by the solid line in FIG. 1, so that the engine
cooling water flowing out from the engine 20 is circulated in the
vapor generator 30.
[0131] Due to the foregoing, the refrigerant circulates in the
order to the gas-liquid separator 12.fwdarw.the first bypass
circuit 31.fwdarw.the vapor generator 30.fwdarw.the reversible
rotary machine (expansion machine) 10.fwdarw.the second bypass
circuit 34.fwdarw.the radiator 11.fwdarw.the gas-liquid separator
12.
[0132] Accordingly, the superheated vapor heated by the vapor
generator 30 flows into the reversible rotary machine 10. While the
vapor refrigerant, which has flowed into the reversible rotary
machine 10, is being isentropically expanded in the reversible
rotary machine 10, the enthalpy is decreased. Therefore, the
reversible rotary machine 10 gives mechanical energy, which
corresponds to decreased enthalpy, to the motor generator 10a.
Electric power generated by the motor generator 10a is stored in a
capacitor or a battery.
[0133] The refrigerant flowing out from the reversible rotary
machine 10 is cooled and condensed by the radiator 11 and stored in
the gas-liquid separator 12. The liquid-phase refrigerant in the
gas-liquid separator 12 is moved to the vapor generator 30 side by
the liquid pump 32.
[0134] As described above, in the waste heat recovering operation
mode, the heat energy, which was lost from the radiator 23 into the
atmosphere as the waste heat, is converted into energy such as
electric power which can be easily utilized. Therefore, the fuel
consumption of the vehicle, that is, the fuel consumption of the
engine 20 can be reduced.
[0135] Further, in the waste heat recovering operation mode,
electric power is generated by the waste heat of the engine 20.
Therefore, it becomes unnecessary to drive a generator such as an
alternator by the engine 20. Accordingly, the fuel consumption of
the engine 20 can be further reduced.
[0136] Next, the control conducted by the electronic control unit
40 will be described as follows. In this embodiment, when an A/C
operation demand signal is sent from the electronic control unit 41
for the air conditioner to the electronic control unit 40, the
compressor 10 integrated with the expansion machine is operated as
a compressor, and the supply of the engine cooling water to the
vapor generator 30 is stopped, so that the priority can be given to
the air conditioning operation mode.
[0137] On the contrary, even when an A/C operation demanding signal
is not sent from the electronic control unit 41 for the air
conditioner to the electronic control unit 40 and when the waste
heat temperature T.sub.w is not less than a predetermined
temperature, the engine cooling water is supplied to the vapor
generator 30, and the reversible rotary machine 10 is operated as
an expansion machine, so that the waste heat recovering operation
mode can be conducted.
[0138] When an A/C operation demanding signal is not sent from the
electronic control unit 41 for the air conditioner to the
electronic control unit 40 and when the waste heat temperature
T.sub.w is not more than a predetermined temperature, under the
condition that the supply of the engine cooling water to the vapor
generator 30 is stopped, an electric current supplied to the
reversible rotary machine 10 is stopped, that is, an electric
current supplied to the motor generator 10a is stopped.
[0139] In this connection, FIG. 3 is an example of the flow chart
showing the controlling operation described above. An outline of
this flow chart will be explained as follows. Simultaneously when
the starting signal to start a vehicle is inputted, the control
program shown in FIG. 3 is started. First, it is judged whether or
not the A/C operation demanding signal has been sent from the
electronic control unit 41 for the air conditioner to the
electronic control unit 40 (S1).
[0140] In the case where the A/C operation demanding signal has
been sent from the electronic control unit 41 for the air
conditioner to the electronic control unit 40, the Rankine cycle is
not operated, and the air conditioning operation mode is executed
(S2).
[0141] On the other hand in the case where the A/C operation
demanding signal has not been sent from the electronic control unit
41 for the air conditioner to the electronic control unit 40, it is
judged whether or not the Rankine cycle is operated according to
the waste heat temperature T.sub.w, that is, it is judged whether
or not the waste heat recovering operation mode is executed (S3).
When the waste heat temperature T.sub.w is not less than the
predetermined temperature, the result of judgment is determined to
be 1, and the Rankine cycle is executed (S4). When the waste heat
temperature T.sub.w is lower than the predetermined temperature,
the result of judgment is determined to be 0, and Rankine cycle is
not executed.
[0142] In this connection, in this embodiment, whether or not the
Rankine cycle is operated according to the waste heat temperature
T.sub.w is judged according to the following predetermined
hysteresis control judgment. When the waste heat temperature
T.sub.w is decreasing, in the case where the waste heat temperature
T.sub.w is not less than the predetermined temperature T.sub.w1,
the result of judgment is determined to be 1 and the Rankine cycle
is executed. In the case where the waste heat temperature T.sub.w
is lower than the predetermined temperature T.sub.w1, the result of
judgment is determined to be 0 and the Rankine cycle is not
executed. When the waste heat temperature T.sub.w is increasing, in
the case where the waste heat temperature T.sub.w is not less than
the predetermined temperature T.sub.w2, which is higher than the
predetermined temperature T.sub.w1 by a predetermined temperature,
the result of judgment is determined to be 1 and the Rankine cycle
is executed. In the case where the waste heat temperature T.sub.w
is lower than the predetermined temperature T.sub.w2, the result of
judgment is determined to be 0 and the Rankine cycle is not
executed. In this way, a predetermined hysteresis control judgment
is conducted.
[0143] Next, referring to FIG. 4, the control in which the
electronic control unit 40 operates the Rankine cycle (S4) will be
explained below in more detail. First, the counter value is reset
(S410). This counter value represents the number of times of the
refrigerant condensing operation (S470 to S500) which will be
described later.
[0144] Next, the timer is reset (S420). This timer stores the
elapsed time (seconds) from the start of the waste heat recovering
operation mode and the air conditioning operation mode. After that,
the electronic control unit 40 sets the liquid pump 32 in motion
and starts the waste heat recovering operation mode (S430). After
that, in S440 and S450, the waste heat recovering operation mode is
operated until the predetermined period of time T.sub.1 (s) (20
seconds in this embodiment) passes.
[0145] After that, the electronic control unit 40 judges whether or
not the pressure difference (P2-P1) between the detection pressure
P1 of the upstream refrigerant pressure sensor 42 and the detection
pressure P2 of the downstream refrigerant pressure sensor 43 is
higher than the setting pressure P (0.3 MPa in this embodiment)
(S460). In the case where the pressure difference (P2-P1) is higher
than the setting pressure P (0.3 MPa in this embodiment), that is,
in the case where the liquid pump 32 gives pressure to the
liquid-phase refrigerant and feeds the refrigerant, the program
proceeds to S5 in FIG. 3.
[0146] In the case where the pressure difference (P2-P1) is lower
than the setting pressure P (0.3 MPa in this embodiment), it is
judged that the liquid pump 32 cannot apply pressure to the
liquid-phase refrigerant. In more detail, it is judged that the
gas-phase refrigerant is mixed in the liquid-phase refrigerant so
that the liquid pump 32 can not apply pressure to the refrigerant.
Therefore, the refrigerant condensing operation (S470 to S500) is
conducted.
[0147] In the refrigerant condensing operation (S470 to S500),
after the stopping of the waste heat recovering operation mode
(S470), the air conditioning operation mode is started (S480).
After that, in S490 and S500, the air conditioning operation mode
is operated until the predetermined period of time T.sub.2 (s) (10
seconds in this embodiment) passes. Then, after the refrigerant
condensing operation has been conducted (S470 to S500), the counter
value is set at (the counter value +1).
[0148] In S520, it is judged whether or not the counter value is
higher than the normal value C (3 times in this embodiment). In the
case where the counter value is not more than the normal value C,
the program returns to S420. In the case where the counter value is
higher than the normal value C, it is judged that Rankine cycle is
in an abnormal state, and operation of the system is stopped.
[0149] In this connection, in the refrigerant condensing operation
(S470 to S500), A/C operation demanding signal is not issued.
Therefore, the blower 14a is not operated. Due to the foregoing,
conditioned air is not blown into the vehicle compartment.
Therefore, the refrigerant condensing operation can be conducted
without a making the passenger uncomfortable.
[0150] Next, the operational effects of the first embodiment will
be enumerated as follows.
[0151] (1) It is possible to prevent bubbles from being mixed into
the liquid-phase pipe 31 and the liquid pump 32. Therefore, the
occurrence of such a problem that the refrigerant can not be
supplied by the liquid pump 32 can be prevented, and the operation
efficiency of the refrigerant can be prevented from being
deteriorated.
[0152] According to this embodiment, in the case where the Rankine
cycle is judged to be in an abnormal state, the air conditioning
operation mode (the refrigerating cycle) is operated, so that the
gas-phase refrigerant can be condensed to the liquid-phase
refrigerant. Further, the refrigerant staying in a complicated
portion of the refrigerant passage in the refrigerating cycle, for
example, the refrigerant staying in the evaporator 14, can be
accumulated in the gas-liquid separator 12 in the form of liquid
refrigerant. After that, by operating the waste heat recovering
operation mode (the Rankine cycle), it is possible to prevent
bubbles from being mixed into the liquid-phase pipe 31, which is
different from the conventional example.
[0153] Accordingly, the liquid pump 32 can positively supply the
liquid-phase refrigerant to the vapor evaporator 30. Accordingly,
the waste heat recovering operation mode (the Rankine cycle) can be
normally started and operated.
[0154] In addition, it is possible to prevent the deterioration of
the operational efficiency of the liquid pump 32 which is caused
when bubbles of the gas-phase refrigerant are mixed into the
liquid-phase pipe 31 and the liquid pump 32. That is, it is
possible to prevent the occurrence of the problem that the
efficiency of the Rankine cycle is deteriorated.
[0155] (2) The control means 40 judges whether the waste heat
recovering operation mode (the Rankine cycle) is normal or
abnormal. In the case where the waste heat recovering operation
mode (the Rankine cycle) is normal, the waste heat recovering
operation mode is continued. In the case where the waste heat
recovering operation mode (the Rankine cycle) is abnormal, the air
conditioning operation mode is operated. Accordingly, it is
possible to prevent the air conditioning mode being unnecessarily
executed.
[0156] (3) As the difference value (P2-P1) between the upstream
side pressure value P1 and the downstream side pressure value P2 of
the liquid pump 32 is compared with the predetermined pressure
value P, it is possible to specifically judge whether the waste
heat recovering operation mode is normal or abnormal.
[0157] In this connection, when the liquid pump 32 is normally
operated, the pressure value P1 detected by the upstream side
refrigerant pressure sensor 42 becomes lower than the pressure
value P2 detected by the downstream side refrigerant pressure
sensor 43. Due to the foregoing, in the case where the difference
value (P2.
[0158] P1) is specifically not more than the predetermined pressure
value P, it is possible to judge that operation of the waste heat
recovering operation mode is abnormal.
[0159] (4) Due to the waste heat recovering operation mode, it is
possible to convert the thermal energy which used to be lost from
the radiator 23 into the atmosphere into energy such as electric
power which can be easily put into practical use. Therefore, it is
possible to reduce the fuel consumption of the vehicle, that is, it
is possible to reduce the fuel consumption of the engine 20. In
more detail, as electric power is generated by the waste heat of
the engine 20, it is possible to reduce the necessity to drive the
generator such as an alternator by the engine 20. Accordingly, the
fuel consumption of the engine 20 can be reduced.
[0160] In this connection, the pressure in the evaporator at the
time of the air conditioning operation mode, that is, the pressure
at the check valve 33c on the evaporator side, which is
approximately 0.3 MPa in this embodiment, is lower than the
pressure at the check valve 33c on the side opposite to the
evaporator, which is approximately 1 MPa in this embodiment, in the
case of recovering energy by the compressor integrated with an
expansion machine. The check valve 33c prevents the refrigerant
from flowing backward to the evaporator, due to this difference in
pressure, at the time of waste heat recovery operation mode.
However, at the time of the waste heat recovery operation mode,
when the radiator and the evaporator are communicated with each
other, the pressure on the evaporator side, that is, the pressure
in the evaporator, which is approximately 0.3 MPa in this
embodiment, may be increased to the pressure of the check valve 33c
on the side opposite to the evaporator, which is approximately 1
MPa in this embodiment, and a malfunction of the check valve 33c
may be caused and the energy recovering operation mode (Rankine
cycle) may fuil.
[0161] Therefore, this embodiment includes a temperature type
expansion valve in which the flow rate adjusting section and the
decompressing section for decompressing the passing refrigerant are
integrated with each other into one body. In this case, the flow
rate adjusting section adjusts the degree of opening of the
refrigerant passage to the shutoff side in the case where the
degree of superheat of the refrigerant at the outlet of the
evaporator is low, and the flow rate adjusting section also adjusts
the degree of opening of the refrigerant passage to the full
opening side in the case where the degree of superheat of the
refrigerant at the outlet of the evaporator is high. This
temperature-type expansion valve functions as a refrigerant shutoff
means for shutting off a flow of the refrigerant into the
evaporator at the time of recovering energy.
[0162] Due to the foregoing, when the compressor stops sucking the
refrigerant, the pressure at the outlet of the evaporator becomes
the saturated pressure of the evaporator temperature in a very
short period of time. At this time, the temperature-type expansion
valve is completely closed and shuts off the refrigerant passage,
and therefore the pressure in the evaporator can be prevented from
increasing in the case where energy is recovered by the energy
recovering machine. Therefore, even when the energy recovering
operation is continuously conducted, the pressure in the evaporator
is not increased so that the pipe can be prevented from being
damaged and a malfunction of the back-flow preventing means can be
prevented.
Second Embodiment
[0163] The constitution of this embodiment is the same as that of
the first embodiment except that the upstream refrigerant pressure
sensor 42 and the downstream refrigerant pressure sensor 43, which
are provided in the first embodiment, are eliminated and, further,
except that an electric current consumed by the liquid pump 32 is
measured by the electronic control unit 40 (shown in FIG. 5). The
control shown in FIG. 3 is the same as that of the first
embodiment.
[0164] However, concerning the detail of S4 of FIG. 3 shown in FIG.
6, the following point is different. Whether or not the Rankine
cycle is normally operated is judged by the electric power
consumption of the liquid pump 32 in this embodiment (S465). That
is, in the case where the liquid pump 32 is normally operated and
the liquid refrigerant can be supplied to the vapor generator 30,
the electric power consumption of the liquid pump 32 is increased
higher than the predetermined value. Therefore, in the case in
which the liquid pump 32 consumes more electric power than the
predetermined electric power consumption W (50 W in this
embodiment), it is judged to be normal. In this connection, the
electric power consumption of the liquid pump 32 is measured by an
electric current sensor in this embodiment.
[0165] On the other hand, in the case where electric power is not
more than the predetermined electric power consumption W, the
program proceeds to S470. An operation to be conducted after that
is the same as that of the first embodiment.
[0166] Due to the foregoing, without providing the upstream
refrigerant pressure sensor 42 and the downstream refrigerant
pressure sensor 43 which are indispensable components for the first
embodiment, it is possible to judge whether the waste heat
recovering operation mode (Rankine cycle) is normal or abnormal.
Therefore, the cost of the overall heat cycle can be reduced.
[0167] In this connection, in this embodiment, the operational
effects (1) to (4) described in the first embodiment can also be
exhibited.
Third Embodiment
[0168] The constitution of this embodiment is the same as that of
the first embodiment, however, a portion of the control in S4
(shown in FIG. 4) is different as shown in FIG. 7. The difference
will be explained in more detail as follows. After the electronic
control unit 40 has started the air conditioning operation mode in
S480, it is judged whether or not the counter value is 0 (S485). In
the case where the counter value is 0, the program proceeds to S495
and S505, and the air conditioning operation mode T3 (s) is
operated until the time T3 (s) passes. The predetermined period of
time of this T3 (s) is shorter than the predetermined period of
time of T2 (s). In this embodiment, the predetermined period of
time of this T3 (s) is 2 seconds. On the other hand, in the case
where the counter value is not 0, the air conditioning operation
mode is continued until the time T2 (s) passes which is 10 seconds
as described before (S490, S500). After that, the program proceeds
to S510. Operation to be conducted after this is the same as that
of the first embodiment.
[0169] In this connection, in the case where the liquid refrigerant
in the gas-liquid separator 12 is a saturated liquid, although the
liquid refrigerant remains in the gas-liquid separator 12,
cavitation is caused in a portion of low pressure in the liquid
pump 32. In this case, when the air conditioning operation mode is
started for a short period of time and pressure in the gas-liquid
separator 12 is raised so as to change the liquid-phase refrigerant
into supercooled liquid, the generation of cavitation can be
reduced.
[0170] In this embodiment, when the counter value is 0, that is,
after it has been judged that the waste heat recovering operation
mode is in an abnormal state (S460 in FIG. 4), the air conditioning
operation mode of the first time is made to be shorter than the air
conditioning operation mode of the second time and after. Due to
the foregoing, without conducting a needless air conditioning
operation mode, the waste heat recovering operation mode can be
quickly put into a normal operation.
[0171] In this connection, the operational effects (1) to (4)
described in the first embodiment can also be exhibited in this
embodiment.
Fourth Embodiment
[0172] In the first, the second and third embodiment, the time
T.sub.2 (S), in which the refrigerant condensing operation is
conducted, is set at a predetermined period of time (10 seconds).
However, in this embodiment, the time T.sub.2 is changed according
to the state of operation of the air conditioning operation mode.
This is a point different from the first, the second and the third
embodiment.
[0173] FIG. 8 is an overall arrangement view showing a vapor
compression type refrigerating machine of this embodiment. The only
different point of this arrangement from the arrangement shown in
FIG. 1 is that the outside air temperature sensor 45 is provided on
the upstream side in the air flowing direction of the condenser 11.
The output value T.sub.am of the outside air temperature sensor 45
is inputted into the electronic control unit 40. In the electronic
control unit 40, the continuation time T.sub.21 (s) to continue the
refrigerant condensing operation is determined according to the
output value T.sub.am of the outside air temperature sensor 45.
[0174] In this embodiment, it is determined so that T.sub.21 can be
extended as the value of T.sub.am is increased. When the outside
temperature is high, the condensing temperature is made high.
Therefore, the temperature at which the liquid-phase refrigerant
can be supercooled is also made high. However, the time to cool the
refrigerant is extended due to the heat capacities of the other
parts composing the heat cycle. Therefore, the relation between the
outside air temperature which was previously measured and the time
at which the liquid-phase refrigerant can be supercooled is stored
in the electronic control unit 40, and T.sub.21 is determined by
the value of T.sub.am.
[0175] The control flow of the electronic control unit 40 of this
embodiment is different as follows. As shown in FIG. 9, with
respect to the first embodiment (shown in FIG. 4), T.sub.am is read
in and T.sub.21 is determined in step S415. In steps S490 and S501,
the air conditioning operation mode is operated until the
continuity time T.sub.21 (s) passes.
[0176] Due to the foregoing, it is possible to ensure the operating
time of the air conditioning operation mode necessary for making
the liquid-phase refrigerant put into the supercooled state.
Therefore, the operating time of the air conditioning operation
mode in the unnecessary refrigerant condensing operation can be
reduced. Further, the operational effects (1) to (4) described in
the first embodiment can be exhibited.
Fifth Embodiment
[0177] In the first to the fourth embodiment, the reversible rotary
machine 10 and the liquid pump 32 are composed separately from each
other. However, in the present invention, as shown in the overall
arrangement view of FIG. 10, the reversible rotary machine 10
includes: an expansion and compression section 100, a generator and
motor section 200, a liquid pump section 300 and a valve mechanism
section 107, etc. which are integrated with each other into one
body. Accordingly, the liquid pump 32 and the control valve 36 are
not independently provided.
[0178] Further, this embodiment is different in the following
points. The reversible rotary machine 10 is attached with a liquid
pump section housing temperature sensor 46 for measuring the
temperature of the pump housing of the liquid pump section 300, and
the output value T.sub.wp of the liquid pump section housing
temperature sensor 46 is inputted into the electronic control unit
40. The other points of the structure of this embodiment are the
same as those of the fourth embodiment.
[0179] Next, referring to the sectional view of FIG. 11, the
reversible rotary machine 10 of this embodiment will be explained
below. The reversible rotary machine 10 includes: a compression and
expansion section 100 for compressing and expanding the gas-phase
refrigerant; a generator and motor section 200 from which electric
energy is outputted when rotary energy is inputted into it and
rotary energy is outputted when electric power is inputted into it;
and a liquid pump section 300 for supplying the liquid-phase
refrigerant to the compression and expansion section 100 with
pressure when the waste heat recovery operation mode is
operated.
[0180] The compression and expansion section 100 has the same
structure as that of the well known scroll-type compression
mechanism. Specifically, the compression and expansion section 100
includes: a stationary scroll (shell) 102 fixed to the stator
housing 230 of the generator and motor section 200 via the middle
housing 101; a movable scroll 103 composing a movable member which
is rotated in the space formed between the middle housing 101 and
the stationary scroll 102; and a valve mechanism section 107 for
opening and closing the communicating passage 105, 106 to
communicate the operation chamber V1 with the high pressure chamber
104.
[0181] In this case, the stationary scroll 102 includes: a
plate-shaped base plate portion 102a; and a spiral tooth portion
102b protruding from the base plate portion 102a to the movable
scroll 103 side. On the other hand, the movable scroll 103a
includes: a spiral tooth portion 103b contacted and meshed with the
tooth portion 102b; and a base plate portion 103a in which the
tooth portion 103b is formed. When the movable scroll 103 is
rotated under the condition that both the tooth portions 102b and
103b are contacted with each other, the volume of the operation
chamber V1, which is composed of both the scrolls 102 and 103, can
be extended and reduced.
[0182] The shaft 108 is pivotally supported by the middle housing
101 via the bearing 108b and is also pivotally supported by the
stator housing 230 via the bearing 108c. One end portion in the
longitudinal direction of the shaft 108 is a crank shaft having an
eccentric portion 108a which is eccentric with respect to the
rotary central axis. The lip seal 108d is a shaft seal device for
preventing the refrigerant from leaking outside the stator housing
230 from a gap between the shaft 108 and the stator housing 230.
The movable scroll 103 is pivotally attached to the eccentric
portion 108a via the bearing 103c.
[0183] The rotation preventing mechanism 109 is composed so that
the movable scroll 103 can be rotated around the eccentric portion
108a by one rotation while the shaft 108 is being rotated by one
rotation. Therefore, when the shaft 108 is rotated, the movable
scroll 103 is revolved round the rotary central axis of the shaft
108 without being rotated. Further, as the operation chamber V1 is
displaced to the central side from the outer diameter side of the
movable scroll 103, the volume of the operation chamber V1 is
reduced. In this connection, a pin-ring-(pin-hole) type
rotation-preventing mechanism 109 is adopted in this
embodiment.
[0184] The communication passage 105 makes the operation chamber
V1, the volume of which becomes minimum at the time of pump mode,
communicate with the high pressure chamber 104, that is, the
communication passage 105 is a discharge port for discharging the
compressed refrigerant. The communication passage 106 makes the
operation chamber V1, the volume of which becomes minimum at the
time of the waste heat recovery operation mode, communicate with
the high pressure chamber 104, that is, the communication passage
106 is a inflow port for guiding the superheated vapor (the
gas-phase refrigerant) of high temperature and high pressure from
the high pressure chamber 104 into the operation chamber V1.
[0185] The high pressure chamber 104 is a space formed in a gap
between the valve mechanism housing 107i and the opposite surface
to the surface on which the tooth portion 102b of the base plate
portion 102a of the movable scroll 102 is composed. The high
pressure chamber 104 has a function of smoothing a pulsation of the
refrigerant discharged from the communicating passage 105 (referred
to as a discharge port 105 hereinafter). In this high pressure
chamber 104, the high pressure port 110, which is connected to the
heater 30 and the radiator 11 side, is provided.
[0186] The low pressure port 111 connected to the evaporator 14 and
the second bypass circuit 34 side is provided in the stator housing
230 and communicated with the outermost diameter portion of the
operation chamber V1 via the inner space 230a in the generator and
motor section 200 and via the middle housing 101.
[0187] Next, the valve mechanism section 107 will be explained in
detail as follows. In the high pressure chamber 104, on the
opposite face to the face on which the tooth portion 102b of the
base plate portion 102a of the movable scroll 102 is composed, the
discharge valve 107a and the valve stopping plate or stopper 107b
are fixed by the bolts 107c. The discharge valve 107a is a
read-valve-shaped check valve for preventing the refrigerant, which
has been discharged from the discharge port 105, from flowing
backward from the high pressure chamber 104 into the operation
chamber V1. The stopper 107b is a valve stopping plate for
regulating the degree of the maximum opening of the discharge valve
107a.
[0188] The spool 107d is a valve body for opening and closing the
communicating passage 106 (referred to as an inflow port 106
hereinafter). The electromagnetic valve 107e is a control valve for
controlling pressure in the back pressure chamber 107f by
controlling the communicating state of the low pressure port 111
side with the back pressure chamber 107f. The spring 107g is an
elastic means for giving an elastic force to the spool 107d so that
the inflow port 106 can be closed. The throttle 107h is a
resistance means for communicating the back pressure chamber 107f
with the high pressure chamber 104 while the throttle 107h has a
predetermined passage resistance. In this connection, the spool
107d, the electromagnetic valve 107e and the spring 107g are
arranged in the valve mechanism housing 107i, and the back pressure
chamber 107f and the throttle 107h are integrated with the valve
mechanism housing 107i into one body.
[0189] When the electromagnetic valve 107e is opened, the pressure
in the back pressure chamber 107f is decreased to be lower than the
pressure in the high pressure chamber 104. Therefore, while the
spool 107d is compressing the spring 107g, it is displaced to the
right in the drawing, so that the inflow port 106 can be opened. In
this connection, a pressure loss in the throttle 107h is very
large. Therefore, the quantity of the refrigerant flowing from the
high pressure chamber 104 into the back pressure chamber 107f is
negligibly small.
[0190] On the contrary, when the electromagnetic valve 107e is
closed, the pressure in the back pressure chamber 107 and the
pressure in the high pressure chamber 104 become equal to each
other. Accordingly, the spool 107d is displaced to the lower side
in the drawing by a force generated by the spring 107g. Therefore,
the inflow port 106 can be closed. Accordingly, a pilot-type
electric opening and closing valve for opening and closing the
inflow port 106 can be composed of the spool 107d, the
electromagnetic valve 107e, the back pressure chamber 107f, the
spring 107g and the throttle 107h etc. In this connection, the
electromagnetic valve 107e is controlled by the electronic control
unit 40. The generator and motor section 200 is a brushless DC
motor having a stator 210 and a rotor 220 rotated on the inner
circumferential side of the stator 210. The stator 210 is a stator
coil in which a coil is wound round an iron core made of magnetic
material such as steel. This stator 210 is fixed in the inner
circumferential section of the stator housing 230.
[0191] The rotor 220 is a magnet rotor in which a permanent magnet
is embedded. On the inner circumferential side of the rotor 220, a
key groove not shown is formed, so that the rotor 220 can be
integrally fixed to the shaft 108 by the key groove.
[0192] The liquid pump section 300 has the same structure as that
of a well-known scroll-type compressor mechanism. Specifically, the
liquid pump section 300 includes: a stationary scroll (shell) 302
fixed to the stator housing 230 of the generator and motor section
200 via the pump housing 301; a movable scroll 303 which is a
movable member rotated in a space formed between the pump housing
301 and the stationary scroll 302; and an operation chamber V2
etc.
[0193] In this case, the stationary scroll 302 includes: a
plate-shaped base plate portion 302a; and a spiral tooth portion
302b protruding from the base plate portion 302a to the movable
scroll 303 side. On the other hand, the movable scroll 303
includes: a spiral tooth portion 303b contacted and meshed with the
tooth portion 302b; and a base plate portion 303a in which the
tooth portion 303b is formed. When the movable scroll 303 is
rotated while both the tooth portions 302b, 303b are in contact
with each other, the operation chamber V2 composed of both the
scrolls 302, 303 is moved from the refrigerant suction port 309
side described later to the refrigerant discharge port 308
side.
[0194] In this connection, the compression ratio of the scroll type
compression mechanism of the liquid pump section 300 is 1.
Therefore, even when the liquid-phase refrigerant is sucked into
the operation chamber V2, the liquid-phase refrigerant is not
compressed. Accordingly, a malfunction of the liquid pump section
300 is not caused by compression of the liquid-phase
refrigerant.
[0195] The pump shaft 304 is pivotally supported by the pump
housing 301 via the bearing 304b. One end portion of the pump shaft
304 in the longitudinal direction is a crank shaft having an
eccentric portion 304a which is eccentric with respect to the
rotary central axis. The pump shaft 304 is connected to an end
portion of the shaft 108, which is a member composing the
compression expansion section 100 and the generator and motor
section 200, on the side opposite to the side on which the
eccentric portion 108a is provided via the one-way clutch 305.
[0196] The one-way clutch 305 is a power transmission means having
a function of transmitting a rotary drive force of the shaft 108 to
the pump shaft 304 only in the waste heat recovery operation mode.
The movable scroll 303 is pivotally connected to the eccentric
portion 304a via the bearing 303c.
[0197] By the rotation preventing mechanism 306, 307, while the
pump shaft 304 is being rotated by one rotation, the movable scroll
303 is rotated round the eccentric portion 304a by one rotation.
Therefore, when the pump shaft 304 is rotated, the movable scroll
303 is revolved round the rotary central axis of the pump shaft 304
without being rotated. Further, the operation chamber V2 is
gradually displaced from the outer diameter side to the central
side. In this connection, the pin-ring-type (pin-hole-type)
mechanism is adopted as the rotation preventing mechanism 306, 307
in this embodiment.
[0198] The refrigerant discharge port 308 is a port from which the
liquid-phase refrigerant is discharged. The refrigerant discharge
port 308 is arranged at a position so that the refrigerant
discharge port 308 can be communicated with the operation chamber
V2 when the operation chamber V2 is moved to the central side of
the liquid pump section 200. The refrigerant suction port 309 is a
port from which the liquid-phase refrigerant is sucked. The
refrigerant suction port 309 is arranged at a position so that the
refrigerant suction port 309 can be communicated with the operation
chamber V2 when the operation chamber V2 is moved to the outer
diameter side of the liquid pump section 200.
[0199] In this connection, the liquid pump section housing
temperature sensor 46 is attached to the pump housing 301, and the
output value T.sub.wp of the liquid pump section housing
temperature sensor 46 is inputted into the electronic control unit
40.
[0200] Next, the operation of the vapor compression type
refrigerating machine having a Rankine cycle of this embodiment
will be described below.
[0201] In the air conditioning operation mode, electric power is
supplied to the generator and motor section 200 of the reversible
rotary machine 10, and the electromagnetic valve 107e is closed and
the three-way valve 21 is changed over as shown by the broken line
in FIG. 10 by the electronic control unit 40.
[0202] When electric power is supplied to the generator and motor
section 200, the rotor 220 and the shaft 108 are rotated integrally
with each other. Due to this rotation, the reversible rotary
machine 10 sucks the gas-phase refrigerant from the low pressure
port 111, compresses the gas-phase refrigerant in the operation
chamber V1 and discharges the gas-phase refrigerant from the high
pressure port 110.
[0203] As the electromagnetic valve 107c is closed, the valve
mechanism section 107 functions as a check valve which only allows
the refrigerant to flow from the reversible rotary machine 10 side
to the vapor generator 30 side. In the air conditioning operation
mode, the one-way clutch 305 does not transmit the rotary drive
force from the shaft 108 to the pump shaft 304. Therefore, the
liquid pump section 300 is not operated.
[0204] Due to the foregoing, in the air conditioning operation
mode, the same refrigerating cycle as that of the first embodiment
can be composed. Further, as the gas-phase refrigerant of low
pressure, which is sucked from the low pressure port 111 of the
compression and expansion section 100, is evaporated in the
evaporator 14 and the temperature of the gas-phase refrigerant is
lowered, when the gas-phase refrigerant passes the inner space
230a, it cools the liquid pump section 300 via the contact face
230b of the liquid pump section 300 of the stator housing 230. Due
to the foregoing, the liquid-phase refrigerant in the liquid pump
section 300 is supercooled. Accordingly, when the waste heat
recovery operation mode is conducted after the air conditioning
operation mode, the liquid pump section 300 can positively supply
the liquid-phase refrigerant to the vapor generator 30.
[0205] Next, in the waste heat recovery operation mode, the
electromagnetic valve 107e is opened, and the three-way valve 21 is
changed over as shown by the solid line in FIG. 10 by the
electronic control unit 40. In this case, although the electronic
control unit 40 does not drive the liquid pump section 300, the
shaft 108 is rotated when the refrigerant is expanded in the
compression and expansion section 100. Accordingly, the rotary
drive force generated at this time is transmitted to the pump shaft
304 via the one-way clutch 305. Therefore, the liquid pump section
300 is operated.
[0206] Due to the foregoing, in the waste heat recovery operation
mode, the same Rankine cycle as that of the first embodiment can be
composed.
[0207] In this connection, in the waste heat recovery operation
mode, the gas-phase refrigerant of low pressure flowing out from
the low pressure port 111 of the compression and expansion section
100 is superheated by the vapor generator 30. Thus, the temperature
of the gas-phase refrigerant is raised high. Therefore, the
following problems may be encountered. As the gas-phase refrigerant
of high temperature also passes through the inner space 230a, the
liquid pump section 300 may be heated by the gas-phase refrigerant
of high temperature via the contact face 230b, and the liquid-phase
refrigerant in the liquid pump section 300 may be heated and
evaporated.
[0208] However, in the waste heat recovery operation mode, the
liquid pump section 300 is operated, and the liquid-phase
refrigerant does not stay in the liquid pump section 300, which is
different from the air conditioning operation mode, but passes
through inside the liquid pump section 300. Therefore, as the
liquid-phase refrigerant is sent to the vapor generator 30 before
it is evaporated, there is no possibility that the refrigerant
inside the liquid pump 300 is evaporated.
[0209] Next, the control operation conducted by the electronic
control unit 40 will be described as follows. In this embodiment,
in the same manner as that of the first embodiment, the electronic
control unit 40 controls the air conditioning operation mode and
the waste heat recovery mode. However, in this embodiment, the
control in the case of operating the Rankine cycle (S4) is
different from that of the first embodiment.
[0210] Specifically, the control is conducted as follows. As shown
in FIG. 12, in step S416, the outside air temperature T.sub.am and
the liquid pump section housing temperature T.sub.wp are read in.
Concerning the operation of the air conditioning operation mode for
conducting the refrigerant condensing operation, as shown in step
S502, the operation is continued until the following relationship
is established (outside air temperature
T.sub.am+.alpha.)>(.beta..times.liquid pump section housing
temperature T.sub.wp).
[0211] In this case, it is possible to grasp the refrigerant
condensing temperature from the outside air temperature T.sub.am.
Since the liquid pump section housing temperature T.sub.wp has a
correlation with the refrigerant temperature in the liquid pump
section 300, it is possible to grasp the refrigerant temperature in
the liquid pump section 300. Further, when the refrigerant
temperature in the liquid pump section 300 is lower than the
refrigerant condensing temperature, it can be judged that the
refrigerant in the liquid pump section 300 is in the supercooled
state.
[0212] Therefore, in this embodiment, the refrigerant condensing
temperature is set aft (outside air temperature T.sub.am+.alpha.),
wherein .alpha.=15.degree. C. in this embodiment, and the
refrigerant condensing operation is conducted until
(.beta..times.liquid pump section housing temperature T.sub.wp) is
decreased to a value not higher than (outside air temperature
T.sub.am+.alpha.). In this case, .beta. is a multiplier for
controlling. Therefore, when the waste heat recovery mode is
operated after the completion of the refrigerant condensing
operation, because the refrigerant inside the liquid pump is in the
supercooled state, the liquid pump section 300 can positively move
the liquid-phase refrigerant to the vapor generator 30.
[0213] Of course, the operation may be conducted as follows. Even
in the case where the outside air temperature T.sub.am is not
measured, the minimum refrigerant condensing temperature (for
example, 10.degree. C.) is previously determined from the minimum
outside air temperature in the environment in which the heat cycle
is used, and the refrigerant condensing operation is conducted
until (.beta..times.liquid pump section housing temperature
T.sub.wp) is decreased to a value not higher than the minimum
refrigerant condensing temperature. Due to the foregoing, it is
possible to eliminate the outside air temperature sensor 45.
Accordingly, the manufacturing cost of the entire heat cycle can be
reduced.
[0214] In this connection, even in this embodiment, the operational
effects (1) to (4) described in the first embodiment can be
exhibited.
Sixth Embodiment
[0215] The above explanations are made into the fifth embodiment in
which the liquid pump section housing temperature sensor 46 for
measuring the pump housing temperature of the liquid pump section
300 is provided. However, in this embodiment, as shown in FIG. 13,
instead of the liquid pump section housing temperature sensor 46,
the evaporator blowout temperature sensor 47 is provided which
measures the temperature of air, the heat of which is exchanged by
the evaporator 14. The other points of the structure are the same
as those of the fifth embodiment.
[0216] The evaporator blowout temperature T.sub.e outputted from
the evaporator blowout temperature sensor 47 is a temperature of
the gas-phase refrigerant of low pressure in the air conditioning
operation mode and a temperature of the gas-phase refrigerant of
low pressure sucked into the reversible rotary machine 10. That is,
the evaporator blowout temperature T.sub.e outputted from the
evaporator blowout temperature sensor 47 is the same temperature as
that of the gas-phase refrigerant to cool the liquid pump section
300. Therefore, the evaporator blowout temperature T.sub.e
outputted from the evaporator blowout temperature sensor 47 has a
correlation with the temperature inside the liquid pump section
300. Accordingly, as shown in steps S417 and S503 shown in FIG. 14,
by using the evaporator blowout temperature T.sub.e instead of the
liquid pump section housing temperature T.sub.wp, the same effect
as that of the fifth embodiment can be obtained.
Seventh Embodiment
[0217] In the first to the sixth embodiment, a reversible rotary
machine 10 is used which functions as a compressor in a
refrigerating cycle and also functions as an expansion machine in a
Rankine cycle. However, in this embodiment, as shown in FIG. 15, a
reversible rotary machine 10 is not used but a compressor 10b
exclusively used for the refrigerating cycle and an expansion
machine 10c exclusively used for Rankine cycle are used so as to
compose the vapor compression type refrigerating machine.
[0218] The compressor 10b has a function of sucking, compressing
and discharging the refrigerant. This compressor 10b is driven by
the engine 20 via the engine side pulley 49, the belt 50 and the
compressor side pulley 51 through the electromagnetic clutch 48,
which is controlled by the electronic control unit 40.
[0219] The structure of the expansion machine 10c is the same as
that of the reversible rotary machine 10 of the fifth embodiment.
In the expansion machine 10c, the expansion section 100, the
generator section 200 and the liquid pump section 300 are
integrated with each other into one body. However, there is no
chance that the expansion machine functions as a compressor.
Therefore, the shaft 108 and the pump shaft 30 are connected with
each other into one body without using a one-way clutch or other
devices.
[0220] When a drive force is transmitted to the compressor by the
electronic control unit 40, the refrigerant is circulated in the
order of the compressor 10b.fwdarw.the radiator 11.fwdarw.the
gas-liquid separator 12.fwdarw.the decompressor 13.fwdarw.the
evaporator 14.fwdarw.the compressor 10b. Due to the foregoing, the
same refrigerating cycle, as that of the first embodiment, can be
composed.
[0221] When the electronic control unit 40 changes over the
three-way valve 21 so that the engine coolant can flow through the
vapor generator 30, the refrigerant, which has been superheated by
the vapor generator 30, expands in the expansion section 100, so
that the generator section 200 and the liquid pump section 300 are
operated. Electric power generated by the generator section 200 is
stored in the battery via the electronic control unit 40. The
liquid pump section 300 further moves the liquid-phase refrigerant
to the vapor generator 30.
[0222] The gas-phase refrigerant flowing out from the expansion
section 100 is circulated in the order of the expansion machine
10c.fwdarw.the radiator 11.fwdarw.the gas-liquid separator
12.fwdarw.the liquid pump section 300.fwdarw.the vapor generator
30.fwdarw.the expansion machine 10c. Due to the foregoing, the same
Rankine cycle as that of the first embodiment can be composed.
[0223] In this case, the high pressure refrigerant discharge port
of the compressor 10b and the low pressure refrigerant flow-out
port of the expansion machine 10c are joined to each other at the
pipe confluence section X. However, as the compressor 10b has a
discharge valve, the refrigerant of low pressure flowing out from
the expansion machine 10c does not flow backward from the high
pressure refrigerant discharge port of compressor 10b into the
compressor 10b. Further, the high pressure refrigerant discharged
from the compressor 10b does not flow backward from the low
pressure refrigerant flow-out port of the expansion machine 10c
into the expansion machine 10c because the check valve 33b is
provided.
[0224] The upstream refrigerant pressure sensor 42, the downstream
refrigerant pressure sensor 43 and the water temperature sensor 44
measure the same physical values as those of the first embodiment,
and the measured values are inputted into the electronic control
unit 40.
[0225] Therefore, according to this embodiment, it is possible to
conduct control in the same manner as that of the first embodiment.
Further, it is possible to conduct control while the refrigerating
cycle and Rankine cycle are independent from each other. That is,
when the refrigerant condensing operation is conducted by the
refrigerating cycle before the waste heat recovery operation mode
is operated by a Rankine cycle, the same effect as that of the
first embodiment can be provided. When the refrigerating cycle is
operated simultaneously when a Rankine cycle is operated, a
sufficiently large quantity of the liquid-phase refrigerant can be
stored in the gas-liquid separator 12 by the refrigerating cycle.
Therefore, no bubbles of the gas-phase refrigerant enter the liquid
pump section 300. Accordingly, the liquid-phase refrigerant can be
positively sent to the vapor generator 30.
Another Embodiment
[0226] The vapor compression type refrigerating machine provided
with Rankine cycle, to which the present invention can be applied,
is not limited to the specific constitution described in the above
embodiments. The vapor compression type refrigerating machine may
have the constitution shown in FIG. 16 in which the evaporator is
used as the condenser in a Rankine cycle and the liquid-phase
refrigerant in the gas-liquid separator 52 in the downstream of the
evaporator 14 is supplied to the vapor generator 30 by the liquid
pump 32. Alternatively, as shown in FIG. 17, the condenser 53 in a
Rankine cycle may be arranged separately from the radiator 11 and
the evaporator 14 arranged in the refrigerating cycle.
[0227] In the control conducted in the third to the seventh
embodiment, the refrigerant pressure sensor 42, 43 of the first
embodiment is used. However, of course, the same effect can be
provided when the control conducted according to the electric power
consumption of the liquid pump of the second embodiment may be
applied. The control of the third embodiment may be applied to the
fourth to the seventh embodiment.
[0228] The heat transfer fin temperature of the evaporator 14 or
the pressure of the low pressure port 111 of the compressor may be
used as physical values having a correlation with the refrigerant
temperature in the liquid pump 32 and the liquid pump section 300
used in the fifth or the sixth embodiment.
[0229] In the embodiments described above, the recovered energy is
stored in a capacitor. However, the recovered energy may be stored
as mechanical energy such as kinetic energy stored by a flywheel or
elastic energy stored by a spring.
[0230] In the above embodiments, the reversible rotary machine 10
is used, that is, the vane type and the scroll type fluid machine
are used as a compressor and an expansion machine. However, it
should be noted that the present invention is not limited to the
above specific embodiment.
[0231] In the above embodiments, when the waste heat recovering
operation mode is controlled, a predetermined hysteresis is
provided. However, it should be noted that the present invention is
not limited to the above specific embodiments.
[0232] It should be noted that the application of the present
invention is not limited to a vehicle.
[0233] The heat generating body is not limited to an internal
combustion engine, that is, the heat generating body can be
variously changed, for example, the heat generating body may be a
fuel cell (FC).
[0234] An opening and closing valve (for example, an
electromagnetic valve for opening and closing when it is energized)
and a capillary tube may be arranged as a refrigerant shutoff
means.
[0235] Due to the foregoing, as the electromagnetic valve
positively shuts off the refrigerant passage, the type of the
decompressing means is not limited to the temperature-type
expansion valve, but an inexpensive capillary tube can be used.
Further, it is possible to make the accumulator cycle, in which an
accumulator is arranged on the downstream side of the refrigerant
flow of the evaporator 14 at the time of air conditioning operation
mode instead of the gas-liquid separator (receiver) arranged on the
downstream side of the refrigerant flow of the radiator 11 at the
time of air conditioning operation mode, exhibit the above
operational effects.
[0236] In the above embodiment, the heater is arranged in series
between the radiator and the compressor integrated with an
expansion machine. However, it is possible to operate Rankine cycle
even when the heater is arranged in parallel between the radiator
and the compressor integrated with an expansion machine.
[0237] Waste heat generated from various devices mounted on a
vehicle, for example, suction heat generated from a turbine, heat
generated from an inverter and waste heat generated from auxiliary
devices may be used as a heat source to heat the refrigerant. Only
one heat source may be used to heat the refrigerant. Alternatively,
a plurality of heat sources may be used to heat the
refrigerant.
[0238] The application of the present invention is not limited to
an air conditioner for vehicle use. It is possible to apply the
present invention to a stationary type refrigerating cycle
(refrigerating machine).
[0239] In the above embodiment, the temperature-type expansion
valve is exemplarily shown in which a flow rate of the refrigerant
is adjusted according to the temperature of a temperature-detecting
cylinder and the temperature at the outlet of the evaporator.
However, the temperature-type expansion valve is not limited to the
above type. For example, it is possible to use an electronic-type
expansion valve having a flow rate adjusting section in which a
thermistor is used for the temperature detecting section and the
degree of opening of a refrigerant passage is adjusted by an
actuator according to the detected temperature.
[0240] As long as it agrees with the concept of the present
invention described in the scope of claim of the patent, any
embodiment may be included in the present invention. It should be
noted that the present invention is not limited to the above
specific embodiments.
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