TECHNICAL FIELD
[0001] The present invention relates to a refrigeration cycle apparatus.
BACKGROUND ART
[0002] As described in Patent Literature 1, there has been known a refrigeration cycle apparatus
including an expander for recovering power from a refrigerant and a sub compressor
integrated with the expander. With reference to FIG. 12, the outline of the refrigeration
cycle apparatus described in Patent Literature 1 is explained.
[0003] As shown in Fig. 12, the refrigeration cycle apparatus 500 described in Patent Literature
1 includes a main compressor 501, a radiator 502, an expander 503, an evaporator 504
and a sub compressor 505. The sub compressor 505 is coupled to the expander 503 by
a shaft 506.
[0004] A refrigerant is compressed in the main compressor 501 so as to be in a high temperature
and high pressure state. The compressed refrigerant is cooled in the radiator 502
and then expanded in the expander 503. The expanded refrigerant changes from a liquid
phase to a gaseous phase in the evaporator 504. The gaseous phase refrigerant is compressed
from a low pressure to an intermediate pressure in the sub compressor 505 and drawn
into the main compressor 501 again.
[0005] The sub compressor 505 is driven by the power that the expander 503 has recovered
from the refrigerant. Since the sub compressor 505 compresses preliminarily the refrigerant
on an upstream of the main compressor 501, the load on a motor 501a of the main compressor
501 is reduced. As a result, the COP (coefficient of performance) of the refrigeration
cycle apparatus 500 is enhanced.
CITATION LIST
Patent Literature
SUMMARY OF INVENTION
Technical Problem
[0007] The refrigeration cycle apparatus 500 shown in FIG. 12 needs two positive displacement
fluid machines, which are the expander 503 and the sub compressor 505. This tends
to increase the cost of the refrigeration cycle apparatus 500 to be higher than that
of a common refrigeration cycle apparatus in which an expansion valve is used. As
described in Patent Literature 2, an expander configured to transfer the recovered
power directly to an compressor also is known, but the expander has a complicated
structure and a considerable cost increase is inevitable.
[0008] The present invention is intended to provide a power recovery type refrigeration
cycle apparatus having a simple structure.
Solution to Problem
[0009] That is, the present invention provides a refrigeration cycle apparatus including:
a compressor for compressing a refrigerant;
a radiator for cooling the refrigerant compressed in the compressor;
a positive displacement fluid machine having a working chamber and an injection port,
and configured to perform (i) a step of drawing, at a first pressure, the refrigerant
cooled in the radiator into the working chamber, (ii) a step of, in the working chamber,
expanding the drawn refrigerant to a second pressure lower than the first pressure
and overexpanding further the refrigerant to a third pressure lower than the second
pressure, (iii) a step of supplying, through the injection port, the refrigerant having
the third pressure to the working chamber so as to mix the supplied refrigerant with
the overexpanded refrigerant, (iv) a step of recompressing, in the working chamber,
the mixed refrigerant to the second pressure by using power recovered from the refrigerant
in the step (ii), and (v) a step of discharging the recompressed refrigerant from
the working chamber;
an evaporator for heating the refrigerant discharged from the positive displacement
fluid machine; and
an injection flow passage through which the refrigerant having the third pressure
is supplied to the injection port of the positive displacement fluid machine.
Advantageous Effects of Invention
[0010] According to the refrigeration cycle apparatus of the present invention, the following
steps are performed in the positive displacement fluid machine. First, the refrigerant
drawn into the working chamber is expanded and overexpanded. Subsequently, the refrigerant
having the same pressure as that of the overexpanded refrigerant is injected into
the working chamber through the injection flow passage so that the injected refrigerant
is mixed with the overexpanded refrigerant in the working chamber. Furthermore, the
mixed refrigerant is recompressed by using the power recovered during the expansion
and overexpansion of the refrigerant. Since the pressure of the refrigerant can be
increased by the recovered power, the load on the compressor is reduced. This improves
the COP of the refrigeration cycle apparatus.
[0011] Particularly, in the present invention, the steps (ii), (iii) and (iv) are performed
as a sequence of steps between a suction process and a discharge process. Thus, in
the present invention, unlike in the refrigeration cycle apparatus described in Patent
Literature 1, the expander and the sub compressor do not need to be provided independently.
Therefore, in the present invention, it is possible to perform each step mentioned
above by using the positive displacement fluid machine having a simpler structure.
Thereby, the production cost of the refrigeration cycle apparatus can be suppressed.
BRIEF DESCRIPTION OF THE DRAWINGS
[0012]
FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to
Embodiment 1 of the present invention.
FIG. 2 is a vertical cross-sectional view of a positive displacement fluid machine
used in the refrigeration cycle apparatus shown in FIG. 1.
FIG. 3A is a transverse cross-sectional view of the positive displacement fluid machine
shown in FIG. 2, taken along the line X-X.
FIG. 3B is a transverse cross-sectional view of the positive displacement fluid machine
shown in FIG. 2, taken along the line Y-Y.
FIG. 4 is a diagram illustrating the operation principle of the positive displacement
fluid machine shown in FIG. 2.
FIG. 5 is a graph showing a relationship between the rotation angle of a shaft and
the volumetric capacity of a working chamber.
FIG. 6 is a graph showing a relationship between the rotation angle of the shaft and
the pressure in the working chamber.
FIG. 7 is a P-V diagram showing a relationship between the pressure in the working
chamber and the volumetric capacity of the working chamber.
FIG. 8 is a configuration diagram of a refrigeration cycle apparatus according to
Embodiment 2 of the present invention.
FIG. 9 is a vertical cross-sectional view of a positive displacement fluid machine
used in the refrigeration cycle apparatus shown in FIG. 8.
FIG. 10 is a transverse cross-sectional view of the positive displacement fluid machine
shown in FIG. 9, taken along the line Z-Z.
FIG. 11 is a diagram illustrating the operation principle of the positive displacement
fluid machine shown in FIG. 10.
FIG. 12 is a configuration diagram of a conventional refrigeration cycle apparatus.
DESCRIPTION OF EMBODIMENTS
[0013] Hereinafter, embodiments of the present invention are described with reference to
the attached drawings. However, the present invention is not limited by the following
embodiments. These embodiments can be combined with each other as long as they do
not depart from the scope of the present invention.
(Embodiment 1)
[0014] FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to
Embodiment 1. The refrigeration cycle apparatus 100 includes a compressor 2, a radiator
3, a positive displacement fluid machine 4, a gas-liquid separator 5, an expansion
valve 6 and an evaporator 7. These components are connected to each other by flow
passages 10a to 10f so as to form a refrigerant circuit 10. Typically, the flow passages
10a to 10f each are composed of a refrigerant pipe. The refrigerant circuit 10 is
filled with a refrigerant, such as hydrofluorocarbon and carbon dioxide, as a working
fluid. The flow passages 10a to 10f may be provided with another component such as
an accumulator.
[0015] The compressor 2 is, for example, a positive displacement compressor such as a rotary
compressor and a scroll compressor. The radiator 3 is a device for removing heat from
the refrigerant compressed in the compressor 2, and typically is composed of a water-refrigerant
heat exchanger or an air-refrigerant heat exchanger. The positive displacement fluid
machine 4 has a function of expanding the refrigerant and a function of compressing
the refrigerant. The gas-liquid separator 5 is a device for separating the refrigerant
discharged from the positive displacement fluid machine 4 into a gas refrigerant and
a liquid refrigerant. The gas-liquid separator 5 is provided with a liquid refrigerant
outlet, a refrigerant inlet and a gas refrigerant outlet. The expansion valve 6 is
a valve with a variable opening, such as an electric expansion valve. The evaporator
7 is a device for providing heat to the liquid refrigerant separated out in the gas-liquid
separator 5, and typically is composed of an air-refrigerant heat exchanger.
[0016] The flow passage 10a connects the compressor 2 to the radiator 3 so that the refrigerant
compressed in the compressor 2 is supplied to the radiator 3. The flow passage 10b
connects the radiator 3 to the positive displacement fluid machine 4 so that the refrigerant
that has flowed out of the radiator 3 is supplied to the positive displacement fluid
machine 4. The flow passage 10c connects the positive displacement fluid machine 4
to the gas-liquid separator 5 so that the refrigerant discharged from the positive
displacement fluid machine 4 is supplied to the gas-liquid separator 5. The flow passage
10d connects the gas-liquid separator 5 to the compressor 2 so that the gas refrigerant
separated out in the gas-liquid separator 5 is supplied to the compressor 2. The flow
passage 10e connects the gas-liquid separator 5 to the evaporator 7 so that the liquid
refrigerant separated out in the gas-liquid separator 5 is supplied to the evaporator
7. The flow passage 10f connects the evaporator 7 to the positive displacement fluid
machine 4 so that the gas refrigerant that has flowed out of the evaporator 7 is supplied
(injected) to the positive displacement fluid machine 4. The cycle explained in this
description can be formed of the flow passages 10a to 10f and the components such
as the compressor 2. Hereinafter, the flow passage 10f is referred to as "the injection
flow passage 10f'.
[0017] In the present embodiment, the expansion valve 6 is provided on the flow passage
10e connecting the gas-liquid separator 5 to the evaporator 7. The expansion valve
6 can lower the pressure of the refrigerant that has been separated out in the gas-liquid
separator 5 and that is to be heated in the evaporator 7. Thereby, the refrigerant
that has flowed out of the evaporator 7 can be drawn smoothly into the positive displacement
fluid machine 4 through the injection flow passage 10f.
[0018] The compressor 2 draws the refrigerant and compresses the drawn refrigerant. The
compressed refrigerant is cooled in the radiator 3 while remaining at a high pressure.
The cooled refrigerant is decompressed to an intermediate pressure in the positive
displacement fluid machine 4 to be turned into a gas-liquid two phase. The gas-liquid
two phase refrigerant flows into the gas-liquid separator 5 and is separated into
a gas refrigerant and a liquid refrigerant. The gas refrigerant is drawn into the
compressor 2. The liquid refrigerant is decompressed by the expansion valve 6 and
supplied to the evaporator 7. The refrigerant is heated and evaporated in the evaporator
7. The gas refrigerant that has flowed out of the evaporator 7 is drawn into the positive
displacement fluid machine 4 and compressed preliminarily to an intermediate pressure.
The gas refrigerant that has been compressed to the intermediate pressure passes again
through the gas-liquid separator 5 to be drawn into the compressor 2. The pressure
of the refrigerant drawn into the compressor 2 is increased to an intermediate pressure,
so that the load on the compressor 2 is reduced. Thereby, the COP of the refrigeration
cycle apparatus 100 is improved.
[0019] The cycle specified in the above stages is equivalent to a so-called "ejector cycle".
In the ejector cycle well known to a person skilled in the art, an "ejector", which
is a kind of non-positive-displacement fluid machine, is used. In contrast, the refrigeration
cycle apparatus 100 of the present embodiment can constitute a cycle equivalent to
the ejector cycle by including the positive displacement fluid machine 4.
[0020] FIG. 2 is a vertical cross-sectional view of the positive displacement fluid machine
shown in FIG. 1. FIG. 3A and FIG. 3B are transverse cross-sectional views of the positive
displacement fluid machine, taken along the line X-X and Y-Y, respectively. The positive
displacement fluid machine 4 has a closed casing 23, a shaft 15, an upper bearing
18, a first cylinder 11, a first piston 13, a first vane 20, an intermediate plate
25, a second cylinder 12, a second piston 14, a second vane 21 and a lower bearing
19. The positive displacement fluid machine 4 is constituted as a two-stage rotary
fluid machine. Parts, such as the cylinders, are accommodated in the closed casing
23.
[0021] As shown in Fig. 2, the shaft 15 has a first eccentric portion 15a and a second eccentric
portion 15b. The first eccentric portion 15a and the second eccentric portion 15b
each protrude radially outward. The shaft 15 extends through the first cylinder 11
and the second cylinder 12, and is supported rotatably by the upper bearing 18 and
the lower bearing 19. The rotation axis of the shaft 15 coincides with the respective
centers of the first cylinder 11 and the second cylinder 12. The second cylinder 12
is disposed concentrically with respect to the first cylinder 11, and separated from
the first cylinder 11 by the intermediate plate 25. The first cylinder 11 is closed
by the upper bearing 18 and the intermediate plate 25, and the second cylinder 12
is closed by the intermediate plate 25 and the lower bearing 19.
[0022] As shown in FIG. 3A, the first piston 13 has a ring shape in plan view, and is disposed
inside the first cylinder 11 so as to form a crescent-shaped first space 16 between
itself and the first cylinder 11. Inside the first cylinder 11, the first piston 13
is fitted around the first eccentric portion 15a of the shaft 15. A first vane groove
40 is formed in the first cylinder 11. The first vane 20 is placed slidably in the
first vane groove 40. The first vane 20 partitions the first space 16 along the circumferential
direction of the first piston 13. Thereby, a first suction space 16a and a first discharge
space 16b are formed inside the first cylinder 11.
[0023] As shown in FIG. 3B, the second piston 14 has a ring shape in plan view, and is disposed
inside the second cylinder 12 so as to form a crescent-shaped second space 17 between
itself and the second cylinder 12. Inside the second cylinder 12, the second piston
14 is fitted around the second eccentric portion 15b of the shaft 15. A second vane
groove 41 is formed in the second cylinder 12. The second vane 21 is placed slidably
in the second vane groove 41. The second vane 21 partitions the second space 17 along
the circumferential direction of the second piston 14. Thereby, a second suction space
17a and a second discharge space 17b are formed inside the second cylinder 12.
[0024] The second space 17 has a larger volumetric capacity than that of the first space
16. Specifically, in the present embodiment, the second cylinder 12 has a larger thickness
than that of the first cylinder 11. Furthermore, the second cylinder 12 has a larger
inner diameter than that of the first cylinder 11. The dimensions of each part are
adjusted appropriately so that the second space 17 has a larger volumetric capacity
than that of the first space 16.
[0025] With respect to the rotational direction of the shaft 15, the direction in which
the first eccentric portion 15a protrudes coincides with the direction in which the
second eccentric portion 15b protrudes. With respect to the rotational direction of
the shaft 15, the angular position at which the first vane 20 is disposed coincides
with the angular position at which the second vane 21 is disposed. Thus, the timing
at which the first piston 13 reaches its top dead center coincides with the timing
at which the second piston 14 reaches its top dead center. The phrase "timing at which
the piston reaches its top dead center" refers to the timing at which the vane is
pressed maximally into the vane groove by the piston.
[0026] As shown respectively in FIG. 3A and FIG. 3B, a first spring 42 is disposed behind
the first vane 20 and a second spring 43 is disposed behind the second vane 21. The
first spring 42 and the second spring 43 press the first vane 20 and the second vane
21, respectively, toward the center of the shaft 15. A lubricating oil held in the
closed casing 23 is supplied to the first vane groove 40 and the second vane groove
41. The first piston 13 and the first vane 20 may be formed of a single component,
a so-called swing piston. The first vane 20 may be engaged with the first piston 13.
This is also the case with the second piston 14 and the second vane 21.
[0027] As shown in Fig. 2, the positive displacement fluid machine 4 further has a suction
pipe 22, a suction port 24, a discharge pipe 26, a discharge port 27, an injection
port 30 and an injection suction pipe 29. The refrigerant can be supplied to the first
space 16 (specifically, the first suction space 16a) through the suction port 24.
The refrigerant can be discharged from the second space 17 (specifically, the second
discharge space 17b) through the discharge port 27. The suction pipe 22 and the discharge
pipe 26 are connected to the suction port 24 and the discharge port 27, respectively.
The suction pipe 22 constitutes a part of the flow passage 10b in the refrigerant
circuit 10 (FIG. 1). The discharge pipe 26 constitutes a part of the flow passage
10c in the refrigerant circuit 10. The discharge port 27 is provided with a discharge
valve 28 (a check valve) for preventing backflow of the refrigerant from the flow
passage 10c to the second discharge space 17b. Typically, the discharge valve 28 is
a reed valve made of a metal thin plate. The discharge valve 28 is opened when the
pressure in the second discharge space 17b exceeds the pressure in the discharge pipe
26 (the pressure in the flow passage 10c). When the pressure in the second discharge
space 17b is equal to or lower than the pressure in the discharge pipe 26, the discharge
valve 28 is closed.
[0028] The suction port 24 and the discharge port 27 are formed in the upper bearing 18
and the lower bearing 19, respectively. However, the suction port 24 may be formed
in the first cylinder 11 and the discharge port 19 may be formed in the second cylinder
12.
[0029] The intermediate plate 25 is provided with a communication hole 25a (a communication
flow passage). The communication hole 25a extends through the intermediate plate 25
in the thickness direction. The first discharge space 16b of the first cylinder 11
is in communication with the second suction space 17a of the second cylinder 12 through
the communication hole 25a. Thereby, the first discharge space 16b, the communication
hole 25a and the second suction space 17a can function as one working chamber. Since
the volumetric capacity of the second space 17 is larger than the volumetric capacity
of the first space 16, the refrigerant confined in the first discharge space 16b,
the communication hole 25a and the second suction space 17a expands while rotating
the shaft 15.
[0030] In the positive displacement fluid machine 4, the "working chamber" is formed of
the first space 16, the second space 17 and the communication hole 25a. The working
chamber increases its volumetric capacity to expand the refrigerant and reduces its
volumetric capacity to compress the refrigerant. Specifically, the first suction space
16a functions as a working chamber into which the refrigerant is drawn. The first
discharge space 16b, the communication hole 25a and the second suction space 17a function
as a working chamber in which the refrigerant is expanded and overexpanded. The second
discharge space 17b functions as a working chamber in which the refrigerant is recompressed
and from which the refrigerant is discharged.
[0031] Particularly, in the present embodiment, the ratio (V2/V1) of a volumetric capacity
V2 of the second space 17 to a volumetric capacity V1 of the first space 16 is adjusted
to a value that allows the refrigerant drawn into the positive displacement fluid
machine 4 to be expanded and overexpanded in the working chamber formed of the first
discharge space 16b, the communication hole 25a and the second suction space 17a.
That is, the volumetric capacity V2 is far larger than the volumetric capacity V1.
Specifically, the volumetric capacity ratio (V2/V1) is set to be almost equal to the
ratio (V
SEP/V
GC) of a volumetric flow rate V
SEP of the refrigerant at the inlet of the gas-liquid separator 5 to a volumetric flow
rate V
GC of the refrigerant at an outlet of the radiator 3.
[0032] The injection port 30 is formed at a position that allows the refrigerant to be supplied
to the second suction space 17a through the injection port 30. Specifically, the injection
port 30 is formed in the second cylinder 12. The injection port 30 is provided with
a check valve 31 for preventing backflow of the refrigerant from the second suction
space 17a or the second discharge space 17b to the injection flow passage 10f. Typically,
the check valve 31 is a reed valve made of a metal thin plate.
[0033] Specifically, the second cylinder 12 is provided with a recessed portion 30a facing
the second space 17. The injection port 30 opens into the recessed portion 30a. The
check valve 31 is fixed to the recessed portion 30a so as to open and close the injection
port 30. The check valve 31 is opened when the pressure in the second suction space
17a falls below the pressure in the injection suction pipe 29 (the pressure in the
injection flow passage 10f). The check valve 31 is closed when the pressure in the
second suction space 17a is equal to or higher than the pressure in the injection
suction pipe 29.
[0034] In the present embodiment, the position where the second vane 21 is disposed (the
position of the second vane groove 41), with respect to the rotational direction of
the shaft 15, is defined as a "reference position" having an angle of 0 degrees. Since
the position at which the first vane 20 is disposed coincides with the position at
which the second vane 21 is disposed, the position at which the first vane 20 is disposed
also coincides with the reference position. The injection port 30 is provided at a
position in the range of, for example, 45 to 135 degrees with respect to the rotational
direction of the shaft 15. By providing the injection port 30 at a position in such
a range, it is possible to prevent the high pressure refrigerant from flowing from
the suction port 24 directly to the injection port 30 through a gap at the check valve
31. Moreover, it is possible to prevent the recovered power from decreasing due to
expansion of the refrigerant in the recessed portion 30a. This is because when the
high pressure drawn refrigerant enters into the recessed portion 30a that is a dead
volume and is expanded in the recessed portion 30a, power cannot be recovered from
the refrigerant expanded in the recessed portion 30a.
[0035] The suction port 24 is provided at a position in the range of, for example, 0 to
40 degrees. The communication hole 25a is provided at a position in the range of,
for example, 0 to 40 degrees when viewed from the second cylinder 12 side. The discharge
port 27 is provided at a position in the range of, for example, 320 to 360 degrees.
[0036] As can be understood from the positional relationship among the suction port 24,
the communication hole 25a and the injection port 30, the injection port 30 is provided
at a position that does not allow the injection port 30 to be in communication with
the suction port 24 through the working chamber (the first space 16, the communication
hole 25a and the second space 17). Such a configuration prevents the recovered power
from decreasing due to the expansion of the refrigerant in the recessed portion 30a.
[0037] The opening area of the suction port 24, the opening area of the injection port 30
and the opening area of the discharge port 27 should be set appropriately taking into
account the flow rate (volumetric flow rate) of the refrigerant passing through each
of these ports. In the refrigeration cycle apparatus 100, the refrigerant flowing
through the injection flow passage 10f has a very high volumetric flow rate. That
is, the refrigerant passing through the injection port 30 has a very high volumetric
flow rate. In contrast, the refrigerant passing through the suction port 24 has a
relatively low volumetric flow rate because it is in a liquid phase (chlorofluorocarbon
alternative) or in a supercritical state (CO
2). Therefore, it is desirable that the opening area of the injection port 30 is larger
than that of the suction port 24, from the viewpoint of reducing the pressure loss.
[0038] Next, the operation of the positive displacement fluid machine is described in detail
with reference to FIGs. 4 to 7. FIG. 4 is an a diagram illustrating the operation
principle of the positive displacement fluid machine. The upper left diagram, upper
right diagram, lower right diagram and lower left diagram in FIG. 4 each show the
positions of the first piston 13 and the second piston 14 when the shaft 15 is rotated
90 degrees each. FIG. 5 is a graph showing a relationship between the rotation angle
of the shaft from the reference position and the volumetric capacity of the working
chamber. FIG. 6 is a graph showing a relationship between the rotation angle of the
shaft from the reference position and the pressure in the working chamber. FIG. 7
is a graph showing a relationship between the pressure in the working chamber and
the volumetric capacity of the working chamber (between the pressure of the refrigerant
and the volume of the refrigerant).
[0039] As shown in the upper left diagram and the upper right diagram in FIG. 4, in the
first cylinder 11, the first suction space 16a is newly generated adjacent to the
suction port 24 when the shaft 15 rotates from the position of 0 degrees to the position
of 90 degrees. Thereby, the refrigerant cooled in the radiator 3 is drawn into the
first suction space 16a through the suction port 24 (suction process). As the shaft
15 rotates, the volumetric capacity of the first suction space 16a increases. When
the shaft 15 rotates 360 degrees, the volumetric capacity of the first suction space
16a reaches to its maximum capacity (= the volumetric capacity of the first space
16). Thereby, the suction process is completed.
[0040] In FIG. 5, the line AB indicates the change in the volumetric capacity of the first
suction space 16a during the suction process. The suction process is completed at
the point B. The volumetric capacity V1 at the point B corresponds to the volumetric
capacity of the first space 16 of the first cylinder 11. In FIG. 6, the line AB indicates
the suction process. The refrigerant drawn into the first suction space 16a during
the suction process is the refrigerant that has been cooled in the radiator 3 while
maintaining a high pressure, and the refrigerant has a suction pressure P1 (a first
pressure).
[0041] Next, as shown in the upper left diagram and the upper right diagram in FIG. 4, the
first suction space 16a changes into the first discharge space 16b when the shaft
15 rotates from the position of 360 degrees to the position of 450 degrees. In the
second cylinder 12, the second suction space 17a is newly generated adjacent to the
communication hole 25a. The first discharge space 16b is in communication with the
second suction space 17a through the communication hole 25a. The first discharge space
16b, the communication hole 25a and the second suction space 17a form one working
chamber that is in communication neither with the suction port 24 nor with the discharge
port 27. As the shaft 15 rotates, the refrigerant is expanded to a discharge pressure
P2 (a second pressure) in the working chamber formed of the first discharge space
16b, the communication hole 25a and the second suction space 17a (expansion process).
[0042] The amount of increase in the volumetric capacity of the second suction space 17a
is significantly larger than the amount of decrease in the volumetric capacity of
the first discharge space 16b, when the shaft 15 rotates only an unit angle. Thus,
the refrigerant is expanded rapidly, and the pressure of the refrigerant falls below
the discharge pressure P2 when the shaft 15 occupies the position of 450 degrees.
As the shaft 15 rotates, the refrigerant is overexpanded to a pressure P3 (a third
pressure) that is lower than the discharge pressure P2 (overexpansion process).
[0043] In the expansion process and the overexpansion process, the refrigerant releases
pressure energy. The pressure energy released from the refrigerant is converted into
a torque of the shaft 15 via the pistons 13 and 14. That is, the positive displacement
fluid machine 4 recovers power from the refrigerant.
[0044] On the other hand, when the rotation angle of the shaft 15 exceeds 450 degrees, the
refrigerant can be supplied to the second suction space 17a through the injection
port 30. When the overexpansion of the refrigerant proceeds and the pressure in the
second suction space 17a falls below the pressure in the injection suction pipe 29,
that is, the evaporating pressure in the evaporator 7, the overexpansion of the refrigerant
stops. At the same time, the refrigerant having the pressure P3 is supplied to the
second suction space 17a through the injection port 30. In the second suction space
17a, the supplied refrigerant is mixed with the overexpanded refrigerant (injection
process).
[0045] Thereafter, as shown in the lower right diagram and the lower left diagram in FIG.
4, the refrigerant having the pressure P3 continues being supplied to the second suction
space 17a through the injection port 30 until the rotation angle of the shaft 15 reaches
720 degrees. As shown in the upper left diagram in FIG. 4, when the shaft 15 rotates
to the position of 720 degrees, the volumetric capacity of the second suction space
17a reaches its maximum capacity (= the volumetric capacity of the second space 17).
Thereby, the injection process is completed.
[0046] In FIG. 5, the dashed line BI indicates the change in the volumetric capacity of
the first discharge space 16b during the expansion process, the overexpansion process
and the injection process. The dashed line JE indicates the change in the volumetric
capacity of the second suction space 17a. The line BE indicates the change in the
volumetric capacity of the working chamber formed of the first discharge space 16b,
the communication hole 25a and the second suction space 17a. The expansion process,
the overexpansion process and the injection process are completed at the point E.
The volumetric capacity V2 at the point E corresponds to the volumetric capacity of
the second space 17 of the second cylinder 12.
[0047] In FIG. 6, the lines BC, CD and DE indicate the expansion process, the overexpansion
process and the injection process, respectively. As the shaft 15 rotates, the pressure
in the working chamber formed of the first discharge space 16b, the communication
hole 25a and the second suction space 17a lowers from the pressure P1 observed at
the start of the expansion process. As mentioned above, the ratio (V2/V1) of the volumetric
capacity V2 of the second space 17 to the volumetric capacity V1 of the first space
16 is very high. Thus, assuming that the injection port 30 is omitted, the pressure
in the working chamber lowers along the dashed line DH on the extension of the line
BCD even after lowering to the pressure P3 of the refrigerant in the evaporator 7.
However, since the positive displacement fluid machine 4 used in the refrigeration
cycle apparatus 100 of the present embodiment has the injection port 30, the refrigerant
having the pressure P3 that has flowed out of the evaporator 7 is supplied to the
second suction space 17a through the injection port 30 when the pressure in the working
chamber lowers to the pressure P3. Thus, the pressure in the working chamber stops
lowering, and the refrigerant having the pressure P3 continues being supplied to the
working chamber until the volumetric capacity of the working chamber reaches the volumetric
capacity V2 specified at the point E in FIG. 5. Thereby, the expansion process, the
overexpansion process and the injection process are completed.
[0048] Next, as shown in the upper left diagram and the upper right diagram in FIG. 4, the
second suction space 17a changes into the second discharge space 17b when the shaft
15 rotates from the position of 720 degrees to the position of 810 degrees. The discharge
port 27 faces the second discharge space 17b. However, as described with reference
to FIG. 2, the discharge port 27 is provided with the discharge valve 28. Thus, the
refrigerant is compressed in the second discharge space 17b until the pressure in
the second discharge space 17b exceeds the pressure in the discharge pipe 26, that
is, the suction pressure in the compressor 2 (recompression process). The refrigerant
to be compressed in the second discharge space 17b includes a fraction of the refrigerant
drawn into the positive displacement fluid machine 4 through the suction port 24 and
a fraction of the refrigerant drawn into the positive displacement fluid machine 4
through the injection port 30.
[0049] The power recovered from the refrigerant during the expansion process and the overexpansion
process is used to compress the refrigerant during the recompression process. As can
be understood from the upper left diagram and the upper right diagram in FIG. 4, when
the recompression process is performed in the second discharge space 17b, the expansion
process and the overexpansion process are performed in the newly generated second
suction space 17a. The power recovered from the refrigerant during the expansion process
and the overexpansion process is consumed as energy for compressing the refrigerant
during the recompression process.
[0050] In the present embodiment, the expansion process and the overexpansion process continue
from a point of time when the first discharge space 16b is brought into communication
with the second suction space 17a through the communication hole 25a until a point
of time when the pressure in the second suction space 17a becomes equal to the pressure
P3 (the third pressure) in the injection flow passage 10f. The recompression process
continues from a point of time when the communication between the first discharge
space 16b and the second suction space 17a through the communication hole 25a is interrupted
until a point of time when the pressure in the second discharge space 17b becomes
equal to the pressure P2 (the second pressure) in the flow passage 10c. In a period
during which the shaft 15 makes one rotation, at least a part of a period during which
the expansion process and the overexpansion process are performed is overlapped with
a period during which the recompression process is performed. With such a configuration,
unevenness in the torque of the shaft 15 is less likely to occur. This contributes
to stable operation of the positive displacement fluid machine 4.
[0051] When the pressure in the second discharge space 17b exceeds the pressure in the discharge
pipe 26, the discharge valve 28 is opened. Thereby, the refrigerant is discharged
from the second discharge space 17b to the discharge pipe 26 through the discharge
port 27 (discharge process). As the shaft 15 rotates, the volumetric capacity of the
second discharge space 17b decreases, and the second discharge space 17b disappears
when the shaft 15 rotates to the position of 1080 degrees. Thereby, the discharge
process is completed.
[0052] In FIG. 5, the line EG indicates the change in the volumetric capacity of the second
discharge space 17b during the recompression process and the discharge process. In
FIG. 6, the line EF and line FG indicate the recompression process and the discharge
process, respectively. Immediately after the completion of the expansion process and
the overexpansion process, the pressure P3 of the refrigerant is lower than the pressure
P2 in the discharge pipe 26. At this time, the discharge valve 28 is closed. As the
volumetric capacity of the second discharge space 17b decreases, the refrigerant is
recompressed to the pressure P2. Thereafter, the pressure in front of the discharge
valve 28 is balanced with the pressure behind the discharge valve 28, so that the
discharge valve 28 is opened and the refrigerant having the pressure P2 is discharged
from the second discharge space 17b to the discharge pipe 26. The discharge process
is completed at the point G.
[0053] FIG. 7 is a P-V diagram showing a relationship between the pressure in the working
chamber and the volumetric capacity of the working chamber. The line AB indicates
the suction process, the line BC indicates the expansion process, the line CD indicates
the overexpansion process, the line DE indicates the injection process, the line EF
indicates the recompression process, and the line FCG indicates the discharge process.
The energy that the positive displacement fluid machine 4 recovers from the refrigerant
corresponds to the area of the region surrounded by the points A, B, C, D, L and G.
The work necessary to recompress the overexpanded refrigerant corresponds to the area
of the region surrounded by the points L, D, E, F, C and G. The recovered energy,
the work necessary for the recompression, and various losses are balanced with each
other. Thus, the positive displacement fluid machine 4 rotates autonomously without
a motor or the like. Since the region surrounded by the points C, D, L and G is common
between the recovered energy and the work necessary for the recompression, it can
be cancelled. Eventually, the energy corresponding to the area of the region surrounded
by the points A, B,C and G is recovered from the refrigerant, and the work corresponding
to the area of the region surrounded by the points C, D, E and F is performed on the
refrigerant by using the recovered energy.
[0054] As described above, in the present embodiment, the expansion process, the overexpansion
process and the recompression process are performed as a sequence of steps between
the suction process and the discharge process. Thus, in the present embodiment, unlike
in the refrigeration cycle apparatus described in Patent Literature 1, the expander
and the sub compressor do not need to be provided independently and it is possible
to perform each step mentioned above by using the positive displacement fluid machine
4 having a simple structure. The parts count of the positive displacement fluid machine
4 is less than that in the case where the expander and the sub compressor are provided
independently. Therefore, the production cost of the refrigeration cycle apparatus
100 can be suppressed.
[0055] Moreover, since the injection port 30 is provided with the check valve 31, it is
possible to prevent backflow of the refrigerant from the second discharge space 17b
to the injection port 30 during the recompression process and the discharge process.
This contributes to the enhancement in the efficiency of the positive displacement
fluid machine 4. In FIG. 4, the check valve 31 prevents the backflow of the refrigerant
from the second discharge space 17b to the injection port 30 during the period in
which the shaft 15 rotates from the position of 720 degrees to the position of 810
degrees.
[0056] Furthermore, since the discharge port 27 is provided with the discharge valve 28,
the work for recompressing and discharging the refrigerant can be reduced. When the
discharge valve 28 is not provided, backflow of the refrigerant may occur from the
discharge pipe 26 (the flow passage 10c) to the second discharge space 17b at the
moment when the rotation angle of the shaft 15 exceeds 720 degrees and the discharge
port 27 faces the second discharge space 17b. In the case where the backflow of the
refrigerant occurs, the recompression process and the discharge process are indicated
by the line EKFG in FIG. 6 and by the line EKFCG in FIG. 7. That is, the work corresponding
to the area of the region surrounded by the points E, K and F is needed as an extra
work for recompressing and discharging the refrigerant. This drawback can be avoided
by providing the discharge valve 28, and thereby the work for recompressing and discharging
the refrigerant can be reduced and also the efficiency of the positive displacement
fluid machine 4 is enhanced. In addition, explosive sound caused by connecting directly
the suction pipe 26 filled with the refrigerant having the pressure P3 to the second
discharge space 17b filled with the refrigerant having the pressure P2 can be prevented
from occurring. Accordingly, noise and vibration of the positive displacement fluid
machine 4 can be suppressed.
[0057] In the present embodiment, the positive displacement fluid machine 4 has a structure
of a two-stage rotary fluid machine. The expansion process and the overexpansion process
proceed in the working chamber formed of the first discharge space 16b, the communication
hole 25a and the second suction space 17a, and the recompression process and the discharge
process proceed in the second discharge space 17b. That is, the expansion process
and the overexpansion process proceed at the same time with the recompression process
and the discharge process in the positive displacement fluid machine 4. Thus, the
energy recovery from the refrigerant can be performed at the same time with the compression
work to the refrigerant. In the case where the energy recovery is performed at the
same time with the compression work, the change in the rotating speed of the shaft
15 is less than in the case where they are performed alternately. Thereby, it is possible
to operate stably the positive displacement fluid machine 4 and also to reduce the
noise and vibration of the positive displacement fluid machine 4. Moreover, it is
possible to prevent the shaft 15 from slowing down and stopping due to the change
in the rotating speed of the shaft 15 when the circulation amount of the refrigerant
in the refrigerant circuit 10 is small.
[0058] In addition, use of the two-stage rotary fluid machine can provide the following
advantages. That is, it is easy to set the ratio (V2/V1) of the volumetric capacity
V2 of the second space 17 to the volumetric capacity V1 of the first space 16 to be
close to the ratio (V
SEP/V
GC) of the volumetric flow rate V
SEP of the refrigerant at the inlet of the gas-liquid separator 5 to the volumetric flow
rate V
GC of the refrigerant at the outlet of the radiator 3.
[0059] In the present embodiment, the refrigerant to be supplied to the injection port 30
of the positive displacement fluid machine 4 through the injection flow passage 10f
is a gas refrigerant. Specifically, the refrigerant that has received heat from a
low temperature side heat source (air, for example) and evaporated from a liquid to
a gas in the evaporator 7 is injected into the positive displacement fluid machine
4. Since the work to compress, in the positive displacement fluid machine 4, the refrigerant
(liquid refrigerant) making no contribution to the thermal energy absorption from
the low temperature side heat source is reduced, the COP of the refrigeration cycle
apparatus 100 is enhanced. Therefore, it is preferable to regulate the opening of
the expansion valve 6 (the expansion valve 45 in Embodiment 2) so that the refrigerant
having a dryness of 1.0 or the overheated refrigerant (that is, only the gas refrigerant)
is supplied to the injection port 30.
[0060] The refrigeration cycle apparatus 100 of the present embodiment can be used suitably
in a hot water supply appliance and a hot water heater. For the purposes of the hot
water supply and hot water heating, switching between cooling and heating, as in an
air conditioner, is not necessary. That is, components, such as a four-way valve,
can be omitted and further cost reduction can be expected.
[0061] Use of the refrigeration cycle apparatus 100 in a hot water supply appliance and
a hot water heater provides the following advantages. Usually, the hot water supply
appliance performs a rated operation in the case of reserving hot water in a tank
by using night power. The hot water heater usually performs a continuous operation.
When a certain period of time has elapsed since the starting of the hot water heater,
the load on the hot water heater is stabilized because the temperature in a building
becomes constant. Taking such an operation style into account, the ratio of the volumetric
flow rate of the refrigerant at the inlet of the gas-liquid separator 5 to the volumetric
flow rate of the refrigerant at the outlet of the radiator 3 is almost constant. Thus,
it is easy to make the ratio (V2/V1) of the volumetric capacity V2 of the second space
17 to the volumetric capacity V1 of the first space 16 coincide with the volumetric
flow rate ratio. Thereby, the effect of power recovery can be obtained more sufficiently.
[0062] The high pressure and the low pressure of a supercritical refrigerant typified by
carbon dioxide is different largely in the refrigeration cycle. Specifically, there
is a large difference between the suction pressure P1 and the discharge pressure P2
in the positive displacement fluid machine 4. Accordingly, the power that can be recovered
by the positive displacement fluid machine 4 also is large. Thus, carbon dioxide is
appropriate as the refrigerant for the refrigeration cycle apparatus 100. The type
of the refrigerant is not particularly limited, of course, and a natural refrigerant
other than carbon dioxide, a chlorofluorocarbon alternative such as R410A, and a low
GWP (Global Warming Potential) refrigerant such as R1234yf can be used.
[0063] By using the positive displacement fluid machine 4 in the refrigeration cycle apparatus
100 as a means to recover power from the refrigerant, it is possible to utilize the
recovered power as a part of the compression work. Since the difference between the
suction pressure and the discharge pressure in the compressor 2 is reduced, the load
on the compressor 2 is reduced and the COP of the refrigeration cycle apparatus 100
is improved. It should be noted, however, that the positive displacement fluid machine
4 described in the present embodiment may be usable also in apparatuses other than
the refrigeration cycle apparatus.
(Embodiment 2)
[0064] FIG. 8 is a configuration diagram of a refrigeration cycle apparatus according to
Embodiment 2 of the present invention. The refrigeration cycle apparatus 200 includes
the compressor 2, the radiator 3, a positive displacement fluid machine 44, an expansion
valve 45 (a decompression valve), a first evaporator 46 and a second evaporator 47.
These components are connected to each other by flow passages 50a to 50f so as to
form a refrigerant circuit 50.
[0065] The compressor 2 and the radiator 3 are the same as in Embodiment 1, as can be understood
from the fact that they are indicated by the same reference numerals as those in Embodiment
1, respectvely. The positive displacement fluid machine 44 has the same function as
that of the positive displacement fluid machine 4 described in Embodiment 1, although
having structural differences. The expansion valve 45 is a valve with a variable opening,
such as an electric expansion valve. The first evaporator 46 and the second evaporator
47 each are a device for providing heat to the refrigerant, and typically is composed
of an air-refrigerant heat exchanger.
[0066] The flow passage 50a connects the compressor 2 to the radiator 3 so that the refrigerant
compressed in the compressor 2 is supplied to the radiator 3. The flow passage 50b
connects the radiator 3 to the positive displacement fluid machine 44 so that a part
of the refrigerant that has flowed out of the radiator 3 is supplied to the positive
displacement fluid machine 44. The flow passage 50c connects the positive displacement
fluid machine 44 to the first evaporator 46 so that the refrigerant discharged from
the positive displacement fluid machine 44 is supplied to the first evaporator 46.
The flow passage 50d connects the first evaporator 46 to the compressor 2 so that
the refrigerant that has flowed out of the first evaporator 46 is supplied to the
compressor 2. The flow passage 50e connects the radiator 3 to the second evaporator
47 so that a part of the refrigerant that has flowed out of the radiator 3 is supplied
to the second evaporator 47. Specifically, the flow passage 50e is a flow passage
(branch flow passage) branched from the flow passage 50b, and has an upstream end
connected to the flow passage 50b between the radiator 3 and the positive displacement
fluid machine 44 and a downstream end connected to the second evaporator 47. The expansion
valve 45 is disposed on the flow passage 50e. The refrigerant is decompressed by the
expansion valve 45 and then flows into the second evaporator 47. The flow passage
50f connects the second evaporator 47 to the positive displacement fluid machine 44
so that the gas refrigerant that has flowed out of the second evaporator 47 is supplied
(injected) to the positive displacement fluid machine 44.
[0067] The first evaporator 46 and the second evaporator 47 are disposed on a flow passage
for a heat medium (air, for example) so that the heat medium cooled in the first evaporator
46 is cooled further in the second evaporator 47. The direction indicated by the arrows
in FIG. 8 is the flowing direction of the heat medium. The temperature of the refrigerant
in the first evaporator 46 is higher than that of the refrigerant in the second evaporator
47. Thus, as shown in Fig. 8, in the case where the first evaporator 46 and the second
evaporator 47 are disposed respectively on an upstream and a downstream of the flow
passage for the heat medium, it is almost like the heat medium (air) and the refrigerant
form mutually opposed flows. Thereby, the efficiency of the heat exchange between
the refrigerant and the heat medium in the evaporators 46 and 47 is enhanced. Moreover,
since the pressure of the refrigerant that has flowed out of the second evaporator
47 is increased in the positive displacement fluid machine 44, the COP of the refrigeration
cycle apparatus 200 is enhanced as in Embodiment 1.
[0068] The compressor 2 draws the refrigerant and compresses the drawn refrigerant. The
compressed refrigerant is cooled in the radiator 3 while remaining at a high pressure.
The cooled refrigerant flows into the two flow passages 50b and 50e. Apart of the
cooled refrigerant is drawn into the positive displacement fluid machine 44 through
the flow passage 50b. The refrigerant drawn into the positive displacement fluid machine
44 is decompressed to an intermediate pressure in the positive displacement fluid
machine 44 to be turned into a gas-liquid two phase. The refrigerant discharged from
the positive displacement fluid machine 44 flows into the first evaporator 46 through
the flow passage 50c. The refrigerant that has flowed into the first evaporator 46
is heated in the first evaporator 46, and then drawn into the compressor 2 through
the flow passage 50d. On the other hand, the remainder of the refrigerant cooled in
the radiator 3 is decompressed by the expansion valve 45 to be turned into a gas-liquid
two phase, and then supplied to the second evaporator 47 through the flow passage
50e. The refrigerant that has flowed into the second evaporator 47 is heated in the
second evaporator 47, and then supplied (injected) to the positive displacement fluid
machine 44 through the injection flow passage 50f.
[0069] FIG. 9 is a vertical cross-sectional view of the positive displacement fluid machine
44 shown in FIG. 8. FIG. 10 is a transverse cross-sectional view of the positive displacement
fluid machine, taken along the line Z-Z. The positive displacement fluid machine 44
has a closed casing 59, a shaft 53, an upper bearing 55, a cylinder 51, a piston 52,
a vane 57 and a lower bearing 56. The positive displacement fluid machine 44 is constituted
as a single-stage rotary fluid machine.
[0070] As shown in Fig. 9, the shaft 53 has an eccentric portion 53a protruding radially
outward. The shaft 53 extends through the cylinder 51 and is supported rotatably by
the upper bearing 55 and the lower bearing 56. The rotation axis of the shaft 53 coincides
with the center of the cylinder 51. The cylinder 51 is closed by the upper bearing
55 and the lower bearing 56.
[0071] As shown in FIG. 10, the piston 52 has a ring shape in plan view, and is disposed
inside the cylinder 51 so as to form a crescent-shaped space 54 between itself and
the cylinder 51. Inside the cylinder 51, the piston 52 is fitted around the eccentric
portion 53a of the shaft 53. Avane groove 68 is formed in the cylinder 51. The vane
57 is placed slidably in the vane groove 68. The vane 57 partitions the space 54 along
the circumferential direction of the piston 52. Thereby, a suction space 54a and a
discharge space 54b are formed inside the cylinder 51. A spring 69 is disposed behind
the vane 57. The spring 69 presses the vane 57 toward the center of the shaft 53.
A lubricating oil held in the closed casing 59 is supplied to the vane groove 68.
The piston 52 and the vane 57 may be formed of a single component, a so-called swing
piston. The vane 57 may be engaged with the piston 52.
[0072] As shown in Fig. 9, the positive displacement fluid machine 44 further has a suction
pipe 58, a suction port 60, a discharge pipe 62, a discharge port 63, an injection
port 67 and an injection suction pipe 65. The refrigerant can be supplied to the space
54 (specifically the suction space 54a) through the suction port 60. The refrigerant
can be discharged from the space 54 (specifically the discharge space 54b) through
the discharge port 63. The suction pipe 58 and the discharge pipe 62 are connected
to the suction port 60 and the discharge port 63, respectively. The suction pipe 58
constitutes a part of the flow passage 50b in the refrigerant circuit 50 (FIG. 8).
The discharge pipe 62 constitutes a part of the flow passage 50c in the refrigerant
circuit 50. The injection port 63 is provided with a discharge valve 64 (a check valve)
for preventing backflow of the refrigerant from the flow passage 50c to the discharge
space 54b. Typically, the discharge valve 64 is a reed valve made of a metal thin
plate. When the pressure in the discharge space 54b exceeds the pressure in the discharge
pipe 62 (the pressure in the flow passage 50c), the discharge valve 64 is opened.
When the pressure in the discharge space 54b is equal to or lower than the pressure
in the discharge pipe 62, the discharge valve 64 is closed.
[0073] The suction port 60 and the discharge port 63 are formed in the upper bearing 55
and the lower bearing 56, respectively. However, the suction port 60 and the discharge
port 63 each may be formed in the cylinder 51.
[0074] The positive displacement fluid machine 44 further has a suction mechanism 61 for
controlling the timing at which the refrigerant flows into the space 54 of the cylinder
51 through the suction port 60. In the present embodiment, the suction mechanism 61
is composed of a solenoid valve including a suction valve 61a and a solenoid 61b.
It is possible to control the open/close operation of the suction valve 61a by switching
on and off the voltage applied to the solenoid 61b.
[0075] The injection port 67 is formed in the cylinder 51 so that the refrigerant can be
supplied to the suction space 54a. The injection port 67 is provided with a check
valve 66 for preventing backflow of the refrigerant from the suction space 54a or
the discharge space 54b to the injection flow passage 50f. The detailed structures
of the injection port 67 and the check valve 66 are as described in Embodiment 1.
[0076] In the present embodiment, the position where the vane 57 is disposed (the position
of the vane groove 68), with respect to the rotational direction of the shaft 53,
is defined as a "reference position" having an angle of 0 degrees. The injection port
67 is provided at a position in the range of, for example, 90 to 180 degrees with
respect to the rotational direction of the shaft 53. The suction port 60 and the discharge
port 63 are provided at positions adjacent to the vane 57.
[0077] In the positive displacement fluid machine 44, the suction space 54a functions as
a working chamber into which the refrigerant is drawn and in which the refrigerant
is expanded and overexpanded. The discharge space 54b functions as a working chamber
in which the refrigerant is recompressed and from which refrigerant is discharged.
[0078] Next, the operation of the positive displacement fluid machine is described in detail
with reference to FIG. 6 and FIG. 11. FIG. 11 is a diagram illustrating the operation
principle of the positive displacement fluid machine. The upper left diagram, upper
right diagram, lower right diagram and lower left diagram in FIG. 11 each show the
position of the piston 52 when the shaft 53 is rotated 90 degrees each. In the present
embodiment, the suction valve 61a is opened when the rotation angle of the shaft 53
is in the range of 0 to 90 degrees, and thereafter repeats being opened and closed
in a cycle of 360 degrees.
[0079] As shown in the upper left diagram in FIG. 11, the suction space 54a is newly generated
adjacent to the suction port 60 when the shaft 53 rotates from the position of 0 degrees
to the position of 90 degrees. The refrigerant is drawn into the suction space 54a
through the suction port 60 (suction process). When the shaft 53 rotates from the
position of 0 degrees to the position of about 90 degrees, the suction valve 61a is
closed. Thereby, the suction process is completed. In FIG. 6, the line AB indicates
the suction process.
[0080] When the suction valve 61a is closed, the refrigerant is expanded to the discharge
pressure P2 in the suction space 54a (expansion process). As the shaft 53 rotates,
the refrigerant is overexpanded to the pressure P3 lower than the discharge pressure
P2 (overexpansion process). The positive displacement fluid machine 44 recovers power
from the refrigerant during the expansion process and the overexpansion process. In
FIG. 6, the line BCD indicates the expansion process and the overexpansion process.
[0081] When the rotation angle of the shaft 53 exceeds about 120 degrees, the refrigerant
can be supplied to the suction space 54a through the injection port 67. When the overexpansion
of the refrigerant proceeds and the pressure in the suction space 54a falls below
the pressure in the injection suction pipe 65, that is, the evaporating pressure in
the second evaporator 47, the overexpansion of the refrigerant stops. At the same
time, the refrigerant having the pressure P3 is supplied to the suction space 54a
through the injection port 67. In the suction space 54a, the supplied refrigerant
is mixed with the overexpanded refrigerant (injection process).
[0082] Thereafter, the refrigerant having the pressure P3 continues being supplied to the
suction space 54a through the injection port until the rotation angle of the shaft
53 reaches 360 degrees. As shown in the upper left diagram in FIG. 11, when the shaft
53 rotates to the position of 360 degrees, the volumetric capacity of the suction
space 54a reaches its maximum capacity (= the volumetric capacity of the space 54).
Thereby, the injection process is completed. In FIG. 6, the line DE indicates the
injection process.
[0083] The volumetric capacity V1 of the working chamber (the suction space 54a) when the
suction process is completed is specified by the rotation angle of the shaft 53 at
the moment when the suction valve 61a is closed. In the present embodiment, the ratio
(V2/V1) of the volumetric capacity V2 when the injection process is completed to the
volumetric capacity V1 when the suction process is completed is almost equal to the
ratio (V
EVAN
GC) of a volumetric flow rate V
EVA of the refrigerant at an inlet of the first evaporator 46 to the volumetric flow
rate V
GC of the refrigerant at the outlet of the radiator 3. Also, the volumetric capacity
ratio (V2/V1) is set to be sufficiently higher than the ratio of the specific volume
of the refrigerant that can be calculated from the ratio of the pressure P3 in the
working chamber (the space 54) when the injection process is completed to the pressure
P1 in the working chamber (the space 54) when the suction process is completed.
[0084] Next, as shown in the upper left diagram and the upper right diagram in FIG. 11,
the suction space 54a changes into the discharge space 54b when the shaft 53 rotates
from the position of 360 degrees to the position of 450 degrees. The discharge port
63 faces the discharge space 54b. However, as described with reference to FIG. 9,
the discharge port 63 is provided with the discharge valve 64. Thus, the refrigerant
is compressed in the discharge space 54b until the pressure in the discharge space
54b exceeds the pressure in the discharge pipe 62, that is, the suction pressure in
the compressor 2 (recompression process).
[0085] When the pressure in the discharge space 54b exceeds the pressure in the discharge
pipe 62, the discharge valve 64 is opened. Thereby, the refrigerant is discharged
from the discharge space 54b to the discharge pipe 62 through the discharge port 63
(discharge process). As the shaft 53 rotates, the volumetric capacity of the discharge
space 54b decreases, and the discharge space 54b disappears when the shaft 53 rotates
to the position of 720 degrees. Thereby, the discharge process is completed. In FIG.
6, the line EF and the line FG indicate the recompression process and the discharge
process, respectively.
[0086] With the configuration and processes described above, the same effects can be obtained
also in the present embodiment as those in Embodiment 1. In the present embodiment,
the positive displacement fluid machine 44 has a structure of a single-stage rotary
fluid machine including a single cylinder and a single piston. Thus, in the present
embodiment, it is possible to reduce the parts count of the positive displacement
fluid machine 44, downsize the positive displacement fluid machine 44, and lower the
cost of the refrigeration cycle apparatus 200.
[0087] Instead of the positive displacement fluid machine 44, the positive displacement
fluid machine 4 described in Embodiment 1 may be used in the refrigeration cycle apparatus
200. Likewise, the positive displacement fluid machine 44 may be used in the refrigeration
cycle apparatus 100 in Embodiment 1. Moreover, other types of fluid machines, such
as a scroll type fluid machine, may be used as these positive displacement fluid machines.
INDUSTRIAL APPLICABILITY
[0088] The refrigeration cycle apparatus of the present invention can be used in a hot water
supply appliance, a hot water heater, an air conditioner and the like.
1. A refrigeration cycle apparatus comprising:
a compressor for compressing a refrigerant;
a radiator for cooling the refrigerant compressed in the compressor;
a positive displacement fluid machine having a working chamber and an injection port,
and configured to perform (i) a step of drawing, at a first pressure, the refrigerant
cooled in the radiator into the working chamber, (ii) a step of, in the working chamber,
expanding the drawn refrigerant to a second pressure lower than the first pressure
and overexpanding further the refrigerant to a third pressure lower than the second
pressure, (iii) a step of supplying, through the injection port, the refrigerant having
the third pressure to the working chamber so as to mix the supplied refrigerant with
the overexpanded refrigerant, (iv) a step of recompressing, in the working chamber,
the mixed refrigerant to the second pressure by using power recovered from the refrigerant
in the step (ii), and (v) a step of discharging the recompressed refrigerant from
the working chamber;
an evaporator for heating the refrigerant discharged from the positive displacement
fluid machine; and
an injection flow passage through which the refrigerant having the third pressure
is supplied to the injection port of the positive displacement fluid machine.
2. The refrigeration cycle apparatus according to claim 1, wherein
the positive displacement fluid machine has:
a first cylinder;
a first piston disposed inside the first cylinder so as to form a first space between
itself and the first cylinder;
a first vane partitioning the first space into a first suction space and a first discharge
space;
a second cylinder disposed concentrically with respect to the first cylinder;
a second piston disposed inside the second cylinder so as to form, between itself
and the second cylinder, a second space having a larger volumetric capacity than that
of the first space;
a second vane partitioning the second space into a second suction space and a second
discharge space;
an intermediate plate disposed between the first cylinder and the second cylinder;
a communication flow passage provided in the intermediate plate so as to bring the
first discharge space into communication with the second suction space;
a suction port through which the refrigerant is drawn into the first suction space;
and
a discharge port through which the refrigerant is discharged from the second discharge
space, and
the working chamber is formed of the first space, the second space and the communication
flow passage, and
the injection port is provided at a position that allows the refrigerant to be supplied
to the second suction space through the injection port.
3. The refrigeration cycle apparatus according to claim 2, wherein
the step (ii) continues from a point of time when the first discharge space is brought
into communication with the second suction space through the communication flow passage
until a point of time when a pressure in the second suction space becomes equal to
the third pressure,
the step (iv) continues from a point of time when the communication between the first
discharge space and the second suction space through the communication flow passage
is interrupted until a point of time when the pressure in the second discharge space
becomes equal to the second pressure, and
in a period during which the shaft makes one rotation, at least a part of a period
during which the step (ii) is performed is overlapped with a period during which the
step (iv) is performed.
4. The refrigeration cycle apparatus according any one of Claims 1 to 3, wherein the
injection flow passage connects the evaporator to the positive displacement fluid
machine so that the refrigerant that has flowed out of the evaporator is supplied
to the positive displacement fluid machine as the refrigerant having the third pressure.
5. The refrigeration cycle apparatus according to claim 4, further comprising:
a gas-liquid separator for separating the refrigerant discharged from the positive
displacement fluid machine into a gas refrigerant and a liquid refrigerant;
a flow passage connecting the gas-liquid separator to the compressor so that the gas
refrigerant separated out in the gas-liquid separator is supplied to the compressor;
and
a flow passage connecting the gas-liquid separator to the evaporator so that the liquid
refrigerant separated out in the gas-liquid separator is supplied to the evaporator.
6. The refrigeration cycle apparatus according to claim 5, further comprising a decompression
valve provided on the flow passage connecting the gas-liquid separator to the evaporator.
7. The refrigeration cycle apparatus according to any one of Claims 1 to 3, further comprising:
a flow passage connecting the radiator to the positive displacement fluid machine
so that the refrigerant that has flowed out of the radiator is supplied to the positive
displacement fluid machine;
a branch flow passage having an upstream end connected to the flow passage between
the radiator and the positive displacement fluid machine;
a decompression valve provided on the branch flow passage; and
a second evaporator to which a downstream end of the branch flow passage is connected,
wherein the injection flow passage connects the second evaporator to the positive
displacement fluid machine so that the refrigerant that has flowed out of the second
evaporator is supplied to the positive displacement fluid machine as the refrigerant
having the third pressure.
8. The refrigeration cycle apparatus according to claim 7, wherein
assuming that the evaporator for heating the refrigerant discharged from the positive
displacement fluid machine is a first evaporator,
the refrigeration cycle apparatus further comprises a flow passage, the flow passage
connecting the first evaporator to the compressor so that the refrigerant heated in
the first evaporator is supplied to the compressor, and
the first evaporator and the second evaporator are disposed respectively on an upstream
and a downstream of a flow passage for a heat medium so that the heat medium that
has heated the refrigerant in the first evaporator flows into the second evaporator.
9. The refrigeration cycle apparatus according to any one of Claims 1 to 8, wherein the
refrigerant to be supplied to the positive displacement fluid machine through the
injection flow passage is a gas refrigerant.
10. The refrigeration cycle apparatus according to any one of Claims 1 to 9, wherein the
refrigerant is carbon dioxide.
11. A hot water supply appliance comprising the refrigeration cycle apparatus according
to any one of Claims 1 to 10.
12. A hot water heater comprising the refrigeration cycle apparatus according to any one
of Claims 1 to 10.